JP2009174643A - Automatic transmission - Google Patents

Automatic transmission Download PDF

Info

Publication number
JP2009174643A
JP2009174643A JP2008014026A JP2008014026A JP2009174643A JP 2009174643 A JP2009174643 A JP 2009174643A JP 2008014026 A JP2008014026 A JP 2008014026A JP 2008014026 A JP2008014026 A JP 2008014026A JP 2009174643 A JP2009174643 A JP 2009174643A
Authority
JP
Japan
Prior art keywords
gear
planetary gear
state
speed
vertical line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
JP2008014026A
Other languages
Japanese (ja)
Inventor
Noriaki Saito
憲明 斉藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Honda Motor Co Ltd
Original Assignee
Honda Motor Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Honda Motor Co Ltd filed Critical Honda Motor Co Ltd
Priority to JP2008014026A priority Critical patent/JP2009174643A/en
Publication of JP2009174643A publication Critical patent/JP2009174643A/en
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • F16H2200/2025—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 5 connections
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means

Landscapes

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

Abstract

<P>PROBLEM TO BE SOLVED: To reduce friction losses by disengaged engagement elements by engaging three engagement elements in each speed change stage in an automatic transmission comprising a planetary gear for deceleration, a double planetary gear for speed change, and six engagement elements. <P>SOLUTION: Four elements of the double planetary gear 5 for speed change are defined as second, third and fourth elements in the order in a velocity diagram, three elements of the planetary gear 4 for deceleration are defined as fifth, sixth and seventh elements in the order in the velocity diagram, and the first element Sm1 is connected to the sixth element Cf. There are provided first, second and third engagement elements C1, C2, C3 for respectively connecting an input member 2 to the fifth element Sf, the second element Cm, and the fourth element Sms, a fourth engagement element C4 for connecting the second element Cm to the seventh element Rf, a fifth engagement element B1 for fixing the fifth element Sf, and a sixth engagement element B2 for fixing the seventh element Rf. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、入力部材の回転を複数段に変速して出力部材に伝達する変速用の複式プラネタリギヤを備える自動変速機に関する。   The present invention relates to an automatic transmission provided with a shift type planetary gear for shifting the rotation of an input member to a plurality of stages and transmitting it to an output member.

従来、特許文献１により、減速用プラネタリギヤと変速用複式プラネタリギヤと６個の係合要素とを用いて、前進８段の変速を行うことができるようにした自動変速機が知られている。このもので変速用複式プラネタリギヤは、２つのプラネタリギヤのサンギヤ、キャリア及びリングギアの一部を互いに連結することで構成される４つの回転要素を有する。例えば、一方のプラネタリギヤのサンギヤと他方のプラネタリギヤのキャリアとを連結することで構成される第１回転要素と、一方のプラネタリギヤのキャリアと他方のプラネタリギヤのリングギヤとを連結することで構成される第２回転要素と、一方のプラネタリギヤのリングギヤから成る第３回転要素と、他方の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乃至第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回転要素が出力部材に連結される。   Conventionally, Patent Document 1 discloses an automatic transmission that can perform a forward eight-speed shift using a speed reduction planetary gear, a speed change double planetary gear, and six engagement elements. The double planetary gear for shifting has four rotating elements configured by connecting parts of the sun gear, the carrier, and the ring gear of the two planetary gears to each other. For example, a first rotating element configured by connecting a sun gear of one planetary gear and a carrier of the other planetary gear, and a second configured by connecting a carrier of one planetary gear and a ring gear of the other planetary gear. A rotating element; a third rotating element formed of a ring gear of one planetary gear; and a fourth rotating element formed of a sun gear of the other 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 coupled to the output member.

また、係合要素として、入力部材の回転を減速用プラネタリギヤを介して第４回転要素に伝達す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、入力部材の回転を減速用プラネタリギヤを介して第１回転要素に伝達する状態とこの伝達を断つ状態とに切換自在な第２クラッチと、入力部材と第２回転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クラッチと、入力部材と第１回転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 engaging element, a first clutch that can be switched between a state in which the rotation of the input member is transmitted to the fourth rotating element via the speed reduction planetary gear and a state in which the transmission is cut off, and a speed reduction planetary gear for the rotation of the input member A second clutch that can be switched between a state of transmitting to the first rotating element via the first and a state of disconnecting the transmission, a state of connecting the input member and the second rotating element, and a state of disconnecting the connection. A third clutch, a fourth clutch that can be switched between a state in which the input member and the first rotating element are connected to each other, and a state in which the connection is disconnected; a state in which the first rotating element is fixed to the transmission case; A first brake that can be switched to a state of being engaged, and a second brake that is switchable to a state of fixing the second rotating element to the transmission case and a state of releasing the fixing.

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２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４クラッチとを係合することで４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５速段が確立され、第３クラッチと第４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３クラッチとを係合することで７速段が確立され、第３クラッチと第１ブレーキとを係合することで８速段が確立される。
特開２００３−１３０１５２号公報（図１、図２） 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 gear is established by engaging the first and second clutches, the fourth gear is established by engaging the first and fourth clutches, and the first and third clutches are engaged. The fifth gear is established by engaging, the sixth gear is established by engaging the third and fourth clutches, and the seventh gear is established by engaging the second and third clutches. Is established, and the eighth gear is established by engaging the third clutch and the first brake.
JP2003-130152A (FIGS. 1 and 2)

上記従来例のものでは、各変速段において係合する係合要素の数が２個になる。そのため、解放している残りの４個の係合要素の引き摺りによるフリクションロスが大きくなり、変速機の効率が悪化する不具合がある。   In the above conventional example, the number of engaging elements to be engaged at each shift stage is two. For this reason, there is a problem that the friction loss due to dragging of the remaining four engagement elements that have been released increases and the efficiency of the transmission deteriorates.

本発明は、以上の点に鑑み、６個の係合要素のうち各変速段において３個の係合要素を係合させて、解放している係合要素によるフリクションロスを低減できるようにした自動変速機を提供することをその課題としている。   In view of the above points, the present invention allows three engagement elements to be engaged at each shift stage among the six engagement elements to reduce the friction loss due to the released engagement elements. The problem is to provide an automatic transmission.

上記課題を解決するために、本願の第１発明は、入力部材の回転を変速機ケース内に配置した減速用プラネタリギヤと変速用複式プラネタリギヤとを介して複数段に変速して出力部材に伝達する自動変速機であって、変速用複式プラネタリギヤは、速度線図においてギヤ比に対応する間隔で並ぶ４つの回転要素を有し、これら回転要素を速度線図における並び順に夫々第１要素、第２要素、第３要素及び第４要素とし、減速用プラネタリギヤのサンギヤ、リングギヤ及びキャリアから成る３つの要素を、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５要素、第６要素及び第７要素として、第１要素と第６要素とが連結されると共に、第３要素が出力部材に連結され、入力部材と第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１係合要素と、入力部材と第２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、入力部材と第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３係合要素と、第２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、第７要素を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第６係合要素とを備えることを特徴とする。   In order to solve the above-mentioned problem, the first invention of the present application shifts the rotation of the input member to a plurality of stages via a speed reduction planetary gear and a speed change planetary gear arranged in the transmission case, and transmits them to the output member. In the automatic transmission, the dual planetary gear for shifting has four rotating elements arranged at intervals corresponding to the gear ratio in the speed diagram, and these rotating elements are arranged in the order of arrangement in the speed diagram, respectively. The third element, the third element, and the fourth element, and the three elements including the sun gear, the ring gear, and the carrier of the speed reduction planetary gear, are arranged in the order corresponding to the gear ratio in the speed diagram, respectively, in the order of arrangement. As the seventh element, the first element and the sixth element are connected, the third element is connected to the output member, the input member and the fifth element are connected, and the connection is broken. The first engaging element, which can be switched between, the input member and the second element are connected, and the second engaging element which is switchable between the state where the connection is disconnected and the state where the connection is broken, and the input member and the fourth element are connected. A third engagement element that is switchable between a state and a state in which this connection is cut off, a fourth engagement element that is switchable between a state in which the second element and the seventh element are connected, and a state in which this connection is cut off, A fifth engagement element that can be switched between a state in which the five elements are fixed to the transmission case and a state in which the fixing is released, and a state in which the seventh element is fixed to the transmission case and a state in which the fixing is released are switched. And a free sixth engaging element.

また、本願の第２発明は、上記第１発明の減速用プラネタリギヤを減速用複式プラネタリギヤに置換したものであり、変速用複式プラネタリギヤの４つの回転要素を速度線図における並び順に夫々第１要素、第２要素、第３要素及び第４要素とし、減速用複式プラネタリギヤの４つの回転要素を速度線図における並び順に夫々第５要素、第６要素、第７要素及び第８要素として、第１要素と第６要素とが連結されると共に、第３要素が出力部材に連結され、入力部材と第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１係合要素と、入力部材と第２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、入力部材と第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３係合要素と、第２要素と第８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７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、第８要素を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第６係合要素とを備えることを特徴とする。   Further, the second invention of the present application is obtained by replacing the speed reduction planetary gear of the first invention with a speed reduction double planetary gear. The second element, the third element, and the fourth element, and the four rotating elements of the deceleration type planetary gear are arranged in the speed diagram in the order of arrangement as the fifth element, the sixth element, the seventh element, and the eighth element, respectively. And the sixth element are connected, the third element is connected to the output member, and the first engagement element is switchable between a state of connecting the input member and the fifth element and a state of disconnecting the connection, Switchable between a state where the input member and the second element are connected and a state where the connection is cut off, a state where the input member and the fourth element are connected and a state where the connection is cut off. A third engagement element and a second Switchable between a state where the element and the eighth element are connected and a state where the connection is cut off, a fourth engaging element, a state where the seventh element is fixed to the transmission case, and a state where the fixing is released A fifth engagement element, and a sixth engagement element switchable between a state in which the eighth element is fixed to the transmission case and a state in which the fixation is released.

第１発明によれば、後述する実施形態の説明から明らかなように、前進８段の変速を行うことができると共に、第１乃至第６の６個の係合要素のうち各変速段において３個の係合要素が係合することになる。また、第２発明によれば、後述する実施形態の説明から明らかなように、前進１０段の変速を行うことができると共に、第１乃至第６の６個の係合要素のうち各変速段において３個の係合要素が係合することになる。そして、第１発明と第２発明の何れにおいても、各変速段で解放している係合要素の数は３個になる。従って、４個の係合要素が解放している従来例のものに比し、解放している係合要素によるフリクションロスを低減でき、変速機の効率が向上する。   According to the first invention, as will be apparent from the description of the embodiment described later, it is possible to perform eight forward shifts, and among the first to sixth six engagement elements, three shift gears are provided. The engagement elements are engaged. Further, according to the second invention, as will be apparent from the description of the embodiment described later, it is possible to perform the forward 10-speed shift, and among each of the first to sixth engaging elements, the respective shift speeds. In this case, three engaging elements are engaged. In both the first invention and the second invention, the number of engagement elements released at each shift stage is three. Therefore, as compared with the conventional example in which four engagement elements are released, the friction loss due to the released engagement elements can be reduced, and the efficiency of the transmission 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実施形態は、変速機ケース１内に回転自在に軸支した、図外のエンジン等の動力源に連結される入力部材たる入力軸２と、入力軸２と同心に配置された出力部材たる出力ギヤ３とを備えている。出力ギヤ３の回転は、図外のデファレンシャルギヤを介して車両の左右の駆動輪に伝達される。   Fig.1 (a) has shown 1st Embodiment of the automatic transmission of this invention. In the first embodiment, an input shaft 2 that is rotatably supported in a transmission case 1 and that is connected to a power source such as an engine (not shown), and an output that is arranged concentrically with the input shaft 2. And an output gear 3 as a member. The rotation of the output gear 3 is transmitted to the left and right drive wheels of the vehicle via a differential gear (not shown).

また、変速機ケース１内には、入力軸２の周りに位置させて、減速用プラネタリギヤ４と、変速用複式プラネタリギヤ５とが配置されている。変速用複式プラネタリギヤ５は、第１サンギヤＳｍｌと、第２サンギヤＳｍｓと、リングギヤＲｍと、第１サンギヤＳｍｌとリングギヤＲｍとに噛合する第１ピニオンＰｍｌと第２サンギヤＳｍｓと第１ピニオンＰｍｌとに噛合する第２ピニオンＰｍｓとを自転及び公転自在に支持するキャリアＣｍとを有するラビニヨ型のプラネタリギヤで構成されている。   Further, in the transmission case 1, a speed reduction planetary gear 4 and a speed change double planetary gear 5 are arranged around the input shaft 2. The shift type planetary gear 5 includes a first sun gear Sml, a second sun gear Sms, a ring gear Rm, a first pinion Pml, a second sun gear Sms, and a first pinion Pml that mesh with the first sun gear Sml and the ring gear Rm. It is composed of a Ravigneaux type planetary gear having a carrier Cm that supports the meshing second pinion Pms so as to rotate and revolve.

図２の下段に示す変速用複式プラネタリギヤ５の速度線図（プラネタリギヤを構成する複数の回転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、変速用複式プラネタリギヤ５の第１サンギヤＳｍｌ、第２サンギヤＳｍｓ、リングギヤＲｍ及びキャリアＣｍから成る４個の回転要素を、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、第３要素及び第４要素とすると、第１要素は第１サンギヤＳｍｌ、第２要素はキャリアＣｍ、第３要素はリングギヤＲｍ、第４要素は第２サンギヤＳｍｓになる。ここで、リングギヤＲｍと第１サンギヤＳｍｌとのギヤ比（リングギヤＲｍの歯数／第１サンギヤＳｍｌの歯数）をｊ１、リングギヤＲｍと第２サンギヤＳｍｓとのギヤ比（リングギヤＲｍの歯数／第２サンギヤＳｍｓの歯数）をｊ２として、第１サンギヤＳｍｌが位置する縦線Ｙ２とキャリアＣｍが位置する縦線Ｙ３間の間隔と、縦線Ｙ３とリングギヤＲｍが位置する縦線Ｙ４間の間隔と、縦線Ｙ４と第２サンギヤＳｍｓが位置する縦線Ｙ５間の間隔の比はｊ１：１：ｊ２−１に設定されている。また、速度線図の下の横線と上の横線は夫々回転速度が「０」と「１」（入力軸２と同じ回転速度）であることを示している。   Referring to the speed diagram of the speed-changing planetary gear 5 shown in the lower part of FIG. 2 (the speed of the plurality of rotating elements constituting the planetary gear can be represented by straight lines), the first sun gear of the speed-changing planetary gear 5 is shown. Four rotating elements consisting of Sml, second sun gear Sms, ring gear Rm and carrier Cm are arranged in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram from the left side, the first element, second element, third element and Assuming the fourth element, the first element is the first sun gear Sml, the second element is the carrier Cm, the third element is the ring gear Rm, and the fourth element is the second sun gear Sms. Here, the gear ratio between the ring gear Rm and the first sun gear Sml (the number of teeth of the ring gear Rm / the number of teeth of the first sun gear Sml) is j1, and the gear ratio between the ring gear Rm and the second sun gear Sms (the number of teeth of the ring gear Rm / J2 as the number of teeth of the second sun gear Sms), the interval between the vertical line Y2 where the first sun gear Sml is located and the vertical line Y3 where the carrier Cm is located, and between the vertical line Y3 and the vertical line Y4 where the ring gear Rm is located. The ratio of the interval and the interval between the vertical line Y4 and the vertical line Y5 where the second sun gear Sms is located is set to j1: 1: j2-1. Further, the lower horizontal line and the upper horizontal line of the velocity diagram indicate that the rotational speeds are “0” and “1” (the same rotational speed as that of the input shaft 2), respectively.

減速用プラネタリギヤ４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とから成る単式プラネタリギヤで構成されている。図２の上段に示す減速用プラネタリギヤ４の速度線図を参照して、減速用プラネタリギヤ４のサンギヤＳｆ、リングギヤＲｆ及びキャリアＣｆから成る３つの要素を、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５要素、第６要素及び第７要素とすると、第５要素はサンギヤＳｆ、第６要素はキャリアＣｆ、第７要素はリングギヤＲｆになる。尚、サンギヤＳｆとキャリアＣｆ間の間隔とキャリアＣｆとリングギヤＲｆ間の間隔との比は、減速用プラネタリギヤ４のギヤ比（リングギヤＲｆの歯数／サンギヤＳｆの歯数）をｉとして、ｉ：１に設定されている。そして、後述する第１クラッチＣ１と第２ブレーキＢ２との係合によりサンギヤＳｆの回転速度が「１」、リングギヤＲｆの回転速度が「０」になったときの減速用プラネタリギヤ４の出力速度（キャリアＣｆの回転速度）Ｎ１は１／（ｉ＋１）になる。   The reduction planetary gear 4 is constituted by a single planetary gear including a sun gear Sf, a ring gear Rf, and a carrier Cf that supports the pinion Pf meshing with the sun gear Sf and the ring gear Rf so as to be capable of rotating and revolving. Referring to the speed diagram of the speed reduction planetary gear 4 shown in the upper part of FIG. 2, the three elements including the sun gear Sf, the ring gear Rf, and the carrier Cf of the speed reduction planetary gear 4 are arranged at intervals corresponding to the gear ratio in the speed diagram. The fifth element is the sun gear Sf, the sixth element is the carrier Cf, and the seventh element is the ring gear Rf. 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: where the gear ratio of the speed reduction planetary gear 4 (number of teeth of the ring gear Rf / number of teeth of the sun gear Sf) is i: 1 is set. The output speed of the planetary gear 4 for deceleration when the rotational speed of the sun gear Sf becomes “1” and the rotational speed of the ring gear Rf becomes “0” due to the engagement of the first clutch C1 and the second brake B2, which will be described later. The rotation speed N1 of the carrier Cf is 1 / (i + 1).

ここで、本実施形態では、変速用複式プラネタリギヤ５の第１サンギヤＳｍｌ（第１要素）と減速用プラネタリギヤ４のキャリアＣｆ（第６要素）とを連結すると共に、変速用複式プラネタリギヤ５のリングギヤＲｍ（第３要素）を出力ギヤ３に連結している。また、係合要素として、入力軸２と減速用プラネタリギヤ４のサンギヤＳｆ（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１係合要素たる第１クラッチＣ１と、入力軸２と変速用複式プラネタリギヤ５のキャリアＣｍ（第２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、入力軸２と変速用複式プラネタリギヤ５の第２サンギヤＳｍｓ（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３係合要素たる第３クラッチＣ３と、変速用複式プラネタリギヤ５のキャリアＣｍ（第２要素）と減速用プラネタリギヤ４のリングギヤＲｆ（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４クラッチＣ４と、減速用プラネタリギヤ４のサンギヤＳｆ（第５要素）を変速機ケース１に固定する状態とこの固定を解除する状態とに切換自在な第５係合要素たる第１ブレーキＢ１と、減速機用プラネタリギヤ４のリングギヤＲｆ（第７要素）を変速機ケース１に固定する状態とこの固定を解除する状態とに切換自在な第６係合要素たる第２ブレーキＢ２とを備えている。   Here, in the present embodiment, the first sun gear Sml (first element) of the speed-changing planetary gear 5 and the carrier Cf (sixth element) of the speed-down planetary gear 4 are connected, and the ring gear Rm of the speed-changing planetary gear 5 is also connected. The (third element) is connected to the output gear 3. Further, as an engagement element, a first clutch C1 as a first engagement element that can be switched between a state in which the input shaft 2 and the sun gear Sf (fifth element) of the speed reduction planetary gear 4 are connected and a state in which the connection is cut off. A second clutch C2 as a second engagement element that can be switched between a state in which the input shaft 2 and the carrier Cm (second element) of the transmission-use planetary gear 5 are connected and a state in which the connection is cut off; The third clutch C3, which is a third engagement element that can be switched between a state in which the second sun gear Sms (fourth element) of the transmission-use planetary gear 5 is connected and a state in which the connection is cut off, and a carrier of the transmission-use planetary gear 5 A fourth clutch C4 as a fourth engagement element that can be switched between a state in which Cm (second element) and the ring gear Rf (seventh element) of the speed reduction planetary gear 4 are connected and a state in which the connection is disconnected; A first brake B1, which is a fifth engagement element that can be switched between a state in which the sun gear Sf (fifth element) of the spur gear 4 is fixed to the transmission case 1 and a state in which the fixing is released, and a ring gear of the planetary gear 4 for the speed reducer. A second brake B2 is provided as a sixth engaging element that can be switched between a state in which Rf (seventh element) is fixed to the transmission case 1 and a state in which the fixing is released.

上記の如く減速用プラネタリギヤ４のキャリアＣｆと変速用複式プラネタリギヤ５の第１サンギヤＳｍｌとを連結することにより、図２の下段に示す複式プラネタリギヤ５の速度線図において、減速用プラネタリギヤ４のキャリアＣｆは、変速用複式プラネタリギヤ５の第１サンギヤＳｍｌと同一の縦線Ｙ２上に位置する。そして、第４クラッチＣ４を係合させると、減速用プラネタリギヤ４のリングギヤＲｆが変速用複式プラネタリギヤ５のキャリアＣｍと同一の縦線Ｙ３上に位置し、減速用プラネタリギヤ４のサンギヤＳｆは、縦線Ｙ２と縦線Ｙ３間の間隔のｉ倍だけ縦線Ｙ２から左側に離れた縦線Ｙ１上に位置する。   By connecting the carrier Cf of the speed reduction planetary gear 4 and the first sun gear Sml of the speed change double planetary gear 5 as described above, the carrier Cf of the speed reduction planetary gear 4 in the speed diagram of the double planetary gear 5 shown in the lower part of FIG. Is located on the same vertical line Y2 as the first sun gear Sml of the double planetary gear 5 for shifting. When the fourth clutch C4 is engaged, the ring gear Rf of the speed reduction planetary gear 4 is positioned on the same vertical line Y3 as the carrier Cm of the speed change double planetary gear 5, and the sun gear Sf of the speed reduction planetary gear 4 is It is located on the vertical line Y1 that is separated from the vertical line Y2 to the left by i times the interval between Y2 and the vertical line Y3.

本実施形態では、第３クラッチＣ３と第４クラッチＣ４と第２ブレーキＢ２とを係合させると、縦線Ｙ３での回転速度が「０」、縦線Ｙ５での回転速度が「１」になり、出力ギヤ３に連結される変速用複式プラネタリギヤ５のリングギヤＲｍが位置する縦線Ｙ４での回転速度は「１ｓｔ」になる。即ち、１速段が確立される。   In this embodiment, when the third clutch C3, the fourth clutch C4, and the second brake B2 are engaged, the rotational speed at the vertical line Y3 is “0”, and the rotational speed at the vertical line Y5 is “1”. Thus, the rotational speed at the vertical line Y4 where the ring gear Rm of the shift type planetary gear 5 connected to the output gear 3 is located is “1st”. That is, the first gear is established.

第３クラッチＣ３と第１ブレーキＢ１と第２ブレーキＢ２とを係合させると、縦線Ｙ２での回転速度が「０」、縦線Ｙ５での回転速度が「１」になり、縦線Ｙ４での回転速度は「２ｎｄ」になる。即ち、２速段が確立される。   When the third clutch C3, the first brake B1, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is "0", the rotational speed at the vertical line Y5 is "1", and the vertical line Y4 The rotation speed at is 2nd. That is, the second gear is established.

第３クラッチＣ３と第４クラッチＣ４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「０」、縦線Ｙ５での回転速度が「１」になり、縦線Ｙ４での回転速度は「３ｒｄ」になる。即ち、３速段が確立される。   When the third clutch C3, the fourth clutch C4, and the first brake B1 are engaged, the rotational speed at the vertical line Y1 is "0", the rotational speed at the vertical line Y5 is "1", and the vertical line Y4 The rotation speed at is “3rd”. That is, the third gear is established.

第１クラッチＣ１と第３クラッチＣ３と第２ブレーキＢ２とを係合させると、縦線Ｙ２での回転速度がＮ１、縦線Ｙ５での回転速度が「１」になり、縦線Ｙ４での回転速度は「４ｔｈ」になる。即ち、４速段が確立される。   When the first clutch C1, the third clutch C3, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y5 is “1”, and the rotational speed at the vertical line Y4 is The rotation speed is “4th”. That is, the fourth gear is established.

第２クラッチＣ２と第３クラッチＣ３とを係合させると、縦線Ｙ３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「５ｔｈ」になる。即ち、５速段が確立される。尚、第１ブレーキＢ１と第２ブレーキＢ２との何れか一方を係合させておいても、第２クラッチＣ２と第３クラッチＣ３とを係合させることで５速段が確立される。   When the second clutch C2 and the third clutch C3 are engaged, the rotational speed at the vertical line Y3 and the rotational speed at the vertical line Y5 are both “1”, and the rotational speed at the vertical line Y4 is also “1”. "5th". That is, the fifth gear is established. Even if one of the first brake B1 and the second brake B2 is engaged, the fifth gear is established by engaging the second clutch C2 and the third clutch C3.

第２クラッチＣ２と第４クラッチＣ４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「０」、縦線Ｙ３での回転速度が「１」になり、縦線Ｙ４での回転速度は「６ｔｈ」になる。即ち、６速段が確立される。   When the second clutch C2, the fourth clutch C4, and the first brake B1 are engaged, the rotational speed at the vertical line Y1 is "0", the rotational speed at the vertical line Y3 is "1", and the vertical line Y4 The rotation speed at is “6th”. That is, the sixth gear is established.

第１クラッチＣ１と第２クラッチＣ２と第２ブレーキＢ２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」になり、縦線Ｙ４での回転速度は「７ｔｈ」になる。即ち、７速段が確立される。   When the first clutch C1, the second clutch C2, and the second brake B2 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 rotation speed is “7th”. That is, the seventh gear is established.

第２クラッチＣ２と第１ブレーキＢ１と第２ブレーキＢ２とを係合させると、縦線Ｙ２での回転速度が「０」、縦線Ｙ３での回転速度が「１」になり、縦線Ｙ４での回転速度は「８ｔｈ」になる。即ち、８速段が確立される。   When the second clutch C2, the first brake B1, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is "0", the rotational speed at the vertical line Y3 is "1", and the vertical line Y4 The rotation speed at is “8th”. That is, the eighth gear is established.

第１クラッチＣ１と第４クラッチＣ４と第２ブレーキＢ２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」になり、縦線Ｙ４での回転速度はマイナスの「Ｒｅｖ」になる。即ち、後進段が確立される。   When the first clutch C1, the fourth clutch C4, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y3 is “0”, and the rotational speed at the vertical line Y4 is The rotation speed becomes negative “Rev”. That is, the reverse gear is established.

図１（ｂ）は、上述した各変速段とクラッチＣ１〜Ｃ４、ブレーキＢ１，Ｂ２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。尚、５速段における第１ブレーキＢ１と第２ブレーキＢ２の（○）は、第１ブレーキＢ１と第２ブレーキＢ２とのいずれか一方を係合させることを表している。ここで、４速段では、第１クラッチＣ１と５速段でも係合する第３クラッチＣ３と第２ブレーキＢ２とが係合するため、第１クラッチＣ１を解放して第２クラッチＣ２を係合させることにより、４速段から５速段にアップシフトされる。また、６速段では、５速段でも係合する第２クラッチＣ２と第４クラッチＣ４と第１ブレーキＢ１とが係合するため、５速段へのアップシフト後に第２ブレーキＢ２に代えて第１ブレーキＢ１を係合させておけば、第３クラッチＣ３を解放して第４クラッチを係合させることにより、５速段から６速段にアップされる。   FIG. 1B is a diagram collectively showing the relationship between the above-described shift speeds and the engagement states of the clutches C1 to C4 and the brakes B1 and B2, and ◯ represents engagement. Note that (◯) of the first brake B1 and the second brake B2 at the fifth speed represents that either one of the first brake B1 and the second brake B2 is engaged. Here, in the fourth speed, the third clutch C3 and the second brake B2 that are engaged even in the first clutch C1 and the fifth speed are engaged, so the first clutch C1 is released and the second clutch C2 is engaged. By combining, the upshift is performed from the fourth gear to the fifth gear. At the sixth speed, the second clutch C2, the fourth clutch C4, and the first brake B1 that are engaged even at the fifth speed are engaged, so that the second brake B2 is replaced after the upshift to the fifth speed. If the first brake B1 is engaged, the third clutch C3 is released and the fourth clutch is engaged, so that the fifth speed is increased to the sixth speed.

また、図１（ｂ）は、上述したギヤ比ｉ，ｊ１，ｊ２を夫々ｉ＝１．３、ｊ１＝１．４、ｊ２＝３．５とした場合における各変速段のギヤレシオ（入力軸２の回転速度／出力ギヤ３の回転速度）も示している。これによれば、公比（各変速段間のギヤレシオの比）が適切になると共に、レンジ（一速レシオ／８速レシオ）も適切になる。   FIG. 1B shows the gear ratio (input shaft 2) of each gear position when the gear ratios i, j1, and j2 are i = 1.3, j1 = 1.4, and j2 = 3.5, respectively. (Rotational speed of the output gear 3 / rotational speed of the output gear 3). According to this, the common ratio (ratio of gear ratios between gears) becomes appropriate, and the range (first speed ratio / 8 speed ratio) becomes appropriate.

また、本実施形態では、６個の係合要素のうち各変速段において３個の係合要素が係合するため、各変速段で解放している係合要素の数は３個になる。従って、４個の係合要素が解放している上記従来例のものに比し、解放している係合要素によるフリクションロスを低減でき、変速機の効率が向上する。   In the present embodiment, among the six engagement elements, three engagement elements are engaged at each shift speed, so the number of engagement elements released at each shift speed is three. Therefore, compared to the conventional example in which the four engagement elements are released, the friction loss due to the released engagement elements can be reduced, and the efficiency of the transmission is improved.

ところで、上記第１実施形態では、変速用複式プラネタリギヤ５をラビニヨ型プラネタリギヤで構成したが、これに限られない。例えば、図３に示す第２実施形態の如く、サンギヤＳｍ１と、リングギヤＲｍ１と、サンギヤＳｍ１とリングギヤＲｍ１とに噛合するピニオンＰｍ１を自転及び公転自在に支持するキャリアＣｍ１とを有する単式プラネタリギヤから成る第１プラネタリギヤ５１と、サンギヤＳｍ２と、リングギヤＲｍ２と、サンギヤＳｍ２とリングギヤＲｍ２とに噛合するピニオンＰｍ２を自転及び公転自在に支持するキャリアＣｍ２とを有する単式プラネタリギヤから成る第２プラネタリギヤ５２とを用い、第１プラネタリギヤ５１のキャリアＣｍ１と第２プラネタリギヤ５２のリングギヤＲｍ２とを連結すると共に、第１プラネタリギヤ５１のリングギヤＲｍ１と第２プラネタリギヤ５２のキャリアＣｍ２とを連結して変速用複式プラネタリギヤ５を構成しても良い。   By the way, in the said 1st Embodiment, although the double planetary gear 5 for transmission was comprised by the Ravigneaux type planetary gear, it is not restricted to this. For example, as in the second embodiment shown in FIG. 3, a first planetary gear having a sun gear Sm1, a ring gear Rm1, and a carrier Cm1 that supports a pinion Pm1 meshing with the sun gear Sm1 and the ring gear Rm1 so as to rotate and revolve. A first planetary gear 51, a sun gear Sm2, a ring gear Rm2, and a second planetary gear 52 composed of a single planetary gear having a carrier Cm2 that supports the sun gear Sm2 and the pinion Pm2 meshing with the ring gear Rm2 so as to rotate and revolve. The carrier Cm1 of the first planetary gear 51 and the ring gear Rm2 of the second planetary gear 52 are connected, and the ring gear Rm1 of the first planetary gear 51 and the carrier Cm2 of the second planetary gear 52 are connected to form the transmission-use planetary gear 5. It may be.

第２実施形態の変速用複式プラネタリギヤ５は、第１プラネタリギヤ５１のサンギヤＳｍ１と、第２プラネタリギヤ５２のサンギヤＳｍ２と、第１プラネタリギヤ５１のキャリアＣｍ１と第２プラネタリギヤ５２のリングギヤＲｍ２との連結体（第１連結体）と、第１プラネタリギヤ５１のリングギヤＲｍ１と第２プラネタリギヤ５２のキャリアＣｍ２との連結体（第２連結体）とから成る４つの回転要素を有することになる。そして、これら回転要素を、図４の下段に示す速度線図におけるギア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、第３要素及び第４要素とすると、第１要素は第１プラネタリギヤ５１のサンギヤＳｍ１、第２要素は第１連結体Ｃｍ１，Ｒｍ２、第３要素は第２連結体Ｒｍ１，Ｃｍ２、第４要素は第２プラネタリギヤ５２のサンギヤＳｍ２になる。尚、第１プラネタリギヤ５１のギヤ比をｊ１、第２プラネタリギヤ５２のギヤ比をｊ２として、第１プラネタリギヤ５１のサンギヤＳｍ１が位置する縦線Ｙ２と第１連結体Ｃｍ１，Ｒｍ２が位置する縦線Ｙ３間の間隔と、縦線Ｙ３と第２連結体Ｒｍ１，Ｃｍ２が位置する縦線Ｙ４間の間隔と、縦線Ｙ４と第２プラネタリギヤ５２のサンギヤＳｍ２が位置する縦線Ｙ５間の間隔との比はｊ１：１：ｊ２に設定されている。   The double planetary gear 5 for shifting according to the second embodiment includes a sun gear Sm1 of the first planetary gear 51, a sun gear Sm2 of the second planetary gear 52, a carrier Cm1 of the first planetary gear 51, and a ring gear Rm2 of the second planetary gear 52 ( The first rotating body includes four rotating elements including a first connecting body and a connecting body (second connecting body) of the ring gear Rm1 of the first planetary gear 51 and the carrier Cm2 of the second planetary gear 52. Then, assuming that these rotating elements are a first element, a second element, a third element, and a fourth element from the left in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram shown in the lower part of FIG. The element is the sun gear Sm1 of the first planetary gear 51, the second element is the first coupling bodies Cm1 and Rm2, the third element is the second coupling bodies Rm1 and Cm2, and the fourth element is the sun gear Sm2 of the second planetary gear 52. Note that the first planetary gear 51 has a gear ratio j1 and the second planetary gear 52 has a gear ratio j2, and the vertical line Y2 where the sun gear Sm1 of the first planetary gear 51 is located and the vertical line Y3 where the first coupling bodies Cm1 and Rm2 are located. And the distance between the vertical line Y3 and the vertical line Y4 where the second coupling bodies Rm1 and Cm2 are located, and the distance between the vertical line Y4 and the vertical line Y5 where the sun gear Sm2 of the second planetary gear 52 is located Is set to j1: 1: j2.

第２実施形態では、第１プラネタリギヤ５１のサンギヤＳｍ１（第１要素）と減速用プラネタリギヤ４のキャリアＣｆ（第６要素）とを連結すると共に、第２連結体Ｒｍ１，Ｃｍ２（第３要素）を出力ギヤ３に連結している。また、入力軸２を、第２クラッチＣ２を介して第１連結体Ｃｍ１，Ｒｍ２（第２要素）に連結すると共に、第３クラッチＣ３を介して第２プラネタリギヤ５２のサンギヤＳｍ２（第４要素）に連結し、更に、第１連結体Ｃｍ１，Ｒｍ２（第２要素）を第４クラッチＣ４を介して減速用プラネタリギヤ４のリングギヤＲｆ（第７要素）に連結している。他の構成は上記第１実施形態と同一である。   In the second embodiment, the sun gear Sm1 (first element) of the first planetary gear 51 and the carrier Cf (sixth element) of the speed reduction planetary gear 4 are coupled, and the second coupling bodies Rm1, Cm2 (third element) are coupled. It is connected to the output gear 3. The input shaft 2 is connected to the first coupling bodies Cm1, Rm2 (second element) via the second clutch C2, and the sun gear Sm2 (fourth element) of the second planetary gear 52 is connected via the third clutch C3. Further, the first coupling bodies Cm1 and Rm2 (second element) are coupled to the ring gear Rf (seventh element) of the speed reduction planetary gear 4 via the fourth clutch C4. Other configurations are the same as those in the first embodiment.

第２実施形態のものも、前進８段、後進１段の変速が行われ、各変速段とクラッチＣ１〜Ｃ４、ブレーキＢ１，Ｂ２の係合状態との関係は図１（ｂ）に示したものと同一になる。更に、減速用プラネタリギヤ４のギヤ比ｉを１．３、第１プラネタリギヤ５１のギヤ比ｊ１を１．４、第２プラネタリギヤ５２のギヤ比ｊ２を２．５に設定すれば、各変速段のギヤレシオも図１（ｂ）に示したものと同一になる。   In the second embodiment as well, eight forward speeds and one reverse speed are shifted, and the relationship between the respective gear speeds and the engagement states of the clutches C1 to C4 and the brakes B1 and B2 is shown in FIG. To be the same. Further, if the gear ratio i of the speed reduction planetary gear 4 is set to 1.3, the gear ratio j1 of the first planetary gear 51 is set to 1.4, and the gear ratio j2 of the second planetary gear 52 is set to 2.5, the gear ratio of each gear stage is set. Is the same as that shown in FIG.

また、上記第１実施形態では、減速用プラネタリギヤ４がシングルピニオン型の単式プラネタリギヤで構成されているが、図５に示す第３実施形態や図７に示す第４実施形態のように、減速用プラネタリギヤ４を、互いに噛合すると共に一方がサンギヤＳｆに噛合し、他方がリングギヤＲｆに噛合する一対のピニオンＰｆ，Ｐｆ´をキャリアＣｆにより自転及び公転自在に支持して成るダブルピニオン型の単式プラネタリギヤで構成することも可能である。   In the first embodiment, the speed reduction planetary gear 4 is a single pinion type planetary gear. However, as in the third embodiment shown in FIG. 5 and the fourth embodiment shown in FIG. The planetary gear 4 is a double-pinion type single planetary gear that is configured to support a pair of pinions Pf and Pf ′ that mesh with each other and one meshes with the sun gear Sf and the other mesh with the ring gear Rf so as to rotate and revolve by the carrier Cf. It is also possible to configure.

ここで、第３実施形態の減速用プラネタリギヤ４のサンギヤＳｆ、リングギヤＲｆ及びキャリアＣｆから成る３つの要素を、図６の上段に示す速度線図におけるギヤ比に対応する並び順に左側から夫々第５要素、第６要素及び第７要素とすると、第５要素はサンギヤＳｆ、第６要素はリングギヤＲｆ、第７要素はキャリアＣｆになる。尚、減速用プラネタリギヤ４のギヤ比をｉとして、サンギヤＳｆとリングギヤＲｆ間の間隔とリングギヤＲｆとキャリアＣｆ間の間隔の比はｉ−１：１に設定されている。そして、サンギヤＳｆの回転速度が「１」、キャリアＣｆの回転速度が「０」であるときの減速用プラネタリギヤ４の出力速度（リングギヤＲｆの回転速度）Ｎ１は１／ｉになる。   Here, the three elements including the sun gear Sf, the ring gear Rf, and the carrier Cf of the speed reduction planetary gear 4 of the third embodiment are arranged in the order from the left side in the order corresponding to the gear ratio in the speed diagram shown in the upper part of FIG. Assuming that the element is the sixth element and the seventh element, the fifth element is the sun gear Sf, the sixth element is the ring gear Rf, and the seventh element is the carrier Cf. The gear ratio of the speed reduction planetary gear 4 is i, and the ratio of the distance between the sun gear Sf and the ring gear Rf and the distance between the ring gear Rf and the carrier Cf is set to i−1: 1. Then, when the rotational speed of the sun gear Sf is “1” and the rotational speed of the carrier Cf is “0”, the output speed (the rotational speed of the ring gear Rf) N1 of the deceleration planetary gear 4 is 1 / i.

第３実施形態では、減速用プラネタリギヤ４のリングギヤＲｆ（第６要素）を変速用複式プラネタリギヤ５の第１サンギヤＳｍｌ（第１要素）に連結し、また、減速用プラネタリギヤ４のキャリアＣｒ（第７要素）を、第４クラッチＣ４を介して変速用複式プラネタリギヤ５のキャリアＣｍ（第２要素）に連結自在とすると共に、第２ブレーキＢ２を介して変速機ケース１に固定自在としている。他の構成は上記第１実施形態と同一である。第３実施形態のものも、前進８段、後進１段の変速が行われ、各変速段とクラッチＣ１〜Ｃ４、ブレーキＢ１，Ｂ２の係合状態との関係は図１（ｂ）に示したものと同一になる。また、減速用プラネタリギヤ４のギヤ比ｉを２．３、変速用複式プラネタリギヤ５のリングギヤＲｍと第１サンギヤＳｍｌのギヤ比ｊ１を１．４、変速用複式プラネタリギヤ５のリングギヤＲｍと第２サンギヤＳｍｓのギヤ比ｊ２を３．５に設定すると、各変速段のギヤレシオは図１（ｂ）に示したものと同一になる。   In the third embodiment, the ring gear Rf (sixth element) of the speed reduction planetary gear 4 is connected to the first sun gear Sml (first element) of the speed change compound planetary gear 5, and the carrier Cr (seventh speed) of the speed reduction planetary gear 4 is connected. Element) is connectable to the carrier Cm (second element) of the shift type planetary gear 5 via the fourth clutch C4, and can be fixed to the transmission case 1 via the second brake B2. Other configurations are the same as those in the first embodiment. In the third embodiment as well, eight forward speeds and one reverse speed are changed, and the relationship between the respective gear speeds and the engagement states of the clutches C1 to C4 and the brakes B1 and B2 is shown in FIG. To be the same. Further, the gear ratio i of the speed reduction planetary gear 4 is 2.3, the gear ratio j1 of the ring gear Rm and the first sun gear Sml of the transmission double planetary gear 5 is 1.4, the ring gear Rm and the second sun gear Sms of the double planetary gear 5 for speed change. When the gear ratio j2 is set to 3.5, the gear ratios of the respective speeds are the same as those shown in FIG.

第４実施形態の減速用プラネタリギヤ４のサンギヤＳｆ、リングギヤＲｆ及びキャリアＣｆから成る３つの要素を、図８の上段に示す速度線図におけるギヤ比に対応する並び順に左側から夫々第５要素、第６要素及び第７要素とすると、第５要素はキャリアＣｆ、第６要素はリングギヤＲｆ、第７要素はサンギヤＳｆになる。尚、減速用プラネタリギヤ４のギヤ比をｉとして、キャリアＣｆとリングギヤＲｆ間の間隔とリングギヤＲｆとサンギヤＳｆ間の間隔の比は１：ｉ−１に設定されている。そして、キャリアＣｆの回転速度が「１」、サンギヤＳｆの回転速度が「０」であるときの減速用プラネタリギヤ４の出力速度（リングギヤＲｆの回転速度）Ｎ１は１／ｉになる。   Three elements including the sun gear Sf, the ring gear Rf, and the carrier Cf of the planetary gear 4 for speed reduction according to the fourth embodiment are arranged in the order corresponding to the gear ratio in the speed diagram shown in the upper part of FIG. Assuming the sixth element and the seventh element, the fifth element is the carrier Cf, the sixth element is the ring gear Rf, and the seventh element is the sun gear Sf. The gear ratio of the planetary gear 4 for reduction is i, and the ratio of the distance between the carrier Cf and the ring gear Rf and the distance between the ring gear Rf and the sun gear Sf is set to 1: i-1. Then, when the rotational speed of the carrier Cf is “1” and the rotational speed of the sun gear Sf is “0”, the output speed (the rotational speed of the ring gear Rf) N1 of the deceleration planetary gear 4 is 1 / i.

第４実施形態では、減速用プラネタリギヤ４のリングギヤＲｆ（第６要素）を変速用複式プラネタリギヤ５の第１サンギヤＳｍｌ（第１要素）に連結し、また、減速用プラネタリギヤ４のキャリアＣｆ（第５要素）を、第１クラッチＣ１を介して入力軸２に連結自在とすると共に、第１ブレーキＢ１を介して変速機ケース１に固定自在とし、更に、減速用プラネタリギヤ４のサンギヤＳｆ（第７要素）を、第４クラッチＣ４を介して変速用複式プラネタリギヤ５のキャリアＣｍ（第２要素）に連結自在とすると共に、第２ブレーキＢ２を介して変速機ケース１に固定自在としている。他の構成は上記第１実施形態と同一である。第４実施形態のものも、前進８段、後進１段の変速が行われ、各変速段とクラッチＣ１〜Ｃ４、ブレーキＢ１，Ｂ２の係合状態との関係は図１（ｂ）に示したものと同一になる。また、減速用プラネタリギヤ４のギヤ比ｉを１．７６９、変速用複式プラネタリギヤ５のリングギヤＲｍと第１サンギヤＳｍｌのギヤ比ｊ１を１．４、変速用複式プラネタリギヤ５のリングギヤＲｍと第２サンギヤＳｍｓのギヤ比ｊ２を３．５に設定すると、各変速段のギヤレシオは図１（ｂ）に示したものと同一になる。   In the fourth embodiment, the ring gear Rf (sixth element) of the speed reduction planetary gear 4 is connected to the first sun gear Sml (first element) of the speed-changing planetary gear 5, and the carrier Cf (fifth speed) of the speed reduction planetary gear 4 is connected. Element) can be connected to the input shaft 2 via the first clutch C1, and can be fixed to the transmission case 1 via the first brake B1, and the sun gear Sf (seventh element) of the planetary gear 4 for speed reduction. ) Can be connected to the carrier Cm (second element) of the shift type planetary gear 5 via the fourth clutch C4, and can be fixed to the transmission case 1 via the second brake B2. Other configurations are the same as those in the first embodiment. In the fourth embodiment as well, eight forward speeds and one reverse speed are changed, and the relationship between the respective gear speeds and the engagement states of the clutches C1 to C4 and the brakes B1 and B2 is shown in FIG. To be the same. Further, the gear ratio i of the speed reduction planetary gear 4 is 1.769, the gear ratio j1 of the ring gear Rm and the first sun gear Sml of the transmission double planetary gear 5 is 1.4, the ring gear Rm and the second sun gear Sms of the double planetary gear 5 for speed change. When the gear ratio j2 is set to 3.5, the gear ratios of the respective speeds are the same as those shown in FIG.

また、上記第２実施形態のものにおいて、減速用プラネタリギヤ４を第３実施形態や第４実施形態のようなダブルピニオン型の単式プラネタリギヤで構成することも可能である。   In the second embodiment, the speed reduction planetary gear 4 can be constituted by a double pinion type single planetary gear as in the third and fourth embodiments.

また、上記第１乃至第４実施形態は、入力軸２の周りに、一端側から順に、第２及び第３クラッチＣ２，Ｃ３と、出力ギヤ３と、変速用複式プラネタリギヤ５と、第４クラッチＣ４と、減速用プラネタリギヤ４及び第２ブレーキＢ２と、第１クラッチＣ１及び第１ブレーキＢ１とを配置したＦＦ車用の自動変速機であるが、ＦＲ車用の自動変速機にも同様に本発明を適用できる。例えば、図９に示す第５実施形態のように、入力軸２の周りに、一端（前端）側から順に、第１クラッチＣ１及び第１ブレーキＢ１と、減速用プラネタリギヤ４及び第２ブレーキＢ２と、第４クラッチＣ４と、変速用複式プラネタリギヤ５と、第２及び第３クラッチＣ２，Ｃ３とを配置し、変速用複式プラネタリギヤ５のリングギヤＲｍ（第３要素）を後方にのびる出力部材たるプロペラシャフト３´に連結しても良い。尚、第５実施形態は第１実施形態の変速機をＦＲ車用のものに変更したものであるが、第２〜第４実施形態の変速機も同様にＦＲ車用のものに変更できる。   Further, in the first to fourth embodiments, the second and third clutches C2 and C3, the output gear 3, the shift compound planetary gear 5, and the fourth clutch are sequentially arranged around the input shaft 2 from one end side. This is an automatic transmission for an FF vehicle in which C4, a planetary gear 4 for deceleration and a second brake B2, and a first clutch C1 and a first brake B1 are arranged. The same applies to an automatic transmission for an FR vehicle. The invention can be applied. For example, as in the fifth embodiment shown in FIG. 9, the first clutch C1 and the first brake B1, the deceleration planetary gear 4 and the second brake B2 around the input shaft 2 in this order from the one end (front end) side. The fourth clutch C4, the shifting double planetary gear 5, and the second and third clutches C2 and C3 are arranged, and the propeller shaft is an output member extending rearward of the ring gear Rm (third element) of the shifting double planetary gear 5. You may connect 3 '. In the fifth embodiment, the transmission of the first embodiment is changed to that for an FR vehicle, but the transmissions of the second to fourth embodiments can be similarly changed to those for an FR vehicle.

次に、図１０（ａ）に示す第６実施形態について説明する。第６実施形態は、上記第１実施形態と同様の変速用複式プラネタリギヤ５を備えると共に、第１実施形態の減速用プラネタリギヤ４に代えて、減速用複式プラネタリギヤ６を備えている。   Next, a sixth embodiment shown in FIG. The sixth embodiment includes a speed-changing planetary gear 5 similar to that of the first embodiment, and includes a speed-reducing planetary gear 6 instead of the speed-reducing planetary gear 4 of the first embodiment.

減速用複式プラネタリギヤ６は、サンギヤＳｆ１と、リングギヤＲｆ１と、サンギヤＳｆ１とリングギヤＲｆ１とに噛合するピニオンＰｆ１を自転及び公転自在に支持するキャリアＣｆ１とを有する減速用第１プラネタリギヤ６１と、サンギヤＳｆ２と、リングギヤＲｆ２と、サンギヤＳｆ２とリングギヤＲｆ２とに噛合するピニオンＰｆ２を自転及び公転自在に支持するキャリアＣｆ２とを有する減速用第２プラネタリギヤ６２とを用い、減速用第１プラネタリギヤ６１のキャリアＣｆ１と減速用第２プラネタリギヤ６２のリングギヤＲｆ２とを連結すると共に、減速用第１プラネタリギヤ６１のリングギヤＲｆ１と減速用第２プラネタリギヤ６２のキャリアＣｆ２とを連結して構成されている。   The reduction type planetary gear 6 includes a sun gear Sf1, a ring gear Rf1, a first reduction planetary gear 61 having a carrier Cf1 that supports the sun gear Sf1 and the pinion Pf1 meshing with the ring gear Rf1, and a sun gear Sf2. , Using a second planetary gear 62 for reduction having a ring gear Rf2 and a carrier Cf2 that supports the pinion Pf2 meshing with the sun gear Sf2 and the ring gear Rf2 so as to rotate and revolve freely, and the carrier Cf1 of the first planetary gear 61 for reduction and the reduction The ring gear Rf2 of the second planetary gear 62 is connected to the ring gear Rf1 of the first planetary gear 61 for reduction and the carrier Cf2 of the second planetary gear 62 for reduction is connected.

この減速用複式プラネタリギヤ６は、減速用第１プラネタリギヤ６１のサンギヤＳｆ１と、減速用第２プラネタリギヤ６２のサンギヤＳｆ２と、減速用第１プラネタリギヤ６１のキャリアＣｆ１と減速用第２プラネタリギヤ６２のリングギヤＲｆ２との連結体（第１連結体）と、減速用第１プラネタリギヤ６１のリングギヤＲｆ１と減速用第２プラネタリギヤ６２のキャリアＣｆ２との連結体（第２連結体）とから成る４つの回転要素を有することになる。そして、これら回転要素を、図１１の上段に示す速度線図におけるギア比に対応する間隔での並び順に左側から夫々第５要素、第６要素、第７要素及び第８要素とすると、第５要素は減速用第１プラネタリギヤ６１のサンギヤＳｆ１、第２要素は第１連結体Ｃｆ１，Ｒｆ２、第３要素は第２連結体Ｒｆ１，Ｃｆ２、第４要素は減速用第２プラネタリギヤ６２のサンギヤＳｆ２になる。尚、減速用第１プラネタリギヤ６１のギヤ比をｉ１、減速用第２プラネタリギヤ６２のギヤ比をｉ２として、減速用第１プラネタリギヤ６１のサンギヤＳｆ１と第１連結体Ｃｆ１，Ｒｆ２間の間隔と、第１連結体Ｃｆ１，Ｒｆ２と第２連結体Ｒｆ１，Ｃｆ２間の間隔と、第２連結体Ｒｆ１，Ｃｆ２と減速用第２プラネタリギヤ６２のサンギヤＳｆ２間の間隔との比はｉ１：１：ｉ２に設定されている。そして、減速用第１プラネタリギヤ６１のサンギヤＳｆ１の回転速度が「１」、第２連結体Ｒｆ１，Ｃｆ２の回転速度が「０」のときの減速用複式プラネタリギヤ６の出力速度（第１連結体Ｃｆ１，Ｒｆ２の回転速度）Ｎ１は１／（ｉ１＋１）になり、減速用第１プラネタリギヤ６１のサンギヤＳｆ１の回転速度が「１」、減速用第２プラネタリギヤ６２のサンギヤＳｆ２の回転速度が「０」のときの減速用複式プラネタリギヤ６の出力速度Ｎ２は（ｉ２＋１）／（ｉ１＋ｉ２＋１）になる。   The double planetary gear 6 for reduction includes a sun gear Sf1 of the first planetary gear 61 for reduction, a sun gear Sf2 of the second planetary gear 62 for reduction, a carrier Cf1 of the first planetary gear 61 for reduction, and a ring gear Rf2 of the second planetary gear 62 for reduction. And four rotating elements comprising a connecting body (second connecting body) of the ring gear Rf1 of the first planetary gear 61 for reduction and the carrier Cf2 of the second planetary gear 62 for reduction. become. Then, if these rotating elements are the fifth element, the sixth element, the seventh element, and the eighth element from the left in the order of arrangement at intervals corresponding to the gear ratio in the velocity diagram shown in the upper part of FIG. The elements are the sun gear Sf1 of the first planetary gear 61 for reduction, the second element is the first coupling bodies Cf1 and Rf2, the third element is the second coupling bodies Rf1 and Cf2, and the fourth element is the sun gear Sf2 of the second planetary gear 62 for reduction. Become. The gear ratio of the first planetary gear for reduction 61 is i1, the gear ratio of the second planetary gear for reduction 62 is i2, and the distance between the sun gear Sf1 of the first planetary gear for reduction 61 and the first coupling bodies Cf1 and Rf2 is The ratio between the interval between the first connector Cf1, Rf2 and the second connector Rf1, Cf2 and the interval between the second connector Rf1, Cf2 and the sun gear Sf2 of the second planetary gear 62 for reduction is set to i1: 1: i2. Has been. Then, when the rotational speed of the sun gear Sf1 of the first planetary gear for deceleration 61 is “1” and the rotational speed of the second coupling bodies Rf1 and Cf2 is “0”, the output speed of the double planetary gear for deceleration 6 (the first coupling body Cf1). , Rf2) N1 becomes 1 / (i1 + 1), the rotation speed of the sun gear Sf1 of the first planetary gear 61 for reduction is “1”, and the rotation speed of the sun gear Sf2 of the second planetary gear 62 for reduction is “0”. The output speed N2 of the double planetary gear 6 for deceleration is (i2 + 1) / (i1 + i2 + 1).

第６実施形態では、変速用複式プラネタリギヤ５の第１サンギヤＳｍｌ（第１要素）と第１連結体Ｃｆ１，Ｒｆ２（第６要素）とを連結すると共に、減速用第１プラネタリギヤ６１のサンギヤＳｆ１（第５要素）を第１クラッチＣ１を介して入力軸２に連結自在としている。更に、減速用第２プラネタリギヤ６２のサンギヤＳｆ２（第８要素）を、第４クラッチＣ４を介して変速用複式プラネタリギヤ５のキャリアＣｍ（第２要素）に連結自在とすると共に、第２ブレーキＢ２を介して変速機ケース１に固定自在とし、また、第２連結体Ｒｆ１，Ｃｆ２（第７要素）を第１ブレーキＢ１を介して変速機ケース１に固定自在としている。他の構成は上記第１実施形態と同一である。   In the sixth embodiment, the first sun gear Sml (first element) of the double planetary gear 5 for transmission and the first coupling bodies Cf1 and Rf2 (sixth element) are coupled and the sun gear Sf1 (first gear gear 61 for deceleration) ( The fifth element) can be connected to the input shaft 2 via the first clutch C1. Further, the sun gear Sf2 (eighth element) of the second planetary gear 62 for deceleration can be freely connected to the carrier Cm (second element) of the compound planetary gear 5 for speed change via the fourth clutch C4, and the second brake B2 is provided. The second connecting bodies Rf1 and Cf2 (seventh element) can be fixed to the transmission case 1 via the first brake B1. Other configurations are the same as those in the first embodiment.

第１連結体Ｃｆ１，Ｒｆ２は、図１１の下段に示す変速用複式プラネタリギヤ５の速度線図において、変速用複式プラネタリギヤ５の第１サンギヤＳｍｌと同一の縦線Ｙ２上に常時位置する。また、第４クラッチＣ４を係合させると、減速用第２プラネタリギヤ６２のサンギヤＳｆ２が変速用複式プラネタリギヤ５のキャリアＣｍと同一の縦線Ｙ４上に位置し、第２連結体Ｒｆ１，Ｃｆ２が縦線Ｙ２から縦線Ｙ２と縦線Ｙ４間の間隔の１／（１＋ｉ２）だけ右側に離れた縦線Ｙ３上に位置し、減速用第１プラネタリギヤ６１のサンギヤＳｆ１が縦線Ｙ２から縦線Ｙ２と縦線Ｙ３間の間隔のｉ１倍だけ左側に離れた縦線Ｙ１上に位置する。尚、変速用複式プラネタリギヤ５のリングギヤＲｍと第１サンギヤＳｍｌとのギヤ比をｊ１、リングギヤＲｍと第２サンギヤＳｍｓとのギヤ比をｊ２として、変速用複式プラネタリギヤ５のリングギヤＲｍは縦線Ｙ４から縦線Ｙ２と縦線Ｙ４間の間隔の１／ｊ１だけ右側に離れた縦線Ｙ５上に位置し、変速用複式プラネタリギヤ５の第２サンギヤＳｍｓは縦線Ｙ５から縦線Ｙ４と縦線Ｙ５間の間隔の（ｊ２−１）倍だけ右側に離れた縦線Ｙ６上に位置する。   The first coupling bodies Cf1 and Rf2 are always located on the same vertical line Y2 as the first sun gear Sml of the transmission double planetary gear 5 in the speed diagram of the transmission double planetary gear 5 shown in the lower part of FIG. Further, when the fourth clutch C4 is engaged, the sun gear Sf2 of the second planetary gear 62 for reduction is positioned on the same vertical line Y4 as the carrier Cm of the double planetary gear 5 for transmission, and the second coupling bodies Rf1 and Cf2 are vertically The sun gear Sf1 of the first planetary gear 61 for speed reduction is located from the vertical line Y2 to the vertical line Y2 and is located on the vertical line Y3 that is 1 / (1 + i2) of the distance between the vertical line Y2 and the vertical line Y4 from the line Y2. It is located on the vertical line Y1 that is separated to the left by i1 times the interval between the vertical lines Y3. Note that the gear ratio between the ring gear Rm and the first sun gear Sml of the double planetary gear 5 for shifting is j1, the gear ratio between the ring gear Rm and the second sun gear Sms is j2, and the ring gear Rm of the double planetary gear 5 for shifting is from the vertical line Y4. The second sun gear Sms of the double planetary gear 5 for shifting is located between the vertical line Y5 and the vertical line Y4 and the vertical line Y5, located on the vertical line Y5 that is separated to the right by 1 / j1 of the interval between the vertical line Y2 and the vertical line Y4. Is located on the vertical line Y6 that is separated to the right by (j2-1) times the interval of.

第６実施形態においては、第３クラッチＣ３と第４クラッチＣ４と第２ブレーキＢ２とを係合させると、縦線Ｙ４での回転速度が「０」、縦線Ｙ６での回転速度が「１」になり、縦線Ｙ５での回転速度は「１ｓｔ」になる。即ち、１速段が確立される。   In the sixth embodiment, when the third clutch C3, the fourth clutch C4, and the second brake B2 are engaged, the rotational speed at the vertical line Y4 is “0”, and the rotational speed at the vertical line Y6 is “1”. ”And the rotation speed along the vertical line Y5 is“ 1st ”. That is, the first gear is established.

第３クラッチＣ３と第４クラッチＣ４と第１ブレーキＢ１とを係合させると、縦線Ｙ３での回転速度が「０」、縦線Ｙ６での回転速度が「１」になり、縦線Ｙ５での回転速度は「２ｎｄ」になる。即ち、２速段が確立される。   When the third clutch C3, the fourth clutch C4, and the first brake B1 are engaged, the rotational speed at the vertical line Y3 becomes “0”, the rotational speed at the vertical line Y6 becomes “1”, and the vertical line Y5 The rotation speed at is 2nd. That is, the second gear is established.

第３クラッチＣ３と第１ブレーキＢ１と第２ブレーキＢ２とを係合させると、縦線Ｙ２での回転速度が「０」、縦線Ｙ６での回転速度が「１」になり、縦線Ｙ５での回転速度は「３ｒｄ」になる。即ち、３速段が確立される。   When the third clutch C3, the first brake B1, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is "0", the rotational speed at the vertical line Y6 is "1", and the vertical line Y5 The rotation speed at is “3rd”. That is, the third gear is established.

第１クラッチＣ１と第３クラッチＣ３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Ｙ６での回転速度が「１」になり、縦線Ｙ５での回転速度は「４ｔｈ」になる。即ち、４速段が確立される。   When the first clutch C1, the third clutch C3, and the first brake B1 are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y6 is “1”, and the vertical line Y5 The rotation speed is “4th”. That is, the fourth gear is established.

第１クラッチＣ１と第３クラッチＣ３と第２ブレーキＢ２とを係合させると、縦線Ｙ２での回転速度がＮ２、縦線Ｙ６での回転速度が「１」になり、縦線Ｙ５での回転速度は「５ｔｈ」になる。即ち、５速段が確立される。   When the first clutch C1, the third clutch C3, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is N2, the rotational speed at the vertical line Y6 is “1”, and the rotational speed at the vertical line Y5 is The rotation speed is “5th”. That is, the fifth gear is established.

第２クラッチＣ２と第３クラッチＣ３とを係合させると、縦線Ｙ４での回転速度と縦線Ｙ６での回転速度とが共に「１」になり、縦線Ｙ５での回転速度も「１」である「６ｔｈ」になる。即ち、６速段が確立される。尚、第１クラッチＣ１を係合させておいても、第２クラッチＣ２と第３クラッチＣ３とを係合させることで６速段が確立される。   When the second clutch C2 and the third clutch C3 are engaged, the rotational speed at the vertical line Y4 and the rotational speed at the vertical line Y6 are both “1”, and the rotational speed at the vertical line Y5 is also “1”. "6th". That is, the sixth gear is established. Even if the first clutch C1 is engaged, the sixth gear is established by engaging the second clutch C2 and the third clutch C3.

第１クラッチＣ１と第２クラッチＣ２と第２ブレーキＢ２とを係合させると、縦線Ｙ２での回転速度がＮ２、縦線Ｙ４での回転速度が「１」になり、縦線Ｙ５での回転速度は「７ｔｈ」になる。即ち、７速段が確立される。   When the first clutch C1, the second clutch C2, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is N2, the rotational speed at the vertical line Y4 is "1", and the vertical line Y5 The rotation speed is “7th”. That is, the seventh gear is established.

第１クラッチＣ１と第２クラッチＣ２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Ｙ４での回転速度が「１」になり、縦線Ｙ５での回転速度は「８ｔｈ」になる。即ち、８速段が確立される。   When the first clutch C1, the second clutch C2, and the first brake B1 are engaged, the rotational speed at the vertical line Y2 is N1, the rotational speed at the vertical line Y4 is "1", and the vertical line Y5 The rotation speed is “8th”. That is, the eighth gear is established.

第２クラッチＣ２と第１ブレーキＢ１と第２ブレーキＢ２とを係合させると、縦線Ｙ２での回転速度が「０」、縦線Ｙ４での回転速度が「１」になり、縦線Ｙ５での回転速度は「９ｔｈ」になる。即ち、９速段が確立される。   When the second clutch C2, the first brake B1, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is "0", the rotational speed at the vertical line Y4 is "1", and the vertical line Y5 The rotation speed at is “9th”. That is, the ninth gear is established.

第２クラッチＣ２と第４クラッチＣ４と第１ブレーキＢ１とを係合させると、縦線Ｙ３での回転速度が「０」、縦線Ｙ４での回転速度が「１」になり、縦線Ｙ５での回転速度は「１０ｔｈ」になる。即ち、１０速段が確立される。   When the second clutch C2, the fourth clutch C4, and the first brake B1 are engaged, the rotational speed at the vertical line Y3 is "0", the rotational speed at the vertical line Y4 is "1", and the vertical line Y5 The rotation speed at is “10th”. That is, the 10th gear is established.

第１クラッチＣ１と第４クラッチＣ４と第２ブレーキＢ２とを係合させると、縦線Ｙ２での回転速度がＮ２、縦線Ｙ４での回転速度が「０」になり、縦線Ｙ５での回転速度はマイナスの「Ｒｅｖ１」になる。即ち、後進１速段が確立される。   When the first clutch C1, the fourth clutch C4, and the second brake B2 are engaged, the rotational speed at the vertical line Y2 is N2, the rotational speed at the vertical line Y4 is "0", and the vertical line Y5 The rotation speed becomes negative “Rev1”. That is, the first reverse speed is established.

第１クラッチＣ１と第４クラッチＣ４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」になり、縦線Ｙ５での回転速度はマイナスの「Ｒｅｖ２」になる。即ち、後進２速段が確立される。   When the first clutch C1, the fourth clutch C4, 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 Y5 The rotation speed is negative “Rev2”. That is, the second reverse speed is established.

図１０（ｂ）は、上述した各変速段とクラッチＣ１〜Ｃ４、ブレーキＢ１，Ｂ２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。第６実施形態では、前進１０段、後進２段の変速を行うことができる。そして、６個の係合要素のうち各変速段において３個の係合要素が係合するため、各変速段で解放している係合要素の数は上記実施形態と同様に３個になり、４個の係合要素が解放している上記従来例のものに比し、解放している係合要素によるフリクションロスを低減でき、変速機の効率が向上する。   FIG. 10B is a diagram summarizing the relationship between the above-described shift speeds and the engagement states of the clutches C1 to C4 and the brakes B1 and B2, and ◯ represents engagement. In the sixth embodiment, it is possible to perform shifts of 10 forward speeds and 2 reverse speeds. And since three engagement elements engage in each gear stage among the six engagement elements, the number of engagement elements released in each gear stage is three as in the above embodiment. Compared to the conventional example in which the four engagement elements are released, the friction loss due to the released engagement elements can be reduced, and the efficiency of the transmission is improved.

また、図１０（ｂ）は、上述したギヤ比ｉ１，ｉ２，ｊ１，ｊ２を夫々ｉ１＝２．０、ｉ２＝１．４、ｊ１＝１．６、ｊ２＝３．５とした場合における各変速段のギヤレシオ（入力軸２の回転速度／出力ギヤ３の回転速度）も示している。これによれば、公比（各変速段間のギヤレシオの比）が適切になると共に、レンジ（一速レシオ／１０速レシオ）も適切になる。   FIG. 10B shows the above-described cases where the gear ratios i1, i2, j1, and j2 are i1 = 2.0, i2 = 1.4, j1 = 1.6, and j2 = 3.5, respectively. The gear ratio of the shift speed (the rotational speed of the input shaft 2 / the rotational speed of the output gear 3) is also shown. According to this, the common ratio (ratio of gear ratios between gears) becomes appropriate, and the range (first speed ratio / 10 speed ratio) becomes appropriate.

ところで、第６実施形態では、単式プラネタリギヤから成る２つのプラネタリギヤ６１，６２を組合せて減速用複式プラネタリギヤ６を構成しているが、図１２に示す第７実施形態のように、減速用複式プラネタリギヤ６として、第１サンギヤＳｆｌと、第２サンギヤＳｆｓと、リングギヤＲｆと、第１サンギヤＳｆｌとリングギヤＲｆとに噛合する第１ピニオンＰｆｌと第２サンギヤＳｆｓと第１ピニオンＰｆｌとに噛合する第２ピニオンＰｆｓとを自転及び公転自在に支持するキャリアＣｆとを有するラビニヨ型のプラネタリギヤを用いても良い。   By the way, in the sixth embodiment, the double planetary gear 6 for reduction is configured by combining the two planetary gears 61 and 62 composed of a single planetary gear. However, as in the seventh embodiment shown in FIG. 12, the double planetary gear 6 for reduction is used. As shown, the first sun gear Sfl, the second sun gear Sfs, the ring gear Rf, the first pinion Pfl that meshes with the first sun gear Sfl and the ring gear Rf, the second sun gear Sfs, and the second pinion that meshes with the first pinion Pfl. A Ravigneaux type planetary gear having a carrier Cf that supports Pfs in a freely rotating and revolving manner may be used.

減速用複式プラネタリギヤ６の第１サンギヤＳｆｌ、第２サンギヤＳｆｓ、リングギヤＲｆ及びキャリアＣｆから成る４個の回転要素を、図１３の上段に示す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５要素、第６要素、第７要素及び第８要素とすると、第５要素は第１サンギヤＳｆｌ、第６要素はキャリアＣｆ、第７要素はリングギヤＲｆ、第８要素は第２サンギヤＳｆｓになる。尚、リングギヤＲｆと第１サンギヤＳｆｌとのギヤ比をｉ１、リングギヤＲｆと第２サンギヤＳｆｓとのギヤ比をｉ２として、第１サンギヤＳｆｌ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、リングギヤＲｆと第２サンギヤＳｍｓ間の間隔の比はｉ１：１：ｉ２−１に設定されている。   Four rotating elements including the first sun gear Sfl, the second sun gear Sfs, the ring gear Rf, and the carrier Cf of the double planetary gear 6 for speed reduction are arranged in an order corresponding to the gear ratio in the speed diagram shown in the upper part of FIG. Assuming the fifth element, the sixth element, the seventh element, and the eighth element from the left side, the fifth element is the first sun gear Sfl, the sixth element is the carrier Cf, the seventh element is the ring gear Rf, and the eighth element is the second element. It becomes the sun gear Sfs. The gear ratio between the ring gear Rf and the first sun gear Sfl is i1, the gear ratio between the ring gear Rf and the second sun gear Sfs is i2, and the distance between the first sun gear Sfl and the carrier Cf and between the carrier Cf and the ring gear Rf. The ratio of the interval and the interval between the ring gear Rf and the second sun gear Sms is set to i1: 1: i2-1.

第７実施形態では、減速用複式プラネタリギヤ６のキャリアＣｆ（第６要素）と変速用複式プラネタリギヤ５の第１サンギヤＳｍｌ（第１要素）とを連結すると共に、減速用複式プラネタリギヤ６の第１サンギヤＳｆ１（第５要素）を第１クラッチＣ１を介して入力軸２に連結している。更に、減速用複式プラネタリギヤ６の第２サンギヤＳｆｓ（第８要素）を、第４クラッチＣ４を介して変速用複式プラネタリギヤ５のキャリアＣｍ（第２要素）に連結自在とすると共に、第２ブレーキＢ２を介して変速機ケース１に固定自在とし、また、減速用複式プラネタリギヤ６のリングギヤＲｆ（第７要素）を第１ブレーキＢ１を介して変速機ケース１に固定自在としている。他の構成は上記第６実施形態と同一である。   In the seventh embodiment, the carrier Cf (sixth element) of the double planetary gear 6 for reduction and the first sun gear Sml (first element) of the double planetary gear 5 for transmission are connected, and the first sun gear of the double planetary gear 6 for reduction is connected. Sf1 (fifth element) is coupled to the input shaft 2 via the first clutch C1. Further, the second sun gear Sfs (eighth element) of the double planetary gear for deceleration 6 can be connected to the carrier Cm (second element) of the double planetary gear for shifting 5 via the fourth clutch C4, and the second brake B2 The ring gear Rf (seventh element) of the speed reduction double planetary gear 6 can be fixed to the transmission case 1 via the first brake B1. Other configurations are the same as those of the sixth embodiment.

第７実施形態のものも、前進１０段、後進２段の変速が行われ、各変速段とクラッチＣ１〜Ｃ４、ブレーキＢ１，Ｂ２の係合状態との関係は図１０（ｂ）に示したものと同一になる。また、減速用複式プラネタリギヤ６のリングギヤＲｆと第１サンギヤＳｆｌのギヤ比ｉ１を２．０、減速用複式プラネタリギヤ６のリングギヤＲｆと第２サンギヤＳｆｓのギヤ比ｉ２を２．４、変速用複式プラネタリギヤ５のリングギヤＲｍと第１サンギヤＳｍｌのギヤ比ｊ１を１．６、変速用複式プラネタリギヤ５のリングギヤＲｍと第２サンギヤＳｍｓのギヤ比ｊ２を３．５に設定すると、各変速段のギヤレシオは図１０（ｂ）に示したものと同一になる。   In the seventh embodiment as well, 10 forward speeds and 2 reverse speeds are changed, and the relationship between the respective gear speeds and the engagement states of the clutches C1 to C4 and the brakes B1 and B2 is shown in FIG. To be the same. Further, the gear ratio i1 between the ring gear Rf and the first sun gear Sfl of the reduction double planetary gear 6 is 2.0, the gear ratio i2 between the ring gear Rf and the second sun gear Sfs of the reduction double planetary gear 6 is 2.4, and the gear change double planetary gear. When the gear ratio j1 between the ring gear Rm 5 and the first sun gear Sml is set to 1.6, and the gear ratio j2 between the ring gear Rm and the second sun gear Sms of the transmission double planetary gear 5 is set to 3.5, the gear ratio of each gear stage is as shown in FIG. This is the same as that shown in 10 (b).

ところで、第６、第７実施形態では、変速用複式プラネタリギヤ５をラビニヨ型プラネタリギヤで構成しているが、第６、第７実施形態の変速用複式プラネタリギヤ５を、上記第２実施形態のような２つの単式プラネタリギヤを組合せて構成される複式プラネタリギヤに変更することも可能である。また、第６、第７実施形態はＦＦ車用の自動変速機であるが、ＦＲ車用の自動変速機にも同様に本発明を適用できる。例えば、図１４に示す第８実施形態のように、入力軸２の周りに一端（前端）側から順に、第１クラッチＣ１と、減速用複式プラネタリギヤ６及び第１ブレーキＢ１と、第２ブレーキＢ２及び第４クラッチＣ４と、変速用複式プラネタリギヤ５と、第２及び第３クラッチＣ２，Ｃ３とを配置し、変速用複式プラネタリギヤ５のリングギヤＲｍ（第３要素）を後方にのびる出力部材たるプロペラシャフト３´に連結しても良い。尚、第８実施形態は第６実施形態の変速機をＦＲ車用のものに変更したものであるが、第７実施形態の変速機も同様にＦＲ車用のものに変更できる。   By the way, in the sixth and seventh embodiments, the speed-changing planetary gear 5 is constituted by a Ravigneaux-type planetary gear. However, the speed-changing planetary gear 5 of the sixth and seventh embodiments is similar to that of the second embodiment. It is also possible to change to a double planetary gear configured by combining two single planetary gears. Moreover, although the sixth and seventh embodiments are automatic transmissions for FF vehicles, the present invention can be similarly applied to automatic transmissions for FR vehicles. For example, as in the eighth embodiment shown in FIG. 14, the first clutch C1, the speed-reducing planetary gear 6 and the first brake B1, and the second brake B2 are sequentially arranged around the input shaft 2 from one end (front end) side. And the fourth clutch C4, the shift type planetary gear 5, and the second and third clutches C2 and C3, and the propeller shaft as an output member extending backward from the ring gear Rm (third element) of the shift type planetary gear 5 You may connect 3 '. In the eighth embodiment, the transmission of the sixth embodiment is changed to that for an FR vehicle, but the transmission of the seventh embodiment can be changed to that for an FR vehicle as well.

（ａ）本発明変速機の第１実施形態のスケルトン図、（ｂ）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 transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear stage. 第１実施形態の減速用プラネタリギヤと変速用複式プラネタリギヤの速度線図。The speed diagram of the planetary gear for deceleration of the 1st Embodiment and the compound planetary gear for gear shifting. 本発明変速機の第２実施形態のスケルトン図。The skeleton figure of 2nd Embodiment of this invention transmission. 第２実施形態の減速用プラネタリギヤと変速用複式プラネタリギヤの速度線図。The speed diagram of the planetary gear for deceleration of the 2nd Embodiment and the compound planetary gear for transmission. 本発明変速機の第３実施形態のスケルトン図。The skeleton figure of 3rd Embodiment of this invention transmission. 第３実施形態の減速用プラネタリギヤと変速用複式プラネタリギヤの速度線図。The speed diagram of the planetary gear for deceleration of the 3rd Embodiment and the compound planetary gear for transmission. 本発明変速機の第４実施形態のスケルトン図。The skeleton figure of 4th Embodiment of this invention transmission. 第４実施形態の減速用プラネタリギヤと変速用複式プラネタリギヤの速度線図。The speed diagram of the planetary gear for deceleration of the 4th Embodiment and the compound planetary gear for gear shifting. 本発明変速機の第５実施形態のスケルトン図。The skeleton figure of 5th Embodiment of this invention transmission. （ａ）本発明変速機の第６実施形態のスケルトン図、（ｂ）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 transmission of the present invention, (b) A diagram collectively showing the engagement state of each engagement element at each gear stage. 第６実施形態の減速用複式プラネタリギヤと変速用複式プラネタリギヤの速度線図。The speed diagram of the double planetary gear for deceleration and the double planetary gear for speed change of 6th Embodiment. 本発明変速機の第７実施形態のスケルトン図。The skeleton figure of 7th Embodiment of this invention transmission. 第７実施形態の減速用複式プラネタリギヤと変速用複式プラネタリギヤの速度線図。The speed diagram of the double planetary gear for deceleration and the double planetary gear for speed change of 7th Embodiment. 本発明変速機の第８実施形態のスケルトン図。The skeleton figure of 8th Embodiment of this invention transmission.

符号の説明Explanation of symbols

１…変速機ケース、２…入力軸（入力部材）、３…出力ギヤ（出力部材）、３´…プロペラシャフト（出力部材）、４…減速用プラネタリギヤ、Ｓｆ…減速用プラネタリギヤのサンギヤ（第１実施形態における第５要素）、Ｃｆ…減速用プラネタリギヤのキャリア（第１実施形態における第６要素）、Ｒｆ…減速用プラネタリギヤのリングギヤ（第１実施形態における第７要素）、５…変速用複式プラネタリギヤ、Ｓｍｌ…変速用複式プラネタリギヤの第１サンギヤ（第１実施形態における第１要素）、Ｓｍｓ…変速用複式プラネタリギヤの第２サンギヤ（第１実施形態における第４要素）、Ｃｍ…変速用複式プラネタリギヤのキャリア（第１実施形態における第２要素）、Ｒｍ…変速用複式プラネタリギヤのリングギヤ（第１実施形態における第３要素）、６…減速用複式プラネタリギヤ、Ｓｆｌ…減速用複式プラネタリギヤの第１サンギヤ（第７実施形態における第５要素）、Ｓｆｓ…減速用複式プラネタリギヤの第２サンギヤ（第７実施形態における第８要素）、Ｃｆ…減速用複式プラネタリギヤのキャリア（第７実施形態における第６要素）、Ｒｆ…減速用複式プラネタリギヤのリングギヤ（第７実施形態における第７要素）、Ｃ１…第１クラッチ（第１係合要素）、Ｃ２…第２クラッチ（第２係合要素）、Ｃ３…第３クラッチ（第３係合要素）、Ｃ４…第４クラッチ（第４係合要素）、Ｂ１…第１ブレーキ（第５係合要素）、Ｂ２…第２ブレーキ（第６係合要素）。   DESCRIPTION OF SYMBOLS 1 ... Transmission case, 2 ... Input shaft (input member), 3 ... Output gear (output member), 3 '... Propeller shaft (output member), 4 ... Reduction planetary gear, Sf ... Sun gear of reduction planetary gear (1st Fifth element in the embodiment), Cf ... Deceleration planetary gear carrier (sixth element in the first embodiment), Rf ... Deceleration planetary gear ring gear (seventh element in the first embodiment), 5 ... Shifting planetary gear , Sml: first sun gear (first element in the first embodiment) of the double planetary gear for shifting, Sms: second sun gear (fourth element in the first embodiment) of the double planetary gear for shifting, Cm: of the double planetary gear for shifting Carrier (second element in the first embodiment), Rm ... ring gear of the double planetary gear for shifting (in the first embodiment , 6 ... deceleration double planetary gear, Sfl ... first sun gear of the reduction double planetary gear (fifth element in the seventh embodiment), Sfs ... second sun gear of the reduction planetary gear (in the seventh embodiment) Eighth element), Cf... Reduction planetary gear carrier (sixth element in the seventh embodiment), Rf... Reduction double planetary gear ring gear (seventh element in the seventh embodiment), C1. 1 engagement element), C2 ... 2nd clutch (2nd engagement element), C3 ... 3rd clutch (3rd engagement element), C4 ... 4th clutch (4th engagement element), B1 ... 1st brake (5th engagement element), B2 ... 2nd brake (6th engagement element).

Claims (2)

入力部材の回転を変速機ケース内に配置した減速用プラネタリギヤと変速用複式プラネタリギヤとを介して複数段に変速して出力部材に伝達する自動変速機であって、
変速用複式プラネタリギヤは、速度線図においてギヤ比に対応する間隔で並ぶ４つの回転要素を有し、これら回転要素を速度線図における並び順に夫々第１要素、第２要素、第３要素及び第４要素とし、減速用プラネタリギヤのサンギヤ、リングギヤ及びキャリアから成る３つの要素を、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５要素、第６要素及び第７要素として、第１要素と第６要素とが連結されると共に、第３要素が出力部材に連結され、
入力部材と第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１係合要素と、
入力部材と第２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、
入力部材と第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３係合要素と、
第２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、
第７要素を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第６係合要素とを備えることを特徴とする自動変速機。 An automatic transmission that shifts the rotation of an input member to a plurality of stages via a speed reduction planetary gear and a speed change planetary gear arranged in a transmission case, and transmits them to an output member.
The dual planetary gear for shifting has four rotating elements arranged at intervals corresponding to the gear ratio in the speed diagram, and these rotating elements are arranged in the order of arrangement in the speed diagram, respectively, the first element, the second element, the third element, and the second element. The four elements, and the three elements consisting of the sun gear, ring gear, and carrier of the planetary gear for reduction, are arranged as the fifth element, the sixth element, and the seventh element, respectively, in order of arrangement at intervals corresponding to the gear ratio in the velocity diagram. The element and the sixth element are coupled, and the third element is coupled to the output member;
A first engagement element switchable between a state of connecting the input member and the fifth element and a state of disconnecting the connection;
A second engagement element switchable between a state of connecting the input member and the second element and a state of disconnecting the connection;
A third engagement element switchable between a state of connecting the input member and the fourth element and a state of disconnecting the connection;
A fourth engagement element that is switchable between a state of connecting the second element and the seventh element and a state of disconnecting the connection;
A fifth 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;
An automatic transmission comprising a sixth engagement element that is switchable between a state in which the seventh element is fixed to the transmission case and a state in which the fixation is released. 入力部材の回転を変速機ケース内に配置した減速用複式プラネタリギヤと変速用複式プラネタリギヤとを介して複数段に変速して出力部材に伝達する自動変速機であって、
変速用と減速用の各複式プラネタリギヤは、速度線図においてギヤ比に対応する間隔で並ぶ４つの回転要素を有し、変速用複式プラネタリギヤの４つの回転要素を速度線図における並び順に夫々第１要素、第２要素、第３要素及び第４要素とし、減速用複式プラネタリギヤの４つの回転要素を速度線図における並び順に夫々第５要素、第６要素、第７要素及び第８要素として、第１要素と第６要素とが連結されると共に、第３要素が出力部材に連結され、
入力部材と第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１係合要素と、
入力部材と第２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、
入力部材と第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３係合要素と、
第２要素と第８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７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、
第８要素を変速機ケースに固定する状態とこの固定を解除する状態とに切換自在な第６係合要素とを備えることを特徴とする自動変速機。 An automatic transmission that shifts the rotation of an input member to a plurality of stages via a speed reduction compound planetary gear and a speed change compound planetary gear that are arranged in a transmission case and transmits them to an output member.
Each of the planetary gears for shifting and decelerating has four rotating elements arranged at intervals corresponding to the gear ratio in the speed diagram, and each of the four rotating elements of the shifting planetary gear is arranged in the order of arrangement in the speed diagram. Element, second element, third element and fourth element, and the four rotating elements of the speed reduction compound planetary gear in the order of arrangement in the velocity diagram as the fifth element, sixth element, seventh element and eighth element, respectively. The first element and the sixth element are connected, and the third element is connected to the output member,
A first engagement element switchable between a state of connecting the input member and the fifth element and a state of disconnecting the connection;
A second engagement element switchable between a state of connecting the input member and the second element and a state of disconnecting the connection;
A third engagement element switchable between a state of connecting the input member and the fourth element and a state of disconnecting the connection;
A fourth engagement element that is switchable between a state of connecting the second element and the eighth element and a state of disconnecting the connection;
A fifth engagement element switchable between a state in which the seventh element is fixed to the transmission case and a state in which the fixation is released;
An automatic transmission comprising a sixth engaging element that is switchable between a state in which the eighth element is fixed to the transmission case and a state in which the fixation is released.
JP2008014026A 2008-01-24 2008-01-24 Automatic transmission Withdrawn JP2009174643A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2008014026A JP2009174643A (en) 2008-01-24 2008-01-24 Automatic transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2008014026A JP2009174643A (en) 2008-01-24 2008-01-24 Automatic transmission

Publications (1)

Publication Number Publication Date
JP2009174643A true JP2009174643A (en) 2009-08-06

Family

ID=41029938

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2008014026A Withdrawn JP2009174643A (en) 2008-01-24 2008-01-24 Automatic transmission

Country Status (1)

Country Link
JP (1) JP2009174643A (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101334519B1 (en) 2012-10-31 2013-11-28 현대 파워텍 주식회사 Power train for automission
WO2015011414A1 (en) * 2013-07-25 2015-01-29 Punch Powerglide Strasbourg (Societe Par Actions Simplifiee) Automatic transmission and corresponding control method
JP2016098854A (en) * 2014-11-18 2016-05-30 ジヤトコ株式会社 Automatic transmission

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101334519B1 (en) 2012-10-31 2013-11-28 현대 파워텍 주식회사 Power train for automission
WO2014069721A1 (en) * 2012-10-31 2014-05-08 현대파워텍 주식회사 Power train of automatic transmission
CN104755809A (en) * 2012-10-31 2015-07-01 现代派沃泰有限公司 Power train of automatic transmission
US9714692B2 (en) 2012-10-31 2017-07-25 Hyundai Powertech Co., Ltd. Power train of automatic transmission
WO2015011414A1 (en) * 2013-07-25 2015-01-29 Punch Powerglide Strasbourg (Societe Par Actions Simplifiee) Automatic transmission and corresponding control method
FR3009053A1 (en) * 2013-07-25 2015-01-30 Punch Powerglide Strasbourg AUTOMATIC TRANSMISSION
CN105705830A (en) * 2013-07-25 2016-06-22 邦志传动斯特拉斯堡简易股份公司 Automatic transmission and corresponding control method
JP2016098854A (en) * 2014-11-18 2016-05-30 ジヤトコ株式会社 Automatic transmission

Similar Documents

Publication Publication Date Title
JP2009174626A (en) Automatic transmission
JP3837125B2 (en) Multistage automatic transmission for vehicles
JP5208809B2 (en) Automatic transmission
JP5187799B2 (en) 6-speed powertrain for automatic transmission
JP5184456B2 (en) Automatic transmission
JP2012247058A (en) Planetary gear train for vehicle automatic transmission
JP2010281388A (en) Automatic transmission
JP2015183853A (en) multi-speed transmission
JP2009174625A (en) Automatic transmission
JP2005042790A (en) Vehicular multi-stage automatic transmission
JP4945790B2 (en) Automatic transmission
JP2010007709A (en) Multi-stage shift planetary gear train
JP5138500B2 (en) Automatic transmission
JP3848242B2 (en) Gear transmission for automatic transmission
JP5123904B2 (en) Automatic transmission
JP2009174643A (en) Automatic transmission
JP5123906B2 (en) Automatic transmission
JP5123905B2 (en) Automatic transmission
JP5143789B2 (en) Automatic transmission
JP2009185862A (en) Automatic transmission
KR100887971B1 (en) Gear train in an automatic transmission for vehicles
JP2009174642A (en) Automatic transmission
JP5113718B2 (en) Automatic transmission
JP2009185863A (en) Automatic transmission
JP5138514B2 (en) Automatic transmission

Legal Events

Date Code Title Description
A300 Withdrawal of application because of no request for examination

Free format text: JAPANESE INTERMEDIATE CODE: A300

Effective date: 20110405