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JP2000257702A - Automatic transmission for vehicle - Google Patents

Automatic transmission for vehicle

Info

Publication number
JP2000257702A
JP2000257702A JP11064385A JP6438599A JP2000257702A JP 2000257702 A JP2000257702 A JP 2000257702A JP 11064385 A JP11064385 A JP 11064385A JP 6438599 A JP6438599 A JP 6438599A JP 2000257702 A JP2000257702 A JP 2000257702A
Authority
JP
Japan
Prior art keywords
gear
bearing
ring gear
ring
planetary gear
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.)
Granted
Application number
JP11064385A
Other languages
Japanese (ja)
Other versions
JP3512666B2 (en
Inventor
Masao Shimamoto
雅夫 嶋本
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.)
Daihatsu Motor Co Ltd
Original Assignee
Daihatsu 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 Daihatsu Motor Co Ltd filed Critical Daihatsu Motor Co Ltd
Priority to JP06438599A priority Critical patent/JP3512666B2/en
Publication of JP2000257702A publication Critical patent/JP2000257702A/en
Application granted granted Critical
Publication of JP3512666B2 publication Critical patent/JP3512666B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

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
    • 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
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one 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
    • F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections

Landscapes

  • General Details Of Gearings (AREA)
  • Structure Of Transmissions (AREA)

Abstract

PROBLEM TO BE SOLVED: To improve supporting rigidity and rotational accuracy of a bearing in addition to space efficiency by bringing a center of the bearing which rotatably supports a hub part of a ring gear close to a center of gravity of a planetary gear. SOLUTION: This transmission comprises a planetary gear 4 and a friction engagement device B2 disposed in an adjacent relationship. A ring gear 4 of the planetary gear 4 where a gear part 4f1 and a hub part 4f2 are rotatably locked is axially prevented from coming off by a snap ring 20. An inner wall of a transmission case 6 is formed with a concave part 6a constituting an oil chamber, and a piston 10 is slidably and axially placed at the concave part 6a. An inner diametrical part of the piston 10 is sealed by a sealing part 6b constituting an inner diametrical side wall of the concave part 6a. One end of the gear part 4f1 of the ring gear 4f engaging with the snap ring 20 overhangs a radial outside of the sealing part 6b, and a bearing 17 is placed at an inner diameter of the sealing part 6b to support the hub part 4f2 of the ring gear 4f.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】本発明は車両用自動変速機、
特に変速機の内部に遊星歯車装置と摩擦係合装置とを隣
接配置した構造に関するものである。The present invention relates to an automatic transmission for a vehicle,
In particular, the present invention relates to a structure in which a planetary gear device and a friction engagement device are arranged adjacent to each other inside a transmission.

【０００２】[0002]

【従来の技術】一般に、自動変速機には、遊星歯車装置
と複数の湿式多板式の摩擦係合装置とが設けられ、これ
ら摩擦係合装置を適宜締結・解放することで、複数の変
速段を実現している。遊星歯車装置のリングギヤのギヤ
部とハブ部とを一体に形成した場合、リングギヤが大型
部品となり、ギヤの加工が難しくなるので、製造コスト
が高くつくという欠点がある。そのため、リングギヤの
ギヤ部とハブ部とを別体で形成し、ギヤ部の内径部とハ
ブ部の外径部とをスプライン嵌合した上、スナップリン
グで抜け止めすることが行なわれている（例えば、特開
平８−２６１２４９号公報参照）。2. Description of the Related Art Generally, an automatic transmission is provided with a planetary gear unit and a plurality of wet-type multi-plate frictional engagement devices. Has been realized. In the case where the gear portion and the hub portion of the ring gear of the planetary gear device are formed integrally, the ring gear becomes a large part, and the machining of the gear becomes difficult. For this reason, the gear portion and the hub portion of the ring gear are formed separately, and the inner diameter portion of the gear portion and the outer diameter portion of the hub portion are spline-fitted, and are prevented from coming off by a snap ring ( For example, see JP-A-8-261249.

【０００３】[0003]

【発明が解決しようとする課題】しかしながら、このよ
うな遊星歯車装置と摩擦係合装置とを隣接配置した自動
変速機の場合、リングギヤのハブ部を回転支持するベア
リングの中心が遊星歯車装置の重心位置から離れてしま
い、スペース効率が低下するばかりか、ベアリングの支
持剛性および回転精度が低下するという問題があった。
すなわち、ギヤ部とハブ部とを別体で形成した場合、ス
ナップリングの厚みおよびその係合代を確保するため
に、ハブ部に対してギヤ部の端部が軸方向へ突出する。
一方、変速機ケースには摩擦係合装置のピストンの内径
部をシールするシール部が一体に形成されており、この
シール部の内径側にベアリングが配置されているが、上
記シール部とリングギヤのギヤ部とが軸方向に直列的に
配置される関係となるので、ベアリングの中心と遊星歯
車装置の重心とを軸方向に近づけることができない。そ
の結果、変速機全体として軸方向寸法が増大するととも
に、ベアリングの支持剛性および回転精度が低下するの
である。However, in the case of such an automatic transmission in which the planetary gear device and the friction engagement device are arranged adjacent to each other, the center of the bearing that rotatably supports the hub portion of the ring gear is located at the center of gravity of the planetary gear device. There is a problem in that the bearing is separated from the position and the space efficiency is reduced, and that the bearing rigidity and rotational accuracy are reduced.
That is, when the gear portion and the hub portion are formed separately, the end portion of the gear portion protrudes in the axial direction with respect to the hub portion in order to secure the thickness of the snap ring and its engagement allowance.
On the other hand, the transmission case is integrally formed with a seal portion for sealing the inner diameter portion of the piston of the friction engagement device, and a bearing is disposed on the inner diameter side of the seal portion. Since the gear portion and the gear portion are arranged in series in the axial direction, the center of the bearing and the center of gravity of the planetary gear device cannot be brought close to the axial direction. As a result, the axial size of the transmission as a whole increases, and the support rigidity and rotational accuracy of the bearings decrease.

【０００４】そこで、本発明の目的は、リングギヤのハ
ブ部を回転支持する軸受の中心と遊星歯車装置の重心と
を近づけ、スペース効率の向上と、軸受の支持剛性およ
び回転精度を向上を図る車両用自動変速機を提供するこ
とにある。Accordingly, an object of the present invention is to make a center of a bearing for rotatably supporting a hub portion of a ring gear closer to a center of gravity of a planetary gear device, thereby improving space efficiency, and supporting rigidity and rotational accuracy of the bearing. To provide an automatic transmission for a vehicle.

【０００５】[0005]

【課題を解決するための手段】上記目的は請求項１に記
載の発明によって達成される。すなわち、遊星歯車装置
と摩擦係合装置とを隣接配置してなる車両用自動変速機
において、遊星歯車装置のリングギヤはギヤ部とハブ部
とが回り止めされ、かつスナップリングによって軸方向
に抜け止めされており、変速機ケースの内側壁に油室を
構成する凹部が形成され、この凹部に軸方向に摺動自在
にピストンが配置され、上記ピストンの内径部は凹部の
内径側側壁を構成するシール部によってシールされ、上
記スナップリングと係合するリングギヤのギヤ部の一端
部がシール部の半径方向外側にオーバーハングしてお
り、上記シール部の内径側にリングギヤのハブ部を支え
る軸受が配置されていることを特徴とする車両用自動変
速機である。The above object is achieved by the present invention. That is, in a vehicular automatic transmission in which a planetary gear device and a friction engagement device are arranged adjacent to each other, the gear portion and the hub portion of the ring gear of the planetary gear device are prevented from rotating and the snap ring prevents the ring gear from slipping off in the axial direction. A recess that forms an oil chamber is formed on the inner wall of the transmission case, and a piston is slidably disposed in the recess in the axial direction. The inner diameter of the piston forms the inner wall of the recess. One end of the gear portion of the ring gear that is sealed by the seal portion and engages with the snap ring overhangs radially outward of the seal portion, and a bearing that supports the hub portion of the ring gear is disposed on the inner diameter side of the seal portion. An automatic transmission for a vehicle, characterized in that:

【０００６】上記のようにスナップリングと係合するリ
ングギヤのギヤ部の一端部がピストンの内径部をシール
するシール部の半径方向外側にオーバーハングしている
ので、それだけリングギヤのハブ部を回転支持する軸受
の中心と遊星歯車装置の重心とを近づけることができ
る。そのため、変速機の軸方向寸法が短縮されるととも
に、軸受の支持剛性および回転精度が向上する。As described above, one end of the gear portion of the ring gear that engages with the snap ring overhangs radially outward of the seal portion that seals the inner diameter portion of the piston, so that the hub portion of the ring gear is rotatably supported. The center of the bearing and the center of gravity of the planetary gear set can be brought closer. Therefore, the axial dimension of the transmission is reduced, and the support rigidity and rotational accuracy of the bearing are improved.

【０００７】なお、本発明で軸受とは、ころがり軸受
（ベアリング）に限らず、すべり軸受であってもよい。
また、本発明の自動変速機はＦＦ車に限らず、ＦＲ車に
も適用できる。しかし、ＦＦ式自動変速機の場合、狭い
エンジンルームに配置する関係で軸方向寸法をできるだ
け短縮する必要があるので、本発明は好適である。The bearing in the present invention is not limited to a rolling bearing (bearing), but may be a sliding bearing.
Further, the automatic transmission according to the present invention is not limited to an FF vehicle but can be applied to an FR vehicle. However, in the case of the FF type automatic transmission, the present invention is preferable because the axial dimension needs to be reduced as much as possible because of the arrangement in the narrow engine room.

【０００８】[0008]

【発明の実施の形態】図１は本発明にかかる車両用自動
変速機、特にＦＦ式自動変速機の概略構成を示す。この
自動変速機は、トルクコンバータ１、トルクコンバータ
１を介してエンジン動力が伝達される入力軸２、３個の
クラッチＣ１〜Ｃ３、２個のブレーキＢ１，Ｂ２、ワン
ウエイクラッチＦ、ラビニヨウ型遊星歯車装置４、出力
ギヤ５、出力軸７、差動装置８などを備えている。FIG. 1 shows a schematic configuration of an automatic transmission for a vehicle, particularly an FF type automatic transmission according to the present invention. This automatic transmission includes a torque converter 1, an input shaft 2, to which engine power is transmitted via the torque converter 1, three clutches C1 to C3, two brakes B1, B2, a one-way clutch F, a Ravigneaux type planetary gear. A device 4, an output gear 5, an output shaft 7, a differential device 8, and the like are provided.

【０００９】遊星歯車装置４のフォワードサンギヤ４ａ
と入力軸２とはＣ１クラッチを介して連結されており、
リヤサンギヤ４ｂと入力軸２とはＣ２クラッチを介して
連結されている。キャリヤ４ｃは中間軸３と連結され、
中間軸３はＣ３クラッチを介して入力軸２と連結されて
いる。また、キャリヤ４ｃはＢ２ブレーキとキャリヤ４
ｃの正転（エンジン回転方向）のみを許容するワンウェ
イクラッチＦとを介して変速機ケース６に連結されてい
る。キャリヤ４ｃは２種類のピニオンギヤ４ｄ，４ｅを
支持しており、フォワードサンギヤ４ａは軸長の長いロ
ングピニオン４ｄと噛み合い、リヤサンギヤ４ｂは軸長
の短いショートピニオン４ｅを介してロングピニオン４
ｄと噛み合っている。ロングピニオン４ｄのみと噛み合
うリングギヤ４ｆは出力ギヤ５に結合されている。出力
ギヤ５は出力軸７を介して差動装置８と接続されてい
る。上記自動変速機は、クラッチＣ１，Ｃ２，Ｃ３、ブ
レーキＢ１，Ｂ２およびワンウェイクラッチＦの作動に
よって前進４段、後退１段の変速段を実現している。The forward sun gear 4a of the planetary gear set 4
And the input shaft 2 are connected via a C1 clutch.
The rear sun gear 4b and the input shaft 2 are connected via a C2 clutch. The carrier 4c is connected to the intermediate shaft 3,
The intermediate shaft 3 is connected to the input shaft 2 via a C3 clutch. The carrier 4c is a B2 brake and a carrier 4c.
The transmission case 6 is connected to the transmission case 6 via a one-way clutch F that allows only the forward rotation of the engine c (the engine rotation direction). The carrier 4c supports two types of pinion gears 4d and 4e, the forward sun gear 4a meshes with a long pinion 4d having a long shaft length, and the rear sun gear 4b is connected to a long pinion 4 via a short pinion 4e having a short shaft length.
is engaged with d. The ring gear 4f that meshes with only the long pinion 4d is connected to the output gear 5. The output gear 5 is connected to a differential 8 via an output shaft 7. The automatic transmission implements four forward speeds and one reverse speed by operating the clutches C1, C2, C3, the brakes B1, B2, and the one-way clutch F.

【００１０】図２は遊星歯車装置４とＢ２ブレーキの具
体的構造を示す。遊星歯車装置４のリングギヤ４ｆは、
ギヤ部４ｆ1 とハブ部４ｆ2 とがスプライン嵌合され、
かつスナップリング２０によって軸方向に抜け止めされ
た構造となっている。なお、ギヤ部４ｆ1 とハブ部４ｆ
2 の回り止め手段としては、スプライン嵌合に限らず、
ドッグクラッチのような噛み合い歯を設けてもよく、そ
の他いかなる手段を用いてもよい。FIG. 2 shows a specific structure of the planetary gear unit 4 and the B2 brake. The ring gear 4f of the planetary gear device 4 is
And the gear portion 4f 1 and the hub portion 4f 2 is spline-fitted,
In addition, the structure is such that it is prevented from coming off in the axial direction by the snap ring 20. It should be noted that the gear portion 4f 1 and the hub portion 4f
The detent means of 2 is not limited to spline fitting,
A meshing tooth such as a dog clutch may be provided, and any other means may be used.

【００１１】変速機ケース６の内側壁には凹部６ａが形
成され、この凹部６ａに軸方向に摺動自在にピストン１
０が配置され、ピストン１０と変速機ケース６との間に
油室１１が形成されている。ピストン１０の一側面（図
２では右側面）は、後述するリングギヤ４ｆのギヤ部４
ｆ1 との干渉を防止するため、凹状に形成されている。
ピストン１０の内径部は凹部６ａの内径側側壁を構成す
るシール部６ｂによって摺動自在にシールされている。
リングギヤ４ｆのギヤ部４ｆ1 はシール部６ｂより大径
であり、ギヤ部４ｆ1 のスナップリング２０を取り付け
た一端部はシール部６ｂの端面より距離Ｓだけオーバー
ハングしている。A recess 6a is formed in the inner wall of the transmission case 6, and the piston 1 is slidably movable in the axial direction in the recess 6a.
0 is arranged, and an oil chamber 11 is formed between the piston 10 and the transmission case 6. One side surface (the right side surface in FIG. 2) of the piston 10 is a gear portion 4 of a ring gear 4f described later.
To prevent interference with f 1, and is formed in a concave shape.
The inner diameter portion of the piston 10 is slidably sealed by a seal portion 6b constituting an inner diameter side wall of the concave portion 6a.
Gear portion 4f 1 of the ring gear 4f is larger in diameter than the sealing portion 6b, one end fitted with a snap ring 20 of the gear portion 4f 1 is overhanging a distance S from the end face of the seal portion 6b.

【００１２】上記ピストン１０の外径部は、リングギヤ
４ｆのギヤ部４ｆ1 の外径側に配置されたディスク１
４，１５を押圧するよう、リングギヤ４ｆのギヤ部４ｆ
1 の外径側を軸方向に延びている。リングギヤ４ｆのギ
ヤ部４ｆ1 の外径側には、キャリヤ４ｃと一体回転する
キャリヤカバー１６がピストン１０と対向方向から延び
ており、ディスク１４，１５はこのキャリヤカバー１６
と変速機ケース６との間に配置されている。なお、ワン
ウエイクラッチＦもキャリヤカバー１６と変速機ケース
６との間に配置されている。ピストン１０の先端部（図
２の右端部）の外周には、ピストン１０を図２の左方へ
付勢するリターンスプリング１２が配置され、リターン
スプリング１２の右端面はスプリングリテーナ１３で支
持されている。[0012] outer diameter of the piston 10, the disk 1 placed on the outer diameter side of the gear portion 4f 1 of the ring gear 4f
Gear portion 4f of ring gear 4f so as to press
The outer diameter side of 1 extends in the axial direction. On the outer diameter side of the gear portion 4f1 of the ring gear 4f, a carrier cover 16 that rotates integrally with the carrier 4c extends in a direction facing the piston 10, and the disks 14, 15
And the transmission case 6. The one-way clutch F is also disposed between the carrier cover 16 and the transmission case 6. A return spring 12 that urges the piston 10 to the left in FIG. 2 is disposed on the outer periphery of the distal end portion (the right end portion in FIG. 2) of the piston 10, and the right end surface of the return spring 12 is supported by a spring retainer 13. I have.

【００１３】上記シール部６ｂの内径側には、リングギ
ヤ４ｆのハブ部４ｆ2 を支えるベアリング１７が配置さ
れている。なお、この例では、ベアリング１７の内側に
出力ギヤ５から突設された円筒部５ａを介してハブ部４
ｆ2 が支持されているが、円筒部５ａを省略してハブ部
４ｆ2 を直接支持してもよい。[0013] the inner diameter side of the seal unit 6b, a bearing 17 for supporting the hub portion 4f 2 of the ring gear 4f are arranged. In this example, the hub portion 4 is provided inside the bearing 17 via the cylindrical portion 5a protruding from the output gear 5.
Although f 2 is supported, it may support a hub portion 4f 2 directly to omit the cylindrical portion 5a.

【００１４】上記のように、リングギヤ４ｆのギヤ部４
ｆ1 がシール部６ｂの外径側にオーバーハングしている
ので、ベアリング１７の中心と遊星歯車装置４の重心と
の距離Ｌを短くすることができる。つまり、変速機の軸
方向寸法が短縮されるとともに、ベアリング１７の支持
剛性および回転精度が向上する。As described above, the gear portion 4 of the ring gear 4f
Since f 1 is overhanging on the outer diameter side of the seal portion 6b, it is possible to shorten the distance L between the center of gravity of the planetary gear unit 4 of the bearing 17. That is, the axial dimension of the transmission is reduced, and the support rigidity and rotational accuracy of the bearing 17 are improved.

【００１５】上記実施例では、摩擦係合装置がＢ２ブレ
ーキの例を示したが、遊星歯車装置と隣接配置されるも
のであれば、他の摩擦係合装置にも同様に適用できる。
また、本発明の遊星歯車装置はラビニヨウ型に限るもの
ではなく、他の形式の遊星歯車装置にも適用可能であ
る。In the above embodiment, the friction engagement device is an example of a B2 brake. However, if the friction engagement device is disposed adjacent to the planetary gear device, the invention can be similarly applied to other friction engagement devices.
Further, the planetary gear device of the present invention is not limited to the Ravigneaux type, but is also applicable to other types of planetary gear devices.

【００１６】[0016]

【発明の効果】以上の説明で明らかなように、本発明に
よれば、遊星リングギヤのギヤ部とハブ部とがスナップ
止めされ、その隣接位置にピストンを配置した自動変速
機において、ギヤ部の一端部がピストンの内径側シール
部の半径方向外側にオーバーハングするように構成し、
シール部の内径部に軸受を配置するようにしたので、軸
受の中心と遊星歯車装置の重心とを近づけることがで
き、変速機の軸方向寸法を短縮できるとともに、軸受の
支持剛性および回転精度を向上させることができる。As is apparent from the above description, according to the present invention, in the automatic transmission in which the gear portion and the hub portion of the planetary ring gear are snapped and the piston is disposed adjacent to the hub, One end is configured to overhang radially outward of the inner diameter side seal portion of the piston,
Since the bearing is arranged at the inner diameter of the seal part, the center of the bearing and the center of gravity of the planetary gear unit can be made closer, the axial dimension of the transmission can be shortened, and the bearing rigidity and rotational accuracy can be reduced. Can be improved.

【図面の簡単な説明】[Brief description of the drawings]

【図１】本発明にかかる車両用自動変速機の一例の概略
機構図である。FIG. 1 is a schematic mechanism diagram of an example of an automatic transmission for a vehicle according to the present invention.

【図２】図１の自動変速機の一部の詳細断面図である。FIG. 2 is a detailed sectional view of a part of the automatic transmission of FIG.

【符号の説明】[Explanation of symbols]

Ｂ２ 摩擦係合装置 ４ 遊星歯車装置 ４ｆ リングギヤ ４ｆ1 ギヤ部 ４ｆ2 ハブ部 ６ 変速機ケース ６ａ 凹部 ６ｂ シール部 １０ ピストン １４，１５ ディスク ２０ スナップリングB2 Friction engagement device 4 Planetary gear device 4f Ring gear 4f 1 gear portion 4f 2 hub portion 6 Transmission case 6a recessed portion 6b seal portion 10 piston 14, 15 disk 20 snap ring

Claims (1)

【特許請求の範囲】[Claims] 【請求項１】遊星歯車装置と摩擦係合装置とを隣接配置
してなる車両用自動変速機において、遊星歯車装置のリ
ングギヤはギヤ部とハブ部とが回り止めされ、かつスナ
ップリングによって軸方向に抜け止めされており、変速
機ケースの内側壁に油室を構成する凹部が形成され、こ
の凹部に軸方向に摺動自在にピストンが配置され、上記
ピストンの内径部は凹部の内径側側壁を構成するシール
部によってシールされ、上記スナップリングと係合する
リングギヤのギヤ部の一端部がシール部の半径方向外側
にオーバーハングしており、上記シール部の内径側にリ
ングギヤのハブ部を支える軸受が配置されていることを
特徴とする車両用自動変速機。In a vehicle automatic transmission in which a planetary gear device and a friction engagement device are disposed adjacent to each other, a ring gear of the planetary gear device has a gear portion and a hub portion that are prevented from rotating, and is axially moved by a snap ring. A recess that forms an oil chamber is formed in the inner wall of the transmission case, and a piston is slidably disposed in the recess in the axial direction. One end of the gear portion of the ring gear engaged with the snap ring overhangs radially outward of the seal portion, and supports the hub portion of the ring gear on the inner diameter side of the seal portion. An automatic transmission for a vehicle, wherein a bearing is arranged.
JP06438599A 1999-03-11 1999-03-11 Automatic transmission for vehicles Expired - Fee Related JP3512666B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP06438599A JP3512666B2 (en) 1999-03-11 1999-03-11 Automatic transmission for vehicles

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP06438599A JP3512666B2 (en) 1999-03-11 1999-03-11 Automatic transmission for vehicles

Publications (2)

Publication Number Publication Date
JP2000257702A true JP2000257702A (en) 2000-09-19
JP3512666B2 JP3512666B2 (en) 2004-03-31

Family

ID=13256809

Family Applications (1)

Application Number Title Priority Date Filing Date
JP06438599A Expired - Fee Related JP3512666B2 (en) 1999-03-11 1999-03-11 Automatic transmission for vehicles

Country Status (1)

Country Link
JP (1) JP3512666B2 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7107867B2 (en) 2003-05-22 2006-09-19 Toyoto Jidosha Kabushiki Kaisha Automatic transmission
WO2015080194A1 (en) * 2013-11-29 2015-06-04 アイシン・エィ・ダブリュ株式会社 Multi-stage transmission

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7107867B2 (en) 2003-05-22 2006-09-19 Toyoto Jidosha Kabushiki Kaisha Automatic transmission
WO2015080194A1 (en) * 2013-11-29 2015-06-04 アイシン・エィ・ダブリュ株式会社 Multi-stage transmission
CN105705828A (en) * 2013-11-29 2016-06-22 爱信艾达株式会社 multi-speed transmission
JPWO2015080194A1 (en) * 2013-11-29 2017-03-16 アイシン・エィ・ダブリュ株式会社 Multi-speed transmission
CN105705828B (en) * 2013-11-29 2018-04-03 爱信艾达株式会社 multi-speed transmission
US10208836B2 (en) 2013-11-29 2019-02-19 Aisin Aw Co., Ltd. Multi-stage transmission

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