JP2000240741A - Transmission - Google Patents
TransmissionInfo
- Publication number
- JP2000240741A JP2000240741A JP11043503A JP4350399A JP2000240741A JP 2000240741 A JP2000240741 A JP 2000240741A JP 11043503 A JP11043503 A JP 11043503A JP 4350399 A JP4350399 A JP 4350399A JP 2000240741 A JP2000240741 A JP 2000240741A
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- planetary gear
- speed
- gear unit
- input shaft
- 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
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
- F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
Landscapes
- Structure Of Transmissions (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は変速装置に関するも
のであり、例えば自動車の自動変速装置に用いられる変
速装置に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission, and more particularly to a transmission used for an automatic transmission of an automobile.
【０００２】[0002]
【従来の技術】従来の変速装置として、例えば特開平６
−３２３３８１号公報に開示される技術がある。この公
報には、３つのプラネタリギヤユニットが直列に配置さ
れ、各プラネタリギヤユニットはそれぞれ１つのリング
ギヤ、キャリヤ、サンギヤを用いている。これらのギヤ
を使用して、外力で駆動される５つの係合要素（２つの
クラッチと３つのブレーキ）を介して６つの前進ギヤ段
と１つの後進ギヤ段を切換え可能な変速装置が開示され
ている。2. Description of the Related Art A conventional transmission is disclosed in, for example,
There is a technique disclosed in JP-A-323381. In this publication, three planetary gear units are arranged in series, and each planetary gear unit uses one ring gear, carrier, and sun gear. A transmission that can switch between six forward gears and one reverse gear through five engagement elements (two clutches and three brakes) driven by external force using these gears is disclosed. ing.
【０００３】[0003]
【発明が解決しようとする課題】ここで、トラック等の
商用系の車両は積載荷重によってエンジントルクに対し
て車両重量が大きくなる傾向があるため、出力軸の駆動
トルクが大きい変速装置を採用することが好ましい。し
かしながら上記公報に開示される変速装置は、前進ギヤ
段を６つ構成しているが、アンダードライブは１速から
４速までで５速と６速はオーバードライブである。した
がって上記の変速装置を商用系の車両へ採用した場合、
オーバードライブである５速と６速は駆動トルクが小さ
くなってしまうため５速と６速の使用頻度が少なくな
り、商用系の車両へ採用するには実用性の面から適切で
はない、という問題がある。Here, since commercial vehicles such as trucks tend to increase the vehicle weight relative to the engine torque due to the loaded load, a transmission having a large driving torque for the output shaft is employed. Is preferred. However, the transmission disclosed in the above publication has six forward gears, but underdrive is from first gear to fourth gear, and fifth and sixth gears are overdrive. Therefore, when the above-described transmission is adopted in a commercial vehicle,
5th and 6th speeds, which are overdrives, have a low drive torque, so the 5th and 6th speeds are used less frequently, and are not suitable for practical use in commercial vehicles. There is.
【０００４】そこで本発明は、上記問題点を解決すべ
く、３列のプラネタリギヤで５つの摩擦係合要素を用い
て、１速から５速がアンダードライブで、６速がオーバ
ードライブである前進６段の変速装置を提供することを
技術的課題とする。In order to solve the above-mentioned problems, the present invention employs three rows of planetary gears and five frictional engagement elements, and the first to fifth speeds are underdrive and the sixth speed is overdrive. It is a technical object to provide a stepped transmission.
【０００５】[0005]
【課題を解決するための手段】上記課題を解決するため
に請求項１の発明は、入力軸と、出力軸と、キャリヤを
入力軸と連結した第１列のダブルピニオンプラネタリギ
ヤと、第２列のシングルピニオンプラネタリギヤのキャ
リヤ及びリングギヤと第３列のシングルピニオンプラネ
タリギヤのリングギヤ及びキャリヤとをそれぞれ連結し
て第１〜第４の軸要素を具備させ且つ第３の軸要素を出
力軸に連結するとともに第４の軸要素を第１列のダブル
ピニオンプラネタリギヤのリングギヤに連結したプラネ
タリギヤユニットと、入力軸とプラネタリギヤユニット
の第２の軸要素とを選択的に連結するための第１の摩擦
クラッチ要素Ｃ１と、入力軸とプラネタリギヤユニット
の第１の軸要素とを選択的に連結するための第２の摩擦
クラッチ要素Ｃ２と、プラネタリギヤユニットの第１の
軸要素を選択的に固定するための第１の摩擦ブレーキ要
素Ｂ１と、プラネタリギヤユニットの第２の軸要素を選
択的に固定するための第２の摩擦ブレーキ要素Ｂ２と、
第１列のダブルピニオンプラネタリギヤのサンギヤを選
択的に固定するための第３の摩擦ブレーキ要素Ｂ３と、
を備える変速装置とした。SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, a first aspect of the present invention provides an input shaft, an output shaft, a first row of double pinion planetary gears having a carrier connected to an input shaft, and a second row. And the third row of single pinion planetary gears and the third row of single pinion planetary gears are respectively connected to the carrier and ring gear of the third row to provide first to fourth shaft elements and to connect the third shaft element to the output shaft. A planetary gear unit in which the fourth shaft element is connected to the ring gear of the first row of double pinion planetary gears; a first friction clutch element C1 for selectively connecting the input shaft and the second shaft element of the planetary gear unit; Friction clutch element C2 for selectively connecting the input shaft and the first shaft element of the planetary gear unit. A first friction brake element B1 for selectively fixing a first shaft element of the planetary gear unit, and a second friction brake element B2 for selectively fixing a second shaft element of the planetary gear unit. ,
A third friction brake element B3 for selectively fixing the sun gear of the first row of double pinion planetary gears;
Transmission.
【０００６】請求項１の変速装置によると、３列のプラ
ネタリギヤで５つの摩擦係合要素（摩擦クラッチ要素Ｃ
１、Ｃ２、摩擦ブレーキ要素Ｂ１、Ｂ２、Ｂ３）を切換
えて１速から５速がアンダードライブ、６速がオーバー
ドライブの前進６段、後進１段の変速装置を構成するこ
とができる。この変速装置を車両重量に比べてエンジン
トルクが比較的小さい車両に採用した場合には、変速装
置の１速から５速がアンダードライブであるため、この
範囲内の変速段で走行しても車速が制限されることなく
通常に走行することが可能になる。更に、１速から５速
の変速段がクロスされるので変速ショックが低減され
る。According to the transmission of the first aspect, three friction engagement elements (friction clutch elements C) are provided by three rows of planetary gears.
1, C2 and the friction brake elements B1, B2, B3) can be switched to form a 6-speed underdrive in the 1st to 5th speed, a 6-speed overdrive forward 6-speed, and a reverse 1-speed transmission. When this transmission is used in a vehicle having a relatively small engine torque compared to the vehicle weight, the first to fifth speeds of the transmission are underdrive. Can be driven normally without restriction. Further, since the first to fifth gears are crossed, the shift shock is reduced.
【０００７】上記課題を解決するために請求項２の発明
は、入力軸と、出力軸と、キャリヤを入力軸と連結し且
つサンギヤを固定した第１列のダブルピニオンプラネタ
リギヤと、第２列のシングルピニオンプラネタリギヤの
キャリヤ及びリングギヤと第３列のシングルピニオンプ
ラネタリギヤのリングギヤ及びキャリヤとをそれぞれ連
結して第１〜第４の軸要素を具備させ且つ第３の軸要素
を出力軸と連結してなるプラネタリギヤユニットと、入
力軸とプラネタリギヤユニットの第２の軸要素とを選択
的に連結するための第１の摩擦クラッチ要素Ｃ１と、入
力軸とプラネタリギヤユニットの第１の軸要素とを選択
的に連結するための第２の摩擦クラッチ要素Ｃ２と、第
１列のダブルピニオンプラネタリギヤのリングギヤとプ
ラネタリギヤユニットの第４の軸要素とを選択的に連結
するための第３の摩擦クラッチ要素Ｃ０と、プラネタリ
ギヤユニットの第１の軸要素を選択的に固定するための
第１の摩擦ブレーキ要素Ｂ１と、プラネタリギヤユニッ
トの第２の軸要素を選択的に固定するための第２の摩擦
ブレーキ要素Ｂ２と、を備える変速装置とした。In order to solve the above-mentioned problems, a second aspect of the present invention is to provide a first row of double pinion planetary gears in which an input shaft, an output shaft, a carrier is connected to an input shaft and a sun gear is fixed, The carrier and ring gear of the single pinion planetary gear and the ring gear and carrier of the third row of single pinion planetary gears are respectively connected to provide first to fourth shaft elements, and the third shaft element is connected to the output shaft. A first friction clutch element C1 for selectively connecting the planetary gear unit, the input shaft and the second shaft element of the planetary gear unit, and a selectively connecting the input shaft and the first shaft element of the planetary gear unit; A second friction clutch element C2, and a ring gear and a planetary gear unit of the first row of double pinion planetary gears. A third friction clutch element C0 for selectively connecting the fourth shaft element of the planetary gear unit, a first friction brake element B1 for selectively fixing the first shaft element of the planetary gear unit, And a second friction brake element B2 for selectively fixing the second shaft element of the planetary gear unit.
【０００８】請求項２に示す変速装置によると、３列の
プラネタリギヤで５つの摩擦係合要素（摩擦クラッチ要
素Ｃ１、Ｃ２、Ｃ０、摩擦ブレーキ要素Ｂ１、Ｂ２）を
切換えて１速から５速がアンダードライブ、６速がオー
バードライブの前進６段、後進１段の変速装置を構成す
ることができる。更に請求項２によると、第３の摩擦ク
ラッチ要素Ｃ０を設けたことで入力軸のトルクがプラネ
タリギヤユニットに入力されることがなくなって、第１
列のダブルピニオンプラネタリギヤのピニオンギヤが無
負荷で高速回転するのを抑えることが可能になり、ギヤ
ノイズを低減するとともにギヤの耐久性を向上すること
ができる。According to a second aspect of the present invention, the first to fifth speeds are changed by switching five friction engagement elements (friction clutch elements C1, C2, C0, and friction brake elements B1, B2) with three rows of planetary gears. An underdrive and a 6th speed can constitute an overdrive forward 6-speed and reverse 1-speed transmission. Further, according to the second aspect, the provision of the third friction clutch element C0 prevents the torque of the input shaft from being input to the planetary gear unit.
It is possible to prevent the pinion gears of the double pinion planetary gears in the row from rotating at high speed without load, thereby reducing gear noise and improving gear durability.
【０００９】[0009]
【実施の形態】本発明の実施の形態を図面を参照して説
明する。本実施の形態では、自動車用の自動変速装置に
用いた場合について説明する。Embodiments of the present invention will be described with reference to the drawings. In the present embodiment, a case where the present invention is used for an automatic transmission for an automobile will be described.
【００１０】図１は本発明の第１の実施の形態における
自動変速装置１０のギヤトレーンを示す概略図である。
自動変速装置１０はハウジング１内に配設され、図示し
ないエンジンの出力を粘性媒体の剪断力を介して変速装
置１０に出力するトルクコンバータ２からの出力を摩擦
係合要素の切換えに応じて前進６速、後進１速に増減速
切換えして、図示しない車軸に出力する。FIG. 1 is a schematic diagram showing a gear train of an automatic transmission 10 according to a first embodiment of the present invention.
The automatic transmission 10 is disposed in the housing 1, and outputs the output of the engine (not shown) to the transmission 10 through the shearing force of the viscous medium. The output from the torque converter 2 advances in accordance with the switching of the friction engagement element. The speed is switched between the sixth speed and the first reverse speed, and output to an axle not shown.
【００１１】変速装置１０は、トルクコンバータ２の出
力軸である入力軸１１と、図示しない差動装置を介して
車軸に連結される出力軸１２と、入力軸１１と連結する
キャリヤＰＣ１を有する第１列のダブルピニオンプラネ
タリギヤＧ１（以下、第１プラネタリギヤＧ１と称す）
と、第２列のシングルピニオンプラネタリギヤＧ２（以
下、第２プラネタリギヤＧ２と称す）及び第３列のシン
グルピニオンプラネタリギヤＧ３（以下、第３プラネタ
リギヤＧ３と称す）を備え、第２プラネタリギヤＧ２の
キャリヤＰＣ２を第３プラネタリギヤＧ３のリングギヤ
Ｒ３に連結するとともに第２プラネタリギヤＧ２のリン
グギヤＲ２を第３プラネタリギヤＧ３のキャリヤＰＣ３
に連結して第１〜第４の軸要素Ｊ１〜Ｊ４を具備し、且
つ第３の軸要素Ｊ３を出力軸１２に連結するとともに第
４の軸要素Ｊ４を第１プラネタリギヤＧ１のリングギヤ
Ｒ１に連結したプラネタリギヤユニットＧ２３と、入力
軸１１とプラネタリギヤユニットＧ２３の第２の軸要素
Ｊ２とを選択的に連結するための第１の摩擦クラッチ要
素Ｃ１と、入力軸１１とプラネタリギヤユニットＧ２３
の第１の軸要素Ｊ１とを選択的に連結するための第２の
摩擦クラッチ要素Ｃ２と、第１プラネタリギヤＧ１のサ
ンギヤＳ１を選択的に固定するための第３の摩擦ブレー
キ要素Ｂ３と、プラネタリギヤユニットＧ２３の第１の
軸要素Ｊ１を選択的に固定するための第１の摩擦ブレー
キ要素Ｂ１と、プラネタリギヤユニットＧ２３の第２の
軸要素Ｊ２を選択的に固定するための第２の摩擦ブレー
キ要素Ｂ２と、を備える。The transmission 10 has an input shaft 11 as an output shaft of the torque converter 2, an output shaft 12 connected to the axle via a differential (not shown), and a carrier PC1 connected to the input shaft 11. One row of double pinion planetary gears G1 (hereinafter, referred to as first planetary gears G1)
And a second row of single pinion planetary gears G2 (hereinafter, referred to as a second planetary gear G2) and a third row of single pinion planetary gears G3 (hereinafter, referred to as a third planetary gear G3). The ring gear R2 of the second planetary gear G2 is connected to the ring gear R3 of the third planetary gear G3 and the carrier PC3 of the third planetary gear G3.
, The first shaft element J3 is connected to the output shaft 12, and the fourth shaft element J4 is connected to the ring gear R1 of the first planetary gear G1. Planetary gear unit G23, a first friction clutch element C1 for selectively connecting the input shaft 11 and the second shaft element J2 of the planetary gear unit G23, an input shaft 11 and a planetary gear unit G23.
A second friction clutch element C2 for selectively connecting the first shaft element J1 to the first shaft element J1, a third friction brake element B3 for selectively fixing the sun gear S1 of the first planetary gear G1, and a planetary gear. A first friction brake element B1 for selectively fixing the first shaft element J1 of the unit G23 and a second friction brake element for selectively fixing the second shaft element J2 of the planetary gear unit G23. B2.
【００１２】第１プラネタリギヤＧ１では、ρ１＝サン
ギヤＳ１の歯数／リングギヤＲ１の歯数＝０．３、第２
プラネタリギヤＧ２では、ρ２＝サンギヤＳ２の歯数／
リングギヤＲ２の歯数＝０．４、第３プラネタリギヤＧ
３では、ρ３＝サンギヤＳ３の歯数／リングギヤＲ３の
歯数＝０．６である。In the first planetary gear G1, ρ1 = the number of teeth of the sun gear S1 / the number of teeth of the ring gear R1 = 0.3, the second
In the planetary gear G2, ρ2 = the number of teeth of the sun gear S2 /
Number of teeth of ring gear R2 = 0.4, third planetary gear G
In No. 3, ρ3 = number of teeth of sun gear S3 / number of teeth of ring gear R3 = 0.6.
【００１３】表１に第１の実施の形態における各係合要
素の組み合せ及びギヤ比を示す。Table 1 shows combinations of engagement elements and gear ratios in the first embodiment.
【００１４】[0014]
【表１】 [Table 1]
【００１５】尚、表１において○は係合状態を、空欄は
開放状態を示している。In Table 1, 表 indicates an engaged state, and a blank indicates an open state.
【００１６】表１における変速段の切換えについて説明
する。１速では、第３の摩擦ブレーキ要素Ｂ３にて第１
プラネタリギヤＧ１のサンギヤＳ１を固定して入力軸１
１のトルクを増大させ、プラネタリギヤユニットＧ２３
の第４の軸要素Ｊ４に入力軸１１のトルクが伝達される
とともに、プラネタリギヤユニットＧ２３の第２の軸要
素Ｊ２を第２の摩擦ブレーキ要素Ｂ２にて固定すること
で第３の軸要素Ｊ３が減速回転され、１速を形成する。A description will now be given of the switching of the shift speeds in Table 1. In the first speed, the first friction brake element B3
With the sun gear S1 of the planetary gear G1 fixed and the input shaft 1
1 to increase the planetary gear unit G23.
The torque of the input shaft 11 is transmitted to the fourth shaft element J4, and the second shaft element J2 of the planetary gear unit G23 is fixed by the second friction brake element B2, so that the third shaft element J3 is It is rotated at a reduced speed to form the first speed.
【００１７】２速では、第３の摩擦ブレーキ要素Ｂ３に
て第１プラネタリギヤＧ１のサンギヤＳ１を固定して入
力軸１１のトルクを増大させ、プラネタリギヤユニット
Ｇ２３の第４の軸要素Ｊ４に入力軸１１のトルクが伝達
されるとともに、プラネタリギヤユニットＧ２３の第１
の軸要素Ｊ１を第１の摩擦ブレーキ要素Ｂ１で固定する
ことで第３の軸要素Ｊ３が減速回転され、２速を形成す
る。In the second speed, the sun gear S1 of the first planetary gear G1 is fixed by the third friction brake element B3 to increase the torque of the input shaft 11, and the input shaft 11 is connected to the fourth shaft element J4 of the planetary gear unit G23. And the first torque of the planetary gear unit G23 is transmitted.
Is fixed by the first friction brake element B1, the third shaft element J3 is decelerated and rotated to form the second speed.
【００１８】３速では、第１の摩擦ブレーキ要素Ｂ１に
て第１プラネタリギヤＧ１のサンギヤＳ１を固定して入
力軸１１のトルクを増大させ、プラネタリギヤユニット
Ｇ２３の第４の軸要素Ｊ４に入力軸１１のトルクが伝達
されるとともに、第２の摩擦クラッチ要素Ｃ２を係合し
て入力軸１１のトルクを第１の軸要素Ｊ１に入力するこ
とで第３の軸要素Ｊ３が減速回転され、３速を形成す
る。In the third speed, the sun gear S1 of the first planetary gear G1 is fixed by the first friction brake element B1 to increase the torque of the input shaft 11, and the input shaft 11 is connected to the fourth shaft element J4 of the planetary gear unit G23. Is transmitted, the second friction clutch element C2 is engaged, and the torque of the input shaft 11 is input to the first shaft element J1, whereby the third shaft element J3 is rotated at a reduced speed. To form
【００１９】４速では、第３の摩擦ブレーキ要素Ｂ３に
て第１プラネタリギヤＧ１のサンギヤＳ１を固定して入
力軸１１のトルクを増大させ、プラネタリギヤユニット
Ｇ２３の第４の軸要素Ｊ４に入力軸１１のトルクが伝達
されるとともに、第１の摩擦クラッチ要素Ｃ１を係合し
て入力軸１１のトルクを第２の軸要素Ｊ２に入力するこ
とで第３の軸要素Ｊ３が減速回転され、４速を形成す
る。In the fourth speed, the sun gear S1 of the first planetary gear G1 is fixed by the third friction brake element B3 to increase the torque of the input shaft 11, and the input shaft 11 is connected to the fourth shaft element J4 of the planetary gear unit G23. Is transmitted, the first friction clutch element C1 is engaged, and the torque of the input shaft 11 is input to the second shaft element J2, so that the third shaft element J3 is rotated at a reduced speed. To form
【００２０】５速では、第１の摩擦クラッチ要素Ｃ１及
び第２の摩擦クラッチ要素Ｃ２を係合して入力軸１１の
トルクをプラネタリギヤユニットＧ２３の第２の軸要素
Ｊ２に伝達することで、プラネタリギヤユニットＧ２３
が入力軸１１と一体回転し、５速を形成する。In the fifth speed, the first friction clutch element C1 and the second friction clutch element C2 are engaged to transmit the torque of the input shaft 11 to the second shaft element J2 of the planetary gear unit G23. Unit G23
Rotate integrally with the input shaft 11 to form the fifth speed.
【００２１】６速では、第１の摩擦クラッチ要素Ｃ１を
係合して入力軸１１のトルクをプラネタリギヤユニット
Ｇ２３の第２の軸要素Ｊ２に伝達するとともに、第１の
摩擦ブレーキ要素Ｂ１にてプラネタリギヤユニットＧ２
３の第１の軸要素Ｊ１を固定することで第３の軸要素Ｊ
３が増速回転され、オーバードライブである６速を形成
する。In the sixth speed, the first friction clutch element C1 is engaged to transmit the torque of the input shaft 11 to the second shaft element J2 of the planetary gear unit G23, and the first friction brake element B1 Unit G2
The third axis element J1 is fixed by fixing the third axis element J1.
3 is rotated at an increased speed to form a sixth speed which is an overdrive.
【００２２】後進では、第２の摩擦クラッチ要素Ｃ２を
係合して入力軸１１のトルクをプラネタリギヤユニット
Ｇ２３の第１の軸要素Ｊ１に伝達し、第２の摩擦ブレー
キ要素Ｂ２にてプラネタリギヤユニットＧ２３の第３の
軸要素Ｊ３が逆回転され、後進を形成する。In reverse, the second friction clutch element C2 is engaged to transmit the torque of the input shaft 11 to the first shaft element J1 of the planetary gear unit G23, and the planetary gear unit G23 is driven by the second friction brake element B2. Of the third shaft element J3 is reversely rotated to form a reverse movement.
【００２３】上述したように各摩擦係合要素を切換える
ことで、３列のプラネタリギヤＧ１、Ｇ２、Ｇ３と５つ
の摩擦係合要素Ｃ１、Ｃ２、Ｂ１、Ｂ２、Ｂ３でアンダ
ードライブ５速、オーバードライブ１速の前進６速、後
進１速の変速装置１０を構成することができる。By switching the friction engagement elements as described above, the three rows of planetary gears G1, G2, G3 and the five friction engagement elements C1, C2, B1, B2, B3 are used to drive underdrive at the fifth speed and overdrive. The transmission 10 having six forward speeds and one reverse speed can be configured.
【００２４】次に、本発明の第２の実施の形態における
変速装置２０について説明する。図２は第２の実施の形
態における自動変速装置２０のギヤトレーンを示す概略
図である。Next, a description will be given of a transmission 20 according to a second embodiment of the present invention. FIG. 2 is a schematic diagram showing a gear train of the automatic transmission 20 according to the second embodiment.
【００２５】第２の実施の形態の変速装置２０は、上述
した第１の実施の形態の変速装置１０に対して、第１プ
ラネタリギヤＧ１のサンギヤＳ１を選択的に固定する摩
擦ブレーキ要素をなくして常にハウジング１に固定させ
るとともに、第１プラネタリギヤＧ１のリングギヤＲ１
とプラネタリギヤユニットＧ２３の第４の軸要素Ｊ４と
を選択的に連結する第３の摩擦クラッチ要素Ｃ０を設け
たことが異なり、これ以外の構成については同一である
ため説明を省略する。The transmission 20 of the second embodiment differs from the transmission 10 of the first embodiment in that the friction brake element for selectively fixing the sun gear S1 of the first planetary gear G1 is eliminated. The ring gear R1 of the first planetary gear G1 is always fixed to the housing 1.
And a third friction clutch element C0 for selectively connecting the third shaft element J4 of the planetary gear unit G23 and the fourth shaft element J4 of the planetary gear unit G23.
【００２６】表２に第２の実施の形態における各係合要
素の組み合せ及びギヤ比を示す。Table 2 shows the combinations of the engagement elements and the gear ratios according to the second embodiment.
【００２７】[0027]
【表２】 [Table 2]
【００２８】尚、表２において○は係合状態を、空欄は
開放状態を示している。In Table 2, .largecircle. Indicates an engaged state, and a blank indicates an open state.
【００２９】表２における変速段の切換えについて説明
する。１速では、第３の摩擦クラッチ要素Ｃ０が係合し
て入力軸１１のトルクを増大させ、プラネタリギヤユニ
ットＧ２３の第４の軸要素Ｊ４に増大したトルクを伝達
するとともに、第２の摩擦ブレーキ要素Ｂ２にて第２の
軸要素Ｊ２を固定することで第３の軸要素Ｊ３が減速回
転され、１速を形成する。A description will now be given of the switching of the shift speed in Table 2. In the first speed, the third friction clutch element C0 is engaged to increase the torque of the input shaft 11 and transmit the increased torque to the fourth shaft element J4 of the planetary gear unit G23, and the second friction brake element By fixing the second shaft element J2 at B2, the third shaft element J3 is rotated at a reduced speed to form the first speed.
【００３０】２速では、第３の摩擦クラッチ要素Ｃ０が
係合して入力軸１１のトルクを増大させ、プラネタリギ
ヤユニットＧ２３の第４の軸要素Ｊ４に増大した伝達す
るとともに、第１の摩擦ブレーキ要素Ｂ１にてプラネタ
リギヤユニットＧ２３の第１の軸要素Ｊ１を固定するこ
とで第３の軸要素Ｊ３が減速回転され、２速を形成す
る。In the second speed, the third friction clutch element C0 is engaged to increase the torque of the input shaft 11 and transmit the increased torque to the fourth shaft element J4 of the planetary gear unit G23, and the first friction brake By fixing the first shaft element J1 of the planetary gear unit G23 by the element B1, the third shaft element J3 is rotated at a reduced speed to form the second speed.
【００３１】３速では、第３の摩擦クラッチ要素Ｃ０が
係合して入力軸１１のトルクを増大させ、プラネタリギ
ヤユニットＧ２３の第４の軸要素Ｊ４に増大したトルク
を伝達するとともに、第２の摩擦クラッチ要素Ｃ２を係
合して第１の軸要素Ｊ１に入力軸１１のトルクを伝達す
ることで第３の軸要素Ｊ３が減速回転され、３速を形成
する。In the third speed, the third friction clutch element C0 is engaged to increase the torque of the input shaft 11, transmit the increased torque to the fourth shaft element J4 of the planetary gear unit G23, and By engaging the friction clutch element C2 and transmitting the torque of the input shaft 11 to the first shaft element J1, the third shaft element J3 is rotated at a reduced speed to form the third speed.
【００３２】４速では、第３の摩擦クラッチ要素Ｃ０が
係合して入力軸１１のトルクを増大させ、プラネタリギ
ヤユニットＧ２３の第４の軸要素Ｊ４に増大したトルク
を伝達するとともに、第１の摩擦クラッチ要素Ｃ１を係
合して第２の軸要素Ｊ２に入力軸１１のトルクを伝達す
ることで、第３の軸要素Ｊ３が減速回転され、４速を形
成する。In the fourth speed, the third friction clutch element C0 is engaged to increase the torque of the input shaft 11 and transmit the increased torque to the fourth shaft element J4 of the planetary gear unit G23. By engaging the friction clutch element C1 and transmitting the torque of the input shaft 11 to the second shaft element J2, the third shaft element J3 is rotated at a reduced speed to form the fourth speed.
【００３３】５速では、第１の摩擦クラッチ要素Ｃ１を
係合して入力軸１１のトルクをプラネタリギヤユニット
Ｇ２３の第２の軸要素Ｊ２に伝達するとともに、第２の
摩擦クラッチ要素Ｃ２を係合してプラネタリギヤユニッ
トＧ２３を一体回転させることで、５速を形成する。In the fifth speed, the first friction clutch element C1 is engaged to transmit the torque of the input shaft 11 to the second shaft element J2 of the planetary gear unit G23, and the second friction clutch element C2 is engaged. The fifth speed is formed by integrally rotating the planetary gear unit G23.
【００３４】６速では、第１の摩擦クラッチ要素Ｃ１を
係合してプラネタリギヤユニットＧ２３の第２の軸要素
Ｊ２に入力軸１１のトルクを伝達するとともに、第１の
摩擦ブレーキ要素Ｂ１にて第１の軸要素Ｊ１を固定する
ことで第３の軸要素Ｊ３が増速回転され、６速を形成す
る。At the sixth speed, the first friction clutch element C1 is engaged to transmit the torque of the input shaft 11 to the second shaft element J2 of the planetary gear unit G23. By fixing the first shaft element J1, the third shaft element J3 is rotated at an increased speed to form the sixth speed.
【００３５】後進は、第２の摩擦クラッチ要素Ｃ２を係
合してプラネタリギヤユニットＧ２３の第１の軸要素Ｊ
１に入力軸１１のトルクを伝達するとともに、第２の摩
擦ブレーキ要素Ｂ２にて第２の軸要素Ｊ２を固定するこ
とで第３の軸要素Ｊ３が逆回転され、後進を形成する。In reverse, the second friction clutch element C2 is engaged to engage the first shaft element J of the planetary gear unit G23.
1, the torque of the input shaft 11 is transmitted to the first shaft element 1, and the second shaft element J2 is fixed by the second friction brake element B2, whereby the third shaft element J3 is rotated in the reverse direction to form a reverse movement.
【００３６】上述したように各摩擦係合要素を切換える
ことで、３列のプラネタリギヤＧ１、Ｇ２、Ｇ３と５つ
の摩擦係合要素Ｃ１、Ｃ２、Ｃ０、Ｂ１、Ｂ２でアンダ
ードライブ５速、オーバードライブ１速の前進６速、後
進１速の変速装置２０を構成することができる。By switching the respective friction engagement elements as described above, the three rows of planetary gears G1, G2, G3 and the five friction engagement elements C1, C2, C0, B1, B2 are used to drive the underdrive at the fifth speed and the overdrive. The transmission 20 having six forward speeds and one reverse speed can be configured.
【００３７】更に、第３の摩擦クラッチ要素Ｃ０を用い
たことによって、第４の軸要素Ｊ４に負荷がかからない
状態ではリングギヤＲ１と第４の軸要素Ｊ４とを切り離
すことが可能になり、６速及び後進時に第１プラネタリ
ギヤＧ１のピニオンギヤが高速無負荷回転することがな
くなる。６速及び後進時におけるギヤノイズを低減する
とともに第１プラネタリギヤＧ１の耐久性を向上するこ
とができる。Further, by using the third friction clutch element C0, the ring gear R1 and the fourth shaft element J4 can be separated from each other when no load is applied to the fourth shaft element J4. In addition, the pinion gear of the first planetary gear G1 does not rotate at high speed and no load during reverse travel. It is possible to reduce gear noise at the sixth speed and at the time of reverse running, and to improve the durability of the first planetary gear G1.
【００３８】プラネタリギヤユニットＧ２３に関して、
第２プラネタリギヤＧ２と第３プラネタリギヤＧ３にお
けるキャリヤＰＣ２、ＰＣ３とリングギヤＲ２、Ｒ３と
の繋ぎの組み合せパターンは、第１及び第２の実施の形
態で説明したパターン以外に４つのパターンが考えられ
る。この４つのパターンを図３〜図６に示す。図３〜図
６に示す構成のプラネタリギヤユニットＧ２３は第１及
び第２の実施の形態で説明したパターンのプラネタリギ
ヤユニットＧ２３と置換可能であり、図３〜図６に示す
プラネタリギヤユニットＧ２３を置換した場合には表１
或いは表２に示す摩擦係合要素の係合・開放の組み合せ
と同一になる。更に置換するプラネタリギヤユニットＧ
２３の歯数を第１及び第２の実施の形態と同一にする
と、表１或いは表２に示すギヤ比も同一になる。With respect to the planetary gear unit G23,
In the second planetary gear G2 and the third planetary gear G3, the combination pattern of the connection between the carriers PC2, PC3 and the ring gears R2, R3 may be four patterns other than the patterns described in the first and second embodiments. These four patterns are shown in FIGS. The planetary gear unit G23 having the configuration shown in FIGS. 3 to 6 can be replaced with the planetary gear unit G23 having the pattern described in the first and second embodiments, and the planetary gear unit G23 shown in FIGS. 3 to 6 is replaced. Table 1
Alternatively, it is the same as the combination of engagement and release of the friction engagement elements shown in Table 2. Planetary gear unit G to be further replaced
When the number of teeth of 23 is the same as in the first and second embodiments, the gear ratios shown in Table 1 or Table 2 also become the same.
【００３９】以上、本発明の実施の形態について説明し
たが、本発明は上述した実施の形態に限定される意図は
なく、本発明の主旨に沿った形態の変速装置であればど
のような形態であってもよい。Although the embodiment of the present invention has been described above, the present invention is not intended to be limited to the above-described embodiment, and any form of transmission that conforms to the gist of the present invention can be used. It may be.
【００４０】[0040]
【発明の効果】請求項１の変速装置によると、３列のプ
ラネタリギヤで５つの摩擦係合要素（摩擦クラッチ要素
Ｃ１、Ｃ２、摩擦ブレーキ要素Ｂ１、Ｂ２、Ｂ３）を切
換えて１速から５速がアンダードライブ、６速がオーバ
ードライブの前進６段、後進１段の変速装置を構成する
ことができる。これにより、この変速装置を車両重量に
比べてエンジントルクが比較的小さい車両に採用した場
合には、変速装置の１速から５速がアンダードライブで
あるため、この範囲内の変速段で走行しても車速が制限
されることなく通常に走行することが可能になる。更
に、１速から５速の変速段がクロスされるので変速ショ
ックが低減される。According to the transmission of the first aspect, three frictional engagement elements (friction clutch elements C1, C2 and friction brake elements B1, B2, B3) are switched by the three rows of planetary gears, and the first to fifth speeds are selected. The transmission can be configured with six forward speeds and six reverse speeds with an underdrive and six speeds with an overdrive. As a result, when the transmission is employed in a vehicle having a relatively small engine torque compared to the vehicle weight, the first to fifth speeds of the transmission are underdriven, so that the vehicle travels at a speed within this range. Even if the vehicle speed is not limited, the vehicle can travel normally. Further, since the first to fifth gears are crossed, the shift shock is reduced.
【００４１】請求項２の変速装置によると、３列のプラ
ネタリギヤで５つの摩擦係合要素（摩擦クラッチ要素Ｃ
１、Ｃ２、Ｃ０、摩擦ブレーキ要素Ｂ１、Ｂ２）を切換
えて１速から５速がアンダードライブ、６速がオーバー
ドライブの前進６段、後進１段の変速装置を構成するこ
とができる。更に請求項２によると、第３の摩擦クラッ
チ要素Ｃ０を設けたことで入力軸のトルクがプラネタリ
ギヤユニットに入力されることがなくなって、第１列の
ダブルピニオンプラネタリギヤのピニオンギヤが無負荷
で高速回転するのを抑えることが可能になり、ギヤノイ
ズを低減するとともにギヤの耐久性を向上することがで
きる。According to the transmission of the second aspect, five friction engagement elements (friction clutch elements C) are provided by three rows of planetary gears.
1, C2, C0, and friction brake elements B1, B2) can be switched to form a 6-speed underdrive, 6-speed overdrive in 6th speed, and a 1-speed reverse drive. Further, according to the second aspect, the provision of the third friction clutch element C0 prevents the torque of the input shaft from being input to the planetary gear unit, and the pinion gears of the first row of double pinion planetary gears rotate at high speed without load. This makes it possible to reduce gear noise and improve the durability of the gear.
【図１】本発明の第１の実施の形態における変速装置の
概略図である。FIG. 1 is a schematic diagram of a transmission according to a first embodiment of the present invention.
【図２】本発明の第２の実施の形態における変速装置の
概略図である。FIG. 2 is a schematic diagram of a transmission according to a second embodiment of the present invention.
【図３】本発明のプラネタリギヤユニットの別の組み合
せパターンを示す概略図である。FIG. 3 is a schematic view showing another combination pattern of the planetary gear unit of the present invention.
【図４】本発明のプラネタリギヤユニットの別の組み合
せパターンを示す概略図である。FIG. 4 is a schematic view showing another combination pattern of the planetary gear unit of the present invention.
【図５】本発明のプラネタリギヤユニットの別の組み合
せパターンを示す概略図である。FIG. 5 is a schematic view showing another combination pattern of the planetary gear unit of the present invention.
【図６】本発明のプラネタリギヤユニットの別の組み合
せパターンを示す概略図である。FIG. 6 is a schematic view showing another combination pattern of the planetary gear unit of the present invention.
１・・・ハウジング ２・・・トルクコンバータ １０、２０・・・変速装置 １１・・・入力軸 １２・・・出力軸 Ｇ１・・・第１列のダブルピニオンプラネタリギヤ Ｇ２・・・第２列のシングルピニオンプラネタリギヤ Ｇ３・・・第３列のシングルピニオンプラネタリギヤ Ｇ２３・・・プラネタリギヤユニット Ｓ１、Ｓ２、Ｓ３・・・サンギヤ Ｒ１、Ｒ２、Ｒ３・・・リングギヤ ＰＣ１、ＰＣ２、ＰＣ３・・・キャリヤ Ｃ０、Ｃ１、Ｃ２・・・摩擦クラッチ要素 Ｂ１、Ｂ２、Ｂ３・・・摩擦ブレーキ要素 Ｊ１、Ｊ２、Ｊ３、Ｊ４・・・軸要素 DESCRIPTION OF SYMBOLS 1 ... Housing 2 ... Torque converter 10, 20 ... Transmission 11 ... Input shaft 12 ... Output shaft G1 ... Double pinion planetary gear of the 1st row G2 ... 2nd row Single pinion planetary gear G3: third row single pinion planetary gear G23: planetary gear unit S1, S2, S3: sun gear R1, R2, R3: ring gear PC1, PC2, PC3: carrier C0, C1 , C2: friction clutch element B1, B2, B3: friction brake element J1, J2, J3, J4: shaft element
Claims (2)
ンプラネタリギヤと、 第２列のシングルピニオンプラネタリギヤのキャリヤ及
びリングギヤと第３列のシングルピニオンプラネタリギ
ヤのリングギヤ及びキャリヤとをそれぞれ連結して第１
〜第４の軸要素を具備させ且つ前記第３の軸要素を前記
出力軸に連結するとともに前記第４の軸要素を前記第１
列のダブルピニオンプラネタリギヤのリングギヤに連結
したプラネタリギヤユニットと、 前記入力軸と前記プラネタリギヤユニットの前記第２の
軸要素とを選択的に連結するための第１の摩擦クラッチ
要素Ｃ１と、 前記入力軸と前記プラネタリギヤユニットの前記第１の
軸要素とを選択的に連結するための第２の摩擦クラッチ
要素Ｃ２と、 前記プラネタリギヤユニットの前記第１の軸要素を選択
的に固定するための第１の摩擦ブレーキ要素Ｂ１と、 前記プラネタリギヤユニットの前記第２の軸要素を選択
的に固定するための第２の摩擦ブレーキ要素Ｂ２と、 前記第１列のダブルピニオンプラネタリギヤのサンギヤ
を選択的に固定するための第３の摩擦ブレーキ要素Ｂ３
と、 を備える変速装置。An input shaft, an output shaft, a first row of double pinion planetary gears having a carrier connected to the input shaft, a second row of single pinion planetary gear carriers and a ring gear, and a third row of single pinion planetary gears. The ring gear and the carrier are connected to each other to
To a fourth shaft element, and connecting the third shaft element to the output shaft, and connecting the fourth shaft element to the first shaft element.
A planetary gear unit connected to a ring gear of a double pinion planetary gear in a row; a first friction clutch element C1 for selectively connecting the input shaft to the second shaft element of the planetary gear unit; A second friction clutch element C2 for selectively connecting the first shaft element of the planetary gear unit, and a first friction for selectively fixing the first shaft element of the planetary gear unit. A brake element B1, a second friction brake element B2 for selectively fixing the second shaft element of the planetary gear unit, and a second frictional brake element B2 for selectively fixing the sun gear of the double pinion planetary gear in the first row. Third friction brake element B3
And a transmission comprising:
第１列のダブルピニオンプラネタリギヤと、 第２列のシングルピニオンプラネタリギヤのキャリヤ及
びリングギヤと第３列のシングルピニオンプラネタリギ
ヤのリングギヤ及びキャリヤとをそれぞれ連結して第１
〜第４の軸要素を具備させ且つ前記第３の軸要素を前記
出力軸と連結してなるプラネタリギヤユニットと、 前記入力軸と前記プラネタリギヤユニットの前記第２の
軸要素とを選択的に連結するための第１の摩擦クラッチ
要素Ｃ１と、 前記入力軸と前記プラネタリギヤユニットの前記第１の
軸要素とを選択的に連結するための第２の摩擦クラッチ
要素Ｃ２と、 前記第１列のダブルピニオンプラネタリギヤのリングギ
ヤと前記プラネタリギヤユニットの前記第４の軸要素と
を選択的に連結するための第３の摩擦クラッチ要素Ｃ０
と、 前記プラネタリギヤユニットの前記第１の軸要素を選択
的に固定するための第１の摩擦ブレーキ要素Ｂ１と、 前記プラネタリギヤユニットの前記第２の軸要素を選択
的に固定するための第２の摩擦ブレーキ要素Ｂ２と、を
備える変速装置。2. An input shaft, an output shaft, a first row of double pinion planetary gears having a carrier connected to the input shaft and fixing a sun gear, a second row of single pinion planetary gear carriers and a ring gear, and a third row. The ring gear and carrier of the single pinion planetary gear of
To a planetary gear unit including a fourth shaft element and connecting the third shaft element to the output shaft; and selectively connecting the input shaft and the second shaft element of the planetary gear unit. Friction clutch element C1 for selectively connecting the input shaft and the first shaft element of the planetary gear unit, and a first row of double pinions A third friction clutch element C0 for selectively connecting a ring gear of a planetary gear and the fourth shaft element of the planetary gear unit;
A first friction brake element B1 for selectively fixing the first shaft element of the planetary gear unit; and a second friction brake element B1 for selectively fixing the second shaft element of the planetary gear unit. And a friction brake element B2.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP04350399A JP4228452B2 (en) | 1999-02-22 | 1999-02-22 | Transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP04350399A JP4228452B2 (en) | 1999-02-22 | 1999-02-22 | Transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2000240741A true JP2000240741A (en) | 2000-09-05 |
| JP4228452B2 JP4228452B2 (en) | 2009-02-25 |
Family
ID=12665537
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP04350399A Expired - Fee Related JP4228452B2 (en) | 1999-02-22 | 1999-02-22 | Transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4228452B2 (en) |
Cited By (29)
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|---|---|---|---|---|
| WO2003054421A1 (en) * | 2001-12-20 | 2003-07-03 | Zf Friedrichshafen Ag | Multi-speed transmission |
| US6626789B2 (en) * | 2001-09-19 | 2003-09-30 | General Motors Corporation | Family of six-speed transmission mechanisms with three planetary gearsets |
| DE10340729A1 (en) * | 2003-09-04 | 2005-04-07 | Zf Friedrichshafen Ag | Multi-speed transmission |
| US6935984B2 (en) | 2003-07-31 | 2005-08-30 | Zf Friedrichshafen Ag | Multi-stage automatic transmission with three planetary gearwheel assemblies |
| US6997845B2 (en) | 2003-07-31 | 2006-02-14 | Zf Friedrichshafen Ag | Multi-stage automatic transmission with three planetary gearwheel assemblies |
| US7025703B2 (en) | 2003-08-01 | 2006-04-11 | Zf Friedrichshafen Ag | Multistage automatic transmission with three planetary gear sets |
| US7037233B2 (en) | 2001-10-30 | 2006-05-02 | Toyota Jidosha Kabushiki Kaisha | Automatic transmission |
| US7052432B2 (en) | 2002-12-03 | 2006-05-30 | Hyundai Motor Company | Six-speed powertrain of an automatic transmission of a vehicle |
| US7101303B2 (en) | 2003-09-04 | 2006-09-05 | Zf Friedrichshafen Ag | Multiple gear stage automatic transmission |
| US7104915B2 (en) | 2003-09-04 | 2006-09-12 | Zf Friedrichshafen Ag | Multiple gear stage automatic transmission |
| KR100623757B1 (en) | 2004-11-19 | 2006-09-19 | 현대자동차주식회사 | A 6th-SPEED POWER TRAIN OF AN AUTOMATIC TRANSMISSION FOR A VEHICLE |
| KR100623780B1 (en) | 2004-11-19 | 2006-09-19 | 현대자동차주식회사 | A 6th-SPEED POWER TRAIN OF AN AUTOMATIC TRANSMISSION FOR A VEHICLE |
| KR100623782B1 (en) | 2004-11-24 | 2006-09-19 | 현대자동차주식회사 | A 6th-SPEED POWER TRAIN OF AN AUTOMATIC TRANSMISSION FOR A VEHICLE |
| KR100623776B1 (en) | 2004-11-19 | 2006-09-19 | 현대자동차주식회사 | A 6th-SPEED POWER TRAIN OF AN AUTOMATIC TRANSMISSION FOR A VEHICLE |
| KR100623781B1 (en) | 2004-11-19 | 2006-09-19 | 현대자동차주식회사 | A 6th-SPEED POWER TRAIN OF AN AUTOMATIC TRANSMISSION FOR A VEHICLE |
| US7115063B2 (en) | 2003-09-04 | 2006-10-03 | Zf Friedrichshafen Ag | Multiple gear stage automatic transmission |
| US7115061B2 (en) | 2003-09-04 | 2006-10-03 | Zf Friedrichshafen Ag | Multiple gear stage automatic transmission |
| US7118511B2 (en) | 2003-09-04 | 2006-10-10 | Zf Friedrichshafen Ag | Multiple gear stage automatic transmission |
| US7137923B2 (en) | 2003-09-04 | 2006-11-21 | Zf Friedrichshafen Ag | Multiple gear stage automatic transmission |
| US7140996B2 (en) | 2003-09-04 | 2006-11-28 | Zf Friedrichshafen Ag | Multiple gear stage automatic transmission |
| US7140997B2 (en) | 2003-07-31 | 2006-11-28 | Zf Friedrichshafen Ag | Multi-stage automatic transmission with three planetary gearwheel assemblies |
| US7156767B2 (en) | 2003-09-04 | 2007-01-02 | Zf Friedrichshafen Ag | Multiple gear stage automatic transmission |
| US7179191B2 (en) | 2003-08-01 | 2007-02-20 | Zf Friedrichshafen Ag | Multistage automatic transmission with three planetary gear sets |
| USRE39960E1 (en) | 1999-03-22 | 2007-12-25 | Zf Friedrichshafen Ag | Automatic transmission for motor vehicles |
| JP2008267473A (en) * | 2007-04-19 | 2008-11-06 | Masahiro Okubo | Multi-stage automatic transmission device |
| US7470208B2 (en) | 2003-10-30 | 2008-12-30 | Zf Friedrichshafen Ag | Multistep automatic transmission with three planetary gear trains |
| KR100887965B1 (en) | 2007-08-16 | 2009-03-12 | 현대자동차주식회사 | Gear train in an automatic transmission for vehicles |
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| US7713160B2 (en) | 2007-02-09 | 2010-05-11 | Zf Friedrichshafen Ag | Multistage automatic transmission with three planetary gear sets |
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1999
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Cited By (34)
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| USRE39960E1 (en) | 1999-03-22 | 2007-12-25 | Zf Friedrichshafen Ag | Automatic transmission for motor vehicles |
| US6626789B2 (en) * | 2001-09-19 | 2003-09-30 | General Motors Corporation | Family of six-speed transmission mechanisms with three planetary gearsets |
| US7037233B2 (en) | 2001-10-30 | 2006-05-02 | Toyota Jidosha Kabushiki Kaisha | Automatic transmission |
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| US6997845B2 (en) | 2003-07-31 | 2006-02-14 | Zf Friedrichshafen Ag | Multi-stage automatic transmission with three planetary gearwheel assemblies |
| US7255661B2 (en) | 2003-07-31 | 2007-08-14 | Zf Friedrichshafen Ag | Multi-stage automatic transmission with three planetary gearwheel assemblies |
| US7217218B2 (en) | 2003-07-31 | 2007-05-15 | Zf Friedrichshafen Ag | Multi-stage automatic transmission with three planetary gearwheel assemblies |
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| JP2008267473A (en) * | 2007-04-19 | 2008-11-06 | Masahiro Okubo | Multi-stage automatic transmission device |
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| JP4228452B2 (en) | 2009-02-25 |
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