JPS6256652A - Automatic speed change gear for vehicle - Google Patents
Automatic speed change gear for vehicleInfo
- Publication number
- JPS6256652A JPS6256652A JP60193963A JP19396385A JPS6256652A JP S6256652 A JPS6256652 A JP S6256652A JP 60193963 A JP60193963 A JP 60193963A JP 19396385 A JP19396385 A JP 19396385A JP S6256652 A JPS6256652 A JP S6256652A
- Authority
- JP
- Japan
- Prior art keywords
- planetary gear
- gear
- shaft
- output shaft
- 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.)
- Pending
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
- 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
-
- 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
- F16H2200/0008—Transmissions for multiple ratios specially adapted for front-wheel-driven vehicles
-
- 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
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2041—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with four engaging means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用性ｆｆ）
未光明は遊星歯車式変速機構を用いた巾ｒ・９川［Ｉ動
変速機に関するものである。DETAILED DESCRIPTION OF THE INVENTION (Industrial Applicability ff) The present invention relates to a dynamic transmission with a width of 9 cm and a planetary gear type transmission mechanism.
（従来技術）
車両用自動変速機としては、エンジン出力軸に対してト
ルクコン・ヘータを介して連結されたカイ歯車式変速機
構を用いるものが一般的である。この遊星歯車式変速機
構としては、シンプソン式あるいはラビニョ式のもの１
一般に２組の遊星歯車を有する３段変速のものが多く、
軽中肉等に、おいては２段変速のものも用いられている
。(Prior Art) Automatic transmissions for vehicles generally use a chi gear type transmission mechanism connected to an engine output shaft via a torque converter. As this planetary gear type transmission mechanism, the Simpson type or Ravigneau type 1
Generally, there are many three-speed gears with two sets of planetary gears.
Two-speed gears are also used for light and medium-duty vehicles.
ところで近時は、エンジンを横置きとするＦＦｊＥ （
フロントエンジン−フロントドライブ中）やミ・・トシ
ソプ車も多くなっており、このようなエンジン横置き式
のものでは、ｊｉｔ幅による１７１ 、釣のため、自動
変速機の＠長を極力短くすることか゛？１珠：される。By the way, recently, FFjE (
There are also many front engine (front drive) and Mi-toshisop cars, and in such horizontally mounted engines, the length of the automatic transmission must be kept as short as possible due to the jit width. Or? 1 bead: Will be done.
このような観点から、オー／へドラ・イブ川′９・１・
１カ［；用変速段を得るだめの補助の７〒尚車を、例え
ば３段変速の主遊星歯車式変速機構と並夕１１に１没け
るようにしたものが提案されている（特開聞（５９ｉ３
３８５２号公報、特開昭５９−１１７９４３壮公報ヅ照
）。From this perspective, O/Hedorah Eve River '9.1.
A system has been proposed in which an auxiliary 7-speed vehicle is used to obtain a 1-speed shift gear, for example, with a 3-speed main planetary gear transmission mechanism and a 11-speed gear shift mechanism. (59i3
No. 3852, Japanese Patent Application Laid-open No. 117943/1983).
（発明が解決しようとする問題点）
しかしながら、従来のものでは、主光う↓歯ｉｐ弐斐速
機構そのものは２組の遊星歯車機構を有して、 このＥ
星歯車機構同志は〃いに連係関係があるため、必然的に
直列に配３没されており、自動変速機軸長が全体として
とうしてもかなり長尺なものとなってしまう、という問
題があった。とりわけ、この２組の遊星歯車機構に対し
ては、変速用アクチュエータとしてのフランチやブレー
キが付、没されて、この変速用アク手ユエータの一部は
遊、！Ｉ！歯車機構の回り（＠心方向周囲）に配設する
ことができても、残りはこの２組の遊星歯車機構と必ず
直列に配設されることになるため、上述した軸長を短く
するには限度があった。(Problem to be solved by the invention) However, in the conventional type, the main light gear mechanism itself has two sets of planetary gear mechanisms.
Since the star gear mechanisms have a very interconnected relationship, they are necessarily arranged in series, and the problem is that the automatic transmission shaft length as a whole becomes quite long. there were. In particular, for these two sets of planetary gear mechanisms, the flanches and brakes that act as shift actuators are sunk, and a portion of these shift actuators are free. I! Even if it can be arranged around the gear mechanism (at the center direction), the rest will always be arranged in series with these two sets of planetary gear mechanisms, so in order to shorten the shaft length mentioned above, There was a limit.
したがって、本発明の目的は、変速のため互いに連係関
係にある２組の遊星歯車機構を有する自動変速機におい
て、この２組のか星歯車機構の配置、ぐ位置関係を並列
になし得るようにして、自動変速機全体とじてその全長
を大幅に短縮化し得るようにした重両用自動変速機を提
供することにある。Therefore, an object of the present invention is to provide an automatic transmission having two sets of planetary gear mechanisms linked to each other for speed change, so that the arrangement and positional relationship of the two sets of planetary gear mechanisms can be made parallel. An object of the present invention is to provide a heavy-duty automatic transmission in which the overall length of the entire automatic transmission can be significantly shortened.
（問題点を解決するだめの手段、作用）前述の目的を達
成するため、本発明にあっては、次のような構成としで
ある。すなわち、エンジン出力軸に連結される入力軸と
、前記入力軸と平行に配置され、アクスル軸に連結され
る出力軸と、
一対の遊星歯車ａ構を有するシンプソン式の遊星歯車式
変速機構における一方の遊星歯車ａａがｌｉ０記入力軸
に配設されると共に、他力の酋星歯車機構が前記出力軸
に配置され、
前記入力軸と出力軸との間に構成された２組のギア列を
介して、前記一対の遊星歯車機構における相対応するギ
ア要素同志が接続されている、ような構成としである。(Means and operations for solving the problems) In order to achieve the above-mentioned object, the present invention has the following configuration. That is, one side of a Simpson-type planetary gear type transmission mechanism having an input shaft connected to an engine output shaft, an output shaft arranged parallel to the input shaft and connected to an axle shaft, and a pair of planetary gears a structure. A planetary gear aa is disposed on the li0 input shaft, and an externally driven planetary gear mechanism is disposed on the output shaft, and two sets of gear trains configured between the input shaft and the output shaft are connected to each other. Corresponding gear elements in the pair of planetary gear mechanisms are connected to each other through the planetary gear mechanism.
このような構成とすることにより、２組のＭ星歯車機構
同志が互いに入力軸と出力軸とに分けて並列に配置没さ
れることに加えて、変速用アクチュ二一夕も入力軸と出
力軸とに分散して配置することか可能となり、全体とし
て軸長を大幅に短縮化することかり能になる。With this configuration, in addition to the two sets of M star gear mechanisms being arranged in parallel with each other, with the input shaft and output shaft separated, the two gearshift actuators are also separated into the input shaft and output shaft. This makes it possible to arrange them in a distributed manner on the shaft, and the shaft length as a whole can be significantly shortened.
（実施例） 以ト本発明の実施例を添付した図面に収いて説明する。(Example) Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
本発明の第１実施例紮示す第１図において、文１、文２
）交３は、それぞれ第１〜第３の軸線で、この３つの軸
線文１、父２）立３は、互いに（１行にかつ憚１方自か
ら見た場合に互いに三角形の旧点部分に位置するような
配、′δ関係とされている。この第１軸線文１上には入
力軸１か、また第２軸線見２上には出力軸２が、さらに
第３軸線文３」二には左右一対のアクスル軸３Ａ、３Ｂ
が位置されている。In FIG. 1 showing the first embodiment of the present invention, text 1 and text 2 are shown.
) Cross 3 are the first to third axes, respectively, and these three axes 1, 2) 3 are the same as each other (in one line and when viewed from one side, they are the old point parts of the triangle) The input shaft 1 is located on the first axis line 1, the output shaft 2 is on the second axis line 2, and the third axis line 3 is located on the first axis line 1. Second, a pair of left and right axle shafts 3A, 3B
is located.
上記入力＠１の一端部には、トルクコンバータ４を合し
てエンジン出力４ｄ５が連結さ、れ、これにより、ニン
ジンからの出力（ｉ・ルク）がトルクコンバータ４を介
して入力軸１に人力される。The torque converter 4 is connected to one end of the input @1 to connect the engine output 4d5, and as a result, the output from the carrot (i/rook) is transferred to the input shaft 1 via the torque converter 4. be done.
ｒｉｉｊ記入力＋１１１と出力軸２とに跨って、シンプ
ソン式の粧星歯＋ｌｊ式変速機構ＡＴが構成されている
か、実施例ではこのＭ星歯車式変速機構ＡＴは、最も一
般的なリバース付の前進３段用とされている。そして、
遊星歯車式変速機構ＡＴの２組のが星尚屯ａ構Ｙ１、Ｙ
、のうち、入力軸１には第１（フロント）遊星歯車機構
Ｙ１が、また出力軸２には第２（リア）Ｍ星歯車機構Ｙ
２が配設されている。A Simpson type decorative star gear + lj type transmission mechanism AT is configured across the riij input input +111 and the output shaft 2. In the embodiment, this M star gear type transmission mechanism AT is the most common type with reverse It is said to be for 3 forward speeds. and,
The two sets of planetary gear type transmission mechanism AT are Seishangtun a structure Y1 and Y.
, the input shaft 1 has a first (front) planetary gear mechanism Y1, and the output shaft 2 has a second (rear) M star gear mechanism Y1.
2 are arranged.
上記第１遊星歯車機構’Ｙ １について説明すると、入
力軸ｌはトルクコンバータ４に連なる第１輛ＩＡと、こ
の第１軸ＩＡに直列な第２軸ＩＢとからなり、第２＠Ｉ
ＢＬに遊星歯ＴＪｊ機構Ｙ１が配置されている。すなわ
ち、第１遊星歯車機構Ｙｌは、サンギアＳＧＬとリング
ギアＲＧＩと該両ギアＳＧＩ、ＲＧＩに噛合するプラネ
タリギアＰＧ１とを有して、サンギアＳＧＩが第２軸Ｉ
Ｂに対して回転自在に配置されている。これ等各ギア要
素、ＳＧＩ、ＲＧＩ、ＰＧＩのうち、サンギアＳＧ１は
、第１クラツチ（フロントクラッチ）Ｃ１を介して第１
＠ｈ ｌ Ａに断続されると共に、第１ブレーキ（セ
カンドブレーキ）Ｂｌによって自動変速機のケーシング
Ｋに断続（固定、フリー）される。また、 リングギア
ＲＧＩは、第２クラツチ（リアクラッチ）Ｃ２を介して
第１軸ＩＡに断続される。そして、プラネタリギアＰＣ
Ｉを保持したプラネタリキャリアＰＣＩが、第２軸ＩＢ
に一体化されている。To explain the first planetary gear mechanism Y1, the input shaft l consists of a first shaft IA connected to the torque converter 4, and a second shaft IB serially connected to the first shaft IA.
A planetary tooth TJj mechanism Y1 is arranged at BL. That is, the first planetary gear mechanism Yl includes a sun gear SGL, a ring gear RGI, and a planetary gear PG1 that meshes with both gears SGI and RGI, and the sun gear SGI is connected to the second shaft I.
It is arranged rotatably with respect to B. Among these gear elements, SGI, RGI, and PGI, the sun gear SG1 is connected to the first gear via the first clutch (front clutch) C1.
At the same time, it is connected and disconnected to the casing K of the automatic transmission (fixed, free) by the first brake (second brake) Bl. Further, the ring gear RGI is connected to and connected to the first shaft IA via a second clutch (rear clutch) C2. And planetary gear PC
The planetary carrier PCI holding I is the second axis IB
is integrated into.
一方、出力軸２は、互いに内外同心状とされた第１軸２
Ａと第２軸２Ｂとから構成されている。On the other hand, the output shaft 2 is a first shaft 2 that is concentric with the inside and outside of each other.
A and a second shaft 2B.
この出力＠２には、遊星歯車式変速機構ＡＴの第２（リ
ア）遊星歯車機構Ｙ２が配設されているか、この遊星歯
車機構Ｙ２もサンギアＳＧ２とリングギアＲＧ２と該両
ギアＳＧ２）ＲＧ２に噛合するプラネタリギアＰＧ２と
からなる。これ等各キア要素のうち、サンギアＳＧ２は
第２軸２Ｂに一体化され、またリングギアＲＧ２はｈ’
Ｔｒ ｌ軸２Ａに一体化されている。そして、プラネタ
リギアＰＧ２を保持するプラネタリキャリアＰＣ２が、
ワンウェイクラッチＷにより所定の方向のみの回転が許
容されるようにケーシングＫに結合されると八に、７ｒ
Ｓ２ブレーキ（ロー参リバースプレーヤ）Ｂ２によ、っ
てヅ１該ケーシングＫに断続される。This output @2 is provided with the second (rear) planetary gear mechanism Y2 of the planetary gear type transmission mechanism AT, or this planetary gear mechanism Y2 is also connected to sun gear SG2, ring gear RG2, and both gears SG2) and RG2. It consists of a planetary gear PG2 that meshes with the planetary gear PG2. Among these chia elements, sun gear SG2 is integrated with the second shaft 2B, and ring gear RG2 is h'
It is integrated into the Tr l axis 2A. Then, the planetary carrier PC2 holding the planetary gear PG2 is
When the one-way clutch W is connected to the casing K so that rotation is allowed only in a predetermined direction, 7r
The S2 brake (low-reverse reverse sprayer) is connected to the casing K by B2.
前述した両敵星、歯Ｉｉｆ ａ構Ｙ】とＹ２とは、その
相対応するキア要素（ＳＧＩとＳＧ２．およびＰＣＩと
ＲＧ２）同志が、カニいにキア比の副しい第１、第２の
２組のキア列Ｇ１、Ｇ２によって接すにされている。こ
の点を詳述すると、第１ギア！Ｊ１１に１は、ＩＵＩい
に噛合するドライブギア６とドリブンギア７とから構成
されて、両すンキアＳＧＩと二）Ｇ２とを接続するもの
である。すなわち、ｉ−ライブギア６は、入力軸１の第
２＠ｌＢ外周に回転１−１在に配置されると共に、サン
ギアＳＧＩに・体化されている。またドリブンギア７は
、出力軸２の第２＠２Ｂに一体化されることによりサン
キ７ＳＧ２と一体化されている。The above-mentioned two enemy stars, teeth Iif a structure Y] and Y2, have their corresponding chia elements (SGI and SG2. and PCI and RG2) in the first and second positions, which have a secondary chia ratio. They are in contact with each other by two sets of gear trains G1 and G2. To elaborate on this point, 1st gear! J111 is composed of a drive gear 6 and a driven gear 7 that mesh with IUI, and connects both Nkia SGI and 2) G2. That is, the i-live gear 6 is disposed on the second @lB outer periphery of the input shaft 1 so as to rotate 1-1, and is integrated into the sun gear SGI. Further, the driven gear 7 is integrated with the second @2B of the output shaft 2, thereby being integrated with the Sanki 7SG2.
一方、第２ギア列Ｇ２は、ｎ］いに噛合するドライブギ
ア８とドリブンギア９とから構成されｒ第１敵♀歯車機
構Ｙ１のプラネタリキャリアＰＣＩと第２ｊｆＬ星歯車
機構のリングギアＲＧ２とを接続するものである。すな
わち、ドライブギア８は、入力＠１の第２軸ＩＢに一体
化されることにより、プラネタリキャリアＰｃｔに一体
化されている。また、ドリブンギア９は出力軸２の第１
軸２Ａに一体化されることによりリングギアＲＧ２に一
体化されている。On the other hand, the second gear train G2 is composed of a drive gear 8 and a driven gear 9 that mesh with the planetary carrier PCI of the first enemy female gear mechanism Y1 and the ring gear RG2 of the second jfL star gear mechanism. It is something that connects. That is, the drive gear 8 is integrated with the second axis IB of the input @1, and thereby integrated with the planetary carrier Pct. Further, the driven gear 9 is the first gear of the output shaft 2.
By being integrated with the shaft 2A, it is integrated with the ring gear RG2.
以上のような構成によって、遊星歯車機構Ｙ１とＹ２と
を直列に配設した従来のシンプソン式のリバース付前進
３段の遊星歯車式変速機構と同じようにしてその変速が
行われることになる。この点を明確にするため、各変速
段とアクチュエータＣ１、Ｃ２）Ｂ１、Ｂ２の作動態様
との関係を次表にまとめて示すことにより、この以上の
詳細な説明は省略する。With the above configuration, the speed change is performed in the same manner as the conventional Simpson type three-speed forward planetary gear transmission mechanism with reverse in which the planetary gear mechanisms Y1 and Y2 are arranged in series. In order to clarify this point, the relationship between each gear stage and the operation mode of the actuators C1, C2) B1, B2 is summarized in the following table, and further detailed explanation will be omitted.
（○＝作動 無印−解除）
１−述のように遊星歯車式変速機構ＡＴにより変速か行
われる動力伝達系路の最終出力））８分を構成するため
、出力軸２の第１ Ｉｋｌｌ ２ Ａには出力ギアｌＯ
が一体化されると共に、この出力ギア１０に対して最終
減速ギア１１が噛合されている。そして、この＠終減速
ギア１１からはデファレンシャルボックス１２を介して
前記アクスル軸３Ａ、３Ｂへ動力が伝達される。(○=operation, no mark - release) 1-Final output of the power transmission system in which the speed is changed by the planetary gear type transmission mechanism AT as described above) is the output gear lO
are integrated, and a final reduction gear 11 is meshed with this output gear 10. Power is transmitted from this final reduction gear 11 to the axle shafts 3A and 3B via a differential box 12.
第２図は本発明の第２実施例を示すもので、前記実施例
と同一構成要素には同一符号を付してその説明は省略す
る。FIG. 2 shows a second embodiment of the present invention, in which the same components as in the previous embodiment are given the same reference numerals and their explanations will be omitted.
本実施例では、第１遊星歯車機構Ｙ１を、両ギア列ＧＩ
、Ｇ２を挟んで、トルクコンバータ４とは反対側に位置
させたものであり、その作用「１体は前記実施例の場合
と回じである。In this embodiment, the first planetary gear mechanism Y1 is connected to both gear trains GI
, G2 are located on the opposite side of the torque converter 4, and its operation is the same as in the previous embodiment.
以北実施例について説明したが、ＭＹｉ車式変速機構Ａ
Ｔとしてはシンプソン式の２速のものであつ−ｃ ｆ、
、−１＝い。また、トルクコンバータ４を用いる代り
に、電子的に断続制御がなされる電磁フランチを用いる
こともできる。Although the embodiments have been described above, the MYi vehicle type transmission mechanism A
The T is a Simpson type two-speed type -c f,
, -1 = yes. Moreover, instead of using the torque converter 4, it is also possible to use an electromagnetic flanch whose intermittent control is performed electronically.
（発明の効果）
本発明は以ト述べたことから明らかなように、従来から
ある遊星歯車式変速機構を利用しつつ、その構成部品の
配置関係をに夫したことにより、全体としての軸長を大
幅に短かくすることができる。(Effects of the Invention) As is clear from the above, the present invention utilizes a conventional planetary gear type transmission mechanism and changes the arrangement of its component parts, thereby increasing the overall shaft length. can be significantly shortened.
第１図は本発明の第１実施例を示すスケルトン図。 ：ｉＳｚ図は本発明の第２実施例を示すスケルトン図。 ＡＴ：遊星歯車式変速機構 Ｇｌ：第１キア列 Ｇ２：：ｆＳ２ギア列 父１．文２）文３：軸線 に入力軸 ２二出力軸 ３Ａ、３Ｂ：アクスル軸 ４：トルクコンバータ ５：エンシン出力袖 １１：最、終減速ギア Ｙｌ、Ｙ２ ：Ｍ星歯車 ＳＧＩ、ＳＧ２ ：サンギア ＲＧｌ、ＲＧ２：リンクギア ＰＣＩ、ＰＧ２：プラネタリギア Ｐｃｔ、ＰＣ２：プラネタリキャリア ＣＩ、Ｃ２：フランチ Ｂ１、Ｂ２ニブレーキ 第１図 FIG. 1 is a skeleton diagram showing a first embodiment of the present invention. :iSz diagram is a skeleton diagram showing a second embodiment of the present invention. AT: Planetary gear type transmission mechanism Gl: 1st gear row G2::fS2 gear train Father 1. Sentence 2) Sentence 3: Axis line input shaft to 22 output shafts 3A, 3B: Axle axis 4: Torque converter 5: Engine output sleeve 11: Last, final reduction gear Yl, Y2: M star gear SGI, SG2: Sangia RGl, RG2: Link gear PCI, PG2: Planetary gear Pct, PC2: Planetary carrier CI, C2: Franch B1, B2 Nibrake Figure 1
Claims (2)
軸と平行に配置され、アクスル軸に連結される出力軸と
、 一対の遊星歯車機構を有するシンプソン式の遊星歯車式
変速機構における一方の遊星歯車機構が前記入力軸に配
設されると共に、他方の遊星歯車機構が前記出力軸に配
置され、 前記入力軸と出力軸との間に構成された２組のギア列を
介して、前記一対の遊星歯車機構における相対応するギ
ア要素同志が接続されている、ことを特徴とする車両用
自動変速機。(1) One side of a Simpson-type planetary gear transmission mechanism that has an input shaft connected to the engine output shaft, an output shaft arranged parallel to the input shaft and connected to an axle shaft, and a pair of planetary gear mechanisms. one planetary gear mechanism is disposed on the input shaft, and the other planetary gear mechanism is disposed on the output shaft, through two sets of gear trains configured between the input shaft and the output shaft, An automatic transmission for a vehicle, characterized in that corresponding gear elements in the pair of planetary gear mechanisms are connected to each other.
ルクコンバータを介してエンジン出力軸に連結されるよ
うにしたもの。(2) The device according to claim 1, wherein the input shaft is connected to the engine output shaft via a torque converter.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60193963A JPS6256652A (en) | 1985-09-04 | 1985-09-04 | Automatic speed change gear for vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60193963A JPS6256652A (en) | 1985-09-04 | 1985-09-04 | Automatic speed change gear for vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS6256652A true JPS6256652A (en) | 1987-03-12 |
Family
ID=16316675
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60193963A Pending JPS6256652A (en) | 1985-09-04 | 1985-09-04 | Automatic speed change gear for vehicle |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6256652A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5213552A (en) * | 1990-06-28 | 1993-05-25 | Mazda Motor Corporation | Vehicle power transmission |
| WO2002079665A2 (en) * | 2001-03-30 | 2002-10-10 | Zf Friedrichshafen Ag | Multi-stage gearbox |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60188645A (en) * | 1984-03-05 | 1985-09-26 | Nissan Motor Co Ltd | Planetary gear transmission |
| JPS60205048A (en) * | 1984-03-30 | 1985-10-16 | Nissan Motor Co Ltd | Gear train of automatic speed changer |
-
1985
- 1985-09-04 JP JP60193963A patent/JPS6256652A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60188645A (en) * | 1984-03-05 | 1985-09-26 | Nissan Motor Co Ltd | Planetary gear transmission |
| JPS60205048A (en) * | 1984-03-30 | 1985-10-16 | Nissan Motor Co Ltd | Gear train of automatic speed changer |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5213552A (en) * | 1990-06-28 | 1993-05-25 | Mazda Motor Corporation | Vehicle power transmission |
| WO2002079665A2 (en) * | 2001-03-30 | 2002-10-10 | Zf Friedrichshafen Ag | Multi-stage gearbox |
| WO2002079665A3 (en) * | 2001-03-30 | 2003-02-20 | Zahnradfabrik Friedrichshafen | Multi-stage gearbox |
| US6984187B2 (en) | 2001-03-30 | 2006-01-10 | Zf Friedrichshafen Ag | Multi-stage gearbox |
| CN1318778C (en) * | 2001-03-30 | 2007-05-30 | 腓特烈斯港齿轮工厂股份公司 | Multi-stage gearbox |
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