JPS60188645A - Planetary gear transmission - Google Patents
Planetary gear transmissionInfo
- Publication number
- JPS60188645A JPS60188645A JP59041850A JP4185084A JPS60188645A JP S60188645 A JPS60188645 A JP S60188645A JP 59041850 A JP59041850 A JP 59041850A JP 4185084 A JP4185084 A JP 4185084A JP S60188645 A JPS60188645 A JP S60188645A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- planetary gear
- clutch
- pinion carrier
- sun 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
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
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0047—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising five 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
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
-
- 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
- F16H2200/2071—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes using three freewheel mechanism
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野〕
この発明は、自動車の自動変速機等に用いられる遊星歯
車変速装置に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a planetary gear transmission used in automatic transmissions of automobiles and the like.
従来の遊星歯車変速装置、特に５速の変速段数を有する
装置としては、例えば特開昭４７−１９２６８号公報（
シンプソン型歯車列ニシングルプラネタリギヤ）、特開
昭４７−２３７５６号公報（ラビニョオ型歯車列ニシン
グルピニオン）、特開昭４７−２３７６４号公報（ラビ
ニョオ型歯車列：ダブルピニオン）等に記載されている
ようなものがある。これらは、サンギヤ、インターナル
ギヤ及びピニオンキャリヤを有する遊星歯車機構をそれ
ぞれ３組備え、その３組の遊星歯車機構を直列に配置し
ている。A conventional planetary gear transmission, particularly a device having five speeds, is disclosed in, for example, Japanese Patent Laid-Open No. 19268/1983 (
Simpson type gear train Nisingle planetary gear), JP-A-47-23756 (Ravigneau-type gear train Nisingle pinion), JP-A-47-23764 (Ravigneau-type gear train: double pinion), etc. There is something like that. These are each equipped with three sets of planetary gear mechanisms each having a sun gear, an internal gear, and a pinion carrier, and the three sets of planetary gear mechanisms are arranged in series.
しかしながら、このような従来の遊星歯車変速装置にあ
っては、３組の遊星歯車機構が直列に配置されていて何
れも装置の全長が長い構造となっていたため、スペース
上の制約が多いい前輪駆動車にこれら装置を搭載するこ
とは困難であるという問題があった。However, in such a conventional planetary gear transmission, three sets of planetary gear mechanisms are arranged in series, and the overall length of each device is long. There has been a problem in that it is difficult to mount these devices on a drive vehicle.
この発明は、このような従来の問題点に着目してなされ
たものであり、遊星歯車機構やクラッチ等を入力軸と出
力軸との２軸に分けて配置することにより、５速の変速
段数を有する全長の短い遊星歯車変速装置を得ることを
目的としている。This invention was made by focusing on these conventional problems, and by arranging the planetary gear mechanism, clutch, etc. on two shafts, the input shaft and the output shaft, it is possible to increase the number of gears in 5 speeds. The objective is to obtain a planetary gear transmission with a short overall length.
而して、この発明は、入力軸と出力軸とを互いに平行に
配置し、前記入力軸上には、第１サンギヤ、第１インタ
ーナルギヤ及び第１ビニオンキヤリヤを有する第１遊星
歯車機構を設け、前記出力軸上には、第２サンギヤ、第
２インターナルギヤ及び第２ビニオンキヤリヤを有する
第２ｔｆ：星歯車機構を設け、前記入力軸と第１インタ
ーナルギヤとは連結可能とし、前記入力軸と第１サンギ
ヤとは連結可能とし、前記第１サンギヤと第２ビニオン
キヤリヤとは第１伝動手段及びクラッチを介して断続可
能に連結し、前記第１サンギヤと第２サンギヤとは前記
第１伝動手段及び上記と異なるクラッチを介して断続可
能に連結し、前記第１ビニオンキヤリヤと出力軸とは第
２伝動手段を介して連結し、前記第２インターナルギヤ
と出力軸とは一体的に連結し、前記第２サンギヤは第１
ブレーキによって静止部に対して固定可能とし、前記第
２ビニオンキヤリヤは第２ブレーキによって静止部に対
して固定可能とした遊星歯車変速装置に係わる。Accordingly, in the present invention, an input shaft and an output shaft are arranged parallel to each other, and a first planetary gear mechanism having a first sun gear, a first internal gear, and a first pinion carrier is provided on the input shaft. , a second TF: star gear mechanism having a second sun gear, a second internal gear, and a second pinion carrier is provided on the output shaft, the input shaft and the first internal gear can be connected, and the input shaft and a first sun gear are connectable to each other, the first sun gear and the second pinion carrier are intermittably connected to each other via a first transmission means and a clutch, and the first sun gear and the second sun gear are connected to each other via the first transmission means and a clutch. and intermittably connected via a clutch different from the above, the first binion carrier and the output shaft are connected via a second transmission means, and the second internal gear and the output shaft are integrally connected, The second sun gear is the first sun gear.
The invention relates to a planetary gear transmission which can be fixed to a stationary part by a brake, and the second pinion carrier can be fixed to a stationary part by a second brake.
以下、この発明を図示実施例に基づいて説明する。 The present invention will be explained below based on illustrated embodiments.
第１図は、この発明に係わる遊星歯車変速装置の第１実
施例を示す図である。FIG. 1 is a diagram showing a first embodiment of a planetary gear transmission according to the present invention.
まず、構成を説明すると、図中■は、図示しないエンジ
ンの出力軸に連結された入力軸であり、この入力軸■は
、第１クラツチＣ１及び第１ワンウエイクラツチＯＣＩ
を直列的に介して第１インターナルギヤＲ１と断続可能
に連結していると共に、両クラッチＣＩ 、ＯＣＩに対
して並列的に配置された第５クラツチＣ５をも介して該
第１インターナルギヤＲ１と断続可能に連結している。First, to explain the configuration, ■ in the figure is an input shaft connected to the output shaft of an engine (not shown), and this input shaft ■ is connected to the first clutch C1 and the first one-way clutch OCI.
The first internal gear R1 is connected in series with the first internal gear R1, and the first internal gear It is intermittently connected to R1.
さらに、入力軸Ｉは、第２クラツチＣ２を介して第１サ
ンギヤＳｌ と断続可能に連結している。Furthermore, the input shaft I is intermittably connected to the first sun gear Sl via a second clutch C2.
第１サンギヤＳｌは、第１ピニオンキヤリヤＰＣＩに回
転自在に支持された第１プラネタリギヤＰｉと外接噛合
し、この第１プラネタリギヤＰ１は、第１インターナル
ギヤＲ１と内接噛合する。The first sun gear Sl externally meshes with a first planetary gear Pi rotatably supported by a first pinion carrier PCI, and the first planetary gear P1 internally meshes with a first internal gear R1.
従って、第１サンギヤＳ１と、第１プラネタリギヤＰ１
と、第１ビニオンキヤリヤＰＣＩと、第１インターナル
ギヤＲｔとは、全体として第１遊星歯車機構Ｘを構成す
る。Therefore, the first sun gear S1 and the first planetary gear P1
, the first binion carrier PCI, and the first internal gear Rt constitute a first planetary gear mechanism X as a whole.
さらに、第１サンギヤＳ１は、第１伝動手段である第１
歯車機構Ｈ１及び第３クラツチＣ３を直列的に介して第
２ピニオンキヤリヤＰＣ２と断続可能に連結している。Furthermore, the first sun gear S1 is a first transmission means.
It is intermittently connected to the second pinion carrier PC2 via the gear mechanism H1 and the third clutch C3 in series.
この第１歯車機構Ｈ１は、第１サンギヤＳｌに一体的に
連結された第１ギヤＧｌと、この第１ギヤＧｌに噛合す
る第２ギヤＧ２とからなり、第２ギヤＧ２は、第３クラ
ツチＣ３の、第２ピニオンキヤリヤＰＣ２とは反対側の
部材に一体的に連結されている。さらに、第１サンギヤ
３１は、同じく第１歯車機構Ｈ１及び第４クラツチＣ４
を直列的に介して第２サンギヤＳ２と断続可能に連結し
ていると共に、この第４クラツチＣ４と並列的に設けら
れた第２ワンウエイクラツチＯＣ２をも介して第２サン
ギヤＳ２に連結している。The first gear mechanism H1 includes a first gear Gl that is integrally connected to the first sun gear Sl, and a second gear G2 that meshes with the first gear Gl, and the second gear G2 is connected to the third clutch. It is integrally connected to a member of C3 on the opposite side from the second pinion carrier PC2. Furthermore, the first sun gear 31 also includes a first gear mechanism H1 and a fourth clutch C4.
It is connected intermittently to the second sun gear S2 via the fourth clutch C4, and is also connected to the second sun gear S2 via a second one-way clutch OC2 provided in parallel with the fourth clutch C4. .
また、前記第１ビニオンキヤリヤＰＣＩは、第２伝動手
段である第２歯車機構Ｈ２を介して出力軸Ｏと常に連結
している。この第２歯車機構Ｈ２は、第１ピニオンキヤ
リヤＰｃｔに一体的に連結された第３ギヤＧ３と、この
第３ギヤＧ３に噛合する第４ギヤＧ４とからなり、第４
ギヤＧ４ば、出力軸０に一体的に連結している。Further, the first pinion carrier PCI is always connected to the output shaft O via a second gear mechanism H2, which is a second transmission means. The second gear mechanism H2 includes a third gear G3 integrally connected to the first pinion carrier Pct, and a fourth gear G4 meshing with the third gear G3.
Gear G4 is integrally connected to output shaft 0.
出力軸０には第２インターナルギヤＲ２が一体的に連結
されていて、この第２インターナルギャＲ２は、第２ピ
ニオンキヤリヤＰＣ２に回転自在に支持された第２プラ
ネタリギヤＰ２と内接噛合し、この第２プラネタリギヤ
Ｐ２は、第２サンギヤＳ２と外接噛合している。従って
、第２サンギヤＳ２と、第２プラネタリギヤＰ２と、第
２ピニオンキヤリヤＰＣ２と、第２インターナルギヤＲ
２とは、全体として第２遊星歯車機構Ｙを構成する。A second internal gear R2 is integrally connected to the output shaft 0, and this second internal gear R2 is internally meshed with a second planetary gear P2 rotatably supported by a second pinion carrier PC2. However, this second planetary gear P2 is in external meshing with the second sun gear S2. Therefore, the second sun gear S2, the second planetary gear P2, the second pinion carrier PC2, and the second internal gear R
2 constitutes the second planetary gear mechanism Y as a whole.
前記第２サンギヤＳ２は、第１ブレーキＢｌによってケ
ーシング等の静止部Ｋに固定可能であり、また第２ピニ
オンキヤリヤＰＣ２は、第２ブレーキＢ２によって同様
に静止部Ｋに固定可能であって、さらにこの静止部にと
第２ピニオンキヤリヤＰＣ２とは、第２ブレーキＢ２と
並列的に設けられた第３ワンウエイクラツチＯＣ３をも
介して連結している。The second sun gear S2 can be fixed to a stationary part K such as a casing by a first brake Bl, and the second pinion carrier PC2 can also be fixed to a stationary part K by a second brake B2, Furthermore, this stationary part and the second pinion carrier PC2 are also connected via a third one-way clutch OC3 provided in parallel with the second brake B2.
以上の構成よりなる遊星歯車変速装置の各クラッチＣ１
、Ｃ２，’ Ｃ３，Ｃ４，Ｃ５、各ブレーキＢｌ、Ｂ２
、及び各ワンウェイクラッチＯＣＩ。Each clutch C1 of the planetary gear transmission having the above configuration
, C2,' C3, C4, C5, each brake Bl, B2
, and each one-way clutch OCI.
ＯＣ２，ＯＣ３を、第２図に示すような組合せで選択的
に作動させることにより、同図に示すように前進５速及
び後退１速を得ることができる。By selectively operating OC2 and OC3 in combination as shown in FIG. 2, five forward speeds and one reverse speed can be obtained as shown in the same figure.
第２図において、Ｏ印は作動状態を示し、無印は非作動
（解放）状態を示すものである。また、同図において、
ρｌは、第１遊星歯車機構Ｘの減速比、Ｒ２は、第２遊
星歯車機構Ｙの減速比、ｉｌは、第１歯車機構Ｈ１の減
速比、１２は、第２歯車機構Ｈ２の減速比であり、これ
ら減速比ρｌ。In FIG. 2, O marks indicate operating states, and no marks indicate non-operating (released) states. Also, in the same figure,
ρl is the reduction ratio of the first planetary gear mechanism X, R2 is the reduction ratio of the second planetary gear mechanism Y, il is the reduction ratio of the first gear mechanism H1, and 12 is the reduction ratio of the second gear mechanism H2. Yes, these reduction ratios ρl.
ρ２＋ １１及び１２は、以下のようにめられる。ρ2+ 11 and 12 are calculated as follows.
ρｌ＝（第１サンギヤ３１の歯数）／
（第１インターナルギヤＲ１の歯数）
ρ２＝（第２サンギヤＳ２の歯数）／
（第２インターナルギヤＲ２の歯数）
ｉｘ ＝ （第２ギヤＧ２の歯数）／
（第１ギヤＧｌの歯数）
１２−（第４ギヤＧ４の歯数）／
（第３ギヤＧ３の歯数）
而して、第２図から明らかなように、２組の遊星歯車機
構と２組の伝動手段とを組合曵ることにより、変速段数
を５速とすることができる。しがち、互いに平行に配置
された入力軸と出力軸とに遊星歯車機構を１組ずつ配置
したため、装置の全長を従来のそれよりも大幅に短くす
ることができる。ρl = (number of teeth of first sun gear 31) / (number of teeth of first internal gear R1) ρ2 = (number of teeth of second sun gear S2) / (number of teeth of second internal gear R2) ix = (number of teeth of second internal gear R2) 2nd gear G2 (number of teeth) / (1st gear Gl) 12 - (4th gear G4) / (3rd gear G3) By combining two sets of planetary gear mechanisms and two sets of transmission means, the number of gears can be set to five. However, since one set of planetary gear mechanisms is arranged on each input shaft and output shaft that are arranged parallel to each other, the total length of the device can be significantly shorter than that of the conventional device.
第３図には、この発明の第２実施例を示す。FIG. 3 shows a second embodiment of the invention.
この実施例は、前記実施例における第５クラツチＣ５を
、第１ビニオンキヤリヤＰｃｔと出力軸０との間に挿入
すると共に、この第５クラツチＣ５と並列的に第１ワン
ウエイクラツチＯＣ１を配置したものである。他の構成
及び作用は前記実施例と同様であり、このように構成す
ることによっても前記実施例と同様の効果を得ることが
できる。In this embodiment, the fifth clutch C5 in the previous embodiment is inserted between the first pinion carrier Pct and the output shaft 0, and a first one-way clutch OC1 is arranged in parallel with the fifth clutch C5. be. The other configurations and operations are the same as those of the embodiment described above, and the same effects as those of the embodiment described above can also be obtained by configuring it in this way.
第４図には、この発明の第３実施例を示す。FIG. 4 shows a third embodiment of the invention.
この実施例は、第１図の第１実施例におけるように、第
１インターナルギヤＲ１が第５クラツチＣ５を介して入
力軸Ｉに断続可能に連結し、且つ第１クラツチＣ１を介
して入力軸Ｉ側の第１ワンウエイクラツチＯＣＩに断続
可能に連結している代りに、第１インターナルギヤＲ１
を入力軸■に一体的に連結し、第１ピニオンキヤリヤＰ
Ｃ１を、入力軸Ｉに同軸回転可能に設けた中空軸Ｍに第
５クラツチＣ５を介して断続可能に連結すると共に、中
空軸Ｍに設けた第１ワンウエイクラツチＯＣ１側に第１
クラツチＣ１を介して断続可能に連結する一方、中空軸
Ｍに第３ギヤＧ３を取り付けたものであり、その他は第
１実施例の構成と同一である。In this embodiment, as in the first embodiment of FIG. 1, the first internal gear R1 is disconnectably connected to the input shaft I via the fifth clutch C5, and the input Instead of being intermittently connected to the first one-way clutch OCI on the shaft I side, the first internal gear R1
is integrally connected to the input shaft ■, and the first pinion carrier P
C1 is intermittably connected to a hollow shaft M provided coaxially rotatably with the input shaft I via a fifth clutch C5, and a first one-way clutch OC1 provided on the hollow shaft M is connected to the first one-way clutch OC1 side.
The third gear G3 is attached to the hollow shaft M while the third gear G3 is connected in an intermittent manner via a clutch C1, and the other structure is the same as that of the first embodiment.
上記のように構成しても、第１実施例と同様の効果を得
ることができる。Even with the above configuration, the same effects as in the first embodiment can be obtained.
なお、第１及び第２実施例における各遊星歯車機構の位
置は、必ずしも第１、第２遊星歯車機構Ｘ、Ｙの順で並
べる必要はなく、各クラッチやブレーキの連結関係を調
整して逆側に配列してもよい。また、前記第１、第２及
び第３実施例における１各ワンウエイクラツチは、各歯
車の無用な逆転を規制するものであり、本発明の目的を
達成する上において必ずしも必要なものではなく、従っ
て各ワンウェイクラッチがないものであってもよい。Note that the positions of the planetary gear mechanisms in the first and second embodiments do not necessarily have to be arranged in the order of the first and second planetary gear mechanisms X and Y. May be arranged on the side. Furthermore, each one-way clutch in the first, second, and third embodiments is for preventing unnecessary reversal of each gear, and is not necessarily necessary to achieve the object of the present invention. The one-way clutch may not be provided.
さらに、前記第１、第２伝動手段と、しては、チェーン
伝動機構やＶベルト伝動機構等各種の動力伝達機構を採
用することができる。Furthermore, various power transmission mechanisms such as a chain transmission mechanism and a V-belt transmission mechanism can be employed as the first and second transmission means.
以上説明してきたように、この発明では、入力軸と出力
軸とを平行に配置すると共に、各軸に遊星歯車機構を１
組ずつ設け、両逆星歯車機構を伝動手段を介して連結す
る構造としたため、２組の遊星歯車機構を用いて５速の
変速段数を得ることができ、しかも装置の軸方向長さを
従来のそれよりも大幅に短くすることができる。従って
、全長の短い遊星歯車変速装置を得ることができ、特に
スペース上の制約が多いい前輪駆動車にも容易に搭載す
ることができると共に、その他の装置のレイアウト上の
自由度を大きくすることができるという効果が得られる
。As explained above, in this invention, the input shaft and the output shaft are arranged in parallel, and one planetary gear mechanism is installed on each shaft.
Since each set is provided in pairs and both inverted star gear mechanisms are connected via a transmission means, it is possible to obtain a 5-speed gear shift using two sets of planetary gear mechanisms, and the axial length of the device has been reduced compared to conventional gears. can be significantly shorter than that of . Therefore, it is possible to obtain a planetary gear transmission with a short overall length, and it can be easily installed especially in a front wheel drive vehicle with many space constraints, and the degree of freedom in layout of other devices is increased. This has the effect of being able to.
第１図はこの発明の一実施例による歯車列を示す概略骨
組図、第２図は第１図に示した遊星歯車変速装置の作動
要素の組合せとその変速比を示す図表、第３図はこの発
明の第２実施例による歯車列を示す概略骨組図、第４図
はこの発明の第３実施例による歯車列を示す概略骨組図
である。
■・・・・・・入力軸、０・・・・・・出力軸、Ｘ・・
・・・・第１Ｍ星歯車機構、Ｙ・・・・・・第２遊星歯
車機構、ｓｌ・・・・・・第１サンギヤ、Ｂ２・・・・
・・第２＋ンギヤ、ＰＣＩ・・・・・・第１ピニオンキ
ヤリヤ、、ＰＯ２・・・・・・第２ピニオンキヤリヤ、
Ｒ１・・・・・・第１インターナルギヤ、Ｒ２・・・・
・・第２インターナルギヤ、ｃｌ・・・・・・第１クラ
ツチ、Ｃ２・・・・・・第２クラツチ、Ｃ３・・・・・
・第３クラツチ、Ｃ４・・・・・・第４クラツチ、Ｃ５
・・・・・・第５クラツチ、Ｂｌ・・・・・・第１ブレ
ーキ、Ｂ２・・・・・・第２ブレーキ、Ｈ，・・・・・
・第１歯車機構（第１伝動手段）、Ｒ２・・・・・・第
２歯車機構（第２伝動手段）、Ｇ１・・・・・・第１ギ
ヤ、Ｇ２・・・・・・第２ギヤ、Ｇ３・・・・・・第３
ギヤ、Ｇ４・・・・・・第４ギヤ、Ｋ・・・・・・静止
部特許出願人
日産自動車株式会社
代理人 弁理士 森 哲也
代理人 弁理士 内藤 嘉昭
代理人 弁理士 清水 正
代理人 弁理士 掘出 債楚FIG. 1 is a schematic diagram showing a gear train according to an embodiment of the present invention, FIG. 2 is a diagram showing combinations of operating elements of the planetary gear transmission shown in FIG. 1 and their gear ratios, and FIG. FIG. 4 is a schematic diagram showing a gear train according to a second embodiment of the present invention, and FIG. 4 is a schematic diagram showing a gear train according to a third embodiment of the invention. ■・・・Input axis, 0・・・Output axis, X...
...First M star gear mechanism, Y...Second planetary gear mechanism, sl...First sun gear, B2...
...2nd gear, PCI...1st pinion carrier, PO2...2nd pinion carrier,
R1...First internal gear, R2...
...Second internal gear, cl...First clutch, C2...Second clutch, C3...
・Third clutch, C4...Fourth clutch, C5
...5th clutch, Bl...1st brake, B2...2nd brake, H, ...
・First gear mechanism (first transmission means), R2... Second gear mechanism (second transmission means), G1... First gear, G2... Second Gear, G3...3rd
Gear, G4...Fourth gear, K...Stationary part Patent applicant Nissan Motor Co., Ltd. Representative Patent attorney Tetsuya Mori Representative Patent attorney Yoshiaki Naito Representative Patent attorney Shimizu Authorized representative Patent attorney Officials dig out debts
Claims (1)
には、第１サンギヤ、第１インターナルギヤ及び第１ピ
ニオンキヤリヤを有する第１遊星歯車機構を設け、前記
出力軸上には、第２サンギヤ、第２インターナルギヤ及
び第２ビニオンキヤリヤを有する第２遊星歯車機構を設
け、前記入力軸と第１インターナルギヤとは連結可能と
し、前記入力軸と第１サンギヤとは連結可能とし、前記
第１サンギヤと第２ビニオンキヤリヤとは第１伝動手段
及びクラッチを介して断続可能に連結し、前記第１サン
ギヤと第２サンギヤとは前記第１伝動手段及び上記と異
なるクラッチを介して断続可能に連結し、前記第１ピニ
オンキヤリヤと出力軸とは第２伝動手段を介して連結し
、前記第２インターナルギヤと出力軸とは一体的に連結
し、前記第２サンギヤは第１ブレーキによって静止部に
対して固定可能とし、前記第２ビニオンキヤリヤは第２
ブレーキによって静止部に対して固定可能としたことを
特徴とする遊星歯車変速装置。An input shaft and an output shaft are arranged parallel to each other, a first planetary gear mechanism having a first sun gear, a first internal gear, and a first pinion carrier is provided on the input shaft, and a first planetary gear mechanism is provided on the output shaft. provides a second planetary gear mechanism having a second sun gear, a second internal gear, and a second pinion carrier, the input shaft and the first internal gear are connectable, and the input shaft and the first sun gear are connectable. The first sun gear and the second pinion carrier are connected in an intermittent manner via a first transmission means and a clutch, and the first sun gear and the second sun gear are connected via the first transmission means and a clutch different from the above. the first pinion carrier and the output shaft are connected via a second transmission means, the second internal gear and the output shaft are integrally connected, and the second sun gear is It can be fixed to a stationary part by a first brake, and the second pinion carrier is fixed to a stationary part by a first brake.
A planetary gear transmission characterized in that it can be fixed to a stationary part using a brake.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59041850A JPS60188645A (en) | 1984-03-05 | 1984-03-05 | Planetary gear transmission |
| DE19853507600 DE3507600A1 (en) | 1984-03-05 | 1985-03-04 | Epicyclic gearing |
| US07/102,300 US4774856A (en) | 1984-03-05 | 1987-09-25 | Planetary gear train |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59041850A JPS60188645A (en) | 1984-03-05 | 1984-03-05 | Planetary gear transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60188645A true JPS60188645A (en) | 1985-09-26 |
| JPH039337B2 JPH039337B2 (en) | 1991-02-08 |
Family
ID=12619724
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59041850A Granted JPS60188645A (en) | 1984-03-05 | 1984-03-05 | Planetary gear transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60188645A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6256652A (en) * | 1985-09-04 | 1987-03-12 | Mazda Motor Corp | Automatic speed change gear for vehicle |
| JP2010504491A (en) * | 2006-09-26 | 2010-02-12 | アントーノフ オートモーティブ テクノロジーズ ベスローテン フェンノートシャップ | Compact multi-ratio transmission |
| WO2016091655A1 (en) * | 2014-12-12 | 2016-06-16 | IFP Energies Nouvelles | Power train for driving a motor vehicle with a variable-speed transmission device having a double planetary gear set and especially a power train for a hybrid-type vehicle |
-
1984
- 1984-03-05 JP JP59041850A patent/JPS60188645A/en active Granted
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6256652A (en) * | 1985-09-04 | 1987-03-12 | Mazda Motor Corp | Automatic speed change gear for vehicle |
| JP2010504491A (en) * | 2006-09-26 | 2010-02-12 | アントーノフ オートモーティブ テクノロジーズ ベスローテン フェンノートシャップ | Compact multi-ratio transmission |
| WO2016091655A1 (en) * | 2014-12-12 | 2016-06-16 | IFP Energies Nouvelles | Power train for driving a motor vehicle with a variable-speed transmission device having a double planetary gear set and especially a power train for a hybrid-type vehicle |
| FR3029854A1 (en) * | 2014-12-12 | 2016-06-17 | Ifp Energies Now | POWER PLANT FOR DRIVING A MOTOR VEHICLE WITH AN EPICYCLOIDAL DOUBLE-AXIS SPEED VARIATION TRANSMISSION DEVICE AND ESPECIALLY A POWER PLANT FOR A HYBRID-TYPE VEHICLE. |
| CN107107734A (en) * | 2014-12-12 | 2017-08-29 | Ifp新能源公司 | Being used for the variable velocity transfer device including double epicyclics train of gears drives the dynamical system of motor vehicles, the dynamical system in particular for hybrid vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH039337B2 (en) | 1991-02-08 |
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| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |