JPH04300442A - Planetary gear line of automatic transmission - Google Patents
Planetary gear line of automatic transmissionInfo
- Publication number
- JPH04300442A JPH04300442A JP3064736A JP6473691A JPH04300442A JP H04300442 A JPH04300442 A JP H04300442A JP 3064736 A JP3064736 A JP 3064736A JP 6473691 A JP6473691 A JP 6473691A JP H04300442 A JPH04300442 A JP H04300442A
- Authority
- JP
- Japan
- Prior art keywords
- planetary gear
- gear
- speed
- additional
- ratio
- 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
- 230000005540 biological transmission Effects 0.000 title claims abstract description 18
- 230000007246 mechanism Effects 0.000 claims abstract description 33
- 238000010586 diagram Methods 0.000 description 7
- 239000000446 fuel Substances 0.000 description 5
- 230000003213 activating effect Effects 0.000 description 1
- 230000003321 amplification Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
- F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set 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
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six 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
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine 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
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three 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
- F16H2200/2051—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with eight 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
- F16H2200/2056—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with ten 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
- F16H2200/2058—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with eleven engaging means
Landscapes
- Structure Of Transmissions (AREA)
Abstract
Description
【0001】0001
【産業上の利用分野】本発明は、一組の単純遊星歯車機
構を追加して変速段数の多段化をはかる自動変速機の遊
星歯車列に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a planetary gear train for an automatic transmission that increases the number of gears by adding a set of simple planetary gear mechanisms.
【0002】0002
【従来の技術】従来の自動変速機の遊星歯車列としては
、例えば特開昭60−57036号公報や特開昭60−
88252号公報に記載されているものがある。BACKGROUND OF THE INVENTION Conventional planetary gear trains for automatic transmissions include, for example, Japanese Patent Application Laid-Open No. 60-57036 and Japanese Patent Application Laid-Open No. 60-60-57036.
There is one described in 88252 publication.
【0003】これらは、二組の単純遊星歯車機構から構
成される複列の遊星歯車列に対して、一組の単純遊星歯
車機構を追加し、且つブレーキやクラッチからなる摩擦
要素を7個備えることにより変速段数の多段化をはかり
、もって前進5段後進1段の変速段数を得ている。These systems add one set of simple planetary gear mechanisms to a double-row planetary gear train consisting of two sets of simple planetary gear mechanisms, and are equipped with seven friction elements consisting of brakes and clutches. As a result, the number of gears is multi-staged, resulting in five forward speeds and one reverse speed.
【0004】0004
【発明が解決しようとする課題】昨今、環境問題等から
車両の燃料消費率低減という社会的な要請が起きている
。[Problem to be Solved by the Invention] Recently, there has been a social demand for reducing the fuel consumption rate of vehicles due to environmental issues and other reasons.
【0005】しかるに、前記従来の自動変速機の遊星歯
車列では、燃料消費率が低減するオーバドライブ状態の
変速段を1段しか得ることができないという問題がある
。本発明は、前記のような問題点に着目してなされたも
ので、一組の単純遊星歯車機構を追加することにより変
速段数の多段化をはかると共に、オーバドライブ状態の
変速段を複数設定可能にすることを目的としている。However, the conventional planetary gear train of the automatic transmission described above has a problem in that it is only possible to obtain one gear in an overdrive state, which reduces the fuel consumption rate. The present invention was made with attention to the above-mentioned problems, and by adding a set of simple planetary gear mechanisms, it is possible to increase the number of gears and set a plurality of gears in an overdrive state. It is intended to be.
【0006】[0006]
【課題を解決するための手段】上記目的を達成するため
に、本発明の自動変速機の遊星歯車機構は、一組の単純
遊星歯車機構からなる増速段遊星歯車とこれに連結され
る別の遊星歯車機構とを有し、その増速段遊星歯車を作
動させることでオーバドライブ状態の変速段を得る複列
の遊星歯車列に、さらに別の一組の単純遊星歯車機構か
らなる追加遊星歯車を追加して、入力軸と前記増速段遊
星歯車のプラネットキャリヤとを連結可能とし、増速段
遊星歯車のプラネットキャリヤと追加遊星歯車のサンギ
ヤとを連結可能とし、増速段遊星歯車のリングギヤと追
加遊星歯車のリングギヤとを連結し、さらに、増速段遊
星歯車及び追加遊星歯車の両サンギヤを静止部に対して
夫々固定可能とすると共に、追加遊星歯車のプラネット
キャリヤと出力軸とを連結する自動変速機の遊星歯車列
において、前記増速段遊星歯車の歯車比を追加遊星歯車
の歯車比よりも大きく設定することを特徴としている。[Means for Solving the Problems] In order to achieve the above object, the planetary gear mechanism of the automatic transmission of the present invention includes a speed increasing planetary gear consisting of a set of simple planetary gear mechanisms, and another planetary gear connected to the planetary gear. A double-row planetary gear train that has a planetary gear mechanism and obtains an overdrive speed by operating the speed-increasing planetary gear, and an additional planetary gear train consisting of another set of simple planetary gear mechanisms. By adding a gear, the input shaft and the planet carrier of the speed increasing planetary gear can be connected, and the planet carrier of the speed increasing stage planetary gear and the sun gear of the additional planetary gear can be connected, and the speed increasing stage planetary gear The ring gear and the ring gear of the additional planetary gear are connected, and both the speed increasing stage planetary gear and the sun gear of the additional planetary gear can be respectively fixed to a stationary part, and the planet carrier of the additional planetary gear and the output shaft are connected. In the planetary gear train of the connected automatic transmission, the gear ratio of the speed increasing planetary gear is set to be larger than the gear ratio of the additional planetary gear.
【0007】前記増速段遊星歯車の歯車比を0.45よ
り大きくし、追加遊星歯車の歯車比を0.4未満に設定
すると共に、(1+追加遊星歯車の歯車比)/(1+増
速段遊星歯車の歯車比)の値を0.9未満に設定すると
するとよい。[0007] The gear ratio of the speed increasing stage planetary gear is set to be larger than 0.45, the gear ratio of the additional planetary gear is set to less than 0.4, and (1+gear ratio of the additional planetary gear)/(1+speed increasing gear ratio). It is preferable to set the value of the gear ratio (gear ratio of the step planetary gear) to less than 0.9.
【0008】[0008]
【作用】二組の遊星歯車機構からなる複列の歯車列に一
組の単純遊星歯車機構を追加することで、変速段数の多
段化をはかる。[Operation] By adding one set of simple planetary gear mechanisms to a double gear train consisting of two sets of planetary gear mechanisms, the number of gears can be increased.
【0009】このとき、増速段遊星歯車及び追加遊星歯
車だけを作動させた場合、その増速段遊星歯車及び追加
遊星歯車の両サンギヤを固定することで(1+追加遊星
歯車の歯車比)/(1+増速段遊星歯車の歯車比)とな
る変速比を得ることができる。また、増速段遊星歯車の
サンギヤを固定し且つ増速段遊星歯車のプラネットキャ
リヤと追加遊星歯車のサンギヤと連結することで(1+
追加遊星歯車の歯車比)/(1+増速段遊星歯車の歯車
比+追加遊星歯車の歯車比)の変速比を得ることができ
る。At this time, when only the speed-up stage planetary gear and the additional planetary gear are operated, by fixing both the sun gears of the speed-up stage planetary gear and the additional planetary gear, (1+gear ratio of the additional planetary gear)/ It is possible to obtain a gear ratio of (1+gear ratio of the planetary gear of the speed increasing stage). In addition, by fixing the sun gear of the speed increasing planetary gear and connecting the planet carrier of the speed increasing stage planetary gear with the sun gear of the additional planetary gear (1+
A gear ratio of (gear ratio of the additional planetary gear)/(1+gear ratio of the speed-increasing stage planetary gear+gear ratio of the additional planetary gear) can be obtained.
【0010】前記後者の変速比は、増速段遊星歯車の歯
車比及び追加遊星歯車の歯車比の値に関係なくオーバド
ライブ状態の変速比となるが、前者の変速比は増速段遊
星歯車の歯車比及び追加遊星歯車の歯車比の値によって
オーバドライブ状態にならないことがある。本発明では
、前記増速段遊星歯車の歯車比を追加遊星歯車の歯車比
よりも大きく設定することで、前記両者の変速比を確実
にオーバドライブ状態の変速比にする。The latter gear ratio is an overdrive gear ratio regardless of the gear ratio of the gear ratio of the gear-up planetary gear and the gear ratio of the additional planetary gear, but the former gear ratio is the gear ratio of the gear ratio of the gear-up planetary gear. The overdrive state may not occur depending on the gear ratio of the additional planetary gear and the gear ratio of the additional planetary gear. In the present invention, by setting the gear ratio of the step-up planetary gear to be larger than the gear ratio of the additional planetary gear, both gear ratios are reliably brought into an overdrive state.
【0011】追加遊星歯車を作動させずに増速段遊星歯
車のみを作動させて、さらにオーバドライブ状態の変速
段を増やすこともできる。なお、前記複列の遊星歯車列
は二組の遊星歯車機構から構成されるものに限るもので
なく三組以上でもよいし一組でも構わない。[0011] It is also possible to operate only the speed increasing planetary gear without activating the additional planetary gear to further increase the number of speeds in the overdrive state. Note that the double-row planetary gear train is not limited to one consisting of two sets of planetary gear mechanisms, and may be three or more sets, or may be one set.
【0012】また、前記増速段遊星歯車の歯車比及び追
加遊星歯車の歯車比において、増速段遊星歯車の歯車比
を0.45より大きくし、追加遊星歯車の歯車比を0.
4未満に設定すると共に、(1+追加遊星歯車の歯車比
)/(1+増速段遊星歯車の歯車比)の値を0.9未満
となるように設定すると、オーバドライブ状態への移行
及びオーバドライブ状態での変速段間の段間差が適切な
値となり、オーバドライブ状態での円滑な変速を可能に
する。Further, in the gear ratio of the speed increasing planetary gear and the gear ratio of the additional planetary gear, the gear ratio of the speed increasing stage planetary gear is set to be greater than 0.45, and the gear ratio of the additional planetary gear is set to 0.45.
If the value of (1+gear ratio of additional planetary gear)/(1+gear ratio of speed-up stage planetary gear) is set to less than 0.9, transition to overdrive state and overdrive will occur. The difference between gears in the drive state becomes an appropriate value, enabling smooth gear changes in the overdrive state.
【0013】[0013]
【実施例】以下、本発明の実施例を図面に基づいて説明
する。図1は、本発明に係わる自動変速機の遊星歯車列
の第1実施例を示す図である。Embodiments Hereinafter, embodiments of the present invention will be explained based on the drawings. FIG. 1 is a diagram showing a first embodiment of a planetary gear train of an automatic transmission according to the present invention.
【0014】まず構成を説明すると、図中Nは図示して
いないエンジン側の出力軸に連結された入力軸を指し、
Uは出力軸を指して、その入力軸Nと出力軸Uとの間に
、2組の単純遊星歯車機構G1,G2からなる複列の遊
星歯車列BG、一組の単純遊星歯車機構からなる追加遊
星歯車、第1〜5クラッチC1〜C5、第1,第2ブレ
ーキB1,B2及び第1〜3ワンウェイクラッチWC1
〜WC3が設けられている。First, to explain the configuration, N in the figure refers to an input shaft connected to an output shaft on the engine side (not shown).
U indicates the output shaft, and between the input shaft N and the output shaft U, there is a double-row planetary gear train BG consisting of two sets of simple planetary gear mechanisms G1 and G2, and one set of simple planetary gear mechanisms. Additional planetary gears, first to fifth clutches C1 to C5, first and second brakes B1, B2, and first to third one-way clutches WC1
~WC3 is provided.
【0015】前記複列の遊星歯車列BGは、第1単純遊
星歯車機構G1と増幅段遊星歯車である第2単純遊星歯
車機構G2から構成されて、当該第1単純遊星歯車機構
G1は第1サンギヤS1,第1リングギヤR1及び第1
プラネットキャリヤPC1からなり、第2単純遊星歯車
機構G2は第2サンギヤS2,第2リングギヤR2及び
第2プラネットキャリヤPC2からなる。The double-row planetary gear train BG is composed of a first simple planetary gear mechanism G1 and a second simple planetary gear mechanism G2 which is an amplification stage planetary gear. Sun gear S1, first ring gear R1 and first
The second simple planetary gear mechanism G2 consists of a second sun gear S2, a second ring gear R2, and a second planet carrier PC2.
【0016】また、前記追加遊星歯車は第3単純遊星歯
車機構G3からなり、その第3単純遊星歯車機構G3は
第3サンギヤS3,第3リングギヤR3及び第3プラネ
ットキャリヤPC3から構成されている。Further, the additional planetary gear is composed of a third simple planetary gear mechanism G3, and the third simple planetary gear mechanism G3 is composed of a third sun gear S3, a third ring gear R3, and a third planet carrier PC3.
【0017】そして、前記入力軸Nは、第1リングギヤ
R1に連結されると共に、該第1リングギヤR1と並列
に配列された第1クラッチC1を介して第1サンギヤS
1に断続可能に連結されている。前記入力軸Nは、第1
クラッチC1と直列に連結された第3クラッチC3若し
くは第1ワンウェイクラッチWC1を介して第2サンギ
ヤS2にも断続可能に連結され、その第2サンギヤS2
は第1ブレーキB1を介して静止部に固定可能となって
いる。また、前記入力軸Nは、前記第3クラッチC3と
並列に配列された第4クラッチC4を介して第2プラネ
ットキャリヤPC2とも断続可能に連結されている。そ
の第2プラネットキャリヤPC2は、静止部であるケー
スKに第2ワンウェイクラッチWC2を介して固定可能
となると共に、第5クラッチC5を介して第3サンギヤ
S3とも断続可能に連結されている。その第3サンギヤ
S3は第2ブレーキB2若しくは第3ワンウェイクラッ
チWC3を介して静止部であるケースKに固定可能とな
っている。The input shaft N is connected to a first ring gear R1, and is connected to a first sun gear S via a first clutch C1 arranged in parallel with the first ring gear R1.
1. The input shaft N is a first
The second sun gear S2 is also intermittently connected to the second sun gear S2 via the third clutch C3 or the first one-way clutch WC1 connected in series with the clutch C1.
can be fixed to a stationary part via the first brake B1. Further, the input shaft N is also connected intermittently to the second planet carrier PC2 via a fourth clutch C4 arranged in parallel with the third clutch C3. The second planet carrier PC2 can be fixed to the case K, which is a stationary part, via the second one-way clutch WC2, and is also connected in an intermittent manner to the third sun gear S3 via the fifth clutch C5. The third sun gear S3 can be fixed to the case K, which is a stationary part, via the second brake B2 or the third one-way clutch WC3.
【0018】また、第1プラネットキャリヤPC1は、
第2クラッチC2を介して第2リングギヤR2及び第3
リングギヤR3と断続可能の連結され、その第3リング
ギヤR3に噛合する第3プラネットキャリヤPC3が出
力軸Uに連結されている。[0018] Furthermore, the first planet carrier PC1 is
The second ring gear R2 and the third ring gear are connected via the second clutch C2.
A third planet carrier PC3 is connected to the output shaft U and is intermittably connected to the ring gear R3 and meshes with the third ring gear R3.
【0019】以上の構成よりなる自動変換機の遊星歯車
列では、各ブレーキB1,B2、クラッチC1〜C5及
びワンウェイクラッチWC1〜WC3を図2(a)に示
す組合せで選択的に作動させることにより、図2(b)
に示される前進6速後進1速を得ることができる。In the planetary gear train of the automatic converter having the above configuration, each brake B1, B2, clutches C1 to C5, and one-way clutches WC1 to WC3 are selectively operated in the combination shown in FIG. 2(a). , Figure 2(b)
Six forward speeds and one reverse speed shown in can be obtained.
【0020】なお、図2(a)において、○印は締結状
態を示し、無印は開放状態を示している。また、α1は
第1リングギヤR1の歯車数に対する第1サンギヤS1
の歯車数の比を表し、α2は第2リングギヤR2の歯車
数に対する第2サンギヤS2の歯車数の比を表し、α3
は第3リングギヤR3の歯車数に対する第3サンギヤS
3の歯車数の比を表している。[0020] In Fig. 2(a), a circle mark indicates a fastened state, and a blank mark indicates an open state. Further, α1 is the first sun gear S1 relative to the number of gears of the first ring gear R1.
α2 represents the ratio of the number of gears of second sun gear S2 to the number of gears of second ring gear R2, α3
is the third sun gear S with respect to the number of gears of the third ring gear R3
It represents the ratio of the number of gears of 3.
【0021】そして、第5及び第6速の変速段において
は、図2に示すように、増速段遊星歯車である第2単純
遊星歯車機構G2と追加遊星歯車機構である第3単純遊
星歯車機構G3だけが作動し、第5速では、第2,第3
サンギヤS2,S3を固定することで(1+α3)/(
1+α2)の変速比を得る。また、第6速では、第2サ
ンギヤS2を固定し且つ第2プラネットキャリヤPC2
と第3サンギヤS3を連結することで(1+α3)/(
1+α2+α3)の変速比を得る。In the fifth and sixth gears, as shown in FIG. 2, the second simple planetary gear mechanism G2, which is a speed-increasing planetary gear, and the third simple planetary gear mechanism, which is an additional planetary gear mechanism. Only mechanism G3 operates, and in 5th gear, the 2nd and 3rd
By fixing sun gears S2 and S3, (1+α3)/(
A gear ratio of 1+α2) is obtained. Further, in the sixth speed, the second sun gear S2 is fixed and the second planet carrier PC2 is fixed.
By connecting the third sun gear S3 to (1+α3)/(
A gear ratio of 1+α2+α3) is obtained.
【0022】このとき、増速段遊星歯車の歯車比である
α2は追加遊星歯車の歯車比であるα3より大きく設定
されるために、当該第5及び第6速時の変速比はオーバ
ドライブ状態になる。かくして、オーバドライブ状態の
変速段を2段設定できることとなる。[0022] At this time, since α2, which is the gear ratio of the speed increasing planetary gear, is set larger than α3, which is the gear ratio of the additional planetary gear, the gear ratio at the fifth and sixth speeds is in an overdrive state. become. In this way, it is possible to set two gears in the overdrive state.
【0023】また、α2を0.50とし、α3を0.3
0とすることで、(1+α3)/(1+α2)の値が0
.867となり、図2に示すように、第4速から第5速
、第5速から第6速への段間差が0.133及び0.1
45となって、オーバドライブ状態の変速段間の段間差
が適切な値となり、オーバドライブ状態への移行及びオ
ーバドライブ状態での円滑な変速を可能にする。[0023] Also, α2 is set to 0.50, and α3 is set to 0.3.
By setting it to 0, the value of (1+α3)/(1+α2) becomes 0.
.. 867, and as shown in Fig. 2, the gear difference from 4th speed to 5th speed and from 5th speed to 6th speed is 0.133 and 0.1.
45, the difference between the gears in the overdrive state becomes an appropriate value, making it possible to shift to the overdrive state and smoothly shift gears in the overdrive state.
【0024】次に第2実施例を説明する。図3は第2実
施例を説明する図である。この実施例は、入力軸Nを、
第1クラッチC1を介して第2サンギヤS2に断続可能
に連結し、また、該入力軸Nを前記第1クラッチC1と
並列に配列された第4クラッチC4を介して第1サンギ
ヤS1に連結すると共に、前記第1クラッチC1と並列
に配列された第3クラッチC3を介して、その入力軸N
は、第1リングギヤR1とも断続可能に連結し、さらに
、その第1リングギヤR1を介して第2プラネットキャ
リヤPC2とも連結されてる。また、第1プラネットキ
ャリヤPC1を第2リングギヤR2及び第3リングギヤ
R3に第2クラッチC2若しくは第1ワンウェイクラッ
チWC1を介して断続可能に連結している。Next, a second embodiment will be explained. FIG. 3 is a diagram illustrating the second embodiment. In this embodiment, the input shaft N is
The input shaft N is intermittably connected to the second sun gear S2 via a first clutch C1, and the input shaft N is connected to the first sun gear S1 via a fourth clutch C4 arranged in parallel with the first clutch C1. At the same time, the input shaft N is connected via a third clutch C3 arranged in parallel with the first clutch C1.
is intermittably connected to the first ring gear R1, and further connected to the second planet carrier PC2 via the first ring gear R1. Further, the first planet carrier PC1 is connected to the second ring gear R2 and the third ring gear R3 in an intermittent manner via the second clutch C2 or the first one-way clutch WC1.
【0025】他の構成は第1実施例と同様であり、各ブ
レーキB1,B2、クラッチC1〜C5及びワンウェイ
クラッチWC1〜WC3を図4(a)に示す組合せで選
択的に作動させることにより、図4(b)に示される前
進6速後進1速を得ることができる。The other configurations are the same as the first embodiment, and by selectively operating the brakes B1, B2, clutches C1 to C5, and one-way clutches WC1 to WC3 in the combination shown in FIG. 4(a), Six forward speeds and one reverse speed shown in FIG. 4(b) can be obtained.
【0026】この場合にも第1実施例と同様に、第5速
及び第6速をオーバドライブ状態の変速段にすることが
できる。次に第3実施例を説明する。図5は第3実施例
を説明する図である。In this case, as in the first embodiment, the fifth and sixth speeds can be set to overdrive. Next, a third embodiment will be described. FIG. 5 is a diagram illustrating the third embodiment.
【0027】この実施例は、第3リングギヤと第3サン
ギヤとを第6クラッチを介して断続可能に連結したほか
は第1実施例と同じ構成である。この場合にも、各ブレ
ーキB1,B2、クラッチC1〜6及びワンウェイクラ
ッチWC1〜3を図6に示す組合せで選択的に作動させ
ることにより、図7に示される前進9速後進1速を得る
ことができる。This embodiment has the same structure as the first embodiment except that the third ring gear and the third sun gear are connected in an intermittent manner via a sixth clutch. In this case as well, by selectively operating each brake B1, B2, clutches C1-6, and one-way clutches WC1-3 in the combination shown in FIG. 6, nine forward speeds and one reverse speed shown in FIG. 7 can be obtained. Can be done.
【0028】この実施例では、第7〜第9速がオーバド
ライブ状態になり、オーバドライブ状態の変速比を3段
得ることができる。以上のように、一組の単純遊星歯車
機構を追加して変速段数の多段化をはかり、車両の連続
的な速度変化に対応したより相応しい変速比を得ると共
に、変速比が1よりも小さい、オーバドライブ状態の変
速段を2〜3段と複数設定することが可能となる。In this embodiment, the 7th to 9th speeds are in the overdrive state, and it is possible to obtain three speed ratios in the overdrive state. As described above, by adding a set of simple planetary gear mechanisms to increase the number of gears, a gear ratio more suitable for responding to continuous speed changes of the vehicle can be obtained, and the gear ratio is smaller than 1. It becomes possible to set a plurality of gear stages in the overdrive state, such as 2 to 3 stages.
【0029】そして、オーバドライブ状態の変速段を複
数設定することによって、比較的高速の定常走行におい
て燃料消費率を重視した変速ポジションが選択可能とな
り、かくしてエンジンの回転数をきめ細かく制御できる
と共に、燃料消費量の低減が期待できる。By setting a plurality of overdrive gears, it is possible to select a gear position that emphasizes the fuel consumption rate during steady driving at relatively high speeds. A reduction in consumption can be expected.
【0030】[0030]
【発明の効果】以上説明してきたように、本発明の自動
遊歯車列は、一組の単純遊星歯車機構を追加して変速段
数の多段化をはかることで、車両の連続的な速度変化に
対応したより相応しい変速比を得ると共に、オーバドラ
イブ状態の変速段を2〜3段と複数設定可能にすること
で、比較的高速の定常走行において燃料消費率を重視し
た変速ポジションを選択して、エンジンの回転数をきめ
細かく制御でき且つ燃料消費量の低減が期待できる。[Effects of the Invention] As explained above, the automatic idler gear train of the present invention is capable of responding to continuous speed changes of a vehicle by adding a set of simple planetary gear mechanisms to increase the number of gears. In addition to obtaining a more appropriate gear ratio, by making it possible to set multiple overdrive gears (2 to 3), it is possible to select a gear position that emphasizes fuel consumption during steady driving at relatively high speeds. The engine speed can be precisely controlled and fuel consumption can be expected to be reduced.
【0031】また、増速段遊星歯車の歯車比を0.45
より大きくし、追加遊星歯車の歯車比を0.4未満に設
定すると共に、(1+追加遊星歯車の歯車比)/(1+
増速段遊星歯車の歯車比)を0.9未満に抑えることで
、オーバドライブ状態への移行及びオーバドライブ状態
での円滑な変速を可能とすることができる。[0031] Also, the gear ratio of the speed increasing stage planetary gear is set to 0.45.
and set the gear ratio of the additional planetary gear to less than 0.4, and (1+gear ratio of the additional planetary gear)/(1+
By suppressing the gear ratio (gear ratio of the speed increasing planetary gear) to less than 0.9, it is possible to shift to an overdrive state and smoothly change gears in the overdrive state.
【図1】第1実施例による自動変速機の遊星歯車列を示
す概略骨組図である。FIG. 1 is a schematic diagram showing a planetary gear train of an automatic transmission according to a first embodiment.
【図2】第1実施例による自動変速機の遊星歯車列の作
動要素の組合せとその変速比を示す図表である。FIG. 2 is a chart showing combinations of operating elements of a planetary gear train of the automatic transmission according to the first embodiment and their gear ratios.
【図3】第2実施例による自動変速機の遊星歯車列を示
す概略骨組図である。FIG. 3 is a schematic diagram showing a planetary gear train of an automatic transmission according to a second embodiment.
【図4】第2実施例による自動変速機の遊星歯車列の作
動要素の組合せとその変速比を示す図表である。FIG. 4 is a chart showing combinations of operating elements of a planetary gear train of an automatic transmission according to a second embodiment and their gear ratios.
【図5】第3実施例による自動変速機の遊星歯車列を示
す概略骨組図である。FIG. 5 is a schematic diagram showing a planetary gear train of an automatic transmission according to a third embodiment.
【図6】第3実施例による自動変速機の遊星歯車列の作
動要素の組合せを示す図表である。FIG. 6 is a diagram showing a combination of operating elements of a planetary gear train of an automatic transmission according to a third embodiment.
【図7】第3実施例による自動変速機の遊星歯車列の変
速比を示す図表である。FIG. 7 is a chart showing the speed ratio of the planetary gear train of the automatic transmission according to the third embodiment.
N 入力軸
U 出力軸
BG 複列の遊星歯車列
G1 第1遊星歯車機構
G2 第2遊星歯車機構(増速段遊星歯車)G3
第3遊星歯車機構(追加遊星歯車)S1
第1サンギヤ
R1 第1リングギヤ
PC1 第1プラネットキャリヤ
S2 第2サンギヤ
R2 第2リングギヤ
PC2 第2プラネットキャリヤ
S3 第3サンギヤ
R3 第3リングギヤ
PC3 第3プラネットキャリヤ
C1 第1クラッチ
C2 第2クラッチ
C3 第3クラッチ
C4 第4クラッチ
C5 第5クラッチ
C6 第6クラッチ
B1 第1ブレーキ
B2 第2ブレーキ
WC1 第1ワンウェイクラッチ
WC2 第2ワンウェイクラッチ
WC3 第3ワンウェイクラッチN Input shaft U Output shaft BG Double-row planetary gear train G1 First planetary gear mechanism G2 Second planetary gear mechanism (speed-up stage planetary gear) G3
Third planetary gear mechanism (additional planetary gear) S1
1st sun gear R1 1st ring gear PC1 1st planet carrier S2 2nd sun gear R2 2nd ring gear PC2 2nd planet carrier S3 3rd sun gear R3 3rd ring gear PC3 3rd planet carrier C1 1st clutch C2 2nd clutch C3 3rd clutch C4 4th clutch C5 5th clutch C6 6th clutch B1 1st brake B2 2nd brake WC1 1st one-way clutch WC2 2nd one-way clutch WC3 3rd one-way clutch
Claims (2)
段遊星歯車とこれに連結される別の遊星歯車機構とを有
し、その増速段遊星歯車を作動させることでオーバドラ
イブ状態の変速段を得る複列の遊星歯車列に、さらに別
の一組の単純遊星歯車機構からなる追加遊星歯車を追加
して、入力軸と前記増速段遊星歯車のプラネットキャリ
ヤとを連結可能とし、増速段遊星歯車のプラネットキャ
リヤと追加遊星歯車のサンギヤとを連結可能とし、増速
段遊星歯車のリングギヤと追加遊星歯車のリングギヤと
を連結し、さらに、増速段遊星歯車及び追加遊星歯車の
両サンギヤを静止部に対して夫々固定可能とすると共に
、追加遊星歯車のプラネットキャリヤと出力軸とを連結
する自動変速機の遊星歯車列において、前記増速段遊星
歯車の歯車比を追加遊星歯車の歯車比よりも大きく設定
することを特徴とする自動変速機の遊星歯車列。Claim 1: A speed increasing planetary gear consisting of a set of simple planetary gear mechanisms and another planetary gear mechanism connected thereto, and by operating the speed increasing planetary gear, an overdrive state is achieved. Adding an additional planetary gear consisting of another set of simple planetary gear mechanisms to the double-row planetary gear train that obtains the speed change stage, so that the input shaft and the planet carrier of the speed increase stage planetary gear can be connected, The planet carrier of the speed-up stage planetary gear and the sun gear of the additional planetary gear can be connected, the ring gear of the speed-up stage planetary gear and the ring gear of the additional planetary gear can be connected, and the planet carrier of the speed-up stage planetary gear and the additional planetary gear can be connected. In a planetary gear train of an automatic transmission in which both sun gears can be respectively fixed to a stationary part and a planet carrier of an additional planetary gear is connected to an output shaft, the gear ratio of the speed increasing stage planetary gear is changed to an additional planetary gear. A planetary gear train for an automatic transmission characterized by having a gear ratio set larger than that of the gear ratio.
り大きくし、追加遊星歯車の歯車比を0.4未満に設定
すると共に、(1+追加遊星歯車の歯車比)/(1+増
速段遊星歯車の歯車比)の値を0.9未満に設定するこ
とを特徴とする請求項1記載の自動変速機の遊星歯車列
。2. The gear ratio of the speed increasing planetary gear is set to be larger than 0.45, the gear ratio of the additional planetary gear is set to less than 0.4, and (1+gear ratio of the additional planetary gear)/(1+increase gear ratio). 2. The planetary gear train for an automatic transmission according to claim 1, wherein the gear ratio of the speed planetary gear is set to less than 0.9.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP3064736A JPH04300442A (en) | 1991-03-28 | 1991-03-28 | Planetary gear line of automatic transmission |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP3064736A JPH04300442A (en) | 1991-03-28 | 1991-03-28 | Planetary gear line of automatic transmission |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH04300442A true JPH04300442A (en) | 1992-10-23 |
Family
ID=13266732
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP3064736A Pending JPH04300442A (en) | 1991-03-28 | 1991-03-28 | Planetary gear line of automatic transmission |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH04300442A (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6783477B2 (en) * | 2002-12-18 | 2004-08-31 | General Motors Corporation | Family of six-speed dual-clutch transmissions having three planetary gear sets |
US7081066B2 (en) * | 2004-08-18 | 2006-07-25 | General Motors Corporation | Planetary transmissions having three non-continuously interconnected gear sets |
KR100610797B1 (en) * | 2004-09-07 | 2006-08-09 | 현대자동차주식회사 | A six-speed powertrain of an automatic transmission |
KR100610798B1 (en) * | 2004-09-07 | 2006-08-09 | 현대자동차주식회사 | A six-speed powertrain of an automatic transmission |
KR100610795B1 (en) * | 2004-09-07 | 2006-08-09 | 현대자동차주식회사 | A six-speed powertrain of an automatic transmission |
KR100610796B1 (en) * | 2004-09-07 | 2006-08-09 | 현대자동차주식회사 | A six-speed powertrain of an automatic transmission |
KR100610794B1 (en) * | 2004-09-07 | 2006-08-09 | 현대자동차주식회사 | A six-speed powertrain of an automatic transmission |
US7198587B2 (en) * | 2003-12-16 | 2007-04-03 | General Motors Corporation | Transmission with selectable braking one-way clutch |
-
1991
- 1991-03-28 JP JP3064736A patent/JPH04300442A/en active Pending
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6783477B2 (en) * | 2002-12-18 | 2004-08-31 | General Motors Corporation | Family of six-speed dual-clutch transmissions having three planetary gear sets |
US7033298B2 (en) * | 2002-12-18 | 2006-04-25 | General Motors Corporation | Family of five-speed dual-clutch transmissions having three planetary gear sets |
US7198587B2 (en) * | 2003-12-16 | 2007-04-03 | General Motors Corporation | Transmission with selectable braking one-way clutch |
US7081066B2 (en) * | 2004-08-18 | 2006-07-25 | General Motors Corporation | Planetary transmissions having three non-continuously interconnected gear sets |
KR100610797B1 (en) * | 2004-09-07 | 2006-08-09 | 현대자동차주식회사 | A six-speed powertrain of an automatic transmission |
KR100610798B1 (en) * | 2004-09-07 | 2006-08-09 | 현대자동차주식회사 | A six-speed powertrain of an automatic transmission |
KR100610795B1 (en) * | 2004-09-07 | 2006-08-09 | 현대자동차주식회사 | A six-speed powertrain of an automatic transmission |
KR100610796B1 (en) * | 2004-09-07 | 2006-08-09 | 현대자동차주식회사 | A six-speed powertrain of an automatic transmission |
KR100610794B1 (en) * | 2004-09-07 | 2006-08-09 | 현대자동차주식회사 | A six-speed powertrain of an automatic transmission |
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