JPH039336B2 - - Google Patents
Info
- Publication number
- JPH039336B2 JPH039336B2 JP58196733A JP19673383A JPH039336B2 JP H039336 B2 JPH039336 B2 JP H039336B2 JP 58196733 A JP58196733 A JP 58196733A JP 19673383 A JP19673383 A JP 19673383A JP H039336 B2 JPH039336 B2 JP H039336B2
- Authority
- JP
- Japan
- Prior art keywords
- gear
- carrier
- sun gear
- planetary gear
- clutch
- 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.)
- Expired - Lifetime
Links
- 230000005540 biological transmission Effects 0.000 claims description 14
- 238000010586 diagram Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、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.
（従来技術）
従来の遊星歯車変速装置としては、２速、３速
の変速段数の他に、第１図に示すような４速の遊
星歯車変速装置があつた（米国特許明細書第
42377449号公報）。(Prior Art) As a conventional planetary gear transmission, in addition to the 2nd and 3rd speeds, there was a 4-speed planetary gear transmission as shown in FIG.
42377449).
しかしながら、車両の連続的な速度変化に対応
し、燃費や回転伝達効率等の見地からよりふさわ
しい変速比を得るためには４速の変速段数では少
ないという問題点があつた。 However, there has been a problem in that four speeds is insufficient in order to respond to continuous speed changes of the vehicle and obtain a gear ratio that is more appropriate from the standpoint of fuel efficiency, rotational transmission efficiency, and the like.
（発明の目的）
そこで本発明は、歯車列の変速段数を５速にし
て、車両の連続的な変速変化に対応したよりふさ
わしい変速比を得ることを目的とする。(Objective of the Invention) Therefore, an object of the present invention is to increase the number of gears of the gear train to five speeds to obtain a gear ratio more suitable for the continuous gear change of the vehicle.
（発明の構成）
本発明に係る遊星歯車変速装置は、入力軸と出
力軸との間でケース内に設けられ、第１サンギ
ヤ、第１キヤリヤおよび第１リングギヤを有する
第１遊星歯車機構と、第２サンギヤ、第２キヤリ
ヤおよび第２リングギヤを有する第２遊星歯車機
構と、第３サンギヤ、第３キヤリヤおよび第３リ
ングギヤを有する第３遊星歯車機構と、を備えた
遊星歯車変速装置において、前記入力軸と第１サ
ンギヤとを第１断続手段を介して連結し、前記入
力軸と第１キヤリヤとを第２断続手段を介して連
結し、前記入力軸と第２サンギヤとを一体的に連
結し、前記第１リングギヤと第２キヤリヤと第３
リングギヤとを一体的に連結し、前記第２リング
ギヤと第１キヤリヤとを第３断続手段を介して連
結し、前記第１キヤリヤと第３サンギヤとを第４
断続手段を介して連結し、前記第３キヤリヤと出
力軸とを一体的に連結し、前記ケースと第１サン
ギヤとを第５断続手段を介して連結し、前記ケー
スと第３サンギヤとを第６断続手段を介して連結
した構成としている。(Structure of the Invention) A planetary gear transmission according to the present invention includes a first planetary gear mechanism provided in a case between an input shaft and an output shaft, and having a first sun gear, a first carrier, and a first ring gear; A planetary gear transmission comprising: a second planetary gear mechanism having a second sun gear, a second carrier, and a second ring gear; and a third planetary gear mechanism having a third sun gear, a third carrier, and a third ring gear; The input shaft and the first sun gear are connected through a first disconnection means, the input shaft and the first carrier are connected through a second disconnection means, and the input shaft and the second sun gear are integrally connected. and the first ring gear, the second carrier and the third
a ring gear, the second ring gear and the first carrier are connected via a third disconnecting means, and the first carrier and the third sun gear are connected to each other through a fourth connecting means.
The third carrier and the output shaft are connected together through a disconnecting means, the third carrier and the output shaft are integrally connected, the case and the first sun gear are connected through a fifth disconnecting means, and the case and the third sun gear are connected through a fifth connecting means. 6. The configuration is such that they are connected via six disconnecting means.
（実施例）
以下、本発明の実施例を図面に基づいて説明す
る。第２ａ図は本発明に係る遊星歯車変速装置の
第１実施例を示す図である。(Example) Hereinafter, an example of the present invention will be described based on the drawings. FIG. 2a is a diagram showing a first embodiment of a planetary gear transmission according to the present invention.
同図において、Ｉは図外のエンジンの出力軸と
連結された入力軸であり、この入力軸Ｉは第１ク
ラツチC1（第１断続手段）を介して断続可能に第
１サンギヤS1と連結しているとともに、第１クラ
ツチC1と並列的に第１ワンウエイクラツチOC1を
も介して連結している。第１サンギヤS1は第１キ
ヤリヤPC1に支持された第１プラネタリギヤP1と
外接噛合し、このプラネタリギヤP1は第１リン
グギヤR1と内接噛合する。したがつて、第１サ
ンギヤS1、第１キヤリヤPC1、第１プラネタリギ
ヤP1および第１リングギヤR1は、全体として第
１遊星歯車機構を構成する。入力軸Ｉは、第２ク
ラツチC2（第２断続手段）を介して断続可能に第
１キヤリヤPC1と連結しているとともに、第２サ
ンギヤS2と一体的に連結している。第２サンギヤ
S2は第２キヤリヤPC2に支持された第２プラネタ
リギヤP2と外接噛合し、この第２プラネタリギ
ヤP2は第２リングギヤR2と内接噛合する。した
がつて、第２サンギヤS2、第２キヤリヤPC2、第
２プラネタリギヤP2および第２リングギヤR2は、
全体として第２遊星歯車機構を構成する。第１リ
ングギヤR1は第２キヤリヤPC2および第３リング
ギヤR3と一体的に連結している。第３リングギ
ヤR3は第３キヤリヤPC3に支持された第３プラネ
タリギヤP3と内接噛合し、この第３プラネタリ
ギヤP3は第３サンギヤS3と外接噛合する。した
がつて、第３サンギヤS3、第３キヤリヤPC3、第
３プラネタリギヤP3および第３リングギヤR3は、
全体として第３遊星歯車機構を構成する。第２リ
ングギヤR2は第３クラツチC3（第３断続手段）を
介して断続可能に第１キヤリヤPC1と連結してい
る。さらに第１キヤリヤPC1は、第４クラツチC4
（第４断続手段）を介して断続可能に第３サンギ
ヤS3と連結しているとともに、第４クラツチC4
と並列的に第２ワンウエイクラツチOC2をも介し
て連結している。第１サンギヤS1は第１ブレーキ
B1（第５断続手段）を介して断続可能にケースＨ
と連結されている。第３サンギヤS3とケースＨと
は、第２ブレーキB2（第６断続手段）を介して断
続可能に連結されているとともに、第２ブレーキ
B2と並列的に第３ワンウエイクラツチOC3をも介
して連結されている。第３キヤリヤPC3と出力軸
Ｏとは一体的に連結している。 In the figure, I is an input shaft connected to the output shaft of an engine (not shown), and this input shaft I is connected to the first sun gear S 1 in an intermittent manner via a first clutch C 1 (first disconnection means). The first clutch C1 is also connected via a first one-way clutch OC1 in parallel with the first clutch C1. The first sun gear S 1 externally meshes with a first planetary gear P 1 supported by a first carrier PC 1 , and this planetary gear P 1 internally meshes with a first ring gear R 1 . Therefore, the first sun gear S 1 , the first carrier PC 1 , the first planetary gear P 1 and the first ring gear R 1 constitute a first planetary gear mechanism as a whole. The input shaft I is intermittably connected to the first carrier PC 1 via a second clutch C 2 (second disconnecting means) and integrally connected to the second sun gear S 2 . 2nd sun gear
S 2 externally meshes with a second planetary gear P 2 supported by a second carrier PC 2 , and this second planetary gear P 2 internally meshes with a second ring gear R 2 . Therefore, second sun gear S 2 , second carrier PC 2 , second planetary gear P 2 and second ring gear R 2 are as follows:
The second planetary gear mechanism is constructed as a whole. The first ring gear R1 is integrally connected to the second carrier PC2 and the third ring gear R3 . The third ring gear R3 is internally meshed with a third planetary gear P3 supported by a third carrier PC3 , and this third planetary gear P3 is externally meshed with a third sun gear S3 . Therefore, the third sun gear S 3 , the third carrier PC 3 , the third planetary gear P 3 and the third ring gear R 3 are as follows:
The third planetary gear mechanism is constructed as a whole. The second ring gear R2 is disconnectably connected to the first carrier PC1 via a third clutch C3 (third disconnecting means). Furthermore, the first carrier PC 1 is connected to the fourth clutch C 4
The fourth clutch C4 is connected to the third sun gear S3 in an intermittent manner via a fourth clutch C4.
In parallel, it is also connected via a second one-way clutch OC2 . 1st sun gear S 1 is the 1st brake
Case H can be disconnected via B 1 (fifth disconnection means)
is connected to. The third sun gear S 3 and the case H are intermittably connected via the second brake B 2 (sixth disconnection means), and the second brake
It is also connected in parallel to B 2 via a third one-way clutch OC 3 . The third carrier PC 3 and the output shaft O are integrally connected.
以上の構成より成る遊星変速装置における各ク
ラツチC1〜C4、各ブレーキB1，B2、各ワンウエ
イクラツチOC1〜OC3の作動状況を示すと別表１
のようになる。この別表１において、〇印は作動
状態を示し、無印は解放状態を示すものである。
また、別表１におけるρ1、ρ2、ρ3は以下の如く求
められる。 The operating conditions of each clutch C 1 to C 4 , each brake B 1 , B 2 , and each one-way clutch OC 1 to OC 3 in the planetary transmission having the above configuration are shown in Attached Table 1.
become that way. In this Attached Table 1, ○ marks indicate operating states, and no marks indicate released states.
Furthermore, ρ 1 , ρ 2 , and ρ 3 in Attached Table 1 are determined as follows.
ρ1＝（第１サンギヤS1の歯数）／
（第１リングギヤR1の歯数）
ρ2＝（第２サンギヤS2の歯数）／
（第２リングギヤR2の歯数）
ρ3＝（第３サンギヤS3の歯数）／
（第３リングギヤR3の歯数）
第３図には、前記第１実施例における第１遊星
歯車機構と第２遊星歯車機構との位置を入れ替え
た第２実施例を示し、第４図には、前記第１実施
例における各クラツチや各ワンウエイクラツチの
配置や数を異ならしめた第３実施例を示す。ま
た、別表２は第３実施例における各クラツチ等の
作動状況を示すものであり、第５速における第３
クラツチC3の作動は動力伝達と無関係であり、
歯車の無用の高速回転を規制するためのものであ
る。 ρ 1 = (Number of teeth on first sun gear S 1 ) / (Number of teeth on first ring gear R 1 ) ρ 2 = (Number of teeth on second sun gear S 2 ) / (Number of teeth on second ring gear R 2 ) ρ 3 = (Number of teeth of third sun gear S 3 ) / (Number of teeth of third ring gear R 3 ) In FIG. 3, the positions of the first planetary gear mechanism and the second planetary gear mechanism in the first embodiment are swapped. FIG. 4 shows a third embodiment in which the arrangement and number of clutches and one-way clutches are different from those of the first embodiment. In addition, Attached Table 2 shows the operating status of each clutch, etc. in the third embodiment, and shows the operating status of each clutch, etc. in the third embodiment.
The operation of clutch C 3 is independent of power transmission,
This is to restrict unnecessary high-speed rotation of gears.
なお、以上の第１〜３実施例における各ワンウ
エイクラツチは各歯車の無用な逆転を規制するも
のであるが、本発明の目的を達成する上において
必ずしも必要ではなく、したがつて各ワンウエイ
クラツチが無いものであつてもよい。 Although each one-way clutch in the first to third embodiments described above is intended to prevent unnecessary reversal of each gear, it is not necessarily necessary to achieve the purpose of the present invention, and therefore each one-way clutch is It can be something that doesn't exist.
第５図には、第４実施例を示す。この第４実施
例においては、前記第１〜第３実施例において入
力軸Ｉと第１サンギヤS1との間に摩擦クラツチを
用いていたのと異なり、摩擦クラツチの替りにド
ツグクラツチＤを用いたものである。このため、
車両の前進時の回転（トルク）伝達効率を向上さ
せることができる。 FIG. 5 shows a fourth embodiment. In this fourth embodiment, unlike the first to third embodiments in which a friction clutch was used between the input shaft I and the first sun gear S1 , a dog clutch D was used instead of the friction clutch. It is something. For this reason,
It is possible to improve the rotation (torque) transmission efficiency when the vehicle moves forward.
（発明の効果）
以上説明してきたように、本発明によれば、歯
車列の変速段数を５速にして車両の連続的な速度
変化に対応したよりふさわしい変速比を得ること
ができる。(Effects of the Invention) As described above, according to the present invention, it is possible to set the number of gears of the gear train to 5 and obtain a more suitable gear ratio corresponding to continuous speed changes of the vehicle.
また、前記第２、第３実施例においては、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。 Furthermore, in the second and third embodiments, the degree of freedom in the layout of the device can be increased.
また、前記第４実施例においては、前記第３実
施例に比較して車両の前進時の回転（トルク）伝
達効率を向上させることができる。 Furthermore, in the fourth embodiment, the rotation (torque) transmission efficiency when the vehicle moves forward can be improved compared to the third embodiment.
第１図は従来の遊星歯車装置を示す概略骨組
図、第２図は本発明に係る遊星歯車装置の第１実
施例を示す概略骨組図、第３図は第２実施例を示
す概略骨組図、第４図は第３実施例を示す概略骨
組図、第５図は第４実施例を示す部分概略骨組図
である。
Ｉ……入力軸、Ｏ……出力軸、Ｈ……ケース、
S1……第１サンギヤ、S2……第２サンギヤ、S3…
…第３サンギヤ、PC1……第１キヤリヤ、PC2…
…第２キヤリヤ、PC3……第３キヤリヤ、R1……
第１リングギヤ、R2……第２リングギヤ、R3…
…第３リングギヤ、C1……第１クラツチ（第１
断続手段）、C2……第２クラツチ（第２断続手
段）、C3……第３クラツチ（第３断続手段）、C4
……第４クラツチ（第４断続手段）、B1……第１
ブレーキ（第５断続手段）、B2……第２ブレーキ
（第６断続手段）。
FIG. 1 is a schematic diagram showing a conventional planetary gear device, FIG. 2 is a schematic diagram showing a first embodiment of the planetary gear device according to the present invention, and FIG. 3 is a schematic diagram showing a second embodiment of the planetary gear device. , FIG. 4 is a schematic diagram showing the third embodiment, and FIG. 5 is a partial schematic diagram showing the fourth embodiment. I...Input shaft, O...Output shaft, H...Case,
S 1 ... 1st sun gear, S 2 ... 2nd sun gear, S 3 ...
...Third sun gear, PC 1 ...First carrier, PC 2 ...
...Second carrier, PC 3 ...Third carrier, R 1 ...
1st ring gear, R 2 ... 2nd ring gear, R 3 ...
...Third ring gear, C 1 ...First clutch (first
C 2 ... second clutch (second intermittent means), C 3 ... third clutch (third intermittent means), C 4
...Fourth clutch (fourth disconnection means), B 1 ...First
Brake (fifth intermittent means), B 2 ... second brake (sixth intermittent means).
【表】【table】
【表】【table】
Claims (1)
れ、第１サンギヤ、第１キヤリヤおよび第１リン
グギヤを有する第１遊星歯車機構と、第２サンギ
ヤ、第２キヤリヤおよび第２リングギヤを有する
第２遊星歯車機構と、第３サンギア、第３キヤリ
ヤおよび第３リングギヤを有する第３遊星歯車機
構と、を備えた遊星歯車変速装置において、前記
入力軸と第１サンギヤとを第１断続手段を介して
連結し、前記入力軸と第１キヤリヤとを第２断続
手段を介して連結し、前記入力軸と第２サンギヤ
とを一体的に連結し、前記第１リングギヤと第２
キヤリヤと第３リングギヤとを一体的に連結し、
前記第２リングギヤと第１キヤリヤとを第３断続
手段を介して連結し、前記第１キヤリヤと第３サ
ンギヤとを第４断続手段を介して連結し、前記第
３キヤリヤと出力軸とを一体的に連結し、前記ケ
ースと第１サンギヤとを第５断続手段を介して連
結し、前記ケースと第３サンギヤとを第６断続手
段を介して連結したことを特徴とする遊星歯車変
速装置。1 A first planetary gear mechanism provided in a case between an input shaft and an output shaft and having a first sun gear, a first carrier, and a first ring gear, and a second planetary gear mechanism having a second sun gear, a second carrier, and a second ring gear. In a planetary gear transmission comprising a second planetary gear mechanism and a third planetary gear mechanism having a third sun gear, a third carrier, and a third ring gear, the input shaft and the first sun gear are connected to each other through a first disconnecting means. the input shaft and the first carrier are connected via a second disconnection means, the input shaft and the second sun gear are integrally connected, and the first ring gear and the second
The carrier and the third ring gear are integrally connected,
The second ring gear and the first carrier are connected through a third disconnection means, the first carrier and the third sun gear are connected through a fourth disconnection means, and the third carrier and the output shaft are integrated. A planetary gear transmission characterized in that the case and the first sun gear are connected through a fifth disconnection means, and the case and the third sun gear are connected through a sixth disconnection means.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58196733A JPS6088249A (en) | 1983-10-20 | 1983-10-20 | Planetary gear transmission gear |
| US06/648,370 US4660439A (en) | 1983-09-08 | 1984-09-07 | Planetary gear train for automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58196733A JPS6088249A (en) | 1983-10-20 | 1983-10-20 | Planetary gear transmission gear |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6088249A JPS6088249A (en) | 1985-05-18 |
| JPH039336B2 true JPH039336B2 (en) | 1991-02-08 |
Family
ID=16362682
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP58196733A Granted JPS6088249A (en) | 1983-09-08 | 1983-10-20 | Planetary gear transmission gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6088249A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5120284A (en) * | 1989-02-03 | 1992-06-09 | Toyota Jidosha Kabushiki Kaisha | Automatic transmission |
| US5087233A (en) * | 1989-05-10 | 1992-02-11 | Toyota Jidosha Kabushiki Kaisha | Duplicate torque-transmitting connection between rotary members and shaft members in transmission |
| JPH0786381B2 (en) * | 1990-03-28 | 1995-09-20 | 本田技研工業株式会社 | Clutch separation type integrated planetary gear transmission |
| JPH0786382B2 (en) * | 1990-06-14 | 1995-09-20 | 本田技研工業株式会社 | Clutch separation type integrated planetary gear transmission |
-
1983
- 1983-10-20 JP JP58196733A patent/JPS6088249A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6088249A (en) | 1985-05-18 |
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