JPS5933778B2

JPS5933778B2 - Planetary gear transmission

Info

Publication number: JPS5933778B2
Application number: JP52035105A
Authority: JP
Inventors: 隆宏山森
Original assignee: Nissan Motor Co Ltd
Current assignee: Nissan Motor Co Ltd
Priority date: 1977-03-29
Filing date: 1977-03-29
Publication date: 1984-08-17
Also published as: JPS53120045A

Description

【発明の詳細な説明】本発明は、トルクコンバータあるいは流体継手等と組合
わせて使用される自動車用の自動変速装置であって、特
に３組の遊星歯車組を組合せた前進４段、後進１段以上
の遊星歯車式変速装置の改良に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention is an automatic transmission for automobiles that is used in combination with a torque converter or a fluid coupling, etc., and in particular has four forward speeds and one reverse speed that combine three sets of planetary gears. This invention relates to an improvement of a planetary gear type transmission with more than one gear.

一般に従来から、前進４段の遊星歯車式変速装置は、数
多く開発されているが、この種の変速装置においては、
各変速段のギヤ比の間隔が相互に関係を持って決まるた
め、ギヤ比の選択にはあまり自由度が無く、従っである
種の車両には適したギヤ比でも他の種の車両に対しては
適さないという不都合を生じた。In general, many planetary gear type transmissions with four forward speeds have been developed, but in this type of transmission,
Since the interval between the gear ratios of each gear is determined in relation to each other, there is not much freedom in selecting the gear ratio. This resulted in the inconvenience that it was not suitable.

本発明は前記の点に鑑みなされたもので、特に内燃機関
付自動車に適したギヤ比が得られる遊星歯車式変速装置
を提供することを目的とする。The present invention has been made in view of the above points, and an object of the present invention is to provide a planetary gear type transmission that provides a gear ratio particularly suitable for an internal combustion engine vehicle.

以下図面に基づいて本発明の実施例を詳細に説明する。Embodiments of the present invention will be described in detail below based on the drawings.

図中１は入力軸で、通常トルクコンバータ又は流体継手
等の流体伝動装置のタービン翼車に結合されており、２
は出力軸である。In the figure, 1 is an input shaft, which is usually connected to a turbine wheel of a fluid transmission device such as a torque converter or a fluid coupling, and 2
is the output shaft.

第１の遊星歯車組Ａはいわゆる単純遊星歯車組であり、
３はそのサンギヤ、４はサンギ゛ヤ３と同心に回転する
りングギャである。The first planetary gear set A is a so-called simple planetary gear set,
3 is its sun gear, and 4 is a ring gear that rotates concentrically with the sun gear 3.

更に５はサンギヤ３およびリングギヤ４に噛合して回転
するピニオン、６はピニオン５を軸支するキャリアで、
中間伝達軸１０を介して出力軸２に結合している。Further, 5 is a pinion that rotates in mesh with the sun gear 3 and ring gear 4, 6 is a carrier that pivotally supports the pinion 5,
It is coupled to the output shaft 2 via an intermediate transmission shaft 10.

第２の遊星歯車組Ｂは第１の遊星歯車組Ａと同じく単純
遊星歯車組であり、７はそのサンギヤで、第１の遊星歯
車組Ａのサンギヤ３と中間メンバー８で結合されている
。The second planetary gear set B is a simple planetary gear set like the first planetary gear set A, and its sun gear 7 is connected to the sun gear 3 of the first planetary gear set A by an intermediate member 8.

９はサンギヤ７と同心に回転するリングギヤで中間メン
バー１１を介して出力軸２と結合した中間伝達軸１０に
結合し、１２はサンギヤ７およびリングギヤ９に噛合し
て回転するピニオン、１３はピニオン１２を軸支するキ
ャリアである。9 is a ring gear that rotates concentrically with the sun gear 7 and is connected to an intermediate transmission shaft 10 that is connected to the output shaft 2 via an intermediate member 11; 12 is a pinion that rotates in mesh with the sun gear 7 and the ring gear 9; and 13 is a pinion 12. It is a carrier that supports the

第３の遊星歯車組Ｃはサンギヤとリングギヤの間に二種
のピニオンを有するいわゆる複合遊星歯車組である。The third planetary gear set C is a so-called composite planetary gear set having two types of pinions between the sun gear and the ring gear.

１４はそのサンギヤで、第２の遊星歯車組Ｂのキャリア
１３と中間メンバー１５を介して結合されている。The sun gear 14 is connected to the carrier 13 of the second planetary gear set B via an intermediate member 15.

１６は前記サンギヤ１４と同心に回転するりングギャで
あり、１７はリングギヤ１６に噛合する第１のピニオン
、１８は第１のピニオン１７およびサンギヤ１４に噛合
した第２のピニオンであり、１９は第１のピニオン１７
および第２のピニオン１８を軸支するキャリアであり、
出力軸２に結合されている。16 is a ring gear that rotates concentrically with the sun gear 14; 17 is a first pinion that meshes with the ring gear 16; 18 is a second pinion that meshes with the first pinion 17 and the sun gear 14; 19 is a second pinion that meshes with the first pinion 17 and the sun gear 14; 1 pinion 17
and a carrier that pivotally supports the second pinion 18,
It is coupled to the output shaft 2.

以上の３組の遊星歯車組Ａ、ＢおよびＣは同心上に配置
されている。The above three planetary gear sets A, B and C are arranged concentrically.

２０で示す第１のクラッチは入力軸１と中間メンバー８
との間に配置し、両者を断接できるようにしている。A first clutch, designated 20, connects the input shaft 1 and the intermediate member 8.
It is placed between the two so that the two can be connected and disconnected.

２１は第２のクラッチで、入力軸１と第１の遊星歯車組
Ａのリングギヤ４との間に配置し、両者を断接できるよ
うにしている。A second clutch 21 is disposed between the input shaft 1 and the ring gear 4 of the first planetary gear set A, and is configured to connect and disconnect the two.

２２は第１のブレーキで、中間メンバー８を介して第１
の遊星歯車組Ａのサンギヤ３および第２の遊星歯車組Ｂ
のサンギヤ７を制動できるように構成されており、２３
は第２のブレーキで、中間メンバー１５を介して第２の
遊星歯車組Ｂのキャリア１３および第３の遊星歯車組Ｃ
のサンギヤ１４を制動できるように構成されており、２
４は第３のブレーキで第３の遊星歯車組Ｃのリングギヤ
１６を制動できるよう構成されている。22 is a first brake, which is connected to the first brake via an intermediate member 8
Sun gear 3 of planetary gear set A and second planetary gear set B
It is configured so that it can brake the sun gear 7 of 23
is a second brake, which is connected to the carrier 13 of the second planetary gear set B and the third planetary gear set C via the intermediate member 15.
It is configured to be able to brake the sun gear 14 of 2.
A third brake 4 is configured to brake the ring gear 16 of the third planetary gear set C.

この遊星歯車変速装置の各変速は各クラッチ、ブレーキ
を次のように選択することにより行なう。Each shift of this planetary gear transmission is performed by selecting each clutch and brake as follows.

前進〔第１速〕第２のクラッチ２１および第３のブレーキ２４を締結す
る。Forward [first speed] Second clutch 21 and third brake 24 are engaged.

〔第２速〕第２のクラッチ２１および第２のブレーキ２３を締結す
る。[Second speed] The second clutch 21 and second brake 23 are engaged.

〔第３速〕第２のクラッチ２１および第１のブレーキ２２を締結す
る。[Third speed] The second clutch 21 and first brake 22 are engaged.

〔第４速〕第１のクラッチ２０および第２のクラッチ２する締結す
る。[Fourth speed] First clutch 20 and second clutch 2 are engaged.

後進〔第２速〕第１のクラッチ２０および第２のブレーキ２３を締結す
る。Reverse [2nd speed] The first clutch 20 and second brake 23 are engaged.

後進〔第１速〕第１のクラッチ２０および第３のブレーキ２４を締結す
る。Reverse [first speed] First clutch 20 and third brake 24 are engaged.

そして各遊星歯車組Ａ、、Ｂ、Ｃにおいては次
の式が成立する。The following equation holds true for each planetary gear set A, B, C.

第１，２の遊星歯車組Ａ、ＨについてＮＲＩ＋αｌＮＳ２−（１＋α１）ＮＯ＋ＮＲＺ＋α２
ＮＳ２−（１＋α２）ＮＯ２第３の遊星歯車組Ｃに
ついてＮＲ３−α５Ｎｓｓ−（１−α３）ＮＣ３ただし、Ｉ’ＪＲ，＋ｔＮＲ２、ＮＲ３・・・各遊星歯車組
Ａ、Ｂ、Ｃのリングギヤの回転数。Regarding the first and second planetary gear sets A and H, NRI+αlNS2-(1+α1)NO+NRZ+α2
NS2-(1+α2) NO2 Regarding the third planetary gear set C NR3-α5 Nss-(1-α3) NC3 However, I'JR, + t NR2, NR3...For the ring gear of each planetary gear set A, B, and C. Number of revolutions.

Ｎｓｌ、Ｎｓ２．Ｎｓ３・・・各遊星歯車組Ａ、Ｂ、Ｃ
のサンギヤの回転数。Nsl, Ns2. Ns3...Each planetary gear set A, B, C
Sun gear rotation speed.

１’ＪｃｔｔＮ０２ｔＮＣ３”’各遊星歯車組
Ａ、Ｂ、、Ｃのキャリアの回転数。1'Jct t N02 t NC3'''The rotation speed of the carrier of each planetary gear set A, B, C.

α１．α２．α３・・・各遊星歯車組Ａ、Ｂ、Ｃのリン
グギヤに対するサンギヤの歯数比。α1. α2. α3: Ratio of the number of teeth of the sun gear to the ring gear of each planetary gear set A, B, and C.

ここで各変速段における減速比をまとめると次表のよう
になり、具体例としてα□−〇、３５、α２−Ｏ，４０
、α３＝０．５０とすると表のような値を得ることがで
きる。Here, the reduction ratios at each gear stage are summarized as shown in the following table. Specific examples include α□-〇, 35, α2-O, 40
, α3=0.50, the values shown in the table can be obtained.

なお、この表中○印は各クラッチ、ブレーキが締結する
箇所を示す。Note that the ○ marks in this table indicate the locations where each clutch and brake are engaged.

かくして、本発明の遊星歯車式変速装置によれ°ば上述
した処から明らかなように、あらゆる自動車に適したギ
ヤ比を得ることができ、又後進の変速比を得るに際して
も、第１のクラッチ２０および第２のブレーキ２３を作
動させるか、第１のクラッチ２０および第３のブレーキ
２４を作動させる２つの方法があり、車輛に応じた後進
用変速比を得ることができる。Thus, according to the planetary gear type transmission of the present invention, as is clear from the above, a gear ratio suitable for all types of automobiles can be obtained, and even when obtaining a reverse gear ratio, the first clutch There are two methods: operating the clutch 20 and the second brake 23, or operating the first clutch 20 and the third brake 24, and it is possible to obtain a reverse gear ratio depending on the vehicle.

[Brief explanation of the drawing]

図面は本発明遊星歯車式変速装置の骨子図である。１・・・・・・入力軸、２・・・・・・出力軸、Ａ・・
・・・・第１の遊星歯車組、Ｂ・・・・・・第２の遊星
歯車組、Ｃ・・・・・・第３の遊星歯車組、３，７．１
４・・・・・・サンギヤ、４゜９．１６・・・・・・リ
ングギヤ、５，１２，１７，１８・・・・・・ピニオン
、６，１３，１９・・・・・・キャリア、８゜１１１５
・・・・・・中間メンバー、１０・・・・・・中間伝達
軸、２０・・・・・・第１のクラッチ、２１・・・・・
・第２のクラッチ、２２・・・・・・第１のブレーキ、
２３・・・・・・第２のブレーキ、２４・・・・・・第
３のブレーキ。The drawing is a schematic diagram of the planetary gear type transmission according to the present invention. 1...Input shaft, 2...Output shaft, A...
...First planetary gear set, B...Second planetary gear set, C...Third planetary gear set, 3,7.1
4... Sun gear, 4゜9.16... Ring gear, 5, 12, 17, 18... Pinion, 6, 13, 19... Carrier, 8°1115
......Intermediate member, 10...Intermediate transmission shaft, 20...First clutch, 21...
・Second clutch, 22...First brake,
23...Second brake, 24...Third brake.

Claims

[Claims] 1. It has a human power shaft, an output shaft, and three planetary gear sets arranged concentrically, and the first planetary gear set and the second planetary gear set mesh with the sun gear, the ring gear, and both gears. The third planetary gear set consists of three types of rotating elements: a carrier that pivotally supports a pinion that rotates; The sun gear of the first planetary gear set and the sun gear of the second planetary gear set are coupled, and both sun gears can be coupled to the input shaft via the first clutch. The ring gear of the first planetary gear set can be coupled to the input shaft via the second clutch, the carrier of the first planetary gear set is coupled to the output shaft, and the ring gear of the first planetary gear set is coupled to the output shaft, The ring gear of the second planetary gear set is coupled to the output shaft, the carrier of the second planetary gear set is coupled to the sun gear of the third planetary gear set, and can be braked by a second brake, and the carrier of the third planetary gear set is output. A planetary gear type transmission device, characterized in that the ring gear of a third planetary gear set can be braked by a third brake coupled to a shaft. 2 Activate the second clutch and third brake to
speed, actuate the second clutch and the second brake to
speed, actuate the second clutch and the first brake to move the third
speed, actuate the first clutch and the second clutch to activate the fourth clutch.
2. The planetary gear type transmission according to claim 1, wherein speed and reverse can be selected by operating the first clutch and the second brake. 3 Activate the second clutch and third brake to
speed, actuate the second clutch and the second brake to
speed, actuate the second clutch and the first brake to move the third
speed, actuate the first clutch and the second clutch to activate the fourth clutch.
2. The planetary gear type transmission according to claim 1, wherein the planetary gear type transmission device can select speed, reverse movement by operating the first clutch, and third brake.