JP4345147B2 - Transmission - Google Patents

Description

【００１３】
尚、表１において○は係合状態を、空欄は開放状態を示している。
【００１４】
表１における変速段の切換えについて説明する。１速では、第１ブレーキＢ１によりキャリヤＰＣ１の回転を係止して入力軸１１のトルクを増大したリングギヤＲ１の出力をプラネタリギヤユニットＧ２３の第１の軸要素Ｊ１に入力し、第２ブレーキＢ２により第４の軸要素Ｊ４の回転を係止することで第３の軸要素Ｊ３が減速回転され、１速を形成する。
【００１５】
２速では、第１クラッチＣ１を連結することにより入力軸１１のトルクを増大して第１の軸要素Ｊ１に入力し、第２ブレーキＢ２により第４の軸要素Ｊ４の回転を係止することで第３の軸要素Ｊ３が減速回転され、２速を形成する。
【００１６】
３速では、第２クラッチＣ２を連結することにより入力軸１１のトルクを第２の軸要素Ｊ２に入力し、第２ブレーキＢ２により第４の軸要素Ｊ４を係止することで第３の軸要素が減速回転され、３速を形成する。
【００１７】
４速では、第２クラッチＣ２を連結することにより第２の軸要素Ｊ２に入力軸１１のトルクを入力し、第１クラッチＣ１を連結することでキャリヤＰＣ１に入力軸１１のトルクを入力することでプラネタリギヤユニットＧ２３が一体回転し、４速を形成する。
【００１８】
５速では、第２クラッチＣ２が連結することにより入力軸１１のトルクを第２の軸要素Ｊ２に入力し、第３ブレーキＢ３によりサンギヤＳ４の回転を係止することで、入力軸１１のトルクを増大したリングギヤＲ４の出力が第１の軸要素Ｊ１に入力することで、第３の軸要素Ｊ３が増速回転され、５速を形成する。
【００１９】
６速では、第２クラッチＣ２を連結することにより第２の軸要素Ｊ２に入力軸１１のトルクを入力し、第１ブレーキＢ１によりキャリヤＰＣ１の回転を係止することで入力軸１１のトルクを増大したリングギヤＲ１の出力を第１の軸要素Ｊ１に入力することで、第３の軸要素Ｊ３が増速回転され、６速を形成する。
【００２０】
後進（Ｒｅｖ）では、第１ブレーキＢ１によりキャリヤＰＣ１の回転を係止することで入力軸１１のトルクを増大したリングギヤＲ１の出力を第１の軸要素Ｊ１に入力し、第１クラッチＣ１によりキャリヤＰＣ１と第２の軸要素Ｊ２を連結することで第２の軸要素Ｊ２の回転が係止される。これによって第３の軸要素Ｊ３は入力軸１１と逆回転し、後進（Ｒｅｖ）を形成する。
【００２１】
上述したように各係合要素を切換えることで、４列のプラネタリギヤＧ１、Ｇ２、Ｇ３、Ｇ４と５つの係合要素Ｃ１、Ｃ２、Ｂ１、Ｂ２、Ｂ３を用いて１速から４速がアンダードライブ、５速と６速がオーバードライブの前進６段、後進１段の変速装置１０を構成することができる。
【００２２】
第１の実施の形態によると、４列のプラネタリギヤで５つの係合要素（クラッチ要素Ｃ１、Ｃ２、ブレーキ要素Ｂ１、Ｂ２、Ｂ３）を切換えて構成される前進６段の変速装置１０は、１速から６速までの変速段を適切なギヤ比に設定でき、また各変速段間のギヤ比ステップ（例えば２速のギヤ比に対する１速のギヤ比）が１．２３３〜１．７４３と、ギヤ比ステップのバラツキを可及的に小さくすることができ、変速を円滑に行なうことが可能になる。更に、この構成によると各プラネタリギヤのピニオン回転数が大きくなるのを抑えることができ、これによってギヤノイズを低減してギヤの耐久性を向上することができる。
【００２３】
次に、本発明の第２の実施の形態における変速装置２０について説明する。図２は第２の実施の形態における自動変速装置２０のギヤトレーンを示す概略図である。変速装置２０は、上述した第１の実施の形態の変速装置１０に対して第２、第３及び第４プラネタリギヤＧ２、Ｇ３及びＧ４の配列を入れ替えただけであり、トルクコンバータ側から第１プラネタリギヤＧ１、第２プラネタリギヤＧ２、第４プラネタリギヤＧ４、そして第３プラネタリギヤＧ３の順番にハウジング内に配列されている。このようなプラネタリギヤの配列の入れ替えは、変速装置の大きさの制約等の様々な条件により任意に行なうものである。
【００２４】
これ以外の構成、及び変速段の切換えについては第１の実施の形態の変速装置１０と同一であるので同一の符号を付し、説明を省略する。
【００２５】
以上、本発明の実施の形態について説明したが、本発明は上述した実施の形態に限定される意図はなく、本発明の主旨に沿った形態の変速装置であればどのような形態であってもよい。
【００２６】
【発明の効果】
本発明の変速装置によると、４列のプラネタリギヤで係合要素（クラッチ要素Ｃ１、Ｃ２、ブレーキ要素Ｂ１、Ｂ２、Ｂ３）を切換えて前進６段の変速装置を構成することができる。本発明では第１列のダブルピニオンプラネタリギヤを用いたことで前進変速段及び後進のギヤ比を適切なギヤ比に設定することができる。
【図面の簡単な説明】
【図１】本発明の第１の実施の形態における変速装置の概略図である。
【図２】本発明の第２の実施の形態における変速装置の概略図である。
【符号の説明】
１・・・ハウジング
２・・・トルクコンバータ
１０、２０・・・変速装置
１１・・・入力軸
１２・・・出力軸
Ｇ１・・・第１列のダブルピニオンプラネタリギヤ
Ｇ２・・・第２列のシングルピニオンプラネタリギヤ
Ｇ３・・・第３列のシングルピニオンプラネタリギヤ
Ｇ４・・・第４列のシングルピニオンプラネタリギヤ
Ｇ２３・・・プラネタリギヤユニット
Ｓ１、Ｓ２、Ｓ３、Ｓ４・・・サンギヤ
Ｒ１、Ｒ２、Ｒ３、Ｒ４・・・リングギヤ
ＰＣ１、ＰＣ２、ＰＣ３、ＰＣ４・・・キャリヤ
Ｃ１、Ｃ２・・・クラッチ要素
Ｂ１、Ｂ２、Ｂ３・・・ブレーキ要素
Ｊ１、Ｊ２、Ｊ３、Ｊ４・・・軸要素[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a transmission, for example, a transmission used in an automatic transmission of an automobile.
[0002]
[Prior art]
As a conventional transmission, there is a technique disclosed in Japanese Patent Laid-Open No. 52-149562. In this publication, three rows of planetary gears each having one ring gear, a carrier, and a sun gear are arranged in series, and have five engagement elements (two clutch elements and three brake elements) driven by external force. A transmission that can switch between six speeds and one reverse speed is disclosed.
[0003]
[Problems to be solved by the invention]
However, in the structure of the transmission disclosed in the above publication, the reverse gear ratio becomes large if an optimum gear ratio step is set. Further, when the gear ratio of the second forward speed is increased, the gear ratio of the fifth forward speed is decreased. Conversely, when the gear ratio of the second forward speed is decreased, the gear ratio of the fifth forward speed is increased, but the gear ratios of the fifth forward speed and the sixth speed are increased. There is a problem that the ratio step becomes inappropriate and the pinion rotation speed at the sixth speed increases.
[0004]
Therefore, in order to solve the above-described problems, it is a technical object of the present invention to provide a transmission having a forward six-speed gear stage that can obtain an appropriate gear ratio without increasing the number of engagement elements. .
[0005]
[Means for Solving the Problems]
In order to solve the above problems, the invention of claim 1 is directed to an input shaft, an output shaft, a first row of double pinion planetary gears in which a sun gear is connected to the input shaft, and a ring gear of a double pinion planetary gear of the first row. Connecting the sun gear of the second row single pinion planetary gear and the sun gear of the third row single pinion planetary gear, and connecting the carrier of the second row single pinion planetary gear and the ring gear of the third row single pinion planetary gear; A first shaft element connected to the ring gear of the second row single pinion planetary gear, a second shaft element connected to the ring gear of the third row single pinion planetary gear, and a carrier of the third pin single pinion planetary gear. Third axis element, third row thin A planetary gear unit having a fourth shaft element connected to the sun gear of the lupinion planetary gear and having the third shaft element connected to the output shaft, and a fourth row in which the carrier is connected to the ring gear of the single pinion planetary gear in the second row The first pinion planetary gear, the first clutch element C1 that selectively connects the carrier of the first pinion planetary gear and the second shaft element, and the input shaft and the second shaft element are selectively connected. The second clutch element C2, the first brake element B1 that selectively fixes the carrier of the first row double pinion planetary gear, and the second clutch element that selectively fixes the sun gear of the single pinion planetary gear of the third row. A third element for selectively fixing the sun gear of the brake element B2 and the fourth row single pinion planetary gear; And rake element B3,
It was set as the transmission provided with.
[0006]
According to the transmission of the first aspect, a forward six-stage transmission can be configured by switching engagement elements (clutch elements C1, C2, brake elements B1, B2, B3) with four rows of planetary gears. In the present invention, the forward gear and the reverse gear ratio can be set to appropriate gear ratios by using the first row double pinion planetary gears.
[0007]
[Embodiment]
Embodiments of the present invention will be described with reference to the drawings. In the present embodiment, a case where the present invention is used in an automatic transmission for an automobile will be described.
[0008]
FIG. 1 is a schematic diagram showing a gear train of an automatic transmission 10 according to a first embodiment of the present invention. The automatic transmission 10 is disposed in the housing 1, and the output from the torque converter 2 that outputs the output of the engine (not shown) to the transmission 10 through the shearing force of the viscous medium is moved forward 6 according to the switching of the engagement element. The speed is increased / decreased to the first speed and the reverse speed, and output to the axle (not shown).
[0009]
The transmission 10 includes an input shaft 11 that is an output shaft of the torque converter 2, an output shaft 12 that is connected to an axle via a differential device (not shown), and a first row double that connects the sun gear S 1 to the input shaft 11. A pinion planetary gear (hereinafter referred to as a first planetary gear) G1 and a sun gear S2 and a third gear of a second row single pinion planetary gear (hereinafter referred to as a second planetary gear) G2 in which the ring gear R2 is connected to the ring gear R1 of the first planetary gear G1. The sun gear S3 of the single pinion planetary gear (hereinafter referred to as the third planetary gear) G3 in the row is connected, the carrier PC2 of the second planetary gear G2 and the ring gear R3 of the third planetary gear G3 are connected, and the ring gear R2 of the second planetary gear G2 is connected. First shaft element J1, third planetar connected to The second shaft element J2 connected to the ring gear R3 of the gear G3, the third shaft element J3 connected to the carrier PC3 of the third planetary gear G3, and the fourth shaft element connected to the sun gear S3 of the third planetary gear G3. A planetary gear unit G23 having J4 and a third shaft element J3 connected to the output shaft 12, and a fourth row single pinion planetary gear (hereinafter referred to as a fourth planetary gear) in which the carrier PC4 is connected to the ring gear R2 of the second planetary gear G2. G4, the first clutch element C1 that selectively connects the carrier PC1 of the first planetary gear G1 and the second shaft element J2, and the input shaft 11 and the second shaft element J2 are selectively connected. The first clutch element C2 for selectively fixing the second clutch element C2 and the carrier PC1 of the first planetary gear G1. When provided with a second brake element B2 which selectively fixes the sun gear S3 of the third planetary gear G3, the third brake element B3 for selectively fixing sun gear S4 of the fourth planetary gear G4, the.
[0010]
In the first planetary gear G1, ρ1 = number of teeth of the sun gear S1 / number of teeth of the ring gear R1 = 0.45, and in the second planetary gear G2, ρ2 = number of teeth of the sun gear S2 / number of teeth of the ring gear R2 = 0.29, third In planetary gear G3, ρ3 = number of teeth of sun gear S3 / number of teeth of ring gear R3 = 0.40, and in fourth planetary gear G4, ρ4 = number of teeth of sun gear S4 / number of teeth of ring gear R4 = 0.34.
[0011]
Table 1 shows combinations and gear ratios of the engagement elements in the first embodiment.
[0012]
[Table 1]

[0013]
In Table 1, ◯ indicates the engaged state, and the blank indicates the released state.
[0014]
The shifting of the gear position in Table 1 will be described. In the first speed, the output of the ring gear R1, which has increased the torque of the input shaft 11 by locking the rotation of the carrier PC1 by the first brake B1, is input to the first shaft element J1 of the planetary gear unit G23, and the second brake B2 By locking the rotation of the fourth shaft element J4, the third shaft element J3 is decelerated and rotated to form the first speed.
[0015]
In the second speed, the torque of the input shaft 11 is increased by connecting the first clutch C1 and input to the first shaft element J1, and the rotation of the fourth shaft element J4 is locked by the second brake B2. Thus, the third shaft element J3 is decelerated and rotated to form the second speed.
[0016]
In the third speed, the torque of the input shaft 11 is input to the second shaft element J2 by connecting the second clutch C2, and the third shaft is locked by locking the fourth shaft element J4 by the second brake B2. The element is rotated at a reduced speed to form the third speed.
[0017]
In the fourth speed, the torque of the input shaft 11 is input to the second shaft element J2 by connecting the second clutch C2, and the torque of the input shaft 11 is input to the carrier PC1 by connecting the first clutch C1. Thus, the planetary gear unit G23 rotates integrally to form the fourth speed.
[0018]
In the fifth speed, the torque of the input shaft 11 is input by inputting the torque of the input shaft 11 to the second shaft element J2 when the second clutch C2 is connected, and the rotation of the sun gear S4 is locked by the third brake B3. When the output of the ring gear R4 having increased is input to the first shaft element J1, the third shaft element J3 is rotated at an increased speed to form the fifth speed.
[0019]
In the sixth speed, the torque of the input shaft 11 is input to the second shaft element J2 by connecting the second clutch C2, and the torque of the input shaft 11 is stopped by locking the rotation of the carrier PC1 by the first brake B1. By inputting the increased output of the ring gear R1 to the first shaft element J1, the third shaft element J3 is rotated at an increased speed to form the sixth speed.
[0020]
In reverse (Rev), the output of the ring gear R1 in which the torque of the input shaft 11 is increased by locking the rotation of the carrier PC1 by the first brake B1 is input to the first shaft element J1, and the carrier is driven by the first clutch C1. The rotation of the second shaft element J2 is locked by connecting the PC1 and the second shaft element J2. As a result, the third shaft element J3 rotates backward with respect to the input shaft 11 and forms reverse (Rev).
[0021]
By switching each engagement element as described above, the first to fourth speeds are underdriven using four rows of planetary gears G1, G2, G3, G4 and five engagement elements C1, C2, B1, B2, B3. The fifth gear and the sixth gear can constitute a transmission device 10 with overdrive 6 forward speeds and 1 reverse speed.
[0022]
According to the first embodiment, a forward six-stage transmission 10 configured by switching five engagement elements (clutch elements C1, C2, brake elements B1, B2, B3) with four rows of planetary gears is: The gear stages from the first speed to the sixth speed can be set to an appropriate gear ratio, and the gear ratio step between each gear stage (for example, the first gear ratio to the second gear ratio) is 1.233 to 1.743, The variation in the gear ratio step can be made as small as possible, and the gear shifting can be performed smoothly. Furthermore, according to this configuration, it is possible to suppress an increase in the pinion rotation speed of each planetary gear, thereby reducing gear noise and improving gear durability.
[0023]
Next, the transmission 20 in the second embodiment of the present invention will be described. FIG. 2 is a schematic diagram showing a gear train of the automatic transmission 20 according to the second embodiment. The transmission 20 is merely the replacement of the arrangement of the second, third, and fourth planetary gears G2, G3, and G4 with respect to the transmission 10 of the first embodiment described above, and the first planetary gear from the torque converter side. G1, the second planetary gear G2, the fourth planetary gear G4, and the third planetary gear G3 are arranged in the housing in this order. Such replacement of the planetary gear arrangement is arbitrarily performed in accordance with various conditions such as a restriction on the size of the transmission.
[0024]
Since the configuration other than this and the shift speed switching are the same as those of the transmission 10 according to the first embodiment, the same reference numerals are given and the description thereof is omitted.
[0025]
The embodiment of the present invention has been described above. However, the present invention is not intended to be limited to the above-described embodiment, and any configuration is possible as long as the transmission is in the form consistent with the gist of the present invention. Also good.
[0026]
【The invention's effect】
According to the transmission of the present invention, a forward six-stage transmission can be configured by switching engagement elements (clutch elements C1, C2, brake elements B1, B2, B3) with four rows of planetary gears. In the present invention, the forward gear and the reverse gear ratio can be set to appropriate gear ratios by using the first row double pinion planetary gears.
[Brief description of the drawings]
FIG. 1 is a schematic diagram of a transmission according to a first embodiment of the present invention.
FIG. 2 is a schematic view of a transmission in a second embodiment of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Housing 2 ... Torque converter 10, 20 ... Transmission 11 ... Input shaft 12 ... Output shaft G1 ... Double pinion planetary gear G2 of 1st row ... Single pinion planetary gear G3... Third row single pinion planetary gear G4... Fourth row single pinion planetary gear G23... Planetary gear units S1, S2, S3, S4... Sun gears R1, R2, R3, R4. ..Ring gears PC1, PC2, PC3, PC4 ... carriers C1, C2 ... clutch elements B1, B2, B3 ... brake elements J1, J2, J3, J4 ... shaft elements

Claims (1)

An input shaft;
An output shaft;
A first row double pinion planetary gear in which a sun gear is connected to the input shaft; a sun gear in a second row single pinion planetary gear in which a ring gear is connected to a ring gear in the first row double pinion planetary gear; and a third pin in a single pinion planetary gear. A first shaft element coupled to the sun gear, coupled to the carrier of the second row single pinion planetary gear and the ring gear of the third row single pinion planetary gear, and coupled to the ring gear of the second row single pinion planetary gear; A second shaft element connected to the ring gear of the third row single pinion planetary gear, a third shaft element connected to the carrier of the third row single pinion planetary gear, and a sun gear of the third row single pinion planetary gear. 4th And the planetary gear unit the and the third shaft element comprises an element coupled to said output shaft,
A fourth row of single pinion planetary gears in which a carrier is coupled to a ring gear of the second row of single pinion planetary gears;
A first clutch element C1 that selectively couples the carrier of the first row double pinion planetary gear and the second shaft element;
A second clutch element C2 that selectively connects the input shaft and the second shaft element;
A first brake element B1 for selectively fixing the carrier of the first row double pinion planetary gear;
A second brake element B2 for selectively fixing a sun gear of the third row single pinion planetary gear;
A third brake element B3 that selectively fixes a sun gear of the fourth row single pinion planetary gear;
A transmission comprising:

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