KR101483636B1 - Power train of automatic transmission - Google Patents

Abstract

A first planetary gear set including a first operating member selectively connected to the transmission case, a second operating member fixedly connected to the input shaft, and a third operating member; A second planetary gear set including a fourth actuating member fixedly connected to the third actuating member, a fifth actuating member selectively connected to the input shaft, and a sixth actuating member fixedly connected to the output shaft; A seventh actuating member fixedly connected to the fourth actuating member and selectively connected to the sixth actuating member, an eighth actuating member selectively connected to the sixth actuating member and selectively connected to the first actuating member, A third planetary gear set including a ninth operating member fixedly connected to the transmission case; And a plurality of friction members selectively connecting the operation members of the first, second, and third planetary gear sets, the input shaft, the output shaft, and the transmission case. .

Automatic transmission, power train, planetary gear set

Description

POWER TRAIN OF AUTOMATIC TRANSMISSION < RTI ID = 0.0 >

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a powertrain of an automatic transmission, and more particularly, to a powertrain of an automatic transmission implementing three forward speeds and one reverse speed using three simple planetary gear sets and six friction elements.

The multi-speed shifting mechanism of the automatic transmission is usually implemented by a combination of a plurality of planetary gear sets. A powertrain in which a plurality of planetary gear sets are combined is used to receive torque from a torque converter included in the automatic transmission, To the output shaft.

However, the more transmission speeds that can be implemented in the transmission, the more appropriate transmission ratio can be designed, and a vehicle having superior power performance and fuel economy can be realized. Therefore, have.

In addition, even if the same number of gear stages are implemented, the durability, power transmission efficiency, and size of the power train are changed according to the combination of the planetary gear sets, thereby making it more robust, Efforts are constantly being made.

In particular, unlike the manual transmission in which the driver incurs an inconvenience that the shift must be frequently performed if the speed change stage is excessively large, the automatic transmission performs shifting by controlling the operation of the power train in accordance with the operation state, Efforts to find the configuration of a powertrain that implements a stage have even more value in an automatic transmission.

SUMMARY OF THE INVENTION Accordingly, the present invention has been made to solve the above-mentioned problems associated with the development of an automatic transmission, and it is an object of the present invention to provide a planetary gear set having three forward planetary gear sets and six friction elements, Thereby providing a powertrain of the automatic transmission.

To achieve these and other advantages and in accordance with the purpose of the present invention, as embodied and broadly described, a powertrain of an automatic transmission includes a first operating member selectively connected to a transmission case, a second operating member fixedly connected to the input shaft, A first planetary gear set; A fourth actuating member fixedly connected to the third actuating member, a fifth actuating member selectively connected to the input shaft, and a sixth actuating member fixedly connected to the output shaft; A seventh actuating member fixedly connected to the fourth actuating member and selectively connected to the sixth actuating member, an eighth actuating member selectively connected to the sixth actuating member and selectively connected to the first actuating member, A third planetary gear set including a ninth operating member fixedly connected to the transmission case; And a plurality of friction members for selectively connecting the operation members of the first, second, and third planetary gear sets, the input shaft, the output shaft, and the transmission case.

The plurality of friction members include: a first clutch that selectively connects the fifth operating member to the input shaft; A second clutch for integrally operating the second planetary gear set; A third clutch selectively connecting the sixth actuating member to the eighth actuating member; A fourth clutch for selectively connecting the first operating member to the eighth operating member; A first brake for selectively stopping the first actuating member; And a second brake for selectively stopping the fifth actuating member.

According to the embodiment, the first planetary gear set is a single pinion planetary gear set including a first sun gear, a first planet carrier, and a first ring gear as its operating members, the first sun gear being a first sun gear, The first planetary carrier acts as a second actuating member, and the first ring gear acts as a third actuating member.

According to the embodiment, the first planetary gear set is a double pinion planetary gear set including a first sun gear, a first ring gear, and a first planetary carrier as operating members thereof, and the first sun gear is a first sun gear, The first ring gear acts as a second actuating member, and the first planetary carrier acts as a third actuating member.

According to the embodiment, the second planetary gear set is a single pinion planetary gear set including a second sun gear, a second planetary carrier, and a second ring gear as operating members thereof, and the second sun gear is a fourth sun gear, The second planetary carrier acts as a fifth actuating member, and the second ring gear acts as a sixth actuating member.

According to the embodiment, the second planetary gear set is a double pinion planetary gear set including a second sun gear, a second ring gear, and a second planetary carrier as operating members thereof, and the second sun gear is a fourth sun gear, The second ring gear acts as a fifth operating member, and the second planetary carrier acts as a sixth operating member.

Wherein the third planetary gear set is a single pinion planetary gear set including a third sun gear, a third planetary carrier, and a third ring gear as its operating members, the third sun gear acting as a seventh operating member, The third planetary carrier acts as the eighth operating member, and the third ring gear acts as the ninth operating member.

The third clutch and the fourth clutch are operated in forward speed 1, the third clutch and the first brake are operated in forward speed 2, the first clutch and the third clutch are operated in forward speed 3, The first clutch and the fourth clutch operate in the fifth forward speed, the first clutch and the second clutch operate in the forward sixth speed, the second clutch and the fourth clutch operate in the forward seventh speed, The second clutch and the first brake are operated, and in the reverse first speed, the fourth clutch and the second brake are operated.

And the second clutch selectively connects the third operating member and the sixth operating member.

And the second clutch may selectively connect the fifth operating member and the sixth operating member.

And the second clutch selectively connects the third operating member and the fifth operating member.

Wherein the first planetary gear set is a double pinion planetary gear set and the second planetary gear set is a single pinion planetary gear set and the third planetary gear set is a single pinion planetary gear set, 2) a first clutch selectively connecting the planetary carrier to the input shaft; A second clutch that selectively connects two operation members of the second planetary gear set; A third clutch selectively connecting the second ring gear and the third planetary carrier; A fourth clutch selectively connecting the first sun gear and the third planetary carrier; A first brake selectively connecting the first sun gear to the transmission case; And a second brake selectively connecting the second planetary carrier to the transmission case.

Wherein the first planetary gear set is a single pinion planetary gear set and the second planetary gear set is a single pinion planetary gear set and the third planetary gear set is a single pinion planetary gear set, 2) a first clutch selectively connecting the planetary carrier to the input shaft; A second clutch that selectively connects two operation members of the second planetary gear set; A third clutch selectively connecting the second ring gear and the third planetary carrier; A fourth clutch selectively connecting the first sun gear and the third planetary carrier; A first brake selectively connecting the first sun gear to the transmission case; And a second brake selectively connecting the second planetary carrier to the transmission case.

Wherein the first planetary gear set is a single pinion planetary gear set and the second planetary gear set is a single pinion planetary gear set and the third planetary gear set is a single pinion planetary gear set, 2) a first clutch selectively connecting the planetary carrier to the input shaft; A second clutch for selectively connecting the second planetary carrier or the second ring gear to the first ring gear; A third clutch selectively connecting the second ring gear and the third planetary carrier; A fourth clutch selectively connecting the first sun gear and the third planetary carrier; A first brake selectively connecting the first sun gear to the transmission case; And a second brake selectively connecting the second planetary carrier to the transmission case.

Wherein the first planetary gear set is a double pinion planetary gear set and the second planetary gear set is a double pinion planetary gear set and the third planetary gear set is a single pinion planetary gear set, A first clutch selectively connecting the two-ring gear to the input shaft; A second clutch that selectively connects two operation members of the second planetary gear set; A third clutch selectively connecting the second planetary carrier and the third planetary carrier; A fourth clutch selectively connecting the first sun gear and the third planetary carrier; A first brake selectively connecting the first sun gear to the transmission case; A second brake selectively connecting the second ring gear to the transmission case; As shown in FIG.

Wherein the first planetary gear set is a single pinion planetary gear set and the second planetary gear set is a double pinion planetary gear set and the third planetary gear set is a single pinion planetary gear set, A first clutch selectively connecting the two-ring gear to the input shaft; A second clutch that selectively connects two operation members of the second planetary gear set; A third clutch selectively connecting the second planetary carrier and the third planetary carrier; A fourth clutch selectively connecting the first sun gear and the third planetary carrier; A first brake selectively connecting the first sun gear to the transmission case; And a second brake selectively connecting the second ring gear to the transmission case.

Wherein the first planetary gear set is a single pinion planetary gear set and the second planetary gear set is a double pinion planetary gear set and the third planetary gear set is a single pinion planetary gear set, A first clutch selectively connecting the two-ring gear to the input shaft; A second clutch for selectively connecting the second planetary carrier or the second ring gear to the first ring gear; A third clutch selectively connecting the second planetary carrier and the third planetary carrier; A fourth clutch selectively connecting the first sun gear and the third planetary carrier; A first brake selectively connecting the first sun gear to the transmission case; And a second brake selectively connecting the second ring gear to the transmission case.

As described above, according to the powertrain of the automatic transmission according to the present invention, three forward planetary gear sets and six clutches can be used to implement forward forward speed and reverse reverse speed.

In addition, since the engine is provided with a large number of gear stages, the power of the engine can be effectively utilized to improve the power transmission performance and reduce the fuel consumption.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

1, the powertrain of the automatic transmission according to the embodiment of the present invention includes an input shaft 10, an output shaft 20, a transmission case 30, and first, second and third planetary gear sets PG1, PG2, PG3).

The input shaft 100 receives the power of an engine (not shown) through a torque converter (not shown).

The output shaft 20 outputs power from the power train.

The first planetary gear set PG1 is a double pinion planetary gear set including a first sun gear S1, a first ring gear R1 and a first planetary carrier PC1 as operating members thereof. The first planetary carrier PC1 is connected to the first sun gear S1 and the first pinion gear P1 that is gear-coupled to the first ring gear R1.

The second planetary gear set PG2 is a single pinion planetary gear set including the second sun gear S2, the second planetary carrier PC2, and the second ring gear R2 as operating members thereof. The second planetary carrier PC2 is connected to the second pinion gear P2 that is gear-coupled to the second sun gear S2 and the second ring gear R2.

The third planetary gear set PG3 is a single pinion planetary gear set including the third sun gear S3, the third planetary carrier PC3, and the third ring gear R3 as operating members thereof. The third planetary carrier PC3 is connected to the third sun gear S3 and the third pinion gear P3 which is gear-coupled to the third ring gear R3.

The first sun gear S1, the first ring gear R1 and the first planetary carrier PC1 are connected to the first, second and third actuating members N1 (first and second) of the powertrain of the automatic transmission according to the embodiment of the present invention, , N2, N3), respectively. The second sun gear S2, the second planetary carrier PC2 and the second ring gear R2 are connected to the fourth, fifth and sixth operating members N4 (N4, N6) of the powertrain of the automatic transmission according to the embodiment of the present invention, , N5, and N6, respectively. The third sun gear S3, the third planetary carrier PC3 and the third ring gear R3 are connected to the seventh, eighth and ninth operating members N7 of the powertrain of the automatic transmission according to the embodiment of the present invention, , N8, N9), respectively.

The first ring gear R1 is fixedly connected to the input shaft 10 and functions as an input member at all times. The first planetary carrier PC1 is fixedly connected to the second sun gear S2. The second sun gear S2 is fixedly connected to the third sun gear S3. The second ring gear R2 is fixedly connected to the output shaft 20 and serves as an output member at all times. The third ring gear R3 is fixedly connected to the transmission case 30 and functions as a stop member at all times.

The powertrain of the automatic transmission according to the embodiment of the present invention uses six friction members.

The plurality of friction members include a first clutch C1 selectively connecting the second planetary carrier PC2 to the input shaft 10; A second clutch C2 selectively connecting the two operating members S2 and R2 of the second planetary gear set PG2; A third clutch C3 selectively connecting the second ring gear R2 and the third planetary carrier PC3; A fourth clutch C4 selectively connecting the first sun gear S1 and the third planetary carrier PC3; A first brake B1 selectively connecting the first sun gear S1 to the transmission case 30; And a second brake B2 for selectively connecting the second planetary carrier PC2 to the transmission case 30. [

In the present embodiment, the second clutch C2 selectively connects the second sun gear S2 and the second ring gear R2. However, the scope of protection of the present invention should not be construed as being limited thereto. Other connection relationships of the second clutch C2 for operating the second planetary gear set PG2 as a whole are possible, and this will be described later as a separate embodiment.

In this embodiment, the first planetary gear set PG1 is a double pinion planetary gear set and the second planetary gear set PG2 is a single pinion planetary gear set. However, the scope of protection of the present invention should not be construed as being limited thereto. The first planetary gear set PG1 can be deformed into a single-pinion planetary gear set and the second planetary gear set PG2 can be modified into a double pinion planetary gear set. This modification will be described later as a separate embodiment.

In the present embodiment, the first brake B1 selectively connects the first sun gear S1 to the transmission case 30, but the protection range of the present invention should not be construed as being limited thereto. The first brake B1 may connect the first sun gear S1 to the third ring gear R3 fixed to the transmission case 30. [

As shown in FIG. 2, the automatic transmission according to the embodiment of the present invention implements a first forward speed and a reverse reverse speed, and two friction members are operated at each speed change stage.

That is, in the forward first speed (D1), the third clutch C3 and the fourth clutch C4 operate. In the forward second speed (D2), the third clutch C3 and the first brake B1 operate. In the forward third speed (D3), the first clutch C1 and the third clutch C3 operate. In the forward fourth speed (D4), the first clutch C1 and the first brake B1 operate. In the forward fifth speed (D5), the first clutch C1 and the fourth clutch C4 operate. In the forward sixth speed (D6), the first clutch C1 and the second clutch C2 operate. In the forward seventh speed (D7), the second clutch C2 and the fourth clutch C4 operate. In the forward 8th gear (D8), the second clutch C2 and the first brake B1 operate. In the reverse first speed R1, the fourth clutch C4 and the second brake B2 operate.

Hereinafter, the formation of the forward 8-speed and the reverse 1-speed in the power train of the automatic transmission according to the embodiment of the present invention will be described in detail.

3 to 11, the first ring gear R1, which always functions as an input member, always rotates at the rotational speed of the input shaft 10. [ Since the first planetary carrier PC1, the second sun gear S2, and the third sun gear S3 are fixedly connected to each other, they always rotate at the same speed. Since the third ring gear R3 is fixedly connected to the transmission case 30, the third ring gear R3 is always stopped.

In this state, forward first to eighth speed and reverse first speed are realized by selective operation of the first clutch C1 to the fourth clutch C4 and the first and second brakes B1 and B2, Will be described in detail.

[Advancing first gen]

In the forward first speed (D1), the third clutch C3 and the fourth clutch C4 operate.

Since the third clutch C3 is operated, the second ring gear R1 and the third planetary carrier PC3 are rotated at the same speed and the fourth clutch C1 is operated, so that the first sun gear S1 and the third sun gear S3 PC3 ) Rotate at the same speed. That is, the first ring gear R1, the second sun gear S2, and the third planetary carrier PC3 all rotate at the same speed.

The first planetary gear set PG1 and the third planetary gear set PG1 are rotated by the condition that these conditions and the first planetary carrier PC1, the second sun gear S2 and the third sun gear S3 rotate at the same speed PG3 are formed as shown in Fig.

Therefore, the second ring gear R2 as the output member rotates at the same speed as the third planetary carrier PC3, and the forward first speed D1 is output.

[Advancing second gen]

In the forward second speed (D2), the third clutch C3 and the first brake B1 operate.

The first sun gear S1 is stopped because the first brake B1 is operated. The first ring gear R1 rotates at the rotational speed of the input shaft 10 so that the speed diagram of the first planetary gearset PG1 is formed as shown in FIG. The rotational speed is determined.

Since the third sun gear S3 rotates at the same speed as the first planetary carrier PC1 and the third ring gear R3 is stopped, the speed line diagram of the third planetary gear set PG3 is shown in Fig. 4 So that the rotation speed of the third planetary carrier PC3 is determined.

Since the third clutch C3 operates, the second ring gear R2, which is an output member, is rotated at the rotational speed of the third planetary carrier PC3 determined in this way, thereby outputting the forward second speed D2.

[Three steps forward]

In the forward third speed (D3), the first clutch C1 and the third clutch C3 operate.

The second planetary carrier PC2 rotates at the rotational speed of the input shaft 10 because the first clutch C1 is operated. In this state, the condition that the second ring gear R2 rotates at the same speed as the third planetary carrier PC3 because the third clutch C3 is operated, and the second sun gear S2 is rotated by the third sun gear S3, The speed line diagram of the second planetary gear set PG2 and the third planetary gear set PG3 is formed as shown in Fig.

According to the speed line thus formed, the third forward speed D3 is outputted through the second ring gear R2 as the output member.

[Advance 4th gen]

In the forward fourth speed (D4), the first clutch C1 and the first brake B1 operate.

The first sun gear S1 is stopped because the first brake B1 is operated. Since the first ring gear R1 rotates at the rotational speed of the input shaft 10, the speed line of the first planetary gear set PG1 is formed as shown in FIG. 6, The rotational speed is determined.

The second sun gear S2 rotates at the same speed as the second planetary carrier PC2 and the second planetary carrier PC2 rotates at the rotational speed of the input shaft 10 because the first clutch C1 operates. Therefore, the speed line diagram of the second planetary gear set PG2 is formed as shown in Fig. 6, and the rotational speed of the second ring gear R2, which is the output member, is determined.

The second ring gear R2 is rotated at the determined rotational speed to output the forward fourth gear D4.

[Five steps forward]

In the forward fifth speed (D5), the first clutch C1 and the fourth clutch C4 operate.

Since the fourth clutch C4 is operated, the first sun gear S1 rotates at the same speed as the third planetary carrier PC3. The first planetary carrier PC1 and the third sun gear S3 fixed to each other rotate at the same speed.

7, the first planetary carrier PC1 and the second sun gear S2 (not shown) are connected to the first planetary gear set PG1 and the third planetary gear set PG3, Is determined.

The second planetary carrier PC2 rotates at the rotational speed of the input shaft 10 and the second sun gear S2 rotates at the rotational speed of the first planetary carrier PC1 because the first clutch C1 operates, 2 planetary gear set PG2 is formed as shown in Fig.

According to the speed line thus formed, the second ring gear R2, which is the output member, rotates and outputs the forward fifth speed D5.

[6 steps forward]

In the forward sixth speed (D6), the first clutch C1 and the second clutch C2 operate.

The second sun gear S2 rotates at the same speed as the second ring gear R2 because the second clutch C2 is operated. Therefore, the second planetary gear set PG2 is rotated integrally.

Since the first clutch C1 is operated, the second planetary carrier PC2 rotates at the rotational speed of the input shaft 10. [ That is, the second planetary gear set PG2 rotates integrally with the rotation speed of the input shaft 10. [

Therefore, the second ring gear R2 as the output member rotates at the rotational speed of the input shaft 10, and the forward sixth gear D6 is output.

[Advancing seven genus]

In the forward seventh speed (D7), the second clutch C2 and the fourth clutch C4 operate.

The first sun gear S1 rotates at the same speed as the third planetary carrier PC3 because the fourth clutch C4 is operated. The first planetary carrier PC1 and the third sun gear S3 fixed to each other rotate at the same speed.

9, the first planetary carrier PC1 and the second sun gear S2 (S2) are formed as shown in Fig. 9. The first planetary carrier PC1 and the second sun gear S2 Is determined.

The first planetary gear set PG1 rotates integrally because the second clutch C2 is operated.

Therefore, while the speed line is formed as shown in Fig. 9, the forward seventh gear D7 is outputted through the second ring gear R2 as the output member.

[Going forward 8]

In the forward 8th gear (D8), the second clutch C2 and the first brake B1 operate.

The second sun gear S2 is stopped and the second planetary carrier PC2 rotates at the rotational speed of the input shaft 10 because the first brake B1 is operated so that the speed line diagram of the second planetary gear set PG2 is shown as 10, respectively.

The second planetary gear set PG2 rotates integrally because the second clutch C2 is operated.

Therefore, while the speed line as shown in Fig. 10 is formed, the forward eighth speed D8 is output through the second ring gear R2 as the output member.

[Backward speed]

In the reverse first speed R1, the fourth clutch C4 and the second brake B2 operate.

The first sun gear S1 rotates at the same speed as the third planetary carrier PC3 because the fourth clutch C4 is operated. The first planetary carrier PC1 and the third sun gear S3 fixed to each other rotate at the same speed.

11, a speed line diagram of the first planetary gear set PG1 and the third planetary gear set PG3 is formed as shown in Fig. 11, whereby the first planetary carrier PC1 and the second sun gear S2 Is determined.

The second planetary carrier PC1 is stopped because the second brake B2 is operated.

Therefore, the speed line diagram of the second planetary gear set PG2 is formed as shown in Fig. According to this speed diagram, the second ring gear R2, which is an output member, rotates in the reverse direction and outputs the reverse first speed R1.

In Fig. 2, examples of possible speed ratios for the eight forward speeds and one reverse speed are described. In this example, the number of sun gear / ring gear teeth of the first planetary gear set PG1 is 10, 20, the number of sun gear / ring gear teeth of the second planetary gear set PG2 is 10, 38, respectively, And the number of sun gear / ring gear teeth of the set PG3 is 10 and 38, respectively.

However, the scope of protection of the present invention should not be construed as being limited thereto. By varying the number of sun gear / ring gear teeth of the first, second and third planetary gear sets PG1, PG2, and PG3, various other speed change ratios can be obtained.

In the description of the above-mentioned embodiment, it is mentioned that the second clutch C2 for rotating the second planetary gear set PG2 integrally is possible. It is noted that the first planetary gear set PG1 can be modified into a single pinion planetary gear set and the second planetary gear set PG2 can be modified into a double pinion planetary gear set.

Hereinafter, other embodiments of the present invention relating to this modification will be described with reference to FIGS. 12 and 16. FIG.

12 is a configuration diagram of a powertrain of an automatic transmission according to a second embodiment of the present invention.

12, in the power train of the automatic transmission according to the second embodiment, the second clutch C2 for integrally rotating the second planetary gearset PG2 is connected to the second planetary gear set PG2, (R2) and the second planetary carrier (PC2).

In the power train of the automatic transmission according to the present embodiment, when the second clutch C2 is operated, the second ring gear R2 and the second planetary carrier PC2 rotate at the same speed, (PG2) rotate integrally.

In the powertrain of the automatic transmission according to the present embodiment, the first planetary gear set PG1 is formed of a single pinion planetary gear set.

3 to 11, the arrangement of the operating members of the first planetary gear set PG1 is the order of the first sun gear S1, the first ring gear R1 and the first planetary carrier PC1, The speed line diagram of the automatic transmission according to the first embodiment is arranged in the order of the first sun gear S1, the first planetary carrier PC1, and the first ring gear R1. 3 to 11, the first planetary carrier PC1 is disposed at the seat of the first ring gear R1 and the first ring gear R1 is disposed at the seat of the first planetary carrier PC1. That is, in the single pinion planetary gear set, in contrast to the double pinion planetary gear set, the arrangement of the operating members on the speed line is reversed between the ring gear and the planetary carrier, and the first planetary gear set PG1 is shifted to the double pinion planetary gear set 3 to 11, the first ring gear R1 and the first planetary carrier (second planetary gear set) in the embodiment of the single pinion planetary gear set, PC1) by replacing the position

In this embodiment, in this embodiment, the first sun gear S1, the first planetary carrier PC1, and the first ring gear R1 are engaged with the first, second, and third operations of the powertrain of the automatic transmission according to the present embodiment Member N1, N2, and N3, respectively.

12, the connection relationship applied to the first ring gear R1, which is the second actuating member N2 in Fig. 1, is the same as that of the first planetary carrier PC1, which is the second actuating member N2 in Fig. 12, ) Is applied as it is. 1, the connection relationship applied to the first planetary carrier PC1 as the third operation member N3 is directly applied to the first ring gear R1 as the third operation member N3 in FIG. 12 Able to know.

That is, the first clutch C1 selectively connects the second planetary carrier PC2 to the input shaft 10. And the second clutch C2 selectively connects the two operation members of the second planetary gear set PG2. The third clutch C3 selectively connects the second ring gear R2 and the third planetary carrier PC3. The fourth clutch C4 selectively connects the first sun gear S1 and the third planetary carrier PC3. The first brake B1 selectively connects the first sun gear S1 to the transmission case 30. [ And the second brake B2 selectively connects the second planetary carrier PC2 to the transmission case 30. [

Therefore, the powertrain of the automatic transmission according to the present embodiment can be controlled by the operation table as shown in Fig. 2, thereby forming a speed line diagram as shown in Figs. 3 to 11, 8-speed and 1-speed reverse. 3 to 11, the first ring gear R1, which is shown as the second actuating member N2, is a second actuating member in the present embodiment, And the first planetary carrier PC1 shown as the third operating member N3 is the first planetary carrier PC1 that is the third operating member N3 in the present embodiment, It should be understood by those skilled in the art.

Next, the powertrain of the automatic transmission according to the third embodiment shown in Fig. 13 shows that another modification of the connection relationship of the second clutch C2 is possible.

13, in the power train of the automatic transmission according to the third embodiment, the second clutch C2 is configured to connect the second planetary carrier PC2 or the second ring gear R2 to the first ring gear R1 ). More specifically, in the present embodiment, the second clutch C2 selectively connects the second planetary carrier PC2 and the first ring gear R1. That is, unlike the previous embodiments in which the second clutch C2 connects the two operation members in the second planetary gear set PG2, the second clutch C2 is engaged with the second planetary gear set PG2, And selectively connects the carrier PC2 with the first ring gear R1 of the first planetary gear set PG1.

The powertrain of the automatic transmission according to this embodiment is the same as the powertrain of the automatic transmission according to the second embodiment.

The second sun gear S2 is fixedly connected to the second sun gear S2 so that the second planetary carrier PC2 is rotated by the second sun gear S2 and the second sun gear S2 when the second clutch C2 is operated in this embodiment. So that the second planetary gear set PG2 is rotated integrally.

Therefore, the powertrain of the automatic transmission according to the present embodiment can be controlled by the operation table as shown in Fig. 2, thereby forming a speed line diagram as shown in Figs. 3 to 11, 8-speed and 1-speed reverse.

Next, the powertrain of the automatic transmission according to the fourth embodiment shown in Fig. 14 shows an example in which the second planetary gear set PG2 is a double pinion planetary gear set.

As shown in Fig. 14, in the power train of the automatic transmission according to the fourth embodiment, the second planetary gear set PG2 is formed of a double pinion planetary gear set.

The arrangement of the operating members of the second planetary gear set PG2 in Figs. 3 to 11 is the order of the second sun gear S2, the second planetary carrier PC2, and the second ring gear R2, The second sun gear S2, the second ring gear R2, and the second planetary carrier PC2 are arranged in this order. 3 to 11, the second planetary carrier PC2 is disposed in the seat of the second ring gear R2 and the second ring gear R2 is disposed in the seat of the second planetary carrier PC2.

In this embodiment, the second sun gear S2, the second ring gear R2, and the second planetary carrier PC2 in the present embodiment are used as the fourth, fifth, and sixth operations of the powertrain of the automatic transmission according to the present embodiment And may be referred to as negatives N4, N5, and N6, respectively.

14, the connection relationship applied to the second planetary carrier PC2, which is the fifth operating member N5 in FIG. 1, is the same as that of the second ring gear R2 ) Is applied as it is. The connection relationship applied to the second ring gear R2, which is the sixth operating member N6 in Fig. 1, is applied to the second planetary carrier PC2, which is the sixth operating member N6 in Fig. 14, .

In other words, the first clutch C1 selectively connects the second ring gear R2 to the input shaft 10. The second clutch C2 selectively connects the two operating members S2, PC2 of the second planetary gear set PG2. The third clutch C3 selectively connects the second planetary carrier PC2 and the third planetary carrier PC3. The fourth clutch C4 selectively connects the first sun gear S1 and the third planetary carrier PC3. The first brake B1 selectively connects the first sun gear S1 to the transmission case 30. [ And the second brake B2 selectively connects the second ring gear R2 to the transmission case 30. [

Therefore, the powertrain of the automatic transmission according to the present embodiment can be controlled by the operation table as shown in Fig. 2, thereby forming a speed line diagram as shown in Figs. 3 to 11, 8-speed and 1-speed reverse. However, in order to understand the shifting of this embodiment with reference to the speed diagrams of Figs. 3 to 11, regarding the planetary gear set in which the single pinion planetary gear set and the double pinion planetary gear set are changed, the ring gear and the planetary carrier It should be understood by those skilled in the art that the indicated actuating members should be understood to be substituted for each other.

The powertrain of the automatic transmission according to the fifth embodiment shown in Fig. 15 shows an example in which the first planetary gear set PG1 is a single pinion planetary gear set in contrast to the powertrain of the automatic transmission according to the fourth embodiment .

As shown in Fig. 15, in the power train of the automatic transmission according to the fifth embodiment, the first planetary gear set PG1 is formed of a single pinion planetary gear set. In this embodiment, the first sun gear S1, the first planetary carrier PC1, and the first ring gear R1 are connected to the first, second and third operating members N1 and N2 of the powertrain of the automatic transmission according to the present embodiment, N2, and N3, respectively.

The powertrain of the automatic transmission according to this embodiment is the same as the powertrain of the automatic transmission according to the fourth embodiment except for these matters.

In the power train of the automatic transmission according to the fourth embodiment, the connection relationship with respect to the first ring gear R1, which is the second actuating member N2, is the same as that in the power train of the automatic transmission according to the present embodiment, ) Is applied to the first planetary carrier PC1.

Therefore, the powertrain of the automatic transmission according to the present embodiment can be controlled by the operation table as shown in Fig. 2, thereby forming a speed line diagram as shown in Figs. 3 to 11, 8-speed and 1-speed reverse. However, in order to understand the shifting of this embodiment with reference to the speed diagrams of Figs. 3 to 11, regarding the planetary gear set in which the single pinion planetary gear set and the double pinion planetary gear set are changed, the ring gear and the planetary carrier It should be understood by those skilled in the art that the indicated actuating members should be understood to be substituted for each other.

The powertrain of the automatic transmission according to the sixth embodiment shown in Fig. 16 shows that the connection relationship of the second clutch C2 can be modified in comparison with the powertrain of the automatic transmission according to the fifth embodiment.

16, in the powertrain of the automatic transmission according to the sixth embodiment, the second clutch C2 is connected to the second planetary carrier PC2 or the second ring gear R2 via the first ring gear R1 ). More specifically, in this embodiment, the second clutch C2 selectively connects the second ring gear R2 to the first ring gear R1. That is, unlike the previous embodiments in which the second clutch C2 connects the two operation members in the second planetary gear set PG2, the second clutch C2 is engaged with the second ring of the second planetary gear set PG2, And selectively connects the gear R2 with the first ring gear R1 of the first planetary gear set PG1.

The powertrain of the automatic transmission according to this embodiment is the same as the powertrain of the automatic transmission according to the fifth embodiment.

Since the first ring gear R1 is fixedly connected to the second sun gear S2 in the present embodiment, the second ring gear R2 meshes with the second sun gear S2 when the second clutch C2 is operated So that the second planetary gear set PG2 is rotated integrally.

Therefore, the powertrain of the automatic transmission according to the present embodiment can be controlled by the operation table as shown in Fig. 2, thereby forming a speed line diagram as shown in Figs. 3 to 11, 8-speed and 1-speed reverse.

While the present invention has been described in connection with what is presently considered to be practical exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, And all changes to the scope that are deemed to be valid.

1 is a configuration diagram of a powertrain of an automatic transmission according to a first embodiment of the present invention.

2 is an operation table of the powertrain of the automatic transmission according to the first embodiment of the present invention.

3 is a speed diagram showing the rotational speeds of the respective operating members in the first forward speed of the power train of the automatic transmission according to the embodiments of the present invention.

4 is a speed diagram showing the rotational speeds of the respective operating members in the second forward speed of the power train of the automatic transmission according to the embodiment of the present invention.

5 is a speed diagram showing the rotational speeds of the respective operating members in the third forward speed of the power train of the automatic transmission according to the embodiment of the present invention.

6 is a speed diagram showing the rotational speeds of the respective operating members in the fourth forward speed of the power train of the automatic transmission according to the embodiment of the present invention.

7 is a speed diagram showing rotational speeds of respective operating members in five forward speeds of a power train of an automatic transmission according to an embodiment of the present invention.

8 is a speed line diagram showing rotational speeds of respective operating members in six forward speeds of a power train of an automatic transmission according to an embodiment of the present invention.

9 is a speed diagram showing the rotational speeds of the respective operating members in the forward seventh speed of the power train of the automatic transmission according to the embodiment of the present invention.

10 is a speed line diagram showing the rotational speeds of the respective operating members in the forward direction of the power train of the automatic transmission according to the embodiment of the present invention.

11 is a speed diagram showing the rotational speeds of the respective operating members in the first reverse speed of the power train of the automatic transmission according to the embodiment of the present invention.

12 is a configuration diagram of a powertrain of an automatic transmission according to a second embodiment of the present invention.

13 is a configuration diagram of a powertrain of an automatic transmission according to a third embodiment of the present invention.

14 is a configuration diagram of a powertrain of an automatic transmission according to a fourth embodiment of the present invention.

15 is a configuration diagram of a powertrain of an automatic transmission according to a fifth embodiment of the present invention.

16 is a configuration diagram of a powertrain of an automatic transmission according to a sixth embodiment of the present invention.

Claims (21)

A first planetary gear set including a first operating member selectively connected to the transmission case, a second operating member fixedly connected to the input shaft, and a third operating member; A fourth actuating member fixedly connected to the third actuating member, a fifth actuating member selectively connected to the input shaft and selectively connected to the transmission case, and a sixth actuating member fixedly connected to the output shaft, 2 planetary gear set; A seventh actuating member fixedly connected to the fourth actuating member and selectively connected to the sixth actuating member, an eighth actuating member selectively connected to the sixth actuating member and selectively connected to the first actuating member, A third planetary gear set including a ninth operating member fixedly connected to the transmission case; And A plurality of friction members selectively connecting the operation members of the first, second and third planetary gear sets, the input shaft, the output shaft, and the transmission case; The powertrain of the automatic transmission. The method according to claim 1, Wherein the plurality of friction members A first clutch selectively connecting the fifth operating member to the input shaft; A second clutch for integrally operating the second planetary gear set; A third clutch selectively connecting the sixth actuating member to the eighth actuating member; A fourth clutch for selectively connecting the first operating member to the eighth operating member; A first brake for selectively stopping the first actuating member; And A second brake for selectively stopping the fifth actuating member; The powertrain of the automatic transmission. The method according to claim 1, Wherein the first planetary gear set is a single pinion planetary gear set including a first sun gear, a first planetary carrier, and a first ring gear as operating members thereof, Characterized in that the first sun gear acts as a first operating member, the first planetary carrier acts as a second operating member, and the first ring gear acts as a third operating member. . The method according to claim 1, Wherein the first planetary gear set is a double pinion planetary gear set including a first sun gear, a first ring gear, and a first planetary carrier as operating members thereof, Characterized in that the first sun gear acts as a first actuating member, the first ring gear acts as a second actuating member, and the first planetary carrier acts as a third actuating member . The method according to claim 1, The second planetary gear set is a single pinion planetary gear set including a second sun gear, a second planetary carrier, and a second ring gear as operating members thereof, Characterized in that the second sun gear acts as a fourth operating member, the second planetary carrier acts as a fifth operating member, and the second ring gear acts as a sixth operating member. . The method according to claim 1, Wherein the second planetary gear set is a double pinion planetary gear set including a second sun gear, a second ring gear, and a second planetary carrier as operating members thereof, Wherein the second sun gear acts as a fourth operating member, the second ring gear acts as a fifth operating member, and the second planetary carrier acts as a sixth operating member. . The method according to claim 1, The third planetary gear set is a single pinion planetary gear set including a third sun gear, a third planetary carrier, and a third ring gear as operating members thereof, Wherein the third sun gear acts as a seventh operating member, the third planetary carrier acts as an eighth operating member, and the third ring gear acts as a ninth operating member. . 3. The method of claim 2, The third clutch and the fourth clutch operate in forward 1 speed, The third clutch and the first brake are actuated in forward 2, In the third speed forward, the first clutch and the third clutch operate, In the fourth forward speed, the first clutch and the first brake are actuated, In the fifth forward speed, the first clutch and the fourth clutch operate, In the sixth forward speed, the first clutch and the second clutch operate, In the forward speed 7, the second clutch and the fourth clutch operate, The second clutch and the first brake are operated in forward speed 8, and And the fourth clutch and the second brake are actuated in reverse 1. 3. The method of claim 2, And said second clutch selectively connects said third operating member and said sixth operating member. 3. The method of claim 2, And said second clutch selectively connects said fifth operating member and said sixth operating member. 3. The method of claim 2, And said second clutch selectively connects said third operating member and said fifth operating member. The method according to claim 1, Wherein the first planetary gear set is a double pinion planetary gear set including a first sun gear, a first ring gear, and a first planetary carrier as operating members, the first sun gear serving as a first operating member, One ring gear acts as a second actuating member, and the first planetary carrier acts as a third actuating member; Wherein the second planetary gear set is a single pinion planetary gear set including a second sun gear, a second planetary carrier, and a second ring gear as its operating members, the second sun gear serving as a fourth operating member, 2 planetary carrier acts as a fifth operating member, and the second planetary carrier acts as a sixth operating member; Wherein the third planetary gear set is a single pinion planetary gear set including a third sun gear, a third planetary carrier, and a third ring gear as its operating members, the third sun gear acting as a seventh operating member, The third planetary carrier acts as an eighth operating member, and the third ring gear acts as a ninth operating member. 13. The method of claim 12, Wherein the plurality of friction members A first clutch selectively connecting the second planetary carrier to the input shaft; A second clutch that selectively connects two operation members of the second planetary gear set; A third clutch selectively connecting the second ring gear and the third planetary carrier; A fourth clutch selectively connecting the first sun gear and the third planetary carrier; A first brake selectively connecting the first sun gear to the transmission case; And A second brake selectively connecting the second planetary carrier to the transmission case; The powertrain of the automatic transmission. The method according to claim 1, Wherein the first planetary gear set is a single pinion planetary gear set including a first sun gear, a first planetary carrier, and a first ring gear as operating members, the first sun gear serving as a first operating member, 1 planetary carrier acts as a second actuating member, and the first ring gear acts as a third actuating member; Wherein the second planetary gear set is a single pinion planetary gear set including a second sun gear, a second planetary carrier, and a second ring gear as its operating members, the second sun gear serving as a fourth operating member, 2 planetary carrier acts as a fifth operating member, and the second planetary carrier acts as a sixth operating member; Wherein the third planetary gear set is a single pinion planetary gear set including a third sun gear, a third planetary carrier, and a third ring gear as its operating members, the third sun gear acting as a seventh operating member, The third planetary carrier acts as an eighth operating member, and the third ring gear acts as a ninth operating member. 15. The method of claim 14, Wherein the plurality of friction members A first clutch selectively connecting the second planetary carrier to the input shaft; A second clutch that selectively connects two operation members of the second planetary gear set; A third clutch selectively connecting the second ring gear and the third planetary carrier; A fourth clutch selectively connecting the first sun gear and the third planetary carrier; A first brake selectively connecting the first sun gear to the transmission case; And A second brake selectively connecting the second planetary carrier to the transmission case; The powertrain of the automatic transmission. 15. The method of claim 14, Wherein the plurality of friction members A first clutch selectively connecting the second planetary carrier to the input shaft; A second clutch for selectively connecting the second planetary carrier or the second ring gear to the first ring gear; A third clutch selectively connecting the second ring gear and the third planetary carrier; A fourth clutch selectively connecting the first sun gear and the third planetary carrier; A first brake selectively connecting the first sun gear to the transmission case; And A second brake selectively connecting the second planetary carrier to the transmission case; The powertrain of the automatic transmission. The method according to claim 1, Wherein the first planetary gear set is a double pinion planetary gear set including a first sun gear, a first ring gear, and a first planetary carrier as operating members, the first sun gear serving as a first operating member, One ring gear acts as a second actuating member, and the first planetary carrier acts as a third actuating member; Wherein the second planetary gear set is a double pinion planetary gear set including a second sun gear, a second ring gear, and a second planetary carrier as its operating members, the second sun gear serving as a fourth operating member, The second ring gear acts as a fifth operating member, and the second planetary carrier acts as a sixth operating member; Wherein the third planetary gear set is a single pinion planetary gear set including a third sun gear, a third planet carrier, and a third ring gear as its operating members, the third sun gear acting as a seventh operating member, The third planetary carrier acts as an eighth operating member, and the third ring gear acts as a ninth operating member. 18. The method of claim 17, Wherein the plurality of friction members A first clutch selectively connecting the second ring gear to the input shaft; A second clutch that selectively connects two operation members of the second planetary gear set; A third clutch selectively connecting the second planetary carrier and the third planetary carrier; A fourth clutch selectively connecting the first sun gear and the third planetary carrier; A first brake selectively connecting the first sun gear to the transmission case; And A second brake selectively connecting the second ring gear to the transmission case; The powertrain of the automatic transmission. The method according to claim 1, Wherein the first planetary gear set is a single pinion planetary gear set including a first sun gear, a first planetary carrier, and a first ring gear as operating members, the first sun gear serving as a first operating member, 1 planetary carrier acts as a second actuating member, and the first ring gear acts as a third actuating member; Wherein the second planetary gear set is a double pinion planetary gear set including a second sun gear, a second ring gear, and a second planetary carrier as its operating members, the second sun gear serving as a fourth operating member, The second ring gear acts as a fifth operating member, and the second planetary carrier acts as a sixth operating member; Wherein the third planetary gear set is a single pinion planetary gear set including a third sun gear, a third planetary carrier, and a third ring gear as its operating members, the third sun gear acting as a seventh operating member, The third planetary carrier acts as an eighth operating member, and the third ring gear acts as a ninth operating member. 20. The method of claim 19, Wherein the plurality of friction members A first clutch selectively connecting the second ring gear to the input shaft; A second clutch that selectively connects two operation members of the second planetary gear set; A third clutch selectively connecting the second planetary carrier and the third planetary carrier; A fourth clutch selectively connecting the first sun gear and the third planetary carrier; A first brake selectively connecting the first sun gear to the transmission case; And A second brake selectively connecting the second ring gear to the transmission case; The powertrain of the automatic transmission. 20. The method of claim 19, Wherein the plurality of friction members A first clutch selectively connecting the second ring gear to the input shaft; A second clutch for selectively connecting the second planetary carrier or the second ring gear to the first ring gear; A third clutch selectively connecting the second planetary carrier and the third planetary carrier; A fourth clutch selectively connecting the first sun gear and the third planetary carrier; A first brake selectively connecting the first sun gear to the transmission case; And A second brake selectively connecting the second ring gear to the transmission case; The powertrain of the automatic transmission.

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