KR101405178B1 - Power train of automatic transmission - Google Patents

Abstract

A first planetary gear set including a first actuating member, a second actuating member fixedly connected to the output shaft, and a third actuating member fixedly connected to the input shaft; A fourth actuating member, a fifth actuating member selectively connected to the third actuating member and selectively connected to the first actuating member, and a sixth actuating member fixedly connected to the second actuating member, Planetary gear set; A seventh actuating member fixedly connected to the first actuating member, an eighth actuating member selectively connected to the fourth actuating member and fixedly connected to the transmission case, a second actuating member selectively connected to the fourth actuating member, A third planetary gear set including a ninth actuating member selectively connected to the fifth actuating member; 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 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 five clutches.

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 occurring in the prior art, and it is an object of the present invention to provide an automatic transmission that implements forward speeds of 8 speeds and reverse speeds using three simple planetary gear sets and five clutches. Thereby providing a powertrain of the transmission.

According to an aspect of the present invention, there is provided a powertrain of an automatic transmission including a first operating member, A first planetary gear set; A fourth actuating member, a fifth actuating member selectively connected to the third actuating member and selectively connected to the first actuating member, and a sixth actuating member fixedly connected to the second actuating member, 2 planetary gear set; A seventh actuating member fixedly connected to the first actuating member, an eighth actuating member selectively connected to the fourth actuating member and fixedly connected to the transmission case, a second actuating member selectively connected to the fourth actuating member, A third planetary gear set including a ninth actuating member selectively connected to the fifth actuating member; 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 selectively connecting the third actuating member to the fifth actuating member; A second clutch for selectively connecting the first actuating member to the fifth actuating member; A third clutch selectively connecting the fourth operating member to the ninth operating member; A fourth clutch for selectively connecting the fifth operating member to the ninth operating member; And a fifth clutch that selectively connects the fourth operating member to the eighth operating member.

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 ring gear 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 fourth clutch and the fifth clutch are operated in the forward second speed, the second clutch and the fourth clutch are operated in the third forward speed, the second clutch and the fourth clutch are engaged in the forward fourth speed, The third clutch and the fifth clutch are operated in the fifth forward speed, the first clutch and the second clutch are operated in the forward sixth speed, the first clutch and the fifth clutch are operated in the forward seventh speed, The first clutch and the third clutch are operated, and in the reverse first speed, the first clutch and the fourth clutch are operated.

As described above, according to the powertrain of the automatic transmission according to the present invention, three forward planetary gear sets and five planetary gears 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 is fixedly connected to the third sun gear S3. The first planetary carrier PC1 is fixedly connected to the input shaft 10 and functions as an input member at all times. The first ring gear R1 is fixedly connected to the second ring gear R2. The first ring gear R1 and the second ring gear R2 fixedly connected to each other are fixedly connected to the output shaft 20 and function as an output member at all times. The third planetary carrier PC3 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 five clutches.

The first clutch C1 selectively connects the first planetary carrier PC1 to the second planetary carrier PC2. The second clutch C2 selectively connects the first sun gear S1 to the second planetary carrier PC2. The third clutch C3 selectively connects the second sun gear S2 to the third ring gear R3. The fourth clutch C4 selectively connects the second planetary carrier PC2 to the third ring gear R3. The fifth clutch C5 selectively connects the second sun gear S2 to the third planetary carrier PC3.

At this time, since the third planetary carrier PC3 selectively connected to the second sun gear S2 by the fifth clutch C5 is fixedly connected to the transmission case 30, the fifth clutch C5 is operated The second sun gear S2 is stopped.

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. And the fourth clutch C4 and the fifth clutch C5 operate in the forward second speed (D2). In the forward third speed (D3), the second clutch C2 and the fourth clutch C4 operate. In the forward fourth speed (D4), the second clutch C2 and the third clutch C3 operate. In the forward fifth speed (D5), the second clutch C2 and the fifth clutch C5 operate. In the forward sixth speed (D6), the first clutch C1 and the second clutch C2 operate. In the forward seventh speed (D7), the first clutch C1 and the fifth clutch C5 operate. In the forward eighth gear (D8), the first clutch C1 and the third clutch C3 operate. In the reverse first speed (R1), the first clutch C1 and the fourth clutch C4 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 sun gear S1 is set to the first operating member N1, the first ring gear R1 is set to the second operating member N2, and the first planetary carrier PC1 Is set to the third operating member N3 and the second sun gear S2 is set to the fourth operating member N4 and the second planetary carrier PC2 is set to the fifth operating member N5, The second ring gear R2 is set to the sixth operating member N6, the third sun gear S3 is set to the seventh operating member N7, and the third planetary carrier PC3 is set to the eighth operating member N8, and the third ring gear R3 is set to the ninth working member N9.

3 to 11, the first planetary carrier PC1, which is always the third operating member N3 serving as the input member, always rotates at the rotational speed of the input shaft 10. [ Since the first sun gear S1 as the first operating member N1 and the third sun gear S3 as the seventh operating member N7 are fixedly connected, they always rotate at the same speed. Since the first ring gear R1 as the third actuating member N3 and the second ring gear R2 as the sixth actuating member N6 are fixedly connected, they rotate at the same speed at all times. Since the third planetary carrier PC3, which is the eighth operating member N8, is fixedly connected to the transmission case 30, the third planetary carrier PC3 is always stopped.

In this state, the first to eighth forward speeds and the reverse first speed are implemented by the selective operation of the first clutch C1 to the fifth clutch C5, which will be described in detail below.

[Advancing first gen]

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

Since the third clutch C3 and the fourth clutch C4 are operated simultaneously, the second planetary gear set PG2 rotates integrally and forms a speed line diagram as shown in Fig.

The third ring gear R3 connected to the second planetary gear set PG2 by the third and fourth clutches C3 and C4 rotates at the same speed as the second planetary gear set PG2 and the third planetary gear set PG2 rotates at the same speed as the second planetary gear set PG2, Is stopped, the third planetary gear set PG3 forms a speed line diagram as shown in Fig.

The first planetary carrier PC1 of the first planetary gear set PG1 rotates at the speed of the input shaft 10 and the first sun gear S1 rotates at the same speed as the third sun gear S3 of the third planetary gear set PG3 The first planetary gear set PG1 forms a speed line diagram as shown in Fig. Accordingly, a speed line diagram as shown in Fig. 3 is formed, and the forward first speed D1 is outputted through the second operation member N2 as the output member.

[Advancing second gen]

And the fourth clutch C4 and the fifth clutch C5 operate in the forward second speed (D2).

The second sun gear S2 is stopped and the fourth clutch C4 is operated so that the second planetary carrier PC2 and the third ring gear R3 rotate at the same speed .

Accordingly, a speed line diagram as shown in Fig. 4 is formed, and the forward second speed D2 is output through the second operation member N2 as the output member.

[Three steps forward]

In the forward third speed (D3), the second clutch C2 and the fourth clutch C4 operate.

The rotational speeds of the third sun gear S3, the second planetary carrier PC2 and the third ring gear R3 are matched because the second clutch C2 and the fourth clutch C4 operate simultaneously. Therefore, the third planetary gear set PG3 operates as a whole because the third sun gear S3 and the third ring gear R3 have the same speed. However, since the third planetary carrier PC3 is stopped, The planetary gear set PG3 is stopped as a whole.

Accordingly, the first sun gear S1 fixedly connected to the third sun gear S3 is also stopped, so that the speed line as shown in FIG. 5 is formed, and the forward third speed (D3) is output.

[Advance 4th gen]

In the forward fourth speed (D4), the second clutch C2 and the third clutch C3 operate.

Since the second clutch C2 is operated, the first sun gear S1 rotates at the same speed as the second planetary carrier PC2.

Since the third clutch C3 is operated, the second sun gear S2 rotates at the same speed as the third ring gear R3.

Accordingly, a speed line diagram as shown in Fig. 6 is formed, and the forward fourth speed D4 is output through the second operation member N2 as the output member.

[Five steps forward]

In the forward fifth speed (D5), the second clutch C2 and the fifth clutch C5 operate.

Since the second clutch C2 is operated, the first sun gear S1 rotates at the same speed as the second planetary carrier PC2.

Since the fifth clutch C5 is operated, the second sun gear S2 is stopped, so that the speed line of the second planetary gear set PG2 is rotated clockwise as compared with the fourth forward speed D4.

Therefore, the speed of the first sun gear S1 connected to the second planetary carrier PC2 by the second clutch C2 is increased as compared with the forward fourth speed D4.

Accordingly, a speed line diagram as shown in Fig. 7 is formed, and the forward fifth speed D5 is outputted through the second operation member N2 as the output member.

[6 steps forward]

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

The first sun gear S1 and the first planetary carrier PC1 have the same speed because the first clutch C1 and the second clutch C2 operate simultaneously. Therefore, the first planetary gear set PG1 rotates integrally with the rotation speed of the input shaft 10. [

Therefore, a speed line diagram as shown in Fig. 8 is formed with respect to the first planetary gear set PG1, and the forward sixth gear D6 is outputted through the second operation member N2 as the output member.

The second ring gear R2 is fixedly connected to the first ring gear R1 and the second planetary carrier PC2 is connected via the first and second clutches C1 and C2 to the first planetary carrier PC1 and first The second planetary gear set PG2 is also rotated integrally with the rotation speed of the input shaft 10. [

The third sun gear S3 fixedly connected to the first sun gear S1 rotates at the rotational speed of the input shaft 10 so that the speed line of the third planetary gear set PG3 is formed as shown in Fig.

[Advancing seven genus]

In the forward seventh speed (D7), the first clutch C1 and the fifth clutch C5 operate.

The second planetary carrier PC2 rotates at the rotational speed of the input shaft 10 because the first clutch C1 is operated. Since the fifth clutch C5 is operated, the second sun gear S2 is stopped. Thus, the second planetary gear set PG2 forms a speed line diagram as shown in Fig.

The first ring gear R1 fixedly connected to the second ring gear R2 is also rotated by the rotation of the input shaft 10. The second ring gear R2 rotates at a speed higher than the rotation speed of the input shaft 10, So that the first planetary gear set PG1 forms a speed line diagram as shown in Fig.

Accordingly, a speed line diagram as shown in Fig. 9 is formed, and the forward seventh speed D7 is outputted through the second operation member N2 as the output member.

[Going forward 8]

In the forward eighth gear (D8), 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. Since the third clutch C3 is operated, the second sun gear S2 rotates at the same speed as the third ring gear R3, that is, at a negative speed.

Therefore, the second planetary gear set PG2 rotates in the counterclockwise direction with respect to the forward seventh gear in the forward eighth gear (D8).

Therefore, the second ring gear R2 rotates at a higher speed than the forward seventh gear D7 in the forward eighth gear D8, and accordingly the first ring gear R1 connected to the second ring gear R2 ) Will be faster than the forward 7 speed.

Accordingly, a speed line diagram as shown in Fig. 10 is formed, and the forward eighth speed D8 is outputted through the second operation member N2 as the output member.

[Backward speed]

In the reverse first speed (R1), the first clutch C1 and the fourth clutch C4 operate.

The second planetary carrier PC2 rotates at the rotational speed of the input shaft 10 because the first clutch C1 is operated.

The third ring gear R3 rotates at the same speed as the second planetary carrier PC2 so that the third ring gear R3 is rotated by the rotation of the input shaft 10 Speed rotation.

Therefore, the speed line diagram of the third planetary gear set PG3 is formed as shown in Fig. 11, and the third sun gear S3 has a negative speed.

Therefore, the third sun gear S3 fixedly connected to the third sun gear S3 also has a negative speed, so that the speed line diagram of the first planetary gear set PG1 is formed as shown in FIG.

Therefore, a speed line diagram as shown in Fig. 11 is formed, and the reverse first speed R1 is outputted through the second operation member N2 as the output member.

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 and 23, the number of sun gear / ring gear teeth of the second planetary gear set PG2 is 10 and 24, respectively, And the number of sun gear / ring gear teeth of the set PG3 is 10 and 22, 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.

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 an embodiment of the present invention.

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

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

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

Claims (6)

A first planetary gear set including a first actuating member, a second actuating member fixedly connected to the output shaft, and a third actuating member fixedly connected to the input shaft; A fourth actuating member, a fifth actuating member selectively connected to the third actuating member and selectively connected to the first actuating member, and a sixth actuating member fixedly connected to the second actuating member, Planetary gear set; A seventh actuating member fixedly connected to the first actuating member, an eighth actuating member selectively connected to the fourth actuating member and fixedly connected to the transmission case, a second actuating member selectively connected to the fourth actuating member, A third planetary gear set including a ninth actuating member selectively connected to the fifth actuating member; 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 third actuating member to the fifth actuating member; A second clutch for selectively connecting the first actuating member to the fifth actuating member; A third clutch selectively connecting the fourth operating member to the ninth operating member; A fourth clutch for selectively connecting the fifth operating member to the ninth operating member; And A fifth clutch for selectively connecting the fourth operating member to the eighth operating member; The powertrain of the automatic transmission. 3. The method of claim 2, The third clutch and the fourth clutch operate in forward 1 speed, The fourth clutch and the fifth clutch are operated in the second forward speed, In the third forward speed, the second clutch and the fourth clutch operate, The second clutch and the third clutch operate in forward speed 4, In the fifth forward speed, the second clutch and the fifth clutch operate, In the sixth forward speed, the first clutch and the second clutch operate, The first clutch and the fifth clutch operate in forward speed 7, The first clutch and the third clutch are operated in forward speed 8, and And the first clutch and the fourth clutch are operated in the reverse 1 speed. 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 its operating members, the first sun gear acting 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 ring gear 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. 5. The method of claim 4, Wherein the plurality of friction members A first clutch selectively connecting the first planetary carrier to the second planetary carrier; A second clutch selectively connecting the first sun gear to the second planetary carrier; A third clutch selectively connecting the second sun gear to the third ring gear; A fourth clutch selectively connecting the second planetary carrier to the third ring gear; And A fifth clutch for selectively connecting the second sun gear to the third planetary carrier; The powertrain of the automatic transmission. 6. The method of claim 5, The third clutch and the fourth clutch operate in forward 1 speed, The fourth clutch and the fifth clutch are operated in the second forward speed, In the third forward speed, the second clutch and the fourth clutch operate, The second clutch and the third clutch operate in forward speed 4, In the fifth forward speed, the second clutch and the fifth clutch operate, In the sixth forward speed, the first clutch and the second clutch operate, The first clutch and the fifth clutch operate in forward speed 7, The first clutch and the third clutch are operated in forward speed 8, and And the first clutch and the fourth clutch are operated in the reverse 1 speed.

Images