KR101483637B1 - Power train of automatic transmission - Google Patents

Abstract

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

And the fourth clutch may selectively connect the fifth operating member and the ninth operating member. And the fourth clutch may selectively connect the first operating member and the second operating member.

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 two-ring gear acts as a fifth operating member, and the second planetary carrier acts as a sixth operating 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 first brake and the second brake are operated in the first forward speed and the fourth clutch and the first brake are operated in the forward forward speed and the second clutch and the first brake are operated in the forward forward speed and the third clutch and the first brake are operated in the forward forward speed, The first clutch and the first brake are operated in the fifth speed forward, the first clutch is operated in the sixth forward speed and at least one clutch of the second, third and fourth clutches is operated, and in the forward seventh speed, The first clutch and the second brake are operated, the third clutch and the second brake are operated in the forward speed 8, and the fourth clutch and the second brake are operated in the reverse speed.

When the second planetary gear set is a double pinion planetary gear set, the plurality of friction members include: a first clutch selectively connecting the input shaft and the first planetary carrier; A second clutch selectively connecting the input shaft to the first sun gear; A third clutch selectively connecting the second ring gear and the third planetary carrier; A fourth clutch for integrally rotating the first planetary gear set; A first brake selectively connecting the third sun gear and the transmission case; And a second brake selectively connecting the first sun gear and the transmission case.

And the fourth clutch can selectively connect the second ring gear and the third ring gear. And the fourth clutch may selectively connect the first sun gear and the first planetary carrier.

When the second planetary gear set is a single pinion planetary gear set, the plurality of friction members include: a first clutch selectively connecting the input shaft and the first planetary carrier; A second clutch selectively connecting the input shaft to the first sun gear; A third clutch selectively connecting the second ring gear and the third planetary carrier; A fourth clutch for integrally rotating the first planetary gear set; A first brake selectively connecting the third sun gear and the transmission case; And a second brake selectively connecting the first sun gear and the transmission case.

The fourth clutch can selectively connect the second planetary carrier and the third ring gear. The fourth clutch can selectively connect the first sun gear and the first planetary carrier.

As described above, according to the powertrain of the automatic transmission according to the present invention, three forward planetary gear sets and six friction elements 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 single pinion planetary gear set including a first sun gear S1, a first planetary carrier PC1, and a first ring gear R1 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 double pinion planetary gear set including the second sun gear S2, the second ring gear R2, and the second planetary carrier PC2 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 planetary carrier PC1 and the first ring gear R1 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 ring gear R2, and the second planetary carrier PC2 are connected to the fourth, fifth, and sixth operating members N4 (first and second planetary gears) 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 sixth actuating member N6 is fixedly connected to the input shaft 10 and always functions as an input member. The eighth operating member N8 is fixedly connected to the output shaft 20 and functions as an output member at all times.

The second actuating member N2 and the ninth actuating member N9 are fixedly connected. The third actuating member N3 and the fifth actuating member N5 are fixedly connected. The fourth actuating member N4 and the seventh actuating member N7 are fixedly connected.

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) for selectively connecting the input shaft (10) and the second actuating member (N2); A second clutch C2 selectively connecting the input shaft 10 and the first actuating member N1; A third clutch C3 for selectively connecting the fifth operating member N5 and the eighth operating member N8; A fourth clutch C4 for operating the first planetary gear set PG1 integrally; A first brake B1 selectively connecting the seventh actuating member N7 and the transmission case 30; And a second brake B2 for selectively connecting the first actuating member N1 and the transmission case 30. [

Way clutch OWC is arranged in parallel on the first brake B1.

In the present embodiment, the fourth clutch C4 selectively connects the fifth operating member N5 and the ninth operating member N9. However, the scope of protection of the present invention should not be construed as being limited thereto. The fourth clutch C4 may selectively connect the first operating member N1 and the second operating member N2.

More specifically, the first clutch C1 selectively connects the input shaft 10 and the first planetary carrier PC1. The second clutch C2 selectively connects the input shaft 10 and the first sun gear S1. The third clutch C3 selectively connects the second ring gear R2 and the third planetary carrier PC3. The fourth clutch C4 rotates the first planetary gear set PG1 integrally. The first brake B1 selectively connects the third sun gear S3 and the transmission case 30. [ The second brake B2 selectively connects the first sun gear S1 and the transmission case 30. [

In the present embodiment, the fourth clutch C4 selectively connects the second ring gear R2 and the third ring gear R3. The second ring gear R2 rotates at the same speed as the third ring gear R3 and the first ring gear R1 fixedly connected to the second ring gear R2 when the fourth clutch C4 is operated, Also rotates at the same speed as the third ring gear R3. The first planetary carrier PC1 fixedly connected to the third ring gear R3 also rotates at the same speed as the third ring gear R3. The first planetary carrier PC1 and the first ring gear R1 rotate at the same speed, so that the first planetary gear set PG1 rotates integrally. However, the scope of protection of the present invention should not be construed as being limited thereto. Various modifications can be applied to the arrangement of the fourth clutch C 4, and this will be described later as a separate embodiment.

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, the first brake B1 and the second brake B2 operate in the forward first speed D1. In the forward second speed (D2), the fourth clutch C4 and the first brake B1 operate. In the forward third speed (D3), the second clutch C2 and the first brake B1 operate. In the forward fourth speed (D4), the third clutch C3 and the first brake B1 operate. In the forward fifth speed (D5), the first clutch C1 and the first brake B1 operate. In the forward sixth speed (D6), the first clutch C1 is operated and at least one of the second, third and fourth clutches C2, C3 and C4 operates. In the forward seventh speed (D7), the first clutch C1 and the second brake B2 operate. In the forward eighth gear (D8), the third clutch C3 and the second brake B2 operate. In the reverse first speed (Rev 1), 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 sixth actuating member N6 always acting as the input member always rotates at the rotational speed of the input shaft 10. [

Since the second actuating member N2 and the ninth actuating member N9 are fixedly connected, they rotate at the same speed at all times. Since the third actuating member N3 and the fifth actuating member N5 are fixedly connected, they rotate at the same speed at all times. Since the fourth actuating member N4 and the seventh actuating member N7 are fixedly connected, they rotate at the same speed at all times.

In this state, forward first to eighth speed and reverse 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 first brake B1 and the second brake B2 operate.

Since the first brake B1 is operated, the seventh actuating member N7 and the fourth actuating member N4 fixedly connected thereto stop. Since the sixth actuating member N6 rotates at the rotational speed of the input shaft 10, the speed line diagram of the second planetary gear set PG2 is formed as shown in Fig.

The third actuating member N3 rotates at the same speed as the fifth actuating member N5 and the first actuating member N1 stops because the second brake B2 is actuated. Accordingly, the speed line diagram of the first planetary gear set PG1 is formed as shown in Fig.

The seventh operation member N7 is stopped and the ninth operation member N9 rotates at the same speed as the second operation member N2.

Therefore, the speed line of the third planetary gear set PG3 is formed as shown in Fig. 3, and the forward first speed D1 is outputted through the eighth working member N8 as the output member.

However, since the one-way clutch OWC is disposed in parallel to the second brake B2, the first forward speed can be output by the operation of the one-way clutch OWC without the forced drive of the second brake B2 .

[Advancing second gen]

In the forward second speed (D2), the fourth clutch C4 and the first brake B1 operate.

Since the first brake B1 is operated, the seventh actuating member N7 and the fourth actuating member N4 fixedly connected thereto stop. Since the sixth actuating member N6 rotates at the rotational speed of the input shaft 10, the speed diagram of the second planetary gear set PG2 is formed as shown in Fig.

The ninth operating member N9 connected to the fifth operating member N5 through the fourth clutch C4 and the eighth operating member N9 connected to the fifth operating member N5 via the fourth clutch C4, And the third actuating member N3 fixedly connected to the fifth actuating member N5 rotate all at the same speed. Since the second actuating member N2 and the third actuating member N3 rotate at the same speed, the first planetary gear set PG1 rotates integrally as shown in Fig.

The seventh actuating member N7 rotates at the same speed as the fifth actuating member N5 while the seventh actuating member N7 is in the stopped state.

Therefore, the speed line diagram of the third planetary gear set PG3 is formed as shown in Fig. 4, and the forward second speed D2 is outputted through the eighth operational member N8 as the output member.

[Three steps forward]

In the forward third speed (D3), the second clutch C2 and the first brake B1 operate.

Since the first brake B1 is operated, the seventh actuating member N7 and the fourth actuating member N4 fixedly connected thereto stop. Since the sixth actuating member N6 rotates at the rotational speed of the input shaft 10, the speed diagram of the second planetary gearset PG2 is formed as shown in Fig.

The third actuating member N3 rotates at the same speed as the fifth actuating member N5 and the first actuating member N1 rotates at the rotational speed of the input shaft 10 because the second clutch C2 is operated. Therefore, the speed line diagram of the first planetary gear set PG1 is formed as shown in Fig.

The seventh operation member N7 is stopped and the ninth operation member N9 rotates at the same speed as the second operation member N2.

Therefore, the speed line diagram of the third planetary gear set PG3 is formed as shown in Fig. 5, and the forward third speed D3 is outputted through the eighth operational member N8 as the output member.

[Advance 4th gen]

In the forward fourth speed (D4), the third clutch C3 and the first brake B1 operate.

Since the first brake B1 is operated, the seventh actuating member N7 and the fourth actuating member N4 fixedly connected thereto stop. Since the sixth actuating member N6 rotates at the rotational speed of the input shaft 10, the speed diagram of the second planetary gearset PG2 is formed as shown in Fig.

Since the third clutch C3 is operated, the eighth operating member N8 rotates at the same speed as the fifth operating member N5.

Accordingly, the speed line of the third planetary gear set PG3 is formed as shown in Fig. 6, and the fourth forward speed D4 is outputted through the eighth operational member N8 as the output member.

[Five steps forward]

In the forward fifth speed (D5), the first clutch C1 and the first brake B1 operate.

The seventh operation member N7 stops because the first brake B1 is operated.

Since the first clutch C1 is operated, the second actuating member N2 and the ninth actuating member N9 fixedly connected thereto rotate at the same speed as the input shaft 10. [

Therefore, the speed line of the third planetary gear set PG3 is formed as shown in Fig. 7, and the forward fifth speed D5 is outputted through the eighth working member N8 as the output member.

[6 steps forward]

In the forward sixth speed (D6), the first clutch C1 is operated and at least one of the second, third and fourth clutches C2, C3 and C4 operates.

First, the case where the first clutch C1 and the second clutch C2 are operated will be described.

The first clutch C1 is operated so that the second operating member N2 rotates at the same speed as the input shaft 10 and the second clutch C2 operates so that the first operating member N1 is also engaged with the input shaft 10 It rotates at the same speed. Therefore, the first planetary gear set PG1 rotates integrally with the rotation speed of the input shaft 10. [

Therefore, the fifth operating member N5 fixedly connected to the third operating member N3 also rotates at the rotational speed of the input shaft 10, so that the second planetary gear set PG2 is integrally formed with the rotational speed of the input shaft 10 Rotate.

Therefore, the seventh actuating member N7 fixedly connected to the fourth actuating member N4 and the ninth actuating member N9 fixedly connected to the second actuating member N2 both rotate at the rotational speed of the input shaft 10 The third planetary gear set PG3 rotates integrally with the rotational speed of the input shaft 10. [

Therefore, the forward sixth gear D6 is outputted at the rotational speed of the input shaft 10 through the eighth working member N8 as the output member.

Next, the case where the first clutch Cl and the third clutch C3 operate will be described.

The first clutch C1 is operated so that the second actuating member N2 rotates at the same speed as the input shaft 10 and the ninth actuating member N9 fixedly connected to the second actuating member N2 is also rotated by the input shaft 10 ). ≪ / RTI > That is, the sixth operation member N6 and the ninth operation member N9 rotate at the same speed.

At this time, since the third clutch C3 is operated, the fifth operating member N5 and the eighth operating member N8 rotate at the same speed. Therefore, the second and third planetary gear sets PG2 and PG3 rotate integrally at the same speed.

Therefore, the forward sixth gear D6 is outputted at the rotational speed of the input shaft 10 through the eighth working member N8 as the output member.

Next, the case where the first clutch C1 and the fourth clutch C4 are operated will be described.

The second operating member N2 rotates at the same speed as the input shaft 10 because the first clutch C1 is operated. Since the fourth clutch C4 is operated, the first planetary gear set PG1 rotates integrally. That is, the first planetary gear set PG1 rotates integrally with the rotational speed of the input shaft 10. [

Therefore, the fifth operating member N5 also rotates at the same speed as the input shaft 10, so that the second planetary gear set PG2 also rotates integrally with the rotational speed of the input shaft 10. [

Therefore, the seventh actuating member N7 fixedly connected to the fourth actuating member N4 and the ninth actuating member N9 connected to the fifth actuating member N5 through the fourth clutch C4 both function as the input shaft 10 ). ≪ / RTI > Therefore, the third planetary gear set PG3 rotates integrally with the rotation speed of the input shaft 10. [

Therefore, the forward sixth gear D6 is outputted at the rotational speed of the input shaft 10 through the eighth working member N8 as the output member.

[Advancing seven genus]

In the forward seventh speed (D7), the first clutch C1 and the second brake B2 operate.

The second operating member N2 rotates at the rotational speed of the input shaft 10 because the first clutch C1 is operated. The first actuating member N1 stops because the second brake B2 is actuated. Accordingly, the speed line diagram of the first planetary gear set PG1 is formed as shown in Fig.

The sixth actuation member N6 rotates at the rotational speed of the input shaft 10 and the fifth actuation member N5 rotates at the same speed as the third actuation member N3 so that the speed of the second planetary gearset PG2 The line is formed as shown in Fig.

The ninth actuating member N9 rotates at the same speed as the second actuating member N2 and the seventh actuating member N7 rotates at the same speed as the fourth actuating member N4.

Therefore, the speed line diagram of the third planetary gear set PG3 is formed as shown in Fig. 9, and the forward seventh gear D7 is outputted through the eighth working member N8 as the output member.

[Going forward 8]

In the forward eighth gear (D8), the third clutch C3 and the second brake B2 operate.

The first actuating member N1 stops because the second brake B2 is actuated. Because the third clutch C3 is operated, the fifth operating member N5 and the eighth operating member N8 rotate at the same speed.

The second actuating member N2 and the ninth actuating member N9 which are fixedly connected rotate at the same speed and the third actuating member N3 and the fifth actuating member N5 fixedly connected rotate at the same speed, The fourth operative member N4 and the seventh operative member N7, which are fixedly connected, rotate at the same speed.

The speed diagrams of the first, second and third planetary gear sets PG1, PG2 and PG3 are shown in Fig. 10 by the interaction of the first, second and third planetary gear sets PG1, PG2, And the forward eighth gear D8 is output through the eighth working member N8 as the output member.

[Backward speed]

In the reverse first speed (Rev 1), the fourth clutch C4 and the second brake B2 operate.

The first actuating member N1 stops because the second brake B2 is actuated. Since the fourth clutch C4 is operated, the first planetary gear set PG1 operates in unison. Therefore, the first planetary gear set PG1 is stopped as a whole.

The fifth operating member N5 fixedly connected to the third operating member N3 is also stopped so that the speed line of the second planetary gearset PG2 is formed as shown in Fig. 11, and the fourth operating member N4 Is reversed.

The ninth actuating member N9 fixedly connected to the second actuating member N2 is stopped and the seventh actuating member N7 is reversed at the same speed as the fourth actuating member N4.

Therefore, the speed line of the third planetary gear set PG3 is formed as shown in Fig. 11, and the reverse first speed Rev1 is outputted through the eighth working member N8 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 25, 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 20, 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 embodiment described above, the example in which the second planetary gear set PG2 is a double pinion planetary gear set has been described. However, the scope of protection of the present invention should not be construed as being limited thereto. Hereinafter, an example in which the second planetary gear set PG2 is a single pinion planetary gear set will be described with reference to Fig.

As shown in Fig. 12, in the powertrain of the automatic transmission according to the second embodiment, the second planetary gear set PG2 is formed of a single 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 ring gear R2, and the second planetary carrier PC2, The second sun gear S2, the second planetary carrier PC2, and the second ring gear R2 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 planetary carrier PC2, and the second ring gear R2 in the present embodiment correspond to the fourth, fifth, and sixth operations of the powertrain of the automatic transmission according to the present embodiment Members N4, N5 and N6, respectively.

12, the connection relationship applied to the second ring gear R2, which is the fifth operating member N5 in Fig. 1, is the same as the connecting relationship applied to the second planetary carrier PC2, which is the fifth operating member N5 in Fig. 12, ) Is applied as it is. The connection relationship applied to the second planetary carrier PC2, which is the sixth operating member N6 in Fig. 1, is applied to the second ring gear R2, which is the sixth operating member N6 in Fig. 12, .

That is, the first ring gear R1 is fixedly connected to the second planetary carrier PC2. The input shaft 10 is fixedly connected to the second ring gear R2. The third clutch C3 selectively connects the second planetary carrier PC2 and the third planetary carrier PC3. The fourth clutch C4 selectively connects the second planetary carrier PC2 and the third ring gear R3.

In the present embodiment, the fourth clutch C4 selectively connects the third ring gear R3 and the second planetary carrier PC2. Therefore, when the fourth clutch C4 is operated, the second planetary carrier PC2 rotates at the same speed as the third ring gear R3, and the first ring gear R1 (R1) fixedly connected to the second planetary carrier PC2 Also rotates at the same speed as the third ring gear R3. The first planetary carrier PC1 fixedly connected to the third ring gear R3 also rotates at the same speed as the third ring gear R3. The first planetary carrier PC1 and the first ring gear R1 rotate at the same speed, so that the first planetary gear set PG1 rotates integrally. However, the scope of protection of the present invention should not be construed as being limited thereto. Various modifications can be applied to the arrangement of the fourth clutch C 4, and this will be described later as a separate embodiment.

In this embodiment, the remaining fixed and selective connection relationships of the first to ninth actuating members N1 to N9 are the same as in the first embodiment.

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.

In the first embodiment of the present invention, the fourth clutch C4 selectively connects the fifth actuating member N5 and the ninth actuating member N9, and various modifications can be made thereto have. Examples of such variations are described below.

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

Referring to Fig. 13 in comparison with Fig. 1, according to the present embodiment, the fourth clutch C4 selectively connects the first operating member N1 and the second operating member N2. More specifically, the fourth clutch C4 selectively connects the first sun gear S1 and the first planetary carrier PC1. The third embodiment of the present invention is different from the first embodiment in that the fourth clutch C4 selectively connects the first sun gear S1 and the first planetary carrier PC1, same.

In the present embodiment, when the fourth clutch C4 is operated, the first sun gear S1 and the first planetary carrier PC1 rotate at the same speed, so that the first planetary gear set PG2 rotates 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.

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

Referring to Fig. 14 in comparison with Fig. 2, according to the present embodiment, the fourth clutch C4 selectively connects the first operating member N1 and the second operating member N2. More specifically, the fourth clutch C4 selectively connects the first sun gear S1 and the first planetary carrier PC1. The fourth embodiment of the present invention is different from the fourth embodiment in that the fourth clutch C4 selectively connects the first sun gear S1 and the first planetary carrier PC1, same.

In the present embodiment, when the fourth clutch C4 is operated, the first sun gear S1 and the first planetary carrier PC1 rotate at the same speed, so that the first planetary gear set PG2 rotates 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.

In the second embodiment of the present invention, the fourth clutch C4 selectively connects the first actuating member N1 and the sixth actuating member N6, and various modifications thereof are possible have. Examples of such variations are described below.

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

Referring to Fig. 16 in comparison with Fig. 13, according to the present embodiment, the fourth clutch C4 selectively connects the first operating member N1 and the fifth operating member N5. More specifically, the fourth clutch C4 selectively connects the first sun gear S1 and the second ring gear R2. Other fixed and variable connection relationships are the same as in the second embodiment.

In this embodiment, when the fourth clutch C4 is operated, the second sun gear S2 and the second ring gear R2 rotate at the same speed, so that the second planetary gear set PG2 rotates 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.

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

Referring to Fig. 17 in comparison with Fig. 13, according to the present embodiment, the fourth clutch C4 selectively connects the eighth operating member N8 and the fifth operating member N5. More specifically, the fourth clutch C4 selectively connects the third ring gear R3 and the second ring gear R2. Other fixed and variable connection relationships are the same as in the second embodiment.

In the present embodiment, when the fourth clutch C4 is operated, the second ring gear R2 and the second planetary carrier PC2 rotate at the same speed, so that the second planetary gear set PG2 rotates 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.

Claims (18)

A first actuating member selectively connected to the input shaft and selectively connected to the transmission case, a second actuating member selectively connected to the input shaft separately from the first actuating member, and a second actuating member selectively connected to the input shaft, set; A second planetary gear set including a fourth operating member, a fifth operating member fixedly connected to the third operating member, and a sixth operating member fixedly connected to the input shaft; A seventh actuating member fixedly connected to the fourth actuating member and selectively connected to the transmission case, an eighth actuating member selectively connected to the fifth actuating member and fixedly connected to the output shaft, A third planetary gear set including a ninth operating member fixedly connected to the first planetary gear set; 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 input shaft and the second operation member; A second clutch selectively connecting the input shaft and the first operation member; A third clutch for selectively connecting the fifth operating member and the eighth operating member; A fourth clutch for operating the first planetary gear set integrally; A first brake selectively connecting the seventh operation member and the transmission case; And A second brake selectively connecting the first operating member and the transmission case; The powertrain of the automatic transmission. 3. The method of claim 2, And the fourth clutch selectively connects the fifth operating member and the ninth operating member. 3. The method of claim 2, And said fourth clutch selectively connects said first operating member and said second operating member. 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 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 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, 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, Characterized in that 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 first brake and the second brake are actuated in forward 1 speed, The fourth clutch and the first brake are actuated in forward 2, In the forward third speed, the second clutch and the first brake are operated, The fourth clutch and the first brake are operated in forward speed 4, In the fifth forward speed, the first clutch and the first brake are actuated, In the sixth forward speed, the first clutch is operated and at least one of the second, third and fourth clutches operates, The first clutch and the second brake are operated in forward speed 7, The third clutch and the second brake are operated in forward speed 8, And the fourth clutch and the second brake are actuated in reverse 1. 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. 11. The method of claim 10, Wherein the plurality of friction members A first clutch selectively connecting the input shaft and the first planetary carrier; A second clutch selectively connecting the input shaft to the first sun gear; A third clutch selectively connecting the second ring gear and the third planetary carrier; A fourth clutch for integrally rotating the first planetary gear set; A first brake selectively connecting the third sun gear and the transmission case; And A second brake selectively connecting the first sun gear and the transmission case; The powertrain of the automatic transmission. 12. The method of claim 11, And the fourth clutch selectively connects the second ring gear and the third ring gear. 12. The method of claim 11, And said fourth clutch selectively connects said first sun gear and said first planetary carrier. 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 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 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. 15. The method of claim 14, Wherein the plurality of friction members A first clutch selectively connecting the input shaft and the first planetary carrier; A second clutch selectively connecting the input shaft to the first sun gear; A third clutch selectively connecting the second ring gear and the third planetary carrier; A fourth clutch for integrally rotating the first planetary gear set; A first brake selectively connecting the third sun gear and the transmission case; And A second brake selectively connecting the first sun gear and the transmission case; The powertrain of the automatic transmission. 16. The method of claim 15, And said fourth clutch selectively connects said second planetary carrier and said third ring gear. 16. The method of claim 15, And said fourth clutch selectively connects said first sun gear and said first planetary carrier. 16. The method according to claim 11 or 15, The first brake and the second brake are actuated in forward 1 speed, The fourth clutch and the first brake are actuated in forward 2, In the forward third speed, the second clutch and the first brake are operated, The fourth clutch and the first brake are operated in forward speed 4, In the fifth forward speed, the first clutch and the first brake are actuated, In the sixth forward speed, the first clutch is operated and at least one of the second, third and fourth clutches operates, The first clutch and the second brake are operated in forward speed 7, The third clutch and the second brake are operated in forward speed 8, And the fourth clutch and the second brake are actuated in reverse 1.

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