KR101416346B1 - Power train of automatic transmission - Google Patents

Abstract

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

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

At least one friction member of the first, second, third, fourth, fifth, and sixth friction members may be disposed between the first planetary gear set and the third planetary gear set.

The first, second, third, fourth, fifth, and sixth friction members may be disposed outside the first, second, and third planetary gear sets.

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 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 friction member and the fifth friction member are operated in the first forward speed, the fourth friction member and the sixth friction member are operated in the forward second speed, the second friction member and the fourth friction member are operated in the forward third speed, The first friction member and the fourth friction member are operated, the first friction member and the second friction member operate in the forward speed 5, the first friction member and the third friction member operate in the forward speed 6, and in the forward speed 7, The first friction member and the sixth friction member are operated, the first friction member and the fifth friction member are operated in the forward speed mode, and the second friction member and the fifth friction member are operated in the reverse speed mode.

The first friction member is a first clutch that selectively connects the eighth operation member and the input shaft and the second friction member is a second clutch that selectively connects the seventh operation member and the output shaft, The third friction member is a third clutch that selectively connects the second operation member and the sixth operation member, and the fourth friction member is a third clutch that selectively connects the second operation member and the eighth operation member, And the fifth friction member is a first brake that selectively connects the second operation member to the transmission case or the fourth operation member fixed to the transmission case, And may be a second brake selectively connecting to the transmission case or the fourth operating member fixed thereto.

The first friction member is a first clutch that selectively connects the eighth operation member and the input shaft and the second friction member is a second clutch that selectively connects the seventh operation member and the output shaft, The third friction member is a third clutch that selectively connects the second operation member and the sixth operation member, and the fourth friction member is a third clutch that selectively connects the second operation member and the eighth operation member, And the fifth friction member is a first brake that selectively connects the second actuating member to the transmission case or the fourth actuating member fixed thereto, and the sixth friction member is a first brake, 5 operating member.

Wherein the first friction member is a first clutch that selectively connects the eighth operation member and the input shaft and the second friction member is a second clutch that selectively connects the eighth operation member and the output shaft, The third friction member is a third clutch that selectively connects the second operation member and the sixth operation member, and the fourth friction member is a third clutch that selectively connects the second operation member and the eighth operation member, And the fifth friction member is a first brake that selectively connects the second actuating member to the transmission case or the fourth actuating member fixed to the transmission case, And a second brake selectively connecting to the case or the fourth actuating member fixed thereto.

Wherein the first friction member is a first clutch that selectively connects the eighth operation member and the input shaft and the second friction member is a second clutch that selectively connects the eighth operation member and the output shaft, The third friction member is a third clutch that selectively connects the second operation member and the sixth operation member, and the fourth friction member is a third clutch that selectively connects the second operation member and the eighth operation member, And the fifth friction member is a first brake that selectively connects the second actuating member to the transmission case or the fourth actuating member fixed thereto, and the sixth friction member is a first brake, 5 operating member.

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 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 first sun gear S1 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 second planetary carrier PC2 is fixedly connected to the third sun gear S3. The third ring gear R3 is fixedly connected to the output shaft 20 and functions as an output member at all times. The second sun gear S2 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 third planetary carrier PC3 and the input shaft 10; A second clutch C2 for operating the third planetary gear set PG3 integrally; A third clutch C3 selectively connecting the first planetary carrier PC1 and the second planetary carrier PC2; A fourth clutch C4 selectively connecting the first planetary carrier PC1 and the third planetary carrier PC3; A first brake B1 selectively connecting the first planetary carrier PC1 to the transmission case 30 or the second sun gear S2 fixed thereto; And a second brake B2 for integrally stopping the second planetary gear set PG2.

In the present embodiment, the second clutch C2 selectively connects the third sun gear S3 and the output shaft 20. [ 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 third planetary gear set PG3 integrally are possible and will be described later as a separate embodiment.

The third sun gear S3 is a friction member for stopping the second planetary gear set PG2 integrally with the transmission case 30 or the second sun gear S2 fixed to the transmission case 30, The second brake B2 is used. However, the scope of protection of the present invention should not be construed as being limited thereto. Other configurations of the friction element for stopping the second planetary gear set PG2 integrally are possible, which will be described later as a separate embodiment.

Although the first brake B1 selectively connects the first planetary carrier PC1 to the second sun gear S2 fixed to the transmission case 30 in the present embodiment, The scope is not necessarily to be construed as being limited thereto. It is also possible that the first brake B1 directly connects the first planetary carrier PC1 to the transmission case 30.

Although the second brake B2 selectively connects the third sun gear S3 to the second sun gear S2 fixed to the transmission case 30 in the present embodiment, Should not be construed as necessarily limited thereto. It is also possible that the first brake B1 directly connects the third sun gear S3 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, the fourth clutch C4 and the first brake B1 operate in the forward first speed (D1). In the forward second speed (D2), the fourth clutch (C4) and the second brake (B2) operate. In the forward third speed (D3), the second clutch C2 and the fourth clutch C4 operate. In the forward fourth speed (D4), the first clutch C1 and the fourth clutch C4 operate. In the forward fifth speed (D5), the first clutch C1 and the second clutch C2 operate. In the forward sixth speed (D6), the first clutch Cl and the third clutch C3 operate. In the forward seventh speed (D7), the first clutch C1 and the second brake B2 operate. In the forward 8th gear (D8), the first clutch C1 and the first brake B1 operate. And the second clutch C2 and the first brake B1 operate in the reverse first speed R1.

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 planetary carrier PC1 is set to the second operating member N2, 1 ring gear R1 is set to the third actuating member N3 and the second sun gear S2 is set to the fourth actuating member N4 and the second ring gear R2 is set to the fifth actuating member N5 , The second planetary carrier PC2 is set to the sixth operating member N6 and the third sun gear S3 is set to the seventh working member N7 and the third planetary carrier PC3 is set to the sixth operating member N6, Is set to the eighth operating member N8, and the third ring gear R3 is set to the ninth operating member N9.

3 to 11, the first sun gear S1, which is always the first operating member N1 serving as the input member, always rotates at the rotational speed of the input shaft 10. [ Since the first ring gear R1 as the third operating member N3 and the second ring gear R2 as the sixth operating member N6 are fixedly connected, they always rotate at the same speed. Since the second planetary carrier PC2 as the sixth operating member N6 and the third sun gear S3 as the seventh operating member N7 are fixedly connected to each other, they always rotate at the same speed. Since the second sun gear S2, which is the fourth operating member N4, is fixedly connected to the transmission case 30, the second sun gear S2 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 fourth clutch C4 and the first brake B1 operate.

The first planetary carrier PC1 is stopped because the first brake B1 is operated. Since the first sun gear S1 acting as the input member rotates at the rotational speed of the input shaft 10, the speed line diagram of the first planetary gear set PG1 is formed as shown in Fig.

Since the second ring gear R2 is fixedly connected to the first ring gear R1, it rotates at the speed of the first ring gear R1. Since the second sun gear S2 is always stopped, the speed line diagram of the second planetary gear set PG2 is formed as shown in Fig.

The third sun gear S3 rotates at the same speed as the second planetary carrier PC2 and the fourth clutch C4 operates in a state in which the first planetary carrier PC1 is stopped, Stopped. Therefore, the speed line diagram of the third planetary gear set PG3 is formed as shown in Fig.

Therefore, a speed line diagram as shown in Fig. 3 is formed, and the forward first speed D1 is outputted through the ninth operation member N9 as the output member.

[Advancing second gen]

In the forward second speed (D2), the fourth clutch (C4) and the second brake (B2) operate.

The third sun gear S3 is stopped because the second brake B2 is operated.

The second planetary carrier PC2 fixedly connected to the third sun gear S3 is also stopped and the second sun gear S2 is always stopped so that the speed line diagram of the second planetary gear set PG2 is as shown in Fig. . That is, the second planetary gear set PG2 is stopped as a whole.

Therefore, the first ring gear R1 fixedly connected to the second ring gear R2 also stops. At this time, since the first sun gear S1 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.

Since the fourth clutch C4 is operated, the third planetary carrier PC3 rotates at the same speed as the first planetary carrier PC1. At this time, since the third sun gear S3 is stopped, the speed line diagram of the third planetary gear set PG3 is formed as shown in Fig.

Accordingly, a speed line diagram as shown in Fig. 4 is formed, and the forward second speed D2 is outputted through the ninth operation member N9 as the output member.

[Three steps forward]

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

The third planetary gear set PG3 rotates integrally because the second clutch C2 is operated.

Since the fourth clutch C4 is operated, the first planetary carrier PC1 rotates at the same speed as the rotation speed of the third planetary gear set PG3.

Accordingly, a speed line diagram as shown in Fig. 5 is formed, and the forward third speed D3 is outputted through the ninth operation member N9 as the output member.

[Advance 4th gen]

In the forward fourth speed (D4), the first clutch C1 and the fourth clutch C4 operate.

The first planetary carrier PC1 rotates at the rotational speed of the input shaft 10 because the first clutch C1 and the fourth clutch C4 operate simultaneously. Thus, the speed diagram of the first planetary gear set PG1 is formed as shown in Fig. That is, the first planetary gear set PG1 rotates integrally with the rotational speed of the input shaft 10. [

The second ring gear R2 fixedly connected to the first ring gear R1 also rotates at the rotational speed of the input shaft 10. [ At this time, since the second sun gear S2 is always stopped, the speed line diagram of the second planetary gear set PG2 is formed as shown in Fig.

The third sun gear S3 rotates at the same speed as the second planetary carrier PC2 and the third planetary carrier PC3 rotates at the rotational speed of the input shaft 10 by the operation of the fourth clutch C4, The speed line of the third planetary gear set PG3 is formed as shown in Fig.

Accordingly, a speed line diagram as shown in Fig. 6 is formed, and the forward fourth speed D4 is outputted through the ninth operation member N9 as the output member.

[Five steps forward]

In the forward fifth speed (D5), the first clutch C1 and the second clutch C2 operate.

The third planetary gear set PG3 rotates integrally because the second clutch C2 is operated. At this time, since the first clutch C1 is operated, the third planetary carrier PC3 rotates at the rotational speed of the input shaft 10. [ That is, the third planetary gear set PG3 rotates integrally with the rotation speed of the input shaft 10. [ 7, the ninth actuating member N9, which is the output member, rotates at the rotational speed of the input shaft 10 and the forward fifth gear (D5 Is output.

Since the second planetary carrier PC2 rotates at the same speed as the third sun gear S3, the speed line diagram of the second planetary gear set PG2 is formed as shown in Fig. Since the first ring gear R1 rotates at the same speed as the second ring gear R2, the speed line diagram of the first planetary gear set PG1 is formed as shown in Fig.

[6 steps forward]

In the forward sixth speed (D6), the first clutch Cl and the third clutch C3 operate.

The third planetary carrier PC3 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 planetary carrier PC2 and the third sun gear S3 fixedly connected rotate at the same speed as the first planetary carrier PC1.

Therefore, a speed line diagram as shown in Fig. 8 is formed, and the forward sixth speed D6 is outputted through the ninth operation member N9 as the output member.

[Advancing seven genus]

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

The third planetary carrier PC3 rotates at the rotational speed of the input shaft 10 because the first clutch C1 is operated. Since the second brake B2 is operated, the third sun gear S3 is stopped. Accordingly, the speed line diagram of the third planetary gear set PG3 is formed as shown in Fig. 9, and the forward seventh speed D7 is outputted through the ninth working member N9 as the output member.

At this time, the second planetary carrier PC2 fixedly connected to the third sun gear S3 is stopped, so that the second planetary gear set PG2 is stopped as a whole, and the first ring gear R2 is fixedly connected to the second ring gear R2. The speed line of the first planetary gear set PG1 is formed as shown in Fig. 9 because the gear R1 is stopped.

[Going forward 8]

In the forward 8th gear (D8), the first clutch C1 and the first brake B1 operate.

The first planetary carrier PC1 is stopped and the speed line diagram of the first planetary gear set PG1 is formed as shown in Fig. 10 because the first brake B1 is operated.

At this time, since the second ring gear R2 is rotated at the same speed as the first ring gear R1, the speed line diagram of the second planetary gear set PG2 is formed as shown in Fig.

The third planetary carrier PC3 rotates at the rotational speed of the input shaft 10 and the third sun gear S3 fixedly connected to the second planetary carrier PC2 is rotated by the second planetary carrier PC2, (PC2).

Therefore, the speed line of the third planetary gear set PG3 is formed as shown in Fig. 10, and the forward eighth gear D8 is outputted through the ninth operation member N9 as the output member.

[Backward speed]

And the second clutch C2 and the first brake B1 operate in the reverse first speed R1.

The first planetary carrier PC1 is stopped and the speed line diagram of the first planetary gear set PG1 is formed as shown in Fig. 11 because the first brake B1 is operated.

At this time, since the second ring gear R2 is rotated at the same speed as the first ring gear R1, the speed line of the second planetary gear set PG2 is formed as shown in Fig.

The third planetary gear set PG3 rotates integrally because the second clutch C2 is operated. At this time, the third sun gear S3 fixedly connected to the second planetary carrier PC2 is rotated at the same speed as the second planetary carrier PC2.

Accordingly, a speed line diagram as shown in Fig. 11 is formed, and the reverse first speed R1 is outputted through the ninth operation member N9 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 28, respectively, And the number of sun gear / ring gear teeth of the set PG3 is 10 and 27, 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 powertrain of the automatic transmission according to the first embodiment of the present invention described above, the first to fourth clutches C1, C2, C3, C4 and the first and second brakes B1 And B2 is disposed between the first planetary gear set PG1 and the third planetary gear set PG3.

However, the scope of protection of the present invention should not be construed as being limited thereto. Variations are possible regarding the arrangement of the clutches. Hereinafter, the powertrain of the automatic transmission according to the second embodiment of the present invention in which the arrangement of the clutches is modified in comparison with the first embodiment will be described with reference to FIG.

12, in the powertrain of the automatic transmission according to the second embodiment of the present invention, the first, second, third and fourth clutches C1, C2, C3 and C4 and the first and second brakes B1 And B2 are disposed outside the first, second, and third planetary gear sets PG1, PG2, and PG3.

The configuration of the first, second and third planetary gear sets PG1, PG2, and PG3 and the fixed and variable connection relationships of the first, second and third planetary gear sets PG1, PG2, and PG3 are the same as those of the first embodiment of the present invention.

Therefore, the powertrain of the automatic transmission according to the second embodiment of the present invention can be shifted by the operation table as shown in Fig. 2, and accordingly, the speed line diagram as shown in Figs. 3 to 11 To form the forward 8-speed and the reverse 1-speed.

In the description of the above-described embodiment, it is possible to modify the friction member for integrally stopping the second planetary gear set PG2, and the second clutch for operating the third planetary gear set PG3 integrally I have mentioned that it is possible to modify it.

Hereinafter, other embodiments of the present invention relating to this modification will be described with reference to FIGS. 13 to 15. FIG.

13, the powertrain of the automatic transmission according to the third embodiment is a friction member for integrally stopping the second planetary gear set PG2, and the second ring gear R2 And a fifth clutch C5 for selectively connecting the first planetary carrier PC1 and the second planetary carrier PC2. That is, in the powertrain of the automatic transmission according to the first embodiment, the second brake B2 is removed and the fifth clutch C5 is added.

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

In the power train of the automatic transmission according to the present embodiment, when the fifth clutch C5 operates, the second ring gear R2 and the second planetary carrier PC2 have the same speed, so that the second planetary gear set PG2 ) Operate as a single unit. However, since the second sun gear S2 is always stopped, the second planetary gear set PG2 is stopped as a whole by the operation of the fifth clutch C5.

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, in the powertrain of the automatic transmission according to the fourth embodiment, as the friction member for operating the third planetary gear set PG3 in unison, the third planetary carrier PC3, And the second clutch C2 selectively connecting the output shaft 20 are used. That is, as compared with the powertrain of the automatic transmission according to the first embodiment, the operating members selectively connected by the second clutch C2 of the operating members of the third planetary gear set PG3 are different.

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

In the power train of the automatic transmission according to the present embodiment, when the second clutch C2 is operated, the third ring gear R3 and the third planetary carrier PC3 have the same speed, so that the third planetary gear set PG3 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.

As shown in Fig. 15, the powertrain of the automatic transmission according to the fifth embodiment is different from the powertrain of the automatic transmission according to the third embodiment described above and the characteristics of the powertrain of the automatic transmission according to the fourth embodiment Respectively.

That is, a fifth clutch C5 for selectively connecting the second ring gear R2 and the second planetary carrier PC2 as a friction member for stopping the second planetary gear set PG2 integrally . As the friction member for operating the third planetary gear set PG3 integrally, a second clutch C2 for selectively connecting the third planetary carrier PC3 and the output shaft 20 is used.

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

Claims (17)

A first planetary gear set including a first operating member fixedly connected to the input shaft, a second operating member selectively stopped, and a third operating member; A second planetary gear set including a fourth actuating member fixedly connected to the transmission case, a fifth actuating member fixedly connected to the third actuating member, and a sixth actuating member selectively connected to the second actuating member; A seventh actuating member fixedly connected to the sixth actuating member, an eighth actuating member selectively connected to the input shaft and selectively connected to the second actuating member, and a ninth actuating member fixedly connected to the output shaft A third 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 friction member for selectively connecting the eighth actuating member to the input shaft; A second friction member for operating the third planetary gear set integrally; A third friction member for selectively connecting the second actuating member to the sixth actuating member; A fourth friction member for selectively connecting the second actuating member to the eighth actuating member; A fifth friction member for selectively stopping the second actuating member; And A sixth friction member for integrally stopping the second planetary gear set; The powertrain of the automatic transmission. 3. The method of claim 2, And at least one friction member of the first, second, third, fourth, fifth, and sixth friction members is disposed between the first planetary gear set and the third planetary gear set. 3. The method of claim 2, Wherein the first, second, third, fourth, fifth, and sixth friction members are disposed outside the first, second, and third planetary gear sets. 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 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 fourth friction member and the fifth friction member are operated in the first forward speed, The fourth friction member and the sixth friction member are operated in the forward second speed, In the forward third speed, the second friction member and the fourth friction member operate, In the fourth speed forward, the first friction member and the fourth friction member are operated, In the fifth forward speed, the first friction member and the second friction member are operated, The first friction member and the third friction member are operated in forward speed 6, The first friction member and the sixth friction member are operated in forward speed 7, The first friction member and the fifth friction member are operated in forward speed 8, and And a second friction member and a fifth friction member are operated in the reverse rotation. 3. The method of claim 2, The first friction member is a first clutch that selectively connects the eighth operating member and the input shaft, The second friction member is a second clutch that selectively connects the seventh operating member and the output shaft, The third friction member is a third clutch that selectively connects the second operating member and the sixth operating member, The fourth friction member is a fourth clutch that selectively connects the second operating member and the eighth operating member, The fifth friction member is a first brake that selectively connects the second actuating member to the transmission case or the fourth actuating member fixed thereto, And the sixth friction member is a second brake that selectively connects the seventh actuating member to the transmission case or the fourth actuating member fixed thereto Wherein the power transmission is a power transmission of an automatic transmission. 3. The method of claim 2, The first friction member is a first clutch that selectively connects the eighth operating member and the input shaft, The second friction member is a second clutch that selectively connects the seventh operating member and the output shaft, The third friction member is a third clutch that selectively connects the second operating member and the sixth operating member, The fourth friction member is a fourth clutch that selectively connects the second operating member and the eighth operating member, The fifth friction member is a first brake that selectively connects the second actuating member to the transmission case or the fourth actuating member fixed thereto, And the sixth friction member is a fifth friction member that selectively connects the sixth operating member and the fifth operating member, Wherein the power transmission is a power transmission of an automatic transmission. 3. The method of claim 2, The first friction member is a first clutch that selectively connects the eighth operating member and the input shaft, The second friction member is a second clutch that selectively connects the eighth operating member and the output shaft, The third friction member is a third clutch that selectively connects the second operating member and the sixth operating member, The fourth friction member is a fourth clutch that selectively connects the second operating member and the eighth operating member, The fifth friction member is a first brake that selectively connects the second actuating member to the transmission case or the fourth actuating member fixed thereto, And the sixth friction member is a second brake that selectively connects the seventh actuating member to the transmission case or the fourth actuating member fixed thereto Wherein the power transmission is a power transmission of an automatic transmission. 3. The method of claim 2, The first friction member is a first clutch that selectively connects the eighth operating member and the input shaft, The second friction member is a second clutch that selectively connects the eighth operating member and the output shaft, The third friction member is a third clutch that selectively connects the second operating member and the sixth operating member, The fourth friction member is a fourth clutch that selectively connects the second operating member and the eighth operating member, The fifth friction member is a first brake that selectively connects the second actuating member to the transmission case or the fourth actuating member fixed thereto, And the sixth friction member is a fifth friction member that selectively connects the sixth operating member and the fifth operating member, Wherein the power transmission is a power transmission of an 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. 14. The method of claim 13, Wherein the plurality of friction members A first clutch selectively connecting the third planetary carrier and the input shaft; A second clutch selectively connecting the third sun gear and the output shaft; A third clutch selectively connecting the first planetary carrier and the second planetary carrier; A fourth clutch selectively connecting the first planetary carrier and the third planetary carrier; A first brake selectively connecting the first planetary carrier to the transmission case or the second sun gear fixed thereto; And A second brake selectively connecting the third sun gear to the transmission case or the second sun gear fixed thereto; And a power transmission mechanism for transmitting power to the automatic transmission. 14. The method of claim 13, Wherein the plurality of friction members A first clutch selectively connecting the third planetary carrier and the input shaft; A second clutch selectively connecting the third sun gear and the output shaft; A third clutch selectively connecting the first planetary carrier and the second planetary carrier; A fourth clutch selectively connecting the first planetary carrier and the third planetary carrier; A first brake selectively connecting the first planetary carrier to the transmission case or the second sun gear fixed thereto; And A fifth clutch selectively connecting the second ring gear and the second planetary carrier; And a power transmission mechanism for transmitting power to the automatic transmission. 14. The method of claim 13, Wherein the plurality of friction members A first clutch selectively connecting the third planetary carrier and the input shaft; A second clutch selectively connecting the third planetary carrier and the output shaft; A third clutch selectively connecting the first planetary carrier and the second planetary carrier; A fourth clutch selectively connecting the first planetary carrier and the third planetary carrier; A first brake selectively connecting the first planetary carrier to the transmission case or the second sun gear fixed thereto; And A second brake selectively connecting the third sun gear to the transmission case or the second sun gear fixed thereto; And a power transmission mechanism for transmitting power to the automatic transmission. 14. The method of claim 13, Wherein the plurality of friction members A first clutch selectively connecting the third planetary carrier and the input shaft; A second clutch selectively connecting the third planetary carrier and the output shaft; A third clutch selectively connecting the first planetary carrier and the second planetary carrier; A fourth clutch selectively connecting the first planetary carrier and the third planetary carrier; A first brake selectively connecting the first planetary carrier to the transmission case or the second sun gear fixed thereto; And A fifth clutch selectively connecting the second ring gear and the second planetary carrier; And a power transmission mechanism for transmitting power to the automatic transmission.

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