KR20090129813A - Power train of automatic transmission - Google Patents

Abstract

PURPOSE: A power train of an automatic transmission is provided to use selective operation of first to fifth clutches and a first brake, thereby realizing forward speeds 1 to 8 and backward speed 2. CONSTITUTION: A first planetary gear set(PG1) comprises a first operation member, a second operation member, and a third operation member. The first operation member is selectively connected to an input shaft. The second operation member is selectively connected to the input shaft, and is selectively interrupted. The third operation member is fixably connected to an output shaft. A second planet gear set(PG2) comprises a fourth operation member, a fifth operation member, and a sixth operation member.

Description

POWER TRAIN OF AUTOMATIC TRANSMISSION}

The present invention relates to a power train of an automatic transmission, and more particularly, to a power train of an automatic transmission that implements eight forward speeds and two reverse speeds using three simple planetary gear sets and six friction elements.

In general, a multi-stage shifting mechanism of an automatic transmission is implemented by combining a plurality of planetary gearsets, and a power train in which the plurality of planetary gearsets is combined receives a torque from a torque converter included in the automatic transmission and shifts it. It will function to transfer to the output shaft.

However, the more transmission stages that can be implemented, the more appropriate transmission ratios can be designed, and the vehicle can be realized in terms of power performance and fuel efficiency. Therefore, automatic transmissions that implement more transmission stages are of interest for continuous research. have.

In addition, even if the same number of gear stages are implemented, the durability, power transmission efficiency, and size of the power train vary according to the combination method of the planetary gear set, so that a more robust, no power loss, and a more compact power train configuration Efforts are always underway to invent.

In particular, unlike manual transmissions in which the driver has to shift frequently if the shift stage is too large, the automatic transmission performs shifting by controlling the operation of the power train by the control unit according to the driving condition. Efforts to find the configuration of the power train that implements the stage become more important for automatic transmissions.

Therefore, the present invention is devised to meet the development of the automatic transmission as described above, the object of the present invention is to implement the eight forward speed and the second reverse speed using three simple planetary gear set and six friction elements. It is to provide the power train of the automatic transmission.

The power train of the automatic transmission according to an embodiment of the present invention for achieving this object, the first operating member selectively connected to the input shaft, the second operating member selectively connected to the input shaft and optionally stopped, the output shaft A first planetary gear set including a third operating member fixedly connected; A second planetary gear set including a fourth operating member fixedly connected to the first operating member, a fifth operating member selectively connected to the third operating member, and a sixth operating member; A third including a seventh operating member fixedly connected to the input shaft, an eighth operating member fixedly connected to the sixth operating member, and a ninth operating member selectively connected to the first operating member and fixedly stopped. Planetary gear sets; 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 may include: a first clutch selectively connecting the input shaft and the first operation member; A second clutch for selectively connecting the input shaft and the second operating member; A third clutch for selectively connecting the third operating member and the fifth operating member; A fourth clutch for integrally rotating the second planetary gear set; A fifth clutch for selectively connecting the first operating member and the ninth operating member; And a first brake for selectively stopping the second operating member.

The fourth clutch may selectively connect the first operating member and the sixth operating member. The fourth clutch may selectively connect the first operating member and the fifth operating member. The fourth clutch may selectively connect the eighth operating member and the fifth operating member.

The first planetary gear set is a single pinion planetary gear set including a first sun gear, a first planet carrier, and a first ring gear as its operating member, wherein the first sun gear acts as a first actuating member. The one planet carrier acts as the second actuating member, and the first ring gear acts as the third actuating member.

The second planetary gear set is a single pinion planetary gear set including a second sun gear, a second planet carrier, and a second ring gear as its operating member, wherein the second sun gear acts as a fourth operating member. The two planetary carriers may act as the fifth operating member, and the second ring gear may act as the sixth operating member.

The second planetary gear set is a double pinion planetary gear set including a second sun gear, a second ring gear, and a second planet carrier as its operating member, wherein the second sun gear acts as a fourth operating member. The second ring gear acts as a fifth actuation member, and the second planetary carrier acts as a sixth actuation member.

The third planetary gear set is a double pinion planetary gear set including a third sun gear, a third ring gear, and a third planet carrier as its operating member, wherein the third sun gear acts as a seventh operating member. The third ring gear acts as an eighth actuation member, and the third planetary carrier acts as a ninth actuation member.

The third clutch and the first brake operate at the first forward speed, the third clutch and the fifth clutch operate at the second forward speed, the third clutch and the fourth clutch operate at the third forward speed, and the first clutch and the first clutch at the fourth forward speed. The third clutch operates, the second clutch and the third clutch operate at the fifth forward speed, the first clutch and the second clutch operate at the sixth forward speed, the second clutch and the fourth clutch operate at the seventh forward speed, and the forward eight The second clutch and the fifth clutch operate in the inside, the fourth clutch and the first brake operate in the reverse speed 1, and the first clutch and the first brake operate in the reverse speed 2.

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

The fourth clutch may selectively connect the first sun gear and the second ring gear. The fourth clutch may selectively connect the first sun gear and the second planet carrier. The fourth clutch may selectively connect the second planet carrier and the third ring gear.

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

In this case, the fourth clutch may selectively connect the first sun gear and the second planet carrier. The fourth clutch may selectively connect the first sun gear and the second ring gear. The fourth clutch may selectively connect the second ring gear and the third ring gear.

As described above, according to the power train of the automatic transmission according to the present invention, three forward planetary gear sets and six friction elements may be used to implement eight forward speeds and two reverse speeds.

In addition, by providing a large number of gear stages it is possible to effectively use the power of the engine to improve the power transmission performance and reduce fuel economy.

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

As shown in FIG. 1, a power train of an automatic transmission according to an exemplary 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 power from 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 planet carrier PC1, and a first ring gear R1 as its operating member. A first pinion gear P1 gear-coupled to the first sun gear S1 and the first ring gear R1 is connected to the first planet carrier PC1 to rotate.

The second planetary gear set PG2 is a single pinion planetary gear set including a second sun gear S2, a second planet carrier PC2, and a second ring gear R2 as its operating member. A second pinion gear P2 gear-coupled to the second sun gear S2 and the second ring gear R2 is connected to the second planet carrier PC2 to rotate.

The third planetary gear set PG3 is a double pinion planetary gear set including a third sun gear S3, a third ring gear R3, and a third planet carrier PC3 as its operating member. The third planet carrier PC3 is connected to and rotates with a third pinion gear P3 gear-coupled with the third sun gear S3 and the third ring gear R3.

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

The seventh operating member N7 is fixedly connected to the input shaft 10 and always acts as an input member. The third operating member N3 is fixedly connected to the output shaft 20 to act as an output member at all times. The ninth operating member N9 is fixedly connected to the transmission case 30 to always function as a stop member.

The first operating member N1 and the fourth operating member N4 are fixedly connected. The sixth operating member N6 and the eighth operating member N8 are fixedly connected.

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

The plurality of friction members may include: a first clutch C1 selectively connecting the input shaft 10 and the first operating member N1; A second clutch (C2) for selectively connecting the input shaft (10) and the second operating member (N2); A third clutch (C3) for selectively connecting the third operating member (N3) and the fifth operating member (N5); A fourth clutch C4 for integrally rotating the second planetary gear set PG2; A fifth clutch (C5) for selectively connecting the first operating member (N1) and the ninth operating member (N9); And a first brake B1 for selectively stopping the second operating member N2.

The one-way clutch OWC is disposed in parallel with the first brake B1.

In the present embodiment, the fourth clutch C4 selectively connects the first operating member N1 and the sixth operating member N6. However, the scope of protection of the present invention should not be understood as being limited thereto. The fourth clutch C4 may selectively connect the first operating member N1 and the fifth operating member N5. In addition, the fourth clutch C4 may selectively connect the eighth operating member N8 and the fifth operating member.

More specifically, the first clutch C1 selectively connects the input shaft 10 and the first sun gear S1. The second clutch C2 selectively connects the input shaft 10 and the first planet carrier PC1. The third clutch C3 selectively connects the first ring gear R1 and the second planet carrier PC2. The fourth clutch C4 rotates the second planetary gear set PG2 integrally. The fifth clutch C5 selectively connects the first sun gear S1 and the third planet carrier PC3. The first brake B1 selectively connects the first planet carrier PC1 to the transmission case 30.

In the present embodiment, the fourth clutch C4 selectively connects the first sun gear S1 and the second ring gear R2. Therefore, when the fourth clutch C4 operates, 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. However, the scope of protection of the present invention should not be understood as being limited thereto. Various modifications may be made to the arrangement of the fourth clutch C4, which 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 8 forward speeds and 2 reverse speeds, and two friction members operate at each shift stage.

That is, in the first forward speed D1, the third clutch C3 and the first brake B1 operate. In the second forward speed D2, the third clutch C3 and the fifth clutch C5 operate. In the third forward speed D3, the third clutch C3 and the fourth clutch C4 operate. At the fourth forward speed D4, the first clutch C1 and the third clutch C3 operate. In the fifth forward speed D5, the second clutch C2 and the third clutch C3 operate. At the sixth forward speed D6, the first clutch C1 and the second clutch C2 operate. In the seventh forward speed D7, the second clutch C2 and the fourth clutch C4 operate. In the eighth forward D8, the second clutch C2 and the fifth clutch C5 operate. In the reverse first speed Rev1, the fourth clutch C4 and the first brake B1 operate. In the second reverse speed Rev2, the first clutch C1 and the first brake B1 operate.

Hereinafter, the formation of eight forward speeds and two reverse speeds in the power train of the automatic transmission according to the embodiment of the present invention will be described in detail.

3 to 12, the seventh operating member N7, which always acts as an input member, is always rotated at the rotational speed of the input shaft 10. Since the ninth operating member N9 is fixedly connected to the transmission case 30, it is always stopped. Therefore, the velocity diagram of the third planetary gear set PG3 is kept constant regardless of the gear stage. That is, the ninth operating member N9 is stopped, the seventh operating member N7 rotates at the rotational speed of the input shaft 10, and the eighth operating member N8 is lower than the rotational speed of the input shaft 10. It will rotate at a reduced speed.

Since the first operating member N1 and the fourth operating member N4 are fixedly connected to each other, they are always rotated at the same speed, and the sixth operating member N6 and the eighth operating member N8 are fixed to each other. As it is connected, it always rotates at the same speed. That is, the sixth operating member N6 always rotates at the same speed as the reduced speed of the eighth operating member N8.

In this state, the first to eighth speeds and the second to second speeds are implemented by selective operation of the first clutches C1 to fifth clutch C5 and the first brake B1, which will be described in detail below. .

The ninth operating member N9 connected to the first operating member N1 through the fifth clutch C5 is fixedly connected to the transmission case 30. Therefore, when the fifth clutch C5 is operated, the first operating member N1 is stopped.

[1st speed forward]

In the first forward speed D1, the third clutch C3 and the first brake B1 operate.

Since the third clutch C3 operates, the third operating member N3 and the fifth operating member N5 rotate at the same speed. Since the first brake B1 operates, the second operating member N2 stops.

Accordingly, the speed diagrams of the first and second planetary gear sets PG1 and PG2 are formed as shown in FIG. 3, and the first forward speed D1 is output through the third operation member N3, which is an output member.

However, since the one-way clutch OWC is disposed in parallel with the first brake B1, the first forward speed may be output by the operation of the one-way clutch OWC without forcibly driving the first brake B1. .

[2 speed forward]

In the second forward speed D2, the third clutch C3 and the fifth clutch C5 operate.

Since the fifth clutch C5 operates, the first operating member N1 stops. Thus, the velocity diagram of the second planetary gear set PG2 is formed as shown in FIG. Since the third clutch C3 operates, the third operating member N3 and the fifth operating member N5 rotate at the same speed.

Accordingly, the speed diagrams of the first and second planetary gear sets PG1 and PG2 are formed as shown in FIG. 4, and the second forward speed D2 is output through the third operation member N3, which is an output member.

[3 speed forward]

In the third forward speed D3, the third clutch C3 and the fourth clutch C4 operate.

Since the fourth clutch C4 operates, the second planetary gear set PG2 rotates integrally. Since the sixth operating member N6 rotates at the reduced rotational speed of the ninth operating member N9, the second planetary gear set PG2 integrally rotates at the reduced rotational speed of the ninth operating member N9. .

Since the third clutch C3 operates, the third operating member N3 and the fifth operating member N5 rotate at the same speed. Since both of the first operating member N1 connected to the fourth operating member N4 and the third operating member N3 connected to the fifth operating member rotate at the reduced speed, the first planetary gear set PG1 is It rotates integrally at a reduced speed.

The third speed D3, which is the reduced speed, is output through the third operating member N3, which is an output member.

[4 forward speed]

At the fourth forward speed D4, the first clutch C1 and the third clutch C3 operate.

Since the first clutch C1 operates, the first operating member N1 rotates at the same speed as the input shaft 10. Thus, the velocity diagram of the second planetary gear set PG2 is formed as shown in FIG.

Since the third clutch C3 operates, the third operating member N3 and the fifth operating member N5 rotate at the same speed.

Therefore, the fourth forward speed D4 that is faster than the reduced speed is output through the third operating member N3 which is an output member.

[5th forward]

In the fifth forward speed D5, the second clutch C2 and the third clutch C3 operate.

Since the second clutch C2 operates, the second operating member N2 rotates at the same speed as the input shaft 10. Since the third clutch C3 operates, the third operating member N3 and the fifth operating member N5 rotate at the same speed.

Accordingly, the speed diagrams of the first and second planetary gear sets PG1 and PG2 are formed as shown in FIG. 7, and the fifth forward speed D5 is output through the third operation member N3, which is an output member.

[6th forward]

At the sixth forward speed D6, the first clutch C1 and the second clutch C2 operate.

Since the first clutch C1 operates, the first operating member N1 rotates at the same speed as the input shaft 10. Thus, the velocity diagram of the second planetary gear set PG2 is formed as shown in FIG.

Since the second clutch C2 operates, the second operating member N2 rotates at the same speed as the input shaft 10.

Accordingly, the speed diagrams of the first and second planetary gear sets PG1 and PG2 are formed as shown in FIG. 8, and the sixth forward speed D6 is output through the third operation member N3, which is an output member.

[7th forward]

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

Since the fourth clutch C4 operates, the second planetary gear set PG2 rotates integrally. Since the sixth operating member N6 rotates at the reduced rotational speed of the ninth operating member N9, the second planetary gear set PG2 integrally rotates at the reduced rotational speed of the ninth operating member N9. .

Since the second clutch C2 operates, the second operating member N2 rotates at the same speed as the input shaft 10.

Accordingly, the speed diagrams of the first and second planetary gear sets PG1 and PG2 are formed as shown in FIG. 9, and the seventh forward speed D7 is output through the third operating member N3, which is an output member.

[8th forward]

At the eighth forward speed D8, the second clutch C2 and the fifth clutch C5 operate.

Since the fifth clutch C5 operates, the first operating member N1 stops. Thus, the velocity diagram of the second planetary gear set PG2 is formed as shown in FIG.

Since the second clutch C2 operates, the second operating member N2 rotates at the same speed as the input shaft 10.

Accordingly, the speed diagrams of the first and second planetary gear sets PG1 and PG2 are formed as shown in FIG. 10, and the eighth forward speed D8 is output through the third operating member N3, which is an output member.

[1 speed reverse]

In the reverse first speed Rev1, the fourth clutch C4 and the first brake B1 operate.

Since the fourth clutch C4 operates, the second planetary gear set PG2 rotates integrally. Since the sixth operating member N6 rotates at the reduced rotational speed of the ninth operating member N9, the second planetary gear set PG2 integrally rotates at the reduced rotational speed of the ninth operating member N9. .

Since the first brake B1 operates, the second operating member N2 stops.

Accordingly, the speed diagrams of the first and second planetary gear sets PG1 and PG2 are formed as shown in FIG. 11, and the reverse first speed Rev1 is output through the third operation member N3, which is an output member.

[2 speed reverse]

In the second reverse speed Rev2, the first clutch C1 and the first brake B1 operate.

Since the first clutch C1 operates, the first operating member N1 rotates at the same speed as the input shaft 10. Therefore, the velocity diagram of the second planetary gear set PG2 is formed as shown in FIG.

Since the first brake B1 operates, the second operating member N2 stops.

Accordingly, the speed diagrams of the first and second planetary gear sets PG1 and PG2 are formed as shown in FIG. 12, and the reverse second speed Rev2 is output through the third operation member N3, which is an output member.

In FIG. 2, an example of the speed ratio which is possible with respect to 8 forward speeds and 1 reverse speed is described. For example, the number of sun gear / ring gear teeth of the first planetary gear set PG1 is 10 and 21, the number of sun gear / ring gear teeth of the second planetary gear set PG2 is 10 and 22, respectively, and the third planetary gear The number of sun gear / ring gear teeth of the set PG3 is 10 and 19, respectively.

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

In the above embodiment, an example in which the second planetary gear set PG2 is a single pinion planetary gear set has been described. However, the protection scope of the present invention should not be understood to be limited thereto. Hereinafter, an example in which the second planetary gear set PG2 is a double pinion planetary gear set will be described with reference to FIG. 13.

As shown in Fig. 13, in the power train of the automatic transmission according to the second embodiment, the second planetary gear set PG2 is formed of a double pinion planetary gear set.

3 to 12, the arrangement of the operating members of the second planetary gear set PG2 is in the order of the second sun gear S2, the second planet carrier PC2, and the second ring gear R2, but this embodiment The speed diagram of the automatic transmission is arranged in the order of the second sun gear S2, the second ring gear R2, and the second planet carrier PC2. That is, in FIG. 3 to FIG. 12, the second planet carrier PC2 is disposed in place of the second ring gear R2, and the second ring gear R2 is disposed in place of the second planet carrier PC2.

With this configuration, in the present embodiment, the second sun gear S2, the second ring gear R2, and the second planet carrier PC2 operate the fourth, fifth and sixth operation of the power train of the automatic transmission according to the present embodiment. The members N4, N5, and N6 may be called respectively.

Referring to FIG. 13, the connection relationship applied to the second planetary carrier PC2, which is the fifth operating member N5 in FIG. 1, is the second ring gear R2, which is the fifth operating member N5 in FIG. 13. You can see that it is applied as is). In addition, it is understood that the connection relationship applied to the second ring gear R2 as the sixth operating member N6 in FIG. 1 is applied to the second planetary carrier PC2 as the sixth operating member N6 in FIG. 13 as it is. Can be.

That is, the second planet carrier PC2 is fixedly connected to the third ring gear R3. The first clutch C1 selectively connects the input shaft 10 and the first sun gear S1. The second clutch C2 selectively connects the input shaft 10 and the first planet carrier PC1. The third clutch C3 selectively connects the first ring gear R1 and the second ring gear R2. The fourth clutch C4 rotates the second planetary gear set PG2 integrally. The fifth clutch C5 selectively connects the first sun gear S1 and the third planet carrier PC3. The first brake B1 selectively connects the first planet carrier PC1 and the transmission case 30.

In the present embodiment, the fourth clutch C4 selectively connects the first sun gear S1 and the second planet carrier PC2. Therefore, when the fourth clutch C4 operates, the second sun gear S2 and the second planet carrier PC2 rotate at the same speed, so that the second planetary gear set PG2 rotates integrally. However, the scope of protection of the present invention should not be understood as being limited thereto. Various modifications may be made to the arrangement of the fourth clutch C4, which will be described later as a separate embodiment.

In this embodiment, the remaining fixed and selective connection relations of the first operating member N1 to the ninth operating member N9 are the same as in the first embodiment.

Therefore, the powertrain of the automatic transmission according to the present embodiment, the shift can be controlled by the operation table as shown in Figure 2, accordingly, to form a speed diagram as shown in Figures 3 to 12 to advance 8 speeds and 2 reverse speeds.

In the first embodiment of the present invention, the fourth clutch C4 selectively connects the first actuating member N1 and the sixth actuating member N6. have. Hereinafter, examples of such modifications will be described.

14 is a configuration diagram showing a power train of an automatic transmission according to the third embodiment of the present invention.

Referring to FIG. 14, in contrast to FIG. 1, 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 planet carrier PC2. Other fixed and variable connection relationships are the same as in the first embodiment.

In the present embodiment, when the fourth clutch C4 operates, the second sun gear S2 and the second planet 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, the shift can be controlled by the operation table as shown in Figure 2, accordingly, to form a speed diagram as shown in Figures 3 to 12 to advance 8 speeds and 2 reverse speeds.

15 is a configuration diagram showing a power train of an automatic transmission according to the fourth embodiment of the present invention.

In contrast to FIG. 15, according to the present exemplary 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 planet carrier PC2. Other fixed and variable connection relationships are the same as in the first embodiment.

In the present embodiment, when the fourth clutch C4 operates, the second ring gear R2 and the second planet 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, the shift can be controlled by the operation table as shown in Figure 2, accordingly, to form a speed diagram as shown in Figures 3 to 12 to advance 8 speeds and 2 reverse speeds.

In the second embodiment of the present invention, the fourth clutch C4 selectively connects the first operating member N1 and the sixth operating member N6, and various modifications thereof are possible. There is a bar. Hereinafter, examples of such modifications will be described.

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

In contrast to FIG. 16, according to the present exemplary 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 the present embodiment, when the fourth clutch C4 operates, 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, the shift can be controlled by the operation table as shown in Figure 2, accordingly, to form a speed diagram as shown in Figures 3 to 12 to advance 8 speeds and 2 reverse speeds.

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

In contrast to FIG. 17, according to the present exemplary 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 operates, the second ring gear R2 and the second planet carrier PC2 rotate at the same speed, so that the second planetary gear set PG2 rotates integrally. All.

Therefore, the powertrain of the automatic transmission according to the present embodiment, the shift can be controlled by the operation table as shown in Figure 2, accordingly, to form a speed diagram as shown in Figures 3 to 12 to advance 8 speeds and 2 reverse speeds.

Although the preferred embodiments of the present invention have been described above, the present invention is not limited to the above embodiments, and easily changed and equalized by those skilled in the art from the embodiments of the present invention. It includes all changes to the extent deemed acceptable.

1 is a block diagram of a power train of an automatic transmission according to a first embodiment of the present invention.

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

3 is a speed diagram showing the rotational speed of each operating member at the forward 1 speed of the power train of the automatic transmission according to the embodiments of the present invention.

Figure 4 is a speed diagram showing the rotational speed of each operating member at the second forward speed of the power train of the automatic transmission according to an embodiment of the present invention.

Figure 5 is a speed diagram showing the rotational speed of each operating member at the third forward speed of the power train of the automatic transmission according to an embodiment of the present invention.

Figure 6 is a speed diagram showing the rotational speed of each operating member at the fourth forward speed of the power train of the automatic transmission according to an embodiment of the present invention.

Figure 7 is a speed diagram showing the rotational speed of each operating member at 5 forward speeds of the power train of the automatic transmission according to the embodiment of the present invention.

8 is a speed diagram showing the rotational speed of each operating member at sixth forward speed of the power train of the automatic transmission according to the embodiment of the present invention.

Figure 9 is a speed diagram showing the rotational speed of each operating member at seven forward speeds of the power train of the automatic transmission according to the embodiment of the present invention.

Figure 10 is a speed diagram showing the rotational speed of each operating member at eight forward speeds of the power train of the automatic transmission according to the embodiment of the present invention.

11 is a speed diagram showing the rotational speed of each operating member at the reverse speed 1 of the power train of the automatic transmission according to the embodiment of the present invention.

12 is a speed diagram showing the rotational speed of each operating member at the second reverse speed of the power train of the automatic transmission according to the embodiment of the present invention.

13 is a configuration diagram of a power train of an automatic transmission according to a second embodiment of the present invention.

14 is a configuration diagram of a power train of an automatic transmission according to a third embodiment of the present invention.

15 is a configuration diagram of a power train of an automatic transmission according to a fourth embodiment of the present invention.

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

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

Claims (21)

A first planetary gear set including a first operating member selectively connected to the input shaft, a second operating member selectively connected to the input shaft and selectively stopped, and a third operating member fixedly connected to the output shaft; A second planetary gear set including a fourth operating member fixedly connected to the first operating member, a fifth operating member selectively connected to the third operating member, and a sixth operating member; A third including a seventh operating member fixedly connected to the input shaft, an eighth operating member fixedly connected to the sixth operating member, and a ninth operating member selectively connected to the first operating member and fixedly stopped. Planetary gear sets; 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; A power train of an automatic transmission comprising a. The method of claim 1, The plurality of friction members, A first clutch selectively connecting the input shaft and the first operating member; A second clutch for selectively connecting the input shaft and the second operating member; A third clutch for selectively connecting the third operating member and the fifth operating member; A fourth clutch for integrally rotating the second planetary gear set; A fifth clutch for selectively connecting the first operating member and the ninth operating member; And A first brake for selectively stopping the second operating member; A power train of an automatic transmission comprising a. The method of claim 2, The fourth clutch is a power train of an automatic transmission for selectively connecting the first operating member and the sixth operating member. The method of claim 2, The fourth clutch is a power train of an automatic transmission for selectively connecting the first operating member and the fifth operating member. The method of claim 2, The fourth clutch is a power train of an automatic transmission for selectively connecting the eighth operating member and the fifth operating member. The method of claim 1, The first planetary gear set is a single pinion planetary gear set including a first sun gear, a first planet carrier, and a first ring gear as its operating member, The first sun gear acts as a first actuating member, the first planet carrier acts as a second actuating member, and the first ring gear acts as a third actuating member. . The method of claim 1, The second planetary gear set is a single pinion planetary gear set including a second sun gear, a second planet carrier, and a second ring gear as its operating member, The second sun gear acts as a fourth actuating member, the second planet carrier acts as a fifth actuating member, and the second ring gear acts as a sixth actuating member. . The method of claim 1, The second planetary gear set is a double pinion planetary gear set including a second sun gear, a second ring gear, and a second planet carrier as its operating member. The second sun gear acts as a fourth actuating member, the second ring gear acts as a fifth actuating member, and the second planetary carrier acts as a sixth actuating member. . The method of claim 1, The third planetary gear set is a double pinion planetary gear set including a third sun gear, a third ring gear, and a third planet carrier as its operating member, The third sun gear acts as a seventh actuating member, the third ring gear acts as an eighth actuating member, and the third planetary carrier acts as a ninth actuating member. . The method of claim 2, At the 1st forward speed, the third clutch and the first brake operate. At the 2nd forward speed, the third clutch and the fifth clutch operate. At the 3rd forward speed, the third clutch and the fourth clutch operate. At the 4th forward speed, the first clutch and the third clutch operate At the 5th forward speed, the second clutch and the third clutch operate At the 6th forward speed, the first clutch and the second clutch operate At the 7th forward speed, the second clutch and the fourth clutch operate. At the 8th forward speed, the second clutch and the fifth clutch operate. The fourth clutch and the first brake operate in reverse 1 speed, and A power train of an automatic transmission, characterized in that the first clutch and the first brake operate at reverse second speed. The method of claim 1, The first planetary gear set is a single pinion planetary gear set including a first sun gear, a first planet carrier, and a first ring gear as its operating member, wherein the first sun gear acts as a first actuating member. The first planetary carrier acts as a second actuating member, and the first ring gear acts as a third actuating member; The second planetary gear set is a single pinion planetary gear set including a second sun gear, a second planet carrier, and a second ring gear as its operating member, wherein the second sun gear acts as a fourth operating member. The planetary carrier acts as the fifth actuating member, and the second ring gear acts as the sixth actuating member; The third planetary gear set is a double pinion planetary gear set including a third sun gear, a third ring gear, and a third planet carrier as its operating member, wherein the third sun gear acts as a seventh operating member. And a third ring gear acts as an eighth actuating member, and the third planet carrier acts as a ninth actuating member. The method of claim 11, The plurality of friction members, A first clutch for selectively connecting the input shaft and the first sun gear; A second clutch for selectively connecting the input shaft and the first planet carrier; A third clutch selectively connecting the first ring gear and the second planet carrier; A fourth clutch for integrally rotating the second planetary gear set; A fifth clutch for selectively connecting the first sun gear and the third planet carrier; And A first brake for selectively connecting the first planet carrier and the transmission case; A power train of an automatic transmission comprising a. The method of claim 12, The fourth clutch is a power train of an automatic transmission selectively connecting the first sun gear and the second ring gear. The method of claim 12, The fourth clutch is a power train of an automatic transmission selectively connecting the first sun gear and the second planet carrier. The method of claim 12, The fourth clutch is a power train of an automatic transmission selectively connecting the second planetary carrier and the third ring gear. The method of claim 1, The first planetary gear set is a single pinion planetary gear set including a first sun gear, a first planet carrier, and a first ring gear as its operating member, wherein the first sun gear acts as a first actuating member. The first planetary carrier acts as a second actuating member, and the first ring gear acts as a third actuating member; The second planetary gear set is a double pinion planetary gear set including a second sun gear, a second ring gear, and a second planet carrier as its operating member, wherein the second sun gear acts as a fourth operating member. The second ring gear acts as a fifth actuation member, and the second planetary carrier acts as a sixth actuation member; The third planetary gear set is a double pinion planetary gear set including a third sun gear, a third ring gear, and a third planet carrier as its operating member, wherein the third sun gear acts as a seventh operating member. And a third ring gear acts as an eighth actuating member, and the third planet carrier acts as a ninth actuating member. The method of claim 16, The plurality of friction members, A first clutch for selectively connecting the input shaft and the first sun gear; A second clutch for selectively connecting the input shaft and the first planet carrier; A third clutch selectively connecting the first ring gear and the second ring gear; A fourth clutch for integrally rotating the second planetary gear set; A fifth clutch for selectively connecting the first sun gear and the third planet carrier; And A first brake for selectively connecting the first planet carrier and the transmission case; A power train of an automatic transmission comprising a. The method of claim 17, The fourth clutch is a power train of an automatic transmission selectively connecting the first sun gear and the second planet carrier. The method of claim 17, The fourth clutch is a power train of an automatic transmission selectively connecting the first sun gear and the second ring gear. The method of claim 17, The fourth clutch is a power train of an automatic transmission for selectively connecting the second ring gear and the third ring gear. The method according to claim 12 or 17, wherein At the 1st forward speed, the third clutch and the first brake operate. At the 2nd forward speed, the third clutch and the fifth clutch operate. At the 3rd forward speed, the third clutch and the fourth clutch operate. At the 4th forward speed, the first clutch and the third clutch operate At the 5th forward speed, the second clutch and the third clutch operate At the 6th forward speed, the first clutch and the second clutch operate At the 7th forward speed, the second clutch and the fourth clutch operate. At the 8th forward speed, the second clutch and the fifth clutch operate. The fourth clutch and the first brake operate in reverse 1 speed, and A power train of an automatic transmission, characterized in that the first clutch and the first brake operate at reverse second speed.

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