KR20090132984A - Power train of automatic transmission - Google Patents

Abstract

PURPOSE: A power train of an auto transmission is provided to use effectively the power of an engine with a shift terminal having many stages, thereby improving the power transmission performance and the fuel efficiency. CONSTITUTION: A first planetary gear set(PG1) comprises a first operation member selectively connected to an input shaft and a transmission case, a second operation member and the third operation member selectively connected to the input shaft. A second planet gear set(PG2) comprises a fourth operation member, a fifth operation member fixably connected to the third operation member, and a sixth operation member fixably connected to the input shaft. A third planetary gear set(PG3) comprises a seventh operation member, an eighth operation member, and a ninth operation member. A plurality of friction members interlinks selectively the operation members, input shaft, output shaft, and transmission case of the first, second, and third planetary gear sets.

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 one reverse speed by 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 first reverse speed by 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 the embodiment of the present invention for achieving this object, the first operating member is selectively connected to the input shaft and selectively connected to the transmission case, the second operating member selectively connected to the input shaft, And a first planetary gear set including a third operating member; A second planetary gear set including a fourth operating member, a fifth operating member fixedly connected to the third operating member, and a sixth operating member fixedly connected to the input shaft; A seventh operating member fixedly connected to the fourth operating member and selectively connected to the transmission case, an eighth operating member selectively connected to the fifth operating member and fixedly connected to the output shaft, and the second operating member A third planetary gear set including a ninth operating member fixedly connected to the 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 plurality of friction members may include: a first clutch selectively connecting the input shaft and the second operation member; A second clutch for selectively connecting the input shaft and the first operating member; A third clutch selectively connecting the fifth operating member and the eighth operating member; A fourth clutch for integrally operating the first planetary gear set; A first brake for selectively connecting the seventh operation member and the transmission case; And a second brake for selectively connecting the first operating member and the transmission case.

The fourth clutch may selectively connect the fifth operating member and the ninth operating member. The fourth clutch may selectively connect the first operating member and the second 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 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 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 third planetary gear set is a single pinion planetary gear set including a third sun gear, a third planet carrier, and a third ring gear as its operating member, wherein the third sun gear acts as a seventh operating member. The three planetary carriers may act as the eighth operating member, and the third ring gear may act as the ninth operating member.

The first brake and the second brake operate at the forward 1 speed, the fourth clutch and the first brake operate at the forward 2 speed, the second clutch and the first brake operate at the forward 3 speed, and the third clutch and the third brake at the forward 4 speed. The first brake operates, the first clutch and the first brake operate at the fifth forward speed, the first clutch operates at the sixth forward speed, and one or more clutches of the second, third, and fourth clutches operate, and the first clutch operates at the seventh forward speed. The first clutch and the second brake operate, the third clutch and the second brake operate at the forward eighth speed, and the fourth clutch and the second brake operate at the reverse first speed.

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 planet carrier; A second clutch for selectively connecting the input shaft and the first sun gear; A third clutch selectively connecting the second ring gear and the third planet carrier; A fourth clutch for integrally rotating the first planetary gear set; A first brake for selectively connecting the third sun gear and the transmission case; And a second brake for selectively connecting the first sun gear and the transmission case.

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

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 planet carrier; A second clutch for selectively connecting the input shaft and the first sun gear; A third clutch selectively connecting the second ring gear and the third planet carrier; A fourth clutch for integrally rotating the first planetary gear set; A first brake for selectively connecting the third sun gear and the transmission case; And a second brake for selectively connecting the first sun gear and the transmission case.

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

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 one reverse speed.

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. The first planetary gear PC1 rotates by connecting a first sun gear S1 and a first pinion gear P1 geared to the first ring gear R1.

The second planetary gear set PG2 is a double pinion planetary gear set including a second sun gear S2, a second ring gear R2, and a second planetary carrier PC2 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 single pinion planetary gear set including a third sun gear S3, a third planet carrier PC3, and a third ring gear R3 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 ring gear R2, and the second planet carrier PC2 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 planet carrier PC3, and the third ring gear R3 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 sixth operating member N6 is fixedly connected to the input shaft 10 and always acts as an input member. The eighth operating member N8 is fixedly connected to the output shaft 20 to act as an output member at all times.

The second operating member N2 and the ninth operating member N9 are fixedly connected. The third operating member N3 and the fifth operating member N5 are fixedly connected. The fourth operating member N4 and the seventh operating member N7 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 second operation member N2; A second clutch (C2) for selectively connecting the input shaft (10) and the first operating member (N1); A third clutch (C3) for selectively connecting the fifth operating member (N5) and the eighth operating member (N8); A fourth clutch C4 for integrally operating the first planetary gear set PG1; A first brake (B1) for selectively connecting the seventh operating member (N7) and the transmission case (30); And a second brake (B2) for selectively connecting the first operating member (N1) and the transmission case (30).

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 fifth operating member N5 and the ninth operating member N9. 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 second operating member N2.

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

In the present embodiment, the fourth clutch C4 selectively connects the second ring gear R2 and the third ring gear R3. Therefore, when the fourth clutch C4 is operated, the second ring gear R2 rotates at the same speed as the third ring gear R3, and the first ring gear R1 fixedly connected to the second ring gear R2. ) Rotates at the same speed as the third ring gear (R3). In addition, the first planet carrier PC1 fixedly connected to the third ring gear R3 also rotates at the same speed as the third ring gear R3. Since the first planet carrier PC1 and the first ring gear R1 rotate at the same speed, the first planetary gear set PG1 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 1 reverse speed, and two friction members operate at each shift stage.

That is, the first brake B1 and the second brake B2 operate at the first forward speed D1. In the second forward speed D2, the fourth clutch C4 and the first brake B1 operate. In the third forward speed D3, the second clutch C2 and the first brake B1 operate. At the fourth forward speed D4, the third clutch C3 and the first brake B1 operate. In the fifth forward speed D5, the first clutch C1 and the first brake B1 operate. At the sixth forward speed D6, the first clutch C1 is operated, and at least one of the second, third, and fourth clutches C2, C3, and C4 is operated. At the seventh forward speed D7, the first clutch C1 and the second brake B2 operate. At the eighth forward speed D8, the third clutch C3 and the second brake B2 operate. In the reverse first speed Rev1, the fourth clutch C4 and the second brake B2 operate.

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

3 to 11, the sixth operating member N6, which always acts as an input member, rotates at a rotational speed of the input shaft 10 at all times.

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

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

[1st speed forward]

At the first forward speed D1, the first brake B1 and the second brake B2 operate.

Since the first brake B1 operates, the seventh operating member N7 and the fourth operating member N4 fixedly connected thereto stop. Since the sixth operating member N6 rotates at the rotational speed of the input shaft 10, the speed diagram of the second planetary gear set PG2 is formed as shown in FIG. 3.

Since the third operating member N3 rotates at the same speed as the fifth operating member N5 and the second brake B2 operates, the first operating member N1 stops. Thus, the velocity diagram of the first planetary gear set PG1 is formed as shown in FIG.

In a state where the seventh operating member N7 is stopped, the ninth operating member N9 rotates at the same speed as the second operating member N2.

Accordingly, the speed diagram of the third planetary gear set PG3 is formed as shown in FIG. 3, and the first forward speed D1 is output through the eighth operation member N8, which is an output member.

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

[2 speed forward]

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

Since the first brake B1 operates, the seventh operating member N7 and the fourth operating member N4 fixedly connected thereto stop. Since the sixth operating member N6 rotates at the rotational speed of the input shaft 10, the speed diagram of the second planetary gear set PG2 is formed as shown in FIG. 4.

Since the fourth clutch C4 is operated, the fifth operating member N5, the ninth operating member N9 connected to the fifth operating member N5 through the fourth clutch C4, and the ninth operating member ( The second operating member N2 fixedly connected to N9), and thereby the third operating member N3 fixedly connected to the fifth operating member N5 rotates at the same speed. Since the second operating member N2 and the third operating member N3 rotate at the same speed, the first planetary gear set PG1 rotates integrally as shown in FIG. 4.

In a state where the seventh operating member N7 is stopped, the ninth operating member N9 rotates at the same speed as the fifth operating member N5.

Accordingly, the speed diagram of the third planetary gear set PG3 is formed as shown in FIG. 4, and the second forward speed D2 is output through the eighth operation member N8, which is an output member.

[3 speed forward]

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

Since the first brake B1 operates, the seventh operating member N7 and the fourth operating member N4 fixedly connected thereto stop. Since the sixth operating member N6 rotates at the rotational speed of the input shaft 10, the speed diagram of the second planetary gear set PG2 is formed as shown in FIG. 5.

Since the third operating member N3 rotates at the same speed as the fifth operating member N5 and the second clutch C2 operates, the first operating member N1 rotates at the rotational speed of the input shaft 10. Thus, the velocity diagram of the first planetary gear set PG1 is formed as shown in FIG.

In a state where the seventh operating member N7 is stopped, the ninth operating member N9 rotates at the same speed as the second operating member N2.

Accordingly, the speed diagram of the third planetary gear set PG3 is formed as shown in FIG. 5, and the third forward speed D3 is output through the eighth operation member N8, which is an output member.

[4 forward speed]

At the fourth forward speed D4, the third clutch C3 and the first brake B1 operate.

Since the first brake B1 operates, the seventh operating member N7 and the fourth operating member N4 fixedly connected thereto stop. Since the sixth operating member N6 rotates at the rotational speed of the input shaft 10, the speed diagram of the second planetary gear set PG2 is formed as shown in FIG. 6.

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

Accordingly, the speed diagram of the third planetary gear set PG3 is formed as shown in FIG. 6, and the fourth forward speed D4 is output through the eighth operation member N8, which is an output member.

[5th forward]

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

Since the first brake B1 operates, the seventh operating member N7 stops.

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

Accordingly, the speed diagram of the third planetary gear set PG3 is formed as shown in FIG. 7, and the fifth forward speed D5 is output through the eighth operation member N8, which is an output member.

[6th forward]

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

First, the case where the first clutch C1 and the second clutch C2 operate is described.

Since the first clutch C1 is operated, the second operating member N2 rotates at the same speed as the input shaft 10, and since the second clutch C2 is operated, the first operating member N1 is also connected to the input shaft 10. Rotate at the same speed Therefore, the first planetary gear set PG1 rotates integrally at the rotational speed of the input shaft 10.

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

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

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

Next, the case where the first clutch C1 and the third clutch C3 operate will be described.

Since the first clutch C1 operates, the second operating member N2 rotates at the same speed as the input shaft 10, and the ninth operating member N9 fixedly connected to the second operating member N2 also has an input shaft 10. Rotate at the same speed as). That is, the sixth operating member N6 and the ninth operating member N9 rotate at the same speed.

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

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

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

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

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

Therefore, both the seventh operating member N7 and the fifth operating member N5 fixedly connected to the fourth operating member N4 and the ninth operating member N9 connected to the fifth operating member N5 through the fourth clutch C4 are input shaft 10. Will rotate at the same speed. Therefore, the third planetary gear set PG3 is integrally rotated at the rotational speed of the input shaft 10.

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

[7th forward]

At the seventh forward speed D7, the first clutch C1 and the second brake B2 operate.

Since the first clutch C1 operates, the second operating member N2 rotates at the rotational speed of the input shaft 10. Since the second brake B2 operates, the first operating member N1 stops. Therefore, the velocity diagram of the first planetary gear set PG1 is formed as shown in FIG.

Since the sixth operating member N6 rotates at the rotational speed of the input shaft 10 and the fifth operating member N5 rotates at the same speed as the third operating member N3, the speed of the second planetary gear set PG2 is increased. The diagram is formed as shown in FIG.

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

Accordingly, the speed diagram of the third planetary gear set PG3 is formed as shown in FIG. 9, and the seventh forward speed D7 is output through the eighth operation member N8, which is an output member.

[8th forward]

At the eighth forward speed D8, the third clutch C3 and the second brake B2 operate.

Since the second brake B2 operates, the first operating member N1 stops. Since the third clutch C3 operates, the fifth operating member N5 and the eighth operating member N8 rotate at the same speed.

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

Under these conditions, the speed diagrams of the first, second and third planetary gear sets PG1, PG2 and PG3 by the interaction of the first, second and third planetary gear sets PG1, PG2 and PG3 are shown in FIG. As described above, the eighth forward speed D8 is output through the eighth operation member N8 as the output member.

[1 speed reverse]

In the reverse first speed Rev1, the fourth clutch C4 and the second brake B2 operate.

Since the second brake B2 operates, the first operating member N1 stops. Since the fourth clutch C4 operates, the first planetary gear set PG1 operates integrally. Therefore, the first planetary gear set PG1 stops integrally.

Since the fifth operating member N5 fixedly connected to the third operating member N3 is also stopped, the speed diagram of the second planetary gear set PG2 is formed as shown in FIG. 11 and the fourth operating member N4. ) Is reversed.

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

Accordingly, the speed diagram of the third planetary gear set PG3 is formed as shown in FIG. 11, and the reverse first speed Rev1 is output through the eighth operation member N8, 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 25, the number of sun gear / ring gear teeth of the second planetary gear set PG2 is 10 and 24, respectively, and the third planetary gear The number of sun gear / ring gear teeth of the set PG3 is 10 and 20, 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 double 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 single pinion planetary gear set will be described with reference to FIG. 12.

As shown in FIG. 12, in the power train of the automatic transmission according to the second embodiment, the second planetary gear set PG2 is formed of a single pinion planetary gear set.

3 to 11, 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 ring gear R2, and the second planet carrier PC2. The speed diagram of the automatic transmission is arranged in the order of the second sun gear S2, the second planet carrier PC2, and the second ring gear R2. That is, in FIGS. 3 to 11, 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 planet carrier PC2, and the second ring gear R2 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.

12, the connection relationship applied to the second ring gear R2 that is the fifth operating member N5 in FIG. 1 is the second planetary carrier PC2 that is the fifth operating member N5 in FIG. 12. You can see that it is applied as is). In addition, it is understood that the connection relationship applied to the second planetary carrier PC2 as the sixth operating member N6 in FIG. 1 is applied to the second ring gear R2 as the sixth operating member N6 in FIG. 12 as it is. Can be.

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

In the present embodiment, the fourth clutch C4 selectively connects the third ring gear R3 and the second planet carrier PC2. Therefore, when the fourth clutch C4 is operated, the second planet carrier PC2 rotates at the same speed as the third ring gear R3, and the first ring gear R1 fixedly connected to the second planet carrier PC2. ) Rotates at the same speed as the third ring gear (R3). In addition, the first planet carrier PC1 fixedly connected to the third ring gear R3 also rotates at the same speed as the third ring gear R3. Since the first planet carrier PC1 and the first ring gear R1 rotate at the same speed, the first planetary gear set PG1 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 11 to advance 8 speeds and 1 reverse speed will be implemented.

In the first embodiment of the present invention, the fourth clutch C4 selectively connects the fifth actuating member N5 and the ninth actuating member N9, and various modifications thereof are possible in this regard. have. Hereinafter, examples of such modifications will be described.

Fig. 13 is a block diagram showing a power train of an automatic transmission according to the third embodiment of the present invention.

13, the fourth clutch C4 selectively connects the first operating member N1 and the second operating member N2 according to the present exemplary embodiment. More specifically, the fourth clutch C4 selectively connects the first sun gear S1 and the first planet carrier PC1. 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 first sun gear S1 and the first planet carrier PC1 rotate at the same speed, so that the first planetary gear set PG2 rotates integrally.

Therefore, the powertrain of the automatic transmission according to the present embodiment, 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 11 to advance 8 speeds and 1 reverse speed will be implemented.

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

Referring to FIG. 14, the fourth clutch C4 selectively connects the first operating member N1 and the second operating member N2 according to the present exemplary embodiment. More specifically, the fourth clutch C4 selectively connects the first sun gear S1 and the first planet carrier PC1. 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 first sun gear S1 and the first planet carrier PC1 rotate at the same speed, so that the first planetary gear set PG2 rotates integrally.

Therefore, the powertrain of the automatic transmission according to the present embodiment, 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 11 to advance 8 speeds and 1 reverse speed will be implemented.

In the second embodiment of the present invention, the fourth clutch C4 selectively connects the first actuating member N1 and the sixth actuating member N6, and various modifications thereof are possible in this regard. have. 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 11 to advance 8 speeds and 1 reverse speed will be implemented.

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. .

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 11 to advance 8 speeds and 1 reverse speed will be implemented.

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

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

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

Claims (18)

A first planetary gear set including a first operating member selectively connected to the input shaft and selectively connected to a transmission case, a second operating member selectively connected to the input shaft, and a third operating member; A second planetary gear set including a fourth operating member, a fifth operating member fixedly connected to the third operating member, and a sixth operating member fixedly connected to the input shaft; A seventh operating member fixedly connected to the fourth operating member and selectively connected to the transmission case, an eighth operating member selectively connected to the fifth operating member and fixedly connected to the output shaft, and the second operating member A third planetary gear set including a ninth operating member fixedly connected to the 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; A power train of an automatic transmission comprising a. The method of claim 1, The plurality of friction members, A first clutch for selectively connecting the input shaft and the second operating member; A second clutch for selectively connecting the input shaft and the first operating member; A third clutch selectively connecting the fifth operating member and the eighth operating member; A fourth clutch for integrally operating the first planetary gear set; A first brake for selectively connecting the seventh operation member and the transmission case; And A second brake for selectively connecting the first operating member and the transmission case; 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 fifth operating member and the ninth 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 second 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 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 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 third planetary gear set is a single pinion planetary gear set including a third sun gear, a third planet carrier, and a third ring gear as its operating member, The third sun gear acts as a seventh actuating member, the third planetary carrier acts as an eighth actuating member, and the third ring gear acts as a ninth actuating member. . The method of claim 2, In the forward 1 speed, the first brake and the second brake are operated, 4th clutch and 1st brake operate at 2nd forward speed, At the 3rd forward speed, the second clutch and the first brake operate, At the 4th forward speed, the third clutch and the first brake operate, At the 5th forward speed, the first clutch and the first brake operate, At sixth forward speed, the first clutch operates and at least one of the second, third and fourth clutches operates. At the 7th forward, the first clutch and the second brake actuate, At the 8th forward speed, the third clutch and the second brake operate, A power train of an automatic transmission, characterized in that the fourth clutch and the second brake operate in reverse 1 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 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 single pinion planetary gear set including a third sun gear, a third planet carrier, and a third ring gear as its operating member, wherein the third sun gear acts as a seventh operating member. 3. The planetary carrier acts as an eighth actuating member, and the third ring gear acts as a ninth actuating member. The method of claim 10, The plurality of friction members, A first clutch for selectively connecting the input shaft and the first planet carrier; A second clutch for selectively connecting the input shaft and the first sun gear; A third clutch selectively connecting the second ring gear and the third planet carrier; A fourth clutch for integrally rotating the first planetary gear set; A first brake for selectively connecting the third sun gear and the transmission case; And A second brake for selectively connecting the first sun gear and the transmission case; A power train of an automatic transmission comprising a. The method of claim 11, 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 of claim 11, The fourth clutch is a power train of an automatic transmission selectively connecting the first sun gear and the first planet carrier. 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 single pinion planetary gear set including a third sun gear, a third planet carrier, and a third ring gear as its operating member, wherein the third sun gear acts as a seventh operating member. 3. The planetary carrier acts as an eighth actuating member, and the third ring gear acts as a ninth actuating member. The method of claim 14, The plurality of friction members, A first clutch for selectively connecting the input shaft and the first planet carrier; A second clutch for selectively connecting the input shaft and the first sun gear; A third clutch selectively connecting the second ring gear and the third planet carrier; A fourth clutch for integrally rotating the first planetary gear set; A first brake for selectively connecting the third sun gear and the transmission case; And A second brake for selectively connecting the first sun gear and the transmission case; A power train of an automatic transmission comprising a. The method of claim 15, 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 15, The fourth clutch is a power train of an automatic transmission selectively connecting the first sun gear and the first planet carrier. The method according to claim 11 or 15, In the forward 1 speed, the first brake and the second brake are operated, 4th clutch and 1st brake operate at 2nd forward speed, At the 3rd forward speed, the second clutch and the first brake operate, At the 4th forward speed, the third clutch and the first brake operate, At the 5th forward speed, the first clutch and the first brake operate, At sixth forward speed, the first clutch operates and at least one of the second, third and fourth clutches operates. At the 7th forward, the first clutch and the second brake actuate, At the 8th forward speed, the third clutch and the second brake operate, A power train of an automatic transmission, characterized in that the fourth clutch and the second brake operate in reverse 1 speed.

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