KR20090126971A - Power train of automatic transmission - Google Patents

Abstract

PURPOSE: A power train of automatic transmission is provided to embody the forward 8 speeds and backward 1 speed by using the simple planetary gear set of 3 and clutch of 6. CONSTITUTION: The first planetary gear set(PG1) comprises the first operation member, fixable connected to the input shaft the selectively suspended second operation member, and the third operation member. The second planet gear set(PG2) comprises the sixth operation member selectively connected to the fifth operation member fixable connected to the always fixed fourth operation member, and the third operation member, and the second operation member. The third planetary gear set(PG3) comprises the seventh operation member, fixable connected to the sixth operation member the eighth operation member. Friction members selectively interlink the operation members of the first, second, third planetary gear set the input shaft, and the output shaft and transmission case. The first planetary gear set the single pinion planetary gear set including the first sun gear, and the first planetary carrier and the first ring gear to the 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 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, an object of the present invention is to realize the automatic 8 speed and the reverse 1 speed using three simple planetary gear sets and five clutches. It is to provide the power train of the transmission.

The power train of the automatic transmission according to the embodiment of the present invention for achieving this object, the first planetary member comprising a first operating member fixedly connected to the input shaft, a second operating member that is optionally stopped, a third operating member Gear set; A second planetary gear set including a fixed fourth operating member, a fifth operating member fixedly connected to the third operating member, and a sixth operating member selectively connected to the second operating member; A seventh operating member fixedly connected to the sixth operating member, an eighth operating member selectively connected to the input shaft and optionally connected to the second operating member, and a ninth operating member fixedly connected to the output shaft; A third planetary gear set comprising; 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 friction member selectively connecting the eighth operating member to the input shaft; A second friction member for integrally operating the third planetary gear set; A third friction member selectively connecting the second operating member to the sixth operating member; A fourth friction member selectively connecting the second operating member to the eighth operating member; A fifth friction member for selectively stopping the second operating member; And a sixth friction member for stopping the second planetary gear set integrally.

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

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

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 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 fourth friction member and the fifth friction member operate at the first forward speed, the fourth friction member and the sixth friction member operate at the second forward speed, the second friction member and the fourth friction member operate at the third forward speed, and The first friction member and the fourth friction member operate in the inside, the first friction member and the second friction member operate in the fifth forward speed, the first friction member and the third friction member in the sixth forward motion, and the seventh at the seventh forward speed. The first friction member and the sixth friction member operate, the first friction member and the fifth friction member operate at the eighth forward speed, and the second friction member and the fifth friction member operate at the first reverse speed.

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

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

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

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

As described above, according to the power train of the automatic transmission according to the present invention, three forward planetary gear sets and six clutches 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 planet 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 first sun gear S1 is fixedly connected to the input shaft 10 and always acts as an input member. The first ring gear R1 is fixedly connected to the second ring gear R2. The second planet carrier PC2 is fixedly connected to the third sun gear S3. The third ring gear R3 is fixedly connected to the output shaft 20 to act as an output member at all times. The second sun gear S2 is fixedly connected to the transmission case 30 and always acts as a stop member.

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 third planet carrier PC3 and the input shaft 10; A second clutch C2 for integrally operating the third planetary gear set PG3; A third clutch C3 selectively connecting the first planet carrier PC1 and the second planet carrier PC2; A fourth clutch C4 for selectively connecting the first planet carrier PC1 and the third planet carrier PC3; A first brake (B1) for selectively connecting the first planet carrier (PC1) to the transmission case (30) or the second sun gear (S2) fixed thereto; And a second brake B2 for integrally stopping the second planetary gear set PG2.

In the present embodiment, the second clutch C2 selectively connects the third sun gear S3 and the output shaft 20. However, the protection scope of the present invention should not be understood to be limited thereto. Other connection relationships of the second clutch C2 for integrally operating the third planetary gear set PG3 are possible, which will be described later as a separate embodiment.

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

In the present embodiment, the first brake B1 selectively connects the first planet carrier PC1 to the second sun gear S2 fixed to the transmission case 30, for example, but the protection of the present invention. It should not be understood that the scope is necessarily limited thereto. The first brake B1 may be configured to directly connect the first planet carrier PC1 to the transmission case 30.

In the present embodiment, the second brake B2 selectively connects the third sun gear S3 to the second sun gear S2 fixed to the transmission case 30, for example, but the protection scope of the present invention. Should not be construed as necessarily limited thereto. The first brake B1 may also be configured to directly connect the third sun gear S3 to the transmission case 30.

As shown in FIG. 2, the automatic transmission according to the embodiment of the present invention implements 8 forward speeds and 1 reverse speed, and two friction members operate at each shift stage.

That is, the fourth clutch C4 and the first brake B1 operate at the first forward speed D1. At the second forward speed D2, the fourth clutch C4 and the second brake B2 operate. In the third forward speed D3, the second clutch C2 and the fourth clutch C4 operate. In the fourth forward speed D4, the first clutch C1 and the fourth clutch C4 operate. In the fifth forward speed D5, the first clutch C1 and the second clutch C2 operate. At the sixth forward speed D6, the first clutch C1 and the third clutch C3 operate. At the seventh forward speed D7, the first clutch C1 and the second brake B2 operate. At the eighth forward speed D8, the first clutch C1 and the first brake B1 operate. In the reverse first speed R1, the second clutch C2 and the first brake B1 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.

As described above, in FIGS. 3 to 11, the first sun gear S1 is set to the first operating member N1, and the first planet carrier PC1 is set to the second operating member N2. The first ring gear R1 is set to the third operating member N3, the second sun gear S2 is set to the fourth operating member N4, and the second ring gear R2 is set to the fifth operating member N5. ), The second planetary carrier PC2 is set to the sixth operating member N6, the third sun gear S3 is set to the seventh operating member N7, and the third planetary carrier PC3 is The eighth operating member N8 is set, and the third ring gear R3 is set to the ninth operating member N9.

3 to 11, the first sun gear S1, which is the first operating member N1, which always acts as an input member, is always rotated at the rotational speed of the input shaft 10. Further, since the first ring gear R1, which is the third operating member N3, and the second ring gear R2, which is the sixth operating member N6, are fixedly connected, they always rotate at the same speed. In addition, since the second planet carrier PC2, which is the sixth operating member N6, and the third sun gear S3, which is the seventh operating member N7, are fixedly connected, they are always rotated at the same speed. In addition, since the second sun gear S2, which is the fourth operating member N4, is fixedly connected to the transmission case 30, it is always stopped.

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]

In the first forward speed D1, the fourth clutch C4 and the first brake B1 operate.

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

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

The third sun gear S3 rotates at the same speed as the second planetary carrier PC2. Since the fourth clutch C4 operates while the first planetary carrier PC1 is stopped, the third planetary carrier PC3 operates. Is stopped. Thus, the velocity diagram of the third planetary gear set PG3 is formed as shown in FIG.

Accordingly, the speed diagram as shown in FIG. 3 is formed, and the first forward speed D1 is output through the ninth operating member N9 as the output member.

[2 speed forward]

At the second forward speed D2, the fourth clutch C4 and the second brake B2 operate.

Since the second brake B2 is operated, the third sun gear S3 is stopped.

Since the second planetary carrier PC2 fixedly connected to the third sun gear S3 is also stopped and the second sun gear S2 is always stopped, the speed diagram of the second planetary gear set PG2 is shown in FIG. 4. Formed together. That is, the second planetary gear set PG2 stops integrally.

Therefore, the first ring gear R1 fixedly connected to the second ring gear R2 also stops. At this time, since the first sun gear S1 is rotating at the rotational speed of the input shaft 10, the speed diagram of the first planetary gear set PG1 is formed as shown in FIG.

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

Therefore, the speed diagram as shown in FIG. 4 is formed, and the second forward speed D2 is output through the ninth operating member N9 as the output member.

[3 speed forward]

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

Since the second clutch C2 operates, the third planetary gear set PG3 rotates integrally.

In addition, since the fourth clutch C4 operates, the first planet carrier PC1 rotates at the same speed as the rotation speed of the third planetary gear set PG3.

Accordingly, the speed diagram as shown in FIG. 5 is formed, and the third forward speed D3 is output through the ninth operating member N9 as the output member.

[4 forward speed]

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

Since the first clutch C1 and the fourth clutch C4 operate simultaneously, the first planet carrier PC1 rotates at the rotational speed of the input shaft 10. Therefore, the velocity diagram of the first planetary gear set PG1 is formed as shown in FIG. That is, the first planetary gear set PG1 rotates integrally at the rotational speed of the input shaft 10.

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

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

Therefore, the speed diagram as shown in FIG. 6 is formed, and the fourth forward speed D4 is output through the ninth operating member N9 as the output member.

[5th forward]

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

Since the second clutch C2 operates, the third planetary gear set PG3 rotates integrally. At this time, since the first clutch C1 operates, the third planet carrier PC3 rotates at the rotational speed of the input shaft 10. That is, the third planetary gear set PG3 is integrally rotated at the rotational speed of the input shaft 10. Therefore, since the velocity diagram of the third planetary gear set PG3 is formed as shown in FIG. ) Is output.

Since the second planet carrier PC2 rotates at the same speed as the third sun gear S3, the speed diagram of the second planetary gear set PG2 is formed as shown in FIG. 7. Since the first ring gear R1 rotates at the same speed as the second ring gear R2, the speed diagram of the first planetary gear set PG1 is formed as shown in FIG. 7.

[6th forward]

At the sixth forward speed D6, the first clutch C1 and the third clutch C3 operate.

Since the first clutch C1 operates, the third planet carrier PC3 rotates at the rotational speed of the input shaft 10. In addition, since the third clutch C3 operates, the second planetary carrier PC2 and the third sun gear S3 that are fixedly connected rotate at the same speed as the first planetary carrier PC1.

Therefore, the speed diagram as shown in FIG. 8 is formed, and the sixth forward speed D6 is output through the ninth operating member N9 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 third planet carrier PC3 rotates at the rotational speed of the input shaft 10. In addition, since the second brake B2 is operated, the third sun gear S3 is stopped. 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 ninth operating member N9 as an output member.

At this time, since the second planetary carrier PC2 fixedly connected to the third sun gear S3 is stopped, the second planetary gear set PG2 is integrally stopped and the first ring fixedly connected to the second ring gear R2. Since the gear R1 is stopped, the speed diagram of the first planetary gear set PG1 is formed as shown in FIG.

[8th forward]

At the eighth forward speed D8, the first clutch C1 and the first brake B1 operate.

Since the first brake B1 is operated, the first planet carrier PC1 is stopped and the speed diagram of the first planetary gear set PG1 is formed as shown in FIG. 10.

At this time, since the second ring gear R2 rotates at the same speed as the first ring gear R1, the speed diagram of the second planetary gear set PG2 is formed as shown in FIG. 10.

Since the first clutch C1 operates, the third planet carrier PC3 rotates at the rotational speed of the input shaft 10, and the third sun gear S3 fixedly connected to the second planet carrier PC2 is the second planet carrier. It will rotate at the same speed as (PC2).

Accordingly, the speed diagram of the third planetary gear set PG3 is formed as shown in FIG. 10, and the eighth forward speed D8 is output through the ninth operating member N9 as an output member.

[1 speed reverse]

In the reverse first speed R1, the second clutch C2 and the first brake B1 operate.

Since the first brake B1 is operated, the first planet carrier PC1 is stopped and the speed diagram of the first planetary gear set PG1 is formed as shown in FIG.

At this time, since the second ring gear R2 rotates at the same speed as the first ring gear R1, the speed diagram of the second planetary gear set PG2 is formed as shown in FIG. 11.

Since the second clutch C2 operates, the third planetary gear set PG3 rotates integrally. At this time, the third sun gear S3 fixedly connected to the second planet carrier PC2 rotates at the same speed as the second planet carrier PC2.

Accordingly, the speed diagram as shown in FIG. 11 is formed, and the reverse first speed R1 is output through the ninth operating member N9 as the 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 28, respectively, and the third planetary gear The number of sun gear / ring gear teeth of the set PG3 is 10 and 27, 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 powertrain of the automatic transmission according to the first embodiment of the present invention described above, as shown in Figure 1, the first to fourth clutch (C1, C2, C3, C4) and the first, second brake (B1) At least one friction member of B2) is disposed between the first planetary gear set PG1 and the third planetary gear set PG3.

However, the protection scope of the present invention should not be understood to be limited thereto. Modifications are possible with regard to the arrangement of the clutches. Hereinafter, a power train of an automatic transmission according to a second embodiment of the present invention in which the arrangement of the clutches is modified in comparison with the first embodiment will be described with reference to FIG. 12.

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

Except for this, the configuration of the first, second and third planetary gear sets PG1, PG2 and PG3 and the fixed and variable connection relations of the operating members thereof are the same as in the first embodiment of the present invention.

Therefore, in the powertrain of the automatic transmission according to the second embodiment of the present invention, the shift can be controlled by the operation table as shown in FIG. 2, and thus the speed line diagram as shown in FIGS. By forming the 8 forward speed and 1 reverse speed will be implemented.

In the description of the above-described embodiment, modifications can be made to the friction member for integrally stopping the second planetary gear set PG2, and related to the second clutch for integrally operating the third planetary gear set PG3. It was mentioned that variations are possible.

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

First, as shown in FIG. 13, in the power train of the automatic transmission according to the third embodiment, the second ring gear R2 is a friction member for stopping the second planetary gear set PG2 integrally. ) And a fifth clutch C5 selectively connecting the second planetary carrier PC2 to each other. That is, in the power train of the automatic transmission according to the first embodiment, the second brake B2 is removed and the fifth clutch C5 is added.

Except for these matters, the power train of the automatic transmission according to the present embodiment is the same as the power train of the automatic transmission according to the first embodiment.

In the powertrain of the automatic transmission according to the present embodiment, when the fifth clutch C5 is operated, the second ring gear R2 and the second planet carrier PC2 have the same speed, so that the second planetary gear set PG2 may be used. ) Will work integrally. However, since the second sun gear S2 is always stopped, the second planetary gear set PG2 is stopped integrally by the operation of the fifth clutch C5.

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.

Next, as shown in FIG. 14, in the power train of the automatic transmission according to the fourth embodiment, the third planet carrier PC3 is a friction member for integrally operating the third planetary gear set PG3. And a second clutch C2 for selectively connecting the output shaft 20 to each other. That is, compared to the power train of the automatic transmission according to the first embodiment, the operating members selectively connected to the second clutch C2 among the operating members of the third planetary gear set PG3 are changed.

Except for this matter, the power train of the automatic transmission according to the present embodiment is the same as the power train of the automatic transmission according to the first embodiment.

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

As shown in FIG. 15, the powertrain of the automatic transmission according to the fifth embodiment is characterized by the powertrain of the automatic transmission according to the third embodiment and the powertrain of the automatic transmission according to the fourth embodiment. Equipped with.

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

Except for these matters, the power train of the automatic transmission according to the present embodiment is the same as the power train of the automatic transmission according to the first embodiment.

Thus, 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, according to this 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.

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

Claims (17)

A first planetary gear set including a first operating member fixedly connected to the input shaft, a second operating member selectively stopped, and a third operating member; A second planetary gear set including a fixed fourth operating member, a fifth operating member fixedly connected to the third operating member, and a sixth operating member selectively connected to the second operating member; And a seventh operating member fixedly connected to the sixth operating member, an eighth operating member selectively connected to the input shaft and selectively connected to the second operating member, and a ninth operating member fixedly connected to the output shaft. A third planetary gear set; And A plurality of friction members selectively connecting the operation members of the first, second and third planetary gear sets, the input shaft, the output shaft and the transmission case; A power train of an automatic transmission comprising a. The method of claim 1, The plurality of friction members, A first friction member selectively connecting the eighth operating member to the input shaft; A second friction member for integrally operating the third planetary gear set; A third friction member selectively connecting the second operating member to the sixth operating member; A fourth friction member selectively connecting the second operating member to the eighth operating member; A fifth friction member for selectively stopping the second operating member; And A sixth friction member for stopping the second planetary gear set integrally; A power train of an automatic transmission comprising a. In claim 2, At least one friction member of the first, second, third, fourth, fifth and sixth friction members is disposed between the first planetary gear set and the third planetary gear set. In claim 2, And the first, second, third, fourth, fifth, and sixth friction members are disposed outside the first, second, and third planetary gear sets. 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 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 planet carrier acts as an eighth actuating member, and the third ring gear acts as a ninth actuating member. . The method of claim 2, At the first forward speed, the fourth friction member and the fifth friction member operate. At the second forward speed, the fourth friction member and the sixth friction member are operated. At the third forward speed, the second friction member and the fourth friction member operate. At the fourth forward speed, the first friction member and the fourth friction member operate. At the fifth forward speed, the first friction member and the second friction member are operated. At the sixth forward speed, the first friction member and the third friction member are operated. At the seventh forward speed, the first friction member and the sixth friction member operate, At the eighth forward speed, the first friction member and the fifth friction member operate; The power train of the automatic transmission, characterized in that the second friction member and the fifth friction member is operated at the reverse speed 1. The method of claim 2, The first friction member is a first clutch for selectively connecting the eighth operating member and the input shaft, The second friction member is a second clutch for selectively connecting the seventh operation member and the output shaft, The third friction member is a third clutch for selectively connecting the second operating member and the sixth operating member, The fourth friction member is a fourth clutch for selectively connecting the second operating member and the eighth operating member, The fifth friction member is a first brake selectively connecting the second operation member to the transmission case or the fourth operation member fixed thereto. The sixth friction member is a second brake for selectively connecting the seventh operating member to the transmission case or the fourth operating member fixed thereto. The powertrain of the automatic transmission, characterized in that. The method of claim 2, The first friction member is a first clutch for selectively connecting the eighth operating member and the input shaft, The second friction member is a second clutch for selectively connecting the seventh operation member and the output shaft, The third friction member is a third clutch for selectively connecting the second operating member and the sixth operating member, The fourth friction member is a fourth clutch for selectively connecting the second operating member and the eighth operating member, The fifth friction member is a first brake selectively connecting the second operation member to the transmission case or the fourth operation member fixed thereto. The sixth friction member is a fifth clutch for selectively connecting the sixth operation member and the fifth operation member. The powertrain of the automatic transmission, characterized in that. The method of claim 2, The first friction member is a first clutch for selectively connecting the eighth operating member and the input shaft, The second friction member is a second clutch for selectively connecting the eighth operation member and the output shaft, The third friction member is a third clutch for selectively connecting the second operating member and the sixth operating member, The fourth friction member is a fourth clutch for selectively connecting the second operating member and the eighth operating member, The fifth friction member is a first brake selectively connecting the second operation member to the transmission case or the fourth operation member fixed thereto. The sixth friction member is a second brake for selectively connecting the seventh operating member to the transmission case or the fourth operating member fixed thereto. The powertrain of the automatic transmission, characterized in that. The method of claim 2, The first friction member is a first clutch for selectively connecting the eighth operating member and the input shaft, The second friction member is a second clutch for selectively connecting the eighth operation member and the output shaft, The third friction member is a third clutch for selectively connecting the second operating member and the sixth operating member, The fourth friction member is a fourth clutch for selectively connecting the second operating member and the eighth operating member, The fifth friction member is a first brake selectively connecting the second operation member to the transmission case or the fourth operation member fixed thereto. The sixth friction member is a fifth clutch for selectively connecting the sixth operation member and the fifth operation member. The powertrain of the automatic transmission, characterized in that. 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 13, The plurality of friction members, A first clutch for selectively connecting the third planetary carrier and the input shaft; A second clutch for selectively connecting the third sun gear and the output shaft; A third clutch for selectively connecting the first planetary carrier and the second planetary carrier; A fourth clutch for selectively connecting the first planetary carrier and the third planetary carrier; A first brake selectively connecting the first planet carrier to the transmission case or the second sun gear fixed thereto; And A second brake selectively connecting the third sun gear to the transmission case or the second sun gear fixed thereto; Powertrain of the automatic transmission, characterized in that it comprises a. The method of claim 13, The plurality of friction members, A first clutch for selectively connecting the third planetary carrier and the input shaft; A second clutch for selectively connecting the third sun gear and the output shaft; A third clutch for selectively connecting the first planetary carrier and the second planetary carrier; A fourth clutch for selectively connecting the first planetary carrier and the third planetary carrier; A first brake selectively connecting the first planet carrier to the transmission case or the second sun gear fixed thereto; And A fifth clutch for selectively connecting the second ring gear and the second planet carrier; Powertrain of the automatic transmission, characterized in that it comprises a. The method of claim 13, The plurality of friction members, A first clutch for selectively connecting the third planetary carrier and the input shaft; A second clutch for selectively connecting the third planetary carrier and the output shaft; A third clutch for selectively connecting the first planetary carrier and the second planetary carrier; A fourth clutch for selectively connecting the first planetary carrier and the third planetary carrier; A first brake selectively connecting the first planet carrier to the transmission case or the second sun gear fixed thereto; And A second brake selectively connecting the third sun gear to the transmission case or the second sun gear fixed thereto; Powertrain of the automatic transmission, characterized in that it comprises a. The method of claim 13, The plurality of friction members, A first clutch for selectively connecting the third planetary carrier and the input shaft; A second clutch for selectively connecting the third planetary carrier and the output shaft; A third clutch for selectively connecting the first planetary carrier and the second planetary carrier; A fourth clutch for selectively connecting the first planetary carrier and the third planetary carrier; A first brake selectively connecting the first planet carrier to the transmission case or the second sun gear fixed thereto; And A fifth clutch for selectively connecting the second ring gear and the second planet carrier; Powertrain of the automatic transmission, characterized in that it comprises a.

Images