KR101338424B1 - Power train of automatic transmission - Google Patents

Abstract

A first planetary gear set including a first actuating member, a second actuating member fixedly connected to the output shaft, and a third actuating member fixedly connected to the input shaft; A second planetary gear set including a fourth operating member selectively connected to the output shaft, a fifth operating member selectively connected to the output shaft, and a sixth operating member fixedly connected to the first operating member; A seventh operating member selectively connected to the input shaft, the fixed first and sixth operating members, and the fifth operating member, an eighth operating member fixedly connected to a transmission case, and fixedly to the fourth operating member. A third planetary gear set including a ninth operating member selectively connected to the output shaft by being connected; And a plurality of friction members selectively connecting the operation members of the first, second and third planetary gear sets, the input shaft, the output shaft, and the transmission case.

Automatic transmission, power train, planetary gear set

Description

POWER TRAIN OF AUTOMATIC TRANSMISSION}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a powertrain of an automatic transmission, and more particularly, to a powertrain of an automatic transmission implementing three forward speeds and one reverse speed using three simple planetary gear sets and five clutches.

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. 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.

SUMMARY OF THE INVENTION Accordingly, the present invention has been made to solve the above-mentioned problems occurring in the prior art, and it is an object of the present invention to provide an automatic transmission that implements forward speeds of 8 speeds and reverse speeds using three simple planetary gear sets and five clutches. Thereby providing a powertrain of the transmission.

According to an aspect of the present invention, there is provided a powertrain of an automatic transmission including a first operating member, A first planetary gear set; A second planetary asset asset including a fourth operating member selectively connected to the output shaft, a fifth operating member selectively connected to the output shaft, and a sixth operating member fixedly connected to the first operating member; A seventh operating member selectively connected to the input shaft, the fixed first and sixth operating members, and the fifth operating member, an eighth operating member fixedly connected to a transmission case, and fixedly to the fourth operating member. A third planetary gear set including a ninth operating member selectively connected to the output shaft by being connected; 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 seventh operating member to the input shaft; A second clutch for selectively connecting the fixedly connected fourth and ninth operating members to the output shaft; A third clutch selectively connecting the fifth operating member to the output shaft; A fourth clutch selectively connecting the fixedly connected first and sixth operating members to the seventh operating member; And a fifth clutch for selectively connecting the fifth operating member to the seventh operating member.

The second and third clutches may be disposed between the second planetary gear set and the third planetary gear set, and the fourth and fifth clutches may be disposed between the first planetary gear sets and the second planetary gear set. have.

The second, third, fourth and fifth clutches 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 first planetary carrier may act as a second actuating member, and the first ring gear may act 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 two planetary carriers may act as the fifth actuating member, and the second ring gear may act 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. The third planetary carrier acts as the eighth actuating member, and the third ring gear can act as the ninth actuating member.

The 2nd and 5th clutches operate at the 1st forward speed, the 2nd and 4th clutches operate at the 2nd forward speed, the 4th and 5th clutches operate at the 3rd forward speed, the 1st and 4th clutches operate at the 4th forward speed, 5 The first and fifth clutches operate in the inside, the first and third clutches operate in the forward sixth speed, the third and fifth clutches operate in the forward seventh speed, the third and fourth clutches operate in the eighth forward speed, and the third and fourth clutches in the reverse first speed The first and second clutches can be operated.

As described above, according to the powertrain of the automatic transmission according to the present invention, three forward planetary gear sets and five planetary gears can be used to implement forward forward speed and reverse 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.

In addition, upshifts and downshifts to all adjacent shifts and skipshifts can be implemented by releasing and engaging only one clutch.

In addition, since all shift stages are implemented by operating only two clutches, the shift between any shift stage and the shift stage can be implemented by releasing and engaging only two clutches.

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

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

The third planetary gear set PG3 is a 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 is fixedly connected to the second ring gear R2. The first planetary carrier PC1 is fixedly connected to the output shaft 20 and serves as an output member at all times. The first ring gear R1 is fixedly connected to the input shaft 10 and always acts as an input member. The second sun gear S2 is fixedly connected to the third ring gear R3. The second planet carrier PC2 is fixedly connected to the transmission case 30 and always serves as a stop member.

The powertrain of the automatic transmission according to the embodiment of the present invention uses five clutches.

The first clutch C1 selectively connects the third sun gear S3 to the input shaft 10. The second clutch C2 selectively connects the fixed second sun gear S2 and the third ring gear R3 to the output shaft 20. The third clutch C3 selectively connects the second planet carrier PC2 to the output shaft 20. The fourth clutch C4 selectively connects the fixed first sun gear S1 and the second ring gear R2 to the third sun gear S3. The fifth clutch C5 selectively connects the second planet carrier PC2 to the third sun gear S3.

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 second and fifth clutches C2 and C5 operate at the first forward speed D1, and the second and fourth clutches C2 and C4 operate at the second forward speed D2 and the third forward speed D3. The fourth and fifth clutches C4 and C5 operate.

The first and fourth clutches C1 and C4 operate at the fourth forward speed D4, and the first and fifth clutches C1 and C5 operate at the fifth forward speed D5 and the first and fourth clutches C1 and C5 operate at the sixth forward speed D6. The first and third clutches C1 and C3 operate.

The third and fifth clutches C3 and C5 operate at the seventh forward speed D7, and the third and fourth clutches C3 and C4 operate at the eighth forward speed D8.

Furthermore, the first and second clutches C1 and C2 operate in the reverse first speed R1.

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 first sun gear S1 is set to the first operating member N1, the first planet carrier PC1 is set to the second operating member N2, and the first ring gear R1. ) Is set as the third operating member N3, the second sun gear S2 is set as the fourth operating member N4, the second planetary carrier PC2 is set as the fifth operating member N5, The second ring gear R2 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 set to the eighth operating member ( N8), and the third ring gear R3 is set to the ninth operating member N9.

3 to 11, the first ring gear R1, which is the third operating member N3, which always acts as an input member, is always rotated at the rotational speed of the input shaft 10. Further, since the first sun gear S1, which is the first operating member N1, 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 sun gear S2, which is the fourth operating member N4, and the third ring gear R3, which is the ninth operating member N9, are fixedly connected, they are always rotated at the same speed. Since the third planetary carrier PC3, which is the eighth operating member N8, is fixedly connected to the transmission case 30, the third planetary carrier PC3 is always stopped.

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

[1st speed forward]

In the forward 1 speed D1, the second and fifth clutches C2 and C5 operate.

By the operation of the second clutch C2, the second operating member N2, which is an output member, has the same speed as the fourth and ninth operating members N4 and N9 that are fixedly connected. In addition, the fifth operating member N5 and the seventh operating member N7 have the same speed by the operation of the fifth clutch C5.

Accordingly, a speed line diagram as shown in Fig. 3 is formed, and the forward first speed D1 is outputted through the second operation member N2 as the output member.

[2 speed forward]

In the second forward speed D2, the second and fourth clutches C2 and C4 operate.

By the operation of the second clutch C2, the second operating member N2, which is an output member, has the same speed as the fourth and ninth operating members N4 and N9 that are fixedly connected. In addition, the sixth operating member N6 and the seventh operating member N7 have the same speed by the operation of the fourth clutch C4.

Accordingly, a speed line diagram as shown in Fig. 4 is formed, and the forward second speed D2 is output through the second operation member N2 as the output member.

[3 speed forward]

In the third forward speed D3, the fourth and fifth clutches C4 and C5 operate.

Therefore, since the fifth and sixth operating members N5 and N6 have the same speed as the seventh operating member N7, the second planetary gear set PG2 rotates integrally. Therefore, since the ninth operating member N9 fixedly connected to the fifth operating member N5 also has the same speed as the seventh operating member N7, the third planetary gear set PG3 rotates integrally. However, since the eighth operating member N8 is always stopped, all of the seventh, eighth and ninth operating members N7, N8 and N9 of the third planetary gear set PG3 are stopped, and the second planetary gear set is similarly stopped. The fourth, fifth and sixth operating members N4, N5 and N6 of PG2 are all stopped.

Therefore, since the first operating member N1 fixedly connected to the sixth operating member N6 is stopped, a speed diagram as shown in FIG. 5 is formed, and is advanced through the second operating member N2 which is an output member. The third speed D3 is output.

[4 forward speed]

At the fourth forward speed D4, the first and fourth clutches C1 and C4 operate.

Since the first clutch C1 operates, the seventh operating member N7 rotates at the same speed as the input shaft 10, so that the speed diagram of the third planetary gear set PG3 is formed as shown in FIG. do.

In addition, the sixth operating member N6 and the seventh operating member N7 have the same speed by the operation of the fourth clutch C4. That is, the sixth operating member N6 is rotated at the same speed as the input shaft 10, so that the speed diagram of the second planetary gear set PG2 is formed as shown in FIG.

Therefore, since the first operating member N1 fixedly connected to the sixth operating member N6 also rotates at the same speed as the input shaft 10, a speed diagram as shown in FIG. 4 forward speed D4 is output through the operation member N2.

[5th forward]

At fifth forward speed D5, the first and fifth clutches C1 and C5 operate.

Since the first clutch C1 is operated, the seventh operating member N7 rotates at the same speed as the input shaft 10, so that the speed diagram of the third planetary gear set PG3 is formed as shown in FIG. do.

In addition, the fifth operating member N5 and the seventh operating member N7 have the same speed by the operation of the fifth clutch C5. That is, the fifth operating member N5 is rotated at the same speed as the input shaft 10, so that the speed diagram of the second planetary gear set PG2 is formed as shown in FIG.

Therefore, since the first operating member N1 fixedly connected to the sixth operating member N6 rotates at a faster speed than the input shaft 10, a speed diagram as shown in FIG. The 5th forward speed D5 is output through 2 operating members N2.

[6th forward]

At 6th forward speed D6, the first and third clutches C1 and C3 operate.

Since the first clutch C1 is operated, the seventh operating member N7 rotates at the same speed as the input shaft 10, so that the speed diagram of the third planetary gear set PG3 is formed as shown in FIG. do.

In addition, the second operating member N2, which is an output member by the operation of the third clutch C3, has the same speed as the fifth operating member N5.

Therefore, the speed diagram as shown in FIG. 8 is formed, and the sixth forward speed D6 is output through the second operating member N2 as the output member.

[7th forward]

At the seventh forward speed D7, the third and fifth clutches C3 and C5 operate.

By the operation of the third clutch C3, the second operating member N2, which is an output member, has the same speed as the fifth operating member N5.

The seventh operating member N7 has the same speed as the fifth operating member N5 by the operation of the fifth clutch C5. Therefore, the second, fifth and seventh operating members N2, N5 and N7 all have the same speed.

Accordingly, a speed line diagram as shown in Fig. 9 is formed, and the forward seventh speed D7 is outputted through the second operation member N2 as the output member.

[8th forward]

At the forward eight speeds D8, the third and fourth clutches C3 and C4 operate.

By the operation of the third clutch C3, the second operating member N2, which is an output member, has the same speed as the fifth operating member N5.

In addition, the sixth operating member N6 and the seventh operating member N7 have the same speed by the operation of the fourth clutch C4.

Accordingly, a speed line diagram as shown in Fig. 10 is formed, and the forward eighth speed D8 is outputted through the second operation member N2 as the output member.

[1 speed reverse]

The first and second clutches C1 and C2 operate in the reverse first speed R1.

Since the first clutch C1 operates, the seventh operating member N7 rotates at the same speed as the input shaft 10, so that the speed diagram of the third planetary gear set PG3 is formed as shown in FIG. do. That is, the ninth operating member N9 rotates at a negative speed.

By the operation of the second clutch C2, the second operating member N2, which is an output member, has the same speed as the fourth and ninth operating members N4 and N9 that are fixedly connected.

Therefore, a speed line diagram as shown in Fig. 11 is formed, and the reverse first speed R1 is outputted through the second operation member N2 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 17, the number of sun gear / ring gear teeth of the second planetary gear set PG2 is 10 and 23, 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 FIG. 1, the second and third clutches C2 and C3 are the second planetary gear set PG2 and the third. The fourth and fifth clutches C4 and C5 are disposed between the planetary gear sets PG3, and the fourth and fifth clutches C4 and C5 are disposed between the first planetary gear sets PG1 and the second planetary gear sets PG2.

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

As shown in FIG. 12, in the powertrain of the automatic transmission according to the second embodiment of the present invention, the second, third, fourth and fifth clutches C2, C3, C4, and C5 are the first, second and third. It is disposed outside the planetary gear sets PG1, PG2 and PG3.

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

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

While the present invention has been described in connection with what is presently considered to be practical exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, And all changes to the scope that are deemed to be valid.

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

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

3 is a speed diagram showing rotational speeds of the respective operating members in the first forward speed of the power train of the automatic transmission according to the embodiment 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.

10 is a speed diagram showing rotational speeds of respective operating members in eight forward speeds of a power train of an automatic transmission according to an embodiment of the present invention.

11 is a speed diagram showing the rotational speeds of the respective operating members in the reverse rotation of the power train of the automatic transmission according to the embodiment of the present invention.

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

Claims (11)

A first planetary gear set including a first actuating member, a second actuating member fixedly connected to the output shaft, and a third actuating member fixedly connected to the input shaft; A second planetary gear set including a fourth operating member selectively connected to the output shaft, a fifth operating member selectively connected to the output shaft, and a sixth operating member fixedly connected to the first operating member; A seventh operating member selectively connected to the input shaft, the fixed first and sixth operating members, and the fifth operating member, an eighth operating member fixedly connected to a transmission case, and fixedly to the fourth operating member. A third planetary gear set including a ninth operating member selectively connected to the output shaft by being connected; 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 according to claim 1, The plurality of friction members, A first clutch selectively connecting the seventh operating member to the input shaft; A second clutch for selectively connecting the fixedly connected fourth and ninth operating members to the output shaft; A third clutch selectively connecting the fifth operating member to the output shaft; A fourth clutch selectively connecting the fixedly connected first and sixth operating members to the seventh operating member; And A fifth clutch for selectively connecting the fifth operating member to the seventh operating member; A power train of an automatic transmission comprising a. 3. The method of claim 2, The second and third clutches are disposed between the second planetary gear set and the third planetary gear set, And the fourth and fifth clutches are disposed between the first planetary gear set and the second planetary gear set. 3. The method of claim 2, And the second, third, fourth and fifth clutches are disposed outside the first, second and third planetary gear sets. The method according to 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 according to 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 according to 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. . 3. The method of claim 2, In the forward 1 speed, the second and fifth clutches operate, The second and fourth clutches operate at the second forward speed, 4th and 5th clutch operate at 3rd forward speed, The first and fourth clutches operate at the fourth forward speed, The first and fifth clutches operate at the fifth forward speed, The first and third clutches operate at six forward speeds, At the forward seventh speed, the third and fifth clutches operate, At the forward eight speeds, the third and fourth clutches operate, and A power train of an automatic transmission, characterized in that the first and second clutches operate in reverse 1 speed. The method according to 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. One planetary carrier acts as a second actuating member, and the first ring gear acts as a third actuating member, Wherein the second planetary gear set is a single pinion planetary gear set including a second sun gear, a second planetary carrier, and a second ring gear as its operating members, the second sun gear serving as a fourth operating member, 2 planetary carrier acts as a fifth operating member, and the second ring gear acts as a sixth operating member, 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. 10. The method of claim 9, The plurality of friction members, A first clutch selectively connecting the third sun gear to the input shaft; A second clutch for selectively coupling the second sun gear and the third ring gear connected to the output shaft; A third clutch selectively connecting the second planetary carrier to the output shaft; A fourth clutch selectively connecting the first sun gear and the second ring gear connected to the third sun gear; And A fifth clutch for selectively connecting the second planet carrier to the third sun gear; A power train of an automatic transmission comprising a. The method of claim 10, In the forward 1 speed, the second and fifth clutches operate, The second and fourth clutches operate at the second forward speed, 4th and 5th clutch operate at 3rd forward speed, The first and fourth clutches operate at the fourth forward speed, The first and fifth clutches operate at the fifth forward speed, The first and third clutches operate at six forward speeds, At the forward seventh speed, the third and fifth clutches operate, At the forward eight speeds, the third and fourth clutches operate, and A power train of an automatic transmission, characterized in that the first and second clutches operate in reverse 1 speed.

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