KR100792571B1 - A 8th-speed power train of an automatic transmission - Google Patents

Abstract

An 8-speed power train of an automatic transmission is provided to prevent an accident by minimizing a shifting vibration by maintaining an operation state of one of manipulation elements during a skip-shift process. A first single planetary gear set(SPG1) includes a first linear gear, a first planetary carrier, and a first ring gear. A second single planetary gear set(SPG2) includes a second linear gear, a second planetary carrier, and a second ring gear. A third single planetary gear set(SPG3) includes a third linear gear, a third planetary carrier, and a third ring gear. The first linear gear is connected to an input shaft. The planetary carrier is gear-coupled with the first linear gear. The first ring gear is gear-coupled with the first planetary carrier. The second linear gear is connected to the first ring gear through a second clutch. The second planetary carrier is gear-coupled with the second linear gear. The second ring gear is connected to the second planetary carrier. The third ring gear is connected to the input shaft through a fourth clutch. The third planetary carrier is directly connected to the output shaft and gear-coupled with the third linear gear. The third ring gear is gear-coupled with the third planetary carrier and directly connected to the second planetary carrier.

Description

8th speed train of automatic transmission {A 8TH-SPEED POWER TRAIN OF AN AUTOMATIC TRANSMISSION}

1 is a schematic diagram showing a conventional six-speed powertrain.

Figure 2 is a table of the operation element of the conventional six-speed powertrain.

3 is a schematic diagram showing an eight-speed powertrain according to the present invention;

Figure 4 is a table of the operating elements of the eight-speed powertrain according to the present invention.

5 is a shift diagram of an eight-speed power train according to the present invention;

6 is a schematic diagram showing an eight-speed power train of another embodiment according to the present invention;

7 is an operating element table of an eight-speed power train of another embodiment according to the present invention.

8 is a shift diagram of an eight-speed power train of another embodiment according to the present invention;

※ Explanation of symbols about main part of drawing ※

1 case 2 output shaft

3: input shaft B1: first brake

B2: Second Brake B3: Third Brake

B4: 4th brake C1: 1st clutch

C2: Second Clutch C3: Third Clutch

C4: fourth clutch C5: fifth clutch

PC1: 1st planetary carrier PC2: 2nd planetary carrier

PC3: 3rd planetary carrier R1: 1st ring gear

R2: 2nd Ring Gear R3: 3rd Ring Gear

S1: First Sun Gear S2: Second Sun Gear

S3: 3rd Sun Gear SPG1: 1st Single Planetary Gear Set

SPG2: Second Single Planetary Gear Set SPG3: Third Single Planetary Gear Set

The present invention relates to an eight-speed power train of an automatic transmission, and more particularly, to an eight-speed power train of an automatic transmission for a vehicle capable of implementing a shift stage of eight forward and backward.

In general, a vehicle is provided with an automatic transmission capable of automatically controlling the traveling speed of the vehicle, and the multi-speed transmission mechanism of the automatic transmission consists of a combination of a plurality of planetary gear sets.

When a plurality of planetary gear sets are combined, the power train performs a function of shifting the multi-stage transmission to the output side when rotation power is input from a torque converter that converts and transmits engine torque.

Since the power train of the automatic transmission has more shift stages, it is advantageous in terms of power performance and fuel consumption rate, and thus, a power train capable of implementing more shift stages is required.

Also, even if the same number of gear stages are implemented, durability, power transmission efficiency, size and weight vary greatly depending on the combination method of the planetary gear set. Therefore, the power train can be more robust and compact while minimizing power loss. Efforts for development are ongoing.

In developing a power train using planetary gear sets, rather than developing any new planetary gear sets, a combination of existing single pinion planetary gear sets, double pinion planetary gear sets, or single and double pinion planetary gear sets The combination of a planet type planetary gear set and the accompanying clutches, brakes, and one-way clutches can be arranged at any position to achieve the desired speed and the gear ratio without any power loss. Various studies are aimed at improving the target.

In particular, in the case of a manual transmission, if there are too many shift stages, the driver should shift frequently. However, in the case of an automatic transmission, the transmission control unit automatically controls the operation of the power train in accordance with the driving state to change the shift. As a practice, developing a power train that can implement more shifts is of great value.

In order to cope with this trend, various studies on the 4th and 5th speed power trains are being conducted, and recently, the power train of the automatic transmission that can realize the 6th forward and 1st speed shift stages has been developed.

As an example, as shown in FIG. 1, three single planetary gear sets SPG1, SPG2, and SPG3 are combined from the front to the rear, and the first sun gear S1 of the first single planetary gear set SPG1 is a transmission case ( 1) is variably fixed through the first brake B1, and the first planet carrier PC1 is fixedly connected to the third ring gear R3 of the third single planetary gear set SPG3. OUT) is mounted to act as an output element.

In addition, the first ring gear R1 of the first single planetary gear set SPG1 is directly connected to the second planet carrier PC2 of the second single planetary gear set SPG2.

The second sun gear S2 of the second single planetary gear set SPG2 is directly connected to the input shaft 3, and the second ring gear R2 is the third planetary gear of the third single pinion planetary gear set SPG3. It is directly connected to the carrier PC3.

Here, the second ring gear R2 and the third planet carrier PC3 are variably connected to the input shaft 3 through the second clutch C2, and at the same time, the transmission case 1 through the second brake B2. Is fixed variably).

The third sun gear S3 of the third single planetary gear set SPG3 is variably connected to the input shaft 3 through the first clutch C1, and at the same time, the transmission case (3) is provided through the third brake B3. It is fixedly fixed to 1).

In this power train, as shown in FIG. 2, the first brake B1 and the second brake B2 operate at the first forward speed, and the first brake B1 and the third brake B3 operate at the second forward speed. The first brake B1 and the first clutch C1 are operated at the third forward speed, and the first brake B1 and the second clutch C2 are operated at the fourth forward speed, and the first and second clutches are operated at the fifth forward speed. C1) (C2) is operated, the second clutch C2 and the third brake B3 are operated at the forward 6 speed, and the first clutch C1 and the second brake B2 are operated at the reverse speed 1, and the drive forward 6 is performed. This will realize the gearshift of the speed 1 and the speed 2 reverse.

However, such a conventional apparatus is limited to six speeds, so that there is a limit to improving power performance and fuel consumption.

The present invention has been invented to solve the above problems, the object of which is to use a plurality of single planetary gear set to implement a shift stage of 8 forward speed and 1 reverse speed or 8 forward speed and 2 reverse speed while driving the vehicle. The present invention provides an eight-speed power train of an automatic transmission that can improve the feeling of shifting and shorten the shifting time, as well as minimize the impact force when a skip shift occurs when the speed of the vehicle is drastically reduced.

Referring to the characteristic configuration of the present invention for achieving the above object is as follows.

The eight-speed power train of the automatic transmission according to the present invention includes a first sun gear connected to an input shaft, a first planet carrier geared to the first sun gear and connected to a case via a second brake, and the first planet carrier (0 to 0). A first single planetary gear set comprising a first ring gear gear-coupled to a case via a first brake; a first clutch connected to the first planet carrier by a first clutch, and a first clutch connected to the first ring gear by a second clutch; A second sun gear connected to the case via a fourth brake; a second planet carrier geared to the second sun gear and connected to the case via a third brake; and directly connected to the output shaft connected to the second planet carrier. A second single planetary gear set including a second ring gear connected to the second shaft, a third sun gear connected to the input shaft via a fourth clutch, and a third gear gear coupled to the third sun gear and directly connected to the output shaft. And a third single planetary gear set consisting of a third planetary carrier and a third ring gear connected to an input shaft via a third clutch while being geared to the third planetary carrier and directly connected to the second planetary carrier.

In addition, the eight-speed powertrain of the automatic transmission according to another embodiment of the present invention includes a first sun gear connected to an input shaft, a first planetary carrier gear connected to the first sun gear and connected to a case via a second brake, and the first gear. A first planetary gear set, comprising: a first planetary gear set geared to 0 and connected to a case via a first brake; a first planetary gear set connected to the case; a first clutch and a third clutch connected to the first planetary carrier; A second sun gear connected to the first ring gear via the second clutch and the third clutch and connected to the case via the fourth brake and the third clutch, and gear-coupled to the second sun gear and connected to the case via the third brake. A second single planetary gear set comprising a second planetary carrier connected to the second planetary carrier, the second planetary gear set geared to the second planetary carrier and directly connected to the output shaft, and a fifth clutch connected to the input shaft. A three-wire gear, a third planetary gear geared to the third sun gear and directly connected to the output shaft, a third planetary gear geared to the third planetary carrier and a second planetary carrier connected directly to the second planetary carrier, and a fourth clutch connected to the input shaft. It includes the third single pinion planetary gear set consisting of a third ring gear connected to the third clutch via the fourth clutch.

Referring to the present invention having such characteristics in detail as follows.

Example 1

Figure 3 is a schematic diagram showing an eight speed power train according to the present invention, Figure 4 is an operating element table of the eight speed power train according to the present invention, Figure 5 is a shift diagram of the eight speed power train according to the present invention.

As referred to herein, the first single planetary gear set SGP1, the second single planetary gear set SGP2, and the third single planetary gear set SGP3 are sequentially installed.

The first single planetary gear set SGP1 is provided with a first sun gear S1 directly connected to the input shaft 3, and the first sun gear S1 is gear-coupled to the first sun gear S1. The second planetary carrier PC2 is connected to the case 1 via a second brake B2.

A first ring gear R1 is gear-coupled to the first planetary carrier PC1, and the first ring gear R1 is connected to the case 1 via a first brake B1.

The second single planetary gear set (SPG2) is provided with a second sun gear (S2), the second sun gear (S2) is connected to the first planetary carrier (PC1) via the first clutch (C1), The second planetary carrier PC2 is gear-coupled to the second sun gear S2, and the second planetary carrier PC2 is connected to the case 1 via the third brake B3.

In addition, a second ring gear R2 is gear-coupled to the second planetary carrier PC2, and the second ring gear R2 is directly connected to the output shaft 2.

The third single planetary gear set SPG3 is provided with a third sun gear S3, and the third sun gear S3 is connected to the input shaft 3 via a fourth clutch C4, and the third The third planetary carrier PC3 is gear-coupled to the sun gear S3, and the third planetary carrier PC3 is directly connected to the output shaft 2.

Meanwhile, a third ring gear R3 is gear-coupled to the third planet carrier PC3, and the third ring gear R3 is directly connected to the second planet carrier PC2 and at the same time a third clutch C3. Is connected to the input shaft (3).

Referring to the present invention configured as described in detail as follows.

As shown in FIGS. 4 and 5, the rotational force of the power input through the input shaft 3 may include the first clutch C1, the second clutch C2, the third clutch C3, the fourth clutch C4, and the first clutch. Shifting at 8 forward speed and 1 reverse speed by any two or three of the operating elements consisting of the first brake B1, the second brake B2, the third brake B3 and the fourth brake B4. After being output through the output shaft (2).

First, the second clutch C2, the second brake B2, and the third brake B3 are operated when output at the first speed in reverse, and the first clutch C1, when output at the first speed in forward. The fourth clutch C4 and the first brake B1 are operated. When the second clutch is output at the second forward speed, the fourth clutch C4 and the third brake B3 are operated. In this case, the first brake B1 is operated. ) Is irrelevant.

On the other hand, when output at the third forward speed, the fourth clutch C4 and the fourth brake B4 are operated. In this case, the operating state of the first brake B1 is irrelevant, and when output at the fourth forward speed, The second clutch C2, the fourth clutch C4 and the second brake B2 are operated, and when the output is performed at five forward speeds, the third clutch C3 and the fourth clutch C4 are operated. In this case, the operating state of the second brake B2 is irrelevant.

In addition, when the sixth forward speed is output, the second clutch C2, the third clutch C3, and the second brake B2 are operated. When the seventh forward speed is output, the third clutch C3 and The fourth brake B4 is operated, and the operating state of the second brake B2 is irrelevant.

In addition, when output at 8 forward speeds, the first clutch C1, the third clutch C3, and the first brake B1 are operated.

As described above, when shifting from 1 forward speed to 8 forward speeds, any one of two or three operating elements in each shifting section is changed without changing the shift section so that the shift time can be shortened. Of course, it is also possible to improve the transmission to the driver.

In addition, during a skip shift operation in which the shift section is changed to two sections due to rapid deceleration while driving the vehicle, at least one operating element is changed so that the shift section is changed, thereby preventing vibration due to rapid deceleration.

Example 2

Figure 6 is a schematic diagram showing an eight speed powertrain of another embodiment according to the present invention, Figure 7 is an operating element table of an eight speed power train of another embodiment according to the present invention, and Figure 8 is an eighth embodiment of another embodiment according to the present invention. This is the shift diagram of the power train.

As referred to herein, the first single planetary gear set SGP1, the second single planetary gear set SGP2, and the third single planetary gear set SGP3 are sequentially installed.

The first single planetary gear set SGP1 is provided with a first sun gear S1 directly connected to the input shaft 3, and the first sun gear S1 is gear-coupled to the first sun gear S1. The second planetary carrier PC2 is connected to the case 1 via a second brake B2.

A first ring gear R1 is gear-coupled to the first planetary carrier PC1, and the first ring gear R1 is connected to the case 1 via a first brake B1.

A second sun gear S2 is provided in the second single planetary gear set SPG2, and the second sun gear S2 is formed of a first planetary carrier (C1) through a first clutch C1 and a third clutch C3. PC1), connected to the first ring gear R1 via the second clutch C2 and the third clutch C3, and simultaneously connected to the fourth brake B4 and the third clutch C3. It is connected to (1).

In addition, a second ring gear R2 is gear-coupled to the second planetary carrier PC2, and the second ring gear R2 is directly connected to the output shaft 2.

The third single planetary gear set SPG3 is provided with a third sun gear S3, which is connected to the input shaft 3 via a fifth clutch C5, and the third sun gear S3 is provided. The third planetary carrier PC3 is gear-coupled to the sun gear S3, and the third planetary carrier PC3 is directly connected to the output shaft 2.

Meanwhile, a third ring gear R3 is gear-coupled to the third planet carrier PC3, and the third ring gear R3 is directly connected to the second planet carrier PC2 and at the same time, the fourth clutch C4. Is connected to the input shaft (3).

Referring to the present invention configured as described in detail as follows.

As shown in FIGS. 7 and 8, the rotational force of the power input through the input shaft 3 may include the first clutch C1, the second clutch C2, the third clutch C3, the fourth clutch C4, and the fourth clutch. Eight forward speeds by any two or three of the operating elements consisting of five clutches C5, first brake B1, second brake B2, third brake B3 and fourth brake B4 And it is output through the output shaft (2) after being shifted at the speed of the reverse 1 speed.

First, the third clutch C3 and the third brake B3 are operated when the output is performed at the reverse 1 speed, and the second clutch C2, the second brake B2 and the second clutch C3 are output when the output is performed at the reverse 2 speed. The third brake B3 is activated.

When the first clutch C1, the fifth clutch C5, and the first brake B1 are operated when output at the first forward speed, the fifth clutch C5 and the first clutch C5 when the second clutch is output at the second forward speed. The third brake B3 is operated, and the operating state of the first brake B1 is irrelevant.

On the other hand, when output at the third forward speed, the fifth clutch C5 and the fourth brake B4 are operated. In this case, the operating state of the first brake B1 is irrelevant, and when output at the fourth forward speed, The second clutch C2, the fifth clutch C5 and the second brake B2 are operated, and the fourth clutch C4 and the fifth clutch C5 are operated when output at the five forward speeds. At this time, the operating state of the second brake (B2) is irrelevant.

In addition, when output at the sixth forward speed, the second clutch C2, the fourth clutch C4, and the second brake B2 are operated. When the output is performed at the seventh forward speed, the fourth clutch C4 and The fourth brake B4 is operated, and the operating state of the second brake B2 is irrelevant.

In addition, when output at 8 forward speeds, the first clutch C1, the fourth clutch C4, and the third brake B3 are operated.

As described above, when shifting to reverse 1 and reverse 2 speeds and shifting from 1 to 8 forward 8 speeds, one of the two or three operating elements in each shifting section remains unchanged. Since the shift section is changed, the shift time can be shortened, and the shift feeling delivered to the driver can be improved.

In addition, during a skip shift operation in which the shift section is changed to two sections due to rapid deceleration while driving the vehicle, at least one operating element is changed so that the shift section is changed, thereby preventing vibration due to rapid deceleration.

As described above, the present invention reduces the shift time and improves the feeling of shifting since at least one operating element is shifted in an unchanged state when shifting from 1 to 8 forward speeds, thereby providing a comfortable driving environment. Has the effect of.

In addition, the present invention is to maintain the operating state of any one of the plurality of operating elements during the skip shift operation due to rapid deceleration during the vehicle driving has a unique effect of minimizing the vibration generated in the automatic transmission to prevent safety accidents in advance have.

Claims (4)

A first planetary gear S1 connected to the input shaft 3, a first planetary carrier PC1 geared to the first sun gear S1 and connected to the case 1 via a second brake B2, and the A first single planetary gear set (SPG1) consisting of a first ring gear (R1) geared to the first planetary carrier (PC1) and connected to the case (1) via a first brake (B1); The first planetary carrier PC1 is connected to the first clutch C1 via the second clutch C2, and the first ring gear R1 is connected to the first planetary carrier PC1 via the fourth brake B4. A second sun gear S2 connected to 1), a second planetary carrier PC2 gear-coupled to the second sun gear S2 and connected to the case 1 via a third brake B3, and the second A second single planetary gear set SPG2 connected to the planetary carrier PC2 and including a second ring gear R2 connected directly to the output shaft 2; And A third sun gear S3 connected to the input shaft 3 via a fourth clutch C4, a third planetary carrier PC3 geared to the third sun gear S3 and directly connected to the output shaft 2; And a third ring gear (R3) gear-coupled to the third planetary carrier (PC3) and directly connected to the second planetary carrier (PC2) and connected to the input shaft (3) via the third clutch (C3). 8-speed powertrain of automatic transmission, characterized by three single planetary gear sets (SPG3). The 8-speed power train of an automatic transmission according to claim 1, wherein the first single planetary gear set (SPG1), the second single planetary gear set (SGP2) and the third single planetary gear set are sequentially installed. A first planetary gear S1 connected to the input shaft 3, a first planetary carrier PC1 geared to the first sun gear S1 and connected to the case 1 via a second brake B2, and the A first single planetary gear set (SPG1) consisting of a first ring gear (R1) geared to the first planetary carrier (0) and connected to the case (1) via a first brake (B1); A first ring gear R1 is connected to the first planet carrier PC1 via a first clutch C1 and a third clutch C3 and is connected to a second clutch C2 and a third clutch C3. A second sun gear S2 connected to the case 1 via a fourth brake B4 and a third clutch C3, and gear-coupled to the second sun gear S2, and the third brake B3. The second single planetary planet consisting of a second planetary carrier (PC2) connected to the case (1) and a second ring gear (R2) gear-coupled to the second planetary carrier (PC2) directly connected to the output shaft (2) via Gear set SPG2; And A third sun gear S3 connected to the input shaft 3 via a fifth clutch C5, a third planetary carrier PC3 geared to the third sun gear S3 and directly connected to the output shaft 2; And gear-coupled to the third planetary carrier PC3 and directly connected to the second planetary carrier PC2 and connected to the input shaft 3 via the fourth clutch C4 and mediate the fourth clutch C4. And a third single planetary gear set (SPG3) consisting of a third ring gear (R3) connected to the third clutch (C3) to the eighth speed train of the automatic transmission. 4. The eight-speed power train of an automatic transmission according to claim 3, wherein the first single planetary gear set (SPG1), the second single planetary gear set (SGP2) and the third single planetary gear set are sequentially installed.

Images