KR100836098B1 - A 8th-speed power train of an automatic transmission - Google Patents

Abstract

A characteristic configuration of the present invention includes a first sun gear connected to a case via a third brake, a second sun gear connected to an input shaft, a third planet carrier coupled to the second sun gear and connected to an input shaft via a first clutch. A first planetary carrier and a second planetary carrier coupled to the first sun gear and the third planetary carrier and connected to a third planetary carrier and connected to the case via a first brake; and the first planetary carrier and the second planetary carrier A Avenue gear set comprising a first ring gear and a second ring gear coupled to each other; A third sun gear connected to the case via a second brake; a fourth planetary carrier coupled to the third sun gear and connected to the case via a fourth brake; and a first ring gear and a first ring gear coupled to the third sun gear. A double pinion planetary gear set comprising the fifth planetary carrier connected to the second ring gear, the third ring gear coupled to the fourth planetary carrier and the fifth planetary carrier and connected to the case via the fifth brake, and the first ring gear. And a fourth sun gear connected to a second ring gear, a sixth planetary carrier coupled to the fourth sun gear and connected to a third ring gear and connected to an input shaft via a second clutch, and an output shaft coupled to the sixth planetary carrier. It includes a single pinion planetary gear set consisting of a fourth ring gear connected to.

Automatic transmission, 8 forward speeds, planetary gear set, sun gear, clutch, brake

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.

Figure 5 is a graph of the relationship between the operating element and the speed of the eight-speed powertrain 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 B5: 5th brake

C1: first clutch C2: second clutch

DPG: Double Pinion Planetary Gear Set PC1: First Planetary Carrier

PC2: 2nd planetary carrier PC3: 3rd planetary carrier

PC4: 4th planetary carrier PC5: 5th planetary carrier

PC6: 6th planetary carrier R1: 1st ring gear

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

R4: 4th Ring Gear RG: Avenue Gear Set

S1: First Sun Gear S2: Second Sun Gear

S3: Third Sun Gear S3: Third Sun Gear

S4: 4th Sun Gear SPG: Single Pinion 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 speeds and one reverse speed.

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-pinion 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-pinion planetary gear set SPG1 is Variablely fixed to the transmission case 1 through the first brake B1, the first planet carrier PC1 is fixedly connected to the third ring gear R3 of the third single-pinion planetary gear set SPG3. Low output gear (OUT) is installed to operate as an output element.

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

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

In addition, the third sun gear S3 of the third single pinion 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 is connected 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.

In the power train as described above, the first, second, and third ring gears R1, R2, and R3 are connected to the second, third, and first planet carriers PC2, PC3, and PC1, respectively. There is a disadvantage in that the total length of the automatic transmission is separated, which causes a problem that a lot of the transmission weight.

In addition, the output gear 2 is connected to the first planetary carrier PC1 to increase its working torque, thereby causing a problem of reducing the durability of the planetary carrier.

In addition, since the shift stage is limited to six speeds in the related art, there is a limit to improving power performance and fuel consumption rate.

The present invention has been invented to solve the above problems, the object is to install a gear set, a double-pinion planetary gear set and a single pinion planetary gear set to implement a shift stage of 8 forward speed and 1 reverse speed. The present invention provides an eight-speed power train of an automatic transmission that can improve a shifting feeling and shorten a shift time while driving a vehicle, and minimize impact force when a skip shift occurs in which 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 the case via a third brake, a second sun gear directly connected to the input shaft, and a gear coupled to the second sun gear and simultaneously coupled to the second clutch. A first planetary carrier and a second planetary carrier connected to the first planetary gear and the third planetary carrier at the same time, connected directly to the third planetary carrier, and connected to the case via the first brake; A) a gear set comprising a first ring gear and a second ring gear coupled to the first planetary carrier and the second planetary carrier; A third sun gear connected to the case via a second brake; a fourth planetary gear geared to the third sun gear and connected to the case via a fourth brake; and a first ring gear geared to the third sun gear. And a second pinion planetary gear set including a fifth planetary carrier directly connected to the second ring gear, a third ring gear gear-coupled to the fourth planetary carrier and the fifth planetary carrier and connected to the case via a fifth brake. A fourth sun gear connected directly to the first ring gear and the second ring gear, a sixth planetary carrier gear connected to the fourth sun gear and directly connected to the third ring gear, and connected to the input shaft via a second clutch; It includes a single pinion planetary gear set consisting of a fourth ring gear geared to the sixth planetary carrier and directly connected to the output shaft.

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

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 diagram of the operating elements and speed of the eight speed power train according to the present invention. Relationship graph.

As referred to herein, the present invention allows the Avenue Gear Set (RG), Double Pinion Planetary Gear Set (DPG) and Single Pinion Planetary Gear Set (SPG) to be connected to the Case 1 via a plurality of clutches and brakes. It is installed sequentially.

The first gear set S1 connected to the case 1 through the third brake B3 is provided in the rev gear set RG.

Meanwhile, a second sun gear S2 connected directly to the input shaft 3 is provided, and a third planet carrier PC3 is gear-coupled to the second sun gear S2, and the third planet carrier PC3 is formed of a second sun gear S3. It is connected to the input shaft 3 via one clutch C1.

In addition, a first planet carrier PC1 and a second planet carrier PC2 are gear-coupled to the first sun gear S1 and the third planet carrier PC3, and the first planet carrier PC1 and the second planet planet are coupled to each other. The carrier PC2 is directly connected to the third planetary carrier PC3 and is connected to the case 1 via the first brake B1.

In addition, a first ring gear R1 and a second ring gear R2 are gear-coupled to the first planetary carrier PC1 and the second planetary carrier PC2.

The double pinion planetary gear set (DPG) is provided with a third sun gear (S3) connected to the case (1) via a second brake (B2), and the third sun gear (S3) is provided with a fourth planet carrier (PC4). Is gear-coupled, and the fourth planetary carrier PC4 is connected to the case 1 via the fourth brake B4.

In addition, a fifth planetary carrier PC5 is gear-coupled to the third sun gear S3, and the fifth planetary carrier PC5 is directly connected to the first ring gear R1 and the second ring gear R2. It is.

In addition, a third ring gear R3 is gear-coupled to the fourth planetary carrier PC4 and the fifth planetary carrier PC5, and the third ring gear R3 is connected to the fifth brake B5 via a fifth brake B5. It is connected to the case (1).

The single pinion planetary gear set SPG is provided with a fourth sun gear S4 connected directly to the first ring gear R1 and the second ring gear R2.

The sixth planetary carrier PC6 is gear-coupled to the fourth sun gear S4, and the sixth planetary carrier PC6 is directly connected to the third ring gear R3 and simultaneously mediates the second clutch C2. Is connected to the input shaft (3).

On the other hand, the fourth ring gear (R4) is gear-coupled to the sixth planetary carrier (PC6), the fourth ring gear (R4) is directly connected to the output shaft (2).

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 first brake B1, the second brake B2, and the first clutch. It is output through the output shaft 2 after being shifted at the speed of 8 forward speed and 1 reverse speed by any of two operation elements consisting of the third brake B3, the fourth brake B4 and the fifth brake B5. will be.

First, the first brake B1 and the fifth brake B5 are operated when outputted at the first forward speed, and the first brake B1 and the second brake B2 are output when the first brake B1 and the fifth brake B5 are operated. The second brake B2 and the third brake B3 are operated when output at the second forward speed.

On the other hand, the first clutch C1 and the second brake B2 are operated when output at the third forward speed, and the second clutch C2 and the second brake B2 are output when the second clutch C2 is output at the fourth forward speed. The first clutch C1 and the second clutch C2 are operated when output at the fifth forward speed.

In addition, when the sixth forward speed is output, the second clutch C2 and the third brake B3 are operated. When the seventh forward speed is output, the second clutch C2 and the first brake B1 are operated. In the case of outputting at 8 forward speeds, the second clutch C2 and the fourth brake B4 are operated.

As described above, when shifting from forward 1 speed to forward 1 speed or when shifting from 1st forward to 8th forward, one of the two operating elements in each shifting section is kept in operation and changed to the other. 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, any one of the two operating elements maintains an operating state and the transmission section is changed by another change, thereby preventing vibration due to rapid deceleration. will be.

As described above, the present invention reduces the shift time and improves the feeling of shifting when the shifting speed is changed to any one of the two operating elements when shifting from the 1st speed to the 8th speed forward, thereby providing a unique driving environment. There is.

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

Claims (2)

Gear is coupled to the first sun gear S1 connected to the case 1 via the third brake B3, the second sun gear S2 directly connected to the input shaft 3, and the second sun gear S2. The third planetary carrier PC3 coupled to the third planetary carrier PC3 connected to the input shaft 3 via the first clutch C1 and the first sun gear S1 and the third planetary carrier PC3 and at the same time ) And a first planetary carrier (PC1) and a second planetary carrier (PC2) connected directly to the case 1 via a first brake (B1), and the first planetary carrier (PC1) and the second planetary carrier Avenue gear set RG consisting of the first ring gear (R1) and the second ring gear (R2) gear coupled to (PC2); A third sun gear S3 connected to the case 1 via a second brake B2 and a gear connected to the third sun gear S3 and connected to the case 1 via a fourth brake B4. A fourth planetary carrier PC4 and a fifth planetary carrier PC5 gear-connected to the third sun gear S3 and directly connected to the first ring gear R1 and the second ring gear R2; Double pinion planetary gear set (DPG) consisting of a third ring gear (R3) geared to the planetary carrier (PC4) and the fifth planetary carrier (PC5) and connected to the case (1) via the fifth brake (B5) and A fourth sun gear S4 directly connected to the first ring gear R1 and the second ring gear R2 and a fourth sun gear S4 are gear-coupled to the fourth ring gear S4 and directly connected to the third ring gear R3. The sixth planetary carrier PC6 connected to the input shaft 3 via the second clutch C2 and the fourth ring gear R4 geared to the sixth planetary carrier PC6 and directly connected to the output shaft 2. The eight-speed powertrain of the automatic transmission, characterized in that it comprises a single pinion planetary gear set (SPG). The 8-speed power train of an automatic transmission according to claim 1, wherein the rev gear set (RG), double pinion planetary gear set (DPG) and single pinion planetary gear set (SPG) are sequentially installed.

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