KR100623779B1 - A 6th-SPEED POWER TRAIN OF AN AUTOMATIC TRANSMISSION FOR A VEHICLE - Google Patents

Abstract

The present invention improves the power transmission efficiency by applying a single pinion planetary gear set and the Lavigny planetary gear set so that the entire gear of the Lavender planetary gear set includes a direct connection in the state where the input shaft power is input at the same speed ratio. At the same time, it provides a six-speed power train of an automatic transmission for a six-speed forward and one-speed vehicle for maximizing power transmission efficiency in a high speed stage of five or more speeds.

Automatic transmission. clutch. Planetary gear set, power train, 6 speed

Description

A 6th-SPEED POWER TRAIN OF AN AUTOMATIC TRANSMISSION FOR A VEHICLE}

1 is a schematic diagram of a power train according to an embodiment of the present invention;

2 is an operating element table of a power train according to an embodiment of the present invention;

3 is a shift diagram of a power train according to an embodiment of the present invention;

4 is a schematic diagram of a conventional power train,

5 is a table of operating elements of a conventional power train, and

6 is a shift diagram of a conventional power train.

The present invention relates to a six-speed power train of an automatic transmission for a vehicle that is applied to an automatic transmission for a vehicle to realize a sixth forward speed and one reverse speed.

For example, the multi-speed gear mechanism of an automatic transmission is composed of a combination of a plurality of planetary gear sets, and a power train in which the plurality of planet gear sets is combined, when a rotational power is input from a torque converter that converts and transmits engine torque, is transmitted. It performs the function of transmitting to the output side by shifting to multiple stages.

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.

Thus, in developing a power train using a planetary gear set, a new planetary gear set is not developed, but a single pinion planetary gear set, a double pinion planetary gear set, or a single and double pinion planetary gear set. How to combine the planetary gear set of the combination type, and the accompanying clutch, brake, and one-way clutch to place a few in any position to implement the desired gear stage and the corresponding gear ratio without possible power loss Various studies are underway with the goal of improving performance.

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 result, developing a power train that can implement more shifts is of great value.

In order to cope with this trend, various researches on 4 speed and 5 speed power trains are being conducted. In addition, recently, a power train of an automatic transmission capable of implementing 6 speed forward and 1 speed reverse gears has been provided.

As an example, as shown in FIG. 4, one single pinion planetary gear set (SPG) is combined with one rib type planetary gear set (LPG) in the rear, and a single pinion planetary gear set (SPG) is used. The first sun gear S1 is fixed to the transmission housing 1, and the output gear OUT is mounted on the second ring gear R2 (R3) of the planetary gear set LPG. Will work.

The first ring gear R1 of the single pinion planetary gear set SPG is directly connected to the input shaft 3 and connects the second and third planetary gears P2 and P3 of the planetary gear set LPG. Three planetary carriers PC3 are variably connected to the input shaft 3 via a third clutch C3.

Further, the first planet carrier PC1 connecting the first planetary gear P1 of the single pinion planetary gear set SPG may have a first clutch between the third sun gear S3 of the rib planetary gear set LPG. They are variably connected to each other via (C1), which in turn are variably connected to each other via a second clutch (C2) between the second sun gear (S2).

In addition, the second sun gear S2 is variably fixed to the transmission housing 1 through the second brake B2 and connects only the second planetary gear P2 of the rib planetary gear set LPG. The second planetary carrier PC2 is variably connected to the transmission housing 1 via a first brake B1 disposed in parallel with the second brake B2 in the transmission housing 1.

As illustrated in FIG. 5, the power train operates the first clutch C1 and the first brake B1 at the first forward speed, and the first clutch C1 and the second brake B2 at the second speed. The first clutch C1 and the second clutch C2 operate in the third speed.

In the fourth speed, the first clutch C1 and the third clutch C3 are operated. In the fifth speed, the second and third clutches C2 and C3 are operated. In the sixth speed, the third clutch C3 and the third clutch are operated. The second brake B2 is operated, and the second clutch C2 and the first brake B1 are operated at the reverse shift stage, thereby implementing a shift stage of 6 forward speed and 1 reverse speed as shown in FIG. 6. .

However, in the power train as described above, as shown in FIG. 6, a gear stage in which three planet gears are powered and rotated is one second gear stage, and a gear stage in which two planet gears are powered and rotates is a first gear stage. The fourth gear and the fifth gear are three, and only one planetary gear is powered by two gears, which are rotated while the third gear and the sixth gear are rotated.

In other words, this is because the planetary gear set LPG, in which the output element is implemented, excludes the shift stages in which all planetary gears are directly connected to each other, that is, the input shaft 3 always decelerated from the single pinion planetary gear set SPG. In the high-speed stage of 5th speed or more, the power loss due to the rolling efficiency of the gear is increased in terms of the power transmission efficiency of the overall automatic transmission.

Accordingly, the present invention has been invented to solve the above problems, the object of the present invention is to apply a single pinion planetary gear set and a rabinyu planetary gear set in the state of receiving the power of the input shaft at the same speed ratio in the rabinyu planet The 6-speed power train of the automatic transmission for the 6th forward and 1st speed vehicle for improving the power transmission efficiency by maximizing the power transmission efficiency by including the direct gear of the gear set at the same time. To provide.

In order to realize the above object, the power train of the present invention is a six-speed power train of an automatic transmission for a vehicle formed by combining a double pinion planetary gear set and a lavender planetary gear set.

In the double pinion planetary gear set, the first sun gear is directly connected to the transmission case and fixed, and one side of the first planet carrier is directly connected to the input shaft.

The above-mentioned planetary planetary gear set has a second sun gear variably connected to the first planet carrier via a first clutch, and is simultaneously fixed to a transmission case through a second brake, and the third sun gear is double-pinion. A third planet carrier connected to the first ring gear of the planetary gear set through a third clutch, and the third planet carrier rotatably fixing the second planetary gear and the third planetary gear is variably through the second clutch on the input shaft. Connected to the first brake and the one-way clutch which are configured in parallel to the transmission case, and the second ring gear is configured as an output element, and the sixth forward speed is controlled by the operation control of the operation element composed of the clutch and the brakes. And it is characterized in that it is combined to implement the speed shift stage of the reverse 1 speed.

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

Figure 1 schematically shows an embodiment of the power train according to the present invention, in which the power train of the present invention has one double pinion planetary gear set with respect to the input shaft 3 connected to the engine output side via a torque converter. (DPG) and Lv. Planetary Gearsets (LPG) are combined to achieve a sixth forward and one reverse speed.

The double pinion planetary gear set DPG includes a first sun gear S1, a first ring gear R1, and two first gears meshed between the first sun gear S1 and the first ring gear R1. The first planetary carrier PC1 for rotatably supporting the planetary gear P1 is configured on both sides.

The planetary planetary gear set LPG includes a second sun gear S2, a third sun gear S3, a second ring gear R2 (R3), these second and third sun gears S2, S3 and a second. The third planetary carrier PC3 for rotatably supporting the second planetary gear P2 and the third planetary gear P3 meshed between the ring gears R2 (R3) is configured on one side.

In the arrangement of the double pinion planetary gear set (DPG) and the rib planetary gear set (LPG), the double pinion planetary gear set (DPG) is disposed on the front side of the transmission, and the rear planetary gear set (LPG) is disposed on the rear side of the transmission. The output gear OUT GEAR is disposed between the double pinion planetary gear set DPG and the rib planetary gear set.

First, the double pinion planetary gear set DPG has a first sun gear S1 directly fixed to the transmission case 1 to operate as a variable fixing element, and one side of the first planet carrier PC1 has an input shaft 3. ) Is composed of input elements.

In addition, the lavender planetary gear set LPG has a second sun gear S2 variably connected to the other side of the first planetary carrier PC1 of the double pinion planetary gear set DPG through the first clutch C1. At the same time, the second sun gear S2 is variably connected to the transmission case 1 through the second brake B2 and is configured to operate as a variable fixing element.

In addition, the rib planetary gear set LPG has a third sun gear S3 variably connected to the first ring gear R1 of the double pinion planetary gear set DPG through a third clutch C3. .

The third planetary carrier PC3 rotatably fixing the second planetary gear P2 and the third planetary gear P3 is variably connected to the input shaft 3 through a second clutch C2 to enable variable input. It is composed of elements, and at the same time connected to the first brake (B1) and one-way clutch (OWC) configured in parallel to the transmission case (1) is also composed of a constant fixing in one direction and a variable fixing element in the other direction.

On the other hand, the second ring gear (R2 (R3)) is connected to the output gear disposed in the outer side of the planetary gear set LPG is composed of an output element.

In the configuration of the six-speed power train, the double pinion planetary gear set DPG is six types of input paths including first, second, second, third, fourth, fifth and sixth input paths. Power is transmitted through the input shaft.

That is, in the first input path and the second speed, the first sun gear S1 is operated by the operation of the third clutch C3 connecting the first ring gear R1 to the third sun gear. Is operated as a fixed element to input the power of the input shaft (3) to the third sun gear (S3) via the first ring gear (R1) as a reduction ratio.

At the third speed, the second input path may include a third clutch C3 and the first planet carrier PC1 connecting the first ring gear R1 to the third sun gear S3 to the second sun gear S2. ) And the first clutch C1 which is variablely connected at the same time to operate the first sun gear S1 as a fixed element to the third sun gear S3 through the first ring gear R1 of the input shaft 3. The power is input at a reduction ratio, and at the same time, the power of the input shaft 3 is input at the same speed ratio to the second sun gear S2 through the first planet carrier PC1.

The third input path has a third clutch C3 connecting the first ring gear R1 to the third sun gear S3 and a third planet carrier PC3 at the fourth speed, and receives the third shaft C3. And second clutch C2 variablely connected to each other are operated at the same time, so that the first sun gear S1 is operated as a fixed element so that the power of the input shaft 3 is applied to the third sun gear S3 through the first ring gear R1. Is inputted as a reduction ratio, and at the same time, the third planetary carrier PC3 and the input shaft 3 are connected to input the power of the input shaft 3 at the same speed ratio.

The fourth input path includes a first clutch C1 and a third planet carrier PC3 that variably connect the first planet carrier PC1 to the second sun gear S2 at a fifth speed. And second clutch C2 which are variablely connected to each other operate simultaneously to input the power of input shaft 3 to the second sun gear S2 at the same speed ratio through the first planetary carrier PC1 and at the same time, the third planetary carrier PC3 and the input shaft 3 are connected so that the power of the input shaft 3 is input at the same speed ratio.

At the sixth speed, the fifth input path may further include a third planetary gear set LPG configured to be operated by a second clutch C2 that variably connects the third planet carrier PC3 to the input shaft 3. The planetary carrier PC3 and the input shaft 3 are connected so that the power of the input shaft 3 is input only at the same speed ratio.

The sixth input path passes through the first planet carrier PC1 by an operation of the first clutch C1 that variably connects the first planet carrier PC1 with the second sun gear S2 at a reverse first speed. To input the power of the input shaft 3 to the second sun gear S2 only at the same speed ratio.

As for each brake and each clutch which are the operating elements of the power train comprised as mentioned above, as shown in the operating element table of FIG. 2, the 3rd clutch C3 and the one-way clutch OWC are operated-controlled by the 1st speed, In the second speed, the second brake B2 is operated and controlled in the state of the first speed, and in the third speed, the first clutch C1 is operated and controlled while the second brake B2 is released in the state of the second speed.

In the fourth speed stage, the second clutch C2 is operated and controlled while the first clutch C1 is released in the third speed stage, and the third clutch C3 is released in the fourth speed stage in the fifth speed stage. The first clutch C1 is operated and controlled, and the second brake B2 is operated while the first clutch C1 is released in the state of the fifth speed at the sixth speed.

In addition, the first clutch C1 and the first brake B1 operate at the first speed reverse.

A power train having such a configuration and operating element table will be described corresponding to seven nodes (NODE) as shown in FIG. 3 by combining a double pinion planetary gear set (DPG) and a lavender planetary gear set (LPG). Can be.

That is, the first node (N1) is the first sun gear (S1), the second node (N2) is the first ring gear (R1), the third node (N3) is the first planet carrier (PC1), the fourth node ( N4 is the second sun gear S2, the fifth node N5 is the second and third planet carriers PC2 and PC3, the sixth node N6 is the second ring gear R2 (R3), and the seventh. The node N7 is set to the third sun gear S3.

3 is a diagram illustrating a shift process of the power train of the present invention. As shown in the first forward speed, the third clutch C3 and the one-way clutch OWC operate.

Then, in the state where the first sun gear S1 operates as a fixed element, the second node, which is the first ring gear R1, is input in a state where an input is made through the third node N3, which is the first planet carrier PC1. The power of the input shaft 3 is input to the seventh node N7 which is the third sun gear S3 as the reduction ratio through N2.

Accordingly, in the planetary gear set LPG, the fifth node N5, which is the third planet carrier PC3, is operated as a fixed element by the one-way clutch OWC, so that the first speed line L1 of FIG. 3 is operated. It forms a speed line as shown, and the output is made as much as D1 through the sixth node (N6) as the output element is a shift of the first forward speed.

In the second forward speed, the second brake B2 is operated and controlled in the state of the first speed.

Then, the first sun gear S1 operates as a fixed element, and the second node N2 which is the first ring gear R1 is input in a state where an input is made through the third node N3 which is the first planet carrier PC1. The power of the input shaft 3 is input to the seventh node N7, which is the third sun gear S3, as a reduction ratio.

Accordingly, in the planetary gear set LPG, the fourth node N4, which is the second sun gear S2, is operated as a fixing element by the operation of the second brake B2, so that the second speed line L2 of FIG. 3 is operated. The speed line is formed as follows, and the output is made as much as D2 through the sixth node N6, which is an output element, and the second speed is shifted.

At the third forward speed, the operation of the second brake B2 is released in the state of the second speed, and the first clutch C1 is operated and controlled.

Then, the first sun gear S1 operates as a fixed element, and the second node N2 which is the first ring gear R1 is input in a state where an input is made through the third node N3 which is the first planet carrier PC1. ) Inputs the power of the input shaft 3 to the seventh node (N7), the third sun gear (S3) at a reduction ratio, and at the same time a second through the third node (N3), the first planetary carrier (PC1). The power of the input shaft 3 is input at the same speed ratio to the fourth node N4 which is the sun gear S2.

Accordingly, the LP planetary gear set LPG operates as a fixed element that is actually driven by the seventh node N7, in which the power of the input shaft 3 is input at a reduction ratio, such as the third speed line L3 of FIG. 3. The speed line is formed, and the output is made as much as D3 through the sixth node N6, which is an output element, and the speed change is performed at the third forward speed.

At the fourth forward speed, the operation of the first clutch C1 is released in the state of the third speed, and the second clutch C2 is controlled to operate.

Then, the first sun gear S1 operates as a fixed element, and the second node N2 which is the first ring gear R1 is input in a state where an input is made through the third node N3 which is the first planet carrier PC1. Input power of the input shaft 3 to the seventh node (N7) of the third sun gear (S3) at a reduction ratio, and at the same time the input shaft (3) to the fifth node (N5) of the third planetary carrier (PC3) ) Power is directly connected and input at the same speed ratio.

Accordingly, the LP planetary gear set LPG operates as a fixed element that is actually driven by the seventh node N7, in which the power of the input shaft 3 is input at the reduction ratio, such as the fourth speed line L4 of FIG. 3. The speed line is formed, and the output is made as much as D4 through the sixth node N6, which is an output element, and thus the fourth forward speed is made.

At the fifth speed, the operation of the third clutch C3 is released in the state of the fourth speed, and the first clutch C1 is operated and controlled.

Then, the power of the input shaft 3 is directly connected to the fifth node N5, which is the third planetary carrier PC3, and is input at the same speed ratio, and through the third node N3, which is the first planetary carrier PC1. The power of the input shaft 3 is input to the fourth node N4 which is the second sun gear S2 at the same speed ratio.

That is, the same input is made to the third planet carrier PC3 and the second sun gear 2 of the rib planetary gear set LPG, and is actually driven integrally with the input shaft 3, and the fifth speed line of FIG. It forms a speed line as shown in (L5), the output is made as much as D5 through the sixth node (N6) as the output element is to be shifted five forward speeds.

At the sixth forward speed, the first clutch C1 is released in the fifth speed state, and the second brake B2 is controlled to operate.

Then, the power of the input shaft 3 is directly connected to the fifth node N5 which is the third planetary carrier PC3 and is input at the same speed ratio.

In addition, the fourth node N4, which is the second sun gear S2, is operated as a fixing element by the operation of the second brake B2 to form the same speed line as the sixth speed line L6 of FIG. The output is made as much as D6 through the sixth node N6, which is an output element, and shifts of six forward speeds are made.

In the first reverse speed, the first clutch C1 and the first brake B1 are operated and controlled.

Then, the power of the input shaft 3 is input at the same speed ratio to the fourth node N4, which is the second sun gear S2, through the third node N3, which is the first planetary carrier PC1.

Accordingly, by the operation of the first brake B1, the fifth node N5, which is the third planet carrier PC3, operates as a fixed element to form a speed line as shown in the reverse line LR of FIG. 3. As the output is made by R through the sixth node N6, which is an output element, the shift speed of reverse 1 is made.

According to the present invention, in the above-described implementation of the shift stage, in particular, the skip shift from the sixth speed to the fourth speed and the fourth speed to the second speed is made possible by changing only one operating element. By contributing to the freedom of movement, it contributes to improving shifting feeling.

Since the speed line for each planetary gear set is well known to those skilled in the art, detailed description thereof will be omitted.

Although the preferred embodiment of the power train of the present invention has been described above, the present invention is not limited to the above embodiment, and those skilled in the art can easily invent from the embodiments of the present invention. It includes all changes to the extent considered equivalent.

As described above, the power train of the present invention is applied to one double pinion planetary gear set and the rib planetary gear set, and the entire gear of the rib planetary gear set is directly connected at 5 speeds while the power of the input shaft is input at the same speed ratio. It is effective to increase the power transmission efficiency by driving to the stage, thereby maximizing the power transmission efficiency in the high-speed stage of more than five speeds.

Claims (21)

In a six-speed power train of an automatic transmission for a vehicle, which is a combination of a double pinion planetary gear set and a lavender planetary gear set, In the double pinion planetary gear set, the first sun gear is fixed to the transmission case, and one side of the first planet carrier is directly connected to the input shaft. In the Lavender planetary gear set, the second sun gear is variably connected to the first planet carrier via the mutual clutch, and at the same time, the brake is variably fixed to the transmission case, and the third sun gear is formed of the double pinion planetary gear set. A third planet carrier, which is connected to the first ring gear via a clutch and rotatably fixes the second planetary gear and the third planetary gear, is variably connected to the input shaft via a clutch, and is connected to the transmission case. It is connected to the brake and the one-way clutch configured in parallel, and the second ring gear is configured as an output element to realize a shift stage of six forward speeds and one reverse speed by operating control of an operating element constituted of the clutch and brakes. A six-speed power train of an automatic transmission for a vehicle, characterized in that it is combined. The six-speed power train of an automatic transmission for a vehicle according to claim 1, wherein the double pinion planetary gear set transmits power to an input shaft through six input paths to the lavender planetary gear set. The method of claim 2, wherein the input path A first input path for operating the first sun gear of the double pinion planetary gear set as a fixed element to input the power of the input shaft to the third sun gear of the rib planetary gear set through the first ring gear at a reduction ratio; The first sun gear of the double pinion planetary gear set operates as a fixed element to input the power of the input shaft to the third sun gear of the rib planetary gear set through the first ring gear at a reduction ratio, and simultaneously through the first planet carrier. A second input path for inputting power of an input shaft at a speed ratio to a second sun gear of the rib planetary gear set; The first sun gear of the double pinion planetary gear set operates as a fixed element to input the power of the input shaft to the third sun gear of the rib planetary gear set through the first ring gear at a reduction ratio, and at the same time, A third input path to which the third planetary carrier and the input shaft are connected so that the power of the input shaft is input at the same speed ratio; The power of the input shaft is inputted to the second sun gear of the rib planetary gear set at the same speed ratio through the first planet carrier of the double pinion planetary gear set, and at the same time, the third planet carrier of the planetary gear set and the input shaft are connected. A fourth input path through which power of the input shaft is input at a speed ratio; A fifth input path connected to a third planet carrier of the planetary gear set and an input shaft such that power of the input shaft is input only at a same speed ratio; A sixth input path for inputting power of an input shaft only at the same speed ratio to the second sun gear of the rib planetary gear set through the first planet carrier of the double pinion planetary gear set; A six-speed power train of an automatic transmission for a vehicle, characterized in that consisting of. The method of claim 3, wherein the first input path Sixth speed power of the automatic transmission for a vehicle, characterized in that the first speed gear and the second speed gear are operated by a clutch connecting the first ring gear of the double pinion planetary gear set to the third sun gear of the rib planetary gear set. Train. The method of claim 3, wherein the second input path In a third speed, the clutch connecting the first ring gear of the double pinion planetary gear set to the third sun gear of the rib planetary gear set and the first planet carrier of the double pinion planetary gear set are the first of the planetary gear set. A six-speed power train for an automatic transmission for a vehicle, characterized in that the two-wheel gear and the variable coupling clutch are operated simultaneously. The method of claim 3, wherein the third input path At the fourth speed, a clutch for connecting the first ring gear of the double pinion planetary gear set to the third sun gear of the rib planetary gear set and the clutch for variably connecting the third planet carrier of the double pinion planetary gear set to the input shaft at the same time A six-speed power train of an automatic transmission for a vehicle, characterized in that the operation is made. The method of claim 3, wherein the fourth input path In a fifth speed, the clutch for variably connecting the first planetary carrier of the double pinion planetary gear set with the second sun gear of the lavender planetary gear set and the clutch that variably connects the third planet carrier of the double pinion planetary gear set with the input shaft. The six-speed power train of the automatic transmission for a vehicle, characterized in that is made by operating simultaneously. The method of claim 3, wherein the fifth input path A sixth speed train of an automatic transmission for a vehicle characterized in that the sixth speed is achieved by operation of a clutch for variably connecting a third planet carrier of the double pinion planetary gear set with an input shaft. The method of claim 3, wherein the sixth input path A six-speed power train of an automatic transmission for a vehicle, characterized in that the first planetary gear set of the double pinion planetary gear set is operated at a reverse speed by a clutch that variably connects the second sun gear of the planetary gear set. The brake and the clutch of claim 1, wherein each of the actuating elements A clutch for connecting the second sun gear and the first planet carrier to the first clutch, a brake for connecting the second sun gear to the transmission case as the second brake, and a clutch for connecting the third planet carrier to the input shaft A second clutch, a clutch for variably connecting the first ring gear to the third sun gear, and a third clutch, and a brake for connecting the third planet carrier to the transmission case as the first brake, At the first speed, the third clutch and the one-way clutch are operated and controlled. At the second speed, the second brake is operated at the state of the first speed, and at the third speed, the second brake is released at the state of the second speed. The first clutch is operated and controlled, and in the fourth speed stage, the second clutch is operated and controlled while the first clutch is released, and in the fifth speed stage, the second clutch is released and the third clutch is released. The first clutch is operated and controlled, and in the sixth speed, the second clutch is operated while the first clutch is released in the fifth speed, and in the reverse first speed, the first clutch and the first brake are operated to shift. 6-speed power train of car automatic transmission. The method of claim 1, wherein the planetary gear set arrangement A double pinion planetary gear set is disposed on the front side of the transmission, a lavender planetary gear set is disposed on the rear side of the transmission, and an output gear is disposed between the double pinion planetary gear set and the rib planetary gear set. 6-speed power train. In a six-speed power train of an automatic transmission for a vehicle, which is a combination of a double pinion planetary gear set and a lavender planet gear set, In the double pinion planetary gear set, the first sun gear is directly connected to the transmission case and fixed, and one side of the first planet carrier is directly connected to the input shaft. The above-mentioned planetary planetary gear set has a second sun gear variably connected to the first planet carrier via a first clutch, and is simultaneously fixed to a transmission case through a second brake, and the third sun gear is double-pinion. A third planet carrier connected to the first ring gear of the planetary gear set through a third clutch, and the third planet carrier rotatably fixing the second planetary gear and the third planetary gear is variably through the second clutch on the input shaft. Connected to the first brake and the one-way clutch which are configured in parallel to the transmission case, and the second ring gear is configured as an output element, and the sixth forward speed is controlled by the operation control of the operation element composed of the clutch and the brakes. And a six-speed power train of an automatic transmission for a vehicle, wherein the sixth speed train is combined to realize a reverse speed stage. The method of claim 12, wherein the double pinion planetary gear set is to transfer the power of the input shaft through the six input paths consisting of the first, second, second, third, fourth, fifth, sixth input path to the cabinet planetary gear set. Featuring a six-speed power train with automatic transmission. The method of claim 13, wherein the first input path At the first speed and the second speed, the first sun gear acts as a fixed element by the operation of a third clutch that connects the first ring gear to the third sun gear to input the shaft to the third sun gear through the first ring gear. The six-speed power train of the automatic transmission for a vehicle, characterized in that the path for inputting the power of the gear ratio. The method of claim 13, wherein the second input path At a third speed, a third clutch for connecting the first ring gear to the third sun gear and a first clutch for variably connecting the first planet carrier to the second sun gear operate simultaneously to operate the first sun gear as a fixed element. And inputting the power of the input shaft to the third sun gear as a reduction ratio through the first ring gear, and simultaneously inputting the power of the input shaft to the second sun gear at the same speed ratio through the first planet carrier. 6-speed power train. The method of claim 13, wherein the third input path At the fourth speed, the third clutch for connecting the first ring gear to the third sun gear and the second clutch for variably connecting the third planet carrier to the input shaft operate simultaneously to operate the first sun gear as a fixing element. The sixth speed of the automatic transmission for a vehicle, wherein the power of the input shaft is input to the third sun gear as a reduction ratio through one ring gear, and at the same time, the third planetary carrier and the input shaft are connected to input the power of the input shaft at the same speed ratio. Power train. The method of claim 13, wherein the fourth input path In a fifth speed, a first clutch for variably connecting the first planetary carrier to the second sun gear and a second clutch for variably connecting the third planetary carrier to the input shaft operate simultaneously to operate the second planetary carrier through the first planetary carrier. The six-speed power train of the automatic transmission for a vehicle, characterized in that the input of the input shaft power to the sun gear at the same speed ratio, and at the same time, the third planetary carrier and the input shaft is connected to the input shaft power. The method of claim 13, wherein the fifth input path In a sixth speed, the third planet carrier of the planetary gear set is connected to the third planet carrier by the operation of a second clutch that variably connects the third planet carrier to the input shaft so that the power of the input shaft is input only at the same speed ratio. A six-speed power train of an automatic transmission for a vehicle. The method of claim 13, wherein the sixth input path It is a path for inputting the power of the input shaft to the second sun gear only at the same speed ratio through the first planet carrier by the operation of the first clutch variably connecting the first planet carrier to the second sun gear at the reverse speed 1. 6-speed power train of vehicle automatic transmission. The brake and clutch of claim 12, wherein each of the actuating elements At the first speed, the third clutch and the one-way clutch are operated and controlled. At the second speed, the second brake is operated at the state of the first speed, and at the third speed, the second brake is released at the state of the second speed. The first clutch is operated and controlled, and in the fourth speed stage, in the state of the third speed, the second clutch is operated and controlled while the first clutch is released, and in the fifth speed stage, the third clutch is released in the state of the fourth speed. The first clutch is operated and controlled, and in the sixth speed, the second clutch is operated while the first clutch is released in the state of the fifth speed, and in the reverse first speed, the first clutch and the first brake are operated to shift. 6-speed power train of vehicle automatic transmission. The method of claim 12, wherein the planetary gear set arrangement A double pinion planetary gear set is disposed at the front side of the transmission, and a lavender planetary gear set is disposed at the rear side of the transmission, and an output gear is disposed between the double pinion planetary gear set and the rib planetary gear set. 6-speed power train.

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