KR100986055B1 - A power train of an automatic transmission - Google Patents

Abstract

The present invention can implement a shift speed of 11 forward and 2 reverse speeds through the planetary planetary gear set, five clutches and two brakes, and to maintain the shift stage with two elements of the clutch element or the brake element. In combination, this provides a power train of an automatic transmission that enables shifting by controlling only one element so that the shifting control is simple and thus the shifting feeling can be improved.

Automatic transmission. clutch. Planetary Gear Sets

Description

Power train of automatic transmission {A POWER TRAIN OF AN AUTOMATIC TRANSMISSION}

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 power train according to the prior art,

5 is a shift diagram of a power train according to the prior art, and

6 is a table of operating elements of a power train according to the prior art.

The present invention relates to a power train of an automatic transmission for a vehicle that is applied to an automatic transmission for a vehicle so as to realize a shift stage of 11 forward speeds and 2 reverse speeds.

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, rather than developing a new planetary gear set, a conventional single pinion planetary gear set, a double pinion planetary gear set, or a single and double pinion planetary gear How to combine a set of combination type planetary gear set and the accompanying clutches, brakes and one-way clutches in any position to achieve the desired speed and the gear ratio without any possible power loss A variety of research aimed at improving the performance of the.

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 have been conducted, and in recent years, power trains of automatic transmissions capable of implementing multi-speed stages having 6 or more forward speeds have been provided.

As an example, as shown in FIG. 4, according to US Pat. No. 6,723,018 (registered April 20, 2004), one composite planetary gear set 16 and one lavender planetary gear set 17 having a step pinion gear 25 are shown. And a combination of three clutches, four brakes, and one one-way clutch, as shown in FIG. 5, a power train of an automatic transmission that realizes a shift stage of up to 12 forward speeds and 2 reverse speeds is disclosed.

That is, as can be seen in Figure 5, in the composite planetary gear set 16, the one-to-one (1: 1) co-speed and two deceleration inputs are delivered to the planetary gear set 17, the ravi The final output is configured through the ring gears R3 and R4 of the new planetary gear set 17.

However, the conventional power train of the automatic transmission comprising the 12th forward speed and the 2nd reverse speed stage as described above, as shown in Figure 6, the combination of the clutch element and the brake element for shifting is disadvantageous to the shift control. It has disadvantages in terms of shifting speed.

That is, as shown in Fig. 6, in each shifting stage, the three elements of the clutch element or the brake element must be maintained in a state of being coupled and controlled at all times. In order to shift to the other end, two elements of the clutch element or the brake element are always present. It is to be released and coupled control, and thus the shift control is complicated, and the shift feeling is reduced.

 Accordingly, the present invention has been invented to solve the disadvantages of the prior art, and an object of the present invention is to provide a shift speed of 11 forward speeds and 2 reverse speeds through two rib planetary gear sets, five clutches, and two brakes. It is to provide a power train of automatic transmission that can be implemented.

In addition, another object of the present invention is to combine the two of the clutch element or the brake element to maintain the shift stage, thereby enabling the shifting by controlling only one element, the shift control is simple, according to the shift feeling It is to provide a power train of the automatic transmission to improve the speed.

The power train of the automatic transmission of the present invention for realizing the above object comprises: an input shaft (3) to which the rotational force of the engine is input; In front of the input shaft 3, the two planetary gears (P1, P2) and the first sun gear (S1), respectively, and includes a first planetary carrier (PC1) for supporting the two planetary gears to share The planet carrier PC1 is directly connected to the input shaft 3 and is always combined as an input element, and the shared first sun gear S1 is fixed to the transmission case 1 and is always combined as a fixed element. The gear R1 is engaged with one planetary gear P1 and is a speed increasing element, and the second ring gear R2 is engaged with another planetary gear P2 and is combined as a deceleration element to implement four operating elements. First composite planetary gear set; At the rear of the input shaft 3, two planetary gears P3 and P4 and a third ring gear R3 are shared, respectively, and include third and fourth planetary carriers supporting the two planetary gears. The third planet carrier PC3 is variably connected to the first and second ring gears R1 and R2 of the first hybrid planetary gear set through a fourth clutch C4 and a second clutch C2, respectively. The fourth planetary carrier PC4 is combined with an input element, and is variably connected to the transmission case 1 through the first brake B1 to be combined into a variable fixed element, and the shared third ring gear R3 is The third sun gear S3, which is combined as an output element and not shared, has a first clutch C1 and a third on the second ring gear R2 and the input shaft 3, respectively, which are deceleration elements of the first hybrid planetary gear set. The fourth sun gear S4, which is variably connected through the clutch C3, is combined into a variable input element, and is not shared, is variable through the fifth clutch C5 on the input shaft 3. Coupled to the variable input element, or variably connected to the transmission case (1) via the second brake (B2) combined to the variable fixed element to implement four operating elements, the input shaft (3) and the first composite planetary The second composite planetary gear set is a power input through the five input paths from the gear set; and characterized in that the speed of the 11 forward speed and 2 reverse speed.

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

1 is a schematic diagram of a power train according to an embodiment of the present invention, in which the power train according to the first embodiment of the present invention is connected to the engine output side via a torque converter (not shown) in front of the first shaft on the input shaft 3. The composite planetary gear set LPG1 and a second composite planetary gear set LPG2 are provided behind it.

The first composite planetary gear set LPG1 shares the first sun gear S1 and is a pair of planetary gears P1 meshed between the first sun gear S1 and the first and second ring gears R1 and R2. , P2) is rotatably supported, and at the same time, a combination of a planetary gear set sharing a first planetary carrier PC1 driven by the revolution.

The second composite planetary gear set LPG2 shares a third ring gear R3 and includes two sets of planetary gears meshed between the third and fourth sun gears S3 and S4 and the third ring gear R3. P3 and P4 are rotatably supported, and at the same time, a combination is made of a rib planetary gear set which shares the third and fourth planet carriers PC3 and PC4 driven by the revolution.

The first planetary gear set LPG1 has the first planetary carrier PC1 directly connected to the input shaft 3 and is always combined as an input element, and the shared first sun gear S1 is fixed to the transmission case 1. It is always combined with the fixed element.

And the first ring gear (R1) is meshed with one planetary gear (P1) and combined with a speed increasing element, the second ring gear (R2) is engaged with another planetary gear (P2) and combined with a deceleration element all Four working elements will be implemented.

In the second composite planetary gear set LPG2, the third planet carrier PC3 may be connected to the first and second ring gears R1 and R2 of the first composite planetary gear set LPG1, respectively, by a fourth clutch C4. The second planetary clutch C2 is variably connected to the variable input element, and the fourth planet carrier PC4 is variably connected to the transmission case 1 through the first brake B1 to be combined into the variable fixed element. do.

The shared third ring gear R3 is combined as an output element, and the non-shared third sun gear S3 is a second ring gear R2 that is a deceleration element of the first composite planetary gear set LPG1. The first shaft C1 and the third clutch C3 are variably connected to the input shaft 3 to be combined into the variable input element.                     

In addition, the fourth sun gear S4 which is not shared is variably connected to the input shaft 3 through the fifth clutch C5 and combined with the variable input element, or the second case B2 is connected to the transmission case 1. The variable connection is combined into a variable fixed element to implement a total of four operating elements.

Here, the first, second, fourth clutch (C1, C2, C4) is between the four operating elements of the first composite planetary gear set LPG1 and the four operating elements of the second composite planetary gear set LPG2. It is preferably arranged in.

In addition, the first and second brakes B1 and B2 and the third and fifth clutches C3 and C5 may be disposed outside the four operating elements of the second composite planetary gear set LPG2.

The second composite planetary gear set LPG2 as described above receives power from five input paths from the input shaft 3 and the first composite planetary gear set LPG1.

That is, of the five input paths through which power of the input shaft 3 is transmitted to the second composite planetary gear set LPG2, the first input path includes the first planetary carrier PC1 of the first composite planetary gear set LPG1. ) Is a path through which power input to the second gear is decelerated through the second ring gear R2 and input to the third sun gear S3 of the second hybrid planetary gear set LPG2. In the fifth, seventh, eleventh, and first reverse speeds, the third sun gear of the second ring gear R2 of the first hybrid planetary gear set LPG1 and the second planetary gear set LPG2 ( It is implemented by the operation of the first clutch (C1) for variable connection of S3).

The second input path is decelerated through the second ring gear R2 by the power inputted to the first planet carrier PC1 of the first hybrid planetary gear set LPG1 to the third of the second planetary gear set LPG2. The second input path is a path input to the planet carrier PC3, and the second ring gear of the first composite planetary gear set LPG1 is formed at the third speed, the fourth speed, the fifth speed, and the sixth speed. It is realized by the operation of the second clutch C2 for variably connecting R2) and the third planetary carrier PC3 of the second composite planetary gear set LPG2.

The third input path is a path through which the power of the input shaft 3 is input at the same speed to the third sun gear S3 of the second composite planetary gear set LPG2. The third input path is the second speed, the fourth speed, At the eighth speed, the tenth speed and the second reverse speed, by the operation of the third clutch C3 which variably connects the input shaft 3 and the third sun gear S3 of the second hybrid planetary gear set LPG2. Is implemented.

The fourth input path is the power input to the first planet carrier PC1 of the first hybrid planetary gear set LPG1 is increased through the first ring gear R1, so that the third of the second planetary gear set LPG2 is increased. The fourth input path is a path input to the planet carrier PC3. The fourth input path includes the first ring gear R1 and the first ring gear R1 of the first hybrid planetary gear set LPG1 in the ninth, tenth, and eleventh speeds. The fourth clutch C4 variably connects to the shared third planetary carrier PC3 of the two-component planetary gear set LPG2.

The fifth input path is a path in which the power of the input shaft 3 is input to the fourth sun gear S4 of the second composite planetary gear set LPG2 at the same speed. The fifth input path is the sixth speed, the seventh speed, and the fifth speed path. In the eighth and ninth speeds, the fifth shaft C5 variably connects the input shaft 3 and the fourth sun gear S4 of the second composite planetary gear set LPG2.

Accordingly, the power train having the configuration as described above implements the shift stages of 11 forward speeds and 2 reverse speeds. As shown in the operating element table shown in FIG. 2, the first clutch C1 and the first clutch at the first speed stage are implemented. It is made by the operation of the second brake (B2), in the second speed is made by the operation of the third clutch (C3) while the first clutch (C1) is released in the state of the first speed.

In the third speed, the third clutch C3 is released in the state of the second speed, and the second clutch C2 is operated. In the fourth speed, the second brake B2 is operated in the third speed. It is made by the operation of the third clutch (C3) while being released.

In the fifth speed, the third clutch C3 is released in the fourth speed, and the first clutch C1 is operated. In the sixth speed, the first clutch C1 is released in the fifth speed. It is made by the operation of the fifth clutch (C5).

In the seventh stage, the second clutch C2 is released in the state of the sixth speed, and the first clutch C1 is operated. In the eighth speed, the first clutch C1 is released in the state of the seventh speed. By the operation of the third clutch (C3).

In the ninth speed, the third clutch C3 is released by the operation of the fourth clutch C4 while the third clutch C3 is released. In the tenth speed, the fifth clutch C5 is operated in the ninth speed. It is made by the operation of the third clutch C3 while being released, and is made by the operation of the first clutch C1 while the third clutch C3 is released in the state of the tenth speed at the eleventh speed.

In the first reverse stage, the first clutch C1 and the first brake B1 are operated, and in the second reverse stage, the third clutch C3 and the first brake B1 are operated.                     

The shifting process of the power train according to the embodiment of the present invention described above will be described in more detail with reference to FIG. 3.

First, as described above, each actuating element is arranged at each node, as shown in the forward 1 to 11 speed and reverse 2 speed diagrams of the power train according to the present invention.

That is, the first sun gear S1 shared by the first node N1, the second node N2, and the third node N3 are connected by the second ring gear R2 and the first planet carrier PC1 to be shared. In the fourth node N4, a first ring gear R1 is set.

The fifth node N5 is the third sun gear S3, the sixth node N6 is the third and fourth planet carriers PC3 and PC4 which are shared, and the seventh node N7 is the third ring gear ( As for R3), the fourth sun gear S4 is set to the eighth node N8.

Accordingly, the second ring gear R2 of the first planetary gear set LPG1 is operated by the first clutch C1 while the first clutch C1 and the second brake B2 are operated. The decelerated input is input to the third sun gear S3 of the second composite planetary gear set LPG2, and at this time, the second composite planetary gear set LPG2 is operated by the operation of the second brake B2. The fourth sun gear S4 of) acts as a fixed element to form the speed line L1 in FIG. 3, and through the seventh node N7 as an output element, that is, the shared ring gear R3, D1. As the output is made as much as one forward speed is made.

In the second forward speed, in the state of the first speed, the operation of the first clutch C1 is released, and the third clutch C3 is controlled to operate.

Then, the power of the input shaft 3 by the operation of the third clutch (C3) is input to the third sun gear (S3) of the second composite planetary gear set LPG2 at the same speed as it is, the operation is maintained By the second brake B2, the fourth sun gear S4 of the second composite planetary gear set LPG2 still operates as a fixed element to form the speed line L2 in FIG. The output is made as much as D2 through the node N7, that is, the shared ring gear R3, and the shifting of the second forward speed is made.

In the third forward speed, in the state of the second speed, the operation of the third clutch C3 is released, and the second clutch C3 is operated and controlled.

Then, the input reduced by the second ring gear R2 of the first composite planetary gear set LPG1 by the operation of the second clutch is the third planetary carrier of the second planetary gear set LPG2 ( The fourth sun gear S4 of the second composite planetary gear set LPG2 is still operated as a fixed element by the operation of the second brake B2, which is input to PC3) and the operation is maintained.

Accordingly, the speed line L3 in FIG. 3 is formed, and output is performed as much as D3 through the seventh node N7, that is, the output ring element R3, which is an output element, so that the speed change of the third forward speed is made. do.

At the fourth forward speed, in the state of the third speed, the operation of the second brake B2 is released, and the third clutch C3 is operation controlled.

Then, the power of the input shaft 3 by the operation of the third clutch (C3) is input to the third sun gear (S3) of the second composite planetary gear set LPG2 at the same speed as it is, the operation is maintained The input decelerated by the second clutch C2 through the second ring gear R2 of the first composite planetary gear set LPG1 to the third planetary carrier PC3 of the second composite planetary gear set LPG2. Is entered.

In this case, the third planetary carrier PC3 of the second composite planetary gear set LPG2 substantially acts as a fixed element, thereby forming a speed line L4 in FIG. 3, and a seventh node as an output element. N7) That is, the output is made as much as D4 through the shared ring gear (R3), the shift is made in the fourth forward speed.

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

Then, the input decelerated through the second ring gear R2 of the first composite planetary gear set LPG1 by the operation of the first clutch C1 is the third of the second composite planetary gear set LPG2. An input decelerated through the second ring gear R2 of the first composite planetary gear set LPG1 by the second clutch C2, which is input to the sun gear S3 and is operated, is input to the second composite planetary gear. It is input to the third planet carrier PC3 of the set LPG2.

That is, the third sun gear S3 and the third planet carrier PC3 of the second planetary gear set LPG2 are decelerated through the second ring gear R2 of the first planetary gear set LPG1. The input is applied in the same way, and forms the speed line L5 in FIG. 3, and outputs as much as D5 through the seventh node N7 that is an output element, that is, the shared ring gear R3. The shift is made.

At the sixth forward speed, in the state of the fifth speed, the operation of the first clutch C1 is released, and the fifth clutch C5 is controlled to operate.

Then, the power of the input shaft 3 by the operation of the fifth clutch (C5) is input to the fourth sun gear (S4) of the second composite planetary gear set LPG2 at the same speed as it is, the operation is maintained The input decelerated by the second clutch C2 through the second ring gear R2 of the first composite planetary gear set LPG1 to the third planetary carrier PC3 of the second composite planetary gear set LPG2. Is entered.

In this case, the third planetary carrier PC3 of the second composite planetary gear set LPG2 substantially acts as a fixed element, thereby forming a speed line L6 in FIG. 3, and a seventh node as an output element. N7) That is, the output is made as much as D6 through the shared ring gear (R3) and the sixth forward speed is made.

At the seventh forward speed, in the state of the sixth speed, the operation of the second clutch C2 is released, and the first clutch C1 is operated and controlled.

Then, the power of the input shaft 3 is inputted as it is to the fourth sun gear S4 of the second composite planetary gear set LPG2 at the same speed by the operation of the fifth clutch C5, which is maintained. The third sun gear S3 of the second composite planetary gear set LPG2 is decelerated through the second ring gear R2 of the first composite planetary gear set LPG1 by the operation of the first clutch C1. Is entered.

At this time, the third sun gear S3 of the second hybrid planetary gear set LPG2 actually acts as a fixed element, thereby forming a speed line L7 in FIG. 3, and a seventh node N7 as an output element. That is, the output is made as much as D7 through the shared ring gear (R3) and the seventh speed shift is made.

At the eighth forward speed, in the state of the seventh speed, the operation of the first clutch C1 is released, and the third clutch C3 is operation controlled.

Then, the power of the input shaft 3 is inputted as it is to the fourth sun gear S4 of the second composite planetary gear set LPG2 at the same speed by the operation of the fifth clutch C5, which is maintained. By the operation of the three clutch C3, the power of the input shaft 3 is directly input to the third sun gear S3 of the second composite planetary gear set LPG2 at the same speed.

That is, the power of the input shaft 3 is equally input to the third sun gear S3 and the fourth sun gear S4 of the second hybrid planetary gear set LPG2 at the same speed, so that the speed line L8 in FIG. ), And the output is made as much as D8 through the seventh node (N7) that is the output element, that is, the shared ring gear (R3).

In true 9 speed, in the state of 8th speed, operation | movement of the 3rd clutch C3 is canceled | released and operation of the 4th clutch C4 is controlled.

Then, the power of the input shaft 3 is inputted as it is to the fourth sun gear S4 of the second composite planetary gear set LPG2 at the same speed by the operation of the fifth clutch C5, which is maintained. The input accelerated through the first ring gear R1 of the first composite planetary gear set LPG1 by the operation of the four clutch C4 is performed by the third planetary carrier PC3 of the second composite planetary gear set LPG2. ) Is entered.

At this time, the fourth sun gear S4 of the second hybrid planetary gear set LPG2 actually acts as a fixed element, thereby forming a speed line L9 in FIG. 3, and a seventh node N7 as an output element. That is, as the output is made as D9 through the shared ring gear (R3), the speed of 9 forward speed is achieved.

At the 10th forward speed, in the state of the ninth speed, the operation of the fifth clutch C5 is released, and the third clutch C3 is operated controlled.

Then, the input speeded up through the first ring gear R1 of the first composite planetary gear set LPG1 by the fourth clutch C4, which is maintained, is controlled by the fourth clutch C4 of the second composite planetary gear set LPG2. The third planetary gear PC3 is input to the third planetary gear set LPG2 of the second hybrid planetary gear set LPG2 at the same speed by the operation of the third clutch C3. Is entered.

At this time, the third sun gear S3 of the second composite planetary gear set LPG2 actually acts as a fixed element to form the speed line L10 in FIG. 3, and the seventh node N7 as an output element. That is, the output is made as much as D10 through the shared ring gear (R3) and the shift of the forward 10 speed is made.

At the 11th forward speed, in the state of the 10th speed, the operation of the third clutch C3 is released, and the first clutch C1 is controlled to operate.

Then, the input speeded up through the first ring gear R1 of the first composite planetary gear set LPG1 by the fourth clutch C4, which is maintained, is controlled by the fourth clutch C4 of the second composite planetary gear set LPG2. The inputted to the planetary carrier PC3 and the input decelerated through the second ring gear R2 of the first composite planetary gear set LPG1 by the operation of the first clutch C1 is the second composite planetary. It is input to the 3rd sun gear S3 of the gear set LPG2.                     

At this time, the third sun gear S3 of the second composite planetary gear set LPG2 actually acts as a fixed element to form the speed line L11 in FIG. 3, and the seventh node N7 as an output element. That is, the output is made as much as D11 through the shared ring gear (R3) and the 11th forward speed is made.

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

Then, the input decelerated through the second ring gear R2 of the first composite planetary gear set LPG1 by the operation of the first clutch C1 is the third of the second composite planetary gear set LPG2. It is input to the sun gear S3, and the fourth planet carrier PC4 of the second composite planetary gear set LPG2 is operated as a fixed element by the operation of the first brake B1.

Accordingly, the second composite planetary gear set LPG2 forms the reverse first speed line LR1 in FIG. 3, and DR1 through the seventh node N7, that is, the shared ring gear R3. As the output is made, the shifting speed of reverse 1 is achieved.

In addition, in the second reverse speed, the third clutch C3 and the first brake B1 are operated and controlled.

Then, the power of the input shaft 3 is input to the third sun gear S3 of the second composite planetary gear set LPG2 at the same speed by the operation of the third clutch C3, and the first brake By operating B1), the fourth planetary carrier PC4 of the second composite planetary gear set LPG2 is operated as a fixed element.

Accordingly, the second composite planetary gear set LPG2 forms the reverse 2-speed line LR2 in FIG. 3, and DR2 through the seventh node N7, that is, the shared ring gear R3. As the output is made, the reverse speed 2 is shifted.

Although the embodiment of the power train of the present invention has been described above, the present invention is not limited to the above embodiment, and can be easily invented by those skilled in the art from the embodiments of the present invention. Includes all changes that are considered to be equivalent.

As described above, the power train of the present invention implements a shift stage of 11 forward speeds and 2 reverse speeds through two lavender planetary gear sets, five clutches, and two brakes. Combination of two elements is maintained to maintain the shift stage, thereby enabling shifting by controlling only one element and thus shifting control is simple, thereby improving the shifting feeling.

Claims (25)

In the power train of the automatic transmission, An input shaft to which rotational force of the engine is input; In front of the input shaft, each planetary gear and sun gear, each of the two planetary gears, including a planetary carrier supporting the two planetary gears, the planetary carrier is always combined into the input element, the shared sharing The sun gear is always combined with a fixed element, one non-shared ring gear is a speed increasing element, the other non-shared ring gear is combined as a deceleration element, the first composite planetary gear set to implement four operating elements; At the rear of the input shaft, one planet carrier includes two planet carriers each sharing two planetary gears and a ring gear, and supporting two planetary planetary gears, wherein one planet carrier is configured to reduce the speed of the first composite planetary gear set. Combined with a variable input element that selectively receives inputs of deceleration and deceleration from the element and the speed increase element, another planetary carrier is combined into a variable fixed element, and the shared sharing ring gear is combined into an output element and not shared. One sun gear is combined with a variable input element that selectively receives the deceleration and the same speed input from the deceleration element and the input shaft of the first composite planetary gear set, and the other non-shared sun gear receives the same speed input from the input shaft. Combined with a variable input element that is optionally delivered, or combined with a variable fixed element to implement four operating elements A second compound planetary gear set; The power train of the automatic transmission, characterized in that to implement the transmission speed of 11 forward and 2 reverse speed. The method of claim 1, wherein the first composite planetary gear set Lavigny planetary, including one sun gear, rotatably supporting two sets of planetary gears engaged and shared between the sun gear and the two ring gears, and at the same time comprising one planet carrier driven by the revolution Power train of an automatic transmission, characterized in that the gear set. The method of claim 1, wherein the second composite planetary gear set Lavigne, which shares one ring gear, rotatably supports two sets of planetary gears engaged and shared between the two sun gears and one ring gear, and simultaneously includes two planet carriers driven by the revolutions. Power train of an automatic transmission, characterized in that the planetary gear set. The method of claim 1, wherein the second composite planetary gear set The one planet carrier is variably connected to the ring gear which is the deceleration element of the first composite planetary gear set and the ring gear which is the speed increase element, respectively through the second clutch and the fourth clutch, and the other planet carrier is attached to the transmission case. One sun gear that is variablely connected through one brake and is not shared is variably connected to the ring gear and the input shaft, which are deceleration elements of the first hybrid planetary gear set, through the first clutch and the third clutch, respectively. One sun gear is variably connected to the input shaft through a fifth clutch, and at the same time, it is variably connected to the transmission case through a second brake to implement four operating elements, and five input paths from the input shaft and the first composite planetary gear set. The power train of the automatic transmission, characterized in that the power is input through the 11th speed forward and 2nd speed reverse. 5. The five input paths according to claim 4, wherein power of an input shaft is transmitted to the second composite planetary gear set. A first input path through which power input to the planetary carrier of the first composite planetary gear set is input to one sun gear of the second composite planetary gear set through a ring gear that is a deceleration element; A second input path through which power input to the planet carrier of the first planetary gear set is input to one planet carrier shared by the second composite planetary gear set through the deceleration element ring gear; A third input path through which power of the input shaft is input at the same speed to one sun gear of the second composite planetary gear set; A fourth input path through which power inputted to the planetary carrier of the first composite planetary gearset is input to one shared planetary carrier of the second composite planetary gearset through a ring gear that is an acceleration element; A fifth input path through which power of the input shaft is input at the same speed to the other sun gear of the second composite planetary gear set; Power train of the automatic transmission, characterized in that it comprises a. The method of claim 5, wherein the first input path In the first speed, the fifth speed, the seventh speed, the eleventh speed, and the first reverse speed, a variable gear between the ring gear which is a deceleration element of the first composite planetary gear set and one sun gear of the second composite planetary gear set is variably connected. The power train of the automatic transmission, characterized by the operation of the first clutch. The method of claim 5, wherein the second input path In the third, fourth, fifth, and sixth speeds, operation of the second clutch that variably connects the ring gear which is the deceleration element of the first composite planetary gear set and one planet carrier of the second composite planetary gear set The power train of the automatic transmission, characterized in that made by. The method of claim 5, wherein the third input path At the second, fourth, eighth, tenth, and second reverse speeds, by an operation of a third clutch that variably connects an input shaft and one sun gear of the second composite planetary gear set. Powertrain of automatic transmission. The method of claim 5, wherein the fourth input path In the ninth, tenth, and eleventh speeds, an operation of the fourth clutch to variably connect the ring gear which is the speed increasing element of the first composite planetary gear set and one planet carrier of the second composite planetary gear set is performed. The power train of the automatic transmission, characterized in that. The method of claim 5, wherein the fifth input path In the sixth, seventh, eighth and ninth speeds, the automatic transmission is characterized by the operation of the fifth clutch for variably connecting the input shaft and the other sun gear of the second composite planetary gear set. Power train. 5. The shift of claim 1, wherein the shift by the combination of the first composite planetary gear set and the second composite planetary gear set is performed by the operation of the first clutch and the second brake at the first speed stage, and the first speed stage at the second speed stage. In the state of the first clutch is released by the operation of the third clutch, the third speed is made by the operation of the second clutch while the third clutch is released in the state of the second speed, and in the fourth speed In the state of the third speed, the second brake is released by the operation of the third clutch, and in the fifth speed, the third clutch is released by the operation of the first clutch while the fourth clutch is released, and the sixth The first stage is made by the operation of the fifth clutch while the first clutch is released in the state of the fifth speed, and the seventh stage is made by the operation of the first clutch while the second clutch is released in the state of the sixth speed, In the eighth speed, the first clutch is released in the state of the seventh speed, by the operation of the third clutch. In the ninth speed, in the state of the eighth speed, the third clutch is released, by the operation of the fourth clutch. In the tenth speed, the fifth clutch is released in the state of the ninth speed, and the third clutch is released. In the eleventh speed, the third clutch is released in the state of the tenth speed, and the first clutch is operated. The sixth speed of the automatic transmission is made by the operation of the first clutch and the first brake in the first reverse stage, and by the operation of the third clutch and the first brake in the second reverse stage. Power train. The method of claim 4, wherein the first, second, fourth clutch And a sixth speed train of the automatic transmission, characterized in that it is arranged between the four operating elements of the first composite planetary gear set and the four operating elements of the second composite planetary gear set. The method of claim 4, wherein the first and second brakes and the third and fifth clutches And a six-speed power train of the automatic transmission, characterized in that it is disposed outside the four operating elements of the second composite planetary gear set. In the power train of the automatic transmission, An input shaft to which rotational force of the engine is input; In front of the input shaft, each of the two planetary gears and the first sun gear, each of the first planetary gear including a first planetary carrier supporting the two sets of planetary gears, the first planetary carrier is directly connected to the input shaft And the shared first sun gear is fixed to the transmission case and is always combined with a fixed element. The first ring gear is engaged with one planetary gear and is a speed increasing element, and the second ring gear is combined with another planetary gear. A first composite planetary gear set engaged with the reduction gear to implement four operating elements; At the rear of the input shaft, the third planetary carrier includes a third and fourth planet carriers each sharing two sets of planetary gears and a third ring gear, and supporting three sets of planetary gears. A fourth clutch and a second clutch are variably connected to the first and second ring gears of the planetary gear set, respectively, and are combined into a variable input element. The fourth planetary carrier is variably fixed to the transmission case through a first brake. The third ring gear is combined as an output element, and the third non-shared third sun gear is a first clutch and an input shaft to the second ring gear and the input shaft, respectively, which are deceleration elements of the first hybrid planetary gear set. The fourth sun gear, which is variably connected through three clutches, is combined into a variable input element, and the fourth sun gear which is not shared is variably connected through the fifth clutch to the input shaft, and is combined into a variable input element, or the second case is connected to the transmission case. A second composite planetary gear set, which is variably connected through a rake, is configured as a variable fixed element to implement four operating elements, and power is input from the input shaft and the first composite planetary gear set through five input paths; A power train of an automatic transmission, characterized by a 11-speed forward and a 2-speed reverse gear. The method of claim 14, wherein the first composite planetary gear set The rib sharing the first sun gear, rotatably supporting two sets of planetary gears meshed between the first sun gear and the first and second ring gears, and at the same time share the first planet carrier driven by the revolution. Power train of an automatic transmission, characterized in that the planetary gear set. The method of claim 14, wherein the second composite planetary gear set The third and fourth planetary gear sharing the third ring gear, and rotatably supports two sets of planetary gears meshed between the third and fourth sun gear and the third ring gear, and at the same time driven by the revolution The powertrain of an automatic transmission, characterized by a shared planetary gear set. 15. The apparatus of claim 14, wherein five input paths through which power of an input shaft is transmitted to the second composite planetary gear set are used. A first input path through which power input to the first planet carrier of the first planetary gear set is decelerated through the second ring gear and input to the third sun gear of the second compound planetary gear set; A second input path through which power input to the first planet carrier of the first planetary gear set is decelerated through the second ring gear and input to the third planet carrier of the second compound planetary gear set; A third input path through which power of the input shaft is input at the same speed to the third sun gear of the second composite planetary gear set; A fourth input path through which power input to the first planetary carrier of the first composite planetary gear set is increased through the first ring gear and input to the third planetary carrier of the second composite planetary gear set; A fifth input path through which power of the input shaft is input at the same speed to the fourth sun gear of the second composite planetary gear set; Power train of the automatic transmission, characterized in that it comprises a. The method of claim 17, wherein the first input path In the first speed, the fifth speed, the seventh speed, the eleventh speed, and the first backward speed, the second ring gear of the first hybrid planetary gear set and the third sun gear of the second hybrid planetary gear set are variably connected. A power train of an automatic transmission, characterized by the operation of one clutch. The method of claim 17, wherein the second input path In the third speed, the fourth speed, the fifth speed, and the sixth speed, the second clutch for variably connecting the second ring gear of the first composite planetary gear set and the third planetary carrier of the second composite planetary gear set is operated. The power train of the automatic transmission, characterized in that made by. The method of claim 17, wherein the third input path At a second speed, a fourth speed, an eighth speed, a tenth speed, and a second reverse speed, by an operation of a third clutch for variably connecting an input shaft and a third sun gear of the second composite planetary gear set. Powertrain of automatic transmission. The method of claim 17, wherein the fourth input path In the ninth, tenth, and eleventh speeds, the fourth clutch variably connects the first ring gear of the first composite planetary gear set and the third planetary carrier of the second composite planetary gear set. The power train of the automatic transmission, characterized in that made. The method of claim 17, wherein the fifth input path In the sixth, seventh, eighth, and ninth speeds, the power of the automatic transmission is made by the operation of a fifth clutch that variably connects the input shaft and the fourth sun gear of the second composite planetary gear set. Train. The method of claim 14, wherein the shift by the combination of the first composite planetary gear set and the second composite planetary gear set is The first clutch is made by the operation of the first clutch and the second brake, the second gear is made by the operation of the third clutch while the first clutch is released in the state of the first gear, and the third is made by the second The third clutch is released by the operation of the second clutch while the third clutch is released, and in the fourth speed, the third clutch is released by the operation of the third clutch while the second brake is released. In the fourth speed is made by the operation of the first clutch while the third clutch is released, in the sixth speed is made by the operation of the fifth clutch while the first clutch is released in the state of the fifth speed, In the seventh stage, the second clutch is released by the operation of the first clutch while the second clutch is released in the sixth speed, and in the eighth speed, the first clutch is released by the operation of the third clutch while the first clutch is released in the seventh speed. In the ninth speed, the third clutch is released by the operation of the fourth clutch while the third clutch is released. In the tenth speed, the fifth clutch is released while the fifth clutch is released in the ninth speed. In the eleventh speed is made by the operation of the first clutch while the third clutch is released in the state of the tenth speed, in the first reverse stage is made by the operation of the first clutch and the first brake, The sixth speed train of the automatic transmission, characterized in that the second reverse stage is made by the operation of the third clutch and the first brake. 15. The method of claim 14, wherein the first, second, fourth clutch And a sixth speed train of the automatic transmission, characterized in that it is arranged between the four operating elements of the first composite planetary gear set and the four operating elements of the second composite planetary gear set. 15. The method of claim 14, wherein the first and second brakes and the third and fifth clutches And a six-speed power train of the automatic transmission, characterized in that it is disposed outside the four operating elements of the second composite planetary gear set.

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