KR100949662B1 - Power train for automatic transmission - Google Patents

Abstract

The present invention is a simple structure that combines four clutches and two brakes in a reduction gear planetary gear set and a compound planetary gear set, and implements a shift stage of seven forward speeds and one reverse speed, thereby reducing the volume and weight of the automatic transmission and mounting the vehicle. The aim is to improve the

According to the present invention for achieving the above object, the first planetary gear set (PG-1) is the first ring gear (R1) connected to the input shaft 10, and the first sun gear (constrained by the transmission case 30) ( S1) and a first carrier C1 for outputting power to the outside; The second planetary gear set PG-2 has a second sun gear S2 connected to the first carrier C1 and a fourth clutch C-4 and a second sun gear S2 externally connected to the second sun gear S2. A second carrier (C2) and a second ring gear (R2) connected to the output shaft (20); The third planetary gear set PG-3 includes a third sun gear S3 connected to the input shaft 10 and the first clutch C-1, and a third ring gear R2 connected to the second ring gear R2. A third ring gear (R3) and a third connected via the input shaft (10) and the second clutch (C-2) and connected through the first carrier (C1) and the third clutch (C-3); It is characterized by including the carrier C3.

Automatic transmission, seven speeds, power train, planetary gear set, clutch, brake

Description

Power train for automatic transmission

The present invention relates to a power train of an automatic transmission, and more particularly, to a seventh speed power train of an automatic transmission that implements shift speeds of seven forward speeds and one reverse speed.

Automatic transmissions have been tried in various forms to change the engine's power to suit the running load. However, the transmission is generally generalized to include a gear train including a planetary gear and a hydraulic control device for manipulating the gear train.

The gear train is configured to form a specific shift stage by an operation combination of a friction element such as a clutch or a brake operated by the hydraulic control device, so that the hydraulic control device is automatically controlled by the driving state of the vehicle and the driver's operation. When operated, the gear shift to the desired speed shift stage is achieved.

As the speed change stage of the automatic transmission is formed in multiple stages, power output from the engine can be transmitted to the driving wheel with higher efficiency, thereby improving fuel economy, acceleration performance, and speed change quality.

Conventional planetary gearsets used in gear trains of automatic transmissions in order to realize a six-speed shift stage or more are used in the Lavigneaux Type. The planetary gearsets of the Lavignon type have long pinions and short carriers. Since the pinion must be supported at the same time, there is a difficulty in manufacturing the carrier, and it is difficult to support more than 4 pairs of pinions due to space constraints. There are disadvantages that result.

 On the other hand, there is always a request to reduce the volume and overall length of the automatic transmission and simplify the structure to improve the mountability on the vehicle, reduce the weight and reduce the manufacturing cost.

Accordingly, the present invention has been made to solve the above-mentioned problems, and one compound planetary gear set which constrains one speed reduction planetary gear set and two planetary gear sets mutually coaxially, and thus clutch 4 It is a simple structure that combines two dogs and two brakes, and realizes the gears of 7th forward and 1st speed to reduce the volume and overall length of the automatic transmission, reduce the weight of the automatic transmission and reduce manufacturing costs. The purpose is to improve the mountability on a vehicle.

The present invention for achieving the above object, the deceleration planetary gear set is directly connected to the input shaft and outputs the rotation of the input shaft in a deceleration rotation, and the non-deceleration rotation and deceleration rotation from the input shaft and the reduction planetary gear set, respectively, It is provided with a composite planetary gear set for receiving a multi-speed transmission rotation to the output shaft receiving the input;

The reduction planetary gear set may include a first operating element that is always restrained by a transmission case, a second operating element that is selectively connected to a plurality of operating elements provided in the composite planetary gear set, and a third operation that is always connected to the input shaft. An element;

The composite planetary gear set may include a fourth operating element selectively connected to the second operating element and selectively restrained to the transmission case, and selectively connected to the input shaft and selectively restrained to the transmission case. A fifth actuating element which always shares a pair of actuating elements of the actuating element of the actuating element; A seventh operating element selectively connected with a second operating element and selectively connected with the input shaft;

A clutch is formed between the input shaft and the fifth operating element, between the input shaft and the seventh operating element, between the second and fourth operating elements, and between the second and seventh operating elements, respectively. Selectively connected by means to transfer power provided from the input shaft to an equivalent transition or a deceleration transition;

The fourth operating element and the fifth operating element are each connected to the transmission case via a brake means, and configured to perform rotational restraint of the corresponding operating element.

According to the power train of the automatic transmission according to the present invention, it implements a shift stage of the seventh forward and one reverse speed with a simple structure, and can reduce the volume and overall length of the automatic transmission, reducing the weight of the automatic transmission and manufacturing cost In this way, the mountability to the vehicle can be improved, and the lubrication and cooling of the automatic transmission can be improved.

In addition, since the one-way clutch acts to convert the operating element into the fixed element in the D range 1 speed, if only the clamping pressure is provided to the newly actuated element when shifting from the D range 1 speed to the 2 speed, Since the automatic release is performed in the operating element fixed by the clutch, the shift control can be facilitated.

In addition, in the shift control for each shift range of the D range, one clutch is operated from 1 to 4 speeds, and the other clutch is operated to be operated from the D range 4 speeds to 7 speeds. The control for releasing only the element and fastening the other friction element not only facilitates the shift control, but also facilitates the two-stage skip shift.

In addition, in the present invention, the output shaft can be arranged on the same axis as the input shaft, when the power train is arranged in the longitudinal direction in the engine room, the output shaft is capable of transmitting power to the rear wheels through a separate propulsion shaft, the electric pipe It can be easily applied to the vehicle of the rear wheel drive (FR).

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

As shown in the figure, the power train of the automatic transmission according to the present invention is the input shaft 10 receives the driving force generated through the combustion action of the engine via a torque converter for implementing the multiplication function of the torque through the flow of the fluid (10) And a deceleration planetary gear set which is directly connected to the input shaft 10 and outputs the rotation provided from the input shaft 10 as a deceleration rotation of a predetermined level of reduction ratio, and the non-deceleration rotation provided from the input shaft 10 and the The planetary gear set includes a planetary gear set configured to selectively receive deceleration rotation transferred from the deceleration planetary gear set and output the shifted rotation of the multi-speed ratio via the output shaft 20.

In the power train of the automatic transmission according to the embodiment of the present invention, the reduction planetary gear set has three operating elements as one planetary gear set, and always outputs the rotation of the input shaft 10 at a constant level of deceleration rotation. .

To this end, the reduction planetary gear set is a first operating element (N1) that is constrained to the transmission case 30, the rotation is always constrained, and a plurality of operating elements provided in the composite planetary gear set A second operation element N2 selectively connected to the second operation element N2 serving as an output element of the deceleration transfer state outputting the power input from the input shaft 10 at a reduction ratio, and always connected to the input shaft 10 to the input shaft 10; A third operating element (N3) acts as an equivalent input element for receiving the power provided from the constant velocity ratio.

In this case, the input shaft 10 is selectively connected to a plurality of operating elements provided in the composite planetary gear set to provide the power of the input shaft 10 at a constant velocity ratio.

In the power train of the automatic transmission according to an embodiment of the present invention, the composite planetary gear set receives the non-deceleration rotation through the input shaft 10 and the deceleration rotation through the reduction planetary gear set, respectively, the output shaft ( In order to output the multi-speed ratio through 20), two pairs of the operating elements of each of the two planetary gear sets are always shared to form four independent operating elements.

To this end, the composite planetary gear set is selectively connected to the second operating element (N2) acts as a deceleration transition input element for receiving the power provided from the input shaft 10 in a deceleration rotation and to the transmission case 30 The fourth operating element (N4) is selectively constrained to act as a fixed element of the rotation is constrained, and is selectively connected to the input shaft 10 to receive the power provided from the input shaft 10 in a non-deceleration rotation A fifth equivalent acting as an input element and selectively restrained by the transmission case 30 to act as a fixed element in which rotation is constrained, and sharing a pair of operating elements of the composite planetary gear set at all times; An operating element N5, which is always connected to the output shaft 20, is input from the input shaft 10 via the interaction between the reduction planetary gear set and the composite planetary gear set. The sixth operating element (N6) and acts as an output element for converting the power to a proper transmission ratio at all times and sharing the other pair of operating elements of the composite planetary gear set at all times, and with the input shaft (10) Optionally connected to act as an equivalent electric input element to receive the power provided from the input shaft 10 in a non-deceleration rotation, and selectively connected to the second operating element (N2) power provided from the input shaft (10) It is provided with a seventh operating element (N7) acting as a deceleration transition input element which is input to the deceleration rotation.

In this case, between the input shaft 10 and the fifth operating element N5 and between the input shaft 10 and the seventh operating element N7, the second operating element N2 and the fourth operating element ( N4) and between the second actuating element N2 and the seventh actuating element N7 are selectively connected to each other via a clutch means to equalize or decelerate the power provided from the input shaft 10. To pass.

In addition, the fourth operating element N4 and the fifth operating element N5 are connected to the transmission case 30 via brake means, respectively, to perform rotational restraint of the corresponding operating element.

According to an embodiment of the present invention, the reduction planetary gear set is a first planetary gear set PG-1 of a single pinion, and the composite planetary gear set is doubled with a second planetary gear set PG-2 of a single pinion. It consists of a third planetary gear set (PG-3) of the pinion.

In the exemplary embodiment of the present invention, the reduction planetary gear set and the composite planetary gear set may include the first planetary gear set PG-1 and the second planetary gear set from the engine side to which the input shaft 10 is connected. PG-2) and the third planetary gear set PG-3, and the input shaft 10 and the output shaft 20 are coaxially spaced apart from each other.

In the embodiment of the present invention, the fifth operating element N5 is selectively connected via the input shaft 10 and the first clutch C-1, and the seventh operating element N7 is the input shaft. (10) and the second clutch (C-2) is selectively connected via the medium, the second operating element (N2) and the seventh operating element (N7) is selectively selected via the third clutch (C-3). The second operating element (N2) and the fourth operating element (N4) is selectively connected via a fourth clutch (C-4), the fourth operating element (N4) is a first brake It is selectively restrained with respect to the transmission case 30 via (B-1), and the fifth actuating element N5 is selective with respect to the transmission case 30 via a second brake B-2. The fifth actuating element N5 is selectively restrained with respect to the transmission case 30 via the one-way clutch OWC, and the one-way clutch OWC is the fifth actuating element N5. Vs) The first is provided in parallel with the second brake (B-2).

In this case, the plurality of operating elements are configured as follows in the embodiment of the present invention.

According to an embodiment of the present invention, the first operating element N1 is composed of the first sun gear S1 of the first planetary gear set PG-1, and the second operating element N2 is formed of the first operating element N2. The first carrier C1 of the first planetary gear set PG-1, and the third operating element N3 comprises the first ring gear R1 of the first planetary gear set PG-1. The fourth operating element N4 includes the second sun gear S2 of the second planetary gear set PG-2, and the fifth operating element N5 includes the second planetary gear set PG. -2) is always connected between the second carrier (C2) and the third sun gear (S3) of the third planetary gear set (PG-3), the sixth operating element (N6) is the second planetary The second ring gear R2 of the gear set PG-2 and the third ring gear R3 of the third planetary gear set PG-3 are always connected to each other. ) Is the third carrier C3 of the third planetary gear set PG-3.

On the other hand, according to an embodiment of the present invention, as shown in Figure 3, the third clutch (C-3) and the one-way clutch (OWC) is operated in the D range 1, D, The first brake B-1 is operated while the third clutch C-3 is maintained in the range 2 speed (the one-way clutch OWC is naturally released), and the D range 3 The fourth clutch C-4 is operated while the first brake B-1 is released while the third clutch C-3 is maintained, and the fourth clutch C-4 is operated. The first clutch C-1 is operated while the fourth clutch C-4 is released while the operation of the third clutch C-3 is maintained, and the first clutch C in the D range 5 speed. The second clutch C-2 is operated while the third clutch C-3 is released while the operation of -1) is maintained, and the first clutch C-1 of the first clutch C-1 Keep working The fourth clutch C-4 is operated while the second clutch C-2 is released while the second clutch C-2 is released, and the first clutch C-1 is maintained in the D range 7. The first brake B-1 is operated while the fourth clutch C-4 is released, and the fourth clutch C-4 and the second brake B-2 are shifted in the R range. This is done.

In addition, the second brake (B-2) may be engaged in place of the one-way clutch (OWC) in the D range 1 speed in order to expect the effect of the engine brake when the vehicle is not driven by the engine while driving, This is usually referred to as L range 1 speed state. Therefore, in the operating element table shown in FIG. 3 of the present invention, the operating element fastened at the D range 1 speed is indicated based on the L range 1 speed, and instead of the second brake B-2 at the D range 1 speed. Therefore, it is well known that one-way clutch (OWC) is provided to facilitate control of the N↔D shift and the 1↔2 shift.

Hereinafter, the shift process for each shift stage in the power train of the automatic transmission according to the present invention will be described as the ratio of the speed by lever analysis.

-D range 1 speed

In the D range 1 speed, the third clutch C-3 and the one-way clutch OWC operate as fastening elements, respectively.

When an input is made to the third operating element N3 through the input shaft 10, the seventh operation is decelerated through the second operating element N2 using the first operating element N1 as a fixed element. The input transferred to the element N7 and the input transferred to the seventh operating element N7 are decelerated through the sixth operating element N6 by using the fifth operating element N5 as a fixed element to decelerate the output shaft 20. Will be displayed.

That is, the speed input to the first ring gear R1 of the first planetary gear set PG-1 through the input shaft 10 is controlled by the first sun gear S1 as a fixed element. After the first deceleration through the carrier C1, the third clutch C-3 is transferred to the third carrier C3 of the third planetary gear set PG-3 through the fastening of the third clutch C-3, and the third carrier is transferred. The speed transferred to (C3) is the output shaft after the second deceleration through the third ring gear (R3) as the third sun gear (S3) acts as a fixed element by the operation of the one-way clutch (OWC). 20) is output at D range 1 speed.

-D range 2 speed

At D range 2 speed, the first brake B-1 operates as a fastening element while the operation of the third clutch C-3 is maintained. At this time, the one-way clutch OWC is naturally released.

When an input is made to the third operating element N3 through the input shaft 10, the seventh operation is decelerated through the second operating element N2 using the first operating element N1 as a fixed element. The input transferred to the element N7 and the input transferred to the seventh operating element N7 are decelerated through the sixth operating element N6 by using the fourth operating element N4 as a fixed element to reduce the output shaft 20. Will be displayed.

That is, the speed input to the first ring gear R1 of the first planetary gear set PG-1 through the input shaft 10 is controlled by the first sun gear S1 as a fixed element. After the first deceleration through the carrier C1, the third clutch C-3 is transferred to the third carrier C3 of the third planetary gear set PG-3 through the fastening of the third clutch C-3, and the third carrier is transferred. The speed transferred to (C3) is the output shaft after the second deceleration through the third ring gear (R3) as the second sun gear (S2) acts as a fixed element by the operation of the one-way clutch (OWC). 20) is output at D range 2 speed.

D range 3-speed

In the D range 3 speed, the fourth clutch C-4 operates as a fastening element while the first brake B-1 is released while the third clutch C-3 is maintained.

When an input is made to the third operating element N3 through the input shaft 10, the first operating element N1 is fixed to the first operating element N2 to be fixed to the third operating element N2. Inputs transitioned to the fourth operating element N4 and the seventh operating element N7, respectively, and the inputs respectively transferred to the fourth operating element N4 and the seventh operating element N7 are the sixth operating element N6. ) Is output to the output shaft 20 in a state where the first reduced level is maintained as it is.

That is, the speed input to the first ring gear R1 of the first planetary gear set PG-1 through the input shaft 10 is controlled by the first sun gear S1 as a fixed element. After the first deceleration through the carrier C1, the fourth clutch C3 is transferred to the third carrier C3 of the third planetary gear set PG-3 through the fastening of the third clutch C-3, and at the same time, the fourth The clutch C-4 is transferred to the second sun gear S2 of the second planetary gear set PG-2 through the engagement of the clutch C-4.

Accordingly, the second planetary gear set PG-2 and the third planetary gear set PG-3 are decelerated and transitioned from the first ring gear R1 of the first planetary gear set PG-1. By maintaining the level as it is to rotate integrally, the output through the third ring gear (R3) of the third planetary gear set (PG-3) is in a state of maintaining the level decelerated in the first carrier (C1) as it is D range is output at 3 speeds.

D range 4-speed

In the D range 4 speed, the fourth clutch C-4 is released while the third clutch C-3 is maintained, and the first clutch C-1 operates as a fastening element.

When an input is made to the third operating element N3 through the input shaft 10, the seventh operation is decelerated through the second operating element N2 using the first operating element N1 as a fixed element. The input of the input shaft 10 is transferred to the fifth operating element N5 as it is.

Accordingly, the speed output to the output shaft 20 through the sixth operating element N6 is smaller than the speed of the input shaft 10 and larger than the speed of the seventh operating element N7.

That is, the speed input to the first ring gear R1 of the first planetary gear set PG-1 through the input shaft 10 is controlled by the first sun gear S1 as a fixed element. After the first deceleration through the carrier (C1) is transferred to the third carrier (C3) of the third planetary gear set (PG-3) via the fastening of the third clutch (C-3), the second The first carrier C-1 is coupled to the second carrier C2 of the planetary gear set PG-2 and the third sun gear S3 of the third planetary gear set PG-3 through the fastening of the first clutch C-1. The input of the input shaft 10 is transferred at constant speed as it is.

As a result, in the third planetary gear set PG-3, the deceleration input of the first carrier C1 input to the third carrier C3 and the input shaft 10 input to the third sun gear S3. Output through the third ring gear (R3) by the constant speed input of less than the speed of the input shaft 10 and greater than the speed input to the third carrier (C3) D range 4 through the output shaft 20 Is output into the system.

-D range 5 speed

In the D-range 5 speed, the third clutch C-3 is released while the first clutch C-1 is maintained, and the second clutch C-2 operates as a fastening element.

When an input is simultaneously made to the fifth operating element N5 and the seventh operating element N7 through the input shaft 10, the input of the input shaft 10 is maintained as it is through the sixth operating element N6. Transitioned and outputted at the D range 6 speed via the output shaft 20.

In other words, the second carrier C2 of the second planetary gear set PG-2 and the third sun gear S3 of the third planetary gear set PG-3 may be formed of the first clutch C-1. The input of the input shaft 10 is transferred at constant speed as it is through the fastening.

In addition, the input of the input shaft 10 is transferred at a constant velocity to the third carrier C3 of the third planetary gear set PG-3 through the fastening of the second clutch C-2.

As a result, since the third ring gear R3 of the third planetary gear set PG-3 has the same speed as the third sun gear S3 and the third carrier C3, the output shaft 20 The speed output through the same state of the so-called constant velocity output becomes the same as the speed of the input shaft (10).

-D range 6 speed

In the D range 6 speed, the fourth clutch C-4 operates as a fastening element while the second clutch C-2 is released while the operation of the first clutch C-1 is maintained.

When an input is made to the third operating element N3 through the input shaft 10, the first operating element N1 is fixed to the first operating element N2 to be fixed to the third operating element N2. The input of the input shaft 10 is transferred to the fourth operating element N5 as it is.

Accordingly, the speed output to the output shaft 20 through the sixth operating element N6 is greater than the speed of the input shaft 10.

That is, the speed input to the first ring gear R1 of the first planetary gear set PG-1 through the input shaft 10 is controlled by the first sun gear S1 as a fixed element. After the first deceleration through the carrier (C1) is transferred to the second sun gear (S2) of the second planetary gear set (PG-2) through the engagement of the fourth clutch (C-4), the second planetary The input shaft is coupled to the second carrier C2 of the gear set PG-2 and the third sun gear S3 of the third planetary gear set PG-3 via the first clutch C-1. The input of (10) is transferred at constant speed as it is.

As a result, in the second planetary gear set PG-2, the deceleration input of the first carrier C1 input to the second sun gear S2 and the input shaft 10 input to the second carrier C2. Output through the second ring gear (R2) by the constant speed input of the speed is increased than the speed of the input shaft 10 is overdrive output to the D range 6 speed through the output shaft (20).

-D range 7 speed

In the D range 7, the first brake B-1 operates as a fastening element while the fourth clutch C-4 is released while the first clutch C-1 is maintained.

The input of the input shaft 10 is directly transferred to the fifth operating element N5 via the first clutch C-1, and the input transferred to the fifth operating element N5 is the fourth operating element N5. The element N4 is increased as a fixed element and output to the output shaft 20.

In other words, the second carrier C2 of the second planetary gear set PG-2 and the third sun gear S3 of the third planetary gear set PG-3 may be formed of the first clutch C-1. The input of the input shaft 10 is transferred at constant speed as it is through the fastening.

Accordingly, in the second planetary gear set PG-2, the constant speed input of the input shaft 10 input to the second carrier C2 causes the second sun gear S2 to receive the first brake B-1. By acting as a fixed element by the operation of)) the output through the second ring gear (R2) is increased to the overdrive output to the D range 8 speed.

R range

In the R range, the fourth clutch C-4 and the second brake B-2 operate as fastening elements, respectively.

When an input is made to the third operating element N3 through the input shaft 10, the fourth operation is decelerated through the second operating element N2 using the first operating element N1 as a fixed element. The input transferred to the element N4 and the input transferred to the fourth operating element N4 are inverted through the sixth operating element N6 with the fifth operating element N5 as a fixed element, thereby reversing the output shaft 20. Will be displayed.

That is, the speed input to the first ring gear R1 of the first planetary gear set PG-1 through the input shaft 10 is controlled by the first sun gear S1 as a fixed element. After the first deceleration through the carrier C1, the second gear is decelerated and transferred to the second sun gear S2 of the second planetary gear set PG-2 through the fastening of the fourth clutch C-4.

Accordingly, in the second planetary gear set PG-2, the deceleration input of the first carrier C1 input to the second sun gear S2 via the fourth clutch C-4 is performed by the second planetary gear set PG-2. As the second carrier C2 acts as a fixed element by the operation of the second brake B-2, the second carrier C2 is decelerated through the second ring gear R2 and is output in the reverse direction through the output shaft 20.

1 is a schematic diagram showing a configuration of a seven-speed power train of an automatic transmission according to an embodiment of the present invention.

FIG. 2 is a diagram illustrating a configuration relationship and a speed relationship for each operating element of a seven-speed power train of an automatic transmission according to an embodiment of the present invention. FIG.

3 is an operating element table showing the operating state of the friction elements for each shift stage for the seven-speed power train of the automatic transmission according to the embodiment of the present invention.

<Description of Symbols for Main Parts of Drawings>

10; Input shaft 20; Output shaft

30; Transmission case

PG-1; First planetary gear set S1; 1st Sun Gear

C1; First carrier R1; 1st ring gear

PG-2; Second planetary gear set S2; 1st Sun Gear

C2; First carrier R2; 1st ring gear

PG-3; Third planetary gear set S3; 1st Sun Gear

C3; First carrier R3; 1st ring gear

C-1; First clutch C-2; Second clutch

C-3; Third clutch C-4; 4th clutch

B-1; First brake B-2; 2nd brake

Claims (5)

Multi-speed shifting to the output shaft 20 by selectively receiving non-deceleration rotation and deceleration rotation from the input shaft 10 and the reduction planetary gear set, respectively, and outputting the rotation of the input shaft 10 as the deceleration rotation. A composite planetary gear set for outputting rotation; The reduction planetary gear set includes a first operating element N1 which is always restrained by the transmission case 30 and a second operating element N2 which is selectively connected to a plurality of operating elements provided in the operating element of the composite planetary gear set. And a third actuating element (N3) always connected to the input shaft (10); The composite planetary gear set is connected to the second operating element (N2) and the fourth operating element (N4) selectively restrained to the transmission case 30, and selectively connected to the input shaft (10) A fifth operating element N5, which is selectively restrained by the transmission case 30 and always shares a pair of operating elements of the composite planetary gear set, is always connected to the output shaft 20 and the composite planetary gear set. The sixth operating element (N6) that always shares the other pair of operating elements of the operating element of, and the seventh operating element selectively connected to the second operating element (N2) and selectively connected to the input shaft (10) Power train of automatic transmission with N7. The method according to claim 1, The reduction planetary gear set is the first planetary gear set PG-1 of the single pinion, and the composite planetary gear set is the second planetary gear set PG-2 of the single pinion and the third planetary gear set of the double pinion ( PG-3); The first operating element N1 is composed of the first sun gear S1 of the first planetary gear set PG-1, and the second operating element N2 is the first planetary gear set PG-1. And a third carrier element (C1), the third actuating element (N3) consists of a first ring gear (R1) of the first planetary gear set (PG-1), the fourth actuating element ( N4) is composed of the second sun gear S2 of the second planetary gear set PG-2, and the fifth operating element N5 is the second carrier of the second planetary gear set PG-2. C2) and the third sun gear (S3) of the third planetary gear set (PG-3) is always connected, and the sixth operating element (N6) of the second planetary gear set (PG-2) The second ring gear R2 and the third ring gear R3 of the third planetary gear set PG-3 are always connected to each other, and the seventh operating element N7 is the third planetary gear set. The power train of the automatic transmission characterized by consisting of the 3rd carrier C3 of (PG-3). The method according to claim 2, The fifth operating element N5 is selectively connected to the input shaft 10 via the first clutch C-1, and the seventh operating element N7 is connected to the input shaft 10 and the second clutch. C-2) is selectively connected via the second operating element (N2) and the seventh operating element (N7) is selectively connected via the third clutch (C-3), the second operation The element N2 and the fourth actuating element N4 are selectively connected to each other via the fourth clutch C-4, and the fourth actuating element N4 is connected to the first brake B-1. Selectively restrained with respect to the transmission case 30, and the fifth actuation element N5 is selectively restrained with respect to the transmission case 30 via a second brake B-2, and the fifth actuation The element N5 is selectively restrained with respect to the transmission case 30 via a one-way clutch OWC, and the one-way clutch OWC is connected to the second brake with respect to the fifth operating element N5. B-2) and Power train of automatic transmission, characterized in that installed in parallel. The method according to claim 3, The first planetary gear set PG-1 and the second planetary gear set PG-2 and the third planetary gear set PG-3 are arranged in order from an engine side to which the input shaft 10 is connected. And the input shaft (10) and the output shaft (20) are coaxially spaced apart from each other. The method according to claim 4, The first clutch C-1, the second clutch C-2, the third clutch C-3, the fourth clutch C-4, and the first brake B-1. The second brake (B-2) and the one-way clutch (OWC) are respectively disposed between the first planetary gear set (PG-1) and the second planetary gear set (PG-2). Power train of automatic transmission.

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