KR20090032842A - 6-speed power train of automatic transmission - Google Patents

Abstract

A 6-speed power train of an automatic transmission is provided to reduce the volume and total length of the automatic transmission by using a simple structure which has two sets of planetary gear trains. A 6-speed power train of an automatic transmission comprises an input shaft(10), the first planetary gear set(PG-1) and the second planetary gear set(PG-2). The driving force is delivered to the input shaft from an engine through a torque converter. The first planetary gear set comprises one actuating element connected with the input shaft. The second planetary gear set comprises two actuating elements, which are variably connected through the medium of the rest two actuating elements of the first planetary gear set and a clutch means, and the rest one actuating element which is connected with an output shaft(20).

Description

6-speed power train of automatic transmission

The present invention relates to a six-speed power train of an automatic transmission, and more particularly, to six-speed power of an automatic transmission that realizes six forward speeds and one reverse speed through two sets of planetary gear trains and a plurality of clutches and brakes. It's about the train.

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 transmission 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 and acceleration performance and improving transmission 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 ravenue type. The planetary gearsets of the lavender type have long pinions and short pinions. It has to be a structure that supports at the same time, there is a difficulty in the production of the carrier, it is difficult to support more than four pairs of pinions due to space constraints, and in order to transmit power of high torque, the width of the gearbox must be increased or the pinion must be made large, resulting in a large transmission. There is a disadvantage.

In addition, the lavender type planetary gear set is to secure the power transmission path of the carrier and the ring gear, to have a structure that can control the power through the friction element of the two sun gears respectively engaged with the long pinion and short pinion, Inevitably, the two sun gears must be formed in an overlapping hollow shaft structure, and one sun gear must completely penetrate the inside of the other sun gear, so that the overlapping hollow shaft structure increases the volume and overall length of the transmission. In addition, the two superimposed hollow shaft structure acts as a major obstacle in forming a flow path of oil transferred radially from the center axis of the transmission, thereby having a structural problem of poor lubricity inside the transmission. .

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.

In addition, the gear train used in the conventional six-speed automatic transmission adopts at least three sets of planetary gears, resulting in excessive volume, length, and weight of the automatic transmission, thereby increasing weight of the vehicle and deteriorating fuel efficiency. have.

Therefore, the present invention has been made to solve the above-mentioned problems, a simple structure combining two planetary gear sets, four clutches and two brakes to implement a six-speed forward and one reverse speed gearbox automatic transmission. The aim is to reduce the volume and overall length of the engine, reduce the weight of the automatic transmission, reduce manufacturing costs, and improve the mountability of the vehicle.

The present invention for achieving the above object comprises a first planetary gear set connected to the input shaft, and a second planetary gear set selectively connected to the first planetary gear set and connected to the output shaft;

The first planetary gear set may include a first operating element connected to the input shaft and acting as an equivalent input element, and a transition output element or selectively rotating to selectively output the power input to the first operating element at a forward rotation of the reduction ratio. A second actuating element acting as the restrained stationary element, and a transition output element for selectively outputting the power input to the first actuating element in reverse rotation of the reduction ratio, or a actuating element acting as the stationary restraint selectively restraining rotation. Three operating elements;

The second planetary gear set includes a fourth operating element selectively acting as a transition input element selectively connected to the third operating element or a fixed element selectively restrained from rotation, and a transition input selectively connected to the second operating element. A fifth operating element acting as an element or a fixed element selectively restrained from rotation or an equivalent input element selectively receiving power from the input shaft as a constant velocity ratio, and connected to the first, second, third, fourth, A sixth operating element serving as an output element for converting the power input from the input shaft into an appropriate transmission ratio via the interaction between the five operating elements and outputting it;

Selectively connecting between the second operating element and the fifth operating element, selectively connecting between the third operating element and the fourth operating element, connecting between the fifth operating element and the sixth operating element And clutch means for connecting between said input shaft and said fifth actuating element;

Selectively constrains rotation of the second operating element and the third operating element, respectively, and rotates the second operating element and the fifth operating element or cooperates with the third operating element via a cooperative action with the clutch means; Brake means for selectively restraining rotation of said fourth actuating element respectively simultaneously.

According to the six-speed power train of the automatic transmission according to the present invention, a simple structure having two sets of planetary gear trains can realize a shift stage of six forward speeds and one reverse speed, thereby reducing the volume and overall length of the automatic transmission. As a result, the weight reduction and manufacturing cost of the automatic transmission can be reduced, and the mountability to the vehicle can be improved.

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

In particular, the present invention, in each operating element of the first planetary gear set and the second planetary gear set, it is possible to limit the speed for the remaining operating elements other than the operating element connected to the output shaft to below the speed of the input shaft, It is possible to prevent the deterioration of the transmission due to the high-speed rotation of a specific operating element.

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

As shown in Figures 1 to 3, the six-speed power train of the automatic transmission according to the present invention is the input shaft 10 receives the driving force from the engine through the torque converter, and the first planetary directly connected to the input shaft 10 A second planetary gear connected to the gear set PG-1 and the input shaft 10 and the first planetary gear set PG-1 via a clutch means and directly connected to the output shaft 20, respectively. It consists of a set PG-2.

The first planetary gear set PG-1 has one operating element that is always connected to the input shaft 10. The second planetary gear set PG-2 includes two operation elements and the output shaft 20 that are variably connected via the clutch means and the remaining two operating elements of the first planetary gear set PG-1. It has one remaining actuating element which is always connected.

The second planetary gear set PG-2 selectively connects one actuating element and the other two actuating elements connected to the output shaft 20 by means of clutch means, so that the second planetary gear set PG- All the operating elements of 2) are configured to work together.

The six-speed power train of the present invention restrains a specific operating element of the operating elements of the first planetary gear set PG-1 and the second planetary gear set PG-2 with respect to the transmission case 30. It further comprises a brake means for stopping the rotation of the operating element.

First, the first planetary gear set PG-1 is a speed reduction planetary gear set that decelerates the rotation provided from the input shaft 10 and outputs it to the second planetary gear set PG-2. ) Is always connected to the first operating element (N1) and acts as an equivalent input element, and the transition output element or selectively rotating to selectively output the power input to the first operating element (N1) in the forward rotation of the reduction ratio The second operating element (N2) acting as a fixing element to be constrained, a transition output element for selectively outputting the power input to the first operating element (N1) in reverse rotation of the reduction ratio, or the fixed element to which rotation is selectively restrained It has a third operating element (N3) acting as.

That is, the first planetary gear set PG-1 may be configured as a fixed element using either the second operating element N2 or the third operating element N3 using the first operating element N1 as an input element. The other one is set as an output element connected to the second planetary gear set PG-2.

In addition, the second planetary gear set PG-2 selectively performs non-deceleration rotation provided directly through the input shaft 10 and deceleration rotation provided indirectly through the first planetary gear set PG-1. A simple planetary gear set that receives an input and outputs a gear ratio of a plurality of stages through the output shaft 20, and functions as a transition input element selectively connected to the third operating element N3 or a fixed element in which rotation is selectively restrained. Selecting the power as the constant velocity ratio from the fourth operating element (N4), the transition input element selectively connected to the second operating element (N2) or the fixed element in the state that the rotation is restricted or the input shaft (10) The fifth operating element (N5) acting as an equivalent input element received by the input, and connected to the output shaft 20, the first, second, third, fourth, fifth operating element (N1, N2, N3, N4, N5) Input from the input shaft 10 via the interaction between And a sixth operating element N6, which acts as an output element for converting power into a proper transmission ratio and outputting the same.

In other words, the second planetary gear set PG-2 has one of the fourth operating element N4 and the fifth operating element N5 as a fixed element, and the other one of the first planetary gear set. A transition input element that receives the output of the reduction ratio provided from the corresponding operating element of PG-1, wherein either the fourth operating element N4 or the fifth operating element N5 is the first planetary gear. The sixth operating element N6 is set as the output element, or the sixth operating element N6 is set as the transition input element of the reduction ratio with respect to the set PG-1 or as the transition input element of the constant velocity ratio with respect to the input shaft 10.

In addition, the clutch means selectively connects between the second actuating element N2 and the fifth actuating element N5 to perform the dependent transition in the rotational state, and the third actuating element N3 and the fourth By selectively connecting between the operating elements (N4) to perform the dependent transition of the rotational state, by connecting between the fifth operating element (N5) and the sixth operating element (N6) the second planetary gear set (PG- Each operating element of 2) is integrally connected, and the constant speed transition of power is performed by connecting between the input shaft 10 and the fifth operating element N5.

In this case, between the second operating element N2 and the fifth operating element N5 and between the third operating element N3 and the fourth operating element N4, the dependent transition of the rotational state is A rotational state that transfers power to deceleration between the corresponding operating elements of the first planetary gear set PG-1 and the second planetary gear set PG-2 and interacts with the brake means. It means the transition of redemption of each.

On the other hand, the brake means selectively restrains the rotation of the second actuating element N2 and the third actuating element N3, respectively, and the second actuating element N2 via a cooperative action with the clutch means. And selectively constrain the rotation of the fifth operating element N5 or the rotation of the third operating element N3 and the fourth operating element N4, respectively.

That is, the brake means selectively restrains the rotation of the second actuating element N2 and the third actuating element N3, respectively, and the clutch when restraining the rotation with respect to the second actuating element N2. Simultaneously constrains rotation of the fifth actuation element N5 through interaction with the means, and the fourth actuation element through interaction with the clutch means upon restraint of rotation with respect to the third actuation element N3. Constrain the rotation of N4 at the same time.

Here, the first and second planetary gear sets PG-1 and PG-2 may include the first planetary gear set PG-1 and the second planetary gear set PG- from the engine side to which the input shaft 10 is connected. 2) the first planetary gear set (PG-1) and the second planetary gear set (PG-2) is composed of a single pinion planetary gear set, respectively, the output shaft 20 is the input shaft It is arranged to be spaced coaxially with (10).

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. A second carrier C2 of -2), and the sixth operating element N6 is formed of a second ring gear R2 of the second planetary gear set PG-2.

In this case, the first sun gear S1 is directly connected to the input shaft 10, and the second ring gear R2 is directly connected to the output shaft 20.

According to an embodiment of the present invention, the clutch means comprises a first clutch C-1, a second clutch C-2, a third clutch C-3 and a fourth clutch C-4. The brake means includes a first brake B-1 and a second brake B-2.

The third operating element N3 and the fourth operating element N4 are selectively variably connected to each other via the first clutch C-1, so that the input shaft C when the first clutch C-1 is fastened. The power provided from 10) is transferred to the deceleration transition, and is selectively variably constrained to the transmission case 30 by the first brake B-1, so that the first brake B-1 is fastened when the first brake B-1 is fastened. The rotational restraint for the third operating element N3 and the fourth operating element N4 is performed.

The second actuating element N2 and the fifth actuating element N5 are selectively variably connected via the second clutch C-2 so that the input shaft C is fastened when the second clutch C-2 is fastened. The power provided from 10) is transferred to the deceleration transition and is selectively variably constrained to the transmission case 30 via the second brake B-2, so that the second brake B-2 is fastened when the second brake B-2 is fastened. Rotational restraint is performed on the second operating element N2 and the fifth operating element N5.

The fifth operating element N5 and the sixth operating element N6 are selectively variably connected via the third clutch C-3 so that the second clutch C-3 is fastened when the third clutch C-3 is fastened. Each operating element of the planetary gear set PG-2 is integrally interlocked. In this case, the third clutch C-3 is referred to as a direct clutch, and when the second planetary gear set is fastened, This function converts the input / output speed ratio into constant velocity ratio by changing the rotational speed of all working elements of (PG-2) to the same state.

The fifth operating element N5 is selectively variably connected through the input shaft 10 and the fourth clutch C-4, and the fourth clutch C-4 is fastened when the input shaft 10 is engaged. Power is output from the fifth operating element (N5) to provide a constant velocity ratio.

According to an embodiment of the present invention, a path through which power is transmitted from the input shaft 10 to the first and second planetary gear sets PG-1 and PG-2 is transmitted from the third operating element N3 to the fourth. A first input path selectively inputted to the operating element N4 at a reduction ratio, and a second input path selectively inputted from the second operating element N2 to the fifth operating element N5 at a reduction ratio; The third planetary gear set PG by integrally connecting a third input path selectively inputted to the fifth operating element N5 at a constant velocity ratio, and between the fifth operating element N5 and the sixth operating element N6; And-a fourth input path for interlocking each operating element of -2).

In this case, the first clutch C variably connects between the third operating element N3 and the fourth operating element N4 at the D ranges 1, 6 speed and the R range, respectively. Set by the operation of -1), the power transmitted from the input shaft 10 is decelerated through the third operating element N3 and then transmitted to the fourth operating element N4.

The second input path is operated by the second clutch C-2 which variably connects the second operating element N2 and the fifth operating element N5 in the D ranges 2 and 3, respectively. It is set by, to decelerate the power transmitted from the input shaft 10 through the second operating element (N2) and then transfer it to the fifth operating element (N5).

In addition, the third input path operates the fourth clutch C-4 to variably connect between the input shaft 10 and the fifth operating element N5 in the D ranges 4, 5, and 6, respectively. It is set by, to directly transfer the power provided from the input shaft 10 to the fifth operating element (N5) at a constant velocity ratio.

On the other hand, the third input (C-) variably connects between the fifth operating element (N5) and the sixth operating element (N6) in the D range 2, 4 speed and the R range, respectively. By the operation of 3), the rotation of the second planetary gear set PG-2 is integrated.

According to the exemplary embodiment of the present invention, the path of which the rotation is restricted by the power cut off in the first and second planetary gear sets PG-1 and PG-2 may include the third operating element N3 and the transmission case 30. Rotation between the first blocking path connecting between the third operating element (N3) and the fourth operating element (N4) via the first clutch C-1. A second blocking path that simultaneously restrains the transmission case 30, a third blocking path connecting the second operating element N2 and the transmission case 30, and the second operating element N2. It is set as a fourth blocking path for simultaneously restraining their rotation with respect to the transmission case 30 in a state in which the fifth operating element N5 is connected via the second clutch C-2.

In this case, the first breaking path operates the first brake B-1, which variably restrains the third operating element N3 and the transmission case 30 in the D ranges 2 and 4, respectively. Is set by.

In addition, the second blocking path is connected between the third operating element N3 and the fourth operating element N4 through the fastening of the first clutch C-1 in the D ranges 3 and 5, respectively. The rotation is set by the operation of the first brake B-1 which variably constrains their rotation with respect to the transmission case 30.

In addition, the third blocking path is operated at the second brake B-2 to variably restrain the second operating element N2 and the transmission case 30 at the D range 6 speed and the R range, respectively. Is set by.

Meanwhile, the fourth blocking path is connected between the second operating element N2 and the fifth operating element N5 through the fastening of the second clutch C-2 in the D range 1 speed. Is set by the operation of the second brake B-2 which variably constrains their rotation with respect to the transmission case 30.

According to the exemplary embodiment of the present invention, each of the operating elements operates the first clutch C-1, the second clutch C-2 and the second brake B-2 in the D range 1. , While the first clutch C-1 and the second brake B-2 are released while the second clutch C-2 is maintained in the D range 2, the third clutch ( C-3) and the first brake (B-1) are operated, respectively, and the operation of the second clutch (C-2) and the first brake (B-1) in the D range 3 is maintained, respectively The first clutch C-1 is operated while the third clutch C-3 is released, and the first brake B-1 is maintained in the D range 4 speed. As the clutch C-1 and the second clutch C-2 are released, the third clutch C-3 and the fourth clutch C-4 operate, respectively. The operation of the fourth clutch C-4 and the first brake B-1 The first clutch C-1 is operated while the third clutch C-3 is released in each retained state, and the first clutch C-1 and the fourth clutch C are operated in the D range 6 speed. The second brake B-2 is operated while the first brake B-1 is released while the operation of C-4 is maintained, and the first clutch C-1 and the first clutch C-1 are operated in the R range. The third clutch C-3 and the second brake B-2 operate to shift.

According to an embodiment of the present invention, the output shaft 20 is arranged to be spaced apart from each other on the same axis line with the input shaft 10, when the six-speed power train in the longitudinal direction in the engine room, the output shaft 20 Since the power transmission is possible to the rear wheels through a separate propulsion shaft, it is possible to apply the six-speed power train of the present invention to the vehicle of the electric tube rear wheel drive (FR).

In addition, the first clutch C-1, the second clutch C-2, and the fourth clutch C-4 may include the first planetary gear set PG-1 and the second planetary gear set. And a third clutch C-3 between the second carrier C2 and the second ring gear R2 of the second planetary gear set PG-2. Is placed.

In addition, the first brake B-1 is disposed in parallel to the connection path between the first ring gear R1 and the first clutch C-1, and is installed in the transmission case 30. The second brake B-2 is installed between the first carrier C1 and the transmission case 30.

Hereinafter, the shift process for each shift stage in the six-speed 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

As shown in FIG. 4, in the D range 1 speed, the first clutch C-1, the second clutch C-2, and the second brake B-2 operate as fastening elements, respectively.

When an input is made to the first operating element N1 through the input shaft 10, the second operating element N2 is fixed to the reverse direction through the third operating element N3 as the fixed element. The input transferred to the fourth operating element N4 and the input transferred to the fourth operating element N4 are decelerated in the forward direction through the sixth operating element N6 with the fifth operating element N5 as a fixed element. It is output to the output shaft 20.

That is, the speed at which the first sun gear S1 of the first planetary gear set PG-1 is input through the input shaft 10 is the first ring as the first carrier C1 acts as a fixed element. After the first deceleration through the gear (R1) is transferred to the second sun gear (S2) of the second planetary gear set (PG-2), the speed transferred to the second sun gear (S2) is the second carrier (C2). ) Acts as a fixed element by the operation of the second brake (B-2) and the second ring gear (R2) after the second deceleration is output through the output shaft 20 at the D range 1 speed.

In this case, the first ring gear R1 of the first planetary gear set PG-1 and the second sun gear S2 of the second planetary gear set PG-2 are the first clutch C-1. The first carrier C1 of the first planetary gear set PG-1 and the second carrier C2 of the second planetary gear set PG-2 are connected to each other by fastening of the second clutch. Simultaneously connected with each other by the fastening of (C-2), the second brake B-2 serves as a fixing element that is simultaneously restrained with respect to the transmission case 30.

-D range 2 speed

As shown in FIG. 5, in the D range 2 speed, the first clutch C-1 and the second brake B-2 are released, respectively, while the operation of the second clutch C-2 is maintained. The third clutch C-3 and the first brake B-1 operate as fastening elements, respectively.

When an input is made to the first operating element N1 through the input shaft 10, the third operating element N3 is fixed as a fixed element and then decelerated in the forward direction through the second operating element N2. The input transitioned to the fifth operating element N5 and the transition to the fifth operating element N5 is output to the output shaft 20 via the sixth operating element N6.

That is, the speed input to the first sun gear S1 of the first planetary gear set PG-1 through the input shaft 10 is the first ring gear R1 as the fixed element acts as the fixed element. After the first deceleration through the carrier C1, the speed is transferred to the second carrier C2 of the second planetary gear set PG-2, and the speed transferred to the second carrier C2 is the third clutch C. -3) is transferred to the second ring gear (R2) at a constant speed, and then output to the D range 2 speed through the output shaft (20).

At this time, the first carrier C1 of the first planetary gear set PG-1 and the second carrier C2 of the second planetary gear set PG-2 are formed of the second clutch C-2. The first ring gear (R1) of the first planetary gear set (PG-1) is connected to each other by a fastening is fixed to the transmission case 30 by the fastening of the first brake (B-1). Each element of the second planetary gear set PG-2 is integrated by the fastening of the third clutch C-3 and is interlocked at a constant speed.

D range 3-speed

As shown in FIG. 6, in the D range 3 speed, the third clutch C-3 is released while the operation of the second clutch C-2 and the first brake B-1 is maintained. The first clutch C-1 acts as a fastening element.

When an input is made to the first operating element N1 through the input shaft 10, the third operating element N3 is fixed as a fixed element and then decelerated in the forward direction through the second operating element N2. The input transferred to the fifth operating element N5 and the input transferred to the fifth operating element N5 are accelerated through the sixth operating element N6 by using the fourth operating element N4 as a fixed element, thereby increasing the output shaft. Is output to (20).

That is, the speed input to the first sun gear S1 of the first planetary gear set PG-1 through the input shaft 10 is the first ring gear R1 as the fixed element acts as the fixed element. After the first deceleration through the carrier C1, the speed is transferred to the second carrier C2 of the second planetary gear set PG-2, and the speed transferred to the second carrier C2 is the second sun gear S2. ) Is constrained to increase through the second ring gear R2 and output through the output shaft 20 at the third speed D range.

At this time, the first carrier C1 of the first planetary gear set PG-1 and the second carrier C2 of the second planetary gear set PG-2 are formed of the second clutch C-2. The first ring gear R1 of the first planetary gear set PG-1 and the second sun gear S2 of the second planetary gear set PG-2 are connected to each other by fastening. Simultaneously connected with each other by the fastening of (C-1), the first brake B-1 acts as a fixing element that is simultaneously restrained with respect to the transmission case 30.

D range 4-speed

As illustrated in FIG. 7, in the D range 4 speed, the first clutch C-1 and the second clutch C-2 are released while the first brake B-1 is maintained. The third clutch C-3 and the fourth clutch C-4 operate as fastening elements, respectively.

When the input is made to the first operating element N1 through the input shaft 10, the third operating element N3 is fixed as a fixed element, but is decelerated in the forward direction through the second operating element N2. Disconnection between the second actuating element N2 and the fifth actuating element N5 prevents further power transfer.

On the other hand, the constant velocity ratio is input to the fifth operating element N5 through the input shaft 10, and the input of the constant velocity ratio transferred to the fifth operating element N5 is the sixth operating element ( It is output to the output shaft 20 via N6).

That is, a speed input at a constant velocity ratio to the second carrier C2 of the second planetary gear set PG-2 through the input shaft 10 may be performed by the operation of the third clutch C-3. The gear is shifted at constant speed to the ring gear R2 and then output at the D range 4 speed through the output shaft 20.

In this case, the first ring gear R1 of the first planetary gear set PG-1 acts as a fixing element that is restrained with respect to the transmission case 30 by fastening the first brake B-1. Each operating element of the second planetary gear set PG-2 is integrated by the third clutch C-3 and interlocked at a constant speed, so that the fourth clutch C-4 is fastened. The input transferred from the input shaft 10 to the second carrier C2 at a constant speed ratio through the second ring gear R2 is output at a constant speed ratio, and the output through the output shaft 20 is output to the input shaft 10. ) Is the same level as the direct drive.

-D range 5 speed

As shown in FIG. 8, in the D range 5 speed, the third clutch C-3 is released while the operations of the fourth clutch C-4 and the first brake B-1 are maintained. The first clutch C-1 operates as a fastening element.

When the input is made to the first operating element N1 through the input shaft 10, the third operating element N3 is fixed as a fixed element, but is decelerated in the forward direction through the second operating element N2. Disconnection between the second actuating element N2 and the fifth actuating element N5 prevents further power transfer.

On the other hand, the input of the constant velocity ratio is made to the fifth operating element (N5) through the input shaft 10, the input of the constant velocity ratio transferred to the fifth operating element (N5) is the fourth operating element ( With N4) as the fixed element, it is increased through the sixth operating element N6 and outputted to the output shaft 20.

That is, a speed input at a constant velocity ratio to the second carrier C2 of the second planetary gear set PG-2 through the input shaft 10 may be performed by the operation of the third clutch C-3. The gear is shifted at constant speed to the ring gear R2 and then output at the D range 5 speed through the output shaft 20.

In this case, the first ring gear R1 of the first planetary gear set PG-1 and the second sun gear S2 of the second planetary gear set PG-2 are the first clutch C-1. It is connected to each other by the fastening of the first brake (B-1) at the same time acts as a fixing element that is constrained to the transmission case 30 at the same time, the fastening of the fourth clutch (C-4) Since the input transferred from the input shaft 10 to the second carrier C2 at a constant speed ratio is increased through the second ring gear R2 and output, the output through the output shaft 20 is in an overdrive state. Is switched.

-D range 6 speed

As shown in FIG. 9, in the D range 6 speed, the first brake B-1 is released while the operations of the first clutch C-1 and the fourth clutch C-4 are maintained. While the second brake B-2 operates as a fastening element.

When an input is made to the first operating element N1 through the input shaft 10, the second operating element N2 is fixed to the reverse direction through the third operating element N3 as the fixed element. The input transferred to the fourth operating element N4 and transferred to the fourth operating element N4 mediates interaction with the input of the constant velocity ratio transferred from the input shaft 10 to the fifth operating element N5. The speed is increased in the forward direction to the D range 6 speed through the output shaft (20).

That is, the input through the input shaft 10 is decelerated through the first ring gear R1 of the first planetary gear set PG-1, so that the second sun gear (PG-2) of the second planetary gear set PG-2 is decelerated. The second ring gear R2 of the second planetary gear set PG-2 is transferred to the second planetary gear set PG-2 at the same time as the transition to S2) and provided to the second carrier C2 of the second planetary gear set PG-2. The output is overdriven.

In this case, the first ring gear R1 of the first planetary gear set PG-1 and the second sun gear S2 of the second planetary gear set PG-2 are the first clutch C-1. The first carrier C1 of the first planetary gear set PG-1 is restrained with respect to the transmission case 30 by the fastening of the second brake B-2. It acts as a fixed element.

R range

As shown in FIG. 10, in the R range, the first clutch C-1, the third clutch C-3, and the second brake B-2 operate as fastening elements, respectively.

When an input is made to the first operating element N1 through the input shaft 10, the second operating element N2 is fixed to the reverse direction through the third operating element N3 as the fixed element. The input transitioned to the fourth actuation element N4 and the transition to the fourth actuation element N4 is output to the output shaft 20 via the sixth actuation element N6.

That is, the speed at which the first sun gear S1 of the first planetary gear set PG-1 is input through the input shaft 10 is the first ring as the first carrier C1 acts as a fixed element. After decelerating in the reverse direction through the gear R1, the reverse rotation state is maintained through the output shaft 20 through the second ring gear R2 of the second planetary gear set PG-2.

In this case, the first ring gear R1 of the first planetary gear set PG-1 and the second sun gear S2 of the second planetary gear set PG-2 are the first clutch C-1. The first carrier C1 of the first planetary gear set PG-1 is restrained with respect to the transmission case 30 by the fastening of the second brake B-2. It acts as a fixing element, each element of the second planetary gear set (PG-2) is integrated by the fastening of the third clutch (C-3) is interlocked at a constant speed.

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

Figure 2 is an analysis diagram showing the configuration of each operating element for the six-speed power train of the automatic transmission according to the present invention.

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

4 to 10 is a lever analysis diagram showing the speed relationship for each shift stage for the six-speed power train of the automatic transmission according to the present invention.

Claims (17)

The first planetary gear set PG-1 connected to the input shaft 10 and the second planetary gear set PG-2 selectively connected to the first planetary gear set PG-1 and connected to the output shaft 20. It includes; The first planetary gear set PG-1 selectively connects the first operating element N1 connected to the input shaft 10 to serve as an equivalent input element and the power input to the first operating element N1. A second operating element N2 acting as a transition output element that outputs the forward rotation of the reduction ratio or a fixed element that is selectively constrained by rotation, and the power input to the first operating element N1 selectively rotates the reduction ratio A third actuating element N3 acting as a transition output element for outputting or a fixed element for which rotation is constrained; The second planetary gear set PG-2 may include a fourth operating element N4 acting as a transition input element selectively connected to the third operating element N3 or a fixing element selectively restrained from rotation, and A transition input element selectively connected to the second actuating element N2, a fixed element selectively restrained from rotation, or a fifth actuating element acting as an equivalent input element selectively receiving power from the input shaft 10 as a constant velocity ratio; (N5) and connected to the output shaft 20 from the input shaft 10 via the interaction between the first, second, third, fourth, fifth operating elements (N1, N2, N3, N4, N5) A sixth operating element (N6) serving as an output element for converting the input power into an appropriate transmission ratio and outputting it; Selectively connecting between the second operating element (N2) and the fifth operating element (N5), selectively connecting between the third operating element (N3) and the fourth operating element (N4), and A clutch means for connecting between a fifth operating element (N5) and the sixth operating element (N6) and connecting between the input shaft (10) and the fifth operating element (N5); Selectively restrains the rotation of the second operating element N2 and the third operating element N3, respectively, and the second operating element N2 and the fifth operating element through a cooperative action with the clutch means; And a brake means for selectively restraining rotation of (N5) or rotation of the third actuation element (N3) and the fourth actuation element (N4), respectively. The method according to claim 1, The first and second planetary gear sets PG-1 and PG-2 may have a first planetary gear set PG-1 and a second planetary gear set PG-2 from an engine side to which the input shaft 10 is connected. The first planetary gear set PG-1 and the second planetary gear set PG-2 are each composed of a single pinion planetary gear set, and the output shaft 20 is the input shaft 10. 6-speed power train of the automatic transmission, characterized in that spaced apart in the same axis. The method according to claim 1, 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), wherein the sixth operating element (N6) is composed of a second ring gear (R2) of the second planetary gear set (PG-2). The method according to claim 3, The first sun gear (S1) is connected to the input shaft (10), the second ring gear (R2) is a six-speed power train of the automatic transmission, characterized in that connected to the output shaft (20). The method according to claim 3, The third operating element N3 and the fourth operating element N4 are selectively variably connected via a first clutch C-1, and the transmission case (1) is provided via a first brake B-1. Optionally variable constrained at 30); The second operating element N2 and the fifth operating element N5 are selectively variably connected via a second clutch C-2, and the transmission case (2) via a second brake B-2. Optionally variable constrained at 30); The fifth operating element (N5) and the sixth operating element (N6) are selectively variably connected via a third clutch (C-3); The fifth operating element (N5) is a six-speed power train of the automatic transmission, characterized in that the variable input selectively connected via the input shaft (10) and the fourth clutch (C-4). The method according to claim 5, The path from which the power is transmitted from the input shaft 10 to the first and second planetary gear sets PG-1 and PG-2 is reduced at a reduction ratio from the third operating element N3 to the fourth operating element N4. A first input path that is input, a second input path that is inputted from the second operating element N2 to the fifth operating element N5 at a reduction ratio, and a third inputted at a constant speed ratio to the fifth operating element N5 An input path and a fourth input path for interlocking each operating element of the second planetary gear set PG-2 by integrally connecting the fifth operating element N5 and the sixth operating element N6. 6 speed power train of the automatic transmission, characterized in that set. The method according to claim 6, The first clutch C-1 in which the first input path is variably connected between the third operating element N3 and the fourth operating element N4 at the D ranges 1, 6 speed, and R range, respectively. The six-speed power train of the automatic transmission, characterized by the operation of. The method according to claim 6, The second input path is operated by the second clutch C-2 which variably connects the second operating element N2 and the fifth operating element N5 in the D ranges 2 and 3, respectively. 6 speed power train of the automatic transmission, characterized in that set. The method according to claim 6, The third input path is operated by the fourth clutch C-4 which variably connects the input shaft 10 and the fifth operating element N5 in the D ranges 4, 5, and 6, respectively. 6 speed power train of the automatic transmission, characterized in that set. The method according to claim 6, The fourth clutch C-3 variably connects the fifth operating element N5 and the sixth operating element N6 at the D ranges 2, 4 speed, and R range, respectively. The six-speed power train of the automatic transmission, characterized by the operation of. The method according to claim 5, The path from which power is cut off in the first and second planetary gear sets PG-1 and PG-2 may include a first blocking path connecting the third operating element N3 and the transmission case 30; A second constraining their rotation with respect to the transmission case 30 in a state in which the third operating element N3 and the fourth operating element N4 are connected through the first clutch C-1; A blocking path, a third blocking path connecting the second operating element N2 and the transmission case 30, and the second operating element N2 and the fifth operating element N5 between the second operating element N2 and the transmission case 30. A six-speed power train of an automatic transmission, characterized in that it is set as a fourth cutoff path for restraining their rotation with respect to the transmission case (30) in the state connected via a clutch (C-2). The method according to claim 11, The first blocking path is set by an operation of the first brake B-1 that variably restrains the third operating element N3 and the transmission case 30 in the D ranges 2 and 4, respectively. The six-speed power train of the automatic transmission, characterized in that. The method according to claim 11, The second blocking path is connected between the third operating element (N3) and the fourth operating element (N4) through the fastening of the first clutch (C-1), respectively, in the D ranges 3 and 5, respectively. The six-speed power train of the automatic transmission, characterized in that it is set by the operation of the first brake (B-1) to variably restrain their rotation with respect to the transmission case (30) in the state. The method according to claim 11, The third blocking path is operated by the second brake B-2 which variably restrains the second operating element N2 and the transmission case 30 at the D range 6 speed and the R range, respectively. 6 speed power train of the automatic transmission, characterized in that set. The method according to claim 11, The fourth blocking path is connected to the second operating element N2 and the fifth operating element N5 through the fastening of the second clutch C-2 in the D range 1 speed. The six-speed power train of the automatic transmission, characterized in that it is set by the operation of the second brake (B-2) that variably restrains the rotation of the transmission case (30). The method according to claim 5, Each of the operating elements operates the first clutch C-1, the second clutch C-2, and the second brake B-2 in the D range 1 speed, and operates the first clutch in the D range 2 speed. In the state where the operation of the second clutch C-2 is maintained, the first clutch C-1 and the second brake B-2 are released, respectively, and the third clutch C-3 and the first clutch are released. The brakes B-1 operate, respectively, and the third clutch C− is operated while the operation of the second clutch C-2 and the first brake B-1 is maintained at the third speed D range. 3) is released, the first clutch C-1 is operated, and the first clutch C-1 and the first clutch C-1 are maintained while the operation of the first brake B-1 is maintained in the D range 4 speed. As the second clutch C-2 is released, the third clutch C-3 and the fourth clutch C-4 operate, respectively, and the fourth clutch C-4 in the D range 5 speed. And the first brake B in the state where the operation of the first brake B-1 is maintained, respectively. The first clutch C-1 is operated while the third clutch C-3 is released, and the operation of the first clutch C-1 and the fourth clutch C-4 is performed at the D range 6 speed. The second brakes B-2 are operated while the first brakes B-1 are released in the maintained state, and the first clutch C-1 and the third clutch C- in the R range. 3) and the sixth speed train of the automatic transmission, characterized in that the shift is performed by operating the second brake (B-2), respectively. The method according to claim 5, The first clutch C-1, the second clutch C-2, and the fourth clutch C-4 are the first planetary gear set PG-1 and the second planetary gear set PG. The third clutch C-3 is disposed between the second carrier C2 and the second ring gear R2 of the second planetary gear set PG-2. The first brake B-1 is disposed in parallel to the connection path between the first ring gear R1 and the first clutch C-1, and is installed in the transmission case 30. The second brake (B-2) is a six-speed power train of the automatic transmission, characterized in that installed between the first carrier (C1) and the transmission case (30).

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