KR20080102475A - 8-speed power train of automatic transmission - Google Patents

Abstract

An 8 step power train of the auto transmission is provided to make the design of transmission more compactable and reduce the quantity of the friction element by applying 4 clutches and 2 brakes. An 8 step power train of the auto transmission comprises the third planetary gear set(PG-3) of the single pinion, the second planet gear set(PG-2) of the double pinion, and the first planetary gear set(PG-1) of the single pinion. The first planetary gear set comprises the first actuating element which is connected to the input shaft(10) and acts on the equivalence input entry; the second actuating element acting on the fixed element; the third actuating element acting on the transition output primitive of the state outputting the power which is input from the input shaft to the moderating ratio.

Description

8-speed power train of automatic transmission

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

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

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

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

5 to 14 are lever analysis diagrams showing the speed relationship for each shift stage of the 8-speed power train of the automatic transmission according to an embodiment of the present invention.

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

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 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 manufacture 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.

 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, a simple planetary gear set, a double pinion planetary gear set and a single pinion planetary gear set, one composite planetary gear set, four clutches and It is a simple structure that combines two brakes, and realizes 8 forward and 2 reverse speeds to reduce the volume and overall length of the automatic transmission, while reducing the weight of the automatic transmission and reducing manufacturing costs. The aim is to provide an eight-speed power train of an automatic transmission that allows for improved mountability in the vehicle.

The present invention for achieving the above object includes a first planetary gear set of a single pinion, a second planetary gear set of a double pinion, and a third planetary gear set of a single pinion;

The first planetary gear set has a first output element connected to an input shaft and acting as an equivalent input element, a second operating element acting as a fixed element, and a transition output in a state of outputting power input from the input shaft at a reduction ratio. A third actuating element acting as the element;

The second planetary gear set and the third planetary gear set may include a transition input element receiving power from the third operating element at a reduction ratio or a fourth operating element acting as an equivalent input element or a fixed element receiving power from the input shaft. And a fifth operating element acting as a transition input element receiving power from the third operating element at a reduction ratio, a sixth operating element acting as an equivalent input element or a fixed element receiving power from the input shaft at a constant speed ratio, and an output shaft. And a seventh operating element acting as an output element connected to it.

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

The eight-speed power train of the automatic transmission according to the present invention includes an input shaft 10 which receives the rotational force of the engine from the engine through a torque converter, a first planetary gear set PG-1 connected to the input shaft 10, and the first gear. A second planetary gear set PG-2 connected to the first planetary gear set PG-1, and the second planetary gear set connected to the input shaft 10 and the second planetary gear set PG-2, respectively. It comprises a third planetary gear set (PG-3) (PG-2) and two operating elements shared with each other and connected to the output shaft (20).

First, the first planetary gear set PG-1 is a simple planetary gear set, which is always connected to the input shaft 10 to act as an equivalent input element, and the first operating element N1 and the rotation are always restrained. It acts as a transition output element in a state in which the second operating element (N2) acting as a fixed element of and the power received from the input shaft (10) is always output at a reduction ratio via the action of the second operating element (N2). It is provided with a third operating element (N3).

In addition, the second planetary gear set PG-2 and the third planetary gear set PG-3 are complex planetary gear sets that share four operating elements with each other to form four independent operating elements. Acts as a transition input element selectively receiving power from the third operating element N3 as a reduction ratio, an equivalent input element selectively directly receiving power from the input shaft 10, or a fixed element in which rotation is constrained selectively; And a fourth operating element N4 sharing one of the operating elements between the second planetary gear set PG-2 and the third planetary gear set PG-3, and the third operating element ( A fifth operating element N5 acting as a transition input element selectively receiving power as a reduction ratio from N3), an equivalent input element selectively receiving power as a constant velocity ratio from the input shaft 10, or optionally rotation is constrained; Fixation of status A sixth operating element N6 which acts as an element and shares another one of the operating elements between the second planetary gear set PG-2 and the third planetary gear set PG-3, and the output shaft Is connected to the (20) and converts the power input from the input shaft 10 into a proper transmission ratio at all times through the interaction between the first to sixth operating elements (N1, N2, N3, N4, N5, N6) It comprises a seventh operating element (N7) acting as an output element for outputting.

In addition, between the input shaft 10 and the fourth and sixth operating elements (N4, N6) is selectively connected via a clutch means to transfer the power provided from the input shaft 10 to an equivalent transition, and the third The operating element N3 and the fourth and fifth operating elements N4 and N5 are selectively connected via a clutch means to transfer the power provided from the input shaft 10 to the deceleration transition.

On the other hand, the fourth operating element (N4) and the sixth operating element (N6) are connected via the transmission case 30 and the brake means, respectively, to perform the rotational restraint of the corresponding operating element.

According to the first embodiment of the present invention, the first operating element N1 is composed of the first ring gear R1 of the first planetary gear set PG-1, and the second operating element N2. Is composed of the first sun gear S1 of the first planetary gear set PG-1, and the third operating element N3 is the first carrier C1 of the first planetary gear set PG-1. The fourth operating element N4 includes a second carrier C2 of the second planetary gear set PG-2 and a third sun gear S3 of the third planetary gear set PG-3. The fifth operating element (N5) is made of a second sun gear (S2) of the second planetary gear set (PG-2), the sixth operating element (N6) is the second planetary The second ring gear R2 of the gear set PG-2 is connected to the third carrier C3 of the third planetary gear set PG-3, and the seventh operation element N7 is And a third ring gear R3 of the third planetary gear set PG-3.

In this case, the first ring gear R1 is directly connected to the input shaft 10, and the third ring gear R3 is directly connected to the output shaft 20.

In addition, the first carrier C1 is configured by integrally connecting a plurality of single pinions engaged between the first sun gear S1 and the first ring gear R1, and the second carrier C2 is A plurality of double pinions engaged between the second sun gear S2 and the second ring gear R2 are integrally connected, and the third carrier C3 is connected to the third sun gear S3 and the first gear. It is configured by integrally connecting a plurality of single pinions engaged between the three ring gear (R3).

According to the second embodiment of the present invention, the first operating element N1 is composed of the first carrier C1 of the first planetary gear set PG-1, and the second operating element N2 is The first sun gear S1 of the first planetary gear set PG-1 is formed, and the third operating element N3 is the first ring gear R1 of the first planetary gear set PG-1. The fourth operating element N4 includes a second carrier C2 of the second planetary gear set PG-2 and a third sun gear S3 of the third planetary gear set PG-3. The fifth operating element (N5) is made of a second sun gear (S2) of the second planetary gear set (PG-2), the sixth operating element (N6) is the second planetary The second ring gear R2 of the gear set PG-2 is connected to the third carrier C3 of the third planetary gear set PG-3, and the seventh operation element N7 is And a third ring gear R3 of the third planetary gear set PG-3.

In this case, the first carrier C1 is directly connected to the input shaft 10, and the third ring gear R3 is directly connected to the output shaft 20.

In addition, the first carrier C1 is configured by integrally connecting a plurality of double pinions engaged between the first sun gear S1 and the first ring gear R1, and the second carrier C2 is A plurality of double pinions engaged between the second sun gear S2 and the second ring gear R2 are integrally connected, and the third carrier C3 is connected to the third sun gear S3 and the first gear. It is configured by integrally connecting a plurality of single pinions engaged between the three ring gear (R3).

According to the first and second embodiments of the present invention, the fourth operating element (N4) is selectively variable connected to the third operating element (N3) as a reduction ratio via the first clutch (C-1), the first It is selectively variably constrained to the transmission case 30 via the brake B-1, and is selectively variably connected to the input shaft 10 at a constant speed ratio via the fourth clutch C-4. The actuating element N5 is selectively variably connected with the third actuating element N3 as a reduction ratio via the second clutch C-2, and the sixth actuating element N6 is the third clutch C-3. In addition, the input shaft 10 is selectively variably connected to the input shaft 10 at a constant velocity ratio, and is selectively variably constrained to the transmission case 30 via the second brake B-2.

In this case, the sixth operating element N6 is selectively provided to the transmission case 30 via a one-way clutch OWC installed in parallel with the second brake B-2 on the transmission case 30. Are variable constrained.

In addition, according to the first embodiment of the present invention, the first clutch C-1 and the second clutch C-2 are connected in parallel with the first carrier C1, and the third clutch C1. -3) and the fourth clutch C-4 are connected to the input shaft 10 in parallel, and the first clutch C-1 and the first brake B-1 are connected to the second carrier C2. ) And the second brake (B-2) and the one-way clutch (OWC) is connected in parallel with the second ring gear (R2).

In addition, according to the second embodiment of the present invention, the first clutch C-1 and the second clutch C-2 are connected in parallel with the first ring gear R1 and the third clutch C-3) and the fourth clutch (C-4) are connected in parallel with the input shaft 10, the first clutch (C-1) and the first brake (B-1) is the second carrier ( C2) is connected in parallel, and the second brake B-2 and the one-way clutch OWC are connected in parallel with the second ring gear R2.

According to the first and second embodiments of the present invention, a path through which power is transmitted from the input shaft 10 to the first to third planetary gear sets PG-1, PG-2, and PG-3 is the first. A first input path input to the fifth operating element N5 at a reduction ratio via an operating element N1 and the third operating element N3, and the first operating element N1 and the third operating element ( A second input path inputted to the fourth operating element N4 at a reduction ratio via N3), a third input path inputted at a constant speed ratio to the fourth operating element N4, and the sixth operating element N6; A fourth input path inputted at a constant speed ratio is set.

In this case, the second input path variably connects between the third operating element N3 and the fifth operating element N5 in the D ranges 1,2, 3, 4, and 5, respectively. It is set by the operation of the clutch C-2.

The second input path may include the first clutch variably connecting the third operating element N3 and the fourth operating element N4 at the D ranges 3, 7 and R range 1, respectively. It is set by the operation of C-1).

In addition, the third input path of the fourth clutch C-4 which variably connects between the first operating element N1 and the fourth operating element N4 in the D ranges 4 and 6, respectively. Is set by operation.

On the other hand, the third input (C) for variably connecting between the first operating element (N1) and the sixth operating element (N6) in the D range 5, 6, 7, and 8, respectively. -3) is set by the operation.

According to the first and second embodiments of the present invention, a path from which power is cut off from the first to third planetary gear sets PG-1, PG-2, and PG-3 is connected to the sixth operating element N6. The first blocking path connecting between the transmission case 30 and the second blocking path connecting the fourth operating element N4 and the transmission case 30 are set.

In this case, the first blocking path is set by the operation of the one-way clutch OWC which variably restrains between the sixth operating element N6 and the transmission case 30 in the D range 1 speed.

In addition, the first brake paths in the R range 1,2 speed and L range, respectively, the second brake (B-2) for variably restraining between the sixth operating element (N6) and the transmission case (30). It is set by the operation of, preferably, the first blocking path in the D range 1, by preventing the reverse rotation of the sixth operating element (N6) by the operation of the one-way clutch (OWC) Is implemented. In addition, in the R range 1,2 speed and L range, the first blocking path restricts the forward / reverse rotation of the sixth operating element N6 by the operation of the second brake B-2, respectively. Is implemented.

In addition, the second blocking path is operated by the first brake B-1 that variably constrains the fourth operating element N4 and the transmission case 30 at D speeds 2 and 8, respectively. Is set.

According to the first and second embodiments of the present invention, each of the operating elements operates the second clutch C-2 and the one-way clutch OWC in the D range 1, and operates the second clutch in the D range 2 speed. The first brake B-1 is operated (in this case, the one-way clutch OWC is naturally released) while the operation of the second clutch C-2 is maintained, and the second at the third speed D range. The first clutch C-1 operates while the first brake B-1 is released while the operation of the clutch C-2 is maintained, and the second clutch C in the D range 4 speed. The fourth clutch C-4 is operated while the first clutch C-1 is released while the operation of -2) is maintained, and the second clutch C-2 of the D range 5 is operated. When the fourth clutch C-4 is released while the operation is maintained, the third clutch C-3 is operated, and the operation of the third clutch C-3 is maintained at the D range 6 speed. The second clutch in a state The fourth clutch C-4 is operated while the tooth C-2 is released, and the fourth clutch C- is maintained while the third clutch C-3 is maintained in the D range 7. 4) is released, the first clutch C-1 is operated, and the first clutch C-1 is released while the operation of the third clutch C-3 is maintained in the D range 8 speed. The first brake B-1 operates, the first clutch C-1 and the second brake B-2 operate in the R range 1, and the fourth brake in the R range 2. The clutch C-4 and the second brake B-2 operate to shift.

According to the first and second embodiments 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 eight-speed power train in the engine room in the longitudinal direction, Since the output shaft 20 is capable of transmitting power to the rear wheels through a separate propulsion shaft, the 8-speed power train of the present invention can be applied to the vehicle of the electric tube rear wheel drive FR.

Hereinafter, the shift process for each shift stage in the eight-speed power train of the automatic transmission according to the present invention will be described as the ratio of the speed by lever analysis. Power transmission in this process will be described based on the power train according to the first embodiment of the present invention.

-D range 1 speed

As illustrated in FIG. 5, in the D range 1 speed, the second clutch C-2 and the one-way clutch OWC operate as fastening elements, respectively.

When an input is made to the first operating element N1 through the input shaft 10, the fifth operation is decelerated through the third operating element N3 by using the second operating element N2 as a fixed element. The input transitioned to the element N5 and the input transitioned to the fifth operating element N5 are decelerated through the seventh operating element N7 with the sixth operating element N6 as a fixed element, so that 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) is transferred to the second sun gear (S2) of the second planetary gear set (PG-2) via the second clutch (C-2), the second sun gear (S2) The speed shifted to the third planetary gear after the second deceleration through the second carrier (C2) as the second ring gear (R2) acts as a fixed element by the operation of the one-way clutch (OWC). The speed transferred to the third sun gear S3 of the set PG-3, and the speed transferred to the third sun gear S3 is fixed by the operation of the one-way clutch OWC by the third carrier C3. After the third deceleration through the third ring gear (R3) is output to the D range 1 speed through the output shaft (20).

-D range 2 speed

As shown in FIG. 6, in the D range 2 speed, the first brake B-1 operates as a fastening element while the operation of the second clutch C-2 is maintained. At this time, the one-way clutch OWC is naturally released.

When an input is made to the first operating element N1 through the input shaft 10, the fifth operation is decelerated through the third operating element N3 by using the second operating element N2 as a fixed element. The input transitioned to the element N5 and the input transitioned to the fifth operating element N5 are decelerated through the seventh operating element N7 with the fourth operating element N4 as a fixed element, so that 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) is transferred to the second sun gear (S2) of the second planetary gear set (PG-2) via the second clutch (C-2), the second sun gear (S2) The speed shifted to) is reduced after the second reduction through the second ring gear R2 as the second carrier C2 acts as a fixed element by the operation of the first brake B-1. The third gear C3 of the planetary gear set PG-3 is transferred to the third carrier C3, and the third sun gear S3 is operated by the first brake B-1. As a fixed element by means of the output through the output shaft 20 at the second speed D range in the state slightly increased than the second reduction through the third ring gear (R3).

D range 3-speed

As illustrated in FIG. 7, in the D range 3 speed, the first clutch C-1 is released while the first brake B-1 is released while the operation of the second clutch C-2 is maintained. It acts as a fastening element.

When an input is made to the first operating element N1 through the input shaft 10, the second operation element N2 is fixed to the first operating element N3 as the fixed element to decelerate first. An input that is simultaneously transitioned to a fourth operating element N4 and a fifth operating element N5, and simultaneously transferred to the fourth operating element N4 and a fifth operating element N5 is configured to move the seventh operating element N7. Through the first decelerated level is maintained as it is output to the output shaft (20).

That is, the output through the third ring gear R3 is output at the D range 3 speed while maintaining the level decelerated in the first carrier C1.

D range 4-speed

As illustrated in FIG. 8, in the D range 4 speed, the fourth clutch C-4 is released while the first clutch C-1 is released while the operation of the second clutch C-2 is maintained. It acts as a fastening element.

When an input is made to the first operating element N1 through the input shaft 10, the fifth operation is decelerated through the third operating element N3 by using the second operating element N2 as a fixed element. The input of the input shaft 10 is transferred to the fourth operating element N4 as it is.

Accordingly, the speed output to the output shaft 20 through the seventh operating element N7 is smaller than the speed of the input shaft 10 and larger than the speed of the fifth operating element N5.

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) via the second clutch (C-2), the third planetary gear set The input of the input shaft 10 is transferred to the third sun gear S3 of PG-3 as it is at a constant speed.

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. The output through the second ring gear (R2) by the constant speed input of is smaller than the speed of the input shaft 10 and larger than the speed input to the second sun gear (S2).

Subsequently, in the third planetary gear set PG-3, an input (which is smaller than a constant velocity input of the input shaft 10) and the input shaft that are equivalently transitioned from the second ring gear R2 to the third carrier C3. The output through the third ring gear R3 is decelerated than the speed of the input shaft 10 by an input equivalently transitioned from (10) to the third sun gear S3, and then through the output shaft 20, D range 4 Is output into the system.

-D range 5 speed

As shown in FIG. 9, in the D range 5 speed, the third clutch C-3 is released while the fourth clutch C-4 is released while the operation of the second clutch C-2 is maintained. It acts as a fastening element.

When an input is made to the first operating element N1 through the input shaft 10, the fifth operation is decelerated through the third operating element N3 by using the second operating element N2 as a fixed element. The input of the input shaft 10 is transferred to the sixth operating element N6 as it is.

Accordingly, the speed output to the output shaft 20 through the seventh operating element N7 is smaller than the speed of the input shaft 10 and larger than the speed of the third operating element N3.

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) via the second clutch (C-2), the third planetary gear set The input of the input shaft 10 is transferred at constant velocity to the third carrier C3 of PG-3.

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 ring gear R2. By the constant velocity input of), the output through the second carrier C2 is larger than the speed of the input shaft 10.

Subsequently, in the third planetary gear set PG-3, an input (which is larger than a constant velocity input of the input shaft 10) and the input shaft that are equivalently transitioned from the second carrier C2 to the third sun gear S3. The output through the third ring gear R3 is decelerated more than the speed of the input shaft 10 by the input equivalently transitioned from (10) to the third carrier C3, and through the output shaft 20, the D range 5 Is output into the system.

-D range 6 speed

As shown in FIG. 10, in the D range 6 speed, the fourth clutch C-4 is released while the second clutch C-2 is released while the operation of the third clutch C-3 is maintained. It acts as a fastening element.

When an input is simultaneously made to the fourth operating element N4 and the sixth operating element N6 through the input shaft 10, the input of the input shaft 10 is maintained as it is through the seventh operating element N7. Transitioned and outputted at the D range 6 speed via the output shaft 20.

That is, the speed output through the output shaft 20 is in a state of so-called constant velocity output which is equal to the speed of the input shaft 10.

-D range 7 speed

As illustrated in FIG. 11, in the D range 7, the first clutch C-1 is released while the fourth clutch C-4 is released while the operation of the third clutch C-3 is maintained. It acts as a fastening element.

When an input is made to the first operating element N1 through the input shaft 10, the fourth operation is decelerated through the third operating element N3 using the second operating element N2 as a fixed element. The input of the input shaft 10 is transferred to the sixth operating element N6 as it is.

Accordingly, the speed output to the output shaft 20 through the seventh operating element N7 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 carrier (C2) of the second planetary gear set (PG-2) via the first clutch (C-1), the third planetary gear set The input of the input shaft 10 is transferred to the third carrier C3 of (PG-3) at constant speed through the third clutch C-3.

As a result, in the third planetary gear set PG-3, the deceleration input of the second carrier C2 input to the third sun gear S3 and the input shaft 10 input to the third carrier C3. The output through the third ring gear (R3) by the constant speed input of the speed is greater than the speed of the input shaft 10 is overdrive output to the D range 7 speed through the output shaft (20).

-D range 8 speed

As shown in FIG. 12, in the D range 8 speed, the first brake C-1 is released while the first clutch C-1 is released while the operation of the third clutch C-3 is maintained. It acts as a fastening element.

The input of the input shaft 10 is transferred to the sixth operating element N6 as it is, and the input transferred to the sixth operating element N6 is increased by using the fourth operating element N4 as a fixed element. It is output to the output shaft 20.

That is, the third clutch C-3 includes the second ring gear R2 of the second planetary gear set PG-3 and the third carrier C3 of the third planetary gear set PG-3. The input of the input shaft 10 is transferred at constant speed as it is.

Accordingly, in the third planetary gear set PG-3, the constant speed input of the input shaft 10 input to the third carrier C3 causes the third sun gear S3 to receive the first brake B-1. By acting as a fixed element by the operation of)) the output through the third ring gear (R3) is increased to the over-drive output to the D range 8 speed.

R range 1 speed

As shown in FIG. 13, in the R range 1 speed, the first clutch C-1 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 fourth operation is decelerated through the third operating element N3 using the second operating element N2 as a fixed element. The input transitioned to the element N4 and the input transitioned to the fourth operating element N4 are reversed through the seventh operating element N7 with the sixth operating element N6 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 C2 is transferred to the second carrier C2 of the second planetary gear set PG-2 via the first clutch C-1.

Accordingly, in the third planetary gear set PG-3, the deceleration input of the first carrier C1 input to the third sun gear S3 through the second carrier C2 is the third carrier C3. ) Acts as a fixed element by the operation of the second brake (B-2) is secondly decelerated through the third ring gear (R3) is output in the reverse direction through the output shaft (20).

R range 2 speed

As shown in FIG. 14, in the R range 2 speed, the fourth clutch C-4 and the second brake B-2 operate as fastening elements, respectively.

When an input is made to the fourth operating element N4 through the input shaft 10, the output shaft 20 is reversed through the seventh operating element N7 using the sixth operating element N6 as a fixed element. )

That is, the speed at which the third sun gear S3 of the third planetary gear set PG-3 is input through the input shaft 10 is controlled by the third carrier C3 as a fixed element. The first gear is decelerated through the gear R3 to output the reverse direction through the output shaft 20. At this time, the output speed is larger than that of the R range 1 speed.

This is because the input transitioned to the third sun gear S3 is a deceleration input through the first carrier C1 at the R range 1 speed, while the input is a constant speed transition through the input shaft 10 at the R range 2 speed.

As described above, according to the eighth speed power train of the automatic transmission according to the present invention, the eighth forward speed and the second reverse speed stage can be implemented with a simple structure, and the volume and the overall length of the automatic transmission can be reduced, The weight reduction and manufacturing cost can be reduced, the mountability to the vehicle can be improved, and the lubrication and cooling of the automatic transmission can be improved.

In addition, the eight-speed power train of the automatic transmission according to the present invention can reduce the number of friction elements compared to the existing eight-speed power train by applying four clutches and two brakes, thereby enabling a more compact design of the transmission. Will be effective.

In addition, since the one-way clutch serves to convert the operating element into a fixed element in the D range 1 speed, if only the clamping pressure is provided to the newly engaged operating 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 present invention, the output shaft can be arranged on the same axis as the input shaft, when the eight-speed power train in the longitudinal direction in the engine room, the output shaft is capable of power transmission to the rear wheels through a separate propulsion shaft, It can be easily applied to a vehicle of electric tube rear wheel drive (FR).

Claims (20)

A first planetary gear set PG-1 connected to the input shaft 10, a second planetary gear set PG-2 connected to the first planetary gear set PG-1, and the input shaft 10 and the A third planetary gear set PG-3 connected to the second planetary gear set PG-2 and sharing the two planetary elements with the second planetary gear set PG-2, and connected to the output shaft 20, respectively. It is configured to include; The first planetary gear set PG-1 is a simple planetary gear set. The first planetary gear set PG-1 is connected to the input shaft 10 and acts as an equivalent input element. The first planetary gear set PG-1 is a fixed element in which rotation is constrained. The second operating element N2 acting and the third operating element acting as a transition output element in a state of outputting power input from the input shaft 10 at a reduction ratio via the action of the second operating element N2. (N3); The second planetary gear set PG-2 and the third planetary gear set PG-3 are complex planetary gear sets each sharing two operating elements to form four independent operating elements. A fourth input acting as a transition input element selectively receiving power from the operating element N3 as a reduction ratio, an equivalent input element selectively directly receiving power from the input shaft 10, or a fixed element in which rotation is constrained selectively; Selecting the operating element N4, the fifth operating element N5 acting as a transition input element selectively receiving power from the third operating element N3 as the reduction ratio, and the power from the input shaft 10 as the constant velocity ratio. The sixth operating element (N6) and the output shaft 20 is connected to the sixth operating element (N6) acting as an equivalent input element or a fixed element of the rotation is constrained selectively, the first to sixth operating elements (N1, N2, Between N3, N4, N5, N6) Having an actuating element of claim 7 (N7) acting to mutually enter the power acting from the input shaft 10 as a medium to an output element that converts to an appropriate gear ratio, and; Between the input shaft 10 and the fourth and sixth operating elements N4 and N6, and between the third and fourth operating elements N3 and the fourth and fifth operating elements N4 and N5 are selectively selected through clutch means. Connected to transfer the power provided from the input shaft (10) to an equivalent transition or a deceleration transition; The fourth actuating element N4 and the sixth actuating element N6 are connected to the transmission case 30 and the brake means, respectively, so as to perform rotational restraint of the corresponding actuating element. Genus power train. The method according to claim 1, The first operating element N1 is composed of a first ring gear R1 of the first planetary gear set PG-1, and the second operating element N2 is the first planetary gear set PG-. The first sun gear (S1) of 1), the third operating element (N3) is made of a first carrier (C1) of the first planetary gear set (PG-1), the fourth operating element ( N4) is made by connecting 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), the fifth operation The element N5 is composed of the second sun gear S2 of the second planetary gear set PG-2, and the sixth operating element N6 is the second of the second planetary gear set PG-2. A ring gear R2 and a third carrier C3 of the third planetary gear set PG-3 are connected to each other, and the seventh operating element N7 is the third planetary gear set PG-3. 8-speed power train of the automatic transmission, characterized in that consisting of a third ring gear (R3) of. The method according to claim 2, The first speed gear train of the automatic transmission, characterized in that the first ring gear (R1) is directly connected to the input shaft (10), the third ring gear (R3) is directly connected to the output shaft (20). The method according to claim 2, The first carrier C1 is configured by integrally connecting a plurality of single pinions engaged between the first sun gear S1 and the first ring gear R1, and the second carrier C2 is configured as the first carrier gear. A plurality of double pinions that are engaged between the two-wire gear (S2) and the second ring gear (R2) is integrally connected, and the third carrier (C3) is the third sun gear (S3) and the third ring An eight-speed power train of an automatic transmission, characterized in that configured by integrally connecting a plurality of single pinions engaged between the gear (R3). The method according to claim 1, The first operating element N1 is composed of the first carrier C1 of the first planetary gear set PG-1, and the second operating element N2 is the first planetary gear set PG-1. It is made of a first sun gear (S1) of, the third operating element (N3) is made of a first ring gear (R1) of the first planetary gear set (PG-1), the fourth operating element ( N4) is made by connecting 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), the fifth operation The element N5 is composed of the second sun gear S2 of the second planetary gear set PG-2, and the sixth operating element N6 is the second of the second planetary gear set PG-2. The ring gear R2 and the third carrier C3 of the third planetary gear set PG-3 are connected to each other, and the seventh operating element N7 is the third planetary gear set PG-3. The eight-speed power train of the automatic transmission, characterized in that consisting of the third ring gear (R3). The method according to claim 5, The eighth speed train of the automatic transmission, characterized in that the first carrier (C1) is directly connected to the input shaft (10), the third ring gear (R3) is directly connected to the output shaft (20). The method according to claim 5, The first carrier C1 is configured by integrally connecting a plurality of double pinions engaged between the first sun gear S1 and the first ring gear R1, and the second carrier C2 is configured as the first carrier gear. A plurality of double pinions that are engaged between the two-wire gear (S2) and the second ring gear (R2) is integrally connected, and the third carrier (C3) is the third sun gear (S3) and the third ring An eight-speed power train of an automatic transmission, characterized in that configured by integrally connecting a plurality of single pinions engaged between the gear (R3). The method according to claim 2 or 5, The fourth operating element N4 is variably connected to the third operating element N3 via the first clutch C-1 as a reduction ratio, and the transmission case 30 is provided via the first brake B-1. It is variably constrained to and is variably connected to the input shaft 10 through the fourth clutch C-4 as a constant velocity ratio, and the fifth operating element N5 is connected to the second clutch C-2 via the second clutch C-2. The sixth operating element N3 is variably connected as a reduction ratio, and the sixth operating element N6 is variably connected to the input shaft 10 as a constant speed ratio via a third clutch C-3 and a second brake is provided. (B-2) the eight-speed power train of the automatic transmission, characterized in that it is variably constrained to the transmission case (30). The method according to claim 8, The sixth operating element N6 is selectively variably constrained to the transmission case 30 via a one-way clutch OWC installed in parallel with the second brake B-2 on the transmission case 30. The eight-speed power train of the automatic transmission characterized in that. The method according to claim 9, The path through which power is transmitted from the input shaft 10 to the first to third planetary gear sets PG-1, PG-2, and PG-3 is the first operating element N1 and the third operating element ( A first input path inputted to the fifth operating element N5 at a reduction ratio via N3), and the fourth operating element N4 via the first operating element N1 and the third operating element N3. The second input path inputted at the reduction ratio, the third input path inputted at the constant speed ratio to the fourth operating element N4, and the fourth input path inputted at the constant speed ratio to the sixth operating element N6. Featuring an eight-speed power train with automatic transmission. The method according to claim 10, The second clutch C variably connects between the third operating element N3 and the fifth operating element N5 in the D ranges 1,2, 3, 4, and 5, respectively, in the D ranges 1,2,3,4,5. 8 speed power train of the automatic transmission, characterized by the operation of -2). The method according to claim 10, The first clutch C− for variably connecting the third operating element N3 and the fourth operating element N4 at the D range 3, 7 speed and the R range 1 speed, respectively. An eight-speed power train of an automatic transmission, characterized by the operation of 1). The method according to claim 10, The third input path is configured to operate the fourth clutch C-4 to variably connect between the first operating element N1 and the fourth operating element N4 in the D ranges 4 and 6, respectively. 8 speed power train of the automatic transmission, characterized in that is set by. The method according to claim 10, The fourth clutch C-3 variably connects between the first operating element N1 and the sixth operating element N6 in the D ranges 5, 6, 7, and 8, respectively. 8-speed power train of the automatic transmission, characterized in that it is set by the operation. The method according to claim 9, The path from which power is cut off from the first to third planetary gear sets PG-1, PG-2, and PG-3 is connected to the sixth operating element N6 and the transmission case 30. And a second cutoff path connecting the cutoff path and the fourth operating element (N4) and the transmission case (30). The method according to claim 15, The first blocking path is set by the operation of the one-way clutch (OWC) that variably restrains between the sixth operating element (N6) and the transmission case 30 in the D range 1 speed. 8-speed power train with automatic transmission. The method according to claim 15, The first breaking path operates the second brake B-2 that variably constrains the sixth operating element N6 and the transmission case 30 in the R range 1,2 speeds and L ranges, respectively. The eight-speed power train of the automatic transmission, characterized in that it is set by. The method according to claim 15, The second blocking path is set by the operation of the first brake B-1 which variably restrains between the fourth operating element N4 and the transmission case 30 at D speeds 2 and 8, respectively. The eight-speed power train of the automatic transmission characterized in that. The method according to claim 9, Each of the operating elements operates the second clutch C-2 and the one-way clutch OWC in the D range 1 speed, and maintains the operation of the second clutch C-2 in the D range 2 speed. The first brake B-1 operates in the state, and the first brake B-1 is released while the operation of the second clutch C-2 is maintained in the D range 3 speed. The first clutch C-1 is released while the first clutch C-1 is operated and the operation of the second clutch C-2 is maintained in the D range 4 speed, and thus the fourth clutch C-1 is released. -4) is operated, the fourth clutch (C-4) is released while the second clutch (C-2) is maintained in the D range 5, the third clutch (C-3) is The fourth clutch C-4 is operated while the second clutch C-2 is released while the third clutch C-3 is maintained in the D range 6 speed. The third clutch in the range 7 speed (C-3) The first clutch C-1 is operated while the fourth clutch C-4 is released while the operation of the fourth clutch C-4 is maintained, and the operation of the third clutch C-3 is performed at the D range 8 speed. The first brake B-1 is operated while the first clutch C-1 is released in the maintained state, and the first clutch C-1 and the second brake B are in the R range 1 speed. -2), and the fourth clutch (C-4) and the second brake (B-2) is operated in the R range 2 speed, the eight speed power train of the automatic transmission, characterized in that the shift. The method according to claim 2 or 5, The output shaft 20 is the eight-speed power train of the automatic transmission, characterized in that arranged in the same axis and spaced apart from each other on the same axis line.

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