KR20090124432A - Power train for automatic transmission - Google Patents

Abstract

PURPOSE: A power train for an automatic transmission is provided to reduce the weight and manufacturing costs by reducing the volume and total length of the auto transmission. CONSTITUTION: In a device, a deceleration planetary gear set outputs rotation of an input shaft(10) to deceleration rotating. A complex planetary gear set outputs change rotation speed of a multi-stage to an output shaft(20). A first actuating element is always restrained by the transmission case(30). A second actuating element is selectively connected to a plurality of actuating elements of the complex planetary gear set. A third actuating element is always connected to an input shaft. A fourth actuating element is always connected to the second actuating element.

Description

Power train for automatic transmission

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 Lavigneaux Type. The planetary gearsets of the Lavignon type have long pinions and short carriers. Since the pinion must be supported at the same time, there is a difficulty in manufacturing the carrier, and it is difficult to support 4 or more pairs of pinions due to space constraints. Therefore, in order to transmit power of high torque, the width of the transmission must be increased or the pinion must be enlarged. There are disadvantages that result.

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

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

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

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

The composite planetary gear set may include a fourth operating element which is always connected to the second operating element, a fifth operating element which is always connected to the output shaft, and an input shaft, which is selectively connected to the transmission case, and selectively restrained by the transmission case. A sixth actuating element which always shares a pair of actuating elements of the gear set, and is selectively connected to the second actuating element and the third actuating element and selectively restrained by the transmission case and the composite planetary gear set; A seventh operating element for selectively sharing another pair of operating elements of the operating elements of;

The input shaft and the sixth operating element, the second operating element and the seventh operating element, and the third operating element and the seventh operating element are respectively selectively connected via a clutch means and provided from the input shaft. Transfers power to an equivalent transition or a deceleration transition;

The sixth operating element and the seventh operating element are each connected to the transmission case via a brake means to be configured to perform rotational restraint of the corresponding operating element.

According to the powertrain of the automatic transmission according to the present invention, the eight-speed forward and reverse two-speed transmission stage with a simple structure, and the volume and overall length of the automatic transmission can be reduced, reducing the weight of the automatic transmission and manufacturing cost In this way, the mountability to the vehicle can be improved, and the lubrication and cooling of the automatic transmission can be improved.

In addition, the 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.

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 the shift control for each shift range of the D range, one clutch is operated from 1 to 5 speeds, and the other clutch is operated from the D range 5 speeds to 8 speeds. The control for releasing only the element and fastening the other friction element not only facilitates the shift control, but also facilitates the two-stage skip shift.

In addition, in the present invention, the output shaft can be arranged on the same axis as the input shaft, when the 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).

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

As shown in the figure, the power train of the automatic transmission according to the present invention is the input shaft 10 receives a driving force generated through the combustion action of the engine via a torque converter for performing power transmission according to the flow of the fluid, and Reduction planetary gear set which is directly connected to the input shaft 10 and outputs the rotation provided from the input shaft 10 in a deceleration rotation of a predetermined level of reduction ratio, and the non-deceleration rotation and the reduction planetary gear provided from the input shaft 10 It is provided with a composite planetary gear set for selectively receiving the deceleration rotation is transferred from the set to each output through the output shaft 20 to output a multi-stage speed ratio rotation.

In the power train of the automatic transmission according to the first and second embodiments of the present invention, the deceleration planetary gear set has three operating elements as one planetary gear set, so that the rotation of the input shaft 10 is always decelerated at a constant level. Output by rotation.

To this end, the reduction planetary gear set is constrained to the transmission case 30 to the first operating element (N1) that acts as a fixed element in a state where the rotation is always restrained, and a plurality of operating elements of the composite planetary gear set, respectively The second operating element (N2) and the input shaft (10) which is always connected to the individual power transmission path and selectively connected to act as the output element of the deceleration before the output of the power input from the input shaft (10) at a reduction ratio; And a third operating element which is always connected to act as an equivalent input element, and selectively connected to the composite planetary gear set, and the power input from the input shaft 10 also acts as an equivalent charge output element in a state of outputting at a constant velocity ratio. (N3) is provided.

In the power train of the automatic transmission according to the first and second embodiments of the present invention, the composite planetary gear set selectively inputs non-deceleration rotation through the input shaft 10 and deceleration rotation through the reduction planetary gear set, respectively. In order to receive the multi-speed transmission ratio through the output shaft 20, a pair of operating elements of each operating element of the two planetary gear sets are always shared to form five independent operating elements, or another pair of operating elements Are optionally further shared to form four independent actuating elements.

To this end, the composite planetary gear set is always connected to the second operating element (N2) and the fourth operating element (N4) which acts as a deceleration transition input element for receiving the power provided from the input shaft 10 in a deceleration rotation; And connected to the output shaft 20 to convert the power input from the input shaft 10 into an appropriate transmission ratio at all times through the interaction between the reduction planetary gear set and the composite planetary gear set. The fifth operating element (N5) to be selectively connected to the input shaft 10 acts as an equivalent electric input element for receiving the power provided from the input shaft 10 in a non-deceleration rotation, the transmission case 30 A sixth actuating element N6, which is selectively constrained to and acts as a fixed element in which the rotation is restrained, and always shares a pair of actuating elements of the compound planetary gear set, and the second actuating element; It is selectively connected to the moving element (N2) and the third operating element (N3) acts as a deceleration transition and equivalent charge input element that receives the power provided from the input shaft 10 in deceleration rotation and non-deceleration rotation, The seventh operating element (N7) is selectively constrained to the transmission case 30 to act as a fixed element in the rotation is restrained, and selectively share another pair of operating elements of the composite planetary gear set Equipped.

In this case, between the input shaft 10 and the sixth operating element N6, between the second operating element N2 and the seventh operating element N7, and the third operating element N3 and the seventh. Each of the operating elements N7 is selectively connected via a clutch means, respectively, to transfer the power provided from the input shaft 10 to an equivalent transition or a deceleration transition.

In addition, the sixth operating element N6 and the seventh operating element N7 are connected to the transmission case 30 via brake means, respectively, to perform rotational restraint of the corresponding operating element.

According to the first embodiment of the present invention, the reduction planetary gear set is the first planetary gear set PG-1 of the double pinion, and the composite planetary gear set is the second planetary gear set PG-2 of the double pinion. And the third planetary gear set (PG-3) of the single pinion.

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

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

In the first and second embodiments of the present invention, the second operating element (N2) and the seventh operating element (N7) is selectively connected via the first clutch (C-1), the seventh Between the pair of actuating elements forming the actuating element N7 is selectively connected via a second clutch C-2, and the sixth actuating element N6 is connected to the input shaft 10 and the third clutch ( C-3) is selectively connected via the third, the third operating element (N3) and the seventh operating element (N7) is selectively connected via the fourth clutch (C-4), the seventh operation The element N7 is selectively restrained with respect to the transmission case 30 via the first brake B-1, and the sixth operating element N6 is the second brake B-2 via the second brake B-2. It is selectively restrained with respect to the transmission case 30, and the sixth operating element N6 is selectively restrained with respect to the transmission case 30 via the one-way clutch OWC, and the one-way clutch OWC. Award The sixth operating element N6 is installed in parallel with the second brake B-2.

In this case, the plurality of operating elements are configured as follows in the first and second embodiments of the present invention.

According to the first 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 The first ring gear (R1) of the first planetary gear set (PG-1), the third operating element (N3) is the first carrier (C1) of the first planetary gear set (PG-1). The fourth operating element (N4) is made of a second sun gear (S2) of the second planetary gear set (PG-2), the fifth operating element (N5) is the third planetary gear set And a third ring gear R3 of PG-3, wherein the sixth operating element N6 includes the second ring gear R2 of the second planetary gear set PG-2 and the third planetary planet. It is made by always connecting between the third carrier (C3) of the gear set (PG-3), the seventh operating element (N7) and the second carrier (C2) of the second planetary gear set (PG-2) It is made by selectively connecting between the third sun gear (S3) of the third planetary gear set (PG-3).

According to the second 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 The first ring gear (R1) of the first planetary gear set (PG-1), the third operating element (N3) is the first carrier (C1) of the first planetary gear set (PG-1). The fourth operating element (N4) is made of a second sun gear (S2) of the second planetary gear set (PG-2), the fifth operating element (N5) is the third planetary gear set And a third ring gear R3 of PG-3, wherein the sixth operating element N6 includes the second carrier C2 and the third planetary gear of the second planetary gear set PG-2. It is made by always connecting between the third carrier (C3) of the set (PG-3), the seventh operating element (N7) and the second ring gear (R2) of the second planetary gear set (PG-2) It is made by selectively connecting between the third sun gear (S3) of the third planetary gear set (PG-3).

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

To this end, the reduction planetary gear set is constrained to the transmission case 30 to the first operating element (N1) that acts as a fixed element in a state where the rotation is always restrained, and a plurality of operating elements of the composite planetary gear set, respectively The second operating element (N2) and the input shaft (10) which is always connected to the individual power transmission path and selectively connected to act as the output element of the deceleration before the output of the power input from the input shaft (10) at a reduction ratio; And a third operating element which is always connected to act as an equivalent input element, and selectively connected to the composite planetary gear set, and the power input from the input shaft 10 also acts as an equivalent charge output element in a state of outputting at a constant velocity ratio. (N3) is provided.

In the power train of the automatic transmission according to the third embodiment of the present invention, the composite planetary gear set receives the non-deceleration rotation through the input shaft 10 and the deceleration rotation through the reduction planetary gear set, respectively, In order to output at multiple gear ratios through the output shaft 20, a pair of operating elements of each operating element of the two planetary gear sets are always shared to form five independent operating elements, or another pair of operating elements is selected. Further shared to form four independent operating elements.

To this end, the composite planetary gear set is always connected to the second operating element (N2) and the fourth operating element (N4) which acts as a deceleration transition input element for receiving the power provided from the input shaft 10 in a deceleration rotation; And connected to the output shaft 20 to convert the power input from the input shaft 10 into an appropriate transmission ratio at all times through the interaction between the reduction planetary gear set and the composite planetary gear set. The fifth operating element (N5) to be selectively connected to the input shaft 10 acts as an equivalent electric input element for receiving the power provided from the input shaft 10 in a non-deceleration rotation, the transmission case 30 A sixth operating element N6 selectively restrained on and acting as a fixed element in which rotation is constrained and selectively sharing a pair of operating elements of the operating planetary gear set; It is selectively connected to the second operating element (N2) and the third operating element (N3) acts as a deceleration transition and equivalent electric charge input element for receiving the power provided from the input shaft 10 in the deceleration rotation and non-deceleration rotation In addition, the seventh operating element (N7) that is selectively restrained to the transmission case 30 to act as a fixed element of the rotation is constrained, and always share another pair of operating elements of the operation of the composite planetary gear set ).

In this case, between the input shaft 10 and the sixth operating element N6, between the second operating element N2 and the seventh operating element N7, and the third operating element N3 and the seventh. Each of the operating elements N7 is selectively connected via a clutch means, respectively, to transfer the power provided from the input shaft 10 to an equivalent transition or a deceleration transition.

In addition, the sixth operating element N6 and the seventh operating element N7 are connected to the transmission case 30 via brake means, respectively, to perform rotational restraint of the corresponding operating element.

According to the third embodiment of the present invention, the reduction planetary gear set is the first planetary gear set PG-1 of the double pinion, and the composite planetary gear set is the second planetary gear set PG-2 of the single pinion. And the third planetary gear set (PG-3) of the single pinion.

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

In a third embodiment of the present invention, the second operating element (N2) and the seventh operating element (N7) is selectively connected via the first clutch (C-1), the sixth operating element ( The pair of actuating elements forming N6 is selectively connected via a second clutch C-2, and the sixth actuating element N6 is connected to the input shaft 10 and the third clutch C-3. Is selectively connected via), and the third operating element (N3) and the seventh operating element (N7) are selectively connected via the fourth clutch (C-4), and the seventh operating element (N7) ) Is selectively restrained with respect to the transmission case 30 via the first brake B-1, and the sixth operating element N6 is connected to the transmission case via the second brake B-2. 30), and the sixth actuating element N6 is selectively restrained with respect to the transmission case 30 via a one-way clutch OWC, and the one-way clutch OWC is About 6 actuating element (N6) is provided in parallel with the second brake (B-2).

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

According to the third 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 The first ring gear (R1) of the first planetary gear set (PG-1), the third operating element (N3) is the first carrier (C1) of the first planetary gear set (PG-1). The fourth operating element (N4) is made of a second sun gear (S2) of the second planetary gear set (PG-2), the fifth operating element (N5) is the third planetary gear set And a third ring gear R3 of PG-3, wherein the sixth operating element N6 includes the second carrier C2 and the third planetary gear of the second planetary gear set PG-2. It is made by selectively connecting between the third carrier (C3) of the set (PG-3), the seventh operating element (N7) is the second ring gear (R2) of the second planetary gear set (PG-2) And the third sun gear S3 of the third planetary gear set PG-3 are always connected.

On the other hand, according to the first, second and third embodiments of the present invention, each of the operating elements is the second clutch (C-2) and the one-way clutch (OWC) in the D range 1, as shown in FIG. ) Operates, the first brake B-1 operates while the second clutch C-2 is maintained in the D range 2, and the one-way clutch OWC is naturally released. The first clutch C-1 is operated while the first brake B-1 is released while the second clutch C-2 is maintained in the D range 3 speed. The fourth clutch C-4 is operated while the first clutch C-1 is released while the second clutch C-2 is maintained in the range 4 speed. The third clutch C-3 is operated while the fourth clutch C-4 is released while the operation of the second clutch C-2 is maintained, and the third clutch in the D range 6 speed. (C-3) 's operation The fourth clutch C-4 is operated while the second clutch C-2 is released in the maintained state, and the third clutch C-3 is maintained in the D range 7 speed. The first clutch C-1 is operated while the fourth clutch C-4 is released, and the first clutch is operated while the operation of the third clutch C-3 is maintained at the D range 8 speed. The first brake B-1 is operated while (C-1) is released, and the first clutch C-1 and the second brake B-2 are operated in R range 1, and R In the second range, the fourth clutch C-4 and the second brake B-2 operate to shift.

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

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

That is, the speed at which the first carrier gear S1 of the first planetary gear set PG-1 is input through the input shaft 10 is the first ring as the first sun gear S1 acts as a fixed element. After the first deceleration through the gear R1, the gear is transferred to the second sun gear S2 of the second planetary gear set PG-2, and the speed transferred to the second sun gear S2 is the second ring gear (S2). The third sun gear S3 of the third planetary gear set PG-3 after the second deceleration through the second carrier C2 as R2 acts as a fixed element by the operation of the one-way clutch OWC. Is transferred to the third sun gear (S3), the third ring gear (R3) as the third carrier (C3) acts as a fixed element by the operation of the one-way clutch (OWC). After the third deceleration through the output shaft 20 is output via the D range 1 speed.

-D range 2 speed

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

When an input is made to the third operating element N3 through the input shaft 10, the fourth operation is decelerated through the second operating element N2 using the first operating element N1 as a fixed element. The input transitioned to the element N4 and the input transitioned to the fourth operating element N4 are decelerated through the fifth operating element N5 with the seventh operating element N7 as a fixed element to decelerate the output shaft 20. Will be displayed.

That is, the speed at which the first carrier gear S1 of the first planetary gear set PG-1 is input through the input shaft 10 is the first ring as the first sun gear S1 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 first brake (B-1), the second carrier of the third planetary gear set (PG-3) after the second deceleration through the second ring gear (R2) The speed is transferred to (C3), the speed transferred to the third carrier (C3) is the third ring as the third sun gear (S3) acts as a fixed element by the operation of the first brake (B-1) In the state slightly increased than the second deceleration through the gear (R3) is output at the second speed D range through the output shaft (20).

D range 3-speed

At D range 3 speed, the first clutch C-1 is operated as a fastening element while the first brake B-1 is released while the second clutch C-2 is maintained.

When an input is made to the third operating element N3 through the input shaft 10, the first operation element N1 is used as a fixed element to decelerate first through the second operating element N2. In addition to being transferred to the fourth operating element N4, the fourth operating element N7 and the seventh operating element N4 are simultaneously transferred to the seventh operating element N7 via the first clutch C-1. The input simultaneously transferred to N7) is output to the output shaft 20 while the first decelerated level is maintained through the fifth operating element N5.

That is, the speed at which the first carrier gear S1 of the first planetary gear set PG-1 is input through the input shaft 10 is the first ring as the first sun gear S1 acts as a fixed element. After the first deceleration through the gear R1, the second planetary gear set PG-2 is transferred to the second sun gear S2, and the third planetary gear is connected to the first clutch C-1. It is also transferred to the third sun gear S3 of the gear set PG-3.

At this time, the input transferred to the third sun gear S3 by the fastening of the second clutch C-2 is also transferred to the second carrier C2 of the second planetary gear set PG-2.

Accordingly, the second ring gear R2 of the second planetary gear set PG-2 receives the input transferred from the first ring gear R1 as it is and is the third of the third planetary gear set PG-3. Transition to the third carrier (C3), the output through the third ring gear (R3) of the third planetary gear set (PG-3) maintains the decelerated level in the first ring gear (R1) D range is output at 3 speeds.

D range 4-speed

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

When an input is made to the third operating element N3 through the input shaft 10, the fourth operation is decelerated through the second operating element N2 using the first operating element N1 as a fixed element. The input of the input shaft 10 is transferred to the seventh operating element N7 as it is.

Accordingly, the speed output to the output shaft 20 through the fifth operating element N5 is smaller than the speed of the input shaft 10 and larger than the speed of the fourth operating element N4.

That is, the speed at which the first carrier gear S1 of the first planetary gear set PG-1 is input through the input shaft 10 is the first ring as the first sun gear S1 acts as a fixed element. After the first deceleration through the gear R1, the gear shifts to the second sun gear S2 of the second planetary gear set PG-2 and the third sun gear S3 of the third planetary gear set PG-3. In the fourth clutch C-4, the input of the input shaft 10 is transferred at a constant speed as it is.

At this time, the input transferred to the third sun gear S3 by the fastening of the second clutch C-2 is also transferred to the second carrier C2 of the second planetary gear set PG-2.

As a result, in the second planetary gear set PG-2, the deceleration input of the first ring gear R1 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 velocity 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 so that the D range 4 through the output shaft 20 is reduced. Is output into the system.

-D range 5 speed

In the D-range 5 speed, the fourth clutch C-4 is released while the second clutch C-2 is maintained, and the third clutch C-3 operates as a fastening element.

When an input is made to the third operating element N3 through the input shaft 10, the fourth operation is decelerated through the second operating element N2 using the first operating element N1 as a fixed element. The input of the input shaft 10 is transferred to the sixth operating element N6 through the third clutch C-3 as it is.

Accordingly, the speed output to the output shaft 20 through the fifth operating element N5 is smaller than the speed of the input shaft 10 and larger than the speed of the fourth operating element N4.

That is, the speed at which the first carrier gear S1 of the first planetary gear set PG-1 is input through the input shaft 10 is the first ring as the first sun gear S1 acts as a fixed element. After the first deceleration through the gear R1, the gear is transferred to the second sun gear S2 of the second planetary gear set PG-2 and the second ring gear R2 of the second planetary gear set PG-2. ) And the input of the input shaft 10 is transferred to the third carrier C3 of the third planetary gear set PG-3 as a constant velocity through the third clutch C-3.

As a result, in the second planetary gear set PG-2, the deceleration input of the first ring gear R1 input to the second sun gear S2 and the input shaft input to the second ring gear R2 ( By the constant speed input of 10), the output through the second carrier C2 becomes 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 than the speed of the input shaft 10 by an input equivalently transitioned to the third carrier C3 from 10), and thus, the speed D range 5 speeds through the output shaft 20. Is output.

-D range 6 speed

In the D range 6 speed, the fourth clutch C-4 operates as a fastening element while the second clutch C-2 is released while the third clutch C-3 is maintained.

When an input is simultaneously made to the third operating element N3 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 fifth operating element N5. 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

In D range 7, the first clutch C-1 operates as a fastening element while the fourth clutch C-4 is released while the operation of the third clutch C-3 is maintained.

When an input is made to the third operating element N3 through the input shaft 10, the fourth operation is decelerated through the second operating element N2 using the first operating element N1 as a fixed element. The input of the input shaft 10 is transferred to the sixth operating element N6 through the third clutch C-3 as it is.

Accordingly, the speed output to the output shaft 20 through the fifth operating element N5 is greater than the speed of the input shaft 10.

That is, the speed at which the first carrier gear S1 of the first planetary gear set PG-1 is input through the input shaft 10 is the first ring as the first sun gear S1 acts as a fixed element. After the first deceleration through the gear (R1) is transferred to the third sun gear (S3) of the third planetary gear set (PG-3) via the first clutch (C-1), the second planetary gear set The second ring gear R2 of PG-2 and the third carrier C3 of the third planetary gear set PG-3 are connected to the input shaft 10 via the third clutch C-3. The input is transferred at constant speed.

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

In the D-range 8 speed, the first brake B-1 operates as a fastening element while the first clutch C-1 is released while the third clutch C-3 is maintained.

The input of the input shaft 10 is directly transferred to the sixth operating element N6 via the third clutch C-3, and the input transferred to the sixth operating element N6 is the seventh operation. The speed is increased by using the element N7 as a fixed element and 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

In the R range 1 speed, the first clutch C-1 and the second brake B-2 operate as fastening elements, respectively.

When the input is made to the third operating element N3 through the input shaft 10, the first clutch is decelerated through the second operating element N2 by using the first operating element N1 as a fixed element. The input transferred to the seventh operating element N7 via (C-1), and the input transferred to the seventh operating element N7 is the fifth operation using the sixth operating element N6 as a fixed element. It is reversed through the element N5 and output to the output shaft 20.

That is, the speed at which the first carrier gear S1 of the first planetary gear set PG-1 is input through the input shaft 10 is the first ring as the first sun gear S1 acts as a fixed element. After the first deceleration through the gear R1, the gear is decelerated and transferred to the third sun gear S3 of the third planetary gear set PG-3 through the first clutch C-1.

Accordingly, in the third planetary gear set PG-3, the deceleration input of the first ring gear R1 input to the third sun gear S3 via the first clutch C-1 is performed. As the third carrier C3 acts as a fixed element by the operation of the second brake B-2, the third carrier C3 is decelerated through the third ring gear R3 and output in the reverse direction through the output shaft 20.

R range 2 speed

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

The input transferred to the third operating element N3 through the input shaft 10 is transferred to the seventh operating element N7 via the fourth clutch C-4, and the seventh operating element ( The input transferred to N7) is reversed through the fifth operating element N5 using the sixth operating element N6 as a fixed element and output to the output shaft 20.

That is, the speed input to the first carrier C1 of the first planetary gear set PG-1 through the input shaft 10 is the third planetary gear set via the fourth clutch C-4. The constant velocity is transferred to the third sun gear S3 of (PG-3).

Accordingly, in the third planetary gear set PG-3, the constant velocity input of the input shaft 10 input to the third sun gear S3 via the fourth clutch C-4 is the third carrier. As (C3) acts as a fixed element by the operation of the second brake (B-2) is decelerated through the third ring gear (R3) to output the reverse direction through the output shaft 20, wherein the output The speed becomes larger than the R range 1 speed.

This is because the input transitioned to the third sun gear S3 is a deceleration input through the first ring gear R1 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.

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

<Description of Symbols for Main Parts of Drawings>

10; Input shaft 20; Output shaft

30; Transmission case

PG-1; First planetary gear set S1; First gear

C1; First carrier R1; 1st ring gear

PG-2; Second planetary gear set S2; First gear

C2; First carrier R2; 1st ring gear

PG-3; Third planetary gear set S3; First gear

C3; First carrier R3; 1st ring gear

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

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

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

OWC; One Way Clutch

Claims (8)

Multi-speed shifting to the output shaft 20 by selectively receiving non-deceleration rotation and deceleration rotation from the input shaft 10 and the reduction planetary gear set, respectively, and outputting the rotation of the input shaft 10 as the deceleration rotation. A composite planetary gear set for outputting rotation; The reduction planetary gear set may include a first operating element N1 which is always restrained by the transmission case 30, a second operating element N2 which is always and selectively connected to a plurality of operating elements of the composite planetary gear set, and A third actuating element (N3) connected at all times with the input shaft (10); The composite planetary gear set includes a fourth operating element N4, which is always connected to the second operating element N2, a fifth operating element N5, which is always connected to the output shaft 20, and the input shaft 10. A sixth operating element (N6) and a second operating element (N2), which are selectively connected and are selectively constrained to the transmission case (30) and always share a pair of operating elements of the operating elements of the composite planetary gear set. And a seventh actuating element selectively connected to the third actuating element N3 and selectively restrained by the transmission case 30 and selectively sharing another pair of actuating elements among the actuating elements of the composite planetary gear set ( Power train of automatic transmission with N7). The method according to claim 1, The reduction planetary gear set is the first planetary gear set PG-1 of the double pinion, and the composite planetary gear set is the second planetary gear set PG-2 of the double pinion and the third planetary gear set of the single pinion ( PG-3); The first operating element N1 is composed of the first sun gear S1 of the first planetary gear set PG-1, and the second operating element N2 is the first planetary gear set PG-1. The first ring gear (R1) of the first, 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 composed of the second sun gear S2 of the second planetary gear set PG-2, and the fifth operating element N5 is the third ring gear of the third planetary gear set PG-3. And the sixth operating element N6 includes a third ring gear R2 of the second planetary gear set PG-2 and a third of the third planetary gear set PG-3. Always connected between the carrier (C3), the seventh operating element (N7) is the second carrier (C2) and the third planetary gear set (PG-3) of the second planetary gear set (PG-2). Power transmission of the automatic transmission, characterized in that it is made by selectively connecting between the third sun gear (S3) of . The method according to claim 1, The reduction planetary gear set is a first planetary gear set PG-1 of a double pinion, and the composite planetary gear set is a second planetary gear set PG-2 of a single pinion and a third planetary gear set of a single pinion ( PG-3); The first operating element N1 is composed of the first sun gear S1 of the first planetary gear set PG-1, and the second operating element N2 is the first planetary gear set PG-1. The first ring gear (R1) of the first, 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 composed of the second sun gear S2 of the second planetary gear set PG-2, and the fifth operating element N5 is the third ring gear of the third planetary gear set PG-3. And the sixth operating element N6 includes a second carrier C2 of the second planetary gear set PG-2 and a third carrier of the third planetary gear set PG-3. (C3) is always connected between the seventh operating element (N7) is the second ring gear (R2) and the third planetary gear set (PG-3) of the second planetary gear set (PG-2). Power transmission of the automatic transmission, characterized in that it is made by selectively connecting between the third sun gear (S3) of . The method according to claim 2 or 3, The second operating element N2 and the seventh operating element N7 are selectively connected through a first clutch C-1, and a pair of operating elements forming the seventh operating element N7. Is selectively connected between the second clutch C-2 through the second clutch C-2, and the sixth operating element N6 is selectively connected through the input shaft 10 and the third clutch C-3. The third operating element N3 and the seventh operating element N7 are selectively connected to each other via the fourth clutch C-4, and the seventh operating element N7 is the first brake B-1. Is selectively restrained with respect to the transmission case 30, and the sixth operating element N6 is selectively restrained with respect to the transmission case 30 via a second brake B-2. The sixth operating element N6 is selectively restrained with respect to the transmission case 30 via the one-way clutch OWC, and the one-way clutch OWC is provided with respect to the sixth operating element N6. Power train of an automatic transmission, characterized in that it is installed in parallel with two brakes (B-2). Multi-speed shifting to the output shaft 20 by selectively receiving non-deceleration rotation and deceleration rotation from the input shaft 10 and the reduction planetary gear set, respectively, and outputting the rotation of the input shaft 10 as the deceleration rotation. A composite planetary gear set for outputting rotation; The reduction planetary gear set may include a first operating element N1 which is always restrained by the transmission case 30, a second operating element N2 which is always and selectively connected to a plurality of operating elements of the composite planetary gear set, and A third actuating element (N3) connected at all times with the input shaft (10); The composite planetary gear set includes a fourth operating element N4, which is always connected to the second operating element N2, a fifth operating element N5, which is always connected to the output shaft 20, and the input shaft 10. A sixth operating element N6 selectively connected and selectively constrained to the transmission case 30 and selectively sharing a pair of operating elements of the operating planetary gear set, and the second operating element N2. ) And a seventh operating element selectively connected to the third operating element N3 and selectively restrained by the transmission case 30 and sharing another pair of operating elements of the composite planetary gear set at all times ( Power train of automatic transmission with N7). The method according to claim 5, The reduction planetary gear set is a first planetary gear set PG-1 of a double pinion, and the composite planetary gear set is a second planetary gear set PG-2 of a single pinion and a third planetary gear set of a single pinion ( PG-3); The first operating element N1 is composed of the first sun gear S1 of the first planetary gear set PG-1, and the second operating element N2 is the first planetary gear set PG-1. The first ring gear (R1) of the first, 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 composed of the second sun gear S2 of the second planetary gear set PG-2, and the fifth operating element N5 is the third ring gear of the third planetary gear set PG-3. And the sixth operating element N6 includes a second carrier C2 of the second planetary gear set PG-2 and a third carrier of the third planetary gear set PG-3. (C3) is selectively connected between the seventh operating element (N7) is the second ring gear (R2) and the third planetary gear set (PG-) of the second planetary gear set (PG-2). 3) the power transmission of the automatic transmission, characterized in that the connection is always made between the third sun gear (S3). . The method according to claim 6, The second operating element N2 and the seventh operating element N7 are selectively connected via a first clutch C-1, and a pair of operating elements forming the sixth operating element N6. Is selectively connected between the second clutch C-2 through the second clutch C-2, and the sixth operating element N6 is selectively connected through the input shaft 10 and the third clutch C-3. The third operating element N3 and the seventh operating element N7 are selectively connected to each other by the fourth clutch C-4, and the seventh operating element N7 is the first brake B-1. Is selectively restrained with respect to the transmission case 30, and the sixth operating element N6 is selectively restrained with respect to the transmission case 30 via a second brake B-2. The sixth operating element N6 is selectively restrained with respect to the transmission case 30 via the one-way clutch OWC, and the one-way clutch OWC is connected to the sixth operating element N6 with respect to the sixth operating element N6. 2, the brake power train of an automatic transmission, characterized in that (B-2) and provided in parallel. The method according to claim 1 or 5, The first planetary gear set PG-1 and the second planetary gear set PG-2 and the third planetary gear set PG-3 are arranged in order from an engine side to which the input shaft 10 is connected. And the input shaft (10) and the output shaft (20) are coaxially spaced apart from each other.

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