KR100911514B1 - 4-speed power train of automatic transmission - Google Patents

Abstract

The present invention is a simple structure that combines a combination of a single planetary gear set and a single pinion planetary gear set and a double pinion planetary gear set, three clutches and two brakes to realize a four-speed forward and a reverse one-speed gearbox. The aim is to reduce the overall volume and length of the engine, reduce the overall weight of the automatic transmission, reduce the manufacturing cost, and improve the mountability of the vehicle body.

In order to achieve the above object, the present invention, the first planetary gear set (PG-1) that is variably connected to the input shaft 10, and is variably constrained to the transmission case 30; A second variable variable connection to the input shaft 10, a variable restraint to the transmission case 30, and sharing the two operating elements with the first planetary gear set (PG-1) is always connected to the output shaft 20 Planetary gear set (PG-2). The first and second planetary gear sets PG-1 and PG-2 may include a first operating element N1 variably connected to the input shaft 10 and a second operating element N2 connected to the output shaft 20. ), A third operating element N3 variably connected to the input shaft 10 and variably restrained with the transmission case 30, and variably connected with the input shaft 10 and variably restrained with the transmission case 30. It is characterized in that it comprises a fourth operating element (N4).

Description

4-speed power train of automatic transmission

1 is a schematic diagram showing the configuration of a four speed power train of an automatic transmission according to the present invention;

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

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

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

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

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

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

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

Conventional planetary gearsets used in the four-speed power train of automatic transmissions are often used in the ravengine type (Ravigneaux Type), the planetary gearset of the ravenue type should be a structure in which the carrier simultaneously supports the long pinion and short pinion. Therefore, there is a difficulty in producing a carrier, and it is difficult to support four or more pairs of pinions due to space limitations, and thus, in order to transmit power of high torque, the width of the gearbox must be increased or the pinion must be increased, resulting in an enlargement of the transmission.

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

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

Accordingly, the present invention has been made to solve the above problems, as a simple structure of combining a combination of a single planetary gear set and a double pinion planetary gear set, a three planetary gear set and three clutches and two brakes. By shifting the 4th forward and 1st speed, it is possible to reduce the overall volume and length of the automatic transmission, reduce the overall weight of the automatic transmission, reduce manufacturing costs, and improve the mountability on the body. Its purpose is to help.

The present invention for achieving the above object, the first planetary gear set is variably connected to the input shaft, and is variably constrained to the transmission case;

A second planetary gear set variably connected to the input shaft and variably constrained to the transmission case and sharing two actuating elements with the first planetary gear set and always connected to the output shaft;

The first planetary gear set and the second planetary gear set are variably connected to the input shaft to act as an equivalent input element, a second actuating element connected to the output shaft to always act as an output element, and the input shaft. And a third operating element which is variably connected to and acts as an equivalent input element, and is variably constrained with the transmission case, and also acts as a fixed element, and is variably connected to the input shaft to act as an equivalent input element and variably constrained to the transmission case. A fourth actuating element also acting as a stationary element;

Between the input shaft and the first, third, and fourth operating elements are selectively connected via clutch means, respectively, to equivalently transfer power provided from the input shaft;

The third and fourth operating elements may be selectively connected to each other by the transmission case and the brake unit, and configured to perform rotational restraint of the corresponding operating element.

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

The four-speed power train of the automatic transmission according to the present invention is the input shaft 10 receives the rotational force of the engine from the engine through the torque converter, and the second planetary gear set PG-2 which is variably connected to the input shaft 10 and described below. The first planetary gear set PG-1, which is always connected to the output shaft 20 and variably constrained to the transmission case 30, and the first planetary gear set PG, which is variably connected to the input shaft 10, -1) and a second planetary gear set (PG-2) is always connected to the output shaft 20 by sharing the two operating elements with each other.

Here, the first planetary gear set PG-1 and the second planetary gear set PG-2 are variably connected to the input shaft 10 so as to receive the power provided from the input shaft 10 as it is. The first operating element N1 acting as an element and the second operating element N2 connected to the output shaft 20 and always acting as output elements for outputting power as a variable speed ratio according to the interaction of the planetary gear set. It is variably connected with the input shaft 10 to act as an equivalent input element that receives the power provided from the input shaft 10 as it is, and is variably constrained with the transmission case 30 to rotate about the corresponding element of the planetary gear set. The third operating element (N3) and also acts as a fixed element to restrain the input shaft 10, and is connected to the input shaft 10 acts as an equivalent input element that receives the power provided from the input shaft 10 as it is and the transmission case ( 3 0) and a fourth actuating element (N4), which is variably constrained to act as a stationary element to restrain rotation about the corresponding element of the planetary gear set.

And, between the input shaft 10 and the first, third, fourth operating element (N1, N3, N4) is selectively connected via a clutch means, respectively, to convert the power provided from the input shaft 10 into an equivalent transition To pass. The third and fourth operating elements N3 and N4 are selectively connected to the transmission case 30 and the brake means, respectively, to perform rotational restraint of the corresponding operating element.

In this case, the first planetary gear set PG-1 consists of a double pinion planetary gear set, and the second planetary gear set PG-2 consists of a single pinion planetary gear set.

According to an embodiment of the present invention, the first operating element N1 is composed of the first sun gear S1 of the first planetary gear set PG-1, and the second operating element N2 is formed of the first operating element N2. It consists of a second ring gear (R2) of the two planetary gear set (PG-2), the third operating element (N3) and the first ring gear (R1) of the first planetary gear set (PG-1) The second carrier C2 of the second planetary gear set PG-3 is connected to each other, and the fourth operating element N4 is the first carrier C1 of the first planetary gear set PG-1. ) And the second sun gear S2 of the second planetary gear set PG-2.

In this case, the first sun gear S1, the first carrier C1, and the second carrier C2 are variably connected to the input shaft 10, respectively, and the first ring gear R1 is the second. The input shaft 10 is variably connected through the carrier C2, and the second sun gear S2 is variably connected to the input shaft 10 through the first carrier C1.

In addition, the second ring gear R2 of the second planetary gear set PG-2 is directly connected to the output shaft 20.

According to the exemplary embodiment of the present invention, the fourth operating element N4 is variably connected to the input shaft 10 at a constant speed ratio via the first clutch C-1, and the first operating element N1 The second shaft C-2 is variably connected to the input shaft 10 at a constant speed ratio, and the third operating element N3 is at a constant speed ratio to the input shaft 10 via a third clutch C-3. Variablely connected, the fourth operating element (N4) is variably constrained to the transmission case 30 via the first brake (B-1), the third operating element (N3) is the second brake (B- 2) is variably constrained to the transmission case (30).

In this case, the third operating element N3 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 embodiment of the present invention, the input shaft 10 and the output shaft 20 are arranged to be spaced coaxially in the transmission case 30, the four-speed power train in the engine room in the longitudinal direction When arranged in, the output shaft 20 is capable of direct power transmission to the rear wheels via a separate propulsion shaft, the four-speed power train of the present invention is suitable for applying to the vehicle of electric tube rear wheel drive (FR) do.

The first clutch C-1 and the second clutch C-2 are disposed on the side of the first planetary gear set PG-1 at the outer circumference of the input shaft 10, and the third clutch C-1 and the second clutch C-2. The clutch C-3 is positioned at a position opposite to the first clutch C-1 and the second clutch C-2 on the outer circumference of the input shaft 10. ), So that each actuating element in the transmission case 30 can be arranged with an even weight distribution throughout the power train.

In addition, the second clutch (C-2) is a parallel arrangement branched from the connection path between the input shaft 10 and the first clutch (C-1) of the first planetary gear set (PG-1). The first sun gear S1 is variably connected.

In addition, the first brake (B-1) is arranged in parallel branching from the connection path between the first clutch (C-1) and the first carrier (C1) of the first planetary gear set (PG-1). As a result, the first carrier C1 of the first planetary gear set PG-1 is variably constrained to the transmission case 30.

According to an embodiment of the present invention, a path through which power is transmitted from the input shaft 10 to the first and second planetary gear sets PG-1 and PG-2 is input to the first operating element N1 at a constant velocity ratio. And a third input path inputted at a constant velocity ratio to the third operating element N3, and a third input path inputted at a constant velocity ratio to the fourth operating element N4.

In this case, the first input path is operated in the second clutch C-2 which variably connects the input shaft 10 and the first sun gear S1 in the D ranges 1,2 and 3 respectively. Is set by.

The second input path is set by the operation of the third clutch C-3 to variably connect the input shaft 10 and the second carrier C2 in the D ranges 3 and 4, respectively. do.

In addition, the third input path is set by the operation of the first clutch C-1 to variably connect between the input shaft 10 and the first carrier C1 in the R range.

According to an embodiment of the present invention, the path from which power is cut off in the first and second planetary gear sets PG-1 and PG-2 is connected between the third operating element N3 and the transmission case 30. And a second blocking path connecting between the fourth operating element N4 and the transmission case 30.

First, the first blocking path includes the second brake B-2 or the one-way clutch that variably restrains the third operating element N3 and the transmission case 30 in the D range 1 speed. OWC), and in the R range, is set by the operation of the second brake B-2 which variably restrains between the third operating element N3 and the transmission case 30.

In this case, the first blocking path is operated by the one-way clutch OWC which variably restrains the third operating element N3 and the transmission case 30 in the D range 1 speed. It is set by restraining rotation of the ring gear R1 and the second carrier C2.

In addition, the first blocking path is operated by the second brake B-2 that variably restrains the third operating element N3 and the transmission case 30 in the R range. It is set by restraining the rotation of the gear R1 and the second carrier C2.

Preferably, the first blocking path is implemented by preventing the reverse rotation with respect to the third operating element N3 by the operation of the one-way clutch OWC in the D range 1 speed. In addition, the first blocking path is implemented by restraining forward / reverse rotation with respect to the third operating element N3 by the operation of the second brake B-2 in the R range.

In addition, the second blocking path is configured to operate the first brake B-1, which variably restrains the fourth operating element N4 and the transmission case 30 in the D ranges 2 and 4, respectively. Is set.

According to an exemplary embodiment 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 speed, and the second clutch C in the D range 2 speed. The first brake B-1 operates while the operation of -2) is maintained, and the first brake B while the operation of the second clutch C-2 is maintained in the D range 3 speed. The third clutch C-3 is operated while -1) is released, and the second clutch C-2 is operated while the operation of the third clutch C-3 is maintained in the D range 4 speed. The first brake B-1 operates while being released, and the first clutch C-1 and the second brake B-2 operate in the R range to shift.

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

-D range 1 speed

As shown in FIG. 4, in the D range 1 speed, the second clutch C-2 and the one-way clutch OWC operate as fastening elements, respectively.

When the input is made to the first operating element N1 through the input shaft 10, the output shaft 20 is decelerated through the second operating element N2 with the third operating element N3 as a fixed element. ), The output of D range 1 speed is achieved.

That is, the speed input to the first sun gear S1 of the first planetary gear set PG-1 from the input shaft 10 by the operation of the second clutch C-2 is the one-way clutch OWC. As the first ring gear R1 is constrained by the operation of the first and second deceleration output in the reverse direction through the first carrier C1, the first deceleration output in the reverse direction through the first carrier C1 The second planetary gear set PG-2 is transferred to the second sun gear S2 at a constant speed ratio, and the speed transferred to the second sun gear S2 is controlled by the one-way clutch OWC. As the carrier C2 is restrained, the second gear is secondly decelerated in the forward direction through the second ring gear R2, and then output through the output shaft 20 at the first speed D range.

-D range 2 speed

As shown in FIG. 5, 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 output shaft 20 is decelerated through the second operating element N2 using the fourth operating element N4 as a fixed element. ), D range 2 speed output is achieved.

That is, the speed input to the first sun gear S1 of the first planetary gear set PG-1 from the input shaft 10 by the operation of the second clutch C-2 is the first brake B. When the first carrier C1 is constrained by the operation of -1), the primary deceleration output is performed through the first ring gear R1, and the primary deceleration output through the first ring gear R1 is The speed shifted to the second carrier C2 of the second planetary gear set PG-2 at a constant speed ratio, and to the second sun gear S2 is controlled by the operation of the first brake B-1. As the two-wire gear S2 is constrained, it is output through the output shaft 20 at the second speed D range as it is at the constant velocity ratio transferred through the second ring gear R2.

D range 3-speed

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

When an input is simultaneously made to the first operating element N1 and the third operating element N3 through the input shaft 10, the input of the input shaft 10 is maintained as it is through the second operating element N2. Transition is performed and output via the output shaft 20 at 3 speeds in the D range.

That is, the speed input to the first sun gear S1 of the first planetary gear set PG-1 from the input shaft 10 by the operation of the second clutch C-2, and the third clutch By the operation of C-3), the speeds input from the input shaft 10 to the second carrier C2 of the second planetary gear set PG-2 are all in the same state as the speed of the input shaft 10. .

Accordingly, all the operating elements of the first planetary gear set PG-1 and the second planetary gear set PG-2 are directly connected, and the speed output through the output shaft 20 is determined by the input shaft ( It becomes the state of what is called constant velocity output becoming the speed of 10).

D range 4-speed

As shown in FIG. 7, in the D range 4 speed, the first clutch B-1 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 made to the third operating element N3 through the input shaft 10, the output shaft 20 is accelerated through the second operating element N2 using the fourth operating element N4 as a fixed element. ), Overdrive output of D range 4 speed is achieved.

That is, the speed input to the second carrier C2 of the second planetary gear set PG-2 from the input shaft 10 by the operation of the third clutch C-3 is the first brake B. As the second sun gear S2 is constrained by the operation of -1), the second sun gear S2 is accelerated through the second ring gear R2 and overdrive output through the output shaft 20 at the D range 4 speed.

R range

As shown in FIG. 8, in the R range, the first clutch C-1 and the second brake B-2 operate as fastening elements, respectively.

When the input is made to the fourth operating element N4 through the input shaft 10, the output shaft 20 is reversed through the second operating element N2 using the third operating element N3 as a fixed element. R range output is made.

That is, the speed input from the input shaft 10 to the first carrier C1 of the first planetary gear set PG-1 by the operation of the first clutch C-1 is the second planetary gear set. The speed transferred to the second sun gear S2 of PG-2 at a constant speed ratio, and the speed transferred to the second sun gear S2 is controlled by the second brake B-2 by the operation of the second carrier C2. As it is constrained, it is reversed through the second ring gear R2 to output the R range to the output shaft 20.

As described above, according to the four-speed power train of the automatic transmission according to the present invention, there is a difficulty in manufacturing a carrier of a conventional planetary planetary gear set, or superimposed to control two sun gears with friction elements, respectively. Problems arising from the structure of the hollow shaft can be eliminated, thereby reducing the volume and overall length of the automatic transmission and improving the mountability on the vehicle, and is easy to manufacture.

In addition, the overlapping hollow shaft structure required for driving two adjacent sun gears can be eliminated, so that oil flow in the radial direction from the transmission center axis can be made relatively easy and smooth, so that lubrication and Cooling is made easier and more efficient.

In addition, since the one-way clutch serves to convert the operating element to the fixed element in the D range 1 speed, the response is improved when the speed is changed to the D range 1 speed, and is newly changed when the speed is changed from the D range 1 speed to the 2 speed. If only the fastening pressure is provided to the operating element to be fastened, since the automatic release is made in the operating element fixed by the one-way clutch, it is possible to facilitate shift control.

In addition, the present invention can be arranged coaxially the input shaft and the output shaft, when the four-speed power train in the longitudinal direction in the engine room, the output shaft can be directly transmitted to the rear wheels through a separate propulsion, so It can be applied to the automatic transmission for vehicles of electric tube rear wheel drive (FR).

Claims (18)

A first planetary gear set PG- 1 that is variably connected to the input shaft 10 and is variably constrained to the transmission case 30, and is variably connected to the input case 10, and is variably constrained to the transmission case 30. And a second planetary gear set PG-2 which is always connected to the output shaft 20 by sharing two operating elements with the first planetary gear set PG-1; The first planetary gear set PG-1 and the second planetary gear set PG-2 are variably connected to the input shaft 10 to act as an equivalent input element, and the first operating element N1 and the output shaft. The second operating element (N2) is connected to the (20) and always acts as an output element, the input shaft 10 is variably connected to act as an equivalent input element, and is variablely constrained with the transmission case (30) as a fixed element The third operating element (N3) also acts, and the fourth operating element (N4) is variably connected to the input shaft (10) to act as an equivalent input element and variably constrained to the transmission case (30) to act as a fixed element. With; Between the input shaft (10) and the first, third, and fourth operating elements (N1, N3, N4) are selectively connected via clutch means, respectively, to equivalently transfer the power provided from the input shaft (10); The third and fourth operating elements N3 and N4 are selectively connected to the transmission case 30 and the brake means, respectively, so as to perform rotational restraint of the corresponding operating element; 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 second planetary gear set PG-2. A second ring gear (R2), and the third operating element (N3) is the first ring gear (R1) and the second planetary gear set (PG) of the first planetary gear set (PG-1). The second carrier C2 of -3) is connected, and the fourth operating element N4 is the first carrier C1 and the second planetary gear set of the first planetary gear set PG-1. It is made by connecting the second sun gear (S2) of (PG-2); The third operating element (N3) is a four-speed power of the automatic transmission characterized in that it is variably constrained to the transmission case 30 via a one-way clutch (OWC) installed in parallel with the second brake (B-2). Train. The method according to claim 1, The first planetary gear set PG-1 consists of a double pinion planetary gear set, and the second planetary gear set PG-2 consists of a single pinion planetary gear set. Train. delete The method according to claim 2, The first sun gear S1, the first carrier C1, the first ring gear R1, the second sun gear S2, and the second carrier C2 are variably connected to the input shaft 10, respectively. The second ring gear (R2) is a four-speed power train of the automatic transmission, characterized in that directly connected to the output shaft (20). The method according to claim 4, The fourth operating element N4 is variably connected to the input shaft 10 at a constant speed ratio via the first clutch C-1, and the first operating element N1 connects the second clutch C-2. The input shaft 10 is variably connected to the input shaft 10 at a constant speed ratio, and the third operating element N3 is variably connected to the input shaft 10 at a constant speed ratio via a third clutch C-3, and the fourth operation is performed. The element N4 is variably constrained to the transmission case 30 via the first brake B-1, and the third operating element N3 is the transmission via the second brake B-2. 4-speed power train of an automatic transmission, characterized in that the case 30 is restrained constrained. delete The method according to claim 5, A path through which power is transmitted from the input shaft 10 to the first and second planetary gear sets PG-1 and PG-2 is a first input path inputted at a constant velocity ratio to the first operating element N1, and The fourth speed power train of the automatic transmission, characterized in that the second input path is input to the third operating element (N3) at a constant speed ratio, and the third input path is input to the fourth operating element (N4) at a constant speed ratio. . The method according to claim 7, The first input path is set by the operation of the second clutch C-2 to variably connect the input shaft 10 and the first sun gear S1 in the D ranges 1,2 and 3 speeds. 4-speed power train of the automatic transmission, characterized in that. The method according to claim 7, The second input path is set by an operation of the third clutch C-3 which variably connects the input shaft 10 and the second carrier C2 in the D ranges 3 and 4. 4-speed power train with automatic transmission. The method according to claim 7, And the third input path is set by an operation of the first clutch C-1 to variably connect the input shaft 10 and the first carrier C1 in the R range. 4-speed power train. The method according to claim 5, The path from which power is cut off in the first and second planetary gear sets PG-1 and PG-2 may include a first blocking path connecting the third operating element N3 and the transmission case 30; A fourth speed power train of the automatic transmission, characterized in that it is set as a second blocking path connecting between the fourth operating element (N4) and the transmission case (30). The method according to claim 11, The first blocking path of the second brake B-2 or the one-way clutch OWC that variably restrains between the third operating element N3 and the transmission case 30 at the D range 1 speed. Is set by the operation, and is set by the operation of the second brake B-2 which variably restrains between the third operating element N3 and the transmission case 30 in the R range. Four-speed power train on the transmission. The method according to claim 11, The second blocking path is set by the operation of the first brake B-1 to variably restrain between the fourth operating element N4 and the transmission case 30 in the D ranges 2 and 4. 4-speed power train of the automatic transmission, characterized in that. The method according to claim 5, 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 third clutch C-3 is operated, and the second clutch C-2 is released while the third clutch C-3 is maintained in the D range 4, so that the first brake C-3 is released. B-1) is operated, and the first clutch (C-1) and the second brake (B-2) in the R range is a four-speed power train of the automatic transmission, characterized in that the shift is made. The method according to claim 5, The input shaft (10) and the output shaft (20) is a four-speed power train of the automatic transmission, characterized in that arranged in the coaxially spaced apart inside the transmission case (30). The method according to claim 15, The first clutch C-1 and the second clutch C-2 are disposed on the side of the first planetary gear set PG-1 at the outer circumference of the input shaft 10, and the third clutch C-3) the second planetary body in a position opposite to the first clutch C-1 and the second clutch C-2 with respect to the input shaft 10 on the outer circumference of the input shaft 10. 4-speed power train of an automatic transmission, characterized in that arranged on the side of the gear set (PG-2). The method according to claim 15, The second clutch C-2 is disposed in parallel on a connection path between the input shaft 10 and the first clutch C-1, so that the first sun gear of the first planetary gear set PG-1 is disposed. 4-speed power train of the automatic transmission, characterized in that the variable transmission (S1). The method according to claim 15, The first brake B-1 is disposed in parallel on a connection path between the first clutch C-1 and the first carrier C1 of the first planetary gear set PG-1. 4-speed power train with automatic transmission.

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