KR101261934B1 - Power train of an automatic transmission for a vehicle - Google Patents

Abstract

A single power train can realize 6 forward speeds or 7 forward speeds, and inputs the deceleration in the low speed area and the same speed input in the high speed area, thereby effectively changing the rotational power of the engine and minimizing the power loss. To provide a power train of a vehicular automatic transmission capable of;

A first planetary gear set, which is a simple planetary gear set that decelerates and outputs rotational power transmitted from an input shaft through a first input path; It holds five operating elements, and acts as two input elements having variable inputs through the second and third input paths, and variable input elements through the fourth input path, and at the same time, one input element is fixed. A second planetary gearset, which is a composite planetary gearset having an element and one always output element; It comprises three clutches and two brakes used to combine the first and second planetary gear sets, wherein the three clutches provide a power train of an automatic transmission for a vehicle disposed at the rear side of the second planetary gear set. .

Automatic transmission. clutch. Planetary gear set, power train

Description

POWER TRAIN OF AN AUTOMATIC TRANSMISSION FOR A VEHICLE}

1 is a schematic diagram of a power train according to the present invention;

2 is a table of six forward speed operating elements of a power train according to the present invention;

3 is a sixth forward speed diagram of a power train according to the present invention;

FIG. 4 is a table of operating elements when implementing the seventh speed shift stage using the power train of FIG. 1. FIG.

5 is a shift diagram when implementing a shift speed of seven forward speeds using the power train of FIG. 1.

6 is a schematic diagram of a conventional power train.

7 is a table of operating elements of a conventional power train.

8 is a shift diagram of a conventional power train.

The present invention relates to a power train applied to an automatic transmission for a vehicle.

The automatic transmission detects the driving state of the vehicle from the detection means disposed in place of the vehicle, and based on this, the transmission control unit (TCU) automatically controls and operates the power train composed of a combination of planetary gear sets. It is configured to perform a shift.

Accordingly, the power train applied to the automatic transmission is preferably configured to implement more transmission stages in order to improve power performance and fuel consumption rate.

Also, even if the same number of gear stages are implemented, durability, power transmission efficiency, size and weight vary greatly depending on the combination method of the planetary gear set. Therefore, the power train can be more robust and compact while minimizing power loss. Efforts for development are ongoing.

In developing a power train using a planetary gear set, a new planetary gear set is not developed, but a simple combination of a conventional planetary gear set and a composite planetary gear set in some way, and the accompanying clutch and brake In addition, various studies have been actively conducted with the aim of realizing a desired shift stage and a shift ratio without any power loss by arranging several one-way clutches at any position.

In particular, in the case of a manual transmission, if there are too many shift stages, the driver should shift frequently. However, in the case of an automatic transmission, the shift is automatically performed according to the driving state. Therefore, more shift stages can be realized. Development of power trains is required.

In order to meet these demands, a variety of researches have recently been conducted on power trains capable of implementing a shift speed of six forward speeds or more.

As an example, as shown in FIG. 6, the first planetary gear set PG1 made of a single pinion planetary gear set is disposed in front, and the second planetary gear set PG2 made of a rib type planetary gear set is placed behind. The first sun gear S1 of the first planetary gear set PG1 is fixed to the transmission housing H, and the second (3) ring gear R2 (R3) of the second planetary gear set PG2 is disposed. The output gear (OUT) is mounted to act as an output element.

The first ring gear R1 of the first planetary gear set PG1 is directly connected to the input shaft 3, and the third and third pinions P2 and P3 of the second planetary gear set PG2 are connected to each other. The planet carrier PC3 is variably connected to the input shaft 3 via the third clutch C3.

In addition, the first planet carrier PC1 connecting the first pinion P1 of the first planetary gear set PG1 may have a first clutch (3) between the third sun gear S3 of the second planetary gear set PG2. They are variably connected to each other via C1), which in turn are variably connected to each other via a second clutch C2 between the second sun gear S2.

The second sun gear S2 is variably fixed to the transmission housing H through the second brake B2, and connects only the second planetary gear P2 of the second planetary gear set PG2. The second planetary carrier PC2 is variably connected to the transmission housing H via the first brake B1 disposed in parallel with the second brake B2 in the transmission housing H.

In the power train, as shown in FIG. 7, the first clutch C1 and the first brake B1 operate at the first forward speed, and the first clutch C1 and the second brake B2 at the second speed. The first clutch C1 and the second clutch C2 operate in the third speed.

In the fourth speed, the first clutch C1 and the third clutch C3 are operated. In the fifth speed, the second and third clutches C2 and C3 are operated. In the sixth speed, the third clutch C3 and the third clutch are operated. The two brakes B2 are operated, and the second gear C2 and the first brake B1 are operated at the reverse shift stage to implement the shift stages of 6 forward speed and 1 reverse speed in the form of the shift diagram of FIG. 8. do.

In the power train as described above, however, as shown in Fig. 8, the first pinion and the third pinion in the forward 1 and 4 speeds, the first and second pinions in the forward 2 speed, and the first pinion in the forward 3 speed, At speed 5, the first and second pinions rotate, while at speed 6, the second pinion is energized.

Accordingly, at least one or more pinions rotate in all transmission stages, thereby causing a large power loss due to gear rolling resistance, and particularly, a high power transmission stage in the fifth or more forward speed stages.

Therefore, the present invention has been invented to solve the above-mentioned conventional problems, the object of the present invention can implement a sixth forward or seventh forward speed with one power train, the deceleration input is made in the low speed region, high speed region In the present invention is to provide a power train of the automatic transmission for a vehicle that can minimize the power loss by effectively changing the rotational power of the engine by making the input of the same speed.

In order to achieve the above object, the present invention includes a first planetary gear set which is a simple planetary gear set for decelerating and outputting rotational power transmitted from an input shaft through a first input path;

Two input elements selectively receiving rotational power from the first planetary gear set through second and third input paths, and selectively receiving rotational power of the same speed as the input shaft through a fourth input path. Second planetary gearset consisting of a combination of two simple planetary gearsets to hold an actuating element acting as a constant or fixed element, an actuating element acting optionally as a stationary element, and an actuating element acting as a constant output element. Wow;
A plurality of clutches applied to the second, third, and fourth input paths to variably transmit power;
A plurality of brakes that variably connect the operating element of the second planetary gearset acting as the fixed element with the transmission housing,
The plurality of clutches respectively applied to the second, third and fourth input paths are all disposed in the second planetary gear set.

The first planetary gear set is a single pinion planetary gear set, and includes: a first sun gear, a first ring gear, and a first pinion rotatably supporting a first pinion engaged between the first sun gear and the first ring gear. It has three operating elements consisting of a planetary carrier,
The second planetary gear set is a two-simple compound planetary gear set combining two single-pinion planetary gear sets. Power of a vehicular automatic transmission comprising: a second planetary carrier rotatably supporting second and third pinions; and five actuating elements comprising second and third ring gears in which the second and third pinions are inscribed. Provide train.

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Hereinafter, with reference to the accompanying drawings, preferred embodiments of the present invention that can specifically realize the above object is as follows.

1 schematically shows an embodiment of a power train according to the present invention, wherein the power train of the present invention comprises a first pinion planetary gear set on an input shaft IS connected to an engine output side via a torque converter. The planetary gear set PG1 and the second planetary gear set PG2 composed of a two-simple type complex planetary gear set are disposed.

The first planetary gear set PG1 is a single pinion planetary gear set, and includes a first sun gear S1, a first ring gear R1, and a first sun gear S1 and a first ring gear R1. It holds three operating elements consisting of a first planetary carrier (PC1) to rotatably support the first pinion (P1) to be engaged to.

The second planetary gear set PG2 is a two-simple compound planetary gear set that combines two single-pinion planetary gear sets. The second planetary gear set PG2 is formed integrally with the second and third sun gears S2 and S3 while varying the outer diameter. The second planet carrier (PC2) rotatably supporting the second, third pinion (P2) (P3) to be engaged with the second, third sun gear (S2) (S3) consisting of a stepped pinion that is And five operating elements consisting of second and third ring gears R2 and R3 in which the second and third pinions P2 and P3 are inscribed.

In the first and second planetary gear sets PG1 and PG2, the first planetary gear set PG1 is disposed on the engine side and the second planetary gear set PG2 is disposed to the rear side. And the first, second and third clutches C1, C2 and C3 and the first and second brakes B1 with the output gear OG disposed between the two planetary gear sets PG1 and PG2. B2) and one-way clutch F1 are combined.

In more detail, the first ring gear R1 of the first planetary gear set PG1 is directly connected to the input shaft IS to always operate as an input element.

The first sun gear S1 is directly fixed to the transmission housing H to always operate as a fixed element, and the first planetary carrier PC1 is rotated and decelerated by the first planetary gear set PG1. It operates as an output element for transmitting power to the second planetary gear set (PG2).

To this end, the first planet carrier PG1 is variably connected to the second sun gear S2 of the second planetary gear set PG2 through the first clutch C1 and at the same time through the second clutch C2. It is also variably connected to the third sun gear S3 of the planetary gear set PG2.

In addition, the second ring gear R2 is variably connected to the input shaft IS through a third clutch C3, so that the second planetary gear set PG2 is selectively input through three paths. do.

In addition, the second ring gear R2 of the second planetary gear set PG2 is variably connected to the transmission housing H via the second brake B2, so that the second ring gear R2 may also operate as an input element and a fixed element. It is composed.

In addition, the third ring gear R2 of the second planetary gear set PG2 is connected to the transmission housing H via a first brake B1 and a one-way clutch F1 arranged in parallel to be fixed and variable. Element, and the second planet carrier PC2 is connected to the output gear OG to operate as an output element at all times.

In the arrangement of the three clutches C1, C2 and C3, all of the clutches are arranged at the rear side of the second planetary gear set PG2, and the first and second clutches C1 and C2 are shafts. Direction was arranged in parallel, and the third clutch C3 was arranged on the outer circumferential side thereof, thereby making it compact.

Accordingly, the power transmission member TS for transmitting the decelerated rotational power from the first planetary gear set PG1 is connected to the rear side of the second planetary gear set PG2, and the power transmission member TS is connected to the first. And the second sun gear S2 and the third sun gear S3 via two clutches C1 and C2.

By the above configuration, the rotational power of the engine is input to the first planetary gear set PG1 through the first input path IP1 and decelerated through the first planetary gear set PG1, and then the first clutch C1. The second sun gear S2 and the third sun gear S3 of the second planetary gear set PG2 via the second input path IP2 by the second path and the third input path IP3 by the second clutch C2. Are respectively entered.

A part of the rotational power of the engine is selectively directly input to the second ring gear R2 of the second planetary gear set PG2 through the fourth input path IP4.

Accordingly, the second planetary gear set PG2 receives rotational power selectively inputted through three input paths IP2, IP3, and IP4, two brakes B1, B2, and one one-way clutch F1. Shift is controlled by the control of).

In more detail, when the first clutch C1 is operated to be input through the second input path IP2, in the case of a six-speed transmission, when the one-way clutch F1 is operated as shown in FIG. When the first speed and the second brake B2 are operated, the second speed and the second clutch C2 are simultaneously operated, the fourth forward speed and the third clutch C3 are simultaneously operated.

When the second clutch C2 is operated to be input to the third input path IP3, when the second brake B2 is operated, the third forward speed is performed, and when the first clutch C1 is operated, the fourth forward speed is applied. When the clutch C3 is operated, shifting is performed at 5 forward speeds.

In addition, when the third clutch C3 is operated to be input through the fourth input path IP4, when the second clutch C2 is operated, 5 forward speeds and when the first clutch C1 is operated, 6 forward speeds. When the first brake B1 is operated, shifting is performed in reverse.

In order to implement the 7th speed shift stage, the 6th speed shift stage as described above, as shown in FIG. 4, is inputted to the third input path IP3 and the first brake B1 is operated. 7 forward speeds can be achieved by adding 2 forward speeds.

Looking at the shifting process in more detail as follows.

First, in the case of 6th forward speed, the shift is made as shown in the shift diagram of FIG. 3. The second planetary gear set PG2, which is a type of planetary gear set of the type, is composed of a second shift gear diagram corresponding to eight nodes.

That is, the first node (N1) is the first sun gear (S1), the second node (N2) is the first planet carrier (PC1), the third node (N3) is the first ring gear (R1), the fourth node ( N4 is the second sun gear S2, the fifth node N5 is the third sun gear S3, the sixth node N6 is the second planet carrier PC2, and the seventh node N7 is the third ring gear. (R3) and the eighth node N8 are set to the second ring gear R2.

Under this node setting, the first clutch C1 and the one-way clutch F1 are operated at the forward 1 speed.

Then, the rotational power input to the first input path IP1 is decelerated by the first planetary gear set PG1 and input through the second sun gear S2 which is the fourth node N4, and the one-way clutch F1 By operation, the third ring gear R3, which is the seventh node N7, is operated as a fixed element.

Accordingly, the same speed line as that of the first speed line L1 of FIG. 3 is formed, and the shift speed of the forward 1 speed is made while being output as much as D1 through the sixth node N6 as an output element.

In the first speed, the first brake B1 is operated regardless of whether the one-way clutch F1 is operated or not.

In the second forward speed, while the second brake B2 is operated and controlled in the state of the first speed, the second ring gear R2 operates as a fixed element to form the same speed line as the second speed line L2. As the output element is output as much as D2 through the sixth node N6, the second speed change is performed.

In the third forward speed, the second clutch C2 is operated while the first clutch C1 is released in the second speed state, and the input element is switched.

Then, the tool force decelerated in the first planetary gear set PG1 is input to the third sun gear S3 that is the fifth node N5 through the third input path IP3 and is operated by the operation of the second brake B2. The second ring gear R2, which is an eight node N8, operates as a fixed element to form the same speed line as the third speed line L3, and is output as D3 through the sixth node N6, which is an output element. A shift of 3 forward speeds is achieved.

At 4th forward speed, the operation of the second brake B2 is released in the state of the third speed, and the first clutch C1 is operated.

Then, input is simultaneously made through the second sun gear S2 as the fourth node N4 and the third sun gear S3 as the fifth node N5. The second planetary gear set PG2 is directly connected. When the output is the same as the input, the same speed line as that of the fourth speed line L4 is formed, and the output speed of the fourth forward speed is made while outputting as much as D4 through the sixth node N6 as an output element. .

At the fifth forward speed, the first clutch C1 is released from the fourth speed state, and the third clutch C3 is operated.

Then, input is simultaneously made through the third sun gear S3, which is the fifth node N5, and the second ring gear R2, which is the eighth node N8. In this case, the input through the fifth node N5 is performed. In the decelerated state, the input is made at the same speed as the engine through the eighth node N8.

Accordingly, the fifth speed line L5 connecting the fifth node N5 and the eighth node N8 is formed. The fifth speed line L5 is output as much as D5 through the sixth node N6, which is an output element. You lose.

At the 6th forward speed, the operation of the second clutch C2 is released in the state of the fifth speed at the 5th forward speed, and the first clutch C1 is operated.

Then, the fourth node N4 and the eighth node N8 are simultaneously inputted through the second sun gear S2 that is the fourth node N4 and the second ring gear R2 that is the eighth node N8. The sixth speed line L6 is connected to the sixth speed line L6. The sixth speed line L6 is output as much as D6 through the sixth node N6.

In the reverse shift stage, the third clutch C3 and the first brake B1 are controlled to operate.

Then, an input is made to the second ring gear R2 that is the eighth node N8, and the eighth node N8 and the seventh node become the fixed element as the third ring gear R3 that is the seventh node N7. The reverse line R1 connecting the N7 is formed, and the reverse shift is performed while being reversed as much as R through the sixth node N6, which is an output element.

5 is a shift diagram when the seventh forward speed is implemented by the power train of the present invention, by controlling to obtain another shift stage between the first speed and the second speed in the shifting process for implementing the forward sixth speed. 7 forward speed is implemented.

More specifically, at the first forward speed, the first clutch C1, the first brake B1, and the one-way clutch F1 are operated.

Then, the rotational power input to the first input path IP1 is decelerated by the first planetary gear set PG1 and input through the second sun gear S2 which is the fourth node N4, and the one-way clutch F1 By operation, the third ring gear R3, which is the seventh node N7, is operated as a fixed element.

Accordingly, the same speed line as that of the first speed line L1 of FIG. 3 is formed, and the shift speed of the forward 1 speed is made while being output as much as D1 through the sixth node N6 as an output element.

At the second forward speed, the operation of the first clutch C1 is released in the state of the first speed, and the third sun gear S3 is operated as an input element while the second clutch C2 is operated and controlled, so that the second speed line L2 is operated. It forms a speed line, such as), and is output as much as D2 through the sixth node (N6) as the output element is a shift in the second forward speed.

At the third forward speed, the operation of the second clutch C2 and the first brake B1 is released, and the operation of the first clutch C1 and the second brake B2 is performed.

Then, the second sun gear S2, which is the N4th node, becomes an input element, and the second ring gear R2, which is the eighth node N8, acts as a fixed element to form the same speed line as the third speed line L3. It is formed, and outputs as much as D3 through the sixth node (N6) as the output element is made to the third speed shift.

In the fourth forward speed, the input element is switched while the first clutch C1 is released in the third speed state.

Then, the second ring gear R2, which is input through the third sun gear S3, which is the fifth node N5, and the eighth node N8, is operated as a fixed element by the operation of the second brake B2. It forms the same speed line as the speed line L4, and is output as much as D4 through the sixth node N6, which is an output element, so that the third forward speed is shifted.

At the fifth forward speed, the second brake b2 is released from the fourth speed state, and the first clutch C1 is operated.

Then, input is simultaneously made through the second sun gear S2 as the fourth node N4 and the third sun gear S3 as the fifth node N5. The second planetary gear set PG2 is directly connected. When the output is the same as the input to form the same speed line as the fifth speed line (L5), it is output as much as D5 through the sixth node (N6) as the output element is shifted to the fifth forward speed.

At the sixth forward speed, the first clutch C1 is released in the fifth speed state, and the third clutch C3 is operated.

Then, input is simultaneously made through the third sun gear S3, which is the fifth node N5, and the second ring gear R2, which is the eighth node N8. In this case, the input is made through the fifth node N5. Is in a decelerated state, and the input is made at the same speed as the engine through the eighth node N8.

Accordingly, the sixth speed line L6 connecting the fifth node N5 and the eighth node N8 is formed. The sixth speed is shifted by outputting D6 through the sixth node N6 as an output element. You lose.

At the seventh forward speed, the second clutch C2 is released in the sixth speed state, and the first clutch C1 is operated.

Then, the fourth node N4 and the eighth node N8 are simultaneously inputted through the second sun gear S2 that is the fourth node N4 and the second ring gear R2 that is the eighth node N8. The seventh speed line L7 is connected to each other, and is output as much as D7 through the sixth node N6, which is an output element.

Since the reverse shift stage is made the same as the reverse shift in the sixth speed, detailed description thereof will be omitted.

In addition, in the power train according to the present invention, detailed descriptions are not described, but from forward 6 speed to 4 forward and 3 speed, from 5 forward to 3 forward and 2 speed, from 4 forward to 2 speed Skip shifting is possible, and this can be realized because skip shifting is possible only by changing control of one operating element while maintaining operation of one operating element, thereby improving the feeling of shifting.

Although the preferred embodiment of the power train of the present invention has been described above, the present invention is not limited to the above embodiment, and those of ordinary skill in the art to which the present invention pertains easily from the embodiment of the present invention. Invention includes all modifications to the extent deemed equivalent.

As described above, the power train of the present invention can realize sixth speed or seventh speed forward with a simple configuration by combining one simple planetary gear set and one compound planetary gear set with three clutches and two brakes. .

In the low speed region, the deceleration is input, and in the high speed region, the input of the same speed is performed, thereby effectively changing the rotational power of the engine and minimizing the power loss.

In addition, the four-speed forward or five forward speed planetary gear set is the invention that allows the power transmission to be made in a direct connection state, to minimize the power loss.

Claims (9)

A first planetary gear set, which is a simple planetary gear set that decelerates and outputs rotational power transmitted from an input shaft through a first input path; Two input elements selectively receiving rotational power from the first planetary gear set through second and third input paths, and selectively receiving rotational power of the same speed as the input shaft through a fourth input path. Second planetary gearset consisting of a combination of two simple planetary gearsets to hold an actuating element acting as a constant or fixed element, an actuating element acting optionally as a stationary element, and an actuating element acting as a constant output element. Wow; A plurality of clutches applied to the second, third and fourth input paths to variably transmit power; A plurality of brakes that variably connect the operating element of the second planetary gearset acting as the fixing element to the transmission housing, The plurality of clutches respectively applied to the second, third and fourth input paths are all disposed in the second planetary gear set. The first planetary gear set is a single pinion planetary gear set, and includes: a first sun gear, a first ring gear, and a first pinion rotatably supporting a first pinion engaged between the first sun gear and the first ring gear. It has three operating elements consisting of a planetary carrier, The second planetary gear set is a two-simple compound planetary gear set that combines two single-pinion planetary gear sets. Power of a vehicular automatic transmission comprising: a second planetary carrier rotatably supporting second and third pinions; and five actuating elements comprising second and third ring gears in which the second and third pinions are inscribed. Train. delete The method of claim 1, The first planetary gear set includes a first ring gear directly connected to the input shaft as a constant input element, a first sun gear fixed directly to a transmission housing as a constant fixing element, and a first planet carrier as a constant output element. Power train of an automatic transmission for a vehicle, characterized in that it is connected to 2 and 3 input paths. The method of claim 1, In the second planetary gear set, the second and third sun gears are connected to the first planet carrier through the first and second clutches, and the second ring gear is connected to the input shaft through the third clutch so that the second, third and fourth inputs are performed. A power train for an automatic transmission for a vehicle, characterized by forming a route. The method of claim 1, And the second planetary gear set is variably connected to the transmission housing via the second and first brakes so that the second and third ring gears can act as fixed elements, respectively. The method of claim 5, And the second brake is connected to the transmission housing between the third clutch and the second ring gear. The method of claim 5, And the third ring gear is connected to the transmission housing with the one-way clutch disposed in parallel with the first brake. The method of claim 1, And the first planetary gear set is disposed at the engine side, the second planetary gear set is disposed at the rear side, and an output gear is disposed between the first and second planetary gear sets. The method of claim 1, The clutches applied to the second and third input paths are arranged in parallel in the axial direction on the rear side of the second planetary gear set, and the clutch on the fourth input path is disposed on the outer circumferential side of the clutch. Power train of the transmission.

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