KR20090017876A - Gear train in an automatic transmission for vehicles - Google Patents

Abstract

A gear train of an automatic transmission for vehicle is provided to reduce capacity of an oil pump and to enhance oil pressure control efficiency by performing a shift operation with two frictional elements at each of shift stages. A first planetary gear set(PG1) includes a first rotation element(N1) to be operated as a fixed element, a third rotation element forming a second intermediate output path(MOP2), and a second rotation element(N2) for forming a first intermediate output path(MOP1). A second planetary gear set(PG2) includes a fourth rotation element(N4) for forming a first intermediate input path(MIP1), a fifth rotation element for forming a second intermediate input path(MIP2) and a third intermediate input path(MIP3), and a six rotation element(N6). A third planetary gear set(PG3) includes a seventh rotation element(N7) for forming a fourth intermediate input path and a ninth operation element.

Description

GEAR TRAIN IN AN AUTOMATIC TRANSMISSION FOR VEHICLES}

The present invention relates to a gear train of an automatic transmission for a vehicle so that three planetary gear sets may be combined with four clutches and two brakes to realize a sixth speed shift stage.

In general, a multi-stage shifting mechanism of an automatic transmission is implemented by combining a plurality of planetary gearsets, and a gear train in which the plurality of planetary gearsets is combined receives a rotational power from a torque converter and shifts it to the output shaft. Will be

In this automatic transmission, the more gears that can be implemented, the more appropriate the gear ratio can be designed and the vehicle can be realized in terms of power performance and fuel efficiency. .

And even if the same shift stage is implemented, the durability, power transmission efficiency, size, etc. of the gear train vary depending on the combination method of the planetary gear set, and thus invent a more robust, power lossless, and more compact gear train configuration. Efforts are always underway.

In particular, unlike a manual transmission in which a shifting speed is more inconvenient for a driver, the automatic transmission shifts by controlling a gear train in accordance with a driving state. Efforts are being made to find a gear train configuration that can be implemented.

From this point of view, the automatic transmission that is currently used is a four-speed and five-speed automatic transmission is the mainstream, but recently the six-speed automatic transmission has been applied to the vehicle in practical use.

Accordingly, the present inventors have proposed the present invention in order to meet the development of the automatic transmission as described above, and an object of the present invention is to combine three simple planetary gearsets with four clutches and two brakes. By providing a speed, the present invention provides a gear train of an automatic transmission for a vehicle to improve power transmission performance and reduce fuel consumption.

In order to realize the above object, the present invention provides a simple planetary gear set having three rotating elements, which is connected to an input shaft and a first rotating element which always operates as a fixed element, and at the same time the input path is formed. A first planetary gear comprising a third rotating element forming a second intermediate output path, and a second rotating element forming a first intermediate output path through which the output power is decelerated by the rotational power input to the third rotating element. Set;

A simple planetary gear set having three rotating elements, comprising: a fourth rotating element for forming a first intermediate input path that is always powered from the first intermediate output path, and a variable power from the second intermediate output path. A fifth intermediate input path that forms a second intermediate input path received at the same time and is variably connected to the second intermediate output path to form a third intermediate input path for receiving power or outputting rotational power input to the second intermediate input path; A second planetary gear set including a rotation element and a sixth rotation element forming a third intermediate output path for selectively rotating and increasing the rotational power input through the first, second and third intermediate input paths; ;

A simple planetary gear set having three rotating elements, comprising: a seventh rotating element forming a fourth intermediate input path receiving power from the third intermediate output mirror; and the seventh rotating element always acting as a final output element. And a ninth operating element selectively variably connected to the eighth operating element, and a ninth operating element variably connected to the first intermediate output path and simultaneously forming a fifth intermediate input path variably connected to the fifth rotating element. 3 provides a gear train for an automatic transmission for a vehicle including a planetary gear set.

Wherein the first planetary gear set is a double pinion planetary gear set, the first rotating element is a first sun gear, the second rotating element is a first ring gear, the third rotating element is a first planetary carrier, the second The planetary gear set is a single pinion planetary gear set, wherein the fourth actuating element is the second sun gear, the fifth rotating element is the second planetary carrier, the sixth rotating element is the second ring gear, and the third planetary gear set is the double The pinion planetary gear set, wherein the seventh rotating element is the third sun gear, the eighth rotating element is the third ring gear, and the ninth rotating element is the third planetary carrier.

The first, second and third planetary gear sets may be combined with four clutches and two brakes, wherein the first rotating element is directly connected to the transmission housing, and the third rotating element is directly connected to the input shaft. With the rotating element and the fourth rotating element directly connected, the sixth rotating element and the seventh rotating element directly connected, and the eighth rotating element connected to the output shaft,

The second rotating element and the ninth rotating element are variably connected by the first clutch, the fifth rotating element and the ninth rotating element are variably connected by the second clutch, and the third rotating element is connected with the fifth rotating element. A third clutch is variably connected, the seventh rotating element and the ninth rotating element are connected by a fourth clutch, the fifth rotating element is variably connected to the transmission housing via the first brake, and the sixth rotating element is It is variably connected with the transmission housing.

Wherein the first clutch is disposed between the first and second planetary gearsets, and the second and fourth clutches are between the second and third planetary gearsets, the second clutch being on the second planetary gearset side and the fourth The clutch is disposed on the third planetary gearset side, the third clutch is disposed in front of the first planetary gearset, and the first and second brakes are disposed on the outer circumferential side of the second planetary gearset.

The gear train of the present invention configured as described above decelerates and outputs the rotational power input from the input shaft at the first planetary gear set at forward 1 speed, and the deceleration input from the first planetary gear set at the second planetary gear set. Reverse rotation output of the state, and the second planetary gear set in the third planetary gear set and the two rotational power input from the first planetary gear set and the deceleration output by complementary operation to realize the speed of the forward 1 speed do.

In the second forward speed, the rotational power input from the input shaft is decelerated and output from the first planetary gear set, and the rotational power input from the first planetary gearset in the third planetary gear set is decelerated and shifted by the operation of the second brake to move forward. It outputs with a gear ratio smaller than 1 speed, and realizes 2 speeds forward.

In the third forward speed, the rotational power input from the input shaft of the first planetary gear set is decelerated and output, while the second and third planetary gear sets are directly connected, the output is output as it is and the third forward speed is realized.

At 4th forward speed, the rotational force input from the input shaft is decelerated and output from the first planetary gear set, and the rotational power input from the first planetary gear set is increased from the second planetary gear set, and the third planetary gear set is output. The rotational power input from the first planetary gear set and the second planetary gear set is complementary to output less than the speed ratio of the third speed, thereby realizing a fourth speed shift.

In the fifth forward speed, the rotational power input from the first planetary gear set is output at a deceleration and the same speed through two paths, and the rotational power input from the first planetary asset through the two paths is input from the first planetary gear set. And outputs through two paths at the same speed and speed, and outputs the rotational power input from the second planetary gear set through the two paths in the third planetary gear set as an overdrive state by complementary operation. We realize shifting.

In the 6th forward speed, the first planetary gear set is output as it is, the second planetary gear set is outputted by increasing the rotational power input from the first planetary gear set, and directly connected to the third planetary gear set. While outputting the rotational power input from the second planetary gear set as it is to realize a six-speed forward.

In reverse 1 speed, decelerating and outputting from the first planetary gear set, and outputting by rotating the rotational power input from the first planetary gear set in the second planetary gear set, decelerating and outputting the third planetary gear set Shifting in reverse speed is realized.

In the second reverse speed, the first planetary gear set is decelerated and output, the second planetary gear set is rotated and outputted from the first planetary gear set, and the third planetary gear set is input from the second planetary gear set. It outputs as it is and realizes 2nd speed shifting.

As described above, by combining three simple planetary gear sets with four clutches and two brakes as friction elements, a shift stage of six forward speeds and two reverse speeds may be implemented to improve power transmission performance and improve fuel economy.

By reversing the speed, the reverse traveling performance can be improved, and the friction element can be distributed to facilitate the configuration of the flow path.

In addition, by shifting the two friction elements in each shift stage while operating, it is possible to reduce the capacity of the oil pump and increase the hydraulic control efficiency.

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

 1 shows an embodiment of a power train according to the present invention, wherein the gear train of the present invention includes first and second planetary gear sets PG1, PG2, and PG3 arranged on the same axis. And clutch means composed of clutches C1, C2, C3, and C4, and brake means composed of two brakes B1 and B2.

Accordingly, the rotation input from the input shaft IS is shifted through the first, second and third planetary gear sets PG1, PG2 and PG3 and output through the output shaft OS. PG1 is arranged on the engine side, and second and third planetary gear sets PG2 and PG3 are sequentially arranged on the rear side.

The input shaft IS refers to the turbine shaft of the torque converter as an input member, which means that the rotational power from the crank shaft of the engine is input while torque conversion is performed through the torque converter, and the output shaft OS is not shown as the output member. The drive wheels are driven by a known differential device via an output gear.

The first planetary gear set PG1 is a double pinion planetary gear set, and includes a first rotating element N1 made of a first sun gear S1 and a second rotating element N2 made of a first ring gear R1. And a third rotating element N3 made of the first planet carrier PC1.

The first rotating element {N1; The first sun gear S1} is directly connected to the transmission housing H so that it can always operate as a fixed element.

The second rotating element {N2; The first ring gear (R1)} forms a first intermediate output path (MOP1) is always a deceleration output, the first intermediate output path (MOP1) is a variable output that is output through the first clutch (C1). It is divided into a path (MAOP) and a direct output path (MDOP).

To this end, the first power transmission member 2 forming the first intermediate output path MOP1 plays a role of the direct output path MDOP and at the same time interposes the second clutch C1 at a predetermined position. By connecting the transmission member 4, the variable output path (MAOP) is formed.

The third rotating element {N3; The first planetary carrier PC1 operates as an input element and an output element, and is directly connected to the input shaft IS to form an input path IP and a second intermediate output path for outputting the input as it is. (MOP2) is formed.

Accordingly, in the first planetary gear set PG1, the rotational power input to the input path IP is decelerated through the first intermediate output path MOP1, and at the same speed through the second intermediate output path MOP2. The output will be made.

The second planetary gear set PG2 is a single pinion planetary gear set, and includes a fourth rotating element N4 made of the second sun gear S2 and a fifth rotating element N5 made of the second planetary carrier PC2. And a sixth rotating element N6 formed of the second ring gear R2.

The fourth rotating element {N4; The second sun gear S2} is directly connected to the first power transmission member 2 forming a direct output path MDOP of the first intermediate output path MOP1 to form a first intermediate input path MIP1. Thus, the rotational power which is decelerated and output from the first planetary gear set PG1 is input.

The fifth rotating element {N5; The second planet carrier PC2} is connected to a third power transmission member 6 connected by starting the second intermediate output path MOP2 and the third clutch C3 of the first planet gear set PG1. Second power transmission member 4 which forms a second intermediate input path MIP2 and simultaneously forms a variable output path MAOP of the first intermediate output path MOP1 of the first planetary gear set PG2. And is variably connected via the second clutch C2 to form a third intermediate input path MIP3.

In the above, the third intermediate input path MIP3 does not necessarily operate only as an input path, and when the second and third clutches C2 and C3 are operated at the same time, a rotation input through the second intermediate input path MIP2 is performed. Output power to the second power transmission member (4).

And the third power transmission member 6 is connected to the transmission housing (H) by opening the one-way clutch (F) to prevent the reverse rotation through the first brake (B1) to operate as a fixed element at the same time. It is variablely connected to the transmission housing (H).

The sixth rotating element {N6; The second ring gear R2} forms a third intermediate output path MOP3 and simultaneously changes the third intermediate output path MOP3 with the transmission housing H through the second brake B2. Connected.

Accordingly, the reverse rotation output is made through the sixth rotating element N6 or the rotational power input through the fourth rotating element N4 is simultaneously input to the fourth and fifth rotating elements N4 and N5. In this case, the speed increase output is performed through the sixth rotating element N6.

The third planetary gear set PG3 is a double pinion planetary gear set. The third planetary gear set PG3 includes a seventh rotating element N7 made of the third sun gear S3 and an eighth rotating element N8 made of the third ring gear R3. And a ninth rotating element N9 made of the third planet carrier PC3.

The seventh rotating element {N7; The third sun gear S3} is connected to the fourth power transmission member 8 forming the third intermediate output path MOP3 to form a fourth intermediate input path MIP4.

The eighth rotating element {N8; The third ring gear R3} forms the final output path OP, and the final shifted rotational power is output through the output shaft OS connected thereto.

The ninth rotating element {N9; The third planet carrier PC3 forms a variable output path MAOP of the first planetary gear set PG1 and is variably connected to the third intermediate input path MIP3 of the second planetary gear set PG2. It is connected to the second power transmission member 4 to form a fifth intermediate input path MIP5.

A fourth clutch C4 is disposed between the seventh rotation element N7 and the ninth rotation element N9 to control the third planetary gear set PG3 in a selective direct connection state.

In the gear train of the present invention configured as described above, basically the first sun gear (S1) is directly connected to the transmission housing (H), the first planet carrier (PC1) is directly connected to the input shaft (IS), The first ring gear R1 and the second sun gear S2 are directly connected, the second ring gear R2 and the third sun gear S3 are directly connected, and the third ring gear R3 is the output shaft OS. ) Are combined by four clutches C1, C2, C3, C4 and two brakes B1, B2.

The first ring gear R1 and the third planet carrier PC3 are variably connected by the first clutch C1, and the second planet carrier PC2 and the third planet carrier PC3 are connected to the second clutch (C1). C1) is variably connected, the first planet carrier (PC1) is variably connected by the second planet carrier (PC2) and the third clutch (C3), the third sun gear (S3) and the third planet carrier (PC3) Is connected by a fourth clutch C4.

In addition, the second planet carrier PC2 is variably connected to the transmission housing H via the first brake B1, and the second ring gear R2 is variably connected to the transmission housing H.

In the above, the first, second, third and fourth clutches C1, C2, C3 and C4 and the first and second brakes B1 and B2 are made of a multi-plate hydraulic friction engagement unit friction-coupled by hydraulic pressure. Is common.

The first clutch C1 is disposed between the first and second planetary gear sets PG1 and PG2, and the second and fourth clutches C2 and C4 are the second and third planetary gear sets PG2. The second clutch C2 is disposed at the second planetary gear set PG2 and the fourth clutch C4 is disposed at the third planetary gear set PG3. C3 is disposed in front of the first planetary gear set PG1.

Further, the first and second brakes B1 and B2 are disposed on the outer circumferential side of the second planetary gear set PG2.

2 is an operation table showing that the friction member, that is, the clutch and the brake applied to the present invention operate at each shift stage, and the power train of the present invention shows that the shift is performed while the two friction members operate at each shift stage. Can be.

That is, the first clutch C1 and the first brake B1 or the one-way clutch F are operated at the first forward speed, and the first clutch C1 and the second brake B2 are operated at the second forward speed. The first clutch C1 and the second clutch C2 are operated at the third speed, and the first clutch C1 and the third clutch C3 are operated at the fourth forward speed, and the second and third clutch C2 are operated at the fifth forward speed. (C3) is operated, the third, fourth clutch (C4) is operated in the sixth forward speed is made to the forward shift.

The second clutch C2 and the first brake B1 are operated at the first reverse speed, and the fourth clutch C4 and the first brake B1 are operated at the second reverse speed, so that the reverse shift is performed.

3 shows a speed change diagram of the power train according to the present invention, in which the horizontal line on the lower side represents the rotational speed "0", and the horizontal line on the upper side represents the rotational speed "1.0", that is, the same rotational speed as the input shaft IS. .

The three vertical lines of the first planetary gear set PG1 are sequentially rotated from the left to the first sun gear S1 as the first rotation element N1, the first ring gear R1 as the second rotation element N2, and the third rotation. The first planetary carrier PC1, which is the element N3, is set, and these intervals are determined according to the gear ratio of the first planetary gear set PG1 (number of teeth of the sun gear / number of rings).

The three vertical lines of the second planetary gear set PG2 are the second sun gear S2, which is the fourth rotating element N4, and the second planetary carrier PC2, which is the fifth rotating element N5, and the sixth rotation, in order from the left. The second ring gear R2, which is the element N6, is set, and these intervals are determined according to the gear ratio of the third planetary gear set PG3 (number of teeth of the sun gear / number of ring gears).

The three vertical lines of the third planetary gear set PG3 are sequentially rotated from the left to the third sun gear S3 as the seventh rotation element N7, the third ring gear R3 as the eighth rotation element N8, and the ninth rotation. The third planetary carrier PC3, which is the element N9, is set according to the gear ratio of the third planetary gear set PG3 (the number of teeth of the sun gear / the number of teeth of the ring gear). Since a person skilled in the art of the power train is known, a detailed description thereof will be omitted.

[1st speed forward]

At the first forward speed, as shown in FIG. 2, the first brake B1 and the one-way clutch F are operated and controlled.

Accordingly, in the first planetary gear set PG1, as shown in FIG. 3, the first rotary element N1 operates as a fixed element while the second rotary element N1 operates as a fixed element. The rotational power output to N2) is the ninth rotating element N9 of the third planetary gear set PG3 by the operation of the fourth rotating element N4 of the second planetary gear set PG2 and the first clutch C2. ) Is entered.

In the second planetary gear set PG2, the fifth operating element N5 is operated as a fixed element by the operation of the one-way clutch F while the input is made to the fourth rotating element N4. The reverse rotation output is made through the sixth rotation element N6, which is an output element, and the reverse rotation output thereof is input to the seventh operation element N7 of the third planetary gear set PG3.

As described above, in the third planetary gear set PG3, the reverse rotation input is performed through the fourth rotation element N7 while the input is made to the ninth rotation element N9 by the operation of the first clutch C1. The first transmission line SP1 is connected to each other to form the first transmission line SP1, and the output is as much as D1 connecting the first transmission line SP1 and the eighth rotation element N8, which is an output element. As the 1st speed shift is made.

That is, when the deceleration output is made through the first intermediate output path MOP1 of the first planetary gear set PG1, the rotational power of the first intermediate output path MOP1 is variable output path MAOP and the fifth. It is input to the ninth rotary element N9 of the third planetary gear set PG3 through the intermediate input path MOP5, and is shifted in reverse rotation from the second planetary gear set PG3, so that the sixth rotary element N6 Reverse rotational power is input to the seventh rotation element N7 of the third planetary gear set PG3 through the third intermediate output path MOP3 and the fourth intermediate input path MIP4 to form the ninth rotation element N9. And the seventh rotation element (N7) is shifted to the highest speed ratio (4.728) by complementary operation according to the rotation speed is output through the eighth rotation element (N8) output element is to be shifted in the first forward speed. .

[2 speed forward]

In the second forward speed, the second brake B2 is operated and controlled in the state of the first forward speed.

Then, in the first planetary gear set PG1, as in the first speed, a deceleration output is performed through the second rotary element N2 and is input to the ninth rotary element N9 of the third planetary gear set PG3. The seventh rotating element N7 is operated as a fixed element by the operation of the second brake B2.

Accordingly, the second shift line SP2 connecting the seventh rotation element N7 and the ninth rotation element N9 is formed, and the second transmission line SP2 and the eighth rotation element N8 that are output elements. ), The output is as much as D2 connecting the 2 forward speed is made.

Of course, at this time, the output of the second rotating element N2 is input through the fourth rotating element N4 of the second planetary gear set PG2, but there is no role by the operation of the second brake B2.

That is, when the deceleration output is made through the first intermediate output path MOP1 of the first planetary gear set PG1, the rotational power of the first intermediate output path MOP1 is the variable output path MAOP and the fifth intermediate. It is input to the ninth rotary element N9 of the third planetary gear set PG3 through the input path MOP5 and the seventh rotary element N7 becomes the fixed element by the operation of the second brake B2. The shift of the inner will be made.

[3 speed forward]

At the third forward speed, as shown in FIG. 2, the second brake B2 is released from the second forward speed, and the second clutch C2 is controlled to operate.

Then, as in the forward 1 and 2 speeds, the second planetary gear set (2) is operated by the operation of the second clutch C2 while the input is made to the ninth rotation element N9 of the third planetary gear set PG3. Input is made to the fifth rotating element N5 of PG2.

Accordingly, the second planetary gear set PG2 is directly input through the fourth rotary element N4 and the fifth rotary element N5, and is directly connected to the third planetary gear set PG3. The third planetary gear set PG3 is also directly connected to form the third shift line SP3, and the third shift line SP3 and the eighth rotation element N8 as an output element. As the output of D3 is connected, the speed of 3rd forward is achieved.

That is, when the deceleration output is made through the first intermediate output path MOP1 of the first planetary gear set PG1, the second and third planetary gear sets PG2 and PG3 are output as they are directly connected. Three forward speeds will be achieved.

[4 forward speed]

In the fourth forward speed, as shown in FIG. 2, the operation of the second clutch C2 is released in the state of the third forward speed, and the third clutch C3 is controlled to operate.

Then, as in the forward 1, 2, and 3 speed, the deceleration output of the first planetary gear set PG2 is input to the ninth rotation element N9 of the third planetary gear set PG3. The input of the input shaft IS is input to the fifth rotating element N5 of the second planetary gear set PG2 by the operation of the clutch C3.

Accordingly, in the second planetary gear set PG2, rotational power of different rotational speeds is simultaneously input through the fourth rotating element N4 and the fifth rotating element N5. ) Is increased to transmit its rotational power to the seventh rotation element N7 of the third planetary gear set PG3 connected thereto.

Then, in the third planetary gear set PG3, rotational power of different rotational speeds is input to the seventh rotation element N7 and the ninth rotation element N9, and the fourth transmission line SP4 is complementary. It is formed, as the output of the D4 connecting the fourth transmission line (SP4) and the eighth rotation element (N8) of the output element is made to be shifted in the fourth forward speed.

That is, while the deceleration output is made through the first intermediate output path MOP1 of the first planetary gear set PG1, its output is transmitted to the third planetary gear set PG3 and at the same time, the second planetary gear set PG2 is provided. In the third planetary gear set (PG3) is increased in the third planetary gear set (PG3) by the complementary operation in the third planetary gear set (PG3) is to be shifted in the fourth forward speed.

[5th forward]

In the fifth forward speed, as shown in FIG. 2, the operation of the first clutch C1 operated in the state of the fourth forward speed is released, and the second clutch C2 is operated and controlled.

Then, the deceleration output through the second rotary element N2 of the first planetary gear set PG2 is transmitted to the fourth rotary element N4 of the second planetary gear set PG2 and at the same time, the third clutch C3 is operated. As a result, the input of the input shaft IS is input to the fifth rotating element N5 of the second planetary gear set PG2.

Accordingly, in the second planetary gear set OPG2, rotational power of different rotational speeds is input to the fourth rotating element N4 and the fifth rotating element N5, and the sixth rotating element N6 is complementary. Is transmitted to the seventh rotation element N7 of the third planetary gear set PG3, and at the same time, the rotation speed of the input shaft IS is maintained by the operation of the second clutch C2 of the third planetary gear set PG3. The fifth shift line SP5 is formed as a complementary action while being input to the ninth rotation element N9, and as much as D4 connecting the fifth shift line SP5 and the eighth rotation element N8 as an output element. As the output of is made, the 5th forward speed of overdrive is achieved.

That is, when the deceleration and the same speed are output through the first and second intermediate output paths MOP1 and MOP2 of the first planetary gear set PG1 and are transmitted to the second planetary gear set PG2, In the gear set PG2, the rotational power of the same speed and speed is transmitted to the third planetary gear set PG3 through two output paths MIP3 and MOP3, and complementary operation is performed in the third planetary gear set OG3. As a result, the output is made at the fifth speed ratio in the overdrive state.

[6th forward]

In the sixth forward speed, as shown in FIG. 2, the operation of the second clutch C2 operated in the fifth forward speed is released, and the fourth clutch C4 is operated and controlled.

Then, the deceleration output through the second rotary element N2 of the first planetary gear set PG2 is transmitted to the fourth rotary element N4 of the second planetary gear set PG2 and at the same time, the third clutch C3 is operated. As a result, the input of the input shaft IS is input to the fifth rotating element N5 of the second planetary gear set PG2.

Accordingly, in the second planetary gear set OPG2, rotational power of different rotational speeds is input to the fourth rotating element N4 and the fifth rotating element N5, and the sixth rotating element N6 is complementary. It is accelerated through and transmitted to the seventh rotation element N7 of the third planetary gear set PG3.

Then, the third planetary gear set PG3 is directly connected by the operation of the fourth clutch C4 to form the sixth shift line SP6 and at the same time as D6 through the eighth rotation element N8 as an output element. As the input of the output is made as it is, the 6th forward speed of the top gear shift is made.

That is, when the first planetary gear set PG1 outputs the input as it is, and the second planetary gear set PG2 increases the speed and transmits it to the third planetary gear set PG3, the third planetary gear set PG3 is transmitted. In the direct connection state, the speed change input from the second planetary gear set PG2 is output as it is, and the forward sixth speed shift is performed.

[1 speed reverse]

In the reverse 1 speed, as shown in FIG. 2, the second clutch C2 and the first brake B1 are operated and controlled.

Accordingly, in the first planetary gear set PG1, as shown in FIG. 3, the first rotary element N1 operates as a fixed element while the second rotary element N1 operates as a fixed element. The rotating power output to N2) is input to the fourth rotating element N4 of the second planetary gear set PG2.

In the second planetary gear set PG2, the fifth operating element N5 is operated as a fixed element by the operation of the first brake B1 while the input is made to the fourth rotating element N4. The reverse rotation output is made through the sixth rotation element N6, which is an output element, and the reverse rotation output thereof is input to the seventh operation element N7 of the third planetary gear set PG3.

Then, in the third planetary gear set PG3, the ninth rotating element N9 is operated as a fixed element by simultaneously operating the first brake B1 and the second clutch C2. SR1) is formed, and as much as the output of RS1 connecting the reverse first speed shift line SR1 and the eighth rotary element N8, which is an output element, the reverse speed 1 is shifted.

That is, in the first planetary gear set PG1, the deceleration output is made through the first intermediate output path MOP1, and the second planetary gear set PG2 is rotated in reverse to the third planetary gear set PG3. If transmitted, the third planetary gear set PG3 decelerates and outputs it, thereby shifting the reverse speed 1.

[2 speed reverse]

In reverse second speed, as shown in FIG. 2, the second clutch C2 is canceled in the reverse first speed state, and the fourth clutch C4 is operated and controlled.

Accordingly, when the deceleration output of the first planetary gear set PG1 is reversely controlled in the second planetary gear set PG2 and transmitted to the third planetary gear set PG3, similarly to the reverse speed 1, the third planetary gear set At PG3, the second clutch 2 is directly connected to the operation of the fourth clutch C4 to form the reverse second shift line SR2, and at the same time, as much as RS2 is output through the eighth rotation element N8, which is an output element, the reverse second speed is achieved. The shift will be made.

That is, in the first planetary gear set PG1, the deceleration output is made through the first intermediate output path MOP1, and in the second planetary gear set PG2, the decelerating output is reversed so that the third planetary gear set PG3 is rotated. In this case, the third planetary gear set PG3 outputs the input as it is, thereby performing shifting in the second reverse speed.

4 shows a second embodiment according to the present invention. Unlike the first embodiment, the third planetary gear set PG3 is applied as a single pinion planetary gear set.

Accordingly, the eighth rotation element N8 is changed from the third ring gear R3 to the third planet carrier PC3, and the ninth rotation element N9 is changed from the third planet carrier PC3 to the third ring gear ( The name of the rotary element, which has been changed to R3) but conceptually given above, is the same, and since the shifting operation is the same as in the first embodiment, detailed description of the configuration and operation is omitted.

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 skilled in the art can easily invent from the embodiment of the present invention. It includes all changes to the extent considered equivalent.

1 is a block diagram of a gear train of a first embodiment according to the present invention;

Figure 2 is a shift-specific operation of the friction member applied to the gear train of the present invention.

3 is a shift diagram of a gear train according to the present invention;

4 is a configuration diagram of a gear train of a second embodiment according to the present invention.

Claims (16)

A simple planetary gear set having three rotating elements, comprising: a first rotating element that always operates as a fixed element, and a third intermediate output path connected to the input shaft to form an input path and at the same time output at the same speed. A first planetary gear set including a rotating element and a second rotating element decelerating a rotating power input to the third rotating element to form a first intermediate output path through which the output is made; A simple planetary gear set having three rotating elements, comprising: a fourth rotating element for forming a first intermediate input path that is always powered from the first intermediate output path, and a variable power from the second intermediate output path. A fifth intermediate input path that forms a second intermediate input path received at the same time and is variably connected to the second intermediate output path to form a third intermediate input path for receiving power or outputting rotational power input to the second intermediate input path; A second planetary gear set including a rotation element and a sixth rotation element forming a third intermediate output path for selectively rotating and increasing the rotational power input through the first, second and third intermediate input paths; ; A simple planetary gear set having three rotating elements, comprising: a seventh rotating element forming a fourth intermediate input path receiving power from the third intermediate output mirror; and the seventh rotating element always acting as a final output element. And a ninth operating element selectively variably connected to the eighth operating element, and a ninth operating element variably connected to the first intermediate output path and simultaneously forming a fifth intermediate input path variably connected to the fifth rotating element. 3 Gear train of automatic transmission for vehicles, including planetary gear sets. 2. The first planetary gearset of claim 1, wherein the first planetary gearset is a double pinion planetary gearset, the first rotating element being a first sun gear, the second rotating element being a first ring gear, and the third rotating element being a first planetary carrier. , The second planetary gear set is a single pinion planetary gear set, the fourth actuating element is composed of a second sun gear, the fifth rotating element is a second planetary carrier, and the sixth rotating element is a second ring gear. The third planetary gear set is a double pinion planetary gear set, wherein the seventh rotating element is the third sun gear, the eighth rotating element is the third ring gear, and the ninth rotating element is the third planet carrier. . 2. The first planetary gearset of claim 1, wherein the first planetary gearset is a double pinion planetary gearset, the first rotating element being a first sun gear, the second rotating element being a first ring gear, and the third rotating element being a first planetary carrier. , The second planetary gear set is a single pinion planetary gear set, the fourth actuating element is composed of a second sun gear, the fifth rotating element is a second planetary carrier, and the sixth rotating element is a second ring gear. The third planetary gear set is a single-pinion planetary gear set, wherein the seventh rotation element is the third sun gear, the eighth rotation element is the third planet carrier, and the ninth rotation element is the third ring gear. . The method of claim 2 or 3, wherein the first, second and third planetary gear sets are combined with four clutches and two brakes, The first rotary element is directly connected to the transmission housing, the third rotary element is directly connected to the input shaft, the second rotary element and the fourth rotary element are directly connected, and the sixth and seventh rotary elements are Directly connected, and with the eighth rotating element connected to the output shaft, The second rotating element and the ninth rotating element are variably connected by the first clutch, the fifth rotating element and the ninth rotating element are variably connected by the second clutch, and the third rotating element is connected with the fifth rotating element. A third clutch is variably connected, the seventh rotating element and the ninth rotating element are connected by a fourth clutch, the fifth rotating element is variably connected to the transmission housing via the first brake, and the sixth rotating element is Gear train of an automatic transmission for a vehicle, characterized by a variable connection with a transmission housing. The method of claim 4, wherein the first clutch is disposed between the first and second planetary gear sets, and the second and fourth clutches are between the second and third planetary gear sets, wherein the second clutch is on the second planetary gear set side. And the fourth clutch is disposed on the third planetary gearset side, the third clutch is disposed on the front of the first planetary gearset, and the first and second brakes are disposed on the outer circumferential side of the second planetary gearset. Gear train of automatic transmission for vehicles. The method according to claim 4, wherein the first clutch and the first brake or one-way clutch F are actuated at the first forward speed, The first clutch and the second brake are operated at the second forward speed, The first clutch and the second clutch are operated at the third forward speed, the first clutch and the third clutch are operated at the fourth forward speed, The second and third clutches are operated at five forward speeds, The third and fourth clutches are operated at six forward speeds; In the reverse 1 speed, the second clutch and the first brake are operated, A gear train of an automatic transmission for a vehicle, wherein the fourth clutch and the first brake are operated at the reverse two speeds. The method according to claim 1 or 6, wherein in the forward 1 speed Decelerating and outputting the rotational power input from the input shaft in the first planetary gear set, In the second planetary gear set, the rotational power of the deceleration state inputted from the first planetary gear set is output in reverse rotation, A gear train of an automatic transmission for a vehicle, characterized in that the third planetary gear set is configured to decelerate and output two rotational powers input from the first planetary gear set and the second planetary gear set in a complementary operation. The method of claim 1 or 6, wherein the second forward speed Decelerating and outputting the rotational power input from the input shaft in the first planetary gear set, The gear train of the automatic transmission for a vehicle, characterized in that the rotational power input from the first planetary gear set in the third planetary gear set is decelerated by the operation of the second brake to output at a transmission ratio smaller than the forward 1 speed. The method according to claim 1 or 6, wherein the third forward speed is Decelerating and outputting the rotational power input from the input shaft in the first planetary gear set, The gear train of the automatic transmission for a vehicle, characterized in that the second and third planetary gear sets are directly connected and output as they are. The method according to claim 1 or 6, wherein the fourth forward speed is Decelerating and outputting the rotational power input from the input shaft in the first planetary gear set, In the second planetary gear set, the rotational power inputted from the first planetary gear set is increased and output. The gear train of the automatic transmission for a vehicle according to claim 3, wherein the third planetary gear set outputs the rotational power input from the first planetary gear set and the second planetary gear set to be smaller than the speed ratio of the third speed by complementary operation. The method of claim 1 or 6, wherein the fifth forward speed Outputs the rotational power input from the first planetary gear set at a reduced speed and the same speed through two paths, In the second planetary gear set, the rotational power inputted through the two paths from the first planetary gear set is outputted through the two paths at the same speed and speed, The gear train of the automatic transmission for a vehicle according to claim 3, wherein the third planetary gear set outputs the rotational power input from the second planetary gear set through two paths in an overdrive state by complementary operation. The method according to claim 1 or 6, wherein the sixth forward speed Output the input as it is from the first planetary gear set, In the second planetary gear set, the rotational power inputted from the first planetary gear set is increased and output. The gear train of the vehicular automatic transmission as set forth in the third planetary gear set is directly connected and outputs the rotational power input from the second planetary gear set as it is. The method of claim 1 or 6, wherein the reverse 1 speed is Decelerating output from the first planetary gear set, In the second planetary gear set, the rotational power inputted from the first planetary gear set is reversed and outputted. Gear train of the automatic transmission for a vehicle, characterized in that by reducing the output from the third planetary gear set. The method of claim 1 or 6, wherein the reverse second speed is Decelerating output from the first planetary gear set, In the second planetary gear set, the rotational power inputted from the first planetary gear set is reversed and outputted. The gear train of the automatic transmission for a vehicle, characterized in that the output from the third planetary gear set as input from the second planetary gear set. A double pinion planetary gear set, comprising: a first planetary gear set, wherein the first rotating element comprises a first sun gear, the second rotating element comprises a first ring gear, and the third rotating element comprises a first planetary carrier; A single pinion planetary gear set, the fourth actuating element comprising a second sun gear, the fifth rotating element comprising a second planet carrier, and the sixth rotating element comprising a second planetary gear set; A double pinion planetary gear set, wherein the seventh rotation element is the third sun gear, the eighth rotation element is the third ring gear, and the ninth rotation element is the third planetary gear set consisting of the third planetary carrier, The first rotary element is directly connected to the transmission housing, the third rotary element is directly connected to the input shaft, the second rotary element and the fourth rotary element are directly connected, and the sixth and seventh rotary elements are Directly connected, and with the eighth rotating element connected to the output shaft, The second rotating element and the ninth rotating element are variably connected by the first clutch, the fifth rotating element and the ninth rotating element are variably connected by the second clutch, and the third rotating element is connected with the fifth rotating element. A third clutch is variably connected, the seventh rotating element and the ninth rotating element are connected by a fourth clutch, the fifth rotating element is variably connected to the transmission housing via the first brake, and the sixth rotating element is Gear train of an automatic transmission for a vehicle, characterized by a variable connection with a transmission housing. A double pinion planetary gear set, comprising: a first planetary gear set, wherein the first rotating element comprises a first sun gear, the second rotating element comprises a first ring gear, and the third rotating element comprises a first planetary carrier; A single pinion planetary gear set, the fourth actuating element comprising a second sun gear, the fifth rotating element comprising a second planet carrier, and the sixth rotating element comprising a second planetary gear set; A single pinion planetary gear set, wherein the seventh rotation element is the third sun gear, the eighth rotation element is the third planetary carrier, and the ninth rotation element is the third planetary gear set consisting of the third ring gear, The first rotary element is directly connected to the transmission housing, the third rotary element is directly connected to the input shaft, the second rotary element and the fourth rotary element are directly connected, and the sixth and seventh rotary elements are Directly connected, and with the eighth rotating element connected to the output shaft, The second rotating element and the ninth rotating element are variably connected by the first clutch, the fifth rotating element and the ninth rotating element are variably connected by the second clutch, and the third rotating element is connected with the fifth rotating element. A third clutch is variably connected, the seventh rotating element and the ninth rotating element are connected by a fourth clutch, the fifth rotating element is variably connected to the transmission housing via the first brake, and the sixth rotating element is Gear train of an automatic transmission for a vehicle, characterized by a variable connection with a transmission housing.

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