KR100887971B1 - Gear train in an automatic transmission for vehicles - Google Patents

Abstract

A gear train in an automatic transmission for a vehicles is provided to reduce the length of a transmission by forming a gear train with three clutches, three breaks, and one way clutch. A gear train comprises a clutch unit, a break unit, and an one one-way clutch(F). The clutch unit is composed of a first and a second planet gear set(PG1,PG2) arranged on the same axis, and three clutch(C1,C2,C3). The break unit is composed of the three brakes(B1,B2,B3). The rotation of input shaft is transmitted to an output gear through the first and the second planet gear.

Description

GEAR TRAIN IN AN AUTOMATIC TRANSMISSION FOR VEHICLES}

The present invention combines one simple planetary gear set and two-simple type planetary gear set with three clutches, three brakes, and one one-way clutch to realize a shift stage of forward 7 speed and reverse 1 speed. It relates to the gear train of an automatic transmission.

For example, the power train of the automatic transmission for vehicles is developed and applied in different forms according to each car maker. Currently, the automatic transmission that is commonly used is mainly composed of four-speed and five-speed transmission, but recently, six-speed automatic transmission Has been developed and applied to some vehicles, while the development of a seven-speed automatic transmission is in progress.

As an example, as shown in FIG. 4 (BENZ 7G-TRONIC 7 speed), two composite planetary gear sets are configured through three clutches, four brakes, and one one-way clutch to allow 7-speed shifting. have,

More specifically, the first composite planetary gear set 100 combines a single pinion planetary gearset and a double pinion planetary gearset, but shares the planetary carrier 102 and the sun gear 104 to form the first sun gear 104. ) And the first planetary carrier 102 and the first and second ring gears 106 and 108.

The second composite planetary gear set 110 combines two single pinion planetary gear sets, and directly connects the third ring gear 112 and the fourth planet carrier 114 to form the third and fourth wire gears 116. 118, the third planet carrier 120, the fourth planet carrier 124, and the fourth ring gear 126.

In connecting each rotary element of the composite planetary gear set 100, 110, the first planet carrier 102 is fixedly connected to the fourth ring gear 126 and at the same time through the one-way clutch (F). It is connected to the transmission housing 128.

The first sun gear 104 is variably connected to the first ring gear 106 using the first clutch K1 and is fixedly fixed to the transmission housing 128 through the first brake B1.

The second ring gear 108 is directly connected to the input shaft 130 to operate as an input element at all times, and the third ring gear 112 is connected to the input shaft 128 through a second clutch K2. Are connected variably.

The third and fourth sun gears 116 and 118 are variably connected via a third clutch K3, and the third sun gear 116 is connected to the transmission housing 128 through a second brake B2. Are connected variably.

The first ring gear 106 and the fourth planet carrier 124 are independently variably connected to the transmission housing 128 through the third and fourth brakes B3 and B4, respectively, and the third planet carrier The 120 is connected to the output shaft 132 to always act as an output element.

As shown in FIG. 5, the seventh-speed power train as described above includes the third clutch K3 and the second and third brakes B2 and B3 at the first forward speed, and the third clutch K3 and the first, 2 brakes B1 (B2), the first and third clutches K1 and K3 at the third forward speed and the second brake B2, and the first and second clutches K1 and K2 and the second brake at the fourth forward speed. B2), the first, second and third clutches K1, K2 and K3 at the fifth forward speed, the second and third clutches K2 and K3 at the sixth forward speed and the first brake B1 and the first at the seventh forward speed. The shifting is performed while the third clutches K1 and K3 and the third brake B3 are operated.

The third clutch K3 and the second and fourth brakes B2 and B4 at the first reverse speed, and the first and third clutches K1 and K3 and the fourth brake B4 at the second reverse speed and the third at the third speed reverse. As the clutch K3 and the third and fourth brakes B3 and B4 are operated, a reverse shift is made.

However, although the above-described power train can realize seven forward speeds and three reverse speeds, three friction elements operate at each shift stage, thereby reducing hydraulic control efficiency and supplying hydraulic pressure to these friction elements. It has a problem that the capacity of.

In addition, the application of seven friction elements has a problem that the overall length of the automatic transmission becomes long and the configuration is complicated.

Therefore, the present invention has been invented to solve the above problems, and the object of the present invention is one simple planetary gear set and two-simple type planetary gear set, three clutches, three brakes, and one one-way clutch In order to realize the 7th forward and the 1st reverse, the gearbox of the automatic transmission is designed to reduce the capacity of the oil pump and increase the hydraulic control efficiency by operating two friction elements at each gear. In providing a train.

In addition, by distributing the six friction elements, it is possible to easily form a flow path formed in the transmission housing to provide a gear train of the automatic transmission for a vehicle to reduce the cost by improving productivity.

In order to realize the above object, the present invention is a simple planetary gear set having three rotating elements,

A first planetary element comprising a first rotating element that always acts as a stationary element, a second rotating element that forms an intermediate output path with constant deceleration output, and a third rotating element connected directly to the input shaft to form an input path A gear set;

A two-simple composite planetary gear set having four rotating elements, which is variably connected to the intermediate output path to form an intermediate input path and at the same time operates as an optional fixed element and connects to the output gear. And a fifth rotating element that is variably connected to the input shaft to form a final output path, and a sixth rotating element that is variably connected to the input shaft to form a second variable input path and acts as an optional fixed element. A gear train of an automatic transmission for a vehicle is provided, which is composed of a combination of a second planetary gear set including a seventh rotating element which forms a variable input path and operates as an optional fixed element.

Wherein the first planetary gear set is a single pinion planetary gear set, the first rotating element is a first sun gear, the second rotating element is a first planetary carrier, the third rotating element is a first ring gear,

The second planetary gear set is composed of a combination of two single pinion planetary gear sets, with the second planet carrier and the third ring gear directly connected, and the second ring gear and the third planet carrier directly connected, The fourth rotating element includes a second sun gear, the fifth rotating element includes a second planetary carrier and a third ring gear, the sixth rotating element includes a second ring gear and a third planetary carrier, and the seventh rotating element includes a third sun gear.

The first and second planetary gear sets are combined with three clutches and three brakes,

With the first rotary element directly connected to the transmission housing, the third rotary element directly connected to the input shaft, and the fifth rotary element connected to the output gear, the first clutch is coupled between the second rotary element and the fourth rotary element. A second clutch is disposed between the input shaft and the seventh rotary element, a third clutch is disposed between the input shaft and the sixth rotary element, and a fourth clutch is disposed between the input shaft and the fourth rotary element, The first brake is disposed between the sixth rotating element and the transmission housing, the second brake is disposed between the seventh rotating element and the transmission housing, and the third brake is disposed between the fourth rotating element and the transmission housing.

The first and third clutches and the third brake are disposed between the first and second planetary gear sets, and the second clutch and the first and second brakes are disposed at the rear side of the second planetary gear set.

The automatic transmission for a vehicle according to the above configuration operates the first clutch and the third brake at the first forward speed, the first clutch and the second brake at the second forward speed, and the second clutch and the third brake at the third forward speed. Is activated, the third clutch and the third brake are operated at the fourth forward speed, the first clutch and the third clutch are operated at the fifth forward speed, the second clutch and the third clutch are operated at the sixth forward speed, The second clutch and the first brake are operated at the seventh speed, and the second clutch and the first brake are operated at the reverse shift stage, and the shift is performed.

As described above, the gear train of the present invention combines one simple planetary gear set and a two-simple type planetary gear set with three clutches, three brakes, and one one-way clutch to realize a forward 7 speed and a reverse 1 speed. This reduces the overall length of the transmission.

In addition, by shifting two friction elements in each shift stage, the shift is achieved, thereby reducing the capacity of the oil pump and increasing the hydraulic control efficiency.

In addition, by distributing the six friction elements, it is possible to easily form a flow path formed in the transmission housing, it is possible to reduce the cost by improving productivity.

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

 1 shows an embodiment of a gear train according to the present invention, wherein the gear train of the present invention includes first and second planetary gear sets PG1 and PG2 arranged on the same axis, and three clutches C1. A clutch means comprising (C2) and (C3), a brake means consisting of three brakes B1, B2 and B3, and one one-way clutch F are included.

Accordingly, the rotation input from the input shaft IS is shifted while passing through the first and second planetary gear sets PG1 and PG2, and output through the output gear OG, wherein the first planetary gear set PG1 is It is arranged on the engine side, and the second planetary gear set PG2 is disposed on the rear side of the first planetary gear set PG1.

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 is output through the output gear OG. The power drives the left and right drive wheels through known differentials.

As described above, the differential device is well known and does not correspond to the gist of the present invention, and a detailed description thereof will be omitted.

In the first planetary gear set PG1, the rotational power input to the input path IP is configured to decelerate the output through the intermediate output path MOP.

To this end, the first planetary gear set PG1 is a single-pinion planetary gear set, which includes a first rotating element made of the first sun gear S1, a second rotating element made of the first planetary carrier PC1, and a first ring. It comprises a third rotating element consisting of gear (R1).

The first sun gear S1, which is the first rotating element, is fixedly connected to the transmission housing H so that the first sun gear S1 can always operate as a fixed element, and the first planet carrier PC1, which is the second rotating element, is an output element. The intermediate output path MOP is formed, and the first ring gear R1, which is the third rotating element, is directly connected to the input shaft IS to form the input path IP.

Accordingly, in the first planetary gear set PG1, the first sun gear S1, which is the first rotating element, always operates as a fixed element in a state where an input is always made through the first ring gear R1, which is a third rotating element. As described above, only the deceleration output is made through the first planet carrier PC1 which is an output element.

The second planetary gear set PG2 is connected to the intermediate input path MIP variably connected to the intermediate output path MOP of the first planetary gear set PG1 and variably connected to the input shaft IS. The final output path OP is performed by shifting the rotational power input through the first variable input path VIP1 and the second variable input path VIP2 variably connected to the input shaft IS to 7 forward speeds and 1 reverse speed. Will be printed via

To this end, the second planetary gear set PG2 is a two-simple (TWO SIMPLE) type planetary gear set consisting of a combination of two single-pinion planetary gear sets, and the second ring gear R2 and the third planet carrier PC3. ) Is directly connected, and the second planet carrier (PC2) and the third ring gear (R3) is directly connected to have four rotating elements.

Accordingly, the second planetary gear set PG2 may include a fourth rotating element including the second sun gear S2, a fifth rotating element including the second planetary carrier PC2 and the third ring gear R3, And a sixth rotating element including the second ring gear R2 and the third planet carrier PC3 and a seventh rotating element including the third sun gear S3.

The second sun gear S2, which is the fourth rotating element, is connected to the intermediate output path MOP via the first clutch C1 to form an intermediate input path MIP, and the seventh rotating element The third sun gear S3 is variably connected to the input shaft IS via the second clutch C2 to form the first variable input path VIP1, and the second ring gear R2 and the sixth rotating element R3 and the third rotation gear S3 are formed. The three planet carriers PC3 are variably connected to the input shaft IS via the third clutch C3 to form the second variable input path VIP2, and the input is performed through three input paths.

That is, the second planetary gear set PG2 has one intermediate input path decelerated by the first planetary gear set PG1 and two variable input paths which are variably connected to the input shaft IS and directly input. Will be.

In addition, the second ring gear R2 and the third planet carrier PC2, which are the sixth rotation element, are variably connected to the transmission housing H via the first brake B1, and the seventh rotation element is the seventh rotation element. The third sun gear S3 is variably connected to the transmission housing H via the second brake B2, and the one-way clutch F and the second sun gear S2, which are fourth operating elements, are connected in series. 3 is variably connected to the transmission housing (H) via the brake (B3) to operate as an optional fixing element.

In addition, the fifth planetary carrier PC2 and the third ring gear R3, which are the fifth rotating element, are connected to the output gear OG to form a final output path OP, and thus always operate as an output element.

By the above combination, the first and third clutches C1 and C3, the third brake B3 and the one-way clutch F are disposed between the first and second planetary gear sets PG1 and PG2. The first and second brakes B1 and B2 and the second clutch C2 are disposed at the rear side of the second planetary gear set PG2.

If the friction elements are arranged as described above, it is possible to easily form a flow path for supplying the working pressure to these friction elements, and in particular, the first and third clutches C1 and C3 are disposed close to each other. The arrangement can be optimized and cam-packed to enable a complex clutch structure.

And by placing the one-way clutch F1 between the third brake (B3) and the second sun gear (S2), even if the precise control of the third brake (B3) is not carried out, the one-way clutch (F1) accommodates it for a sense of shift It will be possible to improve.

However, although the third brake B3 may be omitted by the arrangement of the one-way clutch F, when the third brake B3 is omitted, the second sun gear S2 may be operated as a fixed element during shifting. However, since the operation of the engine brake is not performed during inertial operation, the third brake B3 is necessarily required.

Further, as described above, the friction elements applied to the combination of the first and second planetary gear sets PG1 and PG2, that is, the first, second and third clutches C1, C2, C3 and the first, second, The three brakes B1, B2 and B3 are typically made of a multi-plate hydraulic friction engagement unit that is frictionally coupled by hydraulic pressure.

Figure 2 is an operating table showing the friction member, that is, the clutch and the brake to be applied to each shift stage applied to the present invention, the gear train of the present invention is shifted while the two friction members are operated at each shift stage. Able to know.

That is, the first clutch C1 and the first brake B1 operate at the first forward speed, the first clutch C1 and the second brake B2 operate at the second forward speed, and the second clutch C2 at the third forward speed. ) And the third brake B3 including the one-way clutch F are operated, and at the fourth forward speed, the third brake B3 including the third clutch C3 and the one-way clutch F is operated. The first and third clutches C1 and C3 are operated at the fifth forward speed, and the second and third clutches C2 and C3 are operated at the sixth forward speed, and the third clutch C3 and the second brake are operated at the seventh forward speed. As B2) is activated, forward shifting is achieved.

In the reverse shift stage, the second clutch C2 and the first brake B1 operate.

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. .

On the lever of the first planetary gear set PG1, three operating nodes N1, N2, and N3 are set, and the first operating node N1 is the first sun gear S1 and the second operating node N2. ) Is set to the first planet carrier PC1 and the third operating node N3 to the first ring gear R1.

The distance between the operation nodes is determined according to the gear ratio of the first planetary gear set PG1 (the number of teeth of the sun gear / the number of rings of the ring gear).

Four operating nodes N4, N5, N6, and N7 are set on the lever of the second planetary gear set PG2, and the fourth operating node N4 includes the second sun gear S2 and the fifth. The operation node N5 is the second planetary carrier PC2 and the third ring gear R3, and the sixth operation node N6 is the second ring gear R2 and the third planet carrier PC3, the seventh operation node N7 is set to the third sun gear S3.

The distance between the operating nodes is determined according to the gear ratio of the second planetary gear set PG2 (number of teeth of the sun gear / number of rings of the ring gear). Detailed description thereof will be omitted.

[1st speed forward]

In the forward 1 speed, the transmission control unit (not shown) as shown in FIG. 2 operates and controls the first clutch C1 and the first brake B1.

Then, as shown in FIG. 3, in the first planetary gear set PG1, the first sun gear that is the first operating node N1 in the state where an input is made to the first ring gear R1 that is the third operating node N3. When S1) is operated as a fixed element, the deceleration output is made through the first planet carrier PC1, which is the second operation node N2, which is an output element.

As described above, when the output is made through the intermediate output path MOP through the first planet carrier PC1 which is the second operation node N2 of the first planetary gear set PG1, the second planetary gear set PG2 may be used. In the first clutch C1, the input is made to the second sun gear S2 which is the fourth operating node N4 through the intermediate input path MIP.

As described above, the second ring gear R2 and the third planet carrier PC3, which are the sixth operating node N6 and the third planet carrier PC3, operate as the fixing element by the operation of the first brake B1. Bar, as much as D1 is output through the fifth operating node (N5) as an output element while forming a first shifting line (SP1) connecting the fourth operating node (N4) and the sixth operating node (N6) In other words, the first speed shift is to be made.

In other words, the rotational power decelerated through the intermediate output path MOP of the first planetary gear set PG1 is received through the intermediate input path MIP of the second planetary gear set PG2, and then decelerated again to output the final output. By outputting to the path OP, the shift in the forward 1 speed is achieved.

[2 speed forward]

When the vehicle speed increases in the state of the first forward speed as described above, the transmission control unit releases the operation of the first brake B1 and controls the second brake B2 in the control state of the first forward speed.

Then, the rotational power output through the intermediate output path (MOP) of the first planetary gear set (PG1) is input to the second sun gear (S2) that is the fourth operating node (N4) through the intermediate input path (MIP), In operation, the third sun gear S3, which is the seventh operating node N7, is operated as a fixed element by the operation of the second brake B2.

Accordingly, as much as D2 is output through the fifth operation node N5 which is an output element while forming the second shift line SP2 connecting the fourth operation node N4 and the seventh operation node N7. In other words, the shifting speed of 2nd forward is achieved.

That is, in the second forward speed, the rotational power which is decelerated and output through the intermediate output path MOP of the first planetary gear set PG1, as in the first forward speed, is converted into the intermediate input path MIP of the second planetary gear set PG2. Received through) and decelerated again to output to the final output path (OP), by changing the fixed element, by reducing the deceleration ratio rather than the forward 1 speed, the shift of the 2 forward speed is made.

[3 speed forward]

If the vehicle speed increases in the state of the second forward speed as described above, the transmission control unit releases the operation of the first clutch C1 and the second brake B2 in the control state of the second forward speed, and the second clutch C2 and Operation control of the third brake B3 is performed.

Then, when the rotational power of the input shaft IS is directly input to the third sun gear S3 which is the seventh operating node N7 through the first variable input path VIP1 by the operation of the second clutch C2. 3, the second sun gear S2, which is the fourth operating node N4, is operated as a fixed element by the operation of the brake B3.

Accordingly, as much as D3 is output through the fifth operating node N5 which is an output element while forming the third shifting line SP3 connecting the fourth operating node N4 and the seventh operating node N7. In other words, three speed shifts will be made.

That is, at the third forward speed, the first planetary gear set PG1 is not involved in the shift, and decelerates the rotational power of the input shaft IS input from the second planetary gear set PG2 through the first variable input path VIP1. By outputting the output, the third speed shift is achieved.

[4 forward speed]

When the vehicle speed increases in the state of the third forward speed as described above, the transmission control unit releases the operation of the second clutch C2 in the control state of the third forward speed, and operates the third clutch C3.

Then, as the third clutch C3 operates, the rotational power of the input shaft IS is directly connected to the second ring gear R2 and the third planet carrier, which are the sixth operating node N6, directly through the second variable input path VIP2. The second sun gear S2, which is the fourth operating node N4, is operated as a fixed element by the operation of the third brake B3 while being input to the PC3).

Accordingly, as much as D4 is output through the fifth operating node N5 which is an output element while forming the fourth shifting line SP4 connecting the fourth operating node N4 and the sixth operating node N6. In other words, the 4th forward speed will be achieved.

That is, at the fourth forward speed, the first planetary gear set PG1 is not involved in the shift, and decelerates the rotational power of the input shaft IS input from the second planetary gear set PG2 through the second variable input path VIP2. By outputting it, a shift in the fourth forward speed is achieved.

[5th forward]

When the vehicle speed increases in the state of the fourth forward speed as described above, the transmission control unit releases the operation of the third brake B3 and controls the first clutch C1 in the control state of the fourth forward speed.

Then, as in the fourth forward speed, the second ring gear R2 of which the rotational power of the input shaft IS is the sixth operating node N6 is directly transmitted through the second variable input path VIP2 by the operation of the third clutch C3. ) And the rotational power output through the intermediate output path (MOP) of the first planetary gear set (PG1) in the state of being input to the third planet carrier (PC3) is the second planetary gear set through the intermediate input path (MIP) An input is made to the second sun gear S2 which is the fourth operation node N4 of PG2.

Accordingly, as much as D5 is output through the fifth operating node N5 which is an output element while forming a fifth shift line SP5 connecting the fourth operating node N4 and the sixth operating node N6. 5 forward speed will be achieved.

That is, in the fifth forward speed, power is transmitted from the second planetary gear set PG2 through the intermediate input path MIP and the second variable input path VIP2, and thus the fifth forward speed is made by the complementary operation.

[6th forward]

When the vehicle speed increases in the state of the fifth forward speed, the transmission control unit releases the operation of the first clutch C1 and operates the second clutch C2 in the control state of the fifth forward speed.

Then, as in the fourth forward speed, the second ring gear R2 of which the rotational power of the input shaft IS is the sixth operating node N6 is directly transmitted through the second variable input path VIP2 by the operation of the third clutch C3. ) And the rotational power of the input shaft IS through the first variable input path VIP1 by the operation of the second clutch C2 in the state of being input to the third planet carrier PC3. An input is made to the third sun gear S3 which is the seventh operation node N7.

When the same rotational power is simultaneously input to the sixth and seventh operating nodes N6 and N6 as described above, the second planetary gear set PG2 is in a direct connection to form a sixth shift line SP6 and an output element. Through the fifth operating node (N5) is the output as much as the input D6 is made to the sixth speed shift is made.

That is, in the sixth forward speed, the rotational power of the input shaft IS is input through the first and second variable input paths VIP1 and VIP2 and is output as it is, thereby shifting the sixth forward speed.

[7th forward]

When the vehicle speed increases in the state of the sixth forward speed, the transmission control unit releases the operation of the second clutch C2 in the control state of the sixth forward speed and operates the second brake B2.

Then, as the third clutch C3 operates, the rotational power of the input shaft IS is directly connected to the second ring gear R2 and the third planet carrier, which are the sixth operating node N6, directly through the second variable input path VIP2. The third sun gear S3, which is the seventh operating node N7, is operated as a fixed element by the operation of the second brake B2 while being input to the PC3).

Accordingly, as much as D7 is output through the fifth operation node N5 which is an output element while forming the seventh shift line SP7 connecting the sixth operation node N6 and the seventh operation node N7. In other words, the seventh forward speed will be achieved.

That is, at the seventh forward speed, the first planetary gear set PG1 is not involved in shifting, and the rotational force of the input shaft IS input from the second planetary gear set PG2 through the second variable input path VIP2 is increased. By outputting it, a shift of 7 forward speeds is achieved.

[apse]

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

Then, when the rotational power of the input shaft IS is directly input to the third sun gear S3 which is the seventh operating node N7 through the first variable input path VIP1 by the operation of the second clutch C2. The operation of the first brake B1 causes the second ring gear R2 and the third planet carrier PC3, which are the sixth operating node N6, to operate as the fixing element.

Accordingly, as the reverse shift line SR is connected to the sixth operating node N6 and the seventh operating node N7, the reverse rotational output is generated as much as RS through the fifth operating node N5 as an output element. By doing so, the reverse shift is made.

That is, in the reverse shift stage, the first planetary gear set PG1 is not involved in the shift, and the rotational force of the input shaft IS input from the second planetary gear set PG2 through the first variable input path VIP1. By reverse rotation deceleration output, reverse shift is made.

Although a preferred embodiment of the gear 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 the present invention 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 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;

Figure 4 is an embodiment of a conventional gear train.

5 is an operation table of a friction member applied to the gear train according to FIG.

Claims (18)

Simple planetary gear set with three rotating elements, A first rotating element which always acts as a stationary element, A second rotating element forming an intermediate output path through which deceleration is always performed; A first planetary gear set including a third rotating element connected directly to the input shaft to form an input path; 2-simple complex planetary gear set with four rotating elements, A fourth rotating element variably connected to the intermediate output path to form an intermediate input path and operating as an optional fixed element; A fifth rotating element connected to the output gear to form a final output path; A sixth rotating element that is variably connected to the input shaft to form a second variable input path and operates as an optional fixed element; Gear train of the automatic transmission for a vehicle, characterized in that the combination of the second planetary gear set including a seventh rotating element that is variably connected to the input shaft to form a first variable input path and act as an optional fixed element. The method of claim 1, wherein the first planetary gear set is a single pinion planetary gear set, wherein the first rotating element is a first sun gear, the second rotating element is a first planet carrier, and the third rotating element is a first ring gear. , The second planetary gear set is composed of a combination of two single pinion planetary gear sets, with the second planet carrier and the third ring gear directly connected, and the second ring gear and the third planet carrier directly connected, The fourth rotating element includes the second sun gear, the fifth rotating element includes the second planetary carrier and the third ring gear, the sixth rotating element includes the second ring gear and the third planetary carrier, and the seventh rotating element includes the third sun gear. Featuring a gear train of an automatic transmission for a vehicle. The method of claim 1 or 2, wherein the first and second planetary gear sets are combined with three clutches and three brakes, With the first rotary element directly connected to the transmission housing, the third rotary element directly connected to the input shaft, and the fifth rotary element connected to the output gear, A first clutch is disposed between the second rotary element and the fourth rotary element, A second clutch is disposed between the input shaft and the seventh rotating element, A third clutch is disposed between the input shaft and the sixth rotating element, The first brake is disposed between the sixth rotating element and the transmission housing, A second brake is disposed between the seventh rotating element and the transmission housing, The gear train of the vehicle transmission, characterized in that the third brake is disposed between the fourth rotating element and the transmission housing. 4. The gear train of claim 3, wherein a one-way clutch is disposed between the third brake and the fourth rotating element. The method of claim 3, wherein the first and third clutches and the third brake are disposed between the first and second planetary gear sets, and the second clutch and the first and second brakes are disposed at the rear side of the second planetary gear set. Gear train of automatic transmission The method of claim 3, wherein the first clutch and the third brake are operated at the first forward speed, At the second forward speed, the first clutch and the second brake are operated. At the 3rd forward speed, the second clutch and the third brake are activated, At the 4th forward speed, the third clutch and the third brake are operated. At the 5th forward speed, the first clutch and the third clutch are operated, At the sixth forward speed, the second clutch and the third clutch are operated. At seventh forward speed, the second clutch and the first brake are activated, The gear shifter of the automatic transmission for a vehicle, characterized in that the shift is performed in the reverse shift stage while the second clutch and the first brake are operated. The gear train of an automatic transmission for a vehicle according to claim 4 or 6, wherein the one-way clutch and the third brake are operated simultaneously at the forward three or four speeds. The sixth rotating element is operated as a fixed element according to claim 1, wherein the rotational power decelerated through the intermediate output path of the first planetary gear set is input through the intermediate input path of the second planetary gear set at forward 1 speed. The gear train of the automatic transmission for a vehicle, characterized in that the shift is made and output through the final output path. According to claim 1, At the second forward speed, the seventh rotating element is operated as a fixed element in a state in which the rotational power decelerated through the intermediate output path of the first planetary gear set is input through the intermediate input path of the second planetary gear set. The gear train of the automatic transmission for a vehicle, characterized in that the shift is made and output through the final output path. The gear train of the vehicle automatic transmission according to claim 1, wherein in the third forward speed, the fourth rotational element is operated as a fixed element while the fourth rotational element is input through the first variable input path and is output through the final output path. The gear train of claim 1, wherein the fourth rotational element is operated as a fixed element while the fourth rotational element is input through the second variable input path and is output through the final output path. According to claim 1, At 5 forward speed input through the second variable input path in the state that the rotational power is decelerated output through the intermediate output path of the first planetary gear set is input through the intermediate input path of the second planetary gear set. The gear train of the automatic transmission for a vehicle, characterized in that the shift is made and output through the final output path. The automatic transmission for a vehicle according to claim 1, wherein at the sixth forward speed, simultaneous input is performed through the first and second variable input paths, and the second planetary gear set is directly connected and output through the final output path as it is. Gear train. The vehicle automatic transmission according to claim 1, wherein the seventh forward speed is shifted while the seventh rotating element is operated as a fixed element in the state where the input is made through the second variable input path and is output through the final output path. Gear train. The vehicle automatic transmission of claim 1, wherein the reverse shift stage outputs the reverse rotation through the final output path while the sixth rotating element is operated while the reverse shift stage is being input through the first variable input path. Gear train. A single pinion planetary gear set, comprising: a first planetary gear set having a first rotating element as a first sun gear, a second rotating element as a first planet carrier, and a third rotating element as a first ring gear; Combination of two single pinion planetary gear sets, with the second planetary carrier and the third ring gear connected directly and the second ring gear and the third planet carrier directly connected, The sun gear, the fifth rotating element is the second planetary carrier and the third ring gear, the sixth rotating element is the second ring gear and the third planetary carrier, and the seventh rotating element is the third planetary gear set comprising the third sun gear. Two clutches and three brakes, Directly connecting the first rotating element to the transmission housing, directly connecting the third rotating element to the input shaft, and connecting the fifth rotating element to the output gear; The first clutch is disposed between the second rotary element and the fourth rotary element, the second clutch is disposed between the input shaft and the seventh rotary element, the third clutch is disposed between the input shaft and the sixth rotary element, and the fourth The clutch is disposed between the input shaft and the fourth rotary element, the first brake is disposed between the sixth rotary element and the transmission housing, the second brake is disposed between the seventh rotary element and the transmission housing, and the third brake is 4 A gear train of a vehicle transmission, characterized in that it is arranged between the rotary element and the transmission housing. 17. The gear train of claim 16, wherein a one-way clutch is disposed between the third brake and the fourth rotating element. 17. The method of claim 16, wherein the first and third clutches and the third brake are disposed between the first and second planetary gear sets, and the second clutch and the first and second brakes are disposed behind the second planetary gear sets. Gear train of automatic transmission

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