KR100907075B1 - Gear train of car automatic transmission - Google Patents

Abstract

The present invention combines four planetary gear sets with three clutches and two brakes to realize a shift stage of eight forward speeds or more, and minimizes frictional elements to simplify the configuration of the automatic transmission and improve power transmission performance by multiple stages. To provide a gear train of an automatic transmission for a vehicle to reduce fuel consumption and fuel economy.

Description

GEAR TRAIN OF AUTOMATIC TRANSMISSION FOR VEHICLES}

The present invention relates to a gear train of an automatic transmission for a vehicle in which four planetary gear sets are combined with three clutches and two brakes to achieve a shift speed of eight forward or more forward speeds.

In general, a multistage shifting mechanism of an automatic transmission disposed between an engine and a driving wheel of a vehicle such as an automobile is implemented by combining a plurality of planetary gear sets, and a gear train in which the plurality of planetary gear sets are combined rotates from a torque converter. It receives the power and shifts it to the output shaft.

In such automatic transmissions, the more transmission stages that can be implemented, the more appropriate the transmission ratio can be designed and the vehicle can be realized in terms of power performance and fuel efficiency. Therefore, there is a demand for an automatic transmission that implements more transmission stages.

And even if the same shift stage is implemented, the durability, power transmission efficiency, size, etc. of the gear train are changed according to the combination method of the planetary gear set, so that a more robust, no power loss, and more compact gear train configuration can be invented. Efforts are ongoing.

In particular, unlike the manual transmission, in which the shifting step is more inconvenient for the driver to shift more frequently, the automatic transmission is shifted by the transmission control unit controlling the operation of the gear train in accordance with the driving state. Efforts are being made to find a configuration of gear trains that can implement a stage.

From this point of view, four-speed and five-speed automatic transmissions are the mainstream automatic transmissions currently in use, but recently, six-speed automatic transmissions have been developed and applied to vehicles, while the development of automatic transmissions of eight or more speeds is active. It's going on.

Accordingly, the present inventors have proposed the present invention in order to meet the development of the automatic transmission as described above, and the object of the present invention is a combination of four planetary gear sets with three clutches and two brakes for eight forward speeds. By implementing the above shift stage, it is to provide a gear train of an automatic transmission for a vehicle that can improve power transmission performance and reduce fuel consumption.

In order to achieve the above object, the present invention provides a first planetary gear set PG1 comprising a single pinion planetary gear set having a first sun gear S1, a first planet carrier PC1, and a first ring gear R1. )Wow;

A second planetary gear set PG2 composed of a double pinion planetary gearset having a second sun gear S2, a second planet carrier PC2, and a second ring gear R2;

A third planetary gear set PG3 consisting of a double pinion planetary gearset having a third sun gear S3, a third planet carrier PC3, and a third ring gear R3;

A fourth planetary gear set PG4 comprising a single pinion planetary gear set having a fourth sun gear S4, a fourth planet carrier PC4, and a fourth ring gear R4 includes a first, second and third clutch C1. (C2) (C3) and the first and second brakes (B1) (B2) by applying a combination,

The input shaft IS into which the engine's rotational power is input is the second ring gear R2, the second sun gear S2 is the first sun gear S1, and the first planet carrier PC1 is the fourth ring gear R4. ), The second planet carrier PC2 is directly connected to the third sun gear S3, and the fourth sun gear S4 is directly connected to the third planet carrier PC3,

The second ring gear R2 is the fourth sun gear S4, the first planet carrier PC1 and the fourth ring gear R4 are the third ring gear R3, the second planet carrier PC2 and the first The three sun gear S3 is variably connected to the fourth sun gear S4,

The first sun gear S1 and the first ring gear R1 are connected to the transmission housing H, respectively.

A fourth planetary carrier PC4 provides a gear train of an automatic transmission for a vehicle, which is connected to an output shaft OS.

The input shaft IS and the second ring gear R2 are connected to the first power transmission member TS1, and the second sun gear S1 and the first sun gear S1 are the second power transmission member TS2. The first planet carrier PC1 and the fourth ring gear R4 are connected to the third power transmission member TS3, and the second planet carrier PC2 and the third sun gear S3 are the fourth power. Connecting to the transmission member TS4, and the fourth sun gear S4 and the third planet carrier PC3 are connected to the fifth power transmission member TS5;

The second ring gear R2 and the fourth sun gear S4 are connected to the first variable power transmission member VTS1 including the first clutch C1, and the first planet carrier PC1 and the fourth ring gear ( The third power transmission member TS3 and the third ring gear R3 connecting R4 are connected to the second variable power transmission member VTS2 including the second clutch C2 and the second planet carrier PC2. ) And the fourth power transmission member TS4 connecting the third sun gear S3 to the third power variable transmission member VTS3 including the third clutch C3;

The first sun gear S1 is variably connected to the transmission housing H via the first brake B1, and the first ring gear R2 is variable to the transmission housing H via the second brake B2. It is characterized by a connection box.

The first and fourth planetary gear sets PG1 and PG4 may be formed of a single pinion planetary gear set, and the second and third planetary gear sets PG2 and PG3 may be formed of a double pinion planetary gear set. The 1,2,3,4 planetary gear sets PG1, PG2, PG3 and PG4 are arranged on the same axis, but the first, second, third and fourth planetary gear sets PG1 and PG2 are from the engine side. (PG3) and (PG4) in this order.

Further, the first and second brakes B1 and B2 are disposed on the front side of the first planetary gear set PG1, and the first and third clutch C1 are disposed between the second and third planetary gear sets PG2 and PG3. C3 is disposed, and the second clutch C2 is disposed on the outer circumferential side of the third planetary gear set PG3.

As described above, four planetary gear sets PG1 to PG4 are combined with three clutches C1, C2 and C3 as friction members and two brakes B1 and B2 to shift eight forward speeds and one reverse speed. By implementing a stage, it is possible to improve power transmission performance and fuel economy.

In addition, by distributing the plurality of friction members, the configuration of the flow path can be facilitated.

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

 1 shows a gear train according to the present invention, wherein the gear train according to the present invention includes first, second, third and fourth planetary gear sets PG1, PG2, PG3, and PG4 arranged on the same axis. And a clutch means composed of three clutches C1 (C2) and C3, and a brake means composed of two brakes B1 and B2.

The first, second, third and fourth planetary gear sets PG1, PG2, PG3, and PG4 are sequentially arranged on the same axis from the engine side to shift the rotational power of the engine transmitted from the input shaft IS. Output to the output shaft (OS).

The input shaft IS refers to the turbine shaft of the torque converter as an input member, which is input while the rotational power from the engine crankshaft is converted into torque through the torque converter, and is not shown through the output shaft OS as the output member. One known differential is used to drive the drive wheels.

Wherein the first, second, third, fourth planetary gear sets (PG1 ~ PG4) is composed of a simple planetary gear set, the first planetary gear set (PG1) is a single pinion planetary gear set, the first sun gear (S1) And a first planetary carrier PC1 supporting a pinion external to the first sun gear S1 and a first ring gear R1 in which the pinion is inscribed.

The second planetary gear set PG2 is a double pinion planetary gear set, and includes a second sun gear S2, a second planet carrier PC2 supporting a double pinion circumscribed to the second sun gear S2, and It holds three actuating elements consisting of a second ring gear R2 in which the pinion is inscribed.

The third planetary gear set PG3 is a double pinion planetary gear set, and includes a third sun gear S3, a third planet carrier PC3 for supporting a double pinion circumscribed to the third sun gear S3, and It has three actuating elements consisting of a third ring gear R3 in which the pinion is inscribed.

The fourth planetary gear set PG4 is a single pinion planetary gear set, and includes a fourth sun gear S4, a fourth planet carrier PC4 supporting the pinion circumscribed to the fourth sun gear S4, and the pinion. It holds three actuating elements of the fourth ring gear R4 which is inscribed.

In connecting the operation elements of the first, second, third, and fourth simple planetary gear sets PG1, PG2, PG3, and PG4 to each other, directly connected by five power transmission members TS1 to TS5. And, it is to be variably connected by using the variable power transmission member (VTS1 ~ VTS3) including three clutch (C1) (C2) (C3).

In more detail, the first power transmission member TS1 connects the input shaft IS and the second ring gear R2, and the second power transmission member TS2 connects the first sun gear S1 and the second sun gear. (S2), the third power transmission member TS3 connects the first planetary carrier PC1 and the fourth ring gear R4, and the fourth power transmission member TS4 is the second planetary carrier. PC2 and the third sun gear S3 are connected, and the fifth power transmission member TS5 connects the third planet carrier PC3 and the third ring gear R3.

The first variable power transmission member VTS1 including the first clutch C1 variably connects the second ring gear R2 and the fourth sun gear S4, and includes a second clutch C2. The second variable power transmission member VTS2 variably connects the third power transmission member TS3 and the third ring gear R3, and includes a third variable power transmission member VTS3 including a third clutch C3. ) Variably connects the fourth power transmission member TS4 and the fourth sun gear S4.

In addition, the first brake B1 selectively connects the second power transmission member TS2 connecting the first sun gear S1 and the second sun gear S2 with the transmission housing H to selectively transmit the power transmission member. The second brake B2 selectively connects the first ring gear R1 to the transmission housing H to selectively rotate the first ring gear R1. Placed to stop.

In the above, the friction member composed of the first, second and third clutches C1, C2 and C3 and the first and second brakes B1 and B2 is composed of a multi-plate hydraulic friction engagement unit friction-coupled by hydraulic pressure. It is connected to the hydraulic control device is shifted while being activated and deactivated by the control of the transmission control unit (not shown) according to the operating conditions.

In the arrangement of the friction member as described above, the first and second brakes B1 and B2 are disposed in front of the first planetary gear set PG1, and the first and third clutches C1 and C3 are made of 2 is disposed between the planetary gear set (PG2) and the third planetary gear set (PG3), the second clutch (C2) is disposed on the outer peripheral side of the third planetary gear set (PG3).

By distributing the friction members as described above, the hydraulic flow paths supplied to these friction members are easily formed, and the weight distribution is uniform, so that the overall weight balance of the automatic transmission is improved.

Figure 2 is an operation 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 mark of ● indicates the operation of the friction member, the gear train of the present invention 3 It can be seen that the two friction members operate while shifting is made.

That is, the first clutch C1 and the first and second brakes B1 and B2 operate at the first forward speed,

At the second forward speed, the third clutch C3 and the first and second brakes B1 and B2 operate.

The first and third clutches C1 and C3 and the second brake B2 operate at the third forward speed,

At the fourth forward speed, the second and third clutches C2 and C3 and the second brake B2 operate.

The first and second clutches C1 and C2 and the second brake B2 operate at five forward speeds,

The first, second and third clutches C1, C2 and C3 operate at 6 forward speeds,

The first and second clutches C1 and C2 and the first brake B1 are operated at seven forward speeds,

At the 8th forward speed, the second and third clutches C2 and C3 and the first brake B1 operate.

In reverse, the second clutch C2 and the first and second brakes B1 and B2 are operated to shift.

3 to 11 are views showing the shift process of the gear train according to the present invention, wherein the lower horizontal line represents the rotational speed "0", the upper horizontal line represents the rotational speed "1.0", that is, the input shaft (IS) and It shows the same rotation speed.

The three vertical lines of the first planetary gear set PG1 are set from the first rotating element N1 to the third rotating element N3 in order from the left, and the first rotating element N1 is the first sun gear S1. The second rotary element N2 is set to the first planetary carrier PC1 and the third rotary element N3 is set to the first ring gear R1, and the spacing is each gear ratio of the first planetary gear set PG1. (Number of teeth of sun gear / number of rings).

The three vertical lines of the second planetary gear set PG2 are set from the fourth rotating element N4 to the sixth rotating element N6 in order from the left, and the fourth rotating element N4 is the second sun gear S2. The fifth rotating element N5 is set to the second ring gear R2, and the sixth rotating element N6 is set to the second planetary carrier PC2, and the spacing is each gear ratio of the second planetary gear set PG2. (Number of teeth of sun gear / number of rings).

Three vertical lines of the third planetary gear set PG3 are set from the seventh rotating element N7 to the ninth rotating element N9 in order from the left, and the seventh rotating element N7 is the third sun gear S3. The eighth rotary element N8 is set to the fourth ring gear R3, and the ninth rotary element N9 is set to the third planet carrier PC3, and the spacing is each gear ratio of the third planetary gear set PG4. (Number of teeth of sun gear / number of rings).

Three vertical lines of the fourth planetary gear set PG3 are set from the tenth rotation element N10 to the twelfth rotation element N12 in order from the left, and the tenth rotation element N10 is the fourth sun gear S4. ), The eleventh rotating element N11 is set to the fourth planetary carrier PC4, and the twelfth rotating element N12 is set to the fourth ring gear R4, and the spacing is set at each of the fourth planetary gear sets PG3. It depends on the gear ratio (number of teeth of sun gear / number of rings).

Since the positioning of each rotating element in the above-described shift diagram is well known to those skilled in the art of a gear train, a detailed description thereof will be omitted.

[1st speed forward]

At the first forward speed, as shown in FIG. 2, the first clutch C1 and the first and second brakes B1 and B2 are operated and controlled.

Then, as shown in FIG. 3, the first planetary gear set PG1 is operated by the operation of the first and second brakes B1 and B2 while the input is made to the second ring gear R2, which is the fifth rotating element N5. While the whole is fixed, the second sun gear S2, the fourth rotating element N4, which is directly connected to the first sun gear S1, which is its first rotating element N1, is operated as a fixed element.

Accordingly, the speed increase output is performed through the second planetary carrier PC2, which is the sixth rotation element N6, wherein the rotational power of the input shaft IS is controlled by the operation of the first clutch C1 to the ninth rotation element N9. ) Is transmitted to the third planet carrier PC3 and the fourth sun gear S4 that is the tenth rotating element N10.

In this state, the fourth ring gear R4, which is the twelfth rotating element N12, operates as a fixed element due to the overall fixing of the first planetary gear set PG1. The first transmission line SP1 connecting the twelfth rotation element N12 to the output as much as D1 through the eleventh rotation element N11, which is an output member, and thus the maximum speed ratio (rotational speed of the input member). / Rotation speed of the output member), the forward 1 speed shift of about "4.500" is made.

[2 speed forward]

In the second forward speed, as shown in FIG. 2, the operation of the first clutch C1 operating in the state of the first forward speed is released, and the third clutch C3 is operated and controlled.

Then, as shown in FIG. 4, the first planetary gear set PG1 is fixed as in the first speed, and the first clutch C1 is input to the second ring gear R2 which is the fifth rotating element N5. ), Only the speed increase power of the second planetary carrier PC2, which is the sixth rotating element N6, is transmitted to the seventh rotating element N7.

In this state, the driving force of the second planet carrier PC2, which is the sixth rotation element N4, is transmitted to the fourth sun gear S4, which is the tenth operation element N10, by the operation of the third clutch C3. The fourth ring gear R4, which is the twelfth rotating element N12, operates as a fixed element due to the overall fixing of the first planetary gear set PG1. The output speed of D2 is made through the eleventh rotating element N11 which is an output member while forming the second shifting line SP2 connecting the 12 rotating elements N12, so that the speed ratio is smaller than the forward 1 speed. This is a two-speed forward.

[3 speed forward]

At the third forward speed, as shown in FIG. 2, the operation of the first brake B1 operated in the state of the second forward speed is released, and the first clutch C1 is operated and controlled.

Then, as shown in FIG. 5, while the first and third clutches C1 and C3 are operated, the second planetary gear set PG2 is directly connected and the third planetary gear set is operated by the operation of the third clutch C3. PG3 is in a direct connection state.

Accordingly, the rotational power of the second sun gear S2, which is the fourth rotating element N4, is transmitted to the first sun gear S1, which is the first rotating element N1, wherein the third brake is operated by the second brake B2. When the first ring gear R1, which is the operating element N3, operates as a fixed element, the deceleration output is made through the first planet carrier PC1, which is the second rotating element N2.

In the state where the deceleration power of the second rotating element N2 is input to the fourth ring gear R4 which is the twelfth rotating element N12, the fourth sun gear which is the tenth rotating element N1 as described above. The direct input of the second planetary gear set PG2 is made to S4), and outputs while forming a third transmission line SP3 connecting the tenth rotating element N10 and the twelfth rotating element N12. The output is as much as D3 through the eleventh rotating element N11, which is a member, so that the forward three-speed shift of about 2.077, which is smaller than the second forward speed, is achieved.

[4 forward speed]

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

Then, as shown in FIG. 6, when the third planet carrier PC3, which is the ninth rotation element N9, and the fourth sun gear S4, which is the tenth rotation element N10, are connected to the operation of the second clutch C2. The third ring gear R3, which is the eighth rotation element N8, and the fourth ring gear R4, which is the twelfth rotation element N12, are connected to each other, so that the third and fourth planetary gear sets PG3 and PG4 are It becomes a state of direct connection.

In this state, an input is made to the fifth rotating element N5, and the first ring gear R1, which is the third rotating element N3, operates as a fixed element by operating the second brake B2. In the complementary operation, the second sun gear S2, which is the fourth rotating element N4, and the first sun gear S1, which is the first rotating element N1, are accelerated to increase the first planet carrier PC1, which is the second rotating element N2. Decelerating output is achieved through

In addition, while the rotational power of the second rotating element N2 is transmitted to the fourth planetary gear set PG4 which is in a direct connection state, a fourth transmission line SP4 is formed to correspond to D4 through the eleventh rotating element N11. The output is made such that the forward speed of about 4 speeds of about 1.667, which is smaller than the forward speed of 3 times, is achieved.

[5th forward]

In the fifth forward speed, as shown in FIG. 3, the operation of the third clutch C3 operated in the state of the fourth forward speed is released, and the first clutch C1 is operated and controlled.

Then, as shown in FIG. 7, the first ring gear R3, which is the third rotating element N3, is operated as the fixed element by the operation of the second brake B2 while the input is made to the fifth rotating element N5. The second sun gear S2, which is the fourth rotating element N4, and the first sun gear S1, which is the first rotating element N1, are accelerated by the complementary operation. 1 Deceleration output is made via planet carrier PC1.

In this state, the rotational power input to the fifth rotating element N5 is the fourth sun gear S4 that is the tenth rotating element N10 and the third ninth rotating element N9 by the operation of the first clutch C1. It is transmitted to the planet carrier (PC3), the deceleration power of the first planet carrier (PC1) of the second rotating element (N2) is transmitted to the fourth ring gear (R4) of the twelfth rotating element (N12), As the fifth shift line SP5 connecting the tenth rotating element N10 and the twelfth rotating element N12 is output as much as D5 through the eleventh rotating element N11, the forward 5th speed is achieved. The gearbox has 5 forward speeds of about 1.249 and a smaller speed ratio.

[6th forward]

At the sixth forward speed, as shown in FIG. 2, the operation of the second brake B2 operated in the fifth forward speed is released, and the third clutch C3 is operated and controlled.

Then, as shown in FIG. 8, all three clutches C1, C2, and C3 operate, and the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 are directly connected to each other. The sixth transmission line SP6 is formed in the fourth planetary gear set PG4 and the output ratio is equal to D6 as it is through the eleventh rotation element N11 as an output member, and thus the transmission ratio is greater than the fifth forward speed. 6 forward speeds of about 1.000 will be achieved.

[7th forward]

In the seventh forward speed, as shown in FIG. 2, the operation of the third clutch C3 operated in the sixth forward speed is released, and the first brake B1 is controlled to operate.

Then, as shown in FIG. 9, when the first rotary element N1 and the fourth rotary element N4 operate as the fixed element by the operation of the first brake B1, the input is input to the fifth rotary element N5. As a result, the speed increase output is made through the sixth rotation element N6 as a complementary action, and the rotational power thereof is transmitted to the third sun gear S3, which is the seventh rotation element N7.

In addition, the rotational power of the input shaft IS is input to the ninth rotating element N9 and the tenth rotating element N10 by the operation of the first clutch C1, wherein the eighth rotating element N8 is the seventh rotating element. It is in the state of increasing speed by the smaller input of N7 and the ninth rotating element N9.

In this state, the second clutch C2 is operated, and the rotational power of the eighth rotating element N8 is transmitted to the twelfth rotating element N12 and the second rotating element N2. The seventh shift line SP7 connecting the element N10 and the twelfth rotating element N12 is output as much as D7 through the eleventh rotation element N11 as an output member, so that the speed ratio is higher than the sixth forward speed. A small 7-speed forward of about 0.861 will be achieved.

[8th forward]

At 8th forward speed, as shown in FIG. 2, the operation of the first clutch C1 operating in the 7th forward speed is released, and the third clutch C3 is operated and controlled.

Then, as shown in FIG. 10, the third and fourth planetary gear sets PG3 and PG4 are directly connected by the operation of the second and third clutches C2 and C3, and in this state, the fifth rotating element N5. The first rotation element (N1) and the fourth rotation element (N4) to operate as a fixed element is made by the input of the first brake (B1), the sixth rotation element (N6) by the complementary action As the speed increase output is performed, the rotational power is transmitted to the third sun gear S3, which is the seventh rotation element N7, and the fourth sun gear S4, which is the tenth rotation element N10.

Accordingly, while the eighth shift line SP8 is formed in the direct connection state, the output is output as much as D8 through the eleventh rotation element N11, which is an output member, as the speed increasing input is maintained. The eighth speed shift is achieved.

[apse]

In the reverse shift stage, as shown in FIG. 2, the second clutch C2 and the first and second brakes B1 and B2 are operated and controlled.

Then, as shown in FIG. 11, the first planetary gear set PG1 is operated by operating the first and second brakes B1 and B2 in a state where an input is made to the second ring gear R2, which is the fifth rotating element N5. While the whole is fixed, the second sun gear S2, the fourth rotating element N4, which is directly connected to the first sun gear S1, which is its first rotating element N1, is operated as a fixed element.

Accordingly, the speed increase output is performed through the second ring gear R2, which is the sixth rotation element N6, and the rotational power thereof is input to the seventh rotation element N7, wherein the first planetary gear set PG2 is used. By the fixing of the third ring gear (R3) of the eighth rotating element (N8) and the fourth ring gear (R4) of the twelfth rotating element (N12) to operate as a fixed element, the ninth rotating element ( N9) and the tenth rotating element N10 rotate backwards to form a reverse shift line SR, and a reverse shift ratio is generated through the eleventh rotating element N11 which is an output member as much as RS. 4.200 inches of reverse shift will be 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 at forward 1 speed.

4 is a shift diagram at forward two speeds.

5 is a shift diagram at the third forward speed.

6 is a shift diagram at the fourth forward speed.

7 is a shift diagram at the fifth forward speed.

8 is a shift diagram at sixth forward speed.

9 is a shift diagram at the seventh forward speed.

10 is a shift diagram at eight forward speeds.

11 is a reverse shift diagram.

Claims (4)

A first planetary gear set PG1 composed of a single pinion planetary gear set having a first sun gear S1, a first planet carrier PC1, and a first ring gear R1; A second planetary gear set PG2 composed of a double pinion planetary gearset having a second sun gear S2, a second planet carrier PC2, and a second ring gear R2; A third planetary gear set PG3 consisting of a double pinion planetary gearset having a third sun gear S3, a third planet carrier PC3, and a third ring gear R3; A fourth planetary gear set PG4 comprising a single pinion planetary gear set having a fourth sun gear S4, a fourth planet carrier PC4, and a fourth ring gear R4 includes a first, second and third clutch C1. (C2) (C3) and the first and second brakes (B1) (B2) by applying a combination, The input shaft IS into which the engine's rotational power is input is the second ring gear R2, the second sun gear S2 is the first sun gear S1, and the first planet carrier PC1 is the fourth ring gear R4. ), The second planet carrier PC2 is connected to the third sun gear S3, and the fourth sun gear S4 is connected to the third planet carrier PC3, The second ring gear R2 is the fourth sun gear S4, the first planet carrier PC1 and the fourth ring gear R4 are the third ring gear R3, the second planet carrier PC2 and the first 3 sun gear (S3) is connected to the fourth sun gear (S4), The first sun gear S1 and the first ring gear R1 are connected to the transmission housing H, respectively. Gear train of the automatic transmission for a vehicle, characterized in that the fourth planet carrier (PC4) is connected to the output shaft (OS). The method of claim 1, wherein the input shaft (IS) and the second ring gear (R2) is connected to the first power transmission member TS1, the second sun gear (S2) and the first sun gear (S1) is a second power transmission member. The first planet carrier PC1 and the fourth ring gear R4 are connected by a third power transmission member TS3, and the second planet carrier PC2 and the third sun gear S3 are connected by a TS2. A fourth power transmission member TS4 and a fourth sun gear S4 and a third planet carrier PC3 are connected to a fifth power transmission member TS5; The second ring gear R2 and the fourth sun gear S4 are connected to the first variable power transmission member VTS1 including the first clutch C1, and the first planet carrier PC1 and the fourth ring gear ( The third power transmission member TS3 and the third ring gear R3 connecting R4 are connected to the second variable power transmission member VTS2 including the second clutch C2 and the second planet carrier PC2. ) And the fourth power transmission member TS4 connecting the third sun gear S3 to the third power variable transmission member VTS3 including the third clutch C3; The first sun gear S1 is variably connected to the transmission housing H via the first brake B1, and the first ring gear R2 is variable to the transmission housing H via the second brake B2. Gear train of an automatic transmission for a vehicle characterized by a connection box. 3. The first and second brakes B1 and B2 are disposed on the front side of the first planetary gear set PG1, and the first and third clutches C1 and C3 are second and third planetary gears. The gear train of the automatic transmission for a vehicle, characterized in that disposed between the set (PG2) (PG3), the second clutch (C2) is located on the outer peripheral side of the third planetary gear set (PG3). The first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 are arranged on the same axis, and the first, second, third, and fourth planetary gears from the engine side. Gear train of an automatic transmission for a vehicle, characterized in that arranged in the set (PG1) (PG2) (PG3) (PG4).

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