KR101327087B1 - 8-speed power train of automatic transmission - Google Patents

Abstract

The present invention relates to a power train of an automatic transmission, and more particularly, to an eight speed power train of an automatic transmission that implements a forward eight speed reverse one speed.
To this end, the present invention is a first rotating element (N1) that is variably connected to the input shaft 10, the output shaft 20, the transmission power is drawn out, the transmission housing 30, the rotational power is drawn to operate as an optional fixed element And a second rotating element N2 connected to another rotating element as an idle element to perform related operation, and a third rotating element N3 variably connected to the transmission housing 30 to operate as an optional fixing element. A first planetary gear set PG1 including a fourth rotation element N4 connected to the first rotation element N1, a fifth rotation element N5 connected to the input shaft 10, and an idle element. A second planetary gear set PG2 including a sixth rotating element N6 connected to another rotating element to perform an associated operation, and a seventh rotating element N7 selectively connected to the sixth rotating element N6; And an eighth rotating element N8 selectively connected to the fifth rotating element N5 and an idle element. A third planetary gear set PG3 including a ninth rotating element N9 connected to other rotating elements to perform an associated operation, and a tenth rotating element N10 connected to the seventh rotating element N7; And a fourth planetary gear set PG4 including an eleventh rotating element N11 connected to the ninth rotating element N9 and a twelfth rotating element N12 connected to the output shaft 20. 8 speed power train of automatic transmission is provided.

Description

8-speed power train of automatic transmission {8-SPEED POWER TRAIN OF AUTOMATIC TRANSMISSION}

The present invention relates to a power train of an automatic transmission, and more particularly, to an eight speed power train of an automatic transmission that implements a forward eight speed reverse one speed.

In general, a multi-stage shifting mechanism of an automatic transmission is implemented by combining a plurality of planetary gear sets, and a power train in which the plurality of planetary gear sets is combined receives torque from a torque converter included in the automatic transmission and shifts it to the output shaft. It will serve to deliver.

However, the more transmission stages that can be implemented in transmission, the more appropriate transmission ratio can be designed, and the vehicle can be realized in terms of power performance and fuel efficiency. Therefore, an automatic transmission that implements more transmission stages is of interest for continuous research. have.

In addition, even if the same number of gear stages are implemented, the durability, power transmission efficiency, size, etc. of the powertrain are changed according to the combination method of the planetary gear set, thereby inventing a more robust, no power loss, and a compact powertrain configuration. Efforts are always underway.

In particular, unlike a manual transmission in which the driver has to shift frequently when there are too many shift stages, the automatic transmission performs transmission by controlling the operation of the power train by the transmission control unit according to the driving condition. Efforts have been made to find a configuration of a powertrain that can implement many shift stages.

From this point of view, the four-speed and five-speed automatic transmissions are the mainstream automatic transmissions currently used, but recently, six-speed automatic transmissions have been developed and applied to vehicles, while improving power transmission performance and fuel economy. The development of an automatic transmission of 8 speeds or more that can reduce the speed is required.

Therefore, the present invention was created to solve the above problems, and an object of the present invention is to provide an eight-speed power train of an automatic transmission that implements eight forward and one reverse speed.

The eight-speed power train of the automatic transmission according to an embodiment of the present invention for achieving this object is variable input and the output shaft, the output shaft, the rotational power is drawn out the rotational power is selected to operate as an optional fixing element variablely connected to the transmission housing. A first planetary gear comprising a first rotating element, a second rotating element connected to another rotating element as an idler element to perform an associated operation, and a third rotating element variably connected to the transmission housing to operate as an optional fixed element. A second planetary gear comprising a set, a fourth rotating element connected to the first rotating element, a fifth rotating element connected to the input shaft, and a sixth rotating element connected to another rotating element as an idle element to perform an associated operation. A set, a seventh rotating element selectively connected with the sixth rotating element, an eighth rotating element selectively connected with the fifth rotating element, A third planetary gear set including a ninth rotating element connected to another rotating element as an idle element and performing related operations, a tenth rotating element connected to the seventh rotating element, and an eleventh connected to the ninth rotating element And a fourth planetary gear set including a rotating element and a twelfth rotating element connected to the output shaft.

In addition, the pair of the sixth rotary element and the seventh rotation element is variably connected to the pair of the eighth rotation element variably connected to the fifth rotation element is characterized in that the.

In addition, it characterized in that it comprises a first brake for selectively restraining the first rotating element with respect to the transmission case.

And a second brake for selectively restraining the third rotating element with respect to the transmission case.

In addition, it characterized in that it comprises a first clutch for selectively connecting the sixth rotation element and the seventh rotation element.

In addition, it characterized in that it comprises a third clutch for selectively connecting the fifth rotary element and the eighth rotary element.

In addition, the pair of the sixth rotary element and the seventh rotation element is variable, characterized in that it comprises a second clutch for selectively connected to the pair of the eighth rotation element variably connected to the fifth rotation element.

The first, second, third and fourth planetary gearsets may be arranged coaxially, and the first, second, third and fourth planetary gearsets may be arranged in order from the engine side.

The first, second, third and fourth planetary gearsets may be arranged coaxially, and the second, first, fourth and third planetary gearsets may be arranged in order from the engine side.

The first, second, third and fourth planetary gear sets may be disposed coaxially and arranged in order of the third, fourth, second and first planetary gear sets from the engine side.

The first, second, third and fourth planetary gear sets may be disposed coaxially and arranged in the order of the third, fourth, first and second planetary gear sets from the engine side.

In addition, the first rotating element is a first sun gear, the second rotating element is interlocked with a first planet carrier, the third rotating element is a first ring gear, and the fourth rotating element is a second sun gear, The fifth rotating element is interlocked with the second planetary carrier, the sixth rotating element is the second ring gear, the seventh rotating element is the third sun gear, and the eighth rotating element is interlocked with the third planetary carrier. The ninth rotating element is a third ring gear, the tenth rotating element is a fourth sun gear, the eleventh rotating element is interlocked with a fourth planet carrier, and the twelfth rotating element is a fourth ring gear. It features.

As described above, according to the eight-speed power train of the automatic transmission according to the present invention, by using four planetary gear sets, three clutches and two brakes to implement the transmission speed of the 8 forward speed and 1 reverse speed to improve the power transmission performance. It has the effect of improving and improving fuel economy.

1 is a configuration diagram of an eight-speed power train of an automatic transmission according to a first embodiment of the present invention.
2 is a friction element operation table for operating an eight-speed power train of an automatic transmission according to a first embodiment of the present invention.
3 is a lever analysis diagram showing a relationship between a speed ratio between eight forward speeds and one reverse speed implemented by an eight-speed power train of an automatic transmission according to a first embodiment of the present invention.
4 is a configuration diagram of an eight-speed power train of an automatic transmission according to a second embodiment of the present invention.
5 is a configuration diagram of an eight-speed power train of an automatic transmission according to a third embodiment of the present invention.
6 is a configuration diagram of an eight-speed power train of an automatic transmission according to a fourth embodiment of the present invention.

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

1 is a configuration diagram of an eight-speed power train of an automatic transmission according to a first embodiment of the present invention. As shown in FIG. 1, the eight-speed power train of the automatic transmission according to the first embodiment of the present invention includes a first planetary gear set disposed on an input shaft 10, an output shaft 20, a transmission case 30, and a coaxial shaft. PG1, second planetary gear set PG2, third planetary gear set PG3, fourth planetary gear set PG4, first clutch CL1, second clutch CL2, third clutch CL3 ), A first brake B1 and a second brake BK2.

Here, the first planetary gear set PG1, the second planetary gear set PG2, the third planetary gear set PG3 and the fourth planetary gear set PG4 are first, second, fourth, and third from the engine side. Planetary gear sets (PG1, PG2, PG4, PG3) are arranged on the coaxial in order to shift the rotational power of the engine transmitted from the input shaft 10 to output to the output shaft 20.

The input shaft 10 refers to a 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 via the output shaft 20 as an output member. One known differential is used to drive the drive wheels.

The first, second, third and fourth planetary gear sets PG1, PG2, PG3 and PG4 are simple planetary gear sets. The first planetary gear set PG1 is a single pinion planetary gear set, and includes a first rotation. An element N1, a second rotating element N2 and a third rotating element N3. Here, the first rotating element N1, the second rotating element N2, and the third rotating element N3 are the first sun gear S1, the first planet carrier PC2, and the first ring gear R1, respectively. It may be made of.

That is, the first planetary gear set PG1 may include the first sun gear S1, a first planet carrier PC1 supporting the second rotation element N2 circumscribed to the first sun gear S1, and It includes three rotating elements consisting of a first ring gear (R1) in which the second rotating element (N2) is inscribed. In this case, the first sun gear S1 is variably connected to the transmission housing 30 by the first brake BK1 to operate as an optional fixing element, and the first planet carrier PC1 is another rotation as an idle element. Related operation is made in connection with the element, and the first ring gear R1 is variably connected with the transmission housing 30 by a second brake BK2 to operate as an optional fixing element.

The second planetary gear set PG2 is a single pinion planetary gear set, and includes a fourth rotating element N4, a fifth rotating element N5, and a sixth rotating element N6. Here, the fourth rotating element N4, the fifth rotating element N5, and the sixth rotating element N6 are respectively the second sun gear S2, the second planet carrier PC2, and the second ring gear R2. It may be made of.

That is, the second planetary gear set PG2 may include the second sun gear S2, a second planet carrier PC2 supporting the fifth rotating element N5 circumscribed to the second sun gear S2, and It includes three rotating elements consisting of a second ring gear (R2) in which the fifth rotating element (N5) is inscribed. In this case, the second sun gear S2 is connected to the first sun gear S1, the second planet carrier PC2 is connected to the input shaft 10, and the second ring gear R2 is an idle element. Related operations are made in connection with other rotating elements.

The third planetary gear set PG3 is a double pinion planetary gear set, and includes a seventh rotating element N7, an eighth rotating element N8, and a ninth rotating element N9. Here, the seventh rotation element N7, the eighth rotation element N8, and the ninth rotation element N9 are the third sun gear S3, the third planet carrier PC3, and the third ring gear R3, respectively. It may be made of.

That is, the third planetary gear set PG3 may include the third sun gear S3, the third planet carrier PC3 supporting the eighth rotating element N8 circumscribed to the third sun gear S3, It consists of three rotating elements which consist of the 3rd ring gear R3 in which the 8th rotating element N8 is inscribed. In this case, the third sun gear S3 is selectively connected to the second ring gear R2, and the third planet carrier PC3 is selectively connected to the second planet carrier PC2, and the third The ring gear R3 is an idle element and is connected with other rotating elements to perform related operations. In addition, the second planetary carrier PC2 and the third pair of the second ring gear R2 and the third sun gear S3 variably connected by the first clutch CL1 are variably connected by the third clutch CL3. The second clutch CL2 may be provided to be selectively connected to the planet carrier PC3.

The fourth planetary gear set PG4 is a single pinion planetary gear set, and includes a tenth rotating element N10, an eleventh rotating element N11, and a twelfth rotating element N12. Here, the tenth rotating element N10, the eleventh rotating element N11, and the twelfth rotating element N12 are respectively a fourth sun gear S4, a fourth planet carrier PC4, and a fourth ring gear R4. It may be made of.

That is, the fourth planetary gear set PG4 may include the fourth sun gear S4, the fourth planet carrier PC4 supporting the eleventh rotating element N11 circumscribed to the fourth sun gear S4, The eleventh rotating element N11 includes three rotating elements formed of a fourth ring gear R4 inscribed therein. In this case, the fourth sun gear S4 is connected to the third sun gear S3, the fourth planet carrier PC4 is connected to the third ring gear R3, and the fourth ring gear R4. Is connected to the output element (20).

2 is a friction element operation table for operating an eight-speed power train of an automatic transmission according to a first embodiment of the present invention. Referring to Figure 2, it can be seen that the friction member, that is, the clutch and the brake applied to the eight-speed power train of the automatic transmission according to the first embodiment of the present invention operates in each gear stage.

That is, the third clutch CL3, the first brake BK1 and the second brake BK2 operate at the first forward speed.

At the second forward speed, the second clutch CL2, the first brake BK1 and the second brake BK2 are operated.

The second clutch CL2, the third clutch CL3 and the second brake BK2 operate at the third forward speed,

The first clutch CL1, the second clutch CL2 and the second brake BK2 operate at the fourth forward speed,

The first clutch CL1, the third clutch CL3 and the second brake BK2 operate at five forward speeds,

The first clutch CL1, the second clutch CL2 and the third clutch CL3 operate at six forward speeds,

The first clutch CL1, the third clutch CL3 and the first brake BK1 operate at seven forward speeds,

The first clutch CL1, the second clutch CL2 and the first brake BK1 operate at eight forward speeds,

In reverse, the first clutch CL1, the first brake BK1, and the second brake BK2 are operated to shift.

3 is a lever analysis diagram showing a relationship between a speed ratio between eight forward speeds and one reverse speed implemented by an eight-speed power train of an automatic transmission according to a first embodiment of the present invention. Referring to Figure 3, it can be seen visually the shifting process of the eight-speed power train of the automatic transmission according to an embodiment of the present invention. Here, the vertical line is set from the first rotating element N1 to the twelfth rotating element N12, which is directly connected to each other among the rotating elements of the first, second, third and fourth planetary gear sets PG1, PG2, PG3, and PG4. It is determined by the gear ratio of each rotating element (number of teeth of sun gear / number of teeth of ring gear).

In the above-described shift diagram, the position setting of each rotating element is well known to those skilled in the art of the power train, and thus detailed description thereof will be omitted.

[1st speed forward]

In the forward 1 speed, as shown in FIG. 2, the 3rd clutch CL3, the 1st brake BK1, and the 2nd brake BK2 are operationally controlled.

That is, as shown in FIG. 3, the first brake is input in a state where an input is made to the second planet carrier PC2 of the fifth rotating element N5 and the third planet carrier PC3 of the eighth rotating element N8. By the operation of BK1 and the second brake BK2, the first sun gear S1, the second sun gear S2, and the first ring gear R1, which are the first rotating element N1, operate as the fixed element. Accordingly, the first planetary gear set PG1 is integrally rotated so that the fourth planet carrier PC4 and the third ring gear R3, which are the eleventh rotating element N11, are integrally rotated to realize rotational speed of 1 forward speed. do.

[2 speed forward]

At the 2nd forward speed, as shown in FIG. 2, the 2nd clutch CL2, the 1st brake BK1, and the 2nd brake BK2 are operationally controlled.

That is, as shown in FIG. 3, the first sun gear S2 and the third rotation element (1) which are the first rotation element N1 in the state where an input is made to the second planet carrier PC2 of the fifth rotation element N5. Since the first ring gear R1 of N3) and the second sun gear S2 of the fourth rotating element N4 operate as fixed elements, the first planetary gear set PG1 is rotated integrally to output the rotational power and the first. The rotational power of the 2nd forward speed formed by the 3rd planetary carrier PC3 which is 8 rotation elements N8 is implemented.

[3 speed forward]

At 3rd forward speed, as shown in FIG. 2, the 2nd clutch CL2, the 3rd clutch CL3, and the 2nd brake BK2 are operationally controlled.

That is, as shown in FIG. 3, the first ring gear R1, which is the third rotating element N3, is fixed by the operation of the second clutch CL2, the third clutch CL3, and the second brake BK2. And the second planet carrier PC2 of the fifth rotating element N5, the second ring gear R2 that is the sixth rotating element N6, and the third planet carrier PC3 of the eighth rotating element N8. ) Acts as an input element, and rotational power of the third forward speed is realized through the fourth ring gear R4 which is the twelfth rotating element N12.

[4 forward speed]

At 4th forward speed, as shown in FIG. 2, the 1st clutch CL1, the 2nd clutch CL2, and the 2nd brake BK2 are operationally controlled.

That is, as shown in FIG. 3, the first ring gear R1, which is the third rotating element N3, is fixed by the operation of the first clutch CL1, the second clutch CL2, and the second brake BK2. , The second planetary carrier PC2 of the fifth rotating element N5 operates as an input element, and the third sun gear S3 and the eighth rotating element N8 that are the seventh rotating element N7. Since the third planet carrier PC3 is integrally rotated, the third planetary gear set PG3 is integrally rotated, and rotational power of the fourth forward speed is realized through the fourth ring gear R4 which is the twelfth rotating element N12.

[5th forward]

At the 5th forward speed, as shown in FIG. 2, the first clutch CL1, the third clutch CL3, and the second brake BK2 are operated and controlled.

That is, as shown in FIG. 3, the first ring gear R1, which is the third rotating element N3, is fixed by the operation of the first clutch CL1, the third clutch CL3, and the second brake BK2. The second planetary carrier PC2 of the fifth rotating element N5 and the second ring gear R2 which is the sixth rotating element N6 are integrally rotated and the seventh rotating element N7 As the third planet carrier PC3 of the third sun gear S3 and the eighth rotating element N8 is integrally rotated, rotational force of five forward speeds is realized through the fourth ring gear R4 that is the twelfth rotating element N12. do.

[6th forward]

At 6th forward speed, as shown in FIG. 2, the 1st clutch CL1, the 2nd clutch CL2, and the 3rd clutch CL3 are operationally controlled.

That is, as shown in FIG. 3, the second ring gear R2 and the seventh rotating element N6 are operated by the first clutch CL1, the second clutch CL2, and the third clutch CL3. The third sun gear S3, which is the rotational element N7, and the third planet carrier PC3 of the eighth rotational element N8, are directly connected to the input shaft 10 to rotate at the same speed, thereby making it the 12th rotational element N12. Four forward speed rotational power is realized through the four ring gear (R4).

[7th forward]

At 7th forward speed, as shown in FIG. 2, the 1st clutch CL1, the 3rd clutch CL3, and the 1st brake BK1 are operationally controlled.

That is, as shown in FIG. 3, the first sun gear S1 and the fourth sun gear S1 and the fourth rotating element N1 are operated by the first clutch CL1, the third clutch CL3, and the first brake BK1. The second sun gear S2, which is the rotating element N4, operates as a fixed element, and the second planetary carrier PC2 of the fifth rotating element N5 and the third planetary carrier PC3 of the eighth rotating element N8 are provided. Is connected to the input shaft 10 to operate as an input element, the twelfth rotation by connecting the second ring gear (R2) that is the sixth rotation element (N6) and the third sun gear (S3) that is the seventh rotation element (N7) directly A rotational power of seven forward speeds is realized through the fourth ring gear R4 which is the element N12.

[8th forward]

At 8th forward speed, as shown in FIG. 2, the first clutch CL1, the second clutch CL2, and the first brake BK1 are operated and controlled.

That is, as shown in FIG. 3, the first sun gear S1 and the fourth rotation, which are the first rotating element N1, are operated by the first clutch CL1, the second clutch CL2, and the first brake BK1. The second sun gear S2, which is the element N4, operates as a fixed element, and the rotational power of the input shaft 10 is input to the fifth rotating element N5, and the second ring gear, which is the sixth rotating element N6, R4), the third sun gear S3 as the seventh rotation element N7 and the third planet carrier PC3 of the eighth rotation element N8 are directly connected to each other to form the fourth ring gear R4 as the twelfth rotation element N12. The rotational power of 8 forward speed is realized through

[apse]

In the reverse shift stage, as shown in FIG. 2, the first clutch CL2, the first brake BK1, and the second brake BK2 are operated and controlled.

That is, as shown in FIG. 3, the first sun gear S1 and the third rotation, which are the first rotating element N1, are operated by the first clutch CL2, the first brake BK1, and the second brake BK2. The first ring gear R1, which is the element N3, and the second sun gear S2, which is the fourth rotating element N4, operate as a stationary element, and the second planetary carrier PC2 of the fifth rotating element N5. The rotational force of the input shaft 10 is input, and the fourth planetary gear set (4) is formed by directly connecting the second ring gear R2 that is the sixth rotation element N6 and the third sun gear S3 that is the seventh rotation element N7. The reverse shift is realized through the fourth ring gear R4, which is the twelfth rotating element N12 of PG4.

4 is a block diagram of an eight-speed power train of an automatic transmission according to a second embodiment of the present invention, Figure 5 is a block diagram of an eight-speed power train of an automatic transmission according to a third embodiment of the present invention, Figure 6 Is a configuration diagram of an eight-speed power train of an automatic transmission according to a fourth embodiment of the present invention. As shown in FIG. 4, the eight-speed power train of the automatic transmission according to the second exemplary embodiment of the present invention may arrange the first, second, third and fourth planetary gear sets PG1, PG2, PG3, and PG4 coaxially. The second, first, fourth and third planetary gear sets PG2, PG1, PG4 and PG3 are arranged in order from the engine side. In addition, as shown in FIG. 5, the eight-speed power train of the automatic transmission according to the third exemplary embodiment of the present invention coaxially sets the first, second, third and fourth planetary gear sets PG1, PG2, PG3, and PG4. Arrangement is performed in order of the third, fourth, second and first planetary gear sets PG3, PG4, PG2 and PG1 from the engine side. In addition, as shown in FIG. 6, the eight-speed power train of the automatic transmission according to the fourth embodiment of the present invention coaxially sets the first, second, third and fourth planetary gear sets PG1, PG2, PG3, and PG4. Arrangement is performed in order of the third, fourth, first and second planetary gear sets PG3, PG4, PG1 and PG2 from the engine side. That is, as described above, the eight-speed power train of the automatic transmission according to the second, third, and fourth embodiments of the present invention has a first, second, third, and fourth planetary gear set in comparison with the first embodiment of the present invention. The arrangements of the PG1, PG2, PG3, and PG4 are only different, and as shown in FIG. 2, the friction member operates and is made on the same principle as in FIG. 3 in the shifting process.

While the present invention has been described in connection with what is presently considered to be practical exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, And all changes to the scope that are deemed to be valid.

10: input shaft
20: output shaft
30: transmission case
PG1: 1st planetary gear set
PG2: 2nd planetary gear set
PG3: 3rd planetary gear set
PG4: Fourth planetary gear set
CL1: First clutch
CL2: second clutch
CL3: third clutch
BK1: first brake
BK2: second brake
S1: 1st sun gear
S2: 2nd sun gear
S3: 3rd sun gear
S4: fourth sun gear
R1: first ring gear
R2: second ring gear
R3: third ring gear
R4: fourth ring gear
PC1: first planet carrier
PC2: second planetary carrier
PC3: Third Planetary Carrier
PC4: fourth planetary carrier

Claims (13)

An input shaft 10 through which rotational power is input and an output shaft 20 through which rotational power is drawn;
A first rotating element N1 variably connected to the transmission housing 30 to operate as an optional fixed element, a second rotating element N2 connected to another rotating element as an idle element to perform related operations, and the transmission A first planetary gear set PG1 variably connected to the housing 30 and including a third rotating element N3 operating as an optional fixing element;
A fourth rotating element N4 connected to the first rotating element N1, a fifth rotating element N5 connected to the input shaft 10, and a rotating element connected to another rotating element as an idle element to perform an associated operation A second planetary gear set PG2 including a six rotating element N6;
A seventh rotating element N7 selectively connected with the sixth rotating element N6, an eighth rotating element N8 selectively connected with the fifth rotating element N5, and another rotating element as an idle element A third planetary gear set PG3 including a ninth rotating element N9 connected to and configured to perform an associated operation; And
A tenth rotation element N10 connected to the seventh rotation element N7, an eleventh rotation element N11 connected to the ninth rotation element N9, and a twelfth rotation connected to the output shaft 20. A fourth planetary gear set PG4 comprising an element N12;
An eight-speed power train of an automatic transmission comprising a. The method of claim 1,
The pair of variably connected to the sixth rotating element (N6) and the seventh rotating element (N7) is selectively connected to a pair of eighth rotating element (N8) variably connected to the fifth rotating element (N5). 8-speed powertrain with automatic transmission. The method of claim 1,
And a first brake (BK1) for selectively restraining the first rotating element (N1) with respect to the transmission case (30). The method of claim 1,
And a second brake (BK2) for selectively restraining said third rotating element (N3) with respect to said transmission case (30). The method of claim 1,
And a first clutch (CL1) for selectively connecting the sixth rotating element (N6) and the seventh rotating element (N7). The method of claim 1,
And a third clutch (CL3) for selectively connecting the fifth rotating element (N5) and the eighth rotating element (N8). The method of claim 1,
A second clutch for selectively connecting a pair of the sixth rotating element N6 and a seventh rotating element N7 to a pair of eighth rotating elements N8 that are variably connected to the fifth rotating element N5. An eight-speed power train of an automatic transmission, characterized by including (CL2). The method of claim 7, wherein
The first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 are coaxially disposed, and the first, second, fourth, and third planetary gear sets PG1, PG2, PG4, and PG3 are located from the engine side. 8-speed powertrain of the automatic transmission, characterized in that arranged in order. The method of claim 1,
The first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 are coaxially arranged, and the second, first, fourth, and third planetary gear sets PG2, PG1, PG4, and PG3 are disposed from the engine side. 8-speed powertrain of the automatic transmission, characterized in that arranged in order. The method of claim 1,
The first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 are coaxially arranged, and the third, fourth, second, and first planetary gear sets PG3, PG4, PG2, and PG1 are disposed from the engine side. 8-speed powertrain of the automatic transmission, characterized in that arranged in order. The method of claim 1,
The first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 are coaxially arranged, and the third, fourth, first, and second planetary gear sets PG3, PG4, PG1, and PG2 are disposed from the engine side. 8-speed powertrain of the automatic transmission, characterized in that arranged in order. The method of claim 1,
The first rotating element N1 is a first sun gear S1, the second rotating element N2 is interlocked with a first planet carrier PG1, and the third rotating element N3 is a first ring gear. (R1), the fourth rotating element (N4) is the second sun gear (S2), the fifth rotating element (N5) is interlocked with the second planetary carrier (PG2), the sixth rotating element (N6) Is a second ring gear (R2), the seventh rotation element (N7) is a third sun gear (S3), the eighth rotation element (N8) is interlocked with the third planet carrier (PC3), the ninth The rotating element N9 is a third ring gear R3, the tenth rotating element N10 is a fourth sun gear S4, and the eleventh rotating element N11 is interlocked with a fourth planetary carrier PC4. The twelfth rotating element (N12) is an eight-speed power train of the automatic transmission, characterized in that the fourth ring gear (R4). The method of claim 12,
The third planet carrier is an eight-speed power train of an automatic transmission, characterized in that the double pinion structure consisting of two pinions.

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