KR101063500B1 - Gear train of automatic transmission for vehicles - Google Patents

Abstract

The present invention reduces the overall length of the automatic transmission by disposing three simple planetary gear sets on two shafts and combining four clutches and two brakes to realize a shift stage of at least eight forward speeds and one reverse speed. It is possible to increase the mountability, and to use the extra length to increase the durability of the gear and the friction member, and by applying two transfer gears, the gear ratio configuration can be advantageously applied to improve the transmission performance and operability.

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 three simple planetary gear sets are disposed on two shafts and combined with four clutches and two brakes to realize a shift stage of at least eight forward speeds and one reverse speed. .

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

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

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

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

From this point of view, the four-speed and five-speed automatic transmissions are the mainstream automatic transmissions currently used, but the six-speed automatic transmission has been put into practical use in recent years, and a gear train capable of realizing more transmission stages. Development is taking place.

Accordingly, the present inventors have proposed the present invention in order to meet the development of the automatic transmission as described above, and an object of the present invention is to separate three simple planetary gear sets on two shafts, four clutches and two brakes. By providing a gear stage of at least eight forward speeds and one reverse speed, the gear train of the automatic transmission for a vehicle can be reduced to increase the mountability by reducing the overall length of the automatic transmission.

In order to realize the above object, the present invention provides the first and second planetary gear sets PG1 and PG2 disposed on the first axis 2 and the second arranged in parallel with the first axis 2. A third planetary gear set PG3 disposed on the shaft 4 and connected to the first and second planetary gear sets PG1 and PG2 through first and second transfer gears TF1 and TF2; It comprises a friction member consisting of two clutches (C1) (C2) (C3) (C4) and two brakes (B1) (B2),

The first planetary gear set PG1 is connected to an input shaft IS and a first rotating element N1 which always operates as a fixed element, a second rotating element N2 which always produces a deceleration output, and operates as an input element at all times. At the same time the third rotary element (N3) for outputting as it is made,

The second planetary gear set PG2 is connected to the second rotating element N2 and is always connected to the fourth rotating element N4, which operates as an input element, and selectively connected to the input shaft IS, and the transmission housing H. It is made to include a fifth rotating element (N5) that is variably connected to and acts as an input and a fixed element and at the same time acts as an output element, and a sixth rotating element (N6) always acts as an output element,

The third planetary gear set PG2 is selectively connected to the second, third and sixth rotating elements N2, N3 and N6 and selectively connected to the transmission housing H to operate as an input and a fixed element. A seventh rotating element N7, an eighth rotating element N8 selectively connected to the fifth rotating element N5 to operate as an input element, and a ninth rotating element N9 acting as a final output element. It provides a gear train of an automatic transmission for a vehicle made.

The first planetary gear set PG1 is a double pinion planetary gear set, the second planetary gear set PG2 is a double pinion planetary gear set, and the third planetary gear set PG3 is composed of a single pinion planetary gear set. It is done.

The first rotating element N1 is the first sun gear S1, the second rotating element N2 is the first ring gear R2, and the third rotating element N3 is the first planet carrier PC1, The fourth rotating element N4 is the second sun gear S2, the fifth rotating element N5 is the second ring gear R2, and the sixth rotating element N6 is the second planet carrier PC2, the seventh rotating element. N7 denotes the third sun gear S3, the eighth rotary element N8 includes the third planet carrier PC3, and the ninth rotary element N9 includes the third ring gear R3.

The friction member may include a first clutch C1 disposed between the second planet carrier PC2 and the first transfer gear TF1; A third clutch C3 disposed between the first ring gear R1 and the first transfer gear TF1; A third clutch C3 disposed between the input shaft IS and the second ring gear R2; A fourth clutch C4 disposed between the first planet carrier PC1 and the first transfer gear TF1; A first brake B1 disposed between the second ring gear R2 and the transmission housing H; It characterized in that it comprises a second brake (B2) disposed between the first transfer gear (TF1) and the transmission housing (H).

The first brake (B1) is characterized in that it comprises a one-way clutch (F1) arranged in parallel.

In the friction member, the first clutch C1 and the one-way clutch F1 are operated at the first forward speed, the first clutch C1 and the second brake B2 are operated at the second forward speed, and the third forward speed is performed. First and second clutches C1 and C2 are operated, and first and fourth clutches C1 and C4 are operated at four forward speeds, and first and third clutches C1 and C3 are operated at five forward speeds. Is activated, the third and fourth clutches C3 and C4 are operated at the sixth forward speed, and the second and third clutches C2 and C3 are operated at the seventh forward speed, and the third clutch ( C3) and the second brake (B2) is operated, the second clutch (C2) and the first brake (B1) is operated in the reverse speed 1 is characterized in that the shift is made.

As described above, the present invention separates three simple planetary gear sets on two shafts and combines four clutches and two brakes to realize a shift stage of at least eight forward speeds and one reverse speed. It is possible to increase the mountability by reducing the overall length.

In addition, since the mountability is advantageous, the spare electric field can be used for increasing the durability of the gear and the friction member, and by applying two transfer gears, the gear ratio configuration can be advantageously applied to the transmission performance and the driving performance.

These drawings are for reference in describing exemplary embodiments of the present invention and the technical spirit of the present invention should not be construed as being limited to the accompanying drawings.
1 is a block diagram of a gear train according to the present invention.
Figure 2 is an operation table for each shift stage of the friction member applied to the present invention.
3 is a shift diagram of a gear train according to the present invention.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings so that those skilled in the art may easily implement the present invention. The present invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein.

In order to clearly describe the present invention, parts irrelevant to the description are omitted, and like reference numerals designate like elements throughout the specification.

In the following detailed description, the names of the components are divided into first, second, and the like in order to distinguish the names of the components in the same relationship, and the descriptions of the components are not necessarily limited to the order in the following description.

1 is a configuration diagram of a gear train according to the present invention, wherein the gear train according to the present invention includes first and second planetary gear sets PG1 and PG2 disposed on a first shaft 2 and the first shaft. Clutch means consisting of a third planetary gear set PG3 disposed on a second shaft 4 arranged in parallel with (2), four clutches C1, C2, C3 and C4, and Brake means comprising two brakes B1 and B2.

In the arrangement of the first and second planetary gear sets PG1 and PG2, the second planetary gear set PG2 is disposed toward the engine side, and the third planetary gear set PG3 is connected to the second planetary gear set PG4. Arranged collinearly.

Accordingly, the rotational power input from the input shaft IS is shifted while passing through the first and second planetary gear sets PG1 and PG2, and the third planetary gear set PG3 is provided through two transfer gears TF1 and TF2. ) Is shifted to 8 forward speed and 1 reverse speed and is output through output gear (OG).

The input shaft IS refers to the turbine shaft of the torque converter as an input member, which is input while the rotational power of the engine is converted into torque through the torque converter, and the output gear OG is a known differential device as the output member. The driving wheel is driven through.

The first planetary gear set PG1 is a double pinion planetary gear set, and has three rotating elements consisting of a sun gear, a planet carrier, and a ring gear, as is well known, and for convenience of description, the first gear is a first sun gear S1, a planetary planet. The carrier is referred to as a first planet carrier PC1 and the ring gear is referred to as a first ring gear R1.

The second planetary gear set PG2 is a double pinion planetary gear set, and has three rotating elements consisting of a sun gear, a planet carrier, and a ring gear, as is well known. For convenience of description, the second gear (S2), a planet The carrier is referred to as a second planet carrier PC2 and the ring gear is referred to as a second ring gear R2.

The third planetary gear set PG3 is a single-pinion planetary gear set, and has three rotating elements consisting of a sun gear, a planet carrier, and a ring gear, as is known, and for the sake of explanation, the sun gear is referred to as a third sun gear S3, a planetary planet. The carrier is referred to as a third planet carrier PC3 and the ring gear is referred to as a third ring gear R3.

In combining the first and second planetary gear sets PG1 and PG2, the first sun gear S1 is fixedly connected to the transmission housing H, and the first planet carrier PC1 is directly connected to the input shaft IS. Is connected.

Accordingly, the first sun gear S1 is fixedly connected to the transmission housing H to operate as a fixed element at all times, and the first planet carrier PC2 is connected to the input shaft IS to always operate as an input element. At the same time, the first transfer gear TF1 is variably connected to the first transfer gear TF1, and the first ring gear R1 is an output element that generates a deceleration output at all times and is directly connected to the second sun gear S2 and variably connected to the first transfer gear TF1. Connected with.

The second sun gear S2 is directly connected to the first ring gear R1 through the power transmission member TM to always operate as an input element, and the second planet carrier PC2 is connected to the first transfer gear TF1. Variablely connected to the transmission housing (H) to operate as an optional output element and a fixed element, the second ring gear (R2) is directly connected to the second transfer gear (TF2) to operate as an output element at the same time the input shaft It is variably connected to the IS and the transmission housing H to act as an optional input element and a stationary element.

Further, the plurality of friction members C1, C2, C3, C4, B1, and B2 applied to the present invention are all applied to combining the first and second planetary gear sets PG1 and PG2.

More specifically, the first clutch C1 is disposed between the second planet carrier PC2 and the first transfer gear TF1, and the second clutch C2 is the first ring gear R1 and the first transfer. The third clutch C3 is disposed between the gear TF1, the third clutch C3 is disposed between the input shaft IS and the second ring gear R2, and the fourth clutch C4 is the first planetary carrier PC1 and the first. It is arranged between the transfer gears TF1.

The first brake B1 is disposed between the second ring gear R2 and the transmission housing H, and the one-way clutch F1 is disposed in parallel, and the second brake B2 is the first transfer gear TF1. ) And the transmission housing (H).

As described above, the one-way clutch F1 is shifted up from one speed to two speed as in the known art, and is used to improve shifting feeling when shifted from two speed to one speed, and when there is no one-way clutch F1, The first clutch C1 will work instead.

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

That is, the first clutch C1 and the one-way clutch F1 are operated at the forward 1 speed,

At the second forward speed, the first clutch C1 and the second brake B2 are operated.

The first and second clutches C1 and C2 are operated at three forward speeds,

The first and fourth clutches C1 and C4 are operated at four forward speeds,

The first and third clutches C1 and C3 are operated at five forward speeds,

The third and fourth clutches C3 and C4 are operated at six forward speeds,

The second and third clutches C2 and C3 are operated at seven forward speeds,

At the 8th forward speed, the third clutch C3 and the second brake B2 are operated.

The shift is made while the second clutch C2 and the first brake B1 are operated at the first reverse speed.

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

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

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

The three vertical lines of the third planetary gear set PG3 are the third sun gear S3, which is the seventh rotation element, and the third planet carrier PC3, which is the eighth rotation element N8, and the ninth rotation element N9, in order from the left. ), And the spacing is determined according to the gear ratio of the third planetary gear set PG3 (number of teeth of the sun gear / number of teeth of the ring gear).

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.

And the meaning of "-" in Figure 3 indicates the direction opposite to the rotation direction of the engine, the idling gear in the middle of the connection between the first and second planetary gear set (PG1) (PG2) and the third planetary gear set (PG3) It is externally connected through the first and second transfer gears TF1 and TF2 without the idling gear, and thus the third planetary gear set PG3 rotates in the opposite direction, thereby giving "-".

Therefore, the rotation direction of the rotational power output through the output gear (OG) is to be converted as necessary to be transmitted to the differential device.

[1st speed forward]

First, the first planetary gear set PG1 is always input through the first planet carrier PC1 while the first sun gear S1 is always fixed to the transmission housing H. The first ring The deceleration output is always made through the gear R1.

In this state, at the first forward speed, the first clutch C1 and the one-way clutch F1 are operated and controlled as shown in FIG. 2.

Accordingly, in the second planetary gear set PG2, the second ring gear R2 is operated as a fixed element by the operation of the one-way clutch F1 while the input is made to the second sun gear S2. The reverse rotation output is made by -FM1 through the second planet carrier PC2.

Then, in the third planetary gear set PG3, the third planetary carrier PC2 is connected to the second ring gear R2 through the second transfer gear TF2 to act as a fixing element, and the third sun gear S3 is Since the forward rotation input FM1 is made by the operation of the first clutch C1 as much as -FM1, the first clutch C1 forms the first shift line SP1, and as much as D1 through the third ring gear R3 as an output element. As the output is made, the 1st forward speed is made.

[2 speed forward]

At the 2nd forward speed, the operation of the one-way clutch F1 is canceled in the state of 1st forward speed, and the 2nd brake B2 is operation-controlled.

Then, the second planetary carrier PC2 is operated as a fixing element by the operation of the second brake B2 while the input is made to the second sun gear S2 as in the first forward speed. The deceleration output is made as much as FM2 through the gear R2.

In the third planetary gear set PG3, the third sun gear S3 is connected to the second planet carrier PC2 through the first transfer gear TF1 and the first clutch C1 to act as a fixing element. Since the planetary carrier PC3 has a reverse rotational input (-FM2) as much as the FM2, the output of the D2 through the third ring gear R3, which is an output element, forms the second shift line SP2. As it is achieved, the second forward speed is achieved.

[3 speed forward]

In the third forward speed, as shown in FIG. 2, the operation of the second brake B2 is released in the state of the second forward speed, and the operation of the second clutch C2 is controlled.

Then, as in the second forward speed, the second planetary gear set PG2 is directly connected to the second planetary carrier PC2 while the second sun gear S2 is inputted without the fixed element. The second ring gear (R2) is increased by the number of revolutions of FM3, the second planetary carrier (PC2) is increased by FM4, the output is made.

In the third planetary gear set PG3, the third sun gear S3 is provided with a reverse rotation input (-FM3) as much as the FM3 through the first transfer gear TF1 and the first clutch C1, and the third planetary gear set PG3. Carrier PC3 has a reverse rotational input (-FM4) as much as FM4, and as much as D3 is output through third ring gear R3 as an output element while forming a third shift line SP3. Three forward speeds will be achieved.

[4 forward speed]

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

Then, as in the third forward speed, the second planetary gear set PG2 is input to the first planet carrier PC1 by the operation of the fourth clutch C4 while the second sun gear S2 is being input. As the rotational power of the input shaft IS is input to the second planet carrier PC2 as it is, the second ring gear R2 is increased in rotation speed by FM5, and the second planet carrier PC2 is increased in FM6 so that the output is made. do.

In the third planetary gear set PG3, the third sun gear S3 is provided with a reverse rotation input (-FM5) as much as the FM5 through the first transfer gear TF1 and the first clutch C1, and the third planetary gear set PG3. Carrier PC3 has a reverse rotation input (-FM6) as much as FM6, and as much as D4 is output through third ring gear R3 as an output element while forming a fourth shift line SP4. 4 forward speed will be achieved.

[5th forward]

In the fifth forward speed, as shown in FIG. 2, the operation of the fourth clutch C4 operated in the state of the fourth forward speed is released, and the third clutch C3 is operated and controlled.

Then, in the second planetary gear set PG2 as in the fourth forward speed, the rotational power of the input shaft IS is maintained as it is by the operation of the third clutch C3 while the input is made to the second sun gear S2. Input to the two ring gear (R2) is increased by FM7, the second planet carrier (PC2) is increased by FM8 is made to the output.

In the third planetary gear set PG3, the third sun gear S3 is provided with a reverse rotation input (-FM7) as much as the FM7 through the first transfer gear TF1 and the first clutch C1, and the third planetary gear set PG3. Carrier PC3 has a reverse rotational input (-FM8) as much as FM8, and as much as D5 is output through third ring gear R3 as an output element while forming a fifth shift line SP5. 5 forward speed is to be achieved.

[6th forward]

At the sixth forward speed, as shown in FIG. 2, the operation of the first clutch C1 operated in the state of the fifth forward speed is released, and the fourth clutch C4 is operated and controlled.

Then, the rotational power of the input shaft IS is input to the third planet carrier PC3 through the second transfer gear TF2 by the operation of the third clutch C3, 1 When the rotational power of the planet carrier PC1 is input to the third sun gear S3 through the first transfer gear TF1, the third planetary gear set PG3 is directly connected to the sixth transmission line SP6. ) And as much as D6 is output through the third ring gear (R3) as the output element is to be made six forward speed shift.

[7th forward]

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

Then, in the state where the rotational power of the input shaft IS is input to the third planet carrier PC3 through the second transfer gear TF2 by the operation of the third clutch C3 as in the forward sixth speed. The rotational power of the first ring gear R1 is input to the third sun gear S3 through the first transfer gear TF1 by the operation of the clutch C2. In the third planetary gear set PG3, As the shift line SP7 is formed, as much as D7 is output through the third ring gear R3 as the output element, the seventh forward speed is achieved.

[8th forward]

At the 8th forward speed, as shown in FIG. 2, the operation of the second clutch C2 operated in the 7th forward speed is released, and the second brake B2 is operated and controlled.

Then, as in the seventh speed, the rotational power of the input shaft IS is input to the third planet carrier PC3 through the second transfer gear TF2 by the operation of the third clutch C3. The third sun gear S3 is operated as a fixed element by the operation of the brake B2. In the third planetary gear set PG3, an eighth shift line SP8 is formed and a third ring gear as an output element. As R8) outputs as much as D8, eight forward speeds are 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, the rotational power of the first ring gear R1 is input to the third sun gear S3 through the first transfer gear TF1 by the operation of the second clutch C2. In operation, the third planet carrier PC3 is operated as a fixed element. In the third planet gear set PG3, the reverse planetary gear line PG3 forms a reverse shift line RS, and as much as REV through the third ring gear R3 as an output element. As the output is made, reverse shift is made.

Looking at the shifting process as described above, the first planetary gear set (PG1) is always decelerated and the same speed output, the second planetary gear set (PG2) is always input from the first planetary gear set (PG1). Receives rotational power and rotational power selectively input from the input shaft IS, shifts and outputs them in two paths, and the third planetary gear set PG3 is the first and second planetary gear sets PG1 and PG2. It receives the rotational power input through the two paths from the two paths and shifts the output to eight forward speeds and one reverse speed.

As described above, the preferred embodiments of the present invention have been described, but the present invention is not limited thereto, and various modifications and changes can be made within the scope of the claims and the detailed description of the invention and the accompanying drawings. Naturally, it is within the scope of the present invention.

PG1, PG2, PG3 ... 1st, 2nd, 3rd planetary gear set S1, S2, S3 ... 1st, 2nd, 3rd sun gear
PC1, PC2, PC3 ... First, 2,3 Planetary Carriers R1, R2, R3 ... First, 2,3 Ring Gears
IS ... Input shaft OG ... Output gear
TF1, TF2 ... 1,2nd Transfer Gear

Claims (10)

The first and second planetary gear sets PG1 and PG2 disposed on the first shaft 2 and the second shaft 4 disposed in parallel with the first shaft 2 are disposed. A third planetary gear set PG3 connected to the first and second planetary gear sets PG1 and PG2 through two transfer gears TF1 and TF2, and four clutches C1, C2 and C3. It comprises a friction member consisting of (C4) and two brakes (B1) (B2),
The first planetary gear set PG1 is connected to an input shaft IS and a first rotating element N1 which always operates as a fixed element, a second rotating element N2 which always produces a deceleration output, and operates as an input element at all times. At the same time the third rotary element (N3) for outputting as it is made,
The second planetary gear set PG2 is connected to the second rotating element N2 and is always connected to the fourth rotating element N4, which operates as an input element, and selectively connected to the input shaft IS, and the transmission housing H. It is made to include a fifth rotating element (N5) that is variably connected to and acts as an input and a fixed element and at the same time acts as an output element, and a sixth rotating element (N6) always acts as an output element,
The third planetary gear set PG2 is selectively connected to the second, third and sixth rotating elements N2, N3 and N6 and selectively connected to the transmission housing H to operate as an input and a fixed element. A seventh rotating element N7, an eighth rotating element N8 selectively connected to the fifth rotating element N5 to operate as an input element, and a ninth rotating element N9 acting as a final output element. Gear train of an automatic transmission for a vehicle, characterized in that made. 2. The first planetary gear set (PG1) is a double pinion planetary gear set, the second planetary gear set (PG2) is a double pinion planetary gear set, and the third planetary gear set (PG3) is a single pinion planetary gear set. Gear train of an automatic transmission for a vehicle, characterized in that consisting of. 3. The method of claim 1, wherein the first rotating element N1 is the first sun gear S1, the second rotating element N2 is the first ring gear R2, and the third rotating element N3 is the first rotation element N1. The first planet carrier PC1, the fourth rotary element N4 is the second sun gear S2, the fifth rotary element N5 is the second ring gear R2, and the sixth rotary element N6 is the second planet carrier (PC2), the seventh rotation element (N7) is the third sun gear (S3), the eighth rotation element (N8) is the third planet carrier (PC3), the ninth rotation element (N9) is the third ring gear (R3) Gear train of an automatic transmission for a vehicle, characterized in that consisting of. The friction member of claim 3, further comprising: a first clutch (C1) disposed between the second planet carrier (PC2) and the first transfer gear (TF1); A third clutch C3 disposed between the first ring gear R1 and the first transfer gear TF1; A third clutch C3 disposed between the input shaft IS and the second ring gear R2; A fourth clutch C4 disposed between the first planet carrier PC1 and the first transfer gear TF1; A first brake B1 disposed between the second ring gear R2 and the transmission housing H; A gear train of an automatic transmission for a vehicle, comprising a second brake (B2) disposed between the first transfer gear (TF1) and the transmission housing (H). The gear train of claim 4, wherein the first brake (B1) comprises a one-way clutch (F1) arranged in parallel. The friction member according to claim 4 or 5, wherein the first clutch C1 and the one-way clutch F1 are operated at the first forward speed.
At the second forward speed, the first clutch C1 and the second brake B2 are operated.
The first and second clutches C1 and C2 are operated at three forward speeds,
The first and fourth clutches C1 and C4 are operated at four forward speeds,
The first and third clutches C1 and C3 are operated at five forward speeds,
The third and fourth clutches C3 and C4 are operated at six forward speeds,
The second and third clutches C2 and C3 are operated at seven forward speeds,
At the 8th forward speed, the third clutch C3 and the second brake B2 are operated.
The gear train of the automatic transmission for a vehicle, characterized in that the shift is performed while the second clutch (C2) and the first brake (B1) are operated at the reverse speed 1. First and second planetary gear sets PG1 and PG2 disposed on the first axis 2 as a double pinion planetary gear set, and a single pinion planetary gear set arranged parallel to the first axis 2 as the single pinion planetary gear set. A third planetary gear set PG3 disposed on the two shafts 4 and connected to the first and second planetary gear sets PG1 and PG2 through first and second transfer gears TF1 and TF2; It comprises a friction member consisting of four clutch (C1) (C2) (C3) (C4) and two brakes (B1) (B2),
The first planetary gear set PG1 is always connected to the first sun gear S1 operating as a fixed element, the first ring gear R2 at which the deceleration output is always performed, and the input shaft IS to operate as an input element at all times. And at the same time the first planetary carrier (PC1) for outputting as it is made,
The second planetary gear set PG2 is connected to the first ring gear R1 and is always connected to the second sun gear S2, which operates as an input element, and selectively connected to the input shaft IS, and is connected to the transmission housing H. A second ring gear (R2) that is variably connected to operate as an input and a fixed element and at the same time as an output element, and a second planetary carrier (PC2) to always operate as an output element,
The third planetary gear set PG2 is selectively connected to the first ring gear R1, the first planet carrier PC1, and the second planet carrier PC2, and is selectively connected to the transmission housing H. A third sun gear S3 acting as an input and fixed element, a second planet carrier PC3 acting as an input element connected to the second ring gear R2 and a third ring acting as a final output element. Gear train of an automatic transmission for a vehicle, characterized in that it consists of a gear (R3). 8. The friction member according to claim 7, wherein the friction member comprises: a first clutch (C1) disposed between the second planet carrier (PC2) and the first transfer gear (TF1); A third clutch C3 disposed between the first ring gear R1 and the first transfer gear TF1; A third clutch C3 disposed between the input shaft IS and the second ring gear R2; A fourth clutch C4 disposed between the first planet carrier PC1 and the first transfer gear TF1; A first brake B1 disposed between the second ring gear R2 and the transmission housing H; A gear train of an automatic transmission for a vehicle, comprising a second brake (B2) disposed between the first transfer gear (TF1) and the transmission housing (H). The gear train of claim 8, wherein the first brake (B1) comprises a one-way clutch (F1) arranged in parallel. 10. The friction member according to claim 8 or 9, wherein the first clutch C1 and the one-way clutch F1 are operated at the first forward speed.
At the second forward speed, the first clutch C1 and the second brake B2 are operated.
The first and second clutches C1 and C2 are operated at three forward speeds,
The first and fourth clutches C1 and C4 are operated at four forward speeds,
The first and third clutches C1 and C3 are operated at five forward speeds,
The third and fourth clutches C3 and C4 are operated at six forward speeds,
The second and third clutches C2 and C3 are operated at seven forward speeds,
At the 8th forward speed, the third clutch C3 and the second brake B2 are operated.
The gear train of the automatic transmission for a vehicle, characterized in that the shift is performed while the second clutch (C2) and the first brake (B1) are operated at the reverse speed 1.

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