KR101145634B1

KR101145634B1 - Gear train of automatic transmission for vehicles

Info

Publication number: KR101145634B1
Application number: KR1020100029441A
Authority: KR
Inventors: 김우열
Original assignee: 현대자동차주식회사
Priority date: 2010-03-31
Filing date: 2010-03-31
Publication date: 2012-05-24
Also published as: KR20110109640A

Abstract

The present invention combines two single pinion planetary gear sets and one double pinion planetary gear set with three clutches and three brakes to realize eight forward speeds and one reverse speed while operating three friction elements at each shift stage. The present invention provides a gear train of an automatic transmission for a vehicle that can improve power transmission performance and reduce fuel consumption.

Description

GEAR TRAIN OF AUTOMATIC TRANSMISSION FOR VEHICLES}

The present invention relates to a gear train of an automatic transmission for a vehicle so that three simple planetary gear sets may be combined with three clutches and three brakes to realize a shift speed of eight forward speeds.

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

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 and weight are greatly changed depending on the combination method of the planetary gear set. Therefore, it is possible to develop a gear train that can be more robust and compact while minimizing power loss. Efforts are underway.

In particular, unlike the manual transmission in which the shifting step is more inconvenient for the driver to shift frequently, the automatic transmission is shifted by the transmission control unit (TCU) controls the operation of the gear train according to the driving state, Efforts are being made to find a gear train configuration that can implement more gears.

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 to meet the development of the automatic transmission as described above, and an object of the present invention is to combine three simple planetary gear sets with three clutches and three brakes, It is to provide a gear train of an automatic transmission for a vehicle to improve the power transmission performance and reduce fuel consumption by enabling eight friction speeds and one reverse speed while operating two friction elements.

A first planetary gear set PG1 having first, second and third rotating elements N1, N2 and N3 for realizing the above object; A second planetary gear set PG2 having fourth, fifth and sixth rotating elements N4, N5 and N6; A third planetary gear set PG3 having seventh, eighth and ninth rotating elements N7, N8 and N9 is provided with three clutches C1, C2, C3 and three brakes B1, B2. ) (B3),

The input shaft IS is directly connected to the seventh rotation element N7, the second rotation element N2 and the ninth rotation element N9 are directly connected, and the third rotation element N3 is connected to the fourth rotation element (N). N4) and the output gear OG directly connected to the sixth rotating element N6,

The first clutch C1 connects the eighth rotating element N8 and the fifth rotating element N5,

The second clutch C2 connects the eighth rotating element N8 and the fourth rotating element N4.

The third clutch C3 connects the input shaft IS and the fifth rotating element N5,

The first brake B1 connects the first rotating element N1 and the transmission housing H,

The second brake B2 connects the second rotating element N2 and the transmission housing H,

The third brake B3 provides a gear train of an automatic transmission for a vehicle formed by connecting the fifth rotating element N5 and the transmission housing H.

The first planetary gear set PG1 is a single pinion planetary gear set, wherein the first rotating element N1 is the first sun gear S1 and the second rotating element N2 is the first planet carrier PC1, the first being the first planetary gear set. 3 rotating element (N3) consists of a first ring gear (R1),

The second planetary gear set PG2 is a double pinion planetary gear set, wherein the fourth rotating element N4 is the second sun gear S2, and the fifth rotating element N5 is the second ring gear R2, the sixth rotation. Element N6, consisting of a second planetary carrier PC2,

The third planetary gear set PG3 is a single-pinion planetary gear set, wherein the seventh rotation element N7 is the third sun gear S3 and the eighth rotation element N8 is the third planet carrier PC3, the ninth rotation. The element N9 is characterized in that it consists of a third ring gear R3.

The second planetary gear set PG2 is a single-pinion planetary gear set, where the fourth rotating element N4 is the second sun gear S2 and the fifth rotating element N5 is the second planet carrier PC2, the sixth rotation. Element N6, which is composed of a second ring gear R2,

The third planetary gear set PG3 is a double pinion planetary gear set, in which the seventh rotation element N7 is the third sun gear S3, and the eighth rotation element N8 is the third ring gear R3, the ninth rotation. The element N9 is characterized in that it consists of a third planetary carrier PC3.

By the above configuration, the first clutch C1 and the first and third brakes B1 and B3 are operated at the first forward speed, and the first clutch C1 and the first and second brakes B1 at the second forward speed. B2 is activated, and the first and second clutches C1 and C2 and the first brake B1 are operated at the third forward speed, and the first and third clutches C1 and C3 are operated at the fourth forward speed. The first brake B1 is operated, and the first, second and third clutches C1, C2 and C3 are operated at five forward speeds, and the second and third clutches C2 and C3 are operated at six forward speeds. The first brake B1 is operated, and the second and third clutches C2 and C3 and the second brake B2 are operated at the seventh forward speed, and the third clutch C3 and the first, The second brakes B1 and B2 are operated, and in reverse, the second clutch C2 and the first and third brakes B1 and B3 are operated to shift.

As described above, the first, second, and third planetary gear sets PG1, PG2, and PG3, which consist of three simple planetary gear sets, have three clutches C1, C2, C3 and three brakes, which are friction elements. By combining B1) (B2) (B3) to implement the 8th speed shift stage, it is possible to improve the power transmission performance and fuel economy with multiple speeds.

Since these drawings are for reference in describing exemplary embodiments of the present invention, the technical spirit of the present invention should not be construed as being limited to the accompanying drawings.
1 is a configuration diagram of a gear train according to a first embodiment of the present invention.
Figure 2 is a shift-specific operation of the friction element applied to the gear train according to the present invention.
3 is a forward speed shift diagram of the gear train according to the first embodiment of the present invention;
4 is a two-speed forward speed diagram of a gear train according to the first embodiment of the present invention;
5 is a three-speed forward transmission diagram of the gear train according to the first embodiment of the present invention;
6 is a forward four speed shift diagram of the gear train according to the first embodiment of the present invention;
7 is a five-speed forward line diagram of the gear train according to the first embodiment of the present invention;
8 is a sixth forward speed diagram of a gear train according to the first embodiment of the present invention;
9 is a seventh forward speed diagram of a gear train according to the first embodiment of the present invention;
10 is a forward eighth speed shift diagram of the gear train according to the first embodiment of the present invention;
11 is a reverse shift diagram of a gear train according to the first embodiment of the present invention.
12 is a configuration diagram of a gear train according to a second embodiment of 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 them because the names of the components are the same and are not necessarily limited to the order in the description.

1 shows a first embodiment of a gear train according to the present invention, wherein the gear train of the present invention includes first, second and third planetary gear sets PG1 (PG2) and PG3 disposed on the same axis. And clutch means composed of three clutches C1, C2 and C3, and brake means composed of three brakes B1, B2 and B3.

Accordingly, the rotation input from the input shaft IS is shifted by the complementary operation of the first, second, and third planetary gear sets PG1, PG2, and PG3, and is output through the output gear OG connected to the output element. The first, second, and third planetary gear sets PG1, PG2, and PG3 are sequentially disposed from the engine side to the rear side on the input shaft IS.

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

The first planetary gear set PG1 is a single-pinion planetary gear set, and has three operating elements consisting of a sun gear, a planet carrier, and a ring gear as is known. For the convenience of description, the first gear is a first sun gear S1, The planet 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 operating elements consisting of a sun gear, a planet carrier, and a ring gear, as known, and for the sake of explanation, the sun gear may be a second sun gear S2, The planet carrier is referred to as the second planet carrier PC2 and the ring gear is referred to as the third ring gear R3.

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

In the combination of the first, second and third planetary gears configured as described above, the third sun gear S3 is directly connected to the input shaft IS so that the third sun gear S3 can always operate as an input element, and the second planet carrier PC2. Is connected to the output gear (OG) so that it always acts as an output element.

The first planet carrier PC1 is directly connected to the third ring gear R3, and the first ring gear R1 is directly connected to the second sun gear S2.

In addition, the third planet carrier PC3 is variably connected to the second ring gear R2 via the first clutch C1 and is variable with the second sun gear S2 via the second clutch C2. The input shaft IS is variably connected to the second ring gear R2 via the third clutch C3.

Accordingly, the rotational power of the engine is always input to the third sun gear S3 and at the same time when the third clutch C3 is operated, the input is simultaneously made to the second ring gear R2, and the first and third clutches C1. When C3 operates simultaneously, the third sun gear S3 and the third planet carrier PC3 are simultaneously input, and the third planet gear set PG3 is directly connected.

The first sun gear S1 is variably connected to the transmission housing H via the first brake B1, and the first planet carrier PC1 is connected to the transmission housing H via the second brake B2. ) And the second ring gear B3 is variably connected to the transmission housing H via the third brake B3 to operate as an optional fixing element.

By the combination as described above, the first, second and third planetary gear sets PG1, PG2 and PG3 operate as one compound planetary gear set, and rotational power input from the input shaft IS is applied to the first, second, and third planetary gear sets. 3 It is output through the output gear OG connected to the output element by shifting by the complementary operation of each rotating element constituting the planetary gear set PG1, PG2, PG3.

In the above, the friction elements composed of the first, second and third clutches C1, C2 and C3 and the first, second and third brakes B1, B2 and B3 are multi-plate hydraulic friction frictionally coupled by hydraulic pressure. It is customary to consist of a coupling unit.

Figure 2 is an operating table showing the friction elements applied to the present invention, that is, the clutch and the brake at each shift stage, the gear train of the present invention is known that the shift is made while the three friction elements in each shift stage is operated. Can be.

That is, the first clutch C1 and the first and third brakes B1 and B3 are operated at the first forward speed.

At the second forward speed, the first clutch C1 and the first and second brakes B1 and B2 are operated.

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

The first and third clutches C1 and C3 and the first brake B1 are operated at four forward speeds.

The first, second and third clutches C1, C2 and C3 are operated at five forward speeds,

At the sixth forward speed, the second and third clutches C2 and C3 and the first brake B1 are operated.

At the 7th forward, the second and third clutches C2 and C3 and the second brake B2 are operated.

At the 8th forward speed, the third clutch C3 and the first and second brakes B1 and B2 are operated.

In reverse, the second clutch C2 and the first and third brakes B1 and B3 are operated.

The shift is made.

3 to 11 show a shift diagram of the gear train according to the present invention, in which the lower horizontal line represents the rotational speed "0", and the upper horizontal line represents the rotational speed "1.0", that is, the same rotation as the input shaft IS. Indicates speed.

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 rotating element N1, the first planet carrier PC1 as the second rotating element N2, and the third rotation. The first ring gear R1 which is the element N3 is set, and these intervals are determined according to the gear ratio of the first planetary gear set PG1 (number of teeth of the sun gear / number of teeth of the ring gear).

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 sequentially rotated from the left side to the third sun gear S3 as the seventh rotation element N7, the third planet carrier PC3 as the eighth rotation element N8, and the ninth rotation. The third ring gear R3 which is the element N9 is set, and these intervals are determined according to the gear ratio of the third planetary gear set PG3 (the number of teeth of the sun gear / the number of ring gears).

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 third brakes B1 and B3 are operated and controlled.

Accordingly, the rotational power of the input shaft IS is input to the seventh rotation element N7, as shown in FIG. 3.

In this state, the eighth rotating element N8 is operated as the fixed element by the operation of the first clutch C1 and the third brake B3, and the reverse rotation output is made through the ninth rotating element N9. It consists of a first planetary gear set PG1 through a second rotary element N2 directly connected thereto.

Then, in the first planetary gear set PG1, the reverse rotation input is made to the second rotation element N2, and the first rotation element N1 operates as the fixed element by the operation of the first brake B1. A larger reverse rotation output is made through the third rotating element N3 acting as an element and is input to the second planetary gear set PG2 through the fourth rotating element N4 directly connected thereto.

As described above, the fifth rotating element N5 is operated as a fixed element by the operation of the third brake B3 in the state where an input is made to the second planetary gear set PG2 through the fourth rotating element N4. As a result of outputting as much as D1 through the sixth rotating element N6, which is an output element, the first forward speed is made.

[2 speed forward]

At the second forward speed, the operation of the third brake B3 is released in the state of the first forward speed, and the second brake B2 is operated and controlled.

Then, the operation of the third brake B3 is released in the shifting state of the first forward speed as described above, and the first planetary gear set PG1 is fixed by the operation of the first and second brakes B1 and B2. As shown in 4, while the input is made to the seventh rotating element N7, the ninth rotating element N9 is fixed and the deceleration output is made through the eighth rotating element N8.

The deceleration output of the eighth rotary element N8 is input to the fifth rotary element N5 of the second planetary gear set PG2 through the first clutch C1, where the fourth rotary element N4 is input. The bar is operated as a fixed element together with the third rotating element N3. As the output is performed as much as D2 through the sixth rotating element N6, which is an output element, the second forward speed is made.

[3 speed forward]

At the 3rd forward speed, the operation of the second brake B2 is released in the state of the 2nd forward speed, and the second clutch C2 is operated and controlled.

Then, the rotational power of the eighth rotating element N8 is driven by the operation of the second clutch C2 while the input is made to the seventh rotating element N7 as in the second forward speed as described above. At the same time as being transmitted to N4) and the third rotating element N3, rotational power of the ninth rotating element N9 is transmitted to the second rotating element N2.

In this power transmission process, the first rotating element N1 is operated as a fixed element by the operation of the first brake B1. As shown in FIG. 5, the first, second and third planetary gear sets PG1 and PG2 are illustrated. By the complementary operation of (PG3) is the output of the D3 through the sixth rotating element (N6) as the output element is to perform a three-speed forward.

[4 forward speed]

At the fourth forward speed, the operation of the second clutch C2 is released in the state of the third forward speed, and the third clutch C3 is operated and controlled.

Then, the input is simultaneously made to the eighth rotating element N8 by the operation of the first and third clutches C1 and C3 while the input is made to the seventh rotating element N7 as in the third forward speed. As a result, the third planetary gear set PG3 is directly connected to the entire planetary gear set as it is.

In the above state, an input is made to the fifth rotary element N5 of the second planetary gear set PG2 by the operation of the third clutch C3, and is directly connected to the ninth rotary element N9. 1 The rotational force as it is input is also input to the third rotating element N3 of the planetary gear set PG3.

In this power transmission process, the first rotating element N1 is operated as a fixed element by the operation of the first brake B1. As shown in FIG. 6, the first, second and third planetary gear sets PG1 and PG2 are provided. By the complementary operation of the (PG3) it is output as much as D4 through the sixth rotating element (N6) as the output element is a four-speed forward is made.

[5th forward]

At the 5th forward speed, the operation of the first brake B1 is released in the state of the 4th forward speed, and the second clutch C2 is operated and controlled.

Then, as in the fourth forward speed, the rotational force of the eighth rotating element N8 is controlled by the operation of the second clutch C2 while the third planetary gear set PG3 maintains the direct connection state. The rotational power of the ninth rotating element N9 is transmitted to the second rotating element N2 at the same time as it is transmitted to the N4 and the third rotating element N3, and as shown in FIG. All of the gear sets PG1, PG2, and PG3 are directly connected, and the output is output as much as D5 through the sixth rotating element N6, which is an output element, and thus the forward five-speed shift is made.

[6th forward]

At the sixth forward speed, the first clutch C1 is released in the state of the fifth forward speed, and the first brake B1 is operated and controlled.

Then, the input is made to the fifth rotating element N5 by the operation of the third clutch C3 while the input is made to the seventh rotating element N7, and the first rotation is made by the operation of the first brake B1. As the element N1 operates as a fixed element, as shown in FIG. 8, the sixth rotating element as an output element is formed by complementary operations of the first, second and third planetary gear sets PG1, PG2, and PG3. N6) is output as much as D6 which is overdrive state, and 6 forward speed is made.

[7th forward]

At the seventh forward speed, the operation of the first brake B1 is released in the state of the sixth forward speed, and the second brake B2 is operated and controlled.

Then, as in the sixth forward speed, the first rotary element N1 and the first rotary element N1 are operated by the operation of the second brake B2 while the seventh rotary element N7 and the fifth rotary element N5 are simultaneously input. As the ninth rotating element N9 operates as a fixed element, as shown in FIG. 9, the sixth rotation element N9 is an output element by complementary operation of the first, second and third planetary gear sets PG1, PG2, and PG3. As the output of the overdrive state D7 is made through the rotating element N6, the seventh forward speed is made.

[8th forward]

At the eighth forward speed, the second clutch C2 is released in the state of the seventh forward speed, and the first brake B1 is controlled to operate.

Then, as in the forward seventh speed, the first and second brakes B1 and B2 are simultaneously operated in the state in which simultaneous input is made to the seventh rotary element N7 and the fifth rotary element N5. As the planetary gear set PG1 is fixed, the fourth rotary element N4 of the second planetary gear set PG2 is operated as a fixed element and input to the fifth rotary element N5 as shown in FIG. 10. It is output as much as D8 in the overdrive state through the sixth rotation element N6, which is an output element, so that eight forward speed shifts are made.

[apse]

In the reverse shift stage, the second clutch C2 and the first and third brakes B1 and B3 are operated and controlled.

Then, the eighth rotating element N8 is connected to the fourth rotating element N4 and the third rotating element N3 by the operation of the second clutch C2 while the input is made to the seventh rotating element N7. While the ninth rotating element N9 is directly connected to the second rotating element N2, the first rotating element N1 and the fifth rotating element N5 are fixed by the operation of the first and third brakes B1 and B3. As shown in FIG. 11, the first, second and third planetary gear sets PG1, PG2, and PG3 rotate in a reverse direction through the sixth rotation element N6, which is an output element. As the output (REV) is made, reverse shift is made.

FIG. 12 shows a second embodiment according to the present invention. In the first embodiment, the second planetary gear set PG2 is arranged as a double planetary gear set, and the third planetary gear set PG3 is arranged as a single planetary planet. In the second embodiment, the second planetary gear set PG2 is disposed in a single planetary gear set, and the third planetary gear set PG3 is disposed in a double planetary gear set.

Accordingly, the fourth rotational element N4 of the second planetary gear set PG2 includes the second sun gear S2, the fifth rotational element N5 with the second planetary carrier PC2, and the sixth rotational element N6 with the fourth rotational element N4. The second ring gear (R2), the seventh rotation element (N7) of the third planetary gear set (PG3) is the third sun gear (S3), the eighth rotation element (N8) is the third ring gear (R3). The ninth rotating element N9 is made of the third planet carrier PC3.

In the second embodiment of the present invention as described above, only the configuration of the rotating elements N5, N6, N8, and N9 is different from that of the first embodiment, and the shifting process is the same as the first embodiment. Detailed description thereof will be omitted.

While the present invention has been particularly shown and described with reference to exemplary embodiments thereof, it is to be understood that the invention is not limited to the disclosed exemplary embodiments, but, on the contrary, And it goes without saying that the invention belongs to the scope of the 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

Claims

A first planetary gear set PG1 having first, second and third rotating elements N1, N2 and N3;
A second planetary gear set PG2 having fourth, fifth and sixth rotating elements N4, N5 and N6;
A third planetary gear set PG3 having seventh, eighth and ninth rotating elements N7, N8 and N9 is provided with three clutches C1, C2, C3 and three brakes B1, B2. ) (B3),
The input shaft IS is directly connected to the seventh rotation element N7, the second rotation element N2 and the ninth rotation element N9 are directly connected, and the third rotation element N3 is connected to the fourth rotation element (N). N4) and the output gear OG directly connected to the sixth rotating element N6,
The first clutch C1 connects the eighth rotating element N8 and the fifth rotating element N5,
The second clutch C2 connects the eighth rotating element N8 and the fourth rotating element N4.
The third clutch C3 connects the input shaft IS and the fifth rotating element N5,
The first brake B1 connects the first rotating element N1 and the transmission housing H,
The second brake B2 connects the second rotating element N2 and the transmission housing H,
The third brake (B3) is a gear train of the automatic transmission for a vehicle, characterized in that made by connecting the fifth rotating element (N5) and the transmission housing (H).

The first planetary gear set PG1 is a single pinion planetary gear set, wherein the first rotating element N1 is the first sun gear S1 and the second rotating element N2 is the first planet carrier. PC1), the third rotating element N3 is made of the first ring gear (R1),
The second planetary gear set PG2 is a double pinion planetary gear set, wherein the fourth rotating element N4 is the second sun gear S2, and the fifth rotating element N5 is the second ring gear R2, the sixth rotation. Element N6, consisting of a second planetary carrier PC2,
The third planetary gear set PG3 is a single-pinion planetary gear set, wherein the seventh rotation element N7 is the third sun gear S3 and the eighth rotation element N8 is the third planet carrier PC3, the ninth rotation. Gear train of an automatic transmission for a vehicle, characterized in that the element N9 consists of a third ring gear R3.

The first planetary gear set PG1 is a single pinion planetary gear set, wherein the first rotating element N1 is the first sun gear S1 and the second rotating element N2 is the first planet carrier. PC1), the third rotating element N3 is made of the first ring gear (R1),
The second planetary gear set PG2 is a single-pinion planetary gear set, where the fourth rotating element N4 is the second sun gear S2 and the fifth rotating element N5 is the second planet carrier PC2, the sixth rotation. Element N6, which is composed of a second ring gear R2,
The third planetary gear set PG3 is a double pinion planetary gear set, in which the seventh rotation element N7 is the third sun gear S3, and the eighth rotation element N8 is the third ring gear R3, the ninth rotation. Gear train of an automatic transmission for a vehicle, characterized in that the element N9 consists of a third planet carrier PC3.

2. The gear train of an automatic transmission for a vehicle according to claim 1, wherein the first, second and third planetary gear sets (PG1) (PG2) and (PG3) are sequentially arranged from the engine side to the rear side on the same axis.

The method of claim 1, wherein the first, second, third, and fourth clutches C1, C2, C3, C4, and the first and second brakes B1, B2 are configured at first forward speed C1. And the first and third brakes B1 and B3 are operated, and the first clutch C1 and the first and second brakes B1 and B2 are operated at the second forward speed, and the first and second brakes at the third forward speed. The clutches C1 and C2 and the first brake B1 are actuated, and the first and third clutches C1 and C3 and the first brake B1 are actuated at the fourth forward speed and the first at the fifth forward speed. , 2,3 clutches C1, C2, C3 are activated, the second and third clutches C2, C3 and the first brake B1 are operated at 6 forward speeds, and the 2nd at 7 forward speeds. , The third clutch C2 (C3) and the second brake (B2) is activated, the third clutch (C3) and the first and second brakes (B1) (B2) at the eighth forward speed, the second in reverse A gear train of an automatic transmission for a vehicle, characterized in that shifting is performed while the clutch C2 and the first and third brakes B1 and B3 are operated.

A first planetary gear set PG1 consisting 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 including a double pinion planetary gear set including a second sun gear S2, a second planet carrier PC2, and a second ring gear R2;
A third planetary gear set PG3 comprising a single pinion planetary gear set having a third sun gear S3, a third planet carrier PC3, and a third ring gear R3 includes three clutches C1 and C2. (C3) and three brakes (B1) (B2) (B3),
The input shaft IS is directly connected to the third sun gear S3, the first planet carrier PC1 and the third ring gear R3 are directly connected, and the first ring gear R1 is connected to the second sun gear S2. Direct connection with the output gear OG directly connected to the second planetary carrier PC2,
The first clutch C1 connects the third planet carrier PC3 and the second ring gear R2.
The second clutch C2 connects the third planet carrier PC3 and the second sun gear S2.
The third clutch C3 connects the input shaft IS and the second ring gear R2.
The first brake B1 connects the first sun gear S1 and the transmission housing H,
The second brake B2 connects the first planet carrier PC1 and the transmission housing H.
The third brake (B3) is a gear train of the automatic transmission for a vehicle, characterized in that made by connecting the second ring gear (R2) and the transmission housing (H).

A first planetary gear set PG1 consisting 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 including a single pinion planetary gear set including a second sun gear S2, a second planet carrier PC2, and a second ring gear R2;
A third planetary gear set PG3 comprising a third pinion planetary gear set having a third sun gear S3, a third planet carrier PC3, and a third ring gear R3 includes three clutches C1 and C2. (C3) and three brakes (B1) (B2) (B3),
The input shaft IS is directly connected to the third sun gear S3, the first planet carrier PC1 and the third planet carrier PC3 are directly connected, and the first ring gear R1 is connected to the second sun gear S2. In the state of directly connecting the output gear OG to the second ring gear R2,
The first clutch C1 connects the third ring gear R2 and the second planet carrier PC2,
The second clutch C2 connects the third ring gear R2 and the second sun gear S2.
The third clutch C3 connects the input shaft IS and the second planet carrier PC2,
The first brake B1 connects the first sun gear S1 and the transmission housing H,
The second brake B2 connects the first planet carrier PC1 and the transmission housing H.
The third brake (B3) is a gear train of the automatic transmission for a vehicle, characterized in that made by connecting the second planetary carrier (PC2) and the transmission housing (H).