KR101459424B1 - Gear train of automatic transmission for vehicles - Google Patents

Abstract

The present invention combines two double pinion planetary gear sets and one single pinion planetary gear set with four clutches and two brakes to realize eight forward speeds and two reverse speeds to improve power transmission performance and reduce fuel consumption The present invention provides a gear train of an automatic transmission for a vehicle.

Planetary gear set, sun gear, planetary carrier, ring gear, clutch, brake

Description

Technical Field [0001] The present invention relates to a gear train of an automatic transmission for a vehicle,

The present invention relates to a gear train of a vehicular automatic transmission in which three simple planetary gear sets are combined with four clutches and two brakes so as to realize an 8th speed gear stage.

Generally, a multi-speed shifting mechanism of an automatic transmission is implemented by combining a plurality of planetary gear sets. A gear train in which a plurality of planetary gear sets are combined has a function of receiving rotational power from a torque converter, .

In such an automatic transmission, an automatic transmission that implements more gear positions is required because it is possible to design a more appropriate transmission ratio as the number of gear positions that can be implemented increases, and to realize an excellent vehicle in terms of power performance and fuel economy.

Even if the same gear stage is implemented, the durability, power transmission efficiency, and size and weight of the planetary gear set can be significantly changed according to the combination of the planetary gear set, so that the gear train can be made more compact and compact while minimizing the power loss. Efforts are steadily underway.

In particular, unlike a manual transmission in which a driver must frequently change gears as the number of shift stages increases, the automatic transmission is shifted by controlling the operation of the gear train by the transmission control unit (TCU) Efforts are continuing to find the configuration of a gear train capable of implementing more gear positions.

In view of this, the 4th- and 5-speed automatic transmissions are currently in common use in the currently used automatic transmissions, but in recent years, a 6-speed automatic transmission has been developed and applied to vehicles, As well.

Accordingly, the present inventors have proposed the present invention in order to respond to the development of the automatic transmission as described above, and the object of the present invention is to provide an automatic transmission that combines three simple planetary gear sets with four clutches and two brakes, Speed transmission performance of the automatic transmission can be improved by improving the performance of the power transmission, reducing the fuel consumption, and improving the performance of the reverse transmission.

In order to achieve the above object, the present invention provides a planetary gear set including a first planetary gear set (PG1) comprising a double pinion planetary gear set having three operating elements (S1) (PC1) (R1) A second planetary gear set PG2 comprising a single pinion planetary gear set having a planetary gear set PC2 (R2) and a double pinion planetary gear set having three operating elements S3 (PC3) and R3 The third planetary gear set PG3 is assembled by applying the four clutches C1, C2, C3 and C4 and the two brakes B1 and B2,

The first planetary gearset PG1 includes a first rotary element N1 directly connected to the input shaft IS and operating as an input element at all times, A second rotary element N2 selectively connected to the transmission housing and a third rotary element N3 connected directly to the transmission housing,

The second and third planetary gear sets PG2 and PG3 are combined in the form of a complex planetary gear set in which two operating elements are directly and independently connected to each other and have four rotary elements N4 to N7, A fourth rotary element N4 selectively connected to the rotary element N2 and the input shaft IS to which the rotational power of the engine is input and selectively connected to the transmission housing H, A fifth rotary element N5 selectively connected to the transmission housing IS and selectively connected to the transmission housing H, a sixth rotary element N6 connected to the output gear OG, And a seventh rotary element (N7) selectively connected to the output shaft (N2).

The first planetary gear set PG1 is configured such that the first planetary carrier PC1 has the first rotary element N1, the first ring gear R1 has the second rotary element N2, the first sun gear S3 And a third rotating element N3,

The second and third sun gears S2 and S3 are directly connected to the second and third planetary gear sets PG2 and PG3 while the second and third planetary carriers PC2 and PC3 are directly connected to each other, The sun gear S2 and the third sun gear S2 are connected to the fourth rotary element N4 and the third ring gear R3 is connected to the fifth rotary element N5 and the second and third planetary carriers PC2, N6, and the second ring gear R2 is a seventh rotary element N7.

The first, second and third planetary gear sets PG1, PG2 and PG3 are connected to the first, second and third clutches C1, C2, C3 and C4 and the first and second brake B1 ) ≪ / RTI > (B2)

The first clutch C1 connects the input shaft IS and the fourth rotary element N4,

The second clutch C2 connects the input shaft IS and the fifth rotary element N5,

The third clutch C3 connects the second rotary element N2 and the fourth rotary element N4,

The fourth clutch C4 connects the second rotary element N2 and the seventh rotary element N7,

The first brake B1 connects the fifth rotary element N5 to the transmission housing H,

And the second brake B2 is arranged so as to be able to connect the fourth rotary element N4.

In this case, the fourth clutch C4 and the first brake B1 are actuated in the first forward speed,

The fourth clutch C4 and the second brake B2 are actuated in forward 2,

The fourth clutch C4 and the third clutch C3 are operated in the forward third speed,

The fourth clutch C4 and the first clutch C1 are operated in forward speed 4,

The fourth clutch C4 and the second clutch C2 are operated in forward speed 5,

The second clutch C2 and the first clutch C1 are operated in forward speed 6,

The second clutch C2 and the third clutch C3 are operated in forward speed 7,

The second clutch C2 and the second brake B2 are operated in forward speed 8,

The third clutch C3 and the first brake B1 are operated in reverse 1,

And the shift is performed while the first clutch C1 and the first brake B1 are operated in the reverse second speed.

The first planetary gear set PG1 is configured such that the first planetary carrier PC1 has the first rotary element N1, the first ring gear R1 has the second rotary element N2, the first sun gear S3 And a third rotating element N3,

The second and third sun gears S2 and S3 are directly connected to the second and third planetary gear sets PG2 and PG3 and the third planetary carrier PC3 and the second ring gear R2 are directly connected to each other, The third ring gear R3 is the fifth rotary element N5 and the second planetary carrier PC2 is the sixth rotary element N6, the second and third sun gear S2 and S3 are the fourth rotary element N4, The second ring gear R2 and the third planetary carrier PC3 are constituted by a seventh rotary element N7.

The first, second, and third planetary gear sets PG1, PG2, and PG3 including the three simple planetary gear sets as described above are connected to four clutches C1, C2, C3, and C4, Speed brakes B1 and B2 to realize the forward speeds of the eight forward speeds and the reverse two speeds, thereby improving power transmission performance and improving fuel economy.

Further, by shifting the two friction elements at the respective speed change stages, the capacity reduction of the oil pump and the hydraulic control efficiency can be improved.

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

 FIG. 1 illustrates a first embodiment of a gear train according to the present invention. The gear train of the present invention includes first, second, and third planetary gear sets PG1, PG2, and PG3 disposed on the same axis line, A clutch means composed of four clutches C1, C2, C3 and C4 and a brake means composed of two brakes B1, B2.

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 outputted through the output gear OG connected to the output element , The first, second and third planetary gear sets PG1, PG2 and PG3 are sequentially arranged on the input shaft IS from the rear side toward the engine side.

In this case, the input shaft IS means the turbine shaft of the torque converter as an input member, and the rotational power from the engine crankshaft is input through torque conversion through the torque converter, and the output gear OG is input as an output member And drive the drive wheels through one known differential.

The first planetary gear set PG1 is a double pinion planetary gear set having three operating elements, which are known as a sun gear, a planetary carrier, and a ring gear. For convenience of explanation, the sun gear is referred to as a first sun gear S1, The planetary carrier is referred to as a first planetary carrier PC1, and the ring gear is referred to as a first ring gear R1.

The first planetary gearset PG1 is connected to the input shaft IS as a first rotary element N1 and operates as an input element at all times, and the first ring gear R1 The first sun gear S1 selectively transmits the rotation power decelerated as the second rotary element N2 to the selected two of the operating elements of the second planetary gear set PG2, Which is fixedly connected to the transmission housing H to operate as a fixed element at all times.

Accordingly, the first planetary gearset PG1 decelerates the rotational power input to the first rotary element N1 and outputs the decelerated output through the second rotary element N2.

The second planetary gear set PG2 is a single pinion planetary gear set having three operating elements, which are known as a sun gear, a planetary carrier, and a ring gear. For convenience of explanation, the sun gear is referred to as a second sun gear S2, The planetary carrier is referred to as a second planetary carrier PC2, and the ring gear is referred to as a second ring gear R2.

The third planetary gear set is a double pinion planetary gear set. The third planetary gear set includes three operating elements including a sun gear, a planetary carrier, and a ring gear as known in the art. For convenience of explanation, the sun gear is referred to as a third sun gear S3, The third planetary carrier PC3, and the ring gear as the third ring gear R3.

The second and third planetary gear sets PG2 and PG3 are in the form of a complex planetary gear set in which two operating elements are fixedly connected to each other to have four rotary elements N4 to N7. In the first embodiment, the second sun gear S2 and the third sun gear S3 are directly connected, and the second planetary carrier PC2 and the third planetary carrier PC3 are directly connected.

As a result, the second and third sun gears S2 and S3 are selectively operated as the input element and the fixed element as the fourth rotary element N4 and the third ring gear R3 is operated as the fifth rotary element N5, And the second and third planetary carriers PC2 and PC3 are connected to the output gear OG as the sixth rotary element N6 to operate as the final output element at all times , And the second ring gear R2 operates as an optional input element as the seventh rotary element N7.

The third sun gear S3 as the fourth rotary element N4 is connected to the input shaft IS through the first clutch C1 so that the rotational power of the input shaft IS is selectively input The first planetary carrier PC1 which is the first rotation element N1 is driven by the second clutch C2 and the second clutch C2 is engaged with the transmission housing H via the second brake B2, And is connected to the third ring gear R3 which is the fifth rotary element N5 and selectively transmits the rotational power of the input shaft IS to the third ring gear R3.

The first ring gear R1 as the second rotary element N2 is connected to the second and third sun gears S2 and S3 as the fourth rotary element N4 via the third clutch C3, Is connected to the second ring gear R2 which is the seventh rotary element N7 through the fourth clutch C4 and selectively outputs the reduced output of the second rotary element N2 to the fourth rotary element N4 and the seventh rotary element N4, And the third ring gear R3 as the fifth rotary element N5 is transmitted to the transmission housing N through the first brake B1 in which the one-way clutch F1 is arranged in parallel. And is connected and operated as an optional stationary element.

 With the above configuration, the rotational power of the engine transmitted from the input shaft IS is always input to the first rotation element N1 of the first planetary gearset PG1, and at the same time, the fourth rotation element N4 and the fifth rotation The element N5 shifts to the second forward speed and the reverse reverse speed in the complementary operation to output through the output gear OG as the final output path.

The frictional elements constituted by the first, second, third and fourth clutches C1, C2, C3 and C4 and the first and second brakes B1 and B2 are frictional engagement by hydraulic pressure, And a coupling unit.

And the output gear OG is disposed on the engine side of the third planetary gear set PG3.

FIG. 2 is an operation table showing that friction elements, that is, clutches and brakes applied to the present invention, operate at respective gear positions. In the gear train of the present invention, two friction members are operated at respective gear positions, .

That is, the fourth clutch C4 and the first brake B1 are operated in the forward first speed,

The fourth clutch C4 and the second brake B2 are operated in the forward second speed,

The fourth and third clutches C4 and C3 are operated in the forward third speed,

The fourth and first clutches C4 and C1 are operated in the forward fourth speed,

The fourth and second clutches C4 and C2 are operated in the fifth forward speed,

The second and first clutches (C2) and (C1) are operated in the forward sixth speed,

The second and third clutches (C2) and (C3) are operated in the forward seventh gear,

The second clutch C2 and the second brake B2 are actuated in forward 8 speed,

The first brake B1 and the third clutch C3 are operated in reverse 1,

The shift is performed while the first brake B1 and the first clutch C1 are operated in the reverse second speed.

In the above description, the third clutch C3 and the first brake B1 are actuated in the first forward speed. However, when the first brake B1 is disposed in parallel with the one-way clutch F1 as in the present invention The one-way clutch F1 is operated without operating the first brake B1 in the normal D range 1, thereby improving the shifting feeling at the time of shifting to the second speed.

Fig. 3 shows 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 " .

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

The four vertical lines of the second and third planetary gear sets PG2 and PC3 are the second and third sun gears S2 and S3 which are the fourth rotary element N4 in order from the left side, 3 planetary carrier PC2 and a third ring gear R2 which are the seventh rotary element N7 which are the sixth rotary element N6, (The number of teeth of the sun gear / the number of teeth of the ring gear) of the first, second and third planetary gear sets PG2 and PC3.

The detailed description of the position setting of each rotary element in the above-described transmission line diagram is omitted because it is well known to those skilled in the gear train.

[Advancing first gen]

In the first forward speed, the fourth clutch C4 and the first brake B1 are actuated as shown in Fig.

The seventh rotary element N7 is operated by the operation of the fourth clutch C4 in a state where the rotational power of the input shaft IS is inputted to the first rotary element N1 and the reduced output is made to the second rotary element N2, The deceleration input is performed.

Then, in the state where the input is made to the seventh rotary element N7, the fifth rotary element N5 operates as a fixed element by the operation of the first brake B1 to form the first speed change line SP1, The output of D1 is achieved through the sixth rotary element N6, which is a forward speed change ratio of about "4.333" as the maximum speed change ratio.

The first brake B1 is disposed in parallel with the one-way clutch F1. In the normal first-speed shift, however, the first brake B1 is operated in the forward one- It is normal that the forward first shift is performed while the clutch F1 is operated and the first brake B1 is operated and controlled in the first forward speed in the "L" range.

[Advancing second gen]

In the second forward speed, the operation of the first brake B1 is released and the operation of the second brake B2 is controlled in the forward first speed state.

Then, the fixed element is converted from the fifth rotary element N5 to the fourth rotary element N4 by the operation of the second brake B2 in the forward first speed transmission state to form the second transmission line SP2 The output of D2 is output through the sixth rotary element N6, which is an output element, so that the forward second speed shift of the speed ratio "2.333" is achieved.

[Three steps forward]

In the third forward speed, the operation of the second brake B2, which was operated in the forward second speed state, is released as shown in Fig. 2, and the operation of the third clutch C3 is controlled.

Then, the fourth rotary element N4, which has been operated as a fixed element in the forward second speed state, is released, and at the same time, the rotational force of the second rotary element N2 is transmitted to the fourth Is input to the rotary element N4 and is simultaneously input to the fourth and seventh rotary elements N4 and N7 to be in a direct coupling state to form the third speed change line SP3.

As a result, output of D3 is achieved through the sixth rotary element N6, which is an output element, so that the forward third speed shift of the speed ratio "1.667" is achieved.

[Advance 4th gen]

In the fourth forward speed, as shown in Fig. 2, the operation of the third clutch C3 which was operating in the forward third speed state is released, and the operation of the first clutch C1 is controlled.

The deceleration input of the second rotary element N2 input to the fourth rotary element N4 is interrupted in the third forward speed state as described above and the rotational power of the input shaft IS due to the operation of the first clutch C1 The fourth speed change line SP4 is formed, and the output of the fourth speed change element N6, which is the output element, is made as much as D4, so that the forward fourth speed change of about 1.400 is performed .

[Five steps forward]

In the fifth forward speed, as shown in Fig. 2, the operation of the first clutch C1 that was operating in the forward fourth speed state is released, and the operation of the second clutch C2 is controlled.

The rotational power of the input shaft IS input to the fourth rotary element N4 is interrupted in the fourth forward speed shift state and the rotational power of the input shaft IS is reduced by the operation of the second clutch C2 to the fifth The fifth speed change line SP5 is formed and the output of the fifth speed change element N6 is output through the sixth rotary element N6 as the output element so that the forward fifth speed change speed of about 1.182 .

[6 steps forward]

2, the operation of the fourth clutch C4, which was operated from the forward first speed to the forward fifth speed, is released while the first clutch C1 is in operation, and the first clutch C1 The operation is controlled.

When the rotational force of the input shaft IS is being input to the fifth rotary element N5 by the operation of the second clutch C2, the fourth rotary element N4 is rotated by the operation of the first clutch C1, And the second and third planetary gear sets PG2 and PG3 are directly connected to form the sixth speed change line SP6.

As a result, the rotational power input from the input shaft IS is outputted as D5 through the sixth rotary element N6 as the output element, and the forward sixth speed shift of the speed ratio "1.000 "

[Advancing seven genus]

In the forward speed 7, as shown in Fig. 2, the operation of the first clutch Cl operated in the forward sixth speed state is released, and the operation of the third clutch C3 is controlled.

Then, the fourth clutch C3 is operated by the operation of the second clutch C2 to engage the second rotary element N4 with the fourth rotary element N4 in the state where the rotational power of the input shaft IS is being input to the fifth rotary element N5. The deceleration output of the rotary element N2 is inputted and the seventh speed change line SP7 is formed and the output of D7 is made through the sixth rotary element N6 which is the output element and the forward speed of the speed ratio "0.882" 7-speed shift will be done.

[Going forward 8]

As shown in Fig. 2, in the forward speed 8, the operation of the third clutch C3 that was operating in the forward seventh speed is released, and the second brake B2 is actuated.

When the second clutch C2 is operated and the rotational force of the input shaft IS is input to the fifth rotary element N5, the fourth rotary element N4 is rotated by the operation of the second brake B2, The output of D8 is made through the sixth rotary element N6, which is an output element, while the eighth speed change line SP7 is formed, so that the forward 8-speed shift of the speed ratio "0.750 " will be.

[Backward speed]

In the reverse first speed range, the first brake B1 and the third clutch C3 are actuated as shown in Fig.

The fifth clutch C3 is operated so that the fifth rotary element N5 is operated by the operation of the first brake B1 in a state where the deceleration output of the second rotary element N2 is input to the fourth rotary element N4, And the reverse first transmission line SR1 is formed while the output of the sixth rotary element N6, which is an output element, is output as REV1, The shift is made.

[Backward two-speed]

In the reverse second-gear range, the operation of the third clutch C3 that was operated in the reverse first speed is released as shown in Fig. 2, and the operation of the first clutch C1 is controlled.

The fourth rotary element N4 is operated as an input element by the operation of the first clutch C1 in a state in which the fifth rotary element N5 is operating as a fixed element by the operation of the first brake B1 , The rearward second transmission line SR2 is formed, and the output of REV2 is made through the sixth rotary element N6, which is an output element, so that the reverse second speed shift of about -3.000 is achieved.

In addition to the shift as described above, a skip down shift such as 8? 6, 7? 5, 6? 4, 5? 3, 4? 2, 3? 1, 8? 4, 7? 3, 6? 2, The control can be performed by skipping the skip down shift except for 8 → 4, 6 → 2 releasing one friction element in the other shift and combining the other friction element. Therefore, it is possible to improve the hydraulic control efficiency .

The speed ratio of the first planetary gear set PG1 and the second planetary gear set PG2 are set to 30 and 60, respectively, and the number of teeth of the first sun gear S1 and the first ring gear R1 of the first planetary gearset PG1 is 30 and 60, The number of teeth of the second sun gear S2 and the number of teeth of the second ring gear R2 of the third planetary gearset PG3 is 30.60 and the number of teeth of the third sun gear S3 and the third ring gear R2 of the third planetary gearset PG3 is 30 and 51, respectively.

FIG. 4 illustrates a gear train according to a second embodiment of the present invention. In FIG. 4, the second and third planetary gear sets PG2 and PG3 are combined. In the first embodiment of the present invention, The second and third sun gears S2 and S3 are directly connected and the second planetary carrier PC2 and the second planetary carrier PC3 are integrally connected to each other in the second embodiment, And the second ring gear PC2 and the third ring gear R3 are integrally connected.

Thus, the fourth rotary element N4 is connected to the second, third, and fourth sun gears S2 and S3, the fifth rotary element N5, the third ring gear R3, and the sixth rotary element N6, The second planetary gear PC2 and the seventh rotary element N7 are set to the second ring gear R2 and the third planetary carrier PC3.

2 and 3, only the constituent elements of the sixth and seventh rotary elements N6 and N7 are different from those of the first embodiment only in the shifting process of the gear train according to the second embodiment, The operation of the friction element and the shifting process are the same, so a detailed description of the shifting process will be omitted.

In the second embodiment as described above, the output gear OG must be directly connected to the second planetary carrier PC2, which is the sixth rotary element N6, from the engine side. The third and fourth planetary gear sets PG2 and PG3 are arranged differently from the first embodiment in which the first and third planetary gear sets PG1 and PG2 are sequentially disposed, 2 planetary gear set (PG1) (PG3) (PG2).

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 shall include all modifications of the scope which are deemed to be equivalent.

1 is a structural view of a gear train according to a first embodiment of the present invention;

Fig. 2 is an operation diagram of a friction element applied to a gear train according to the present invention, for each gear position.

3 is a view showing a shift of a gear train according to the first embodiment of the present invention.

4 is a configuration diagram of a gear train according to a second embodiment of the present invention.

Claims (10)

A first planetary gear set PG1 consisting of a double pinion planetary gear set having three operating elements S1 (PC1) R1 and a second planetary gear set PG1 having three operating elements S2 (PC2) A second planetary gearset PG2 of a pinion planetary gear set and a third planetary gearset PG3 of a double pinion planetary gearset having three operating elements S3, The clutches C1, C2, C3 and C4 and the two brakes B1 and B2 are applied, The first planetary gearset PG1 includes a first rotary element N1 directly connected to the input shaft IS and operating as an input element at all times, A second rotary element N2 selectively connected to the transmission housing and a third rotary element N3 connected directly to the transmission housing, The second and third planetary gear sets PG2 and PG3 are combined in the form of a complex planetary gear set in which two operating elements are directly and independently connected to each other and have four rotary elements N4 to N7, A fourth rotary element N4 selectively connected to the rotary element N2 and the input shaft IS to which the rotational power of the engine is input and selectively connected to the transmission housing H, A fifth rotary element N5 selectively connected to the transmission housing IS and selectively connected to the transmission housing H, a sixth rotary element N6 connected to the output gear OG, And a seventh rotary element (N7) selectively connected to the first rotary element (N2). 2. The planetary gear set according to claim 1, wherein the first planetary gear set PG1 is a planetary gear set having a first planetary carrier PC1 as a first rotary element N1, a first ring gear R1 as a second rotary element N2, (S3) is constituted by a third rotary element (N3) The second and third sun gears S2 and S3 are directly connected to the second and third planetary gear sets PG2 and PG3 while the second and third planetary carriers PC2 and PC3 are directly connected to each other, The sun gear S2 and the third sun gear S2 are connected to the fourth rotary element N4 and the third ring gear R3 is connected to the fifth rotary element N5 and the second and third planetary carriers PC2, N6) and the second ring gear (R2) is a seventh rotary element (N7). 3. The gear train of claim 2, wherein the first, second and third planetary gear sets (PG1, PG2, PG3) are sequentially arranged on the same axis from the rear side toward the engine side. 3. The planetary gear set according to claim 1 or 2, wherein the first, second and third planetary gear sets (PG1, PG2, PG3) comprise first, second, third and fourth clutches C1, C2, C3, And the first and second brakes B1 and B2, The first clutch C1 connects the input shaft IS and the fourth rotary element N4, The second clutch C2 connects the input shaft IS and the fifth rotary element N5, The third clutch C3 connects the second rotary element N2 and the fourth rotary element N4, The fourth clutch C4 connects the second rotary element N2 and the seventh rotary element N7, The first brake B1 connects the fifth rotary element N5 to the transmission housing H, And the second brake (B2) is arranged so as to be able to connect the fourth rotary element (N4). The gear train of claim 4, wherein the first clutch (C1) is arranged in parallel with the one-way clutch (F1). 5. The automatic transmission according to claim 4, wherein the fourth clutch (C4) and the first brake (B1) The fourth clutch C4 and the second brake B2 are actuated in forward 2, The fourth clutch C4 and the third clutch C3 are operated in the forward third speed, The fourth clutch C4 and the first clutch C1 are operated in forward speed 4, The fourth clutch C4 and the second clutch C2 are operated in forward speed 5, The second clutch C2 and the first clutch C1 are operated in forward speed 6, The second clutch C2 and the third clutch C3 are operated in forward speed 7, The second clutch C2 and the second brake B2 are operated in forward speed 8, The third clutch C3 and the first brake B1 are operated in reverse 1, And the shift is made while the first clutch (C1) and the first brake (B1) are operated in the second reverse range. 2. The planetary gear set according to claim 1, wherein the first planetary gear set PG1 is a planetary gear set having a first planetary carrier PC1 as a first rotary element N1, a first ring gear R1 as a second rotary element N2, (S3) is constituted by a third rotary element (N3) The second and third sun gears S2 and S3 are directly connected to the second and third planetary gear sets PG2 and PG3 and the third planetary carrier PC3 and the second ring gear R2 are directly connected to each other, The third ring gear R3 is the fifth rotary element N5 and the second planetary carrier PC2 is the sixth rotary element N6, the second and third sun gear S2 and S3 are the fourth rotary element N4, , The second ring gear (R2) and the third planetary carrier (PC3) constitute a seventh rotary element (N7). 8. The planetary gear set according to claim 7, wherein the first, third and the third planetary gear sets PG1, PG2, PG3 are arranged on the same axis from the rear side toward the engine side, (PG3) are arranged in this order. A first planetary gear set PG1 composed of a double pinion planetary gear set having a first sun gear S1, a first planetary carrier PC1 and a first ring gear R1, A second planetary gear set PG2 composed of a single pinion planetary gear set having a second sun gear S2, a second planetary carrier PC2 and a second ring gear R2, The third planetary gear set PG3 constituted by the double pinion planetary gear set having the third sun gear S3, the third planetary carrier PC3 and the third ring gear R3 is connected to the four clutches C1 ) C3, C4 and two brakes B1, B2, The input shaft IS is directly connected to the first planetary carrier PC1 and the second and third planetary gears PC2 and PC3 are directly connected while directly connecting the second and third sun gears S2 and S3 The third planetary carrier PC3 is connected to the output gear OG and the first sun gear S1 is directly connected to the transmission housing H, The first clutch C1 connects the input shaft IS and the third sun gear S3, The second clutch C2 connects the first planetary carrier PC1 and the third ring gear R3, The third clutch C3 connects the first ring gear R1 and the second sun gear S2, The fourth clutch C4 connects the first ring gear R1 and the second ring gear R2, The first brake B1 connects the third ring gear R3 and the transmission housing H together with the one-way clutch F1, And the second brake B2 connects the third sun gear S3 and the transmission housing H. The gear train of the automatic transmission for a vehicle according to claim 1, A first planetary gear set PG1 composed of a double pinion planetary gear set having a first sun gear S1, a first planetary carrier PC1 and a first ring gear R1, A second planetary gear set PG2 composed of a single pinion planetary gear set having a second sun gear S2, a second planetary carrier PC2 and a second ring gear R2, The third planetary gear set PG3 constituted by the double pinion planetary gear set having the third sun gear S3, the third planetary carrier PC3 and the third ring gear R3 is connected to the four clutches C1 ) C3, C4 and two brakes B1, B2, The input shaft IS is directly connected to the first planetary carrier PC1 and the second and third sun gears S2 and S3 are directly connected and the third planetary carrier PC3 and the second ring gear R2 In a state where the second planetary carrier PC2 is connected to the output gear OG and the first sun gear S1 is directly connected to the transmission housing H, The first clutch C1 connects the input shaft IS and the second sun gear S2, The second clutch C2 connects the first planetary carrier PC1 and the third ring gear R3, The third clutch C3 connects the first ring gear R1 and the third sun gear S3, The fourth clutch C4 connects the first ring gear R1 and the third planetary carrier PC3, The first brake B1 connects the third ring gear R3 and the transmission housing H together with the one-way clutch F1, , And the second brake (B2) connects the second sun gear (S2) and the transmission housing (H).

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