KR101338425B1 - Gear train of automatic transmission for vehicles - Google Patents

Abstract

The present invention combines a second planetary gearset consisting of a first planetary gearset combining two simple planetary gearsets and a planetary planetary gearset of a rib type with five clutches and two brakes. The present invention provides a gear train of an automatic transmission for a vehicle that can improve power transmission performance and reduce fuel consumption.

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 combines a second planetary gear set consisting of a first planetary gear set combining two simple planetary gear sets and a planetary planetary gear set of a rib type with five clutches and two brakes to implement a shift speed of 10 forward speeds. It relates to a gear train of an automatic transmission for a vehicle.

The multi-speed shifting mechanism of the automatic transmission is usually implemented by combining a plurality of planetary gear sets. The gear train in which the plurality of planetary gear sets are combined has a function of receiving rotational power from the torque converter and shifting it to the output shaft .

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.

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

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

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 to meet the development of the automatic transmission as described above, and an object of the present invention is a planetary gear set of a first planetary gear set and a combination of two simple planetary gear sets. By combining the second planetary gear set consisting of five clutches and two brakes to implement 10 forward speeds and 3 reverse speeds, it is possible to improve power transmission performance, reduce fuel consumption, and improve reverse shift performance. To provide a gear train of a vehicle automatic transmission.

In order to achieve the above object, the present invention, as in claim 1, combines the first and second simple planetary gear set (SPG1) (SPG2), the first sun gear (S1) and the second planetary carrier ( PC1) and the first rotational element (N1) which is composed of the second sun gear (S2) and always acts as a fixed element in a state in which the first planetary carrier (PC1) and the second ring gear (R2) are directly connected. ), A second rotating element (N2) formed of a first planetary carrier (PC1) and a second ring gear (R2) to form a first intermediate output path (MOP1), and the first ring gear (R1) 2 consists of a third rotating element (N3) forming the intermediate output path (MOP2), the first sun gear (S1) and the second planet carrier (PC2) to form an input path (IP) connected to the input shaft (IS). And a first planetary gear set PG1 having a fourth rotating element N4 for forming a third intermediate output path for outputting the input as it is.

A combination of a single pinion planetary gear set and a double pinion planetary gear set, but a planetary planetary gear set sharing a planetary carrier with a ring gear, comprising a third sun gear (S3) meshing with the long pinion (P1). A first variable input path VIP1 variably connected to the first intermediate output path MOP1, a second variable input path VIP2 variably connected to the second intermediate output path MOP2, and the third intermediate output path MOP1. The fifth rotating element N5 and the third planetary carrier PC3, which form a third variable input path VIP3 variably connected to the MOP3 and act as an optional fixed element, are composed of an input shaft IS and A fourth variable input path VIP4 that is variably connected and a sixth rotating element N6 operating as an optional fixed element and a third ring gear R3 are directly connected to the output shaft OS. A fourth rotating gear N7 and a fourth sun gear forming a final output path OP A second planetary gear set PG2 configured to have an eighth rotating element N8 which is formed of S4 to form a fifth variable input path VIP5 variably connected to the first intermediate output path MOP1;

A plurality of clutches C1, C2, C3, C4 and C5 disposed in the first, second, third, fourth and fifth variable input paths VIP1 to VIP5; A gear train of an automatic transmission for a vehicle including a friction member including a plurality of brakes B1 and B2 disposed between the transmission housings H is provided.

In forming the first planetary gear set PG1, as in claim 2, the first simple planetary gear set SPG is a double pinion planetary gear set, and the second simple planetary gear set SPG2 is a single pinion. It is characterized by consisting of a planetary gear set.

The friction member may include a first clutch C1 disposed on a fifth variable input path VIP5 as in claim 3; A second clutch C2 disposed on the first variable input path VIP1; A third clutch C3 disposed on the second variable input path VIP2; A fourth clutch C4 disposed on the third variable input path VIP3; A fifth clutch C5 disposed on the fourth variable input path VIP4; A first brake B1 disposed between the third planet carrier PC3 and the transmission housing H; It characterized in that it comprises a second brake (B2) disposed between the third sun gear (S3) and the transmission housing (H).

In the above friction member, as in claim 4, the first clutch C1 and the first brake B1 are operated at the first forward speed, and the first clutch C1 and the second brake at the second forward speed. B2) is activated, the first and second clutches C1 and C2 are operated at the third forward speed, and the first and third clutches C1 and C3 are operated at the fourth forward speed and the first at the fifth forward speed. , 4 clutches C1 and C4 are operated, first and fifth clutches C1 and C5 are operated at 6 forward speeds, and 4 and 5 clutches C4 and C5 are operated at 7 forward speeds, The third and fifth clutches C3 and C5 are operated at the eighth forward speed, and the second and fifth clutches C2 and C5 are operated at the nineth forward speed, and the fifth clutch C5 is operated at the tenth forward speed. The second brake B2 is activated, the second clutch C2 and the first brake B1 are operated at the reverse speed 1, and the third clutch C3 and the first brake B1 are operated at the reverse speed 2. In addition, the fourth clutch (C4) and the first brake (B1) is operated at the third reverse speed is characterized in that the shift is made. It is gong.

In arranging the friction member, as in claim 5, the third clutch C3 is disposed in front of the first planetary gear set PG1, and the first, second and third clutches C1 and C2. (C3) and the first and second brakes B1 and B2 are disposed between the first planetary gear set PG1 and the second planetary gear set PG2, and the fifth clutch C5 is the third planetary gear set. It is characterized in that it is disposed behind (PG3).

The first planetary gear set PG1 combining two simple planetary gear sets SPG1 and SPG2 as described above, and the second planetary gear set PG2 consisting of a planetary gear set of the cage type, have five clutches C1. (C2) (C3) (C4) (C5) combined with two brakes (B1) and (B2) to realize the gearshifts of 10 forward and 3 reverse speeds to improve power transmission performance and fuel economy. do.

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

In addition, by shifting the two friction elements in each shift stage while operating, it is possible to reduce the capacity of the oil pump and increase the hydraulic control efficiency.

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

 1 illustrates an embodiment of a power train according to the present invention, wherein the gear train of the present invention comprises a first planetary gear set PG1 formed by combining first and second simple planetary gear sets SPG1 and SPG2. And a second planetary gear set PG2 composed of a planetary planetary gear set on the same axis, and rotating elements thereof are set to five clutches C1, C2, C3, C4 and C5. And two brakes B1 and B2.

Accordingly, the rotation input from the input shaft IS is shifted through the first and second planetary gear sets PG1 and PG2 and output through the output shaft OS. The first planetary gear set PG1 is an engine. And the second planetary gear set PG2 is disposed sequentially.

Further, in arranging the first and second simple planetary gear sets SPG1 and SPG2 constituting the first planetary gear set PG1, the second simple planetary gear set SPG2 is disposed on the engine side, and then to the rear side. The first simple planetary gear set SPG1 is disposed.

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 while torque conversion is performed through the torque converter, and the output shaft OS is not shown as the output member. The drive wheel is driven through a known gear through an output gear.

The first simple planetary gear set SPG1 constituting the first planetary gear set PG1 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 described. For convenience, the sun gear is referred to as a first sun gear S1, a planet carrier as a first planet carrier PC1, and a ring gear as a first ring gear R1.

The second simple planetary gear set PG2 constituting 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 known. For convenience of description, the sun gear is referred to as a second sun gear S2, the planet carrier is referred to as a second planet carrier PC2, and the ring gear is referred to as a second ring gear R2.

In combining the first and second simple planetary gear sets SPG1 and SPG2 as described above, the first sun gear S1 and the second planet carrier PC2 are directly connected, and the first planet carrier PC1 The second ring gear R2 is directly connected.

Accordingly, the first rotating element N1 made of the second sun gear S2, the second rotating element N2 made of the first planetary carrier PC1 and the second ring gear R2, and the first ring gear And a third rotating element N3 made of R1, and a fourth rotating element made of the first sun gear S1 and the second planet carrier PC2.

The first rotating element N1 is always fixedly connected to the transmission housing H to always operate as a fixed element, and the second rotating element N2 forms a first intermediate output path MOP1. The third rotating element N3 forms the second intermediate output path MOP2, and the fourth rotating element N4 is directly connected to the input shaft IS to form the input path IP and at the same time, The third intermediate output path MOP3 to be output is formed.

The second planetary gear set PG2 is a combination of a single pinion planetary gear set and a double pinion planetary gear set, but a planetary planetary gear set sharing a planetary carrier with a ring gear. 3 The sun gear that meshes the ring gear R3 and the planetary carrier with the third planet carrier PC3 and the long pinion P1 is connected to the third sun gear S3 and the short pinion P2, and the fourth sun gear S4. It is referred to as).

The fifth rotating element N5 including the third sun gear S3 may include a first variable input path VIP1 variably connected to the first intermediate output path MOP1, and the second intermediate output path S3. A second variable input path (VIP2) variably connected to MOP2) and a third variable input path (VIP3) variably connected to the third intermediate output path (MOP3) are formed and are operated as an optional fixed element. Done.

In addition, the sixth rotary element N6 is formed as the third planetary carrier PC3 and forms a fourth variable input path VIP4 that is variably connected to the input shaft IS. The seventh rotation element N4 formed of the third ring gear R3 forms a final output path OP directly connected to the output shaft OS, and the eighth rotation element formed of the fourth sun gear S4 N8) forms a fifth variable input path VIP5 that is variably connected to the first intermediate output path MOP1.

A second clutch C2 is disposed in the first variable input path VIP1 such that an output of the first intermediate output path MOP1 is a fifth rotating element N5 according to the operation of the second clutch C2. It is transmitted to the third sun gear S3.

A third clutch C3 is disposed in the second variable input path VIP2 such that an output of the second intermediate output path MOP2 is a fifth rotating element N5 according to the operation of the third clutch C3. It is transmitted to the third sun gear S3.

A fourth clutch C4 is disposed in the third variable input path VIP3 such that an output of the third intermediate output path MOP3 is a fifth rotating element N5 according to the operation of the fourth clutch C4. It is transmitted to the third sun gear S3.

A fifth clutch C5 is disposed in the fourth variable input path VIP4 such that the rotational force of the input shaft IS is the sixth rotation element N6 according to the operation of the fifth clutch C5. Delivered to a carrier PC3.

A first clutch C1 is disposed in the fifth variable input path VIP5 such that an output of the first intermediate output path MOP1 is an eighth rotary element N8 according to the operation of the first clutch C1. It is transmitted to the fourth sun gear S4.

In addition, the first brake B1 is connected between the third planet carrier PC3 and the transmission housing H such that the third planet carrier PC3, which is the sixth rotating element N6, may operate as an optional fixing element. Is disposed, and the second brake (B2) is provided between the third sun gear (S3) and the transmission housing (H) so that the third sun gear (S3), the fifth rotating element (N5), can operate as an optional fixing element. Is placed.

The order (first, second, third, ...) assigned to each clutch and brake is for distinguishing each clutch and brake, and the order is determined by first operating in the process of shifting up from the first forward speed. There is no meaning other than meaning.

The rotational power of the engine transmitted from the input shaft IS is shifted to 10 forward speeds and 3 reverse speeds while passing through the first and second planetary gear sets PG2. The output is made through the output shaft OS.

In the above, the friction element consisting of the first, second, third, fourth and fifth clutches C1, C2, C3, C4 and C5 and the first and second brakes B1 and B2 is frictionally coupled by hydraulic pressure. It is customary to consist of a multi-plate hydraulic friction engagement unit.

In the above, the third clutch C3 is disposed in front of the first planetary gear set PG1, and the first, second, and third clutches C1, C2, C3 and the first and second brakes B1 are provided. B2 is disposed between the first planetary gear set PG1 and the second planetary gear set PG2, and the fifth clutch C5 is disposed behind the second planetary gear set PG2.

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

FIG. 2 is an operation table showing that a friction member, that is, a clutch and a brake, operating at respective speed change stages, according to the present invention is operated. In the gear train of the present invention, .

That is, the first clutch C1 and the first brake B1 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 third clutches C1 and C3 are operated at four forward speeds,

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

The first and fifth clutches C1 and C5 are operated at six forward speeds,

The fourth and fifth clutches C4 and C5 are operated at seven forward speeds,

The third and fifth clutches C3 and C5 are operated at eight forward speeds,

The second and fifth clutches C2 and C5 are operated at 9 forward speeds,

At the 10th forward speed, the fifth clutch C5 and the second brake B2 are operated.

In the first reverse speed, the second clutch C2 and the first brake B1 are operated.

At the second reverse speed, the third clutch C3 and the first brake B1 are operated.

When the fourth clutch C4 and the first brake B1 are operated at the third reverse speed, shifting is performed.

Will be done.

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 four vertical lines of the first planetary gear set PG1 have a second sun gear S2, which is the first rotating element N1, and a first planet carrier PC1, which is the second rotating element N2, and a second ring, in order from the left. The gear R2, the first ring gear R1 as the third rotating element N3, the first sun gear S1 as the fourth rotating element N4 and the second planet carrier PC2 are set. The gear ratio of the first planetary gear set PG1 (the number of teeth of the sun gear / the number of rings of the ring gear) is determined.

The four vertical lines of the second planetary gear set PG2 are sequentially rotated from the left side to the third sun gear S3 as the fifth rotating element N5, the third planet carrier PC3 as the sixth rotating element N6 and the seventh rotation. The third ring gear R3, which is the element N7, and the fourth sun gear S4, which is the eighth rotary element N8, are set at the gear ratio of the second planetary gear set PG2 (number of teeth / ring of the sun gear). Number of teeth).

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.

[1st speed forward]

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

Accordingly, in the first planetary gear set PG1, the first rotary element N1 operates as a stationary element while the first rotary element N1 is input to the fourth rotary element N4 forming the input path IP. 2 Deceleration output is made through the intermediate output path (MOP1) (MOP2), and output is output as it is through the third intermediate output path (MOP3), the operation of the first planetary gear set (PG1) is a full shift. It is done in stages.

In this state, the first clutch C1 is operated so that the output of the first intermediate output path MOP1 is the eighth rotary element of the second planetary gear set PG2 through the fifth variable input path VIP5. An input is made to the fourth sun gear S4, N8).

As described above, the sixth rotation element N6 is operated as a fixed element by the operation of the first brake B1 in the state where the input is made to the eighth rotation element N8. It is to form a, as the output of the first shift line (SP1) and the vertical line of the seventh rotation element (N7) that is the output element is made as D1 is to be made the first forward speed shift.

[2 speed forward]

At the 2nd forward speed, the operation of the 1st brake B1 is canceled in the state of 1st forward speed, and the 2nd brake B2 is operationally controlled.

Then, the fifth rotation element N5 is operated as a fixed element by the operation of the second brake B2 in the state where the input is made to the eighth rotation element N8 as in the first forward speed. A line SP2 is formed, and as the output of D2 intersects the vertical line of the second shift line SP2 and the seventh rotation element N7, which is an output element, the second forward shift is made.

[3 speed forward]

At the third forward speed, as shown in FIG. 2, the second brake B2 is released from the second forward speed, and the second brake C2 is controlled to operate.

Then, the output of the first intermediate output path MOP1 of the first planetary gear set PG1 is simultaneously transmitted to the fifth rotary element N5 and the eighth rotary element N8 of the first and second clutches C1 and C2. As it is input, the entire second planetary gear set PG2 is directly connected to form a third transmission line SP3, and the third transmission line SP3 and the seventh rotation element N7 which is an output element. As the output of D3 intersecting the vertical line of is made, 3 forward speed is made.

[4 forward speed]

In the fourth forward speed, as shown in FIG. 2, the operation of the second clutch C2 operated in the state of the third forward speed is released, and the third clutch C3 is operated and controlled.

Then, as described above, the rotational power of the second intermediate output path MOP2 is changed to the second variable input path VIP2 by the operation of the third clutch C3 while the input is made to the eighth rotation element N8. The fourth transmission line SP4 is formed through the fifth rotation element N5 through the complementary operation, and the vertical line of the fourth transmission line SP4 and the seventh rotation element N7 which is an output element. As the output of this crossover D4 is made, the forward four-speed shift is made.

[5th forward]

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

Then, as described above, the rotational power of the third intermediate output path MOP3, which is the input of the input shaft IS, is maintained by the operation of the fourth clutch C4 in the state where the input is made to the eighth rotating element N8. The fifth transmission line SP5 is transmitted to the fifth rotation element N5 through the variable input path VIP3 to form a fifth transmission line SP5 through complementary operation, and the fifth transmission line SP5 and the seventh output element. As the output of D5 crossing the vertical line of the rotating element N7 is made, the forward five-speed shift is made.

[6th forward]

At the sixth forward speed, as shown in FIG. 2, the operation of the fourth clutch C4 operated in the state of the fifth forward speed is released, and the fifth clutch C5 is operated and controlled.

Then, as described above, the rotational power of the input shaft IS is rotated sixth through the fourth variable input path VIP4 by the operation of the fifth clutch C5 while the input is made to the eighth rotating element N8. The sixth shift line SP6 is formed by the complementary operation of the sixth shift line SP6, and the vertical line of the sixth shift line SP6 and the seventh rotation element N7 that is an output element crosses each other. As long as the output is achieved, 6 forward speed is achieved.

[7th forward]

In the seventh forward speed, as shown in FIG. 2, the operation of the first clutch C1 operated from the first forward speed to the sixth forward speed is released, and the fourth clutch C4 is operated and controlled.

Then, as in the sixth forward speed, the rotational power of the input shaft IS is input to the sixth rotation element N6 through the fourth variable input path VIP4 by the operation of the fifth clutch C5. 4 The rotational power of the third intermediate output path MOP3, which is the same as the input from the input shaft IS, is input to the fifth rotating element N5 through the third variable input path VIP3 by the operation of the clutch C4. As the entire second planetary gear set PG2 is directly connected, the seventh transmission line SP7 is formed, and the seventh transmission line SP7 and the vertical line of the seventh rotation element N7 that is an output element intersect each other. As much as D7 output is achieved, the input 7-speed shift is made as it is.

[8th forward]

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

Then, in the state where the rotational power of the input shaft IS is input to the sixth rotation element N6 through the fourth variable input path VIP4 by the operation of the fifth clutch C5 as in the forward seventh speed. The rotational power of the second intermediate output path MOP2 is input to the fifth rotating element N5 through the second variable input path VIP2 by the operation of the clutch C3. An eighth shift line SP8 connecting the sixth rotation element N6 is formed, and as much as D8 at which the eighth shift line SP8 intersects the vertical line of the seventh rotation element N7 which is an output element. As this is achieved, eight forward speed shifts are achieved.

[9 speed forward]

At the 9th forward speed, as shown in FIG. 2, the operation of the third clutch C3 is released in the state of the 8th forward speed, and the second clutch C2 is controlled to operate.

Then, as in the eighth forward speed, in the state in which the rotational power of the input shaft IS is input to the sixth rotation element N6 through the fourth variable input path VIP4 by the operation of the fifth clutch C5. The rotational power of the first intermediate output path MOP1 is input to the fifth rotating element N5 through the first variable input path VIP1 by the operation of the clutch C2. A ninth shift line SP9 connecting the sixth rotation element N6 is formed, and the output is as much as D9 where the ninth shift line SP9 intersects the vertical line of the seventh rotation element N7 which is an output element. As this is achieved, the speed change is performed as it is.

[10 speed forward]

At the 10th forward speed, as shown in FIG. 2, the second clutch C2 is released from the 9th forward speed, and the second brake B2 is controlled to operate.

Then, in the state where the rotational power of the input shaft IS is input to the sixth rotation element N6 through the fourth variable input path VIP4 by the operation of the fifth clutch C5 as in the forward 9 speed. The fifth rotating element N5 is operated as a fixed element by the operation of the brake B2. A tenth transmission line SP10 connecting the fifth rotating element N5 and the sixth rotating element N6 is provided. It is formed, the output of the 10th shift line (SP10) and the vertical line of the seventh rotation element (N7) of the output element is made as much as the output D10 is made as the forward 10-speed shift as it is.

[1 speed reverse]

In the reverse 1 speed shift stage, as shown in FIG. 2, the second clutch C2 and the first brake B1 are operated and controlled.

Accordingly, in the first planetary gear set PG1, the first rotary element N1 operates as a stationary element while the first rotary element N1 is input to the fourth rotary element N4 forming the input path IP. 2 The deceleration output is made through the intermediate output path MOP1 and MOP2, and the output is output as it is through the third intermediate output path MOP3.

Then, in the second planetary gear set PG2, the rotational power of the first intermediate output path MOP1 is input to the fifth rotating element N5 through the first variable input path VIP1 by the operation of the second clutch C2. When the sixth rotating element N6 is operated as a fixed element by the operation of the first brake B1, the reverse agent connecting the fifth rotating element N5 and the sixth rotating element N6. The first shift line SR1 is formed, and the reverse first speed shift is performed as much as the reverse rotation output of REV1 where the longitudinal first shift line SR1 intersects the vertical line of the seventh rotation element N7 as the output element. Will be done.

[2 speed reverse]

In the second reverse speed, as shown in FIG. 2, the second clutch C2 is released from the reverse first speed shift stage, and the third clutch C3 is controlled to operate.

Then, in the second planetary gear set PG2, the rotational power of the second intermediate output path MOP2 is input to the fifth rotating element N5 through the second variable input path VIP2 by the operation of the third clutch C3. When the sixth rotating element N6 is operated as a fixed element by the operation of the first brake B1, the reverse agent connecting the fifth rotating element N5 and the sixth rotating element N6. The second shift line SR2 is formed, and the reverse two-speed shift is performed as much as the reverse rotation output of REV2 where the reverse second shift line SR2 and the vertical line of the seventh rotation element N7 that is the output element intersect. Will be done.

[3 reverse speed]

In the third reverse speed, as shown in FIG. 2, the third clutch C3 is released from the reverse second speed shift stage, and the fourth clutch C4 is operated and controlled.

Then, in the second planetary gear set PG2, the rotational power of the third intermediate output path MOP3 is input to the fifth rotating element N5 through the third variable input path VIP3 by the operation of the fourth clutch C4. When the sixth rotating element N6 is operated as a fixed element by the operation of the first brake B1, the reverse agent connecting the fifth rotating element N5 and the sixth rotating element N6. The third shift line SR3 is formed, and the reverse third speed shift is performed as much as the reverse rotation output of REV3 in which the vertical third shift line SR3 and the vertical line of the seventh rotation element N7 that are the output elements intersect. Will be done.

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.

As an example, it is easy for those skilled in the art to arrange a one-way brake in parallel with the first brake B1 so that the one-way clutch is operated without operating the first brake B1 at the first forward speed. As a matter of course, it is included in the present invention.

1 is a block diagram of a gear train according to the present invention;

Figure 2 is a shift-specific operation of the friction member applied to the gear train of the present invention.

3 is a shift diagram of a gear train according to the present invention.

Claims (5)

Combining the first and second simple planetary gear sets (SPG1) (SPG2), directly connecting the first sun gear (S1) and the second planetary carrier (PC2), the first planetary carrier (PC1) and the second ring gear It consists of a first rotating element (N1) that always operates as a fixed element made of a second sun gear (S2) in the state directly connected (R2), the first planetary carrier (PC1) and a second ring gear (R2) A second rotating element N2 forming the first intermediate output path MOP1, a third rotating element N3 consisting of the first ring gear R1 forming the second intermediate output path MOP2, and A fourth rotating element formed of a first sun gear S1 and a second planetary carrier PC2 to form an input path IP connected to the input shaft IS and a third intermediate output path for outputting the input as it is; A first planetary gear set PG1 having N4); A combination of a single pinion planetary gear set and a double pinion planetary gear set, but a planetary planetary gear set sharing a planetary carrier with a ring gear, comprising a third sun gear (S3) meshing with the long pinion (P1). A first variable input path VIP1 variably connected to the first intermediate output path MOP1, a second variable input path VIP2 variably connected to the second intermediate output path MOP2, and the third intermediate output path MOP1. The fifth rotating element N5 and the third planetary carrier PC3, which form a third variable input path VIP3 variably connected to the MOP3 and act as an optional fixed element, are composed of an input shaft IS and A fourth variable input path VIP4 that is variably connected and a sixth rotating element N6 operating as an optional fixed element and a third ring gear R3 are directly connected to the output shaft OS. A fourth rotating element N7 and a fourth winding machine forming a final output path OP Made up (S4) and the second planetary gear set (PG2) to hold the eighth rotary element (N8) to form the first intermediate output path (MOP1) and variable fifth variable input path (VIP5) is connected to; A plurality of clutches C1, C2, C3, C4 and C5 disposed in the first, second, third, fourth and fifth variable input paths VIP1 to VIP5; A gear train of an automatic transmission for a vehicle, comprising a friction member consisting of a plurality of brakes B1 and B2 disposed between the transmission housings H. 2. The gear train of claim 1, wherein the first simple planetary gear set (SPG) comprises a double pinion planetary gear set and the second simple planetary gear set (SPG2) consists of a single pinion planetary gear set. The friction member of claim 1, further comprising: a first clutch (C1) disposed on a fifth variable input path (VIP5); A second clutch C2 disposed on the first variable input path VIP1; A third clutch C3 disposed on the second variable input path VIP2; A fourth clutch C4 disposed on the third variable input path VIP3; A fifth clutch C5 disposed on the fourth variable input path VIP4; A first brake B1 disposed between the third planet carrier PC3 and the transmission housing H; And a second brake (B2) disposed between the third sun gear (S3) and the transmission housing (H). The method of claim 3, wherein the friction member At the first forward speed, the first clutch C1 and the first brake B1 are operated, 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 third clutches C1 and C3 are operated at four forward speeds, The first and fourth clutches C1 and C4 are operated at five forward speeds, The first and fifth clutches C1 and C5 are operated at six forward speeds, The fourth and fifth clutches C4 and C5 are operated at seven forward speeds, The third and fifth clutches C3 and C5 are operated at eight forward speeds, The second and fifth clutches C2 and C5 are operated at 9 forward speeds, At the 10th forward speed, the fifth clutch C5 and the second brake B2 are operated. In the first reverse speed, the second clutch C2 and the first brake B1 are operated. At the second reverse speed, the third clutch C3 and the first brake B1 are operated. When the fourth clutch C4 and the first brake B1 are operated at the third reverse speed, shifting is performed. Gear train of an automatic transmission for a vehicle, characterized in that made. The method of claim 3, wherein in arranging the friction member, the third clutch C3 is disposed in front of the first planetary asset asset PG1, and the first, second and third clutches C1, C2, and C3. And the first and second brakes B1 and B2 are disposed between the first planetary gear set PG1 and the second planetary gear set PG2, and the fifth clutch C5 is the third planetary gear set PG3. The gear train of the automatic transmission for a vehicle, characterized in that arranged in the rear of the.

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