KR101028558B1 - Gear train of automatic transmission for vehicles - Google Patents

Abstract

The present invention combines two single pinion planetary gear sets and a combination of planetary type planetary gear sets with three clutches and three brakes to implement eight forward speeds and one reverse speed, thereby improving power transmission performance and improving fuel economy. It provides a gear train of an automatic transmission for a vehicle that can be reduced.

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

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 two simple planetary gear sets and one compound planetary gear set 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 in order to meet the development of the automatic transmission as described above, and an object of the present invention is to replace two simple planetary gear sets and one compound planetary gear set with three clutches and three brakes. By combining the eight forward speed and one reverse speed, it is possible to provide a gear train of an automatic transmission for a vehicle to improve power transmission performance and reduce fuel economy.

In order to achieve the above object, the present invention provides a first and second planetary gear set (PG1) (PG2) consisting of a simple planetary gear set each having three rotating elements, and a composite planetary gear having four rotating elements. In the gear train of the automatic transmission for a vehicle made of a combination of a third planetary gear set (PG3) consisting of a set,

The first planetary gear set PG1 is directly connected to the input shaft IS and always operates as an input element. The first planetary gear set PG1 and the third planetary gear set PG3 operate as an optional fixed element. The second rotating element (N2) is directly connected to any one of the rotating element of the) and, optionally acting as a fixed element and is connected to any one of the rotating element of the second planetary gear set (PG2) A third rotating element N3,

The second planetary gear set PG2 is directly connected to the input shaft IS to always operate as an input element, and a fourth rotating element N4 and selectively connected to the third rotating element N3 to operate as an output element. A fifth rotating element N5 and a sixth rotating element N6 that always operates as a fixed element,

The third planetary gear set PG3 includes a seventh rotating element N7 directly connected to the second rotating element N2 and an eighth selectively connected to the input shaft IS to operate as an optional input element. A rotating element N8, a ninth rotating element N9 connected to the output gear OG and always operating as an output element, and a tenth rotating element selectively connected to the input shaft IS and operating as an optional input element. Provided is a gear train of an automatic transmission for a vehicle, including (N10).

The first, second and third planetary gear sets (PG1) (PG2) (PG3) are arranged in the above, with the first planetary gear set (PG1) in the center, and the third planetary gear set (PG3) on the engine side The second planetary gear set PG2 is disposed at the rear side.

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, 3 rotating element (N3) consists of a first ring gear (R1),

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

The third planetary gear set PG3 is composed of a combination of a single pinion planetary gear set and a double pinion planetary gear set, and is a lavender type planetary gear set sharing a planetary gear with a ring gear, and the seventh rotating element N7 is The fourth sun gear S4 meshed with the short pinion P2, the eighth rotation element N8 is the third ring gear R3, and the ninth rotation element N9 is the third planet carrier PC3, the tenth rotation. Element N10 is characterized in that it consists of a third sun gear S3 meshing with the long pinion P1.

The first, second, and third planetary gear sets PG1, PG2, and PG3 are combined with three clutches C1, C2, C3, and three brakes B1, B2, and B3.

The first rotary element N1 is directly connected to the input shaft IS and is directly connected to the fourth rotary element N4, and the second rotary element N2 is directly connected to the seventh rotary element N7. in,

The second rotating element N2 is selectively connected to the transmission housing H through the first brake B1, and the third rotating element N3 is connected to the transmission housing H via the second brake B2. And the eighth rotating element N4 is selectively connected to the transmission housing H via the third brake B3, and the seventh rotating element N7 is interposed through the first clutch C1. To the input shaft IS, and the eighth rotating element N8 is connected to the input shaft IS via the second clutch C2, and the third rotating element N3 is interposed to the third clutch C3. It is characterized in that the connection with the fifth rotating element (N5).

The third brake (B3) is characterized in that arranged in parallel with the one-way clutch (F1).

In the above-described gear train, the first clutch C1 and the third brake B3 operate at the first forward speed, and the first clutch C1 and the first brake B1 operate at the second forward speed. The first clutch C1 and the second brake B2 are operated in the inside, and the first and third clutches C1 and C3 are operated at the fourth forward speed, and the first and second clutches C1 and C2 at the fifth forward speed. At the 6th forward, the second and third clutches C2 and C3 are operated, at the 7th forward speed, the second clutch C2 and the second brake B2 are operated, and at the 8th forward speed, the second clutch C2 is operated. ) And the first brake B1 are operated, and in reverse, the third clutch C3 and the third brake B3 are operated to shift.

As described above, the first and second planetary gear sets PG1 and PG2 consisting of two simple planetary gear sets and the third planetary gear set PG3 consisting of a composite planetary gear set are three clutches C1 as friction elements. Combination of (C2) (C3) and three brakes (B1) (B2) (B3) to implement a shift stage of 8 forward speed and 1 reverse speed can improve the power transmission performance and fuel economy.

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 shows 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 three clutches. Clutch means comprising C1, C2, and C3, and brake means comprising 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 connected to an output element of the third planetary gear set PG3. Output through the output gear (OG), the third planetary gear set (PG3) is disposed on the engine side, the second planetary gear set (PG2) is disposed on the rear side based on the first planetary gear set (PG1). .

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 rotating elements consisting of a sun gear, a planet carrier, and a ring gear, as is well known.For 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.

In the first planetary gear set PG1, the first sun gear S1 is operated as an input element at all times as the first rotation element N1, and the first planet carrier PC1 is the second rotation element N2. It is configured to operate as an optional fixed element and at the same time as an optional output element, the first ring gear (R1) as a third rotating element (N3), configured to operate as an optional input element and a fixed element do.

To this end, the first sun gear S1, which is the first rotating element N1, is directly connected to the input shaft IS, and the first planet carrier PC1, which is the second rotating element N2, has a first brake B1. The first ring which is selectively connected to the transmission housing (H) via the first and at the same time is directly connected to the rotating element acting as an optional input element in the third planetary gear set (PG3), the first ring which is the third rotating element (N3) The gear R1 is selectively connected to the transmission housing H via the second brake B2 and selectively connected to the output element of the second planetary gear set PG3.

The second planetary gear set PG2 is a single-pinion planetary gear set, and has three rotating elements consisting of a sun gear, a planet carrier, and a ring gear, as is well known, and the sun gear is referred to as 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 second ring gear R2.

In the second planetary gear set PG2, the second sun gear S2 always operates as an input element as the fourth rotating element N4, and the second planetary carrier PC2 as the fifth rotating element N5. It operates as an output element at which the deceleration output is always performed, and the second ring gear R2 is operated as a fixed element at all times as the sixth rotation element N6.

To this end, the second sun gear S2, which is the fourth rotating element N4, is directly connected to the input shaft IS, and the second planetary carrier PC2, which is the fifth rotating element N5, uses the third clutch C3. The first ring gear R1, which is the third rotary element N3 of the first planetary gear set PG1, is selectively connected to each other, and the second ring gear R2, which is the sixth rotary element N6, is connected to the transmission. It is directly connected to the housing (H).

The third planetary gear set PG3 combines a single pinion planetary gear set and a double pinion planetary gear set, and is composed of a planetary type planetary gear set that shares a planetary carrier with a ring gear.

Accordingly, a ring gear, a planet carrier, and two sun gears are included. For convenience of description, the ring gear is engaged with the third ring gear R3, and the planet carrier is joined with the third planet carrier PC3 and the long pinion P1. The sun gear to be meshed with the third sun gear S3 and the short pinion P2 is referred to as a fourth sun gear S4.

The fourth sun gear S4 acts as an optional deceleration input element as the seventh rotation element N7, and the third ring gear R3 acts as an optional input element as the eighth rotation element N8. At the same time acting as an optional fixed element, the third planet carrier PC3 acts as an output element at all times as the ninth rotating element N9, and the third sun gear S3 acts as an optional input element.

To this end, the fourth sun gear S4, which is the seventh rotation element N3, is directly connected to the second rotation element N2, which is an output element of the first planetary gear set PG1, and the eighth rotation element N8. The third ring gear (R3) is a transmission housing via a third brake (B3) which is selectively connected to the input shaft (IS) via the second clutch (C2) and arranged in parallel with the one-way clutch (F1). Optionally connected with (H).

Although the third brake B3 is described in parallel with the one-way clutch F1, the one-way clutch F1 may be omitted.

The third planetary carrier PC3, which is the ninth rotation element N9, is directly connected to the output gear OG as an output element, and the third sun gear S3, which is the tenth rotation element N10, is a first clutch. It is selectively connected to the input shaft IS via (C1).

The rotational power of the engine transmitted from the input shaft IS is always input to each of the rotating elements N1 and N4 of the first and second planetary gear sets PG1 and PG2. 3 Two rotational elements (N7) (N8) of planetary gear set (PG3) are selectively input and shifted to 8 forward speed and 1 reverse speed by complementary operation, and through output gear (OG), the final output path. The output will be made.

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.

The third brake B3 including the first and second clutches C1 and C2 and the one-way clutch F1 is disposed at the front side of the third planetary gear set PG3 and the output gear OG. And the first brake B1 are disposed between the third planetary gear set PG3 and the first planetary gear set PG1, and the second brake B2 and the third clutch C3 are the first and second planetary gears. It is arranged between the sets PG1 and PG2.

By the arrangement of the friction elements as described above it is easy to form the hydraulic pipeline, each friction element is properly distributed arrangement, it is possible to minimize the imbalance due to the weight bias of the transmission.

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 two friction members at each shift stage operating. Can be.

That is, the first clutch C1 and the third brake B3 are operated at the first forward speed,

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

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

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

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

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

At the 7th forward speed, the second clutch C2 and the second brake B2 are operated,

At the 8th forward speed, the second clutch C2 and the first brake B1 are operated.

In reverse, the third clutch C3 and the third brake B3 are operated to shift.

Of course, the third brake B3 is described in the first forward speed, but when the one-way clutch F1 is applied as in the present embodiment, the one-way clutch F1 is moved instead of the third brake B3. The first speed can be realized, and at this time, the shifting feeling can be improved when shifting to the second speed.

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

The three vertical lines of the first planetary gear set PG1 are sequentially rotated from the left to the first sun gear S1 as the first 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 are the second sun gear S2, which is the fourth rotating element N4, and the second planetary carrier PC2, which is the fifth rotating element N5, and the sixth rotation, in order from the left. The second ring gear R2, 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 ring gears).

Four vertical lines of the third planetary gear set PG3 are sequentially rotated from the left to the fourth sun gear S4 as the seventh rotation element N7, the third ring gear R3 as the eighth rotation element N8, and the ninth rotation. The third planetary carrier PC3, which is the element N9, and the third sun gear S3, which is the tenth rotating element N10, are set to the gear ratio of the third planetary gear set PG3 (number of teeth / ring of the sun gear). Number of teeth).

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 third brake B3 are operated and controlled.

Accordingly, the rotational power of the input shaft IS is simultaneously input to the first rotating element N1 and the fourth rotating element N4 and simultaneously input to the tenth rotating element N10 by the operation of the first clutch C1. This is done.

At this time, in the third planetary gear set PG3, the eighth rotating element N8 is operated as the fixed element by the operation of the third brake B3 while the input is made to the tenth rotating element N10. , As much as D1 is output through the ninth rotation element N9 which is an output element while forming the first shift line SP1 and thus the maximum speed ratio (rotational speed of the input shaft IS / rotational speed of the output gear OG). }, The forward 1 speed shift of about "3.545" is achieved.

In the first forward speed shifting process as described above, the first planetary gear set PG1 is directly connected to the seventh rotation element N7 while the second rotation element N2 is being input to the first rotation element N1. The bar is connected while forming the first speed line PG1-1.

In addition, the second planetary gear set PG2 is operated by the sixth rotating element N6 as a fixed element in a state where an input is made to the fourth rotating element N4, and thus, the first speed line PG2-1. While outputting is made to the fifth rotating element N5 while forming the third clutch C3, the operation is not performed, and thus there is no influence on the shift.

Although the third brake B3 is operated in the first speed shifting process, when the one-way clutch F1 is applied as in the present invention, the one-way clutch is not operated even if the third brake B3 is not operated. It is a matter of course that the eighth rotating element (N8) can be operated as a fixed element by the operation of (F1).

[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 first brake B1 is controlled to operate.

Accordingly, the rotational power of the input shaft IS is simultaneously input to the first rotating element N1 and the fourth rotating element N4 and simultaneously input to the tenth rotating element N10 by the operation of the first clutch C1. This is done.

Then, in the first planetary gear set PG1, the second rotation element N2 is operated as a fixed element by the operation of the first brake B1 while the input is made to the first rotation element N1. Rotation is made while forming line PG1-2.

In addition, in the second planetary gear set PG2, the sixth planetary gear set PG2 is operated as the fixed element in the state in which the second planetary gear set PG2 is input to the fourth rotation element N4. Although the output is made to the fifth rotating element N5 while forming the first speed line PG2-1, the third clutch C3 does not operate, and thus does not affect the shift.

In addition, in the third planetary gear set PG3, the seventh rotation element N7 is operated as a fixed element by the operation of the first brake B1 while the input is made to the tenth rotation element N10. As the second shift line SP2 is formed, the output is made as much as D2 through the ninth rotation element N9 which is an output element. As a result, a forward two speed shift of about "1.909" is achieved.

[3 speed forward]

In the third forward speed, as shown in FIG. 2, the operation of the first brake B1 operated in the state of the second forward speed is released, and the second brake B2 is operated and controlled.

Accordingly, the rotational power of the input shaft IS is simultaneously input to the first rotating element N1 and the fourth rotating element N4 and simultaneously input to the tenth rotating element N10 by the operation of the first clutch C1. This is done.

Then, the first planetary gear set PG1 is rotated while the third speed line PG1-3 is formed by the operation of the second brake B2 while the first rotation element N1 is being input.

In addition, in the second planetary gear set PG2, the sixth rotation element N6 operates as a fixed element while the fourth rotation element N4 is input, and thus, the first speed line PG2-1. While outputting is made to the fifth rotating element N5 while forming the third clutch C3, the operation is not performed, and thus there is no influence on the shift.

In addition, in the third planetary gear set PG3, the seventh rotation element N7 is connected to the second rotation element N2 in a state where an input is made to the tenth rotation element N10. The deceleration output of the gear set PG1 is input to the seventh rotation element N7 to form the third shift line SP3.

As a result, as much as D3 is output through the ninth rotating element N9, which is an output element. As a maximum speed ratio (rotational speed of the input shaft IS / rotational speed of the output gear OG), a forward 3 of about 1.441 is achieved. Speed shifts will be made.

[4 forward speed]

In the fourth forward speed, as shown in FIG. 2, the operation of the second brake B2 operated in the third forward speed is released, and the third clutch C3 is operated and controlled.

Accordingly, the rotational power of the input shaft IS is simultaneously input to the first rotating element N1 and the fourth rotating element N4 and simultaneously input to the tenth rotating element N10 by the operation of the first clutch C1. This is done.

In this state, in the second planetary gear set PG2, the sixth rotation element N6 operates as the fixed element while the input is made to the fourth rotation element N4. The first speed line PG2- While forming 1), the output is made to the fifth rotating element N5. At this time, the third clutch C2 is operated, and the rotating power thereof is the third rotating element N3 of the first planetary gear set PG1. Will be input.

Then, in the first planetary gear set PG1, the deceleration output of the second planetary gear set PG2 is performed through the third rotary element N3 while the input shaft IS is input to the first rotary element N1. The bar is rotated while forming the fourth speed line PG1-4.

In the third planetary gear set PG3, the seventh rotation element N7 is connected to the second rotation element N2 in a state where an input is made to the tenth rotation element N10. As the deceleration output of the planetary gear set PG1 is input to the seventh rotation element N7, the fourth shift line SP4 is formed.

As a result, as much as D4 is output through the ninth rotating element N9, which is an output element. Four-speed shift will be achieved.

[5th forward]

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

Then, the rotational power of the input shaft IS is simultaneously input to the tenth and eighth rotating elements N10 and N8 of the third planetary gear set PG3 by the operation of the first and second clutches C1 and C2. In this state, the fifth speed shift line SP-5 is formed, and the output is made as much as D5 through the ninth rotation element N9 which is an output element, and thus the fifth speed shift is performed.

The first and second planetary gear sets PG1 and PG2 do not have any influence in the state of 5 forward speeds as described above.

[6th forward]

At the sixth forward speed, as shown in FIG. 2, the operation of the first clutch C1 operated in the state of the fifth forward speed is released, and the third clutch C3 is operated and controlled.

Accordingly, the rotational power of the input shaft IS is simultaneously inputted through the first rotating element N1 and the fourth rotating element N4 and simultaneously operated by the second clutch C2 to the eighth rotating element N8. Input is made.

In this state, in the second planetary gear set PG2, the sixth rotation element N6 operates as the fixed element while the input is made to the fourth rotation element N4. The first speed line PG2- While forming 1), the output is made to the fifth rotating element N5. At this time, the third clutch C2 is operated, and the rotating power thereof is the third rotating element N3 of the first planetary gear set PG1. Will be input.

Then, in the first planetary gear set PG1, the deceleration output of the second planetary gear set PG2 is performed through the third rotary element N3 while the input shaft IS is input to the first rotary element N1. The bar is rotated while forming the fourth speed line PG1-4.

In the third planetary gear set PG3, the seventh rotation element N7 is the second rotation element N2 in a state where an input is made to the eighth rotation element N8 by the operation of the second clutch C2. ), The deceleration output of the first planetary gear set PG1 is input to the seventh rotation element N7 to form a sixth transmission line SP6.

Accordingly, as much as D6 is output through the ninth rotating element N9, which is an output element. As a maximum speed ratio (rotational speed of the input shaft IS / rotational speed of the output gear OG), the forward 6 is about 0.808. Speed shifts will be made.

[7th forward]

In the seventh forward speed, as shown in FIG. 2, the operation of the third clutch C3 operated in the sixth forward speed is released, and the second brake B2 is operated and controlled.

Accordingly, the rotational power of the input shaft IS is simultaneously input to the first rotating element N1 and the fourth rotating element N4 and simultaneously input to the eighth rotating element N8 by the operation of the second clutch C2. This is done.

Then, the first planetary gear set PG1 is rotated while the third speed line PG1-3 is formed by the operation of the second brake B2 while the first rotation element N1 is being input.

In addition, in the second planetary gear set PG2, the sixth rotation element N6 operates as a fixed element while the fourth rotation element N4 is input, and thus, the first speed line PG2-1. While outputting is made to the fifth rotating element N5 while forming the third clutch C3, the operation is not performed, and thus there is no influence on the shift.

In addition, in the third planetary gear set PG3, the seventh rotation element N7 is connected to the second rotation element N2 in a state where an input is made to the eighth rotation element N8. The deceleration output of the gear set PG1 is input to the seventh rotation element N7 to form the seventh shift line SP7.

As a result, as much as D7 is output through the ninth rotating element N9, which is an output element. Speed shifts will be made.

[8th forward]

In the eighth forward speed, as shown in FIG. 2, the operation of the second brake B2 operated in the seventh forward speed is released, and the first brake B1 is operated and controlled.

Accordingly, the rotational power of the input shaft IS is simultaneously input to the first rotating element N1 and the fourth rotating element N4 and simultaneously input to the eighth rotating element N8 by the operation of the second clutch C2. This is done.

Then, in the first planetary gear set PG1, the second rotation element N2 is operated as a fixed element by the operation of the first brake B1 while the input is made to the first rotation element N1. Rotation is made while forming line PG1-2.

In addition, in the second planetary gear set PG2, the sixth planetary gear set PG2 is operated as the fixed element in the state in which the second planetary gear set PG2 is input to the fourth rotation element N4. Although the output is made to the fifth rotating element N5 while forming the first speed line PG2-1, the third clutch C3 does not operate, and thus does not affect the shift.

In addition, in the third planetary gear set PG3, the seventh rotation element N7 is operated as a fixed element by the operation of the first brake B1 while the input is made to the eighth rotation element N8. As much as D8 is output through the ninth rotation element N9 which is the output element while forming the second shift line SP2, the maximum speed ratio (rotational speed of the input shaft IS / rotational speed of the output gear OG). As a result, the eighth speed shift, which is the highest shift speed of "0.643", is achieved.

[apse]

In the reverse shift stage, as shown in FIG. 2, the third clutch C3 and the third brake B3 are operated and controlled.

Accordingly, the rotational power of the input shaft IS is simultaneously input to the first rotating element N1 and the fourth rotating element N4.

In this state, in the second planetary gear set PG2, the sixth rotation element N6 operates as the fixed element while the input is made to the fourth rotation element N4. The first speed line PG2- While forming 1), the output is made to the fifth rotating element N5. At this time, the third clutch C3 is operated, and the rotating power thereof is the third rotating element N3 of the first planetary gear set PG1. Will be input.

Then, in the first planetary gear set PG1, the deceleration output of the second planetary gear set PG2 is performed through the third rotary element N3 while the input shaft IS is input to the first rotary element N1. The bar is rotated while forming the fourth speed line PG1-4.

In addition, in the third planetary gear set PG3, the seventh rotation element N7 is the second rotation element in a state in which the eighth rotation element N8 is operated as the fixed element by the operation of the third brake B3. As it is connected to N2), the deceleration output of the first planetary gear set PG1 is input to the seventh rotation element N7 to form the reverse shift line SR.

Accordingly, as much as REV is output through the ninth rotating element N9, which is an output element, and a reverse shift of about -3.150 as a speed ratio ratio (rotational speed of the input shaft IS / rotational speed of the output gear OG). This will be done.

The shift ratios presented at the respective shift stages of the shifting process may include the number of teeth of the first sun gear S1 as the first rotating element N1 and the first ring gear R1 as the third rotating element N3 to 10 and 18. and,

The number of teeth of the second sun gear S2, which is the fourth rotating element N4, and the second ring gear R2, which is the sixth rotating element N6, is 10 and 20,

The number of teeth of the third sun gear S3, which is the seventh rotation element N7, the fourth sun gear S4, which is the tenth rotation element N10, and the third ring gear R3, which is the ninth rotation element N9, is 10, You can get it when you set 20 and 28.

Although a preferred embodiment of the gear train of the present invention has been described above, the present invention is not limited to the above embodiment, and those skilled in the art can easily invent the present invention from the embodiment of the present invention. It includes all changes to the extent considered equivalent.

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 according to the present invention.

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

Claims (8)

First and second planetary gear sets PG1 and PG2 each consisting of a simple planetary gear set having three rotating elements, and a third planetary gear set PG3 consisting of a composite planetary gear set having four rotating elements. In the gear train of the automatic transmission for a vehicle consisting of The first planetary gear set PG1 is directly connected to the input shaft IS and always operates as an input element. The first planetary gear set PG1 and the third planetary gear set PG3 operate as an optional fixed element. The second rotating element (N2) is directly connected to any one of the rotating element of the) and, optionally acting as a fixed element and is connected to any one of the rotating element of the second planetary gear set (PG2) A third rotating element N3, The second planetary gear set PG2 is directly connected to the input shaft IS to always operate as an input element, and a fourth rotating element N4 and selectively connected to the third rotating element N3 to operate as an output element. A fifth rotating element N5 and a sixth rotating element N6 that always operates as a fixed element, The third planetary gear set PG3 includes a seventh rotating element N7 directly connected to the second rotating element N2 and an eighth selectively connected to the input shaft IS to operate as an optional input element. A rotating element N8, a ninth rotating element N9 connected to the output gear OG and always operating as an output element, and a tenth rotating element selectively connected to the input shaft IS and operating as an optional input element. A gear train of an automatic transmission for a vehicle, characterized by comprising (N10). According to claim 1, wherein the first, second and third planetary gear sets (PG1) (PG2) (PG3) are disposed, with the first planetary gear set (PG1) in the center, the third planetary gear set (PG3) A gear train for an automatic transmission for a vehicle, characterized by being disposed on the engine side, and the second planetary gear set PG2 disposed on the rear side. 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 a first ring gear (R1), The second planetary gear set PG2 is a single pinion planetary gear set. The fourth rotating element N4 is the second sun gear S2, and the fifth rotating element N5 is the second planetary carrier PC2, the sixth rotation. Element N6 consists of a second ring gear R2, The third planetary gear set PG3 is composed of a combination of a single pinion planetary gear set and a double pinion planetary gear set, and is a lavender type planetary gear set sharing a planetary gear with a ring gear, and the seventh rotating element N7 is The fourth sun gear S4 meshed with the short pinion P2, the eighth rotation element N8 is the third ring gear R3, and the ninth rotation element N9 is the third planet carrier PC3, the tenth rotation. Element N10 is a gear train of an automatic transmission for a vehicle, characterized in that it consists of a third sun gear (S3) meshing with the long pinion (P1). 4. The first, second and third planetary gear sets PG1, PG2 and PG3 have three clutches C1, C2 and C3 and three brakes B1 and B2. ) (B3), The first rotary element N1 is directly connected to the input shaft IS and is directly connected to the fourth rotary element N4, and the second rotary element N2 is directly connected to the seventh rotary element N7. in, The second rotating element N2 is selectively connected to the transmission housing H through the first brake B1, and the third rotating element N3 is connected to the transmission housing H via the second brake B2. And the eighth rotary element N8 is selectively connected to the transmission housing H via the third brake B3, and the seventh rotary element N7 is interposed through the first clutch C1. To the input shaft IS, and the eighth rotating element N8 is connected to the input shaft IS via the second clutch C2, and the third rotating element N3 is interposed to the third clutch C3. The gear train of the automatic transmission for a vehicle, characterized in that the connection with the fifth rotating element (N5). The gear train of claim 4, wherein the third brake (B3) is arranged in parallel with the one-way clutch (F1). The method of claim 4, wherein the first clutch (C1) and the third brake (B3) is activated at the first forward speed, At the second forward speed, the first clutch C1 and the first brake B1 are operated. At the third forward speed, the first clutch C1 and the second brake B2 are operated. At the 4th forward speed, the first and third clutches C1 and C3 are operated. At the 5th forward speed, the first and second clutches C1 and C2 are operated. At the sixth forward speed, the second and third clutches C2 and C3 are operated. At the 7th forward speed, the second clutch C2 and the second brake B2 are operated. At the 8th forward speed, the second clutch C2 and the first brake B1 are operated. The reverse gear train of the vehicle automatic transmission, characterized in that the shift is made while the third clutch (C3) and the third brake (B3) is 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 single pinion planetary gear set including a second sun gear S2, a second planet carrier PC2, and a second ring gear R2; A combination of a single pinion planetary gear set and a double pinion planetary gear set, but a combination of ring gear and planetary carrier type planetary gear set, the third sun gear (S3) and third meshing with the long pinion P1 The third planetary gear set PG3 including the planet carrier PC3, the third ring gear R3, and the fourth sun gear S4 meshed with the short pinion P2 includes three clutches C1 and C2 ( C3) and three brakes (B1) (B2) (B3), The first sun gear S1 is directly connected to the input shaft IS and is directly connected to the second sun gear S2, and the first planet carrier PC1 is directly connected to the fourth sun gear S4, and the third planet is Carrier PC3 is directly connected to the output gear OG. The first planet carrier PC1 is connected to the transmission housing H via the first brake B1, and the first ring gear R1 is connected to the transmission housing H via the second brake B2. At the same time, the fifth rotary element N5 and the third clutch C3 are connected to each other, the second ring gear R2 is directly connected to the transmission housing H, and the third sun gear S1 is connected to the first. The third ring gear R3 is connected to the input shaft IS via the clutch C1, and the third ring gear R3 is connected to the input shaft IS via the second clutch C3 and is interposed with the third brake B3. Gear train of the automatic transmission for a vehicle, characterized in that the connection is made to the transmission housing (H). 8. A gear train according to claim 7, wherein the third brake (B3) is arranged in parallel with the one-way clutch (F1).

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