KR100907066B1 - Gear train of car automatic transmission - Google Patents

Abstract

A gear train of automatic transmission for vehicles is provided to reduce gas mileage by arranging a plurality of frictional elements dispersively. The first planetary gear set(PG1) comprises the first rotation element(N1), and the second rotation element(N2) and the third rotation element(N3). The second planet gear set(PG2) comprises the fourth rotation element(N4), and the fifth rotation element(N5) and sixth rotation element(N6). The third planetary gear set(PG3) holds the seventh rotation element(N7), the eighth rotation element(N8), and the ninth rotation element(N9) and the tenth rotation element(N10). A plurality of clutches(C1)(C2)(C3)(C4)(C5) is arranged between rotation elements. A plurality of brakes(B1)(B2) changeably connects a part of the rotation elements with the transmission housing(H).

Description

GEAR TRAIN OF AUTOMATIC TRANSMISSION FOR VEHICLES}

The present invention combines two simple planetary gear sets and one compound planetary gear set with five clutches, two brakes, and one one-way clutch in the gear train of the automatic transmission for a vehicle to realize a shift speed of 10 forward speeds. It is about.

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

In 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, 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.

From this point of view, four-speed and five-speed automatic transmissions are the mainstream automatic transmissions currently in use, but recently, six-speed automatic transmissions have been developed and applied to vehicles, while the development of automatic transmissions of eight or more speeds is active. It's going on.

Accordingly, the present inventors have proposed the present invention to meet the development of the automatic transmission as described above, and an object of the present invention is to provide two clutches, two brakes, and one simple planetary gear set and one compound planetary gear set. By combining a single one-way clutch to achieve 10 forward speeds and 1 reverse speed, the present invention provides a gear train of an automatic transmission for a vehicle that can improve power transmission performance and reduce fuel consumption.

In order to realize the above object, the present invention provides a double pinion planetary gear set, comprising: a first rotating element (N1) which always operates as a fixed element, and a first intermediate output path (MOP1) in which a deceleration output is always made; A first rotating element N2 and a third rotating element N3 forming a second intermediate output path MOP2 at which the same speed output is made while forming an input path IS connected to the input shaft IS. Planetary gear set PG1;

A single pinion planetary gear set, comprising: a fourth rotating element N4 forming a first intermediate input path MIP1 directly receiving power from the second rotating element N2, and the third rotating element N3; A fifth intermediate output path MOP3 that forms a first variable input path VIP1 that is variably connected and at the same time increases and outputs rotational power input through the first intermediate input path MIP1. A sixth rotating element N6 forming a rotating element N5 and a second variable input path VIP2 variably connected to the second intermediate output path MOP2, and the fifth rotating element N5. ) And a second planetary gear set (PG2) to be selectively connected to the remaining two rotary elements to be in a selective direct connection state;

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, the second intermediate input path being connected to the third intermediate output path (MOP3) MIP2) forms a third variable input path (VIP3) while being variably connected to the seventh rotating element (N7) and the input shaft (IS7), which act as an input element and act as an optional fixed element. The eighth rotating element N8 acting as a fixed element, the ninth rotating element N9 connected to the output shaft OS and forming a final output path OP, and the first intermediate output path MOP1 are variable. A third planetary gear set PG2 connected to the second planetary gear set PG2 having a tenth rotating element N10 forming a fourth variable input path VIP4;

A plurality of clutches C1, C2, C3, C4 and C5 disposed between the rotating elements and variably connected to each other, and a plurality of clutches variably connecting some of the rotating elements to the transmission housing H. A gear train of an automatic transmission for a vehicle including a friction element consisting of brakes B1 and B2 is provided.

In the first planetary gear set PG1, the first rotational element N1 includes the first sun gear S1, the second rotational element N2 includes the first ring gear R2, and the third rotational element N3. The first planetary gear set PG2 includes the first planetary gear set PG2, and the fourth rotational element N4 is the second sun gear S2, and the fifth rotational element N5 is the second planetary carrier PC2. The third sun gear S3 in which the sixth rotation element N6 is formed of the second ring gear R2, and the third planetary gear set PG3 is engaged with the long pinion P1 by the seventh rotation element N7. ), The eighth rotating element N8 is engaged with the third planet carrier PC3, the ninth rotating element N9 is engaged with the third ring gear R3, and the tenth rotating element N10 with the short pinion P2. It is characterized in that the fourth sun gear (S4).

The friction element includes a first clutch (C1) disposed between the third rotary element (N3) and the fifth rotary element (N5); A second clutch C2 disposed between the third rotating element N3 and the sixth rotating element N6; A third clutch C3 disposed between the fifth rotating element N5 and the sixth rotating element N6; A fourth clutch C4 disposed between the input shaft IS and the eighth rotating element N8; A fifth clutch C5 disposed between the fourth rotating element N4 and the tenth rotating element N10; A first brake B1 disposed between the seventh rotating element N7 and the transmission housing H; It is characterized in that it comprises a second brake (B2) disposed in parallel with the one-way clutch (F) is disposed between the eighth rotating element (N8) and the transmission housing (H).

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 five clutches C1 as friction elements. (C2) (C3) (C4) (C5) combined with two brakes (B1) (B2) and one one-way clutch (F) to realize a gearshift of 10 forward speed and 1 reverse speed To improve fuel efficiency.

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 shows an embodiment of a power 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. Clutch means comprising four clutches C1, C2, C3 and C4, brake means consisting of three brakes B1, B2 and B3, and one one-way clutch F. It is done by

Accordingly, the rotation input from the input shaft IS is shifted through the first, second and third planetary gear sets PG1, PG2 and PG3 and output through the output shaft OS. PG1 is disposed on the engine side, and second and third planetary gear sets PG2 and PG3 are sequentially disposed on the rear side.

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 planetary gear set PG1 is a double pinion planetary gear set, and has three rotating elements consisting of a sun gear, a planet carrier, and a ring gear, as is well known.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 fixedly connected to the transmission housing H, and the first planetary carrier PC1 is directly connected to the input shaft IS.

Accordingly, in the first planetary gear set PG1, the first sun gear S1 is fixedly connected to the transmission housing H as the first rotating element N1 to operate as a fixed element at all times, and the first ring gear While R1 forms the first intermediate output path MOP1 as the second rotary element N2, the first planetary carrier PC1 is operated as an output element that generates a deceleration output at all times. It is directly connected to the input shaft (IS) as a) to form a second intermediate output path (MOP2) to operate as an input element at the same time and output the input as it is at all times.

The second planetary gear set PG2 is a single-pinion planetary gear set, which holds three rotating elements consisting of a sun gear, a planet carrier, and a ring gear as is known, and for the sake of explanation, the sun gear is 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 addition, the second planetary gear set PG2 has the second sun gear S2 directly connected to the first ring gear R1, and the second planetary carrier PC2 and the second ring gear R2 are connected to the second planetary gear set PG2. The first planetary carrier PC1 is variably connected to each other.

Accordingly, in the second planetary gear set PG2, the second sun gear S2 is directly connected to the first intermediate output path MOP1 of the second rotating element N2 as the fourth rotating element N4. A first intermediate input path MIP1 is formed, and the second planet carrier PC2 is variably connected to the second intermediate output path MOP2 of the third rotating element N3 as the fifth rotating element N4. A first variable input path VIP1 is formed and a third intermediate output path MOP3 is formed as an output element, and the second ring gear R2 is the sixth rotary element N6 as the third rotary element N3. It is variably connected to the second intermediate output path (MOP2) of the) to form a second variable input path (VIP2) to operate as an optional input element.

In order to variably connect the third rotating element N3 with the fifth and sixth rotating elements N5 and N6, respectively, the first clutch C1 and the second clutch C2 which are friction elements are disposed therebetween. do.

The second planetary gear set PG2 variably connects the fifth rotating element N5 with the fourth rotating element N4 or the sixth rotating element N6 to selectively connect the second planetary gear set PG2. The third clutch C3 is arranged to be able to maintain the direct connection state.

In the first embodiment of the present invention, the third clutch C3 is disposed between the fifth rotating element N5 and the sixth rotating element N6, but is disposed at the rear side of the second planetary gear set PG2.

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.

In addition, the third planetary gear set PG3 has a third sun gear S3 directly connected to the second planetary carrier PC2 and is variably connected to the transmission housing H, and a third planetary carrier PC3 is connected to the third planetary gear set PG3. It is variably connected to the input shaft IS and variably connected to the transmission housing H, the third ring gear R3 is directly connected to the output shaft OS, and the fourth sun gear S4 is the second sun gear. It is variably connected with (S2).

Accordingly, in the third planetary gear set PG3, the third sun gear S3 is directly connected to the third intermediate output path MOP3 of the fifth rotating element N5 as the seventh rotating element N7. The third variable input path (3) is formed as a second intermediate input path (MIP2) and acts as a fixed element, the third planetary carrier (PC3) is variably connected to the input shaft (IS) as the eighth rotary element (N8) The third ring gear R3 forms the final output path OP as the ninth rotating element N9, and the fourth sun gear S4 is the tenth rotary yaw. As the small N10, a fourth variable input path VIP4 variably connected to the fourth rotating element N4 is formed.

The fourth clutch C4 is disposed to variably connect the input shaft IS and the eighth rotating element N8, and variably connects the fourth rotating element N10 and the tenth rotating element N10. The third clutch C3, which is a friction element, is disposed therebetween, so that the fifth rotary element N5 and the seventh rotary element N7, which are directly connected to each other, can operate as an optional fixing element. A first brake B1 is disposed between H, and a one-way clutch F between the transmission housing H so that the eighth rotating element N8 can operate as an optional fixing element. Is arranged in parallel with the second brake B2.

The rotational power of the engine transmitted from the input shaft IS is shifted to 10 forward speeds and 1 reverse speed while passing through the first, second, and third planetary gear sets PG1, PG2, and PG3. The output is made through the output shaft OS, which is the path OP.

In the above, the friction element composed of the first, second, third and fourth clutches C1, C2, C3 and C4 and the first, second and third brakes B1, B2 and B3 is frictionally coupled by hydraulic pressure. It is customary to consist of a multi-plate hydraulic friction engagement unit.

In addition, the first and second clutches C1 and C2 are disposed in front of the first planetary gear set PG1, and the third clutch C30 is disposed in front or rear of the second planetary gear set PG2. , The fourth and fifth clutches C4 and C5 are disposed at the rear of the third planetary gear set PG2, and the first brake B1 is disposed at the outer circumferential side of the second planetary gear set PG2. The two brakes B2 and the one-way clutch F are arranged on the outer circumferential side between the second and third planetary gear sets PG1 and PG2.

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

2 is an operation table showing that the friction elements applied to the present invention, that is, the clutch and the brake at each shift stage, the power train of the present invention knows that the shift is made while the two friction members operate at each shift stage. Can be.

That is, at the first forward speed, the fifth clutch C5 and the one-way clutch F are operated.

At the second forward speed, the fifth clutch C5 and the first brake B1 are operated.

At the third forward speed, the fifth clutch C5 and the third clutch C3 are operated.

At the fourth forward speed, the fifth clutch C5 and the second clutch C2 are operated.

At fifth speed, the fifth clutch C5 and the first clutch C1 are operated.

At the sixth forward speed, the fifth clutch C5 and the fourth clutch C4 are operated.

At seventh forward speed, the first clutch C1 and the fourth clutch C4 are operated.

At the 8th forward speed, the second clutch C2 and the fourth clutch C4 are operated.

At the 9th forward speed, the third clutch C3 and the fourth clutch C4 are operated.

At the 10th forward speed, the fourth clutch C4 and the first brake B1 are operated.

In the reverse direction, the shift is performed while the third clutch C3 and the second brake B2 are operated.

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

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

The three vertical lines of the second planetary gear set PG2 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 (the number of teeth of the sun gear / the number of teeth of the ring gear).

Four vertical lines of the third planetary gear set PG3 are sequentially rotated from the left to the third sun gear S3 as the seventh rotation element N7, and the third planet carrier PC3 as the eighth rotation element N8 and the ninth rotation. The third ring gear R3, which is the element N9, and the fourth sun gear S4, which is the tenth rotating element N10, are set to the gear ratio of the second planetary gear set PG2 (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 third clutch C3 and the one-way clutch F are controlled to operate.

Accordingly, in the first planetary gear set PG1, the first rotary element N1 operates as a fixed element in a state where an input is made to the third rotary element N3 forming the input path IP, thereby operating at a first speed. The output is decelerated through the second rotating element N2 which forms the line T1 and forms the first intermediate output path MOP1.

The rotational power of the first intermediate output path MOP1 is transmitted to the second planetary gear set PG2 through the fourth rotating element N4 forming the first intermediate input path MIP1 and at the same time, the fifth clutch C5. ) Is transferred to the tenth rotary element N10 of the third planetary gear set PG3 that forms the fourth variable input path VIP4.

Then, the second planetary gear set PG2 is in an idle state without any operation, and in the third planetary gear set PG3, the one-way clutch F is being input to the tenth rotating element N10. The eighth operating element (N8) is operated as a fixed element by the operation of the bar, thereby forming a first transmission line (SP1), its first transmission line (SP1) and the output element of the ninth rotating element ( As the output of D1 intersecting the vertical line of N9) is made, the shift of 1 forward speed is made.

That is, in the first planetary gear set PG1, the rotational power input from the input shaft IS through the input path IP is decelerated and output through the first intermediate output path MOP1.

The one-way clutch receives the rotational power output from the third planetary gear set PG3 through the first intermediate output path MOP1 through the fourth variable input path VIP4 by the operation of the fifth clutch C5. By decelerating speed change by the operation of F) and outputting it through the final output path OP, the speed change of forward 1 speed is achieved.

[2 speed forward]

At the second forward speed, the first brake B1 is controlled to operate in the state of the first forward speed.

Then, in the first planetary gear set PG1, the first rotating element N1 operates as a fixed element while the first rotating element N3 forms an input path IP, thereby operating the first speed line. Deceleration is output through the second rotating element N2 forming the first intermediate output path MOP1 while forming the T1.

The rotational power of the first intermediate output path MOP1 is transmitted to the second planetary gear set PG2 through the fourth rotating element N4 forming the first intermediate input path MIP1 and at the same time, the fifth clutch C5. ) Is transferred to the tenth rotary element N10 of the third planetary gear set PG3 that forms the fourth variable input path VIP4.

Then, the second planetary gear set PG2 is in an idle state without any operation, and in the third planetary gear set PG3, the first brake B1 is being input to the tenth rotating element N10. The seventh operating element (N7) is operated as a fixed element by the operation of the bar, to form a second transmission line (SP2), the second transmission line (SP2) and the output element of the ninth rotating element ( As the output of D2 intersecting the vertical line of N9) is made, the shift of the second forward speed is made.

That is, in the first planetary gear set PG1, the rotational power inputted from the input shaft IS through the input path IP is decelerated and output through the first intermediate output path MOP1, and the third planetary gear set PG3. ) Receives the rotational power output through the first intermediate output path (MOP1) through the fourth variable input path (VIP4) by the operation of the fifth clutch (C5) to decelerate to the operation of the second brake (B2). By shifting and outputting through the final output path OP, the shift in the forward 2 speed is achieved.

[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 first brake B1 is controlled to operate.

Then, in the first planetary gear set PG1, the first rotating element N1 operates as a fixed element while the first rotating element N3 forms an input path IP, thereby operating the first speed line. Deceleration is output through the second rotating element N2 forming the first intermediate output path MOP1 while forming the T1.

The rotational power of the first intermediate output path MOP1 is transmitted to the second planetary gear set PG2 through the fourth rotating element N4 forming the first intermediate input path MIP1 and at the same time, the fifth clutch C5. ) Is transferred to the tenth rotary element N10 of the third planetary gear set PG3 that forms the fourth variable input path VIP4.

At this time, in the second planetary gear set PG2, the third clutch C3 is directly connected by the operation of the third clutch C3 while the fourth planetary gear set PG2 is input to the third intermediate output path ( When outputting through MOP3), its rotational power is input to the seventh rotating element N7 through the second intermediate input path MIP2.

Then, in the third planetary gear set PG3, the input is simultaneously made to the seventh operating element N7 while the input is made to the tenth rotating element N10. SP3 is formed, and as much as D3 of the third shift line SP3 and the vertical line of the ninth rotation element N9 that is an output element is output, the shift of the third forward speed is made.

That is, the rotational power input from the input shaft IS through the input path IP in the first planetary gear set PG1 is decelerated and output through the first intermediate output path MOP1, and the second planetary gear set PG2 is rotated. ) And the output power through the third intermediate output path (MOP3) as it is being directly connected to the first intermediate output path (MOP1) as it is, the third planetary gear set (PG3) in the first, third intermediate The rotational power of the same number of revolutions outputted through the output paths MOP1 and MOP3 is transmitted through the fourth variable input path VIP4 and the second intermediate input path MIP2 to receive the rotational power as it is in the direct connection state. By outputting through the final output path (OP), the three-speed forward is made.

[4 forward speed]

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

Then, in the first planetary gear set PG1, the first rotating element N1 operates as a fixed element while the first rotating element N3 forms an input path IP, thereby operating the first speed line. Deceleration is output through the second rotating element N2 forming the first intermediate output path MOP1 while forming the T1.

The rotational power of the first intermediate output path MOP1 is transmitted to the second planetary gear set PG2 through the fourth rotating element N4 forming the first intermediate input path MIP1 and at the same time the fifth clutch By the operation of C5) it is transmitted to the tenth rotation element (N10) of the third planetary gear set (PG3) forming the fourth variable input path (VIP4).

At this time, in the second planetary gear set PG2, the input shaft IS is rotated on the sixth rotating element N6 by the operation of the second clutch C2 while being input to the fourth rotating element N4. When the power is input as it is, the rotational power output through the fifth rotating element N5 forming the third intermediate output path MOP3 while forming the second speed line T2 is the second intermediate input path MIP2. It is input to the seventh rotation element (N7) through.

Then, in the third planetary gear set PG3, the input is made to the seventh operating element N7 while the input is made to the tenth rotation element N10 to form a fourth transmission line SP4. As the output of the fourth shift line SP4 and the vertical line of the ninth rotation element N9 which is the output element crosses as much as D4, the shift of the fourth forward speed is made.

That is, the rotational power input from the input shaft IS through the input path IP in the first planetary gear set PG1 is decelerated and output through the first intermediate output path MOP1, and in the second planetary gear set, Receiving the rotational power of the first intermediate input path (MOP1) and simultaneously receiving the rotational power of the input shaft (IS) input to the input path (IP) by the operation of the second clutch (C2) at the same time complementary operation When the speed is lowered than the rotational power of IS and output through the third intermediate output path MOP3, the third planetary gear set PG3 is output through the first and third intermediate output paths MOP1 and MOP3. By receiving the rotational power through the fourth variable input path (VIP4) and the second intermediate input path (MIP2) and shifts to the complementary operation and outputs through the final output path (OP), the fourth forward speed is made.

[5th forward]

At the 5th forward speed, as shown in FIG. 2, the operation of the second clutch C2 operated in the state of the 4th forward speed is released, and the first clutch C1 is operated and controlled.

Then, in the first planetary gear set PG1, the first rotating element N1 operates as a fixed element while the first rotating element N3 forms an input path IP, thereby operating the first speed line. Deceleration is output through the second rotating element N2 forming the first intermediate output path MOP1 while forming the T1.

The rotational power of the first intermediate output path MOP1 is transmitted to the second planetary gear set PG2 through the fourth rotating element N4 forming the first intermediate input path MIP1 and at the same time, the fifth clutch C5. ) Is transferred to the tenth rotary element N10 of the third planetary gear set PG3 that forms the fourth variable input path VIP4.

In this case, in the second planetary gear set PG2, the rotational power of the input shaft IS is directly input to the fifth rotating element N5 by the operation of the first clutch C1, and the rotational power thereof is directly connected. 2 is input to the seventh rotation element N7 through the intermediate input path MIP2.

Then, in the third planetary gear set PG3, the input is made to the seventh operating element N7 while the input is made to the tenth rotation element N10 to form a fifth shift line SP5. As the output of the fifth shift line SP5 and the vertical line of the ninth rotation element N9 which is the output element crosses as much as D5, the shift of the fifth forward speed is made.

That is, the rotational power input from the input shaft IS through the input path IP in the first planetary gear set PG1 is decelerated and output through the first intermediate output path MOP1, and in the second planetary gear set, Receiving the rotational power of the first intermediate input path (MOP1) and at the same time receiving the rotational power of the input shaft (IS) input to the input path (IP) by the operation of the first clutch (C1) at the third intermediate output path When outputting through MOP3, the rotational power output from the third planetary gear set PG3 through the first and third intermediate output paths MOP1 and MOP3 is converted into a fourth variable input path VIP4 and a second one. Received through the intermediate input path (MIP2) is shifted to the complementary operation and output through the final output path (OP), the five-speed forward is made.

[6th forward]

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

Then, in the first planetary gear set PG1, as in the first forward speed, the first rotary element N1 is a fixed element in the state where an input is made to the third rotary element N3 forming the input path IP. It operates to decelerate through the second rotating element N2 which forms the first speed line T1 and forms the first intermediate output path MOP1.

The rotational power of the first intermediate output path MOP1 is transmitted to the second planetary gear set PG2 through the fourth rotating element N4 forming the first intermediate input path MIP1 and at the same time, the fifth clutch C5. ) Is transferred to the tenth rotary element N10 of the third planetary gear set PG3 that forms the fourth variable input path VIP4.

Then, the second planetary gear set PG2 is in an idle state without any operation, and in the third planetary gear set PG3, the fourth clutch C4 is being input to the tenth rotating element N10. The rotational power of the input shaft IS is input to the eighth rotary element N8 by the operation of the bar, thereby forming a sixth shift line SP6, and the sixth shift line SP6 and the ninth output element. As the output of D6 crossing the vertical line of the rotating element N9 is made, shifting of six forward speeds is achieved.

That is, in the first planetary gear set PG1, the rotational power inputted from the input shaft IS through the input path IP is decelerated and output through the first intermediate output path MOP1, and the third planetary gear set PG3. ) Receives the rotational power output through the first intermediate output path (MOP1) through the fourth variable input path (VIP4) by the operation of the fifth clutch (C53) and at the same time the rotational power of the input shaft (IS) By receiving the third variable input path (VIP3) by the operation of the fourth clutch (C4) is shifted to the complementary operation to output through the final output path (OP), the sixth forward speed is made.

[7th forward]

In the seventh forward speed, as shown in FIG. 2, the operation of the fifth clutch C5 which is operated in the sixth forward speed is released, and the first clutch C1 is controlled to operate.

Then, the rotational power of the input shaft IS is directly input to the fifth rotating element N5 of the second planetary gear set PG2 by the operation of the first clutch C1 and output through the third intermediate output path MOP3. In this case, its rotational power is input to the seventh rotation element N7 through the second intermediate input path MIP2.

Accordingly, in the third planetary gear set PG3, the operation of the first clutch C1 is performed while the rotational power of the input shaft IP is input to the eighth rotation element N8 by the operation of the fourth clutch C4. As the rotational power of the input shaft IP is directly connected to the seventh rotating element N4 at the same time, the D7 is formed through the ninth rotating element N9 as an output element while forming the seventh transmission line SP7 as it is. The output of the seven forward speed is to be made.

That is, the rotational power of the input shaft IS to the seventh rotary element N7 and the eighth rotary element N8 of the third planetary gear set PG3 by the operation of the first clutch C1 and the fourth clutch C4. At the same time, the third planetary gear set PG3 outputs the rotational power of the input shaft IS as it is through the final output path OP, thereby shifting the seventh forward speed.

[8th forward]

At the eighth forward speed, as shown in FIG. 2, the first clutch C1 is released in the state of the seventh forward speed, and the second clutch C2 is controlled to operate.

Then, in the first planetary gear set PG1, the first rotating element N1 operates as a fixed element while the first rotating element N3 forms an input path IP, thereby operating the first speed line. Deceleration is output through the second rotating element N2 forming the first intermediate output path MOP1 while forming the T1.

The rotational power of the first intermediate output path MOP1 is transmitted to the second planetary gear set PG2 through the fourth rotating element N4 forming the first intermediate input path MIP1, wherein the second clutch When the rotational power of the input shaft IS is input directly to the sixth rotating element N6 by the operation of the C2, the fifth intermediate line forming the third intermediate output path MOP3 while forming the second speed line T2. The rotating power output through the rotating element N5 is input to the seventh rotating element N7 through the second intermediate input path MIP2.

Then, in the third planetary gear set PG3, the rotational power of the input shaft IS is driven to the eighth operating element N8 by the operation of the fourth clutch C4 while the input is made to the seventh rotating element N7. As the input is made, an eighth shift line SP8 is formed, and as much as the output of D8 where the eighth shift line SP8 intersects the vertical line of the ninth rotation element N9 that is an output element. 8 forward speed is to be achieved.

That is, the rotational power input from the input shaft IS through the input path IP in the first planetary gear set PG1 is decelerated and output through the first intermediate output path MOP1, and in the second planetary gear set, Receiving the rotational power of the first intermediate input path (MOP1) and simultaneously receiving the rotational power of the input shaft (IS) input to the input path (IP) by the operation of the second clutch (C2) at the same time complementary operation When the speed is lower than the rotational power of IS and output through the third intermediate output path MOP3, the rotational power of the third intermediate output path MOP3 is converted to the second intermediate input path in the third planetary gear set PG3. MIP2) is received through the drive, and the rotational power of the input shaft IS is transmitted through the fourth variable input path VIP4 by the operation of the fourth clutch C4 to shift to the complementary operation to the final output path OP. By outputting through, the eighth speed shift is achieved.

[9 speed forward]

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

Then, in the first planetary gear set PG1, the first rotating element N1 operates as a fixed element while the first rotating element N3 forms an input path IP, thereby operating the first speed line. Deceleration is output through the second rotating element N2 forming the first intermediate output path MOP1 while forming the T1.

The rotational power of the first intermediate output path MOP1 is transmitted to the second planetary gear set PG2 through the fourth rotating element N4 forming the first intermediate input path MIP1, wherein the second The planetary gear set PG2 is directly connected to the fourth clutch C3 by the operation of the third clutch C3 while being input to the fourth rotating element N4, and is output as it is through the third intermediate output path MOP3. The rotational power thereof is input to the seventh rotation element N7 through the second intermediate input path MIP2.

Then, in the third planetary gear set PG3, the rotational power of the input shaft IS is driven to the eighth operating element N8 by the operation of the fourth clutch C4 while the input is made to the seventh rotating element N7. As the input is made, a ninth shift line SP9 is formed, and as much as D9 at which the vertical line of the ninth shift line SP9 and the ninth rotation element N9 that is an output element intersect is made. 9 forward speed is to be achieved.

That is, the rotational power input from the input shaft IS through the input path IP in the first planetary gear set PG1 is decelerated and output through the first intermediate output path MOP1, and the second planetary gear set PG2 is rotated. In the direct connection in the state) outputs the rotational power output as the first intermediate output path (MOP1) through the third intermediate output path (MOP3), the third intermediate output from the planetary gear set (PG3) The rotational power output through the path MOP3 is transmitted through the second intermediate input path MIP2 and at the same time, the rotational power of the input shaft IS is transmitted through the fourth variable input path VIP4 to shift to the complementary operation. By outputting through the final output path (OP), the shift in the forward 9 speed is achieved.

[10 speed forward]

At the 10th forward speed, as shown in FIG. 2, the third clutch C3 is released from the 9th forward speed, and the second brake B2 is controlled to operate.

Then, in the third planetary gear set PG3, when the rotational power of the input shaft IS is applied to the eighth rotating element N8 by the operation of the fourth clutch C4, the third brake B2 is operated. As the seventh operating element N7 operates as a fixed element, it forms a tenth shift line SP10, and a vertical line of the tenth shift line SP10 and the ninth rotation element N9 as an output element intersect. As the output of D10 is achieved, the shifting speed of 10 forwards, which is the highest speed shifting stage, is achieved.

That is, the rotational power of the input shaft IS is transmitted from the third planetary gear set PG3 through the fourth variable input path VIP4 by the operation of the fourth clutch C4 and at the same time the By shifting to the complementary operation by the rotation stop of the second intermediate input path (MIP2) by the operation and output through the final output path (OP), the shift of the forward 10 speed is achieved.

[apse]

In the reverse shift stage, as shown in FIG. 2, the third clutch C3 and the second brake B2 are operated and controlled.

Then, in the first planetary gear set PG1, the first rotating element N1 operates as a fixed element while the first rotating element N3 forms an input path IP, thereby operating the first speed line. Deceleration is output through the second rotating element N2 forming the first intermediate output path MOP1 while forming the T1.

The rotational power of the first intermediate output path MOP1 is transmitted to the second planetary gear set PG2 through the fourth rotating element N4 forming the first intermediate input path MIP1, wherein the second The planetary gear set PG2 is directly connected to the fourth clutch C3 by the operation of the third clutch C3 while being input to the fourth rotating element N4, and is output as it is through the third intermediate output path MOP3. The rotational power thereof is input to the seventh rotation element N7 through the second intermediate input path MIP2.

Then, in the third planetary gear set PG3, the eighth rotating element N8 is operated as the fixed element by the operation of the second brake B2 while the input is made to the seventh rotating element N7. The reverse shift line SR is formed, and the reverse shift output is performed as much as the reverse rotation output RS is generated by crossing the reverse shift line SR and the vertical line of the ninth rotation element N9 that is the output element. .

That is, the rotational power input from the input shaft IS through the input path IP in the first planetary gear set PG1 is decelerated and output through the first intermediate output path MOP1, and the second planetary gear set PG2 is rotated. When the rotational power output from the first intermediate output path (MOP1) is decelerated through the third intermediate output path (MOP3), the third intermediate output path (MOP3) in the third planetary gear set (PG3) Receives the rotational power output through the second intermediate input path (MIP2) receives the reverse rotation by the operation of the second brake (B2) and outputs through the final output path (OP), the reverse shift is made.

4 to 5 show a gear train according to the second, third and fourth embodiments of the present invention, all configurations are configured in the same manner as the first embodiment, but the second planetary gear set PG2 is selectively selected. The arrangement position and the connection configuration of the fourth clutch (C4) to make the state of direct connection by different.

That is, in the second embodiment, as shown in FIG. 4, the third clutch C3 is the second planetary carrier PC2 and the sixth rotation element N6, which are the fifth rotation element N5, as in the first embodiment. It is arranged between the second ring gear (R2), and the position is placed on the front side of the second planetary gear set (PG2).

In the third embodiment, as shown in FIG. 5, the third clutch C3 is disposed between the second planet carrier PC2, which is the fifth rotary element N5, and the second sun gear S2, which is the fourth rotary element N4. It is arranged at the rear side of the second planetary gear set PG2.

In addition, in the fourth exemplary embodiment, as shown in FIG. 6, the third clutch C3 includes the second planet carrier PC2, which is the fifth rotary element N5, and the second sun gear S2, which is the fourth rotary element N4. Arranged in between, but the position is placed on the front side of the second planetary gear set (PG2),

As described above, the third clutch C3 differs only in position from the first embodiment, and performs only a role of variably directly connecting the third planetary gear set PG3. Since the same, detailed description of the shifting process will be omitted.

Although the 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 facilitate the present invention. Invention includes all modifications to the extent deemed equivalent.

1 is a configuration diagram of a gear train according to a first embodiment of the present invention.

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

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

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

5 is a configuration diagram of a gear train according to a third embodiment of the present invention.

6 is a configuration diagram of a gear train according to a fourth embodiment of the present invention.

Claims (6)

A double pinion planetary gear set comprising: a first rotating element (N1), which always operates as a fixed element, a second rotating element (N2), which forms a first intermediate output path (MOP1), in which a deceleration output is always performed, and an input shaft (IS). A first planetary gear set PG1 having a third rotating element N3 forming a second intermediate output path MOP2 at the same speed while forming an input path IS connected thereto; A single pinion planetary gear set, comprising: a fourth rotating element N4 forming a first intermediate input path MIP1 directly receiving power from the second rotating element N2, and the third rotating element N3; A fifth intermediate output path MOP3 that forms a first variable input path VIP1 that is variably connected and at the same time increases and outputs rotational power input through the first intermediate input path MIP1. A sixth rotating element N6 forming a rotating element N5 and a second variable input path VIP2 variably connected to the second intermediate output path MOP2, and the fifth rotating element N5. ) And a second planetary gear set (PG2) to be selectively connected to the remaining two rotary elements to be in a selective direct connection state; 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, the second intermediate input path being connected to the third intermediate output path (MOP3) An eighth rotation element N7 which forms an MIP2) and operates as an input element and optionally as a fixed element; and an eighth that is variably connected to the input shaft IS to form a third variable input path VIP3. A fourth variable being variably connected to the rotating element N8, the ninth rotating element N9 connected to the output shaft OS to form a final output path OP, and the first intermediate output path MOP1. A third planetary gear set PG2 having a tenth rotating element N10 forming an input path VIP4; A plurality of clutches C1, C2, C3, C4 and C5 disposed between the rotating elements and variably connected to each other, and a plurality of clutches variably connecting some of the rotating elements to the transmission housing H. A gear train of an automatic transmission for a vehicle comprising a friction element consisting of brakes B1 and B2. The first planetary gear set PG1 has a first rotational element N1 as a first sun gear S1, a second rotational element N2 as a first ring gear R2, and a third rotational element. N3 is made of the first planetary carrier PC1, In the second planetary gear set PG2, the fourth rotating element N4 is the second sun gear S2, the fifth rotating element N5 is the second planetary carrier PC2, and the sixth rotating element N6 is the second Ring gear (R2), The third planetary gear set PG3 includes a third sun gear S3 in which the seventh rotation element N7 meshes with the long pinion P1, and the eighth rotation element N8 includes a third planet carrier PC3, a ninth rotation element N7. A gear train of a vehicular automatic transmission, characterized in that the rotating element (N9) consists of a third ring gear (R3), and a tenth rotating element (N10) is engaged with the short pinion (P2). The friction element according to claim 1, further comprising: a first clutch (C1) disposed between the third rotating element (N3) and the fifth rotating element (N5); A second clutch C2 disposed between the third rotating element N3 and the sixth rotating element N6; A third clutch C3 disposed between the fifth rotating element N5 and the sixth rotating element N6; A fourth clutch C4 disposed between the input shaft IS and the eighth rotating element N8; A fifth clutch C5 disposed between the fourth rotating element N4 and the tenth rotating element N10; A first brake B1 disposed between the seventh rotating element N7 and the transmission housing H; And a second brake (B2) disposed in parallel with the one-way clutch (F) and disposed between the eighth rotating element (N8) and the transmission housing (H). The fifth clutch C5 and the one-way clutch F are operated at the first forward speed, At the second forward speed, the fifth clutch C5 and the first brake B1 are operated. At the third forward speed, the fifth clutch C5 and the third clutch C3 are operated. At the fourth forward speed, the fifth clutch C5 and the second clutch C2 are operated. At fifth speed, the fifth clutch C5 and the first clutch C1 are operated. At the sixth forward speed, the fifth clutch C5 and the fourth clutch C4 are operated. At the seventh forward speed, the fourth clutch C4 and the first clutch C1 are operated. At the 8th forward speed, the fourth clutch C4 and the second clutch C2 are operated. At the 9th forward speed, the fourth clutch C4 and the third clutch C3 are operated. At the 10th forward speed, the fourth clutch C4 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 second brake (B2) is operated. A double pinion planetary gear set, comprising: a first planetary gear set PG1 composed of a first sun gear S1, a first ring gear R2, and a first planet carrier PC1; A single pinion planetary gear set, comprising: a second planetary gear set PG1 composed of a second sun gear S2, a second planet carrier PC2, and a second ring gear R2; A planetary type planetary gear set that shares a planetary gear with a ring gear, and includes a third sun gear (S3), a third planet carrier (PC3), a third ring gear (R3), and a short pinion meshing with the long pinion (P1). Combine the third planetary gear set (PG3) consisting of the fourth sun gear (S4) meshed with (P2), The first planet carrier PC1 is directly connected to the input shaft IS, the first ring gear R1 and the second sun gear S2 are directly connected, and the second planet carrier PC2 and the first planet carrier are directly connected to each other. In a state in which the three sun gears S3 are directly connected and the third ring gear R3 is directly connected to the output shaft OS, A first clutch C1 is disposed between the first planet carrier PC1 and the second planet carrier PC2, and a second clutch (B) is disposed between the first planet carrier PC1 and the second ring gear R2. C2) is disposed, and a third clutch C3 is disposed between the second planetary carrier PC2 and the second ring gear R2, and a third clutch C3 is disposed between the input shaft IS and the third planetary carrier PC3. Fourth clutch C4 is disposed, and the fifth clutch C5 is disposed between the second sun gear S2 and the fourth sun gear S4, and between the third sun gear S3 and the transmission housing H. The first brake (B1) is disposed on the second planetary carrier (PC3) and the transmission housing (H) is arranged by placing a second brake (B2) disposed in parallel with the one-way clutch (F) Gear train of automatic transmission The vehicle of claim 5, wherein the third clutch C3 is disposed between the second planetary carrier PC2 and the second sun gear S2, and is located at the rear side of the second planetary gear set PG2. Gear train of automatic transmission.

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