KR100907070B1 - Gear train of automatic transmission for vehicles - Google Patents

Abstract

A gear train of automatic transmission for vehicles is provided to perform forward 10 speeds backward 2 speeds of transmission by arranging dispersively a plurality of frictional elements. The first planetary gear set(PG1) comprises the first sun gear(S1), and the first ring gear(R1) and the first planetary carrier(PC1). The second planet gear set(PG2) comprises the second sun gear(S2), and the second ring gear(R2) and the second planet carrier(PC2). The third planetary gear set(PG3) comprises the third sun gear(S3), the third planetary carrier(PC3), the third ring gear(R3), the fourth sun gear(S4), the fourth clutch(C4). The first clutch(C1) and the first brake(B1) are arranged between the first and second planetary gear set. The second and third brake(B2)(B3) and fourth clutch are arranged between the second and third planetary gear set. The second and third clutch(C2)(C3) are arranged behind the third planetary gear set.

Description

GEAR TRAIN OF AUTOMATIC TRANSMISSION FOR VEHICLES}

The present invention combines two simple planetary gear sets and one compound planetary gear set with four clutches, three brakes, and one one-way clutch in the gear train of an 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 in order to meet the development of the automatic transmission as described above, and an object of the present invention is to provide two clutches and three brakes with one planetary gearset and one compound planetary gearset. By combining a single one-way clutch to achieve 10 forward speeds and 2 reverse speeds, 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 as in claim 1, wherein the first sun gear S1, which is a first rotating element N1, which always operates as a fixed element, A first planetary gear having a first ring gear R1 that is a second rotation element N2 to which a deceleration output is made, and a first planet carrier PC1 that is a third rotation element N3 directly connected to the input shaft IS. A gear set PG1;

A double pinion planetary gear set comprising: a second sun gear (S2), which is a fourth rotating element (N4) directly connected to the second rotating element (N2), and a reduction of rotational power input to the fourth rotating element (N4). And a second ring gear R2, which is a fifth rotary element N5, which is increased in speed and output, and is connected to each other via the third rotary element N3 and the first clutch C1. A second planetary gear set PG2 having a second planetary carrier PC2 interposed therebetween and connected to the transmission housing H;

A combination of a single-pinion planetary gear set and a double-pinion planetary gearset, but a planetary planetary gear set sharing a planetary carrier with a ring gear, which is directly connected to the fifth rotating element N5 and at the same time a second brake B2. ) Is connected via the third sun gear S3, which is the seventh rotation element N7 connected to the transmission housing H, and the input shaft IS and the third clutch C3, and is a one-way clutch F. ) And a third planet carrier PC3, which is an eighth rotation element N8 connected to the transmission housing H, via a third clutch C3 disposed in parallel to the transmission housing H, and a ninth rotation element connected to the output shaft OS. A third ring gear R3 which is N9 and a fourth sun gear S4 which is a tenth rotation element N10 connected through the fourth rotation element N4 and the second clutch C2; The fourth clutch C4 may be configured to variably connect any two rotary elements of the four rotary elements N7, N8, N9, and N10. It provides a gear train of an automatic transmission for a vehicle including a third planetary gear set (PG3) made in comparison.

As described in claim 2, the fourth clutch C4 is disposed between the seventh rotary element N7 and the eighth rotary element N8, but is disposed on the front side of the third planetary gear set PG3. It is characterized by.

As described in claim 3, the fourth clutch C4 is disposed between the seventh rotary element N7 and the eighth rotary element N8, but is disposed at the rear side of the third planetary gear set PG3. It is characterized by.

As described in claim 4, the fourth clutch C4 is disposed between the eighth rotating element N8 and the ninth rotating element N9, but is disposed on the front side of the third planetary gear set PG3. It is characterized by.

In the above, the fourth clutch C4 is disposed between the eighth rotating element N8 and the ninth rotating element N9, as in claim 5, and is disposed on the rear side of the third planetary gear set PG3. It is characterized by.

As described in claim 6, the fourth clutch C4 is disposed between the seventh rotary element N7 and the tenth rotary element N10, but is disposed on the front side of the third planetary gear set PG3. It is characterized by.

The first and second planetary gear sets PG1 and PG2 composed of two simple planetary gear sets as described above, and the four clutches C1 serving as friction members between the third planetary gear set PG3 composed of a composite planetary gear set. (C2) (C3) (C4) combined with three brakes (B1), (B2) and (B3), and one one-way clutch (F) to realize transmission speeds of 10 forward and 2 reverse speeds. 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 driving wheels are driven through a known gearbox through the 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. ) Is directly connected to the input shaft (IS) to form an input path (IP) and at the same time forms a second intermediate output path (MOP2) for outputting the input as it is.

The second planetary gear set PG2 is a double 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.

The second planetary gear set PG2 has the second sun gear S2 directly connected to the first ring gear R1, and the second planet carrier PC2 has the first planetary carrier PC1. And variably connected to the transmission housing (H) at the same time.

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. 1 forms the intermediate input path MIP1, the second ring gear R2 forms the third intermediate output path MOP3 as the fifth rotating element N4, and the second planet carrier PC2 rotates the sixth rotation. The element N6 is variably connected to the second intermediate output path MOP2 of the third rotating element N3 to form a first variable input path VIP1 and acts as an optional input element, and at the same time the transmission housing ( It is variably connected to H) to act as an optional fixing element.

In order to variably connect the third rotary element N3 and the sixth rotary element N6, a first clutch C1, which is a friction element, is disposed therebetween, and the sixth rotary element N6 is selectively selected. A first brake B1 is disposed between the sixth rotating element N6 and the transmission housing H in order to be able to operate as a stationary element.

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 ring gear R2, and is variably connected to the transmission housing H, and a fourth sun gear S4. Variablely connected to the second sun gear (S2), the third planet carrier (PC3) is variably connected to the input shaft (IS) and at the same time variably connected to the transmission housing (H), the third ring gear (R3) is output shaft (OS) is directly connected.

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 second variable input path (2) 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 second ring gear R3 forms the final output path OP as the ninth rotary element N9 and the fourth sun gear S4 is the tenth rotary element. As N10, a third variable input path VIP3 is variably connected to the fourth rotating element N4.

In order to variably connect the fourth rotating element N10 and the tenth rotating element N10, a second clutch C2, which is a friction element, is disposed therebetween, and the input shaft IS and the eighth rotating element N8 are disposed therebetween. The third clutch (C3) is arranged to variably connect (), the transmission housing so that the fifth rotating element (N5) and the seventh rotating element (N7) that are directly connected to each other to operate as an optional fixing element A second brake B2 is disposed between H, and a one-way clutch F between the transmission housing H and the transmission housing H to allow the eighth rotating element N8 to operate as an optional fixing element. Are arranged in parallel with the third brake B3.

In addition, a fourth clutch C4 is applied to the third planetary gear set PG3 so that the third planetary gear set PG3 may be selectively maintained in a direct connection state. The fourth clutch C4 is disposed between the third sun gear S3, which is the seventh rotation element N7, and the third planet carrier PC3, which is the eighth rotation element N8. During operation of C4), the third planetary gear set PG3 is locked so that it can be directly connected.

The rotational power of the engine transmitted from the input shaft IS is shifted to 10 forward speeds and 2 reverse speeds 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 a path OP.

In the above, the friction member 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 the arrangement of the friction members, in the first embodiment of the present invention, the first clutch C1 and the first brake B1 are disposed between the first and second planetary gear sets PG1 and PG2. The second and third brakes B2 and B3 and the fourth clutch C4 are disposed between the second and third planetary gear sets PG2 and PG3, and the second and third clutches C2 and C3 are removed. 3 is disposed behind the planetary gear set PG2.

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

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

That is, at the first forward speed, the second clutch C2 and the one-way clutch F are operated.

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

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

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

At the 5th forward speed, the second clutch C2 and the first clutch C1 are operated.

At the sixth forward speed, the second clutch C2 and the third clutch C3 are operated.

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

At the 8th forward speed, the third clutch C3 and the first clutch C1 are operated.

At the 9th forward speed, the third clutch C3 and the first brake B1 are operated.

At the 10th forward speed, the third clutch C3 and the second brake B2 are operated.

At the first reverse speed, the first brake B1 and the third brake B3 are operated.

At the second reverse speed, the first brake B1 and the first clutch C1 are operated to shift.

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 have a first sun gear S1, which is the first rotation element N1, and a first ring gear R1, which is the second rotation element N2, and a third, in order from the left. The first planetary carrier PC1, which is the rotating element N3, is set, and these intervals are determined according to the gear ratio of the first planetary gear set PG1 (number of teeth of the sun gear / number of teeth of the ring gear).

The three vertical lines of the second planetary gear set PG2 rotate in order from the left to the second sun gear S2 as the fourth rotating element N4, the second ring gear R2 as the fifth rotating element N5, and the sixth rotation. The second planetary carrier PC2, which is the element N6, is set, and these intervals are determined according to the gear ratio of the second planetary gear set PG2 (number of teeth of the sun gear / number of rings).

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 forward 1 speed, as shown in FIG. 2, the second clutch C2 and the one-way clutch F are controlled to operate.

Accordingly, in the first planetary gear set PG1, as shown in FIG. 3, the first rotating element N1 is a fixed element in the state where an input is made to the third rotating element N3 forming the input path IP. It is operated to form a first speed line (T1) while decelerating through the second rotating element (N2) to form a 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 second clutch C2. ) Is transmitted to the tenth rotation element N10 of the third planetary gear set PG3 which forms the third variable input path VIP3.

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 third variable input path VIP3 by the operation of the second clutch C2. By decelerating speed change by the operation of F) and outputting it through the final output path OP, the speed change of the forward 1 speed is achieved.

[2 speed forward]

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

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 second clutch C2. ) Is transmitted to the tenth rotation element N10 of the third planetary gear set PG3 which forms the third variable input path VIP3.

Then, the second planetary gear set PG2 forms the second speed line T2 while the fifth rotating element N5 operates as a fixed element by the operation of the second brake B2, and at the same time, the fifth rotating element The seventh rotating element N7 directly connected to N5 operates as a fixed element, thereby forming a second transmission line SP2, and a second transmission line SP2 and an output element. 9 As the output of D2 intersecting the vertical line of the rotating element 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. ) The rotational power output through the first intermediate output path (MOP1) is received through the third variable input path (VIP3) by the operation of the second clutch (C2) to reduce the speed change to the operation of the second brake (B2). By outputting through the final output path (OP), the shift in the second forward speed is made.

[3 speed forward]

At the third forward speed, as shown in FIG. 2, the second brake B2 is released from the second forward speed, and the first brake B1 is controlled to operate.

Then, in the first planetary gear set PG1, the first rotary element N1 is fixed to the fixed element in the state where the input is made to the third rotary element N3 forming the input path IP as in the second forward speed. 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 second clutch C2. ) Is transmitted to the tenth rotation element N10 of the third planetary gear set PG3 which forms the third variable input path VIP3.

In this case, in the second planetary gear set PG2, the sixth rotating element N6 is operated as a fixed element by the operation of the first brake B1 while being input to the fourth rotating element N4. The rotational power that is decelerated and output through the fifth rotating element N5 forming the third intermediate output path MOP3 while forming the third speed line T3 is set to the seventh through the second intermediate input path MIP2. It is input to the rotating element N7.

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 third transmission line SP3. As the output of the third shift line SP3 and the vertical line of the ninth rotation element N9, which is an output element, is output as much as D3, 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. When the rotational power output from the first intermediate output path (MOP1) is decelerated again by the operation of the first brake (B1) and decelerated output through the third intermediate output path (MOP3), the third planetary gear set ( PG3) receives the rotational power output through the first and third intermediate output paths MOP1 and MOP3 through a third variable input path VIP3 and a second intermediate input path MIP2, and shifts to the complementary operation. By outputting through the final output path (OP), the three-speed forward is made.

[4 forward speed]

At the fourth forward speed, as shown in FIG. 2, the first brake B1 is released from the third forward speed, and the fourth clutch C4 is controlled to operate.

Then, in the first planetary gear set PG1, as in the third 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 second clutch C2. ) Is transmitted to the tenth rotation element N10 of the third planetary gear set PG3 which forms the third variable input path VIP3.

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. ) Is directly connected to the bar by forming the fourth shift line (SP4) as it is input, and outputting as much as D4 through the ninth rotating element (N9), which is an output element, so that the fourth 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. ) In the direct output state while receiving the rotational power output through the first intermediate output path (MOP1) through the third variable input path (VIP3) by the operation of the second clutch (C2) in the final output path By outputting via (OP), a shift of 4 forward speeds is achieved.

[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, as in the fourth 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 second clutch By the operation of C2) it is transmitted to the tenth rotation element (N10) of the third planetary gear set (PG3) forming the third variable input path (VIP3).

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 first clutch C1 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 fourth speed line T4 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 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 the second planetary gear set PG2 is rotated. ) Receives 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) to complement each other When the operation is slowed down than the rotational power of the input shaft IS and output through the third intermediate output path MOP3, the first and third intermediate output paths MOP1 and MOP3 are transferred from the third planetary gear set PG3. The rotational power output through the third variable input path (VIP3) and the second intermediate input path (MIP2) is received and shifted to the complementary operation to output through the final output path (OP), the shift of 5 forward It is done.

[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.

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 second clutch C2. ) Is transmitted to the tenth rotation element N10 of the third planetary gear set PG3 which forms the third variable input path VIP3.

Then, the second planetary gear set PG2 is in an idle state without any operation, and in the third planetary gear set PG3, the third clutch C3 is 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, the rotational force 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 third planetary gear set PG3. ) Receives the rotational power output through the first intermediate output path (MOP1) through the third variable input path (VIP3) by the operation of the second clutch (C2) and at the same time the rotational power of the input shaft (IS) By receiving the second variable input path (VIP2) by the operation of the third clutch (C3) 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 second clutch C2 operated in the sixth forward speed is released, and the fourth clutch C4 is controlled to operate.

Then, the first and second planetary gear sets PG1 and PG2 are in an idle state, and in the third planetary gear set PG3, the third shaft C3 is operated to input the input shaft IP to the eighth rotating element N8. Bar is directly connected to the operation of the fourth clutch C4 in the state that the rotational power is being input. Through the ninth rotation element N9 which is an output element, the seventh transmission line SP7 is formed as it is. As much as the output of D7, the shifting speed is 7th.

That is, the third planetary gear set PG3 is directly connected to the operation of the fourth clutch C4, and the rotational power of the input shaft IS input through the second variable input path VIP2 is maintained as it is. By outputting through OP), a shift of 7 forward speeds is achieved.

[8th forward]

At 8th forward speed, as shown in FIG. 2, the operation of the fourth clutch C4 is released and the first clutch C1 is controlled to operate in the state of the 7th 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, wherein the first clutch When the rotational power of the input shaft IS is directly input to the sixth rotating element N6 by the operation of C1, the fifth intermediate line forming the third intermediate output path MOP3 while forming the fourth speed line T4. 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 moved to the eighth operating element N8 by the operation of the third clutch C3 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 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 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. At the same time as receiving the MIP2, the rotational power of the input shaft IS is transmitted through the second variable input path VIP2 by the operation of the third clutch C3 and shifted to the complementary operation to the final output path OP. By outputting through), shifting of 8 forward speeds is achieved.

[9 speed forward]

At the 9th forward speed, as shown in FIG. 2, the operation of the first clutch C1 is released and the first brake B1 is controlled to operate in the 8th forward speed state.

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 In the planetary gear set PG2, the sixth rotating element N6 is operated as the fixed element by the operation of the first brake B1. The third intermediate output path MOP3 forms the third speed line T3. The rotational power which is decelerated and output through the fifth rotating element N5 forming a is input to the seventh rotating element N7 through the second intermediate input path MIP2.

Then, in the third planetary gear set PG3, while the input is made to the seventh rotation element N7, the rotational power of the input shaft IS is driven by the operation of the third clutch C3 to the eighth operation element N8. As the input is made, the 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 which is an output element intersect is made. As you build, 9 speeds will 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. When the rotational power output from the first intermediate output path (MOP1) is decelerated again by the operation of the first brake (B1) and decelerated output through the third intermediate output path (MOP3), the third planetary gear set ( PG3) receives the rotational power output through the third intermediate output path (MOP3) through the second intermediate input path (MIP2) and at the same time the rotational power of the input shaft (IS) through the second variable input path (VIP2) Receives the shift to the complementary operation and outputs through the final output path (OP), the shift of the 9 forward speed is made.

[10 speed forward]

At the 10th forward speed, as shown in FIG. 2, the first brake B1 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 third clutch C3, 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 second variable input path VIP2 by the operation of the third clutch C3 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.

[1 speed reverse]

In the reverse 1 speed, as shown in FIG. 2, the first brake B1 and the third brake B3 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 In the planetary gear set PG2, the sixth rotating element N6 is operated as the fixed element by the operation of the first brake B1. The third intermediate output path MOP3 forms the third speed line T3. The rotational power which is decelerated and output through the fifth rotating element N5 forming a is input to the seventh rotating 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 third brake B3 while the input is made to the seventh rotating element N7. A reverse shift line SR1 is formed, and a reverse shift output is performed as much as RS1 at which the reverse shift line SR1 and the vertical line of the ninth rotary element N9 intersecting the reverse shift line SR1 are made, so that the shift of the reverse 1 speed is made. Will be.

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 again by the operation of the first brake (B1) and decelerated output through the third intermediate output path (MOP3), the third planetary gear set ( PG3 receives the rotational power output through the third intermediate output path MOP3 through the second intermediate input path MIP2 and reverses the operation of the third brake B3 to reverse the final output path OP. By outputting through, reverse speed of 1 speed is achieved.

[2 speed reverse]

At the second forward speed, as shown in FIG. 2, the operation of the first brake B1 operated in the reverse first speed state is released, and the first clutch C1 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 first clutch (MOP1). By the operation of C1), it is transmitted to the sixth rotating element N6 of the second planetary gear set PG2 which forms the first variable input path VIP1.

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 first clutch C1 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 fourth speed line T4 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 eighth rotating element N8 is operated as a fixed element by the operation of the third brake B3 while the input is made to the seventh operating element N7. The second reverse shift line SR2 is formed, and the output of the second reverse speed line SR2 and RS2 where the vertical line of the ninth rotation element N9 that is the output element intersect is made. Will be done.

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. ) Receives 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) to complement each other When the output is reduced through the rotational power of the input shaft IS and output through the third intermediate output path MOP3, the third planetary gear set PG3 receives the second intermediate input path MIP2 and receives a third brake. By rotating in the reverse direction (B3) and outputting through the final output path (OP), the second shift speed is achieved.

4 to 7 illustrate gear trains according to the second, third and fifth embodiments of the present invention, all of which are configured in the same manner as the first embodiment, except that two of the third planetary gear sets PG3 are provided. The connection configuration of the fourth clutch (C4) to selectively connect the four rotating elements to make a direct connection state is different.

That is, in the second embodiment, as shown in FIG. 4, the fourth clutch C4 is disposed between the fourth sun gear S4, which is the tenth rotation element N10, and the third planet carrier PC3, which is the eighth rotation element N8. It is arranged in the rear of the third planetary gear set PG3.

In the third embodiment, as shown in FIG. 5, the fourth clutch C4 is disposed between the third planet carrier PC3, which is the eighth rotation element N8, and the third ring gear R3, which is the ninth rotation element N9. The fourth clutch C4 is disposed at the front side of the third planetary gear set PG3.

In the fourth embodiment, as in the third embodiment, the fourth clutch C4 uses the third planet carrier PC3, which is the eighth rotation element N8, and the third ring gear R3, which is the ninth rotation element N9. The fourth clutch C4 is disposed at the rear side of the third planetary gear set PG3 as shown in FIG. 6.

In the fifth embodiment, as shown in FIG. 7, the fourth clutch C4 is disposed between the third sun gear S3, which is the seventh rotation element N7, and the fourth sun gear S4, which is the tenth rotation element N10. The fourth clutch C4 is disposed on the front side of the third planetary gear set PG3.

In addition, since the fourth clutch C4 differs only in position from the first embodiment, only the variable position of the fourth planetary gear set PG3 is directly connected to the fourth clutch C4, and thus the shifting process is the same as in the first embodiment. Detailed description of the shifting process will be omitted.

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 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.

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

7 is a configuration diagram of a gear train according to a fifth embodiment of the present invention.

Claims (8)

A double pinion planetary gear set comprising: a first sun gear S1, which is a first rotating element N1, which always operates as a fixed element; and a first ring gear R1, which is a second rotating element N2, which is always decelerated. A first planetary gear set PG1 having a first planetary carrier PC1 which is a third rotating element N3 directly connected to the input shaft IS; A double pinion planetary gear set comprising: a second sun gear (S2), which is a fourth rotating element (N4) directly connected to the second rotating element (N2), and a reduction of rotational power input to the fourth rotating element (N4). And a second ring gear R2, which is a fifth rotary element N5, which is increased in speed and output, and is connected to each other via the third rotary element N3 and the first clutch C1. A second planetary gear set PG2 having a second planetary carrier PC2 interposed therebetween and connected to the transmission housing H; 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. ) Is connected via the third sun gear S3, which is the seventh rotation element N7 connected to the transmission housing H, and the input shaft IS and the third clutch C3, and is a one-way clutch F. ) And a third planet carrier PC3, which is an eighth rotation element N8 connected to the transmission housing H, via a third clutch C3 disposed in parallel to the transmission housing H, and a ninth rotation element connected to the output shaft OS. And a third ring gear R3, which is N9, and a fourth sun gear S4, which is a tenth rotation element N10 connected through the fourth rotation element N4 and the second clutch C2. The fourth clutch (C4) for selectively variably connecting any two rotary elements of the four rotary elements (N7), (N8), (N9) (N10) The third planetary gear set (PG3) of the vehicle automatic transmission gear train including a comparison made. The vehicle of claim 1, wherein the fourth clutch C4 is disposed between the seventh rotation element N7 and the eighth rotation element N8 and is disposed on the front side of the third planetary gear set PG3. Gear train of automatic transmission. The vehicle of claim 1, wherein the fourth clutch C4 is disposed between the seventh rotation element N7 and the eighth rotation element N8, but is disposed at the rear side of the third planetary gear set PG3. Gear train of automatic transmission. The vehicle of claim 1, wherein the fourth clutch C4 is disposed between the eighth rotation element N8 and the ninth rotation element N9, and is disposed on the front side of the third planetary gear set PG3. Gear train of automatic transmission. The vehicle of claim 1, wherein the fourth clutch C4 is disposed between the eighth rotary element N8 and the ninth rotary element N9, but is disposed at the rear side of the third planetary gear set PG3. Gear train of automatic transmission. The vehicle of claim 1, wherein the fourth clutch C4 is disposed between the seventh rotation element N7 and the tenth rotation element N10, and is disposed on the front side of the third planetary gear set PG3. Gear train of automatic transmission. 2. The first clutch C1 and the first brake B1 are disposed between the first and second planetary gear sets PG1 and PG2, and the second and third brakes B2 and B3. The fourth clutch C4 is disposed between the second and third planetary gear sets PG2 and PG3, and the second and third clutch C2 and C3 are disposed behind the third planetary gear sets PG3. Featuring a gear train of an automatic transmission for a vehicle. 2. The first clutch C1 and the first brake B1 are disposed between the first and second planetary gear sets PG1 and PG2, and the second and third brakes B2 and B3 are It is disposed between the second and third planetary gear sets PG2 and PG3, and the second and third clutches C2 and C3 and the fourth clutch C4 are disposed behind the third planetary gear sets PG3. Featuring a gear train of an automatic transmission for a vehicle.

Images