KR101063501B1

KR101063501B1 - Gear train of automatic transmission for vehicles

Info

Publication number: KR101063501B1
Application number: KR1020100029440A
Authority: KR
Inventors: 서강수; 황성욱
Original assignee: 현대자동차주식회사
Priority date: 2010-03-31
Filing date: 2010-03-31
Publication date: 2011-09-07

Abstract

The present invention combines three single-pinion planetary gear sets with four clutches and two brakes so that three friction elements are operated at each shift stage, so that the forward 7 speed and the reverse 1 speed can be realized, thereby improving power transmission performance. To provide a gear train of an automatic transmission for a vehicle to reduce the fuel consumption and reduce fuel economy.

Description

GEAR TRAIN OF AUTOMATIC TRANSMISSION FOR VEHICLES}

The present invention relates to a gear train of an automatic transmission for a vehicle so that three simple planetary gear sets may be combined with four clutches and two brakes to realize a shift stage of at least seven forward speeds.

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 this automatic transmission, the more gears that can be implemented, the more appropriate the gear ratio can be designed and the vehicle can be realized in terms of power performance and fuel efficiency. .

And even if the same shift stage is implemented, the durability, power transmission efficiency, size, etc. of the gear train vary according to the combination method of the planetary gear set, and thus, to invent a more robust, power-free, and more compact gear train configuration Efforts are always going on.

In particular, unlike a manual transmission in which a shifting speed is more inconvenient for a driver, the automatic transmission shifts by controlling a gear train in accordance with a driving state. Efforts are being made to find a gear train configuration that can be implemented.

From this point of view, the four-speed and five-speed automatic transmissions are the mainstream automatic transmissions currently used, but the six-speed automatic transmission has been put into practical use in recent years, and a gear train capable of realizing more transmission stages. Development is taking place.

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 combine three simple planetary gear sets with four clutches and two brakes at least seven forward speeds. By providing a gear stage, it is possible to provide a gear train of an automatic transmission for a vehicle that simplifies the configuration of the automatic transmission, improves power transmission performance, and reduces fuel consumption.

In order to achieve the above object, the present invention provides a first planetary gear set PG1 including a first sun gear S1, a first planet carrier PC1, and a first ring gear R1; A second planetary gear set PG2 having a second sun gear S2, a second planet carrier PC2, and a second ring gear R2; The third planetary gear set PG3 including the third sun gear S3, the third planet carrier PC3, and the third ring gear R3 is provided with four clutches C1, C2, C3, and C4. Combination with two brakes (B1) (B2)

The input shaft IS is directly connected to the first ring gear R1, the first sun gear S1 is directly connected to the transmission housing H, and the second planet carrier PC2 and the third ring gear R3 are connected. With the direct connection to the output shaft (OS),

The first clutch C1 variably connects the first ring gear R1 and the second sun gear S2, and the second clutch C2 variably varies the first planet carrier PC1 and the second ring gear R2. The third clutch C3 variably connects the second sun gear S2 and the third sun gear S3, and the fourth clutch C4 connects the second sun gear S2 and the third planet carrier PC3. Variable connection, the first brake (B1) connects the third sun gear (S3) and the transmission housing (H), the second brake (B2) connects the third planetary carrier (PC3) and the transmission housing (H) It provides a gear train of an automatic transmission for a vehicle made.

The first, second and third planetary gear sets (PG1) (PG2) (PG3) is composed of a single pinion planetary gear set, the first, second and third planetary gear sets (PG1) (PG2) (PG3) is Characterized in that arranged sequentially from the engine side to the rear side.

In the above, the first and second clutches C1 and C2 are disposed between the first and second planetary gear sets PG1 and PG2 and the first and second brakes B1 and B2 and the third clutch C3. Is disposed between the second and third planetary gear sets PG2 and PG4, and the fourth clutch C4 is disposed at the rear side of the third planetary gear set PG3.

In the above, the first, second, third and fourth clutches C1, C2, C3 and C4 and the first and second brakes B1 and B2 are the second and third clutches C2 and C3 at the first forward speed. ) And the second brake (B2) is operated, the second, third clutch (C2) (C3) and the first brake (B1) is operated at the second forward speed, the second, fourth clutch (C2) at the third forward speed (C4) and the first brake (B1) is operated, the second, third, fourth clutch (C2) (C3) (C4) is operated at the fourth forward speed, the first, second, third clutch ( C1) (C2) (C3) is activated, the first, third and fourth clutches (C1) (C3) (C4) are operated at six forward speeds, and the first and fourth clutches (C1) (C4) at seven forward speeds. ) And the first brake (B1) is operated, the shift in the reverse as the first, third clutch (C1) (C3) and the second brake (B2) is operated.

As described above, by combining three simple planetary gear sets with four clutches and two brakes, a shift stage of at least seven forward speeds can be implemented to improve power transmission performance and improve fuel economy.

By distributing the friction elements, the flow path can be easily configured, and the weight balance of the automatic transmission can be improved.

These drawings are for the purpose of describing an exemplary embodiment of the present invention, and therefore the technical idea of the present invention should not be construed as being limited to the accompanying drawings.
1 is a block diagram of a gear train according to the present invention.
Figure 2 is an operation table for each shift stage of the friction element applied to the present invention.
Figure 3 is a shift diagram at the forward 1, 2, 4, 5 speed and the reverse gear stage of the gear train according to the present invention.
4 is a shift diagram at the speeds 3, 6 and 7 of the gear train according to the present invention.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings so that those skilled in the art may easily implement the present invention. The present invention may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein.

In order to clearly describe the present invention, parts irrelevant to the description are omitted, and like reference numerals designate like elements throughout the specification.

In the following detailed description, the names of the components are divided into first, second, and the like in order to distinguish the names of the components in the same relationship, and the descriptions of the components are not necessarily limited to the order in the following description.

1 is a block diagram of a gear train according to the present invention, in which the gear train according to the present invention includes first, second and third planetary gear sets PG1, PG2 and PG3 disposed on the same axis, and four clutches. And clutch means composed of (C1) (C2) (C3) and C4, and brake means composed of two brakes (B1) and (B2).

In the first planetary gear set PG1, the rotational power input from the input shaft IS is transmitted to the second planetary gear set PG2 at a slow speed or at the same speed, and the second and third planetary gear sets PG2 ( In the PG3), the rotational power transmitted from the first planetary gear set PG1 is shifted to the forward 7 speed and the reverse 1 speed according to the operation of the clutch and the brake and output through the output shaft OS.

To this end, the first planetary gear set PG1 is disposed to the engine side, and the second and third planetary gear sets PG2 and PG3 are sequentially disposed to 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 crank shaft of the engine 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 wheels are driven by a known differential device via an output gear.

The first planetary gear set PG1 is a single-pinion planetary gear set, and has three operating elements consisting of a sun gear, a planet carrier, and a ring gear as is known. For the 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.

The second planetary gear set PG2 is a single pinion planetary gear set, and has three operating elements consisting of a sun gear, a planet carrier, and a ring gear, as is well known. The planet carrier is referred to as the second planet carrier PC2 and the ring gear is referred to as the third ring gear R3.

The third planetary gear set PG3 is a single-pinion planetary gear set, which holds three operating elements consisting of a sun gear, a planet carrier, and a ring gear as known, and for the sake of explanation, the sun gear is referred to as a third sun gear S3, The planet carrier is referred to as a third planet carrier PC3 and the ring gear is referred to as a third ring gear R3.

The first planetary gear set PG1 has a first ring gear R1 directly connected to the input shaft IS to operate as an input element at all times, and the first sun gear S1 is directly connected to the transmission housing H. It is always operated as a fixed element, the first planetary carrier (PC1) is always the deceleration output is made as an output element.

In the second planetary gear set PG2, the second sun gear S2 is variably connected to each other via the first ring gear R1 and the first clutch C1 of the first planetary gear set PG1. Element and the second ring gear R2 is variably connected via the first planet carrier PC1 and the second clutch C2 of the first planetary gear set PG1 to operate as an optional input element. The second planet carrier PC2 is connected to the output shaft OS to operate as an output element.

In the third planetary gear set PG3, a third sun gear S3 is variably connected via a second sun gear S2 of the second planetary gear set PG2 and a third clutch C3 to selectively input the third planetary gear set PG3. Element and at the same time is variably connected to the transmission housing (H) via the first brake (B1) to operate as an optional fixed element, the third planet carrier (PC3) of the second planetary gear set (PG2) It is variably connected via the second sun gear S2 and the fourth clutch C4 to operate as an optional input element, and at the same time, it is variably connected to the transmission housing H via the second brake B2 to selectively It operates as a fixed element, the third ring gear (R3) is directly connected to the output shaft (OS) to operate as an output element.

In the above, the first, second, third and fourth clutches C1, C2, C3 and C4 and the first and second brakes B1 and B2 are made of a multi-plate hydraulic friction engagement unit friction-coupled by hydraulic pressure. Is common.

In arranging the friction member, the first and second clutches C1 and C2 are disposed between the first and second planetary gear sets PG1 and PG2, and the first and second brakes B1 and B2 and the first and second brakes C1 and C2. The third clutch C3 is disposed between the second and third planetary gear sets PG2 and PG4, and the fourth clutch C4 is disposed at the rear side of the third planetary gear set PG3.

By distributing the friction members as described above, it is possible to maintain a stable center of gravity, and there is an advantage in that it is very convenient to form a flow path for supplying hydraulic pressure to these friction members.

Figure 2 is an operating table showing that the friction member, that is, the clutch and the brake applied to the present invention operates in each shift stage, the gear train of the present invention is known that the shift is made while the three friction members operate in each shift stage. Can be.

That is, the second and third clutches C2 and C3 and the second brake B2 are operated at the first forward speed.

At the second forward speed, the second and third clutches C2 and C3 and the first brake B1 are operated.

At the third forward speed, the second and fourth clutches C2 and C4 and the first brake B1 are operated.

The second, third and fourth clutches C2, C3 and C4 are operated at four forward speeds,

The first, second and third clutches C1, C2 and C3 are operated at five forward speeds,

The first, third and fourth clutches C1, C3 and C4 are operated at six forward speeds,

At the seventh forward speed, the first and fourth clutches C1 and C4 and the first brake B1 are operated.

In reverse, the first and third clutches C1 and C3 and the second brake B2 are operated to shift.

Although the first, second, and third clutches C1, C2, and C3 are operated at the fifth forward speed, the third planetary gear set PG3 is not necessarily directly connected at the fifth forward speed. If necessary, the third clutch C3 may not be operated.

Figure 3 shows the shift diagram at the forward 1,2,4,5 speed and reverse shift stage of the gear train according to the present invention, the lower horizontal line represents the rotational speed "0", the upper horizontal line is 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 by the first rotating element {N1; First sun gear S1}, second rotating element N2; First planet carrier PC1}, third rotating element {N3; First ring gear (R1)}, and these intervals are determined according to the gear ratio (number of teeth of ring gear / number of ring gears) of the first planetary gear set PG1 forming the first planetary gear set PG1. .

In the forward 1,2,4,5 and reverse shift stages, the fourth clutch C4 is released and the third clutch C3 is operated. Thus, the second planet carrier PC2 and the third ring are operated. The second sun gear S2 and the third sun gear S3 are connected by the operation of the third clutch C3 while the gear R3 is directly connected.

Accordingly, the four vertical lines of the second and third planetary gear sets PG2 and PG3 are sequentially rotated from the left by the fourth rotating element {N4; 2nd, 3rd sun gear S2 (S3)}, the fifth rotating element {N5; Third planet carrier PC3}, sixth rotating element {N6; Second planet carrier PC2 and third ring gear R3}, seventh rotating element {N7; Second ring gear (R2)}, and these intervals are determined according to the gear ratio (number of teeth of the sun gear / number of rings) of the second and third planetary gear sets PG2 and PG3.

Figure 4 shows the speed change diagram of the gear train in the forward 3, 6, 7 speed shift stage of the present invention, the horizontal line on the lower side represents the rotation speed "0", the horizontal line on the upper side is the rotation speed "1.0" , The same rotation speed as the input shaft IS.

In addition, the third clutch C3 is released and the fourth clutch C4 is operated at the forward three, six, and seventh speed shift stages, and thus the second planet carrier PC2 and the third ring gear R3 are operated. The second sun gear S2 and the third planet carrier PC3 are connected by the operation of the fourth clutch C4 in a state in which the second clutch is directly connected.

Accordingly, the four vertical lines of the second and third planetary gear sets PG2 and PG3 are sequentially rotated from the left by the fourth rotating element {N4; Third sun gear S3}, fifth rotating element {N5; Second sun gear S2 and third planet carrier PC3}, sixth rotating element {N6; Second planet carrier PC2 and third ring gear R3}, seventh rotating element {N7; Second ring gear (R2)}, and these intervals are determined according to the gear ratio (number of teeth of the sun gear / number of rings) of the second and third planetary gear sets PG2 and PG3.

Since the rotation element setting of the shift diagram as described above is well known to those skilled in the art of a gear train, detailed description thereof will be omitted.

Hereinafter, a shift process of the gear train according to the present invention will be described.

[1st speed forward]

In the forward 1 speed, as shown in FIG. 2, the second and third clutches C2 and C3 and the second brake B2 are operated and controlled.

Then, in the first planetary gear set PG1, the first sun gear S1 is always operated as a fixed element in a state where an input is made to the first ring gear R1, which is the third rotating element N3. The deceleration output is made through the first planet carrier PC1, which is the element N2.

In this state, the rotational power which is decelerated and output of the second rotating element N2 by the operation of the second clutch C2 is input through the second ring gear R2 which is the seventh rotating element N7 as shown in FIG. 3. In this case, the third planetary carrier PC3, which is the fifth rotating element N5, is operated as a fixed element by the operation of the second brake B2, and thus the seventh rotating element N7 and the fifth rotating element N5 are provided. By forming the first shift line (SP1) connecting the output through the sixth rotation element (N6) as much as D1 output is made to be a forward 1 speed shift.

[2 speed forward]

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

Then, the fixing element is changed to the second and third sun gears S2 and S3 which are the fourth rotating elements N4 in the same state as the first forward speed, so that the seventh rotating element N7 and the fourth rotation as shown in FIG. 3. As the second shift line SP2 connecting the element N4 is formed, as much as D2 is output through the sixth rotation element N6, which is an output element, and thus the forward two-speed shift is performed.

[3 speed forward]

At the third forward speed, the third clutch C3 is released from the second forward speed, and the fourth clutch C4 is operated.

Then, unlike the forward 1,2 speeds in which the third clutch C3 is operated, the fourth clutch C4 is operated, and the shift is performed according to the shift diagram as shown in FIG. 4.

That is, as in the first and second speeds, the rotational power of the second rotary element N2 is input to the seventh rotary element N7, and the fourth rotary element N4 is operated as the fixed element. Although the same as, but the fourth rotation element (N4) is changed to the third sun gear (S3) while forming a third transmission line (SP3) connecting the seventh rotation element (N7) and the fourth rotation element (N4) Through the sixth rotating element N6, which is an output element, the output of D3 is made, so that the forward three-speed shift is made.

At this time, the same rotating element is operated as an input and a fixed element at the 2nd forward speed and the 3rd forward speed, and the shift ratio is different. In the forward 1,2, the fourth rotating element N4 is the second and third sun gear S2 and S3. Although the fifth rotating element N5 is composed of the third planetary carrier PC3, at the third forward speed, the fourth rotating element N4 is the third sun gear S3, and the fifth rotating element N5 is the second sun gear (3). S2) and the third planetary carrier PC3 are caused by the difference in the gear ratios of the second and third planetary gear sets PG2 and PG3.

In FIG. 3, A is a set position of the fifth rotating element N5 in FIG. 3, but the fifth rotating element N5 and the fifth rotating element N5 are formed by changing the components of the fourth and fifth rotating elements N4 and N5. As the distance between the six rotating elements N6 increases, the positions of the fourth and fifth rotating elements N4 and N5 are changed, thereby changing the speed ratio.

[4 forward speed]

At the fourth forward speed, the first brake B1 is released from the third forward speed and the third clutch C3 is operated.

Then, in the second and third planetary gear sets PG2 and PG3, the third and fourth clutches C3 and C4 operate simultaneously when the first brake B1 is released. And the second and third planetary gear sets PG2 and PG3 are in direct connection, so that the rotational power input from the second rotating element N2 to the seventh rotating element N7 is input as is. While forming the output through the sixth rotary element (N6) as the output of D4 is made to be a four-speed forward is made.

[5th forward]

At the 5th forward speed, the operation of the fourth clutch C4 is released in the state of the 4th forward speed, and the first clutch C1 is operated and controlled.

Then, when the output of the second rotary element N2 is input to the seventh rotary element N7 by the operation of the second clutch C2, the rotational power of the input shaft IS is increased by the operation of the first clutch C1. The fifth shift line SP5 connecting the seventh rotation element N7 and the fourth rotation element N4 is input to the second and third sun gears S2 and S3 which are the fourth rotation element N4. While forming the output as much as D5 through the sixth rotating element (N6) output element is to be a five-speed forward.

Although the third clutch C3 is described as operating at the fifth forward speed, there is no problem in the fifth forward speed shift even when the third clutch C3 is released.

[6th forward]

At the sixth forward speed, the second clutch C2 is released in the state of the fifth forward speed, and the fourth clutch C4 is controlled to operate.

Then, the output of the second rotating element N2 is prevented from being transmitted to the seventh rotating element N7 by releasing the operation of the second clutch C2, and the operation of the third and fourth clutches C3 and C4 is stopped. 2 and 3 planetary gear sets PG2 and PG3 are directly connected.

In addition, the rotational power of the input shaft IS is transmitted to the second sun gear S2 and the third planet carrier PC3, which are the fifth rotating elements N5, by the operation of the first clutch C1. ) And as much as D6 output as it is through the sixth rotating element (N6) as the output element is to be made six-speed forward.

[7th forward]

At the 7th forward speed, the operation of the third clutch C3 is released in the state of the 6th forward speed, and the first brake B1 is operated and controlled.

Then, when the rotational power of the input shaft IS is input to the fifth rotating element N5 as shown in FIG. 4 by the operation of the first clutch C1, the fourth rotating element ( The third sun gear S3, which is N4, is operated as the fixed element, and thus the seventh transmission line SP7 connecting the fifth and fourth rotary elements N5 and N4 forms an output element. As much as D7 is output through the six rotating elements N6, the seventh speed shift in the overdrive state is achieved.

[apse]

In the forward shift stage, the first and third clutches C1 and C3 and the second brake B2 are operated and controlled.

Then, the shift is performed in the speed change diagram as shown in FIG. 3 by the operation of the third clutch C3, wherein the rotation power of the input shaft IS is the fourth rotation element N4 by the operation of the first clutch C1. The third planet carrier PC3, which is the fifth rotating element N5, is operated as a fixed element by the operation of the second brake B2 while being input to the second and third sun gears S2 and S3. The reverse shift output is made as much as REV through the sixth rotating element N6 which is an output element while forming the reverse shifting line RS connecting the fifth rotating element N5 and the fourth rotating element N4. This will be done.

As described above, the preferred embodiments of the present invention have been described, but the present invention is not limited thereto, and various modifications and changes can be made within the scope of the claims and the detailed description of the invention and the accompanying drawings. Naturally, it is within the scope of the present invention.

PG1, PG2, PG3 ... 1st, 2nd, 3rd planetary gear set S1, S2, S3 ... 1st, 2nd, 3rd sun gear
PC1, PC2, PC3 ... First, 2,3 Planetary Carriers R1, R2, R3 ... First, 2,3 Ring Gears
IS ... Input shaft OS ... Output shaft

Claims

A first planetary gear set PG1 having a first sun gear S1, a first planet carrier PC1, and a first ring gear R1;
A second planetary gear set PG2 having a second sun gear S2, a second planet carrier PC2, and a second ring gear R2;
The third planetary gear set PG3 including the third sun gear S3, the third planet carrier PC3, and the third ring gear R3 is provided with four clutches C1, C2, C3, and C4. Combination with two brakes (B1) (B2)
The input shaft IS is directly connected to the first ring gear R1, the first sun gear S1 is directly connected to the transmission housing H, and the second planet carrier PC2 and the third ring gear R3 are connected. With the direct connection to the output shaft (OS),
The first clutch C1 variably connects the first ring gear R1 and the second sun gear S2,
The second clutch C2 variably connects the first planet carrier PC1 and the second ring gear R2.
The third clutch C3 variably connects the second sun gear S2 and the third sun gear S3,
The fourth clutch C4 variably connects the second sun gear S2 and the third planet carrier PC3.
The first brake B1 connects the third sun gear S3 and the transmission housing H,
The second brake (B2) is a gear train of the automatic transmission for a vehicle, characterized in that made by connecting the third planet carrier (PC3) and the transmission housing (H).

The gear train of an automatic transmission for a vehicle according to claim 1, wherein the first, second and third planetary gear sets (PG1) (PG2) and (PG3) consist of a single pinion planetary gear set.

2. The gear train of an automatic transmission for a vehicle according to claim 1, wherein the first, second and third planetary gear sets (PG1) (PG2) (PG3) are sequentially arranged from the engine side to the rear side.

2. The first and second clutches C1 and C2 are disposed between the first and second planetary gear sets PG1 and PG2, and the first and second brakes B1 and B2 and the third and third clutches C1 and C2. The clutch C3 is disposed between the second and third planetary gear sets PG2 and PG4, and the fourth clutch C4 is disposed at the rear side of the third planetary gear set PG3. Gear train.

The method of claim 1, wherein the first, second, third, and fourth clutches C1, C2, C3, C4, and the first and second brakes B1, B2 are configured as the second and third clutches at the first forward speed. C2) (C3) and the second brake (B2) are operated, the second and third clutches (C2) (C3) and the first brake (B1) at the second forward speed, the second, fourth at the third forward speed The clutches C2 and C4 and the first brake B1 are actuated, and the second, third and fourth clutches C2 and C3 and C4 are actuated at the fourth forward speed and the first and second at the fifth forward speed. , 3 clutches C1, C2 and C3 are operated, and the first, third and fourth clutches C1, C3 and C4 are operated at six forward speeds, and the first and fourth clutches are operated at seven forward speeds. C1) (C4) and the first brake (B1) is operated, the reverse of the vehicle automatic transmission characterized in that the first and third clutch (C1) (C3) and the second brake (B2) is operated while shifting. Gear crane.