KR20060001516A - A six-speed power train of an automatic transmission - Google Patents

Abstract

Power transmission efficiency by inputting two input speed ratios (direct coupling ratio and deceleration ratio) of the front single pinion planetary gear set (SPG) into rear planetary gear set (LPG) to include direct connection with each other. It provides a six-speed power train for the automatic transmission that improves the performance.

Automatic transmission. clutch. Planetary Gear Sets

Description

Six speed power train of automatic transmission {A SIX-SPEED POWER TRAIN OF AN AUTOMATIC TRANSMISSION}

1 is a schematic diagram of a power train according to an embodiment of the present invention;

2 is a table of the operating elements of the power train according to an embodiment of the present invention,

3 is a forward speed to three speed shift diagram of the power train according to the present invention,

4 is a forward four speed to sixth speed and a reverse shift diagram of the power train according to the present invention;

5 is a schematic diagram of a conventional power train,

6 is an operating element table of the power train according to FIG. 5, and

7 is a forward speed 1 to 6 speed and a reverse shift diagram of a conventional power train.

The present invention relates to a six-speed power train of an automatic transmission for a vehicle that is applied to an automatic transmission for a vehicle to realize a sixth forward speed and one reverse speed.

For example, the multi-speed gear mechanism of an automatic transmission is composed of a combination of a plurality of planetary gear sets, and a power train in which the plurality of planet gear sets is combined, when a rotational power is input from a torque converter that converts and transmits engine torque, is transmitted. It performs the function of transmitting to the output side by shifting to multiple stages.

Since the power train of the automatic transmission has more shift stages, it is advantageous in terms of power performance and fuel consumption rate, and thus, a power train capable of implementing more shift stages is required.

Also, even if the same number of gear stages are implemented, durability, power transmission efficiency, size and weight vary greatly depending on the combination method of the planetary gear set. Therefore, the power train can be more robust and compact while minimizing power loss. Efforts for development are ongoing.

In developing a power train using planetary gearsets, rather than developing any new planetary gearset, a combination of the existing single-pinion planetary gearset, double-pinion planetary gearset or single and double-pinion planetary gearset The combination of a planet type planetary gear set and the accompanying clutches, brakes, and one-way clutches can be arranged at any position to achieve the desired speed and the gear ratio without any power loss. Various studies are aimed at improving the target.

In particular, in the case of a manual transmission, if there are too many shift stages, the driver should shift frequently. However, in the case of an automatic transmission, the transmission control unit automatically controls the operation of the power train in accordance with the driving state to change the shift. As a result, developing a power train that can implement more shifts is of great value.

In order to cope with this trend, various researches on 4 speed and 5 speed power trains are being conducted, and in recent years, power trains of automatic transmissions capable of implementing 6 speed forward and 1 speed reverse gears have been provided.

As an example, as shown in FIG. 5, one single pinion planetary gear set (SPG) in front and one lavender type planetary gear set (LPG) in the rear are combined, but the single pinion planetary gear set (SPG) is combined. The first sun gear S1 is fixed to the transmission case 1, and the second (3) ring gear R2 (R3) of the planetary gear set LPG is mounted with an output gear OUT. Will work.

The first ring gear R1 of the single pinion planetary gear set SPG is directly connected to the input shaft 3, and connects the second and third planetary gears P2 and P3 of the rib planetary gear set LPG. The third planet carrier PC3 is variably connected to the input shaft 3 via the second clutch C2.

Further, the first planet carrier PC1 connecting the first planetary gear P1 of the single pinion planetary gear set SPG may have a first clutch between the third sun gear S3 of the rib planetary gear set LPG. They are variably connected to each other via (C1), which in turn are variably connected to each other via a third clutch (C3) between the second sun gear (S2).

In addition, the second sun gear S2 is connected to the transmission case 1 via the first brake B1 and connects the second and third planetary gears P2 and P3 of the rib planetary gear set LPG. The third planet carrier PC3 to be connected is connected to the transmission case 1 via a second brake B2 arranged in parallel with the transmission case 1 and a one-way clutch OWC.

In this power train, as shown in FIG. 6, the first clutch C1 and the one-way clutch OWC operate at the first forward speed, and the first clutch C1 and the first brake B1 operate at the second speed. In the third speed, the first clutch C1 and the third clutch C3 operate, and in the fourth speed, the first clutch C1 and the second clutch C2 operate, and in the fifth speed, the second and third clutches ( C2) (C3) is operated, the second clutch C2 and the first brake B1 are operated at the sixth speed, and the third clutch C3 and the second brake B2 are moved forward at the reverse shift stage. The sixth gear and the first gear of the reverse speed will be implemented.

However, in the power train as described above, as shown in Fig. 7, three planetary gears are powered by one second speed stage, and two planetary gears are powered and rotated by the first speed stage, first. There are three gears in the fourth and fifth gears, and only one planetary gear is powered by two gears in the third and sixth gears.

In other words, by excluding the stages in which all planetary gears are directly connected to each other, in terms of power transmission efficiency of the overall automatic transmission, it means that the power loss due to the cloud efficiency of the gear increases accordingly. It has some disadvantages in terms of efficiency.

Accordingly, the present invention has been invented to solve the disadvantages of the prior art, and an object of the present invention is to provide two input speed ratios (direct ratio and reduction ratio) of the front single-pinion planetary gear set (SPG) at the rear of the avenue. By providing a variety of input to the planetary gear set (LPG) to include a direct connection between each other, to provide a six-speed power train of the automatic transmission to improve the power transmission efficiency.

In order to realize the above object, the present invention provides a single pinion planetary structure comprising a first sun gear as a first actuating element, a first planet carrier as a second actuating element, and a first ring gear as a third actuating element. The gear set and the second and third sun gears as the fourth and fifth operating elements, the second and third planet carriers as the sixth operating elements, and one ring gear as the seventh operating elements as output elements, respectively. In the power train of the automatic transmission made by combining the combination of the planetary planetary gear set,

The first operating element is fixed to the transmission case, the fourth operating element is variably connected to the transmission case and the second operating element through the first brake and the third clutch, respectively, and the fifth operating element is connected to the third through the first clutch. Variable connection with the operating element, the third operating element is connected to one side of the seventh operating element through the second clutch again, and the sixth operating element is connected to the transmission case and the second brake through the other side is combined It is characterized by.

An input path through which power of an input shaft is transmitted to the single pinion planetary gear set and the rib planetary gear set, together with the third operating element, is input to the fifth operating element at a speed ratio; A second input path input to the fourth operating element via the second operating element at a reduction ratio together with the third operating element; And a third input path which is input to the sixth operating element at the same speed ratio together with the third operating element.

Each of the operating elements operates the first clutch and the second brake at the first speed, the second brake is released while the second brake is released in the state of the first speed at the second speed, and the second at the third speed. The third clutch is operated while the first brake is released in the state of fast speed, and the third clutch is operated in the state of third speed in the fourth speed, and the second clutch is operated while the third clutch is released, and the state of the fourth speed is in the fifth speed. The first clutch is released while the first clutch is released, and the first brake is operated while the third clutch is released in the state of the fifth speed in the sixth speed, and the third clutch and the second brake are operated in the reverse shift stage. It characterized in that the shift is made.

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

1 is a schematic diagram of a power train according to an embodiment of the present invention, in which the power train of the present invention has a first sun gear S1 and a first planet carrier in front of an input shaft 3 connected to an engine output side via a torque converter. Single pinion planetary gear set (SPG) consisting of PC1) and first ring gear (R1), and second and third sun gears (S2, S3), second and third planet carriers (PC2, PC3) and third ring Lavender planetary gear sets LPG made of gear R3 are arranged in combination with each other.

The single pinion planetary gear set SPG includes a first sun gear S1, a first ring gear R1, and a first planetary gear meshed between the first sun gear S1 and the first ring gear R1. And a first planetary carrier PC1 for rotatably supporting P1.

The planetary planetary gear set LPG is formed between the second sun gear S2, the third sun gear S3, the third ring gear R3, and the second sun gear S2 and the third ring gear R3. The second planetary gear P2 which rotatably supports the second planetary gear P2 to be engaged and the second planetary gear P2 and the third sun gear S3 that are meshed with the third ring gear R3. And a third planetary carrier PC3 rotatably supporting the third planetary gear P3 meshed therebetween with the second planetary gear P2.

In the arrangement of the planetary gear set, a single pinion planetary gear set (SPG) is disposed on the front side of the transmission, and a lavender planetary gear set (LPG) is disposed on the rear side of the transmission, and among the operating elements, a first operating element The sun gear S1, the second actuating element as the first planetary carrier PC1, the third actuating element as the first ring gear R1, the fourth actuating element as the second sun gear S2, The fifth operating element is the third sun gear S3, the sixth operating element is the second planetary carrier PC2 and the third planetary carrier PC3, and the seventh operating element is the third ring gear R3. In this case, of the operating elements, the first operating element is fixed to the transmission case 1.

The fourth operating element is variably connected to the transmission case 1 and the second operating element via the first brake B1 and the third clutch C3, respectively, and the fifth operating element is connected to the first clutch C1. Variable connection with the third operating element, the third operating element is variable connection with one side of the sixth operating element through the second clutch (C2) again, and again the sixth operating element to the transmission case (1) through the other side It is combined with the second brake B2.

That is, the first sun gear S1 is fixed to the transmission case 1 to act as a constant fixing element, and the second sun gear S2 is first brake to the transmission case 1 and the first planet carrier PC1. Through variable connection (B1) and the third clutch (C3) respectively to operate as a variable fixed element or a power transmission element.

The third sun gear S3 is variably connected to the first ring gear R1 via the first clutch C1 to act as a power transmission element, and the first ring gear R1 is directly connected to the input shaft 3. It acts as an input element at all times.

The third planet carrier PC3 is variably connected to the first ring gear R1 through the second clutch C2 to act as a power transmission element, and the second planet carrier PC2 is connected to the transmission case 1. In conjunction with the second brake (B2) acts as a variable fixing element.

The third ring gear R3 is connected to an output gear (not shown) to operate as an output element at all times.

In the power train having the above configuration, the single pinion planetary gear set SPG and the rib planetary gear set LPG have three input paths through which power is transmitted from the input shaft 3.

That is, at the first speed, the second speed, the third speed, and the fourth speed, the first clutch C1 variably connects the first ring gear R1 and the third sun gear S3. And a first input path through which power is transmitted at the same speed ratio.

The single pinion planetary gear set SPG is operated by the third clutch C3 which variably connects the first planet carrier PC1 and the second sun gear S2 at the third speed, the fifth speed, and the reverse stage. Has a second input path through which power is transmitted at a reduced gear ratio.

In addition, at the fourth speed, the fifth speed and the sixth speed, the same speed is directly connected by the operation of the second clutch C2 which variably connects the first ring gear R1 and the third planet carrier PC3. Rain has a third input path through which power is transmitted.

In the power train having three input paths, the first clutch C1 and the second brake B2 operate at the first forward speed and the second speed as shown in the operating element table shown in FIG. 2. In the first speed B1 is released while the second brake B2 is released in the state of the first speed, and the third clutch C3 is released when the first brake B1 is released in the state of the second speed. ) Is operated, and the fourth clutch C2 is operated while the third clutch C3 is released in the third speed stage in the fourth speed stage, and the first clutch C1 is operated in the fourth speed stage in the fifth speed stage. ) Is released and the third clutch C3 is operated. At the sixth speed, the third clutch C3 is released in the state of the fifth speed, and the first brake B1 is operated. The third clutch is operated at the reverse shift stage. By operating the C3 and the second brake B2, the shift stages of 6 forward speeds and 1 reverse speed are realized.

The shifting process of the power train according to the embodiment of the present invention described above will be described in more detail with reference to FIGS. 3 and 4.

First, irrespective of the acting element, as in the forward 1 to 6 speed and backward shift diagrams of the power train according to the present invention of FIGS. 3 and 4, the first node N1 is a third sun gear S3. ), The second node N2 is the third ring gear R3, the third node N3 is the second and third planet carriers PC2 and PC3, and the fourth node N4 is the second sun gear S2. The fifth node N5 is set to the first ring gear R1, the sixth node N6 is set to the first planet carrier PC1, and the seventh node N7 is set to the first sun gear S1.

Therefore, when an input is made through the fifth node N5 which is the first ring gear R1 of the single pinion planetary gear set SPG, the Ravi is made through the fifth node N5 which is the first ring gear R1. In the state where the input is transmitted to the third sun gear S3 of the new planetary gear set LPG, the third node N3 and the seventh node N7 operate as fixed elements, and the single pinion planetary gear set SPG and Complementary action of the planetary planetary gear set (LPG) to form a speed line as shown in the first speed diagram of FIG. 3, the output is advanced as D1 through the second node (N2) output element 1 The shift of the inside is made.

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

Then, an input is made through the fifth node N5, which is the first ring gear R1 of the single pinion planetary gear set SPG, and is simultaneously input to the third sun gear S3 of the rib planetary gear set LPG. This is done.

In this state, while the fourth node N4 and the seventh node N7 operate as fixed elements, the second pin of FIG. 3 is complemented by the single pinion planetary gear set SPG and the rib planetary gear set LPG. As shown in the figure, the speed line is formed, and the output is made as much as D2 through the second node N2, which is an output element, so that the speed of the second forward is made.

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

Then, input is made through the fifth node N5, which is the first ring gear R1 of the single pinion planetary gear set SPG, and at the same time, the Ravi is made through the sixth node N6, which is the first planet carrier PC1. The input is transmitted to the second sun gear S2 of the new planetary gear set LPG.

Accordingly, the fourth node (N4) acts as a fixed element in the planetary planetary gear set LPG, and the seventh node N7 operates as a fixed element in the single pinion planetary gear set SPG. As shown in the 3rd speed diagram of 3, the speed line is formed, and as the output is made by D3 through the second node N2 as the output element, the shift of the forward 3 is made.

At the fourth forward speed, the operation of the third clutch C3 is released in the state of the third speed, and the second clutch C2 is controlled to operate.

Then, the fifth node N5 which is the first ring gear R1 of the single pinion planetary gear set SPG and the third node which is the second and third planetary carriers PC2 and PC3 of the LPG planet An input is made in a state in which N3 and the first node N1, which is the third sun gear S3, and the third node N4, which is the third planet carrier PC3, are directly connected, and the first ring gear R1. In addition to the fifth node (N5), the input is made to the third sun gear (S3) and the third planet carrier (PC3) of the planetary gear set LPG.

Accordingly, the single pinion planetary gear set (SPG) and the rib planetary gear set (LPG) form a speed line as shown in FIG. 4 by the complementary action, and the second node N2 as an output element. ), The output is 1: 1 as D4, and the 4th speed change is made.

At the fifth forward speed, the first clutch C1 is released from the fourth speed state, and the third clutch C3 is operated.

Then, the sixth node N6, which is the first planetary carrier PC1 of the single pinion planetary gear set SPG, and the fourth node N4, which is the second sun gear S2 of the planetary gearset LPG, are actually The input is made by maintaining the direct connection state, and the input is transmitted to the third planet carrier PC3 of the planetary gear set LPG through the fifth node N5 which is the first ring gear R1, The fourth node N4, which is the second sun gear S2 of the new planetary gear set LPG, is actually operated as a fixed element.

Accordingly, the single pinion planetary gear set (SPG) and the rib planetary gear set (LPG) form a speed line as shown in the fifth speed drawing of FIG. 4 by complementary action, and the second node N2 as an output element. ), The output is as much as D5, and the 5th forward speed is made.

At the sixth forward speed, the third clutch C3 is released in the fifth speed state, and the first brake B1 is controlled to operate.

Then, the fifth node N5 which is the first ring gear R1 of the single pinion planetary gear set SPG and the third node which is the second and third planetary carriers PC2 and PC3 of the LPG planet The input is made while N3 is substantially directly connected, and the fourth node N4 and the second pinion planetary gear set SPG of the second planetary gear set LPG are connected. The seventh node N7, which is the first sun gear S1, operates as a fixed element and forms a speed line as shown in the sixth speed diagram of FIG. 4, and outputs D6 through the second node N2, which is an output element. This is achieved by shifting the sixth forward.

In the reverse shift stage, the third clutch C3 and the second brake B2 are operated and controlled.

Then, the sixth node N6, which is the first planetary carrier PC1 of the single pinion planetary gear set SPG, and the fourth node N4, which is the second sun gear S2 of the planetary gearset LPG, are actually The input is made by maintaining a direct connection, and the third node N3, which is the second and third planet carriers PC2 and PC3 of the planetary planetary gear set LPG, operates as a fixed element.

Accordingly, the single pinion planetary gear set (SPG) and the rib planetary gear set (LPG) form a speed line as shown in the backward view of FIG. 4 by the complementary action, and the second node N2 as an output element. The output is as much as R through the reverse shift.

Since the speed line for each planetary gear set is well known to those skilled in the art, detailed description thereof will be omitted.

Although the preferred embodiment of the power 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 from the embodiments of the present invention. It includes all changes to the extent considered equivalent.

As described above, the power train of the present invention inputs two input speed ratios (direct ratio and reduction ratio) of the front single pinion planetary gear set (SPG) to the rearward planetary gear set (LPG) in various ways. In this case, three planetary gears are powered and rotated by one third speed, and two planetary gears are powered and rotated by two second and fifth speeds. Only one planetary gear is powered and two stages are rotated into the first and sixth speed stages, and a fourth speed stage in which the planetary gears rotate integrally is formed.

Therefore, the planetary gears include the stages directly connected to each other, thereby reducing the power loss due to the cloud efficiency of the gears in terms of the power transmission efficiency of the overall automatic transmission, and thus the power transmission efficiency in terms of gear efficiency. There is an effect to improve.

Claims (9)

Single pinion planetary gear set comprising the first sun gear as the first actuating element in the front, the first planetary carrier as the second actuating element, and the first ring gear as the third actuating element; The combination of a planetary gear set consisting of sun gear as the fourth and fifth operating elements, the second and third planet carriers as the sixth operating element, and one ring gear as the seventh operating element as the output element, respectively. In the power train of the automatic transmission, The first operating element is fixed to the transmission case, the fourth operating element is variably connected to the transmission case and the second operating element through the first brake and the third clutch, respectively, and the fifth operating element is connected to the third through the first clutch. Variable connection with the operating element, the third operating element is again connected to one side of the sixth operating element via the second clutch, and again the sixth operating element is combined with the second brake to the transmission case on the other side is combined Featuring a six-speed power train with automatic transmission. The input path of claim 1, wherein power of an input shaft is transmitted to the single pinion planetary gear set and the rib planetary gear set. A first input path which is input to the fifth operating element at the same speed ratio together with the third operating element; A second input path input to the fourth operating element via the second operating element at a reduction ratio together with the third operating element; And a third input path inputted to the sixth operating element at the same speed ratio together with the third operating element. 6-speed power train of the automatic transmission, characterized in that consisting of. The method of claim 2, wherein the first input path The sixth speed power of the automatic transmission, characterized in that by the operation of the first clutch variably connects the third operating element and the fifth operating element at the first speed, the second speed, the third speed and the fourth speed. Train. The method of claim 2, wherein the second input path A sixth speed power train of an automatic transmission, wherein the third speed, the fifth speed, and the reverse speed are operated by a third clutch that variably connects the second and fourth operating elements. The method of claim 2, wherein the third input path The sixth speed train of the automatic transmission, characterized in that at the fourth speed, the fifth speed and the sixth speed, the second clutch variably connects one side of the third operating element and the sixth operating element. According to claim 1, wherein each of the operating element is the first clutch and the second brake is operated at the first speed, the second brake is released in the state of the first speed is the first brake is operated, In the third speed, the third clutch is operated while the first brake is released in the state of the second speed, and in the fourth speed, the second clutch is operated while the third clutch is released in the state of the third speed, and the fifth speed is In the fourth speed, the first clutch is released while the first clutch is released, and in the sixth speed, the third clutch is released while the third clutch is released in the fifth speed, and the third clutch is operated in the reverse shift stage. And a sixth speed train of the automatic transmission, wherein the second brake operates to shift. Single-pinion planetary gear set consisting of the first sun gear, the first planet carrier and the first ring gear in front, and the second planet gear of the second and third sun gear, second and third planet carrier and one ring gear in the rear. In the power train of an automatic transmission made by combining sets of The first sun gear is fixed to the transmission case, the second sun gear is variably connected to the transmission case and the first planet carrier through the first brake and the third clutch, and the third sun gear is connected to the first ring gear through the first clutch. Variable connection, the first ring gear is always the input element, and at the same time, the second planetary variable variable connection with the third planetary carrier, the second planetary carrier is connected to the second brake to the transmission case, the third A six-speed power train of an automatic transmission, characterized in that seven operating elements are combined by operating the ring gear as an output element. 8. The input path of claim 7, wherein power of the input shaft is transmitted to the single pinion planetary gear set and the rib planetary gear set. A first input path at a first speed, a second speed, a third speed, and a fourth speed, wherein power is transmitted at a speed ratio by an operation of a first clutch that variably connects the first ring gear and the third sun gear; A second input path through which power is transmitted at a reduction ratio by an operation of a third clutch that variably connects the first planet carrier and the second sun gear at the third speed, the fifth speed, and the reverse speed; At a fourth speed, a fifth speed, and a sixth speed, a third input path configured to transmit power at the same speed ratio by an operation of a second clutch that variably connects the first ring gear and the third planetary carrier. 6-speed power train with automatic transmission. According to claim 7, wherein each of the operating element is the first clutch and the second brake is operated at the first speed, the second brake is released in the state of the first speed at the second speed is the first brake is operated, In the third speed, the third clutch is operated while the first brake is released in the state of the second speed, and in the fourth speed, the second clutch is operated while the third clutch is released in the third speed, and in the fifth speed The third clutch is operated while the first clutch is released in the state of the fourth speed, and the first brake is operated while the third clutch is released in the state of the fifth speed in the sixth speed, and the third clutch and A six-speed power train of an automatic transmission, characterized in that the second brake is operated to shift.

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