KR100802933B1 - A six-speed power train of an automatic transmission for a vehicle - Google Patents

Abstract

By appropriately distributing the brake and clutch to facilitate the formation of the flow path, and to provide a six-speed power train of the automatic transmission for a vehicle that can improve the driving performance by optimizing the gear ratio;

A double pinion planetary gear set, comprising: a first actuating element, optionally acting as an input, an output and a fixed element; A second actuating element which always acts as a stationary element; A first planetary gear set having a third actuating element, optionally acting as an input and an output element;

A planetary planetary gear set sharing a planetary carrier with a ring gear, comprising: a first actuating element variablely connected to each of the first and third actuating elements of the first oiling asset independently of the first gear element; A second actuating element, a third actuating element variably connected to the third actuating element of the first planetary gear set while always acting as an input element, and a second actuating element variably connected to the first actuating element of the first planetary gearset. A six-speed power train of an automatic transmission for a vehicle is provided by combining a second planetary gear set having four operating elements using five clutches and one brake.

Automatic transmission. clutch. Planetary Gear Sets

Description

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

1 shows an embodiment of a power train according to the invention.

Figure 2 is a work table for each shift stage of the friction element applied to the present invention.

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

Figure 4 is an embodiment of a conventional power train.

FIG. 5 is a table of operating elements of the power train according to FIG. 4. FIG.

The present invention relates to a six-speed powertrain of an automatic transmission for a vehicle applied to an automatic transmission for a vehicle to realize a six-speed transmission stage.

The vehicle automatic transmission detects the driving state of the vehicle from the detection means disposed in place of the vehicle, and based on this, the transmission control unit (TCU) automatically controls the power train composed of a combination of planetary gear sets to automatically control the vehicle. It is configured to carry out shifting.

Accordingly, the power train applied to the automatic transmission is preferably configured to implement more transmission stages in order to improve power performance and fuel consumption rate.

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 a planetary gear set, a new planetary gear set is not developed, but a simple combination of a conventional planetary gear set and a composite planetary gear set in some way, and the accompanying clutch and brake In addition, various studies have been actively conducted with the aim of realizing a desired shift stage and a shift ratio without any power loss by arranging several one-way clutches at any position.

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 shift is automatically performed according to the driving state. Therefore, more shift stages can be realized. Developing a power train is very important.

In order to cope with this trend, a variety of researches have recently been conducted on power trains that can realize a shift speed of six forward speeds or more.

As an example, as shown in Figure 4, three single pinion planetary gear set (PG1) (PG2) (PG3) is combined, the first planetary carrier 102 and the second ring gear 104 is connected, 2 is connected to the planet carrier 106 and the third ring gear 108, the first ring gear 110 and the third planet carrier 112 is connected.

The second sun gear 114 is directly connected to the input shaft 100, the first sun gear 116 is variably connected to the input shaft 100 via the first clutch C1, and the first planet carrier 102. Is variably connected to the input shaft 100 via the second clutch C2.

In addition, the third sun gear 118 is connected to the housing 120 via the first brake B1, and the first planet carrier 102 and the first sun gear 116 are the second and third brakes B2, respectively. It is connected to the housing 120 via (B3), the third planet carrier 112 is mounted with an output gear 122 to operate as an output element.

In the power train, as shown in FIG. 5, the first and second brakes B1 and B2 operate at the first forward speed, the first and third brakes B1 and B3 operate at the second speed, and at the third speed. The first clutch C1 and the first brake B1 operate, the second clutch C2 and the first brake B1 operate at the fourth speed, and the first and second clutch C1 (C2) at the fifth speed. ) Is operated, the second clutch C2 and the third brake B3 are operated at the sixth speed, and the first clutch C1 and the second brake B2 are operated at the reverse shift stage, and the forward six speeds and the reverse It is to realize the gear stage of 1 speed.

However, in the power train as described above, since both the clutch and the brake are disposed at the rear of the transmission, there is a problem in that the formation of the operation flow path is disadvantageous.

In addition, since the reverse speed ratio is small, the reverse climbing performance is disadvantageous, and because the speed ratio between the 2nd and 3rd stages is large, the tip shock is large in the downtown driving area of the low speed region, and the speed ratio of 1 forward speed is large, resulting in tire slip when starting. The low gear ratio at the gearshift stage implies a problem of poor driving force.

Therefore, the present invention has been invented to solve the above conventional problems, the object of the present invention is to facilitate the formation of the flow path by distributing the brakes and clutches appropriately, it is possible to optimize the step ratio to improve the operability To provide a six-speed power train for a vehicle automatic transmission.

In addition, since the drive is in the overdrive state at the 5th and 6th speed forward, it provides a 6-speed power train of the automatic transmission for a vehicle that can improve the high-speed driving performance.

In order to realize the above object, the present invention is a double pinion planetary gear set, comprising: a first operation element comprising a first sun gear, a second operation element consisting of a first ring gear, and a third operation consisting of a first planet carrier A first planetary gearset comprising an element;
A cabinet type planetary gear set comprising: a first actuating element comprising a second sun gear meshing with a short pinion, a second actuating element comprising a second ring gear, a third actuating element comprising a second planetary carrier, and a long pinion A second planetary gear set including a fourth operating element comprising a third sun gear meshing with the second sun gear,
The third actuating element of the second planetary gearset is directly connected to the input shaft, the output gear is connected to the second actuating element of the second planetary gearset, and the second actuating element of the first planetary gearset is connected to the transmission housing. In direct connection,
A first clutch for variably connecting the first actuating element of the first planetary gear set to the input shaft, and a variably connecting the first actuating element of the first planetary gearset to the fourth actuating element of the second planetary gearset A third clutch for variably connecting the first actuating element of the first planetary gearset to the first actuating element of the second planetary gearset, and a third actuation of the first planetary gearset A fourth clutch that variably connects the element to the first actuating element of the second planetary gear set, and a third actuating element of the first planetary gearset to the third actuating element of the second planetary gearset A clutch means comprising a fifth clutch;
A six-speed power train of an automatic transmission for a vehicle combined with a brake means including a first brake for variably connecting a first operating element of the first planetary gear set to a transmission housing.

delete

delete

delete

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

 1 illustrates an embodiment of a power train according to the present invention, wherein the power train of the present invention includes first and second planetary gear sets PG1 and PG2 disposed on the same axis, and five clutches C1. (C2), C3, C4, and C5, and a brake means comprising one brake B1.

Wherein the first planetary gear set (PG1) is composed of a double pinion planetary gear set having two pinions, the second planetary gear set (PG2) is a combination of a single pinion planetary gear set and a double pinion planetary gear set, It consists of a composite type planetary gear set of a combination of ring gears and planetary carriers.

The first planetary gear set PG1 includes a first operating element consisting of a first sun gear S1, a second operating element consisting of a first ring gear R1, and a third consisting of a first planetary carrier PC1. It includes an actuating element.

In addition, the second planetary gear set PG2 may include a first operating element including a second sun gear S2 meshed with the short pinion P1, and a second pin support P1 and the long pinion P2. A fourth operating element comprising a second operating element consisting of a planetary carrier PC2, a third operating element consisting of a second ring gear R2, and a third sun gear S3 engaged with the long pinion P2. It is made to include.

In combining the first and second planetary gear sets PG1 and PG2 as described above, the first sun gear S1, which is the first operating element of the first planetary gear set PG1, is connected to the input shaft IS and the first clutch. Variablely connected via (C1) to operate as a variable input element, the first ring gear (R1) of the second operating element of the first planetary gear set (PG1) is directly connected to the transmission housing (H). It can be operated as a fixed element at all times.

The first sun gear S1, which is the first actuating element of the first planetary gear set PG1, is interposed between the second and third clutch C2, C3, and the fourth actuating element of the second planetary gear set PG2. The third sun gear S3 and the second sun gear S2 which are the first operating elements are variably connected so that the output of the first sun gear S1 is selectively input to the third sun gear S3 and the second sun gear S2. It was made.

In addition, the first planetary carrier PC1, which is the third actuating element of the first planetary gearset PG1, may be disposed between the first and second planetary gearset PG2 through the fourth and fifth clutches C4 and C5. It is variably connected to the second sun gear S2, which is an operating element, and the second planet carrier PC2, which is a third operating element, and the second planet carrier PC2, which is the third operating element of the second planetary gear set PG2. Is also directly connected to the input shaft (IS).

In addition, an output gear OG is connected to the second ring gear R2, which is a second operating element of the second planetary gear set PG2, to operate as an output element at all times, the output gear OG of which is the final reduction gear. Although the structure for transmitting power to the differential device through the omission is omitted, such a structure can be used in the known, and also it is possible to realize the purpose of the present invention, whatever the structure of the structure will be omitted the detailed description will be omitted. .

In the power train of the present invention configured as described above, as shown in FIG. 2, each friction element is selectively operated, and shifting is performed.

In FIG. 3, the operating node on the lever of the first planetary gear set PG1 is set with three operating nodes N1, N2, and N3, and the first operating node N1 includes the first sun gear S1 and the first operating gear N1. The 2nd operation node N2 is set with the 1st ring gear R1, and the 3rd operation node N3 is set with the 1st planetary carrier PC1.

The operating node on the lever of the second planetary gear set PG2 is set with four operating nodes N4, N5, N6, and N7, and the fourth operating node N4 includes the second sun gear S2, The fifth operating node N5 is set with the second ring gear R2, the sixth operating node N6 with the second planet carrier PC2, and the seventh operating node N7 with the third sun gear S3.

As described above, the method for setting each operation node is known according to a combination configuration, which can be easily understood by a person skilled in the art of power train, and detailed description thereof will be omitted.

[1st speed forward]

In the forward 1 speed, as shown in FIG. 2, the third and fifth clutches C3 and C5 are operated and controlled.

Then, the rotational power input to the sixth operating node N6, which is the third operating element (second planetary carrier PC2) of the second planetary gear set PG2 by the operation of the fifth clutch C5, is directly applied to the first. It is input to the third operating element which is the third operating element of the planetary gear set PG1 (first planet carrier PC1).

In the first planetary gear set PG1, the second operating node N2, which is the second operating element {first ring gear R1}, is always operated as a fixed element and is connected to the first operating node N1 as an output element. Reverse rotation output is made.

Accordingly, the rotational power output to the first operating node N1 of the first planetary gear set PG1 is controlled by the operation of the third clutch C3 and thus the first operating element of the second planetary gear set PG2 {second The sixth operating node which is the third operating element (second planetary carrier PC2) of the second planetary gear set PG2 as described above in the state of being inputted through the fourth operating node N4 which is the sun gear S2}. As the rotational power of the input shaft IS is simultaneously input through the N6, a first speed line SP1 connecting the fourth operating node N4 and the sixth operating node N6 is formed, and the output element 5 As the output is made as D1 through the working node (N5), the speed change of the forward 1 speed is made.

delete

[2 speed forward]

At the second forward speed, the third and fifth clutches C3 and C5 operated in the state of the first forward speed are released, and the first and fourth clutches C1 and C4 are controlled to operate.

Then, when the input is made through the first operating node N1 which is the first operating element (first sun gear S1) of the first planetary gear set PG1 by the operation of the first clutch C1, a second is performed. The operation node N2 is operated as a fixed element, and thus the reverse rotation is output through the third operation node N3 as an output element.

Accordingly, the rotational power output to the third operating node N3 of the first planetary gear set PG1 is controlled by the fourth clutch C4 to operate the first operating element of the second planetary gear set PG2 {second Sixth operating node N6 which is the third operating element {second planetary carrier PC2) of the second planetary gear set PG2 while being input via the fourth operating node N4 which is the sun gear S2}. By simultaneously inputting the rotational power of the input shaft IS, a second speed line SP2 connecting the fourth operating node N4 and the sixth operating node N6 is formed, and the fifth operating node as an output element. As the output is made as D2 through (N5), the shift of the 2nd forward is made.

delete

[3 speed forward]

At the third forward speed, the first and fourth clutches C1 and C4 operated in the state of the second forward speed are released, and the third and fourth clutches C3 and C4 are controlled to operate.

Then, the second sun gear S2, which is the first operating element of the second planetary gear set PG2, is connected to both the first and third operating elements of the first planetary gear set PG1, thereby providing the first planetary gear set PG1. Becomes a fixed state, and accordingly, the second sun gear S2, which is the fourth operating node N4, operates as the fixed element.

Accordingly, the fourth operating node N4 is operated as a fixed element in the state where an input is made through the second planetary carrier PC2 which is the sixth operating node N6, and thus the sixth operating node N6 and the fourth A third speed line SP3 connecting the operating node N4 is formed, and the output is made as much as D3 through the fifth operating node N5, which is an output element, so that the transmission is made at the third forward speed.

[4 forward speed]

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

Then, as the second planetary gear set PG2 is directly connected by the operation of the second and third clutches C2 and C3, the fourth forward speed SP4 is formed to output as much as D4 as it is. A shift of 4 forward speeds is achieved.

[5th forward]

At the 5th forward speed, the operation of the third clutch C3 operated in the state of the 4th forward speed is released, and the first brake B1 is operated and controlled.

Then, the first planetary gear set PG1 is not operated by the operation of the first brake B1, and in this state, the fourth operation of the second planetary gear set PG2 is performed by the operation of the second clutch C2. A seventh operating node N7, which is an element {third sun gear S3}, operates as a fixed element.

Accordingly, the input is made through the sixth operating node N6 while the seventh operating node N7 is operated as a fixed element, and thus the forward connection connecting the seventh operating node N7 and the sixth operating node N6 is performed. The fifth speed line SP5 is formed, and as much as D5 is output as it is through the fifth operation node N5 which is an output element, a shift of five forward speeds is achieved.

[6th forward]

At the 6th forward speed, the operation of the first brake B1 operated in the state of the 5th forward speed is released, and the fifth clutch C5 is operated and controlled.

Then, the rotational power input to the sixth operation node N6, which is the third operation element (second planet carrier PC2) of the second planetary gear set PG2 by the operation of the fifth clutch C5, is directly applied. 1 An input is made through a third operating node N3, which is the third operating element of the planetary gear set PG1 (first planet carrier PC1).

In the first planetary gear set PG1, the second operating node N2, which is the second operating element {first ring gear R1}, operates as a fixed element, and thus, the first operating node N1 as an output element. ), The output of reverse rotation is achieved.

Accordingly, the rotational power output from the reverse rotation output to the first operating node N1 of the first planetary gear set PG1 is controlled by the second clutch C2 and thus the fourth operating element of the second planetary gear set PG2 { When the normal forward rotation input is made through the sixth operating node N6 while being input through the seventh operating node N7 which is the third sun gear S3}, the seventh operating node N7 and the seventh operating node N7 are made. The sixth speed line SP6 connecting the sixth operation node N6 is formed, and the output is made as much as D6 through the fifth operation node N5 which is an output element, and thus the sixth forward speed is shifted.

delete

[apse]

In the reverse direction, the second clutch C2 and the fourth clutch C4 are operated and controlled.

Then, the first operating node N1 and the second planetary gear set PG2 which are the first operating elements {first sun gear S1) of the first planetary gear set PG1 are operated by the second clutch C2. The seventh operating node N7, which is the fourth operating element {third sun gear S3}, is integrated and the third operating element of the first planetary gear set PG1 is operated by the operation of the fourth clutch C4. The third operating node N3, which is the first planetary carrier PC1}, and the fourth operating node N4, which is the first operating element (the second sun gear S2) of the second planetary gear set PG2, are integrated. .

Accordingly, as shown in the lever diagram of FIG. 3, the reverse speed line SR is formed by the complementary operation, and as the output is made as much as RS through the fifth operation node N5, which is an output element, the reverse shift is made.

In addition, in the shifting process as described above, it is possible to perform a skip shift. During the skip shift, the operation of one of the two friction elements that are currently operating is converted to the other friction element while maintaining the operation state. By doing so.

Accordingly, in the embodiment of the present invention, in the case of the skip down shift, the shift of 6 → 4, 5 → 3, 4 → 2, 3 → 1, 6 → 3, 5 → 2, 4 → 1 In the case of skip-up shift, it is possible to carry out in reverse order.

In the power train of the present invention in which the shift is performed as described above, the number of teeth of the first sun gear S1 and the first ring gear R1 is set to 35 and 80, and the second sun gear S2, the third sun gear S3, and the first When the number of teeth of the two ring gears R2 is 30, 40, 100, as shown in Fig. 2, 3.182 at 1st forward, 2.143 at 2nd forward, 1.429 at 3rd forward, 1.000 at 4th forward, 1.714 at 5th forward At 6th forward, it is set to 0.522 to optimize the gear ratio of each gear.

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 embodiment of the present invention. It includes all changes to the extent considered equivalent.

As described above, the power train of the present invention can facilitate the formation of the flow path by distributing the brakes and the clutches back and forth as compared with the related art, and can improve the operability by optimizing the gear ratio.

In addition, since the drive is in the overdrive state at the 5th speed and the 6th speed, it is an invention that can improve high-speed driving performance.

Claims (6)

A double pinion planetary gear set, comprising: a first planetary gear set including a first actuating element made of a first sun gear, a second actuating element made of a first ring gear, and a third actuating element made of a first planetary carrier; A cabinet type planetary gear set comprising: a first actuating element comprising a second sun gear meshing with a short pinion, a second actuating element comprising a second ring gear, a third actuating element comprising a second planetary carrier, and a long pinion A second planetary gear set including a fourth operating element including a third sun gear meshing with the second sun gear, The third actuating element of the second planetary gearset is directly connected to the input shaft, the output gear is connected to the second actuating element of the second planetary gearset, and the second actuating element of the first planetary gearset is connected to the transmission housing. In direct connection, A first clutch for variably connecting the first actuating element of the first planetary gear set to the input shaft, and a variably connecting the first actuating element of the first planetary gearset to the fourth actuating element of the second planetary gearset A third clutch for variably connecting the first actuating element of the first planetary gearset to the first actuating element of the second planetary gearset, and a third actuation of the first planetary gearset A fourth clutch that variably connects the element to the first actuating element of the second planetary gearset, and a third actuating element of the first planetary gearset to the third actuating element of the second planetary gearset A clutch means comprising a fifth clutch; And a brake means including a first brake for variably connecting the first operating element of the first planetary gear set to the transmission housing. delete delete delete delete delete

Images