KR100836913B1 - 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 gearset, wherein the first actuating element is variably connected to the input shaft and at the same time variably connected to the fourth actuating element of the second planetary gearset, and the second actuating element is directly connected to the second actuating element of the second planetary gearset. A first planetary gear set connected to the transmission housing and variably connected to the transmission housing, the first planetary gear being directly connected to the input and output, and variably connected to the fourth operating element of the second planetary gear set;

A cabinet type planetary gearset, wherein a first actuating element is variably connected with a transmission housing, a second actuating element is directly connected with a second actuating element of the first planetary gearset, and a third actuating element is connected with the output gear. A sixth speed of an automatic transmission for a vehicle, comprising a second planetary gear set connected to the fourth planetary member independently of the first and third actuators of the first planetary gearset and variably connected to the transmission housing. Provide a power train.

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 is a view showing an embodiment of a power train to which the present invention is applied.

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 order to realize the above object, the present invention provides a double pinion planetary gear set, comprising: a first planetary gear set having three actuating elements comprising a first sun gear, a first ring gear, and a first planet carrier;
A planet type planetary gear set comprising: a second sun gear meshing with a short pinion; a second ring gear meshing with a long pinion; a second planet carrier supporting short pinion and a long pinion; and a third gear meshing with a long pinion. Combining the second planetary gear set having four operating elements consisting of sun gear,
In a state where the first planetary carrier and the input shaft are directly connected, the first ring gear and the second ring gear are directly connected, and the second planetary carrier and the output gear are connected,
A first clutch for variably connecting an input shaft and the first sun gear, a second clutch for variably connecting the first sun gear and the third sun gear, and a third clutch for variably connecting the first planetary carrier and the third sun gear. Clutch means comprising;
A first brake for variably connecting the first ring gear to the transmission housing, a second brake for variably connecting the second sun gear to the transmission housing, and a third brake for variably connecting the third sun gear to the transmission housing. It provides a six-speed power train of an automatic transmission for a vehicle which is combined by a brake means.

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 three clutches C1. Clutch means comprising C2 and C3 and brake means comprising three brakes B1, B2 and B3.

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 PG2 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 planetary carrier PC1, which is the third operating element of the first planetary gear set PG1, is directly connected to the input shaft IS. In one state, the first ring gear R1, which is the second operating element of the first planetary gear set PG1, and the second ring gear R2, which is the second operating element of the second planetary gear set PG2, are directly connected. .

In addition, the first sun gear S1, which is the first operating element of the first planetary gear set PG1, is variably connected to the input shaft IS via the first clutch C1, and at the same time, the second planetary gear set ( The third sun gear S3, which is the fourth operating element of PG2), and the second clutch C2 are connected to each other.

In addition, the first planet carrier PC1, which is the third actuating element of the first planetary gear set PG1, is a third actuating element of the second planetary gear set PG2, via the third clutch C3. Connected to the sun gear (S3).

The first ring gear R1, which is the second operating element of the first planetary gear set PG1, is variably connected to the transmission housing h via the first brake B1, and the second planetary gear set is provided. The second sun gear S2, which is the first operating element of PG2, and the third sun gear S3, which is the fourth operating element, are independently provided with the transmission housing H through the second and third brakes B2, B3. It was variably linked.

An output gear OG is connected to the second planetary carrier PC2, which is the third operating element of the second planetary gear set PG2, to operate as an output element at all times, the output gear OG of which the final reduction gear Although a structure for transmitting power to the differential device is omitted, such a structure may be used in the known, and it may also realize the object intended by the present invention, whatever the structure of the structure 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. The first operating node N5 includes the first sun gear S1 and the first operating node N5. 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 provided with the second ring gear R2, the sixth operating node N6 is set with the first 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]

At the first forward speed, as shown in FIG. 2, the first brake B1 and the third clutch C3 are operated and controlled.

Then, the rotational power input to the first planetary carrier PC1, which is the third actuating element of the first planetary gearset PG1, by the operation of the third clutch C3, remains the third of the second planetary gearset PG2. As it is input to the sun gear S3, the input is made through the seventh operation node N7.

In addition, since the second ring gear R2 is operated as the fixed element by the operation of the first brake B1, the first forward speed SP1 is formed while the fifth operating node N5 is operated as the fixed element. By outputting as much as D1 through the sixth operation node N6, which is an element, the shift of the forward 1 speed is achieved.

[2 speed forward]

At the 2nd forward speed, the operation of the 1st brake B1 and the 3rd clutch C3 which were operated in the state of the said 1st forward speed is canceled | released, and the 3rd brake B3 and the 2nd clutch C2 are operated and controlled.

Then, the first sun gear S1 of the first planetary gear set OPG2 is operated as a fixed element according to the operation control of the third brake B3 and the second clutch C2. The first operating node (N1) is operated as a fixed element in the state that the input is made through, the deceleration output is made through the second operating node (N2) as the output element.

The second planetary gear set PG2 is connected to the second planetary gear set PG2 through a second ring gear R2 which is a fifth operation node N5 directly connected to the first ring gear R1 forming the second operation node N2. The input is made, and in this state, the third sun gear S3 is operated as a fixed element by the operation of the third brake B3.

Accordingly, the second speed line SP2 of FIG. 3 is formed, and outputs as much as D2 through the sixth operation node N6, which is an output element, thereby shifting forward two speeds.

[3 speed forward]

At the third forward speed, the operation of the third brake B3 and the second clutch C2 operated in the state of the second forward speed is released, and the second brake B2 and the third clutch C3 are operated and controlled.

Then, the rotational power input to the first planetary carrier PC1, which is the third actuating element of the first planetary gearset PG1, by the operation of the third clutch C3, remains the third of the second planetary gearset PG2. As it is input to the sun gear S3, the input is made through the seventh operation node N7.

In this state, the second sun gear S2 is operated as a fixed element by the operation of the second brake B2. As a fourth operation node N4 is operated as the fixed element, a third forward speed line SP3 is formed. By outputting as much as D3 through the sixth operation node N6, which is an output element, a shift of three forward speeds is achieved.

[4 forward speed]

At the fourth forward speed, both of the operations of the second brake B2 and the third clutch C3 operated in the state of the third forward speed are released, and the third brake B3 and the first clutch C1 are operated and controlled.

Then, the first planetary gear set PG1 is directly connected by the operation of the first clutch C1, and the second ring gear which is the second operating element of the second planetary gear set PG2 remains intact. As it is delivered to (R2), the input is made through the fifth working node (N5).

In this input state, the third sun gear S3 of the second planetary gear set PG2 becomes a fixed element by the operation of the third brake B3, and the seventh operating node N5 operates as the fixed element and moves forward 4. Speed line SP4 is formed, and as much as D4 is output through the sixth operation node N6, which is an output element, a shift of 4 forward speeds is achieved.

[5th forward]

At the 5th forward speed, the operation of the third brake B3 operated in the state of the 4th forward speed is released, and the second clutch C2 is operated and controlled.

Then, the first planetary gear set PG1 is directly connected by the operation of the first clutch C1, and the second planetary gear set PG2 is connected to the fifth operation node (C2) by the operation of the second clutch C2. Input is simultaneously made through N5) and the seventh operating node N7, resulting in a direct connection state.

Accordingly, the fifth forward speed SP5 is formed, and the output of the fifth forward speed SP5 is made as much as D5 as it is through the sixth operation node N6 as an output element, thereby shifting the fifth forward speed.

[6th forward]

At the 6th forward speed, the operation of the first clutch C1 operated in the state of the 5th forward speed is released, and the second brake B2 is operated and controlled.

Then, the first planetary gear set PG1 is directly connected by the operation of the first clutch C1, and the second ring gear, which is the second operating element of the second planetary gear set PG2, remains intact. As it is transmitted to (R2), the input is made through the fifth operating node (N5).

In this input state, the second sun gear S2 of the second planetary gear set PG2 becomes a fixed element by the operation of the second brake B2, and the fourth operating node N4 operates as the fixed element and moves forward. A speed line SP6 is formed, and as much as D6 is output through the sixth operation node N6, which is an output element, a shift of six forward speeds is achieved.

[apse]

In the reverse direction, the first brake B1 and the second clutch C2 are operated and controlled.

Then, in the first planetary gear set PG1, an input is made through the first planet carrier PC1, which is a third actuating element, and the first brake B1 is performed through the third actuating node N3. As the second operating node (N2) is operated as a fixed element by the operation of)) the reverse rotational power is output through the first operating node (N1) as the output element.

In addition, the reverse rotational power is input to the third sun gear S3 which is the fourth operating element of the second planetary gear set PG2 by the operation of the second clutch C2. The second ring gear R2 is operated as a fixed element by the operation of the first brake B1 in the state where the input is made through N7), and the backward speed line while the fifth operating node N5 is operated as the fixed element. SR is formed, and as much as RS is output through the sixth operation node N6 as an output element, the reverse shift is performed.

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 2, the number of teeth of the ring gear (R2) is 30, 40, 100, and as shown in Fig. 2, 3.500 at 1st forward, 2.489 at 2nd forward, 1.750 at 3rd forward, 1.400 at 4th forward, 1.000 at 5th forward At 6th forward speed, it is set to 0.700 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 is an invention that 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 step ratio.

Claims (8)

A double pinion planetary gear set, comprising: a first planetary gear set having three actuating elements comprising a first sun gear, a first ring gear, and a first planet carrier; A planet type planetary gear set comprising: a second sun gear meshing with a short pinion; a second ring gear meshing with a long pinion; a second planet carrier supporting short pinion and a long pinion; and a third gear meshing with a long pinion. Combining the second planetary gear set having four operating elements consisting of sun gear, In a state where the first planetary carrier and the input shaft are directly connected, the first ring gear and the second ring gear are directly connected, and the second planetary carrier and the output gear are connected, A first clutch for variably connecting an input shaft and the first sun gear, a second clutch for variably connecting the first sun gear and the third sun gear, and a third clutch for variably connecting the first planetary carrier and the third sun gear. Clutch means comprising; A first brake for variably connecting the first ring gear to the transmission housing, a second brake for variably connecting the second sun gear to the transmission housing, and a third brake for variably connecting the third sun gear to the transmission housing. A six-speed power train of an automatic transmission for a vehicle, characterized in that the combination by the brake means. delete delete delete delete delete delete delete

Images