KR100802936B1 - A six-speed power train of an automatic transmission for a vehicle - Google Patents

Abstract

By appropriately distributing brakes and clutches, it is possible to facilitate the formation of flow paths, optimize the step ratio, improve driving performance, and improve the backplate performance by making two reverse shifts 6 For the purpose of providing a powertrain;

A planetary planetary gear set comprising: a first actuating element that always acts as an input element; A first planetary gear set having second and third actuating elements, optionally acting as fixed and output elements, and a fourth actuating element acting as an optional stationary element;

A first pinion planetary gear set comprising three actuating elements, the first actuating element being variably connected to the second and third actuating elements of the first planetary gearset to always operate as an output element, and the first planetary gear. A second actuating element variably connected to the third actuating element of the set to operate as an optional input element, and a second actuating element variably connected to the second actuating element and always acting as a stationary element. It provides a six-speed power train for an automatic transmission for vehicles that combines a planetary gear set with four clutches and two brakes.

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 block diagram of a power train applied according to a first embodiment of the present invention.

2 is an operation table of the friction element applied to the present invention.

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

4 is a block diagram of a power train applied according to a second embodiment of the present invention.

5 is an embodiment of a conventional power train.

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

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 FIG. 5, three single pinion planetary gear sets PG1, PG2, and PG3 are combined, and the first planet carrier 102 and the second ring gear 104 are connected to each other. 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. 6, the first and second brakes B1 and B2 operate in the first forward speed, the first and third brakes B1 and B3 operate in the second speed, and in 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 In addition, the present invention provides a six-speed power train of an automatic transmission for a vehicle that can improve reverse climbing performance by two-speed reverse shift.

In order to realize the above object, the present invention,

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

 1 shows an embodiment of a power train according to the present invention, in which the power train of the present invention includes first and second planetary gear sets PG1 and PG2 arranged on the same axis, and four clutches C1. C2, C3, C4, and two brakes B1, B2.

Wherein the first planetary gear set (PG1) is a combination of a single pinion planetary gear set and a double pinion planetary gear set, consisting of a combination type planetary gear set of the combination of the ring gear and planetary carrier, so that the first 2 Planetary gear set PG2 consists of a double pinion planetary gear set with two pinions.

Accordingly, the first planetary gear set PG1 may include a first operating element including a first sun gear S1 meshed with the short pinion P1, a second operating element including a first ring gear R1, and A third operating element comprising a first planet carrier PC1 supporting the short pinion P1 and the long pinion P2, and a fourth operating element comprising a second sun gear S2 meshing with the long pinion P2. It is made, including.

The second planetary gear set PG2 includes a first operating element consisting of a third sun gear S3, a sixth operating element consisting of a third ring gear R3, and a third planetary carrier PC3. It consists of seven working elements.

In combining the first and second planetary gear sets PG1 and PG2 as described above, the second sun gear S2, which is the fourth operating element of the first planetary gear set PG1, is directly connected to the input shaft IS. It always works as an input element.

The first planetary carrier PC1, which is the third operating element of the first planetary gear set PG1, is a second ring gear that is the second operating element of the second planetary gear set PG2, via the first clutch C1. The first ring gear R1, which is variably connected to R2, and which is the second operating element of the first planetary gear set PG1, is disposed between the second planetary gear set PG2 via the second clutch C2. It was variably connected with the third working element, the second planet carrier (PC2).

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 transmission housing H via the first brake B1, and the first planetary gear set The first planet carrier PC1, which is the third operating element of PG1, is variably connected to the transmission housing H via the second brake B2.

The second planetary carrier PC2, which is the third actuating element of the second planetary gear set PG2, is fixedly connected to the transmission housing H, and the second actuating element that is the first actuating element of the second planetary gearset PG2. The third sun gear S3 is connected to the output gear OG as an output element and is the first operating element of the first planetary gear set PG1 via the third and fourth clutches C3 and C4. Variable connection was made independently of the ring gear R1 and the first planet carrier PC1, which is the third operating element.

The output gear (OG) connected to the third sun gear (S3) of the second planetary gear set (PG2) has a structure for transmitting power to the differential device through the final reduction gear, the structure of which can be known In addition, even if any other structure is used, the objective which this invention intends can be achieved, and detailed description is abbreviate | omitted.

In the power train of the present invention configured as described above, each friction element is selectively operated as shown in FIG. 2, and the shift is visually shown in FIG. 3.

In FIG. 3, four operating nodes N1, N2, N3, and N4 are set as operating nodes on the lever of the first planetary gear set PG1, and the first operating node N1 is the first sun gear S1. ), The second operating node (N1) is set by the first ring gear (R1), the third operating node (N1) by the first planetary carrier (PC1), and the fourth operating node (N4) by the second sun gear (S2). do.

The operating node on the lever of the second planetary gear set PG2 is set with three operating nodes N5, N6, and N7, and the fifth operating node N5 is the third sun gear S3 and the sixth operation. The node N6 has a second ring gear R2, and the seventh working node N7 has a second planet carrier PC2.

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]

First, in the forward 1 speed, as shown in FIG. 2, the second clutch C2 and the fourth clutch C4 are controlled to operate.

Then, the first ring gear R1, which is the second operating element of the first planetary gear set PG1, is operated by the operation of the second clutch C2 and the second planetary carrier PC2 of the second planetary gear set PG2. When connected, it acts as a stationary element.

Accordingly, the rotational power input through the fourth operating node N4, which is the fourth operating element {second sun gear S2} of the first planetary gear set PG1, is obtained by operating the second operating node N2 as a fixed element. The deceleration output is performed through the third operating node N3, which is the third operating element of the first planetary gear set PG1 (first planet carrier PC1).

In addition, the rotational power output through the third operating node N3 is a fifth operating element {third sun gear S3} of the second planetary gear set PG2 by the operation of the fourth clutch C4. The seventh operating node N7, which is transmitted to the operating node N5 and is the third operating element (second planetary carrier PC2) of the second planetary gear set PG2, is operated as the fixed element.

Accordingly, a first speed line SP1 connecting the fifth operating node N5 and the seventh operating node N7 is formed, and outputs as much as D1 through the fifth operating node N5 as an output element. This is achieved while the shift of the first forward speed is made.

[2 speed forward]

In the second forward speed, the second and fourth clutches C2 and C4 operated in the state of the first forward speed are released, and the first brake B1 and the third clutch C3 are controlled to operate.

Then, in the first planetary gear set PG1, the first operating element is operated by the operation of the first brake B1 in a state where an input is made through the fourth operating node M4 which is the fourth operating element {second sun gear S2}. The first operating node N1, which is the {first sun gear S1}, operates as a fixed element.

Accordingly, output is made through the second operating node N2 which is the second operating element {first ring gear R1} and the third operating node N3 which is the third operating element {first planet carrier PC1}. In this case, the fifth operating node N5 whose power of the second operating node N2 is the first operating element (third sun gear) of the second planetary gear set PG2 by the operation of the third clutch C3. Is delivered.

In the second planetary gear set PG2, the seventh operating node N7, which is the third operating element {the second planetary carrier PC2}, is operated as a fixed element, and thus the fifth operating node N5 and the seventh. A second speed line SP2 connecting the operating node N7 is formed, and as much as the output of D2 as it is, through the fifth operating node N5, which is an output element, the second speed line is shifted.

[3 speed forward]

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

Then, in the first planetary gear set PG1, the same operation is performed as in the second forward speed, while the second operating node N2 and the third operating element {first ring gear R1) which are the second operating element {first ring gear R1} are performed. The output is made through the third operating node N3, which is the planetary carrier PC1. At this time, the power of the third operating node N3 is controlled by the operation of the fourth clutch C4. The first operating element {third sun gear)} to the fifth operating node N5.

In the second planetary gear set PG2, the seventh operating node N7, which is the third operating element {the second planetary carrier PC2}, is operated as a fixed element, and thus the fifth operating node N5 and the seventh. A third speed line SP3 connecting the operating node N7 is formed, and the output of the third speed line 3 is made as the output of D3 is maintained as it is through the fifth operating node N5 which is an output element.

[4 forward speed]

At the fourth forward speed, both the operations of the first brake B1 and the fourth clutch C4, which were operated in the state of the third forward speed, are released, and the first and second clutches C1 and C2 are operated and controlled.

Then, the first ring gear R1, which is the second operating element of the first planetary gear set PG1, is operated by the operation of the second clutch C2 and the second planetary carrier PC2 of the second planetary gear set PG2. When connected, it acts as a stationary element.

Accordingly, the rotational power input through the fourth operating node N4 which is the fourth operating element {second sun gear S2} of the first planetary gear set PG1 is operated by the second operating node N2 as a fixed element. As a result, the deceleration output is performed through the third operation node N3 which is the third operation element (first planet carrier PC1) of the first planetary gear set PG1.

The rotational power output through the third operating node N3 is a second operating element (second ring gear R2) of the second planetary gear set PG2 by the operation of the first clutch C1. The sixth operating node N7, which is transmitted to the six operating node N6 and is the third operating element of the second planetary gear set PG2 (the second planetary carrier PC2), operates as a fixed element.

Accordingly, a fourth speed line SP4 connecting the sixth operating node N6 and the seventh operating node N7 is formed, and outputs as much as D4 through the fifth operating node N5 as an output element. As the 4th speed change is achieved.

[5th forward]

At the fifth forward speed, the first and second clutches C1 and C2 operated in the state of the fourth forward speed are released, and the third and fourth clutches C3 and C4 are controlled to operate.

Then, the first planetary gear set PG1 is directly connected to the third sun gear S3 of the second planetary gear set PG2 while being directly connected by the simultaneous operation of the third and fourth clutches C3 and 4. Will be delivered.

Accordingly, a fifth forward speed line SP5 connecting the fifth operating node N5 and the seventh operating node N7 of the second planetary gear set PG2 is formed, and the fifth operating node N5 as an output element is formed. By outputting as much as D5 as it is through the input, the five-speed forward is made.

[6th forward]

At the sixth forward speed, the third and fourth clutches C3 and C4 operated in the fifth forward speed are released, and the first brake B1 and the first clutch C1 are operated and controlled.

Then, in the first planetary gear set PG1 as in the forward 2 and 3 speeds, the first brake (B) is input in a state where an input is made through the fourth operating node M4 which is the fourth operating element (second sun gear S2). The operation of B1) causes the first operating node N1, which is the first operating element (first sun gear S1), to operate as a fixed element.

Accordingly, output is made through the second operating node N2 which is the second operating element {first ring gear R1} and the third operating node N3 which is the third operating element {first planet carrier PC1}. In this case, the sixth operating node (the second operating element {second ring gear) of the second planetary gear set PG2 is driven by the operation of the first clutch C1. N6).

In the second planetary gear set PG2, the seventh operating node N7, which is the third operating element {the second planetary carrier PC2}, is operated as a fixed element, and thus the sixth operating node N6 and the seventh. A sixth speed line SP6 connecting the operation node N7 is formed, and outputs as much as D6 through the fifth operation node N5, which is an output element, so that the sixth speed is shifted.

[1 speed reverse]

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

Then, in the first planetary gear set PG1, the third operating element is operated by the operation of the second brake B2 while the input is made through the fourth operating node M4, which is the fourth operating element {second sun gear S2). The third operating node N3, which is the {first planet carrier PC1}, is operated as the fixed element.

Accordingly, the output is made through the second operating node N2 which is the second operating element {first ring gear R1} and the first operating node N1 which is the first operating element {first sun gear S1}. In this case, the fifth operating node (the third operating gear S3) of which the power of the second operating node N2 is the first operating element (third sun gear S3) of the second planetary gear set PG2 by the operation of the third clutch C3. N5).

In the second planetary gear set PG2, the seventh operating node N7, which is the third operating element {the second planetary carrier PC2}, is operated as a fixed element, and thus the fifth operating node N5 and the seventh. The reverse 1 speed line SR1 connecting the operating node N7 is formed, and as much as the output of RS1 as the input is made through the fifth operating node N5, which is an output element, the shift of the reverse 1 speed is made.

[2 speed reverse]

In the reverse direction, the first clutch C1 and the third clutch C3 are operated and controlled.

Then, the third actuating node N3 and the second planetary gear set PG2 which are the third actuating elements (the first planet carrier PC1) of the first planetary gear set PG1 are operated by the first clutch C1. Of the second operating element of the first planetary gear set PG1 (the first ring gear R1) is integrated with the second operating element of the first planetary gear set PG1 by the operation of the third clutch C3. }, The first operating element (third sun gear S3) of the second operating node N2 and the second planetary gear set PG2 are integrated.

Accordingly, the reverse two-speed line is formed by the complementary operation, and as much as RS2 is output through the fifth operating node N5 which is the output element, the second-speed 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, shifts of 6 → 3, 6 → 4, 5 → 2, 5 → 3, 4 → 2 are possible as shown in FIG. Can be carried out in the reverse order.

In the skip down shift process as described above, 6 → 5 → 3 and 6 → 4 → 3 shifts can be used, but shifting to 6 → 5 → 3 is preferable to suppress inertia change and improve shifting feeling. Also, 5 → 4 → 2 and 5 → 3 → 2 shifts can be used for 5 → 2 shifts, but it is preferable to shift to 5 → 4 → 2 for suppressing inertia change and improving shift feeling.

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 The number of teeth of the ring gear R2 is set to 30, 40, 100, and as shown in Fig. 2, 3.500 at 1st forward, 2.500 at 2nd forward, 1.750 at 3rd forward, 1.531 at 4th forward, 1.000 at 5th forward In the 6th forward speed, it is set to 0.766 to optimize the gear ratio of each gear.

4 shows a second embodiment according to the present invention. In the first embodiment of the present invention, the third and fourth clutches C3 and C4 are disposed on the rear side of the second planetary gear set PG2. In the second embodiment, the third and fourth clutches C3 and C4 are arranged between the first and second planetary gear sets PG1 and PG2.

In addition, since the second embodiment differs only in the arrangement positions of the third and fourth clutches C3 and C4, the effect thereof is the same as that of the first embodiment, and thus the 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 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.

And it is an invention that can improve the reverse climbing performance by speeding up the reverse shift.

Claims (9)

delete delete delete delete delete delete A cabinet type planetary gear set, comprising: a first operating element comprising a first sun gear, a second operating element comprising a first ring gear, a third operating element comprising a first planet carrier, and a fourth consisting of a second sun gear A first planetary gear set having an actuating element; A double pinion planetary gear set, comprising a second planetary gear set having a first actuating element comprised of a third sun gear, a second actuating element comprised of a second ring gear, and a third actuating element comprised of a second planetary carrier. By the way, In a state in which the fourth operating element of the first planetary gear set is directly connected to the input shaft as an input element, and the first operating element of the second planetary gear set is connected to the output gear as an output element, A first clutch disposed between the third actuating element of the first planetary gearset and the second actuating element of the second planetary gearset, the second actuating element of the first planetary gearset and the second planetary gearset; A third clutch disposed between the third actuating element, a third clutch disposed between the second actuating element of the first planetary gearset and the first actuating element of the second planetary gearset, and of the first planetary gearset Clutch means including a fourth clutch disposed between the third actuating element and the first actuating element of the second planetary gearset; Brake means including a first brake disposed between the first actuating element of the first planetary gearset and the transmission housing and a second brake disposed between the third actuating element of the first planetary gearset and the transmission housing. 6-speed power train of an automatic transmission for a vehicle, characterized in that combined by. 8. The clutch of claim 7, wherein the first and second brakes are disposed on the front side of the first planetary gearset, the first and second clutches are disposed on the outer circumferential side of the first planetary gearset, and the third and fourth clutches are the second planetary planetary gears. A six-speed power train for an automatic transmission for a vehicle, characterized in that it is disposed at the rear of the gear set. 8. The clutch of claim 7, wherein the first and second brakes are disposed on the front side of the first planetary gearset, the first and second clutches are disposed on the outer circumferential side of the first planetary gearset, and the third and fourth clutches are the first planetary gear. A six-speed power train of an automatic transmission for a vehicle, characterized in that it is disposed between the gear set and the second planetary gear set.

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