KR100579274B1 - 7-shift power train in an automatic transmission for vehicles - Google Patents

Abstract

By adding only one clutch to the combination of three single-pinion planetary gear sets, it is advantageous to the gear ratio and the gear ratio ratio, and it is possible to easily realize the forward seven shoes with improved shift feeling by reducing operating elements during shifting;

The first ring gear and the second planet carrier, the second ring gear and the third planet carrier, the third ring gear and the first planet carrier are fixedly connected, respectively,

The first sun gear is selectively connected and fixed between the input shaft and the transmission case via a second clutch operating at fifth and sixth speeds and a first brake operating at first to fourth speeds, respectively. The two-wire gear is fixedly connected to the input shaft so as to operate as an input element at all times. Selectively connected and fixed through a third brake operating at seventh speed, and the second planetary carrier is interposed between the input shaft on the other side and the first clutch operating at the fourth and sixth speeds and the seventh speed. And the third planet carrier is selectively fixed and connected to the transmission case through a second brake operating at the reverse side and a one-way clutch operating at the first speed, and a third ringer. Provides a power train for a vehicle automatic transmission according to claim 7 in the configured by connecting at the other with the output gear.

Planetary gear set, input element, output element, power train

Description

7-SHIFT POWER TRAIN IN AN AUTOMATIC TRANSMISSION FOR VEHICLES}

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

2 is a friction element operating element table in the shifting process of the power train according to an embodiment of the present invention,

3 is a speed diagram of a lever analysis method visually showing a shifting process from the first speed to the fourth speed of the power train according to an embodiment of the present invention;

4 is a speed line diagram of a lever analysis method visually showing the shifting process of the fifth to seventh speeds and the reverse of the power train according to an embodiment of the present invention,

5 is a stick diagram illustrating one embodiment of a conventional seven-speed power train, and

6 is an operating element table of the friction element for shifting of FIG. 4.

The present invention relates to a power train of a seven-speed automatic transmission for a front wheel drive vehicle.

For example, the powertrain of the automatic transmission for vehicles is being developed and applied in different types according to each car maker. Currently, the automatic transmission that is commonly used is mainly composed of four-speed and five-speed transmission, but recently six-speed automatic While the transmission has been developed and applied to some vehicles, the development of a seven-speed automatic transmission is actively in progress.

As an example, as shown in FIG. 5, a single pinion planetary gear set and a combination of a combination of planetary type planetary gear sets are configured through three clutches and three brakes to enable 7-speed shifting.

More specifically, the single pinion planetary gear set 200 is disposed on the rear side of the composite planetary gear set 202, so that the first planetary carrier PC1 of the single pinion planetary gear set 200 is always operated as an input element. The third sun gear S3 of the composite planetary gear set 202 is directly connected to the input shaft 204 and the first ring gear R1 of the single pinion planetary gear set 200 is interposed with the first clutch C1. ) And at the same time, it was variably connected to the second sun gear (S2) of the composite planetary gear set 202 via the second clutch (C2).

The third planetary carrier PC3 of the composite planetary gear set 202 is connected to the input shaft 204 via a third clutch C3 to operate as a variable input element and at the same time, the second planetary carrier on the opposite side. PC2 is variably connected to the transmission case 206 via the first brake B1 to operate as an optional reaction force element, and the third ring gear R3 of the composite planetary gear set 202 is connected. It is connected to the output gear 208 to operate as an output element.

In addition, the second planetary carrier PC2 of the composite planetary gear set 202 is connected to the transmission case 206 via a one-way clutch OWC to prevent reverse rotation. The second sun gear of the compound planetary gear set 202 is connected between the clutch C2 and the second sun gear S2 of the compound planetary gear set 202 via the second brake B2 and connected to the transmission case 206. S2) to act as an optional reaction force element, the first sun gear (S1) of the single-pinion planetary gear set 200 is connected to the transmission case 206 via a third brake (B3) to the single-pinion planetary The first sun gear S1 of the gear set 200 is configured to operate as an optional reaction force element.

As shown in FIG. 6, the power train made as above is shifted while the first clutch C1 and the first and third brakes B1 and B3 are operated at the first speed, and at the second speed, In this state, the first brake B1 is released while the second brake B2 is operated to shift.

In the third speed, the second clutch C2 is operated while the second brake B2 is released in the state of the second speed, and the shift is performed. In the fourth speed, the second clutch C2 is performed in the third speed state. ) Is released, the third clutch (C3) is operated to shift.

In the fifth speed, the second clutch C2 is operated while the third brake B3 is released in the fourth speed, and the shift is performed. In the sixth speed, the first clutch C1 is performed in the fifth speed. ) Is released, the third brake (B3) is operated to shift.

In the seventh speed, the second clutch B2 is operated while the second clutch C2 is released in the sixth speed state, and the shift is performed, and in the reverse shift stage, the second clutch C2 and the first and third parts are performed. As the brakes B1 and B3 are operated, shifting is performed.

However, although the above-described power train can realize the forward 7 speed and the reverse 1 speed, the placement position of the third brake interferes with the flow path for supplying the working pressure to the first and second clutches in the actual layout design, which causes problems in practical use. There is this.

In addition, it is disadvantageous to Drag Torque because of the large radial type planetary gear set, which is difficult to control due to the large number of operating elements. There are disadvantageous problems.

Accordingly, the present invention has been invented to solve the above problems, and an object of the present invention is to provide a gear ratio and a simple ratio structure by adding only one clutch to a combination of three single-pinion planetary gear sets of a conventional six-speed power train. It is advantageous to provide a seven-speed automatic transmission that can easily realize forward seven-speed with improved shifting feeling by reducing operating elements during shifting.

Another object of the present invention is to combine the single pinion planetary gear set only to secure the durability of the planetary gear, to secure the productivity and design freedom, in the forward 4, 5, 6, 7 shift stage, it is possible to skip within three steps Therefore, the 7-speed automatic transmission is provided to improve the performance of the automatic transmission by improving the response.

In order to realize the above object, the present invention provides a power train of an automatic transmission for an all-wheel drive vehicle formed by combining a first, second, third single-pinion planetary gear set and a plurality of operating elements on an input shaft.

The first ring gear and the second planet carrier, the second ring gear and the third planet carrier, the third ring gear and the first planet carrier are fixedly connected, respectively,

The first sun gear is selectively connected and fixed between the input shaft and the transmission case via a second clutch operating at fifth and sixth speeds and a first brake operating at first to fourth speeds, respectively. The two-wire gear is fixedly connected to the input shaft so as to operate as an input element at all times. Selectively connected and secured via a third brake operating at seven speeds,

The second planetary carrier is selectively connected between the input shaft on the other side via the first clutch operating in the fourth and sixth speeds and the seventh speed, and the third planetary carrier is operated on the reverse side from the other side. It is to be selectively fixed and connected to the transmission case through the two-wheel and the one-way clutch operating in the first speed, the third ring gear is characterized in that it is configured by connecting to the output gear on the other side.

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

1 is a stick diagram of a power train according to an embodiment of the present invention, wherein the power train of the present invention is a first, second and third planetary gear set PG1 on an input shaft 2 connected to an engine output side via a torque converter. (PG2) and (PG3) are arranged in combination from the rear side to the front side.

The first planetary gear set PG1 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. It consists of a single pinion planetary gear set including a first planetary carrier (PC1) for rotatably supporting (P1).

The second planetary gear set PG2 includes a second sun gear S2, a second ring gear R2, and a second planetary gear meshed between the second sun gear S2 and the second ring gear R2. It consists of a single pinion planetary gear set including a second planetary carrier (PC2) for rotatably supporting (P2).

The third planetary gear set PG3 includes a third sun gear S3, a third ring gear R3, and a third planetary gear meshed between the third sun gear S3 and the third ring gear R3. It consists of a single pinion planetary gear set including a third planetary carrier (PC3) for rotatably supporting (P3).

The first, second and third planetary gear sets PG1, PG2 and PG3 are arranged in the order of the first, second and third planetary gear sets PG1, PG2 and PG3 from the rear side to the front side of the transmission. Among the above components, the first ring gear R1 and the second planetary carrier PC2, the second ring gear R2 and the third planet carrier PC3, the first planet carrier PC1 and the third ring The gears R3 are each fixedly connected.

A second sun gear S2 is fixedly connected to the input shaft 2 to operate as an input element at all times, and the first sun gear S1, the third sun gear S3, and the first ring gear R1 are also input shafts (S1). The second clutch C2, the third clutch C3, and the first clutch C1 are interposed between 2) and selectively act as an input element.

In this case, the first sun gear S1 and the third sun gear S3 are respectively disposed between the transmission case 4 and the first brake B1 and the third brake B3 to selectively operate as a fixing element. do.

In addition, the third planet carrier PC3 is connected to operate as a variable fixing element via the second brake B2 and the one-way clutch OWC disposed in parallel with the transmission case 4, and the third ring The gear R3 is equipped with an output gear 6 which always operates as an output element.

According to the above configuration, the first and second clutches C1 and C2 and the first brake B1 are located in the rear of the transmission case, and the third clutch C3 and the second and third brakes B2 and B3. ) Is disposed in front of the transmission case.

The power train configured as described above has the first brake B1 and the one-way clutch OWC at the first forward speed, the first and third brakes B1 and B3 at the second forward speed, as shown in the operation element table of FIG. 2. At the third speed, the third clutch C3 and the first brake B1 are operated, at the fourth forward speed, the first clutch C1 and the first brake B1, and at the fifth forward speed, the second clutch C2 and the third brake ( B3), 1st and 2nd clutch (C1) (C2) at 6th forward, 1st clutch (C1) and 3rd brake (B3) at 7th forward, and 3rd clutch (C3) and 2nd brake (B2) at reverse By operating), the shift stage of 7th forward and 1st reverse speed is realized.

The power train of the present invention combines three single pinion planetary gear sets, but includes a first ring gear (R1), a second planet carrier (PC2), a second ring gear (R2), and a third planet carrier (PC3). ), The third ring gear R3 and the first planet carrier PC1 are fixedly connected to each other, and are represented by six nodes NODE as shown in FIG. 3.

Accordingly, the first node N1 is the second sun gear S2, the second node N2 is the third sun gear S3, and the third node N3 is the first ring gear R1 and the second planet carrier. PC2), the fourth node (N4) is the second ring gear (R2) and the third planetary carrier (PC3), the fifth node (N5) is the first planetary carrier (PC1) and the third ring gear (R3), The six nodes N6 are set to the first sun gear S1.

3 and 4 visually show the shift process of the power train of the present invention by the lever analysis method, the first brake (B1) and the one-way clutch (OWC) is operated at the first forward speed.

Then, the first, second and third planetary gear sets are operated while the fourth node N4 and the sixth node N6 operate as fixed elements while the input is made through the first node N1 as the second sun gear S2. By the complementary action of (PG1) (PG2) (PG3) to form a speed line as shown in the first speed of Figure 3, the output is advanced as D1 through the fifth node (N5) output element One speed shift is achieved.
Although the second brake B2 is not operated and controlled in the first forward speed, it is because the one-way clutch OWC disposed for flexible shifting is operated, and the second brake B2 is Operational control with the one-way clutch (OWC) may be used.

In the second forward speed, the third brake B3 is operated and controlled in the state of the first speed.

Then, the first, second and third planetary gear sets are operated while the second node N2 and the sixth node N6 operate as fixed elements while an input is made through the first node N1 which is the second sun gear S2. By the complementary action of (PG1) (PG2) (PG3) to form a speed line as shown in the second speed diagram of Figure 3, the output is advanced as D2 through the fifth node (N5) output element Two speed shifts are achieved.

At the third forward speed, the operation of the third brake B3 is released in the state of the second speed, and the third clutch C3 is controlled to operate.

Then, the sixth node N6 operates as the fixed element while the input is simultaneously made through the first node N1 as the second sun gear S2 and the second node N2 as the third sun gear S3. Complementary action of the 1,2,3 planetary gear sets PG1, PG2, and PG3 forms a speed line as shown in FIG. 3, and through the fifth node N5 as an output element. As output is made as D3, shifting of 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 first clutch C1 is operated and controlled.

Then, the second planetary gear set PG2 is integrally rotated by simultaneously inputting through the first node N1, which is the second sun gear S2, and the third node N3, which is the second planetary carrier PC2. The sixth node N6 acts as a fixed element, and as a result of the complementary action of the first, second and third planetary gear sets PG1, PG2 and PG3, the same speed as in the fourth speed diagram of FIG. A line is formed, and the output is made as much as D4 through the fifth node N5, which is an output element, and the fourth forward speed is made.

At the 5th forward speed, the first clutch C1 and the first brake B1 are released at the same time in the state of the fourth speed, and the second clutch C2 and the third brake B3 are operated and controlled.

Then, input is simultaneously made through the first node N1, the second sun gear S2, and the sixth node N6, the first sun gear S1, and the second node N6 operates as a fixed element. By the complementary action of the first, second, and third planetary gear sets PG1, PG2, and PG3, outputs as much as D5 through the fifth node N5, which is an output element, as shown in FIG. This is accomplished by shifting five forward speeds.

At the sixth forward speed, the third brake B3 is released from the fifth speed state, and the first clutch C1 is controlled to operate.

Then, input is made through the first node N1, the second sun gear S2, the third node N3, the second planet carrier PC2, and the sixth node N6, the first sun gear S1. Since there is no fixed element, all of the first, second, and third planetary gear sets PG1, PG2, and PG3 are directly connected to each other, as shown in FIG. Through N5), the output is made by the same D6 as the input, and the 6th forward speed is made.

At the seventh forward speed, the second clutch C2 is released in the sixth speed state, and the third brake B3 is controlled to operate.

Then, the second planetary gear set PG2 is integrally rotated by simultaneously inputting through the first node N1, which is the second sun gear S2, and the third node N3, which is the second planetary carrier PC2. 4, the second node N2, which is the third sun gear S3, acts as a fixed element and is complemented by the first, second and third planetary gear sets PG1, PG2 and PG3. As shown in the figure, the speed line is formed, and the output is made as much as D7 through the fifth node N5, which is an output element, and the shift of the forward 7 speed is made.

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

Then, while the input is made through the first node N1, which is the second sun gear S2, and the second node N2, which is the third sun gear S3, the fourth node N4 operates as a fixed element, Complementary action of the 1,2,3 planetary gear sets PG1, PG2, and PG3 forms the same speed line as in the reverse shift diagram of FIG. 4, and is provided through the fifth node N5 as an output element. As the output is made by R, the reverse shift is made.

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

The power train of the present invention, which is shifted as described above, is set to 4.947 at 1st forward, 2.924 at 2nd forward, 1.908 at 3rd forward, 1.391 at 4th forward, 1.223 at 5th forward, 1.000 at 6th forward, and 0.792 at 7th forward, respectively. It is possible to optimize the gear ratio of the gear shift stage.

And, as shown in Fig. 3, the skip shift within three stages to deactivate one operating element and to operate one operating element, or to deactivate two operating elements and operation control of two operating elements. The skip shift can be made, thereby improving the shift performance of the automatic transmission.

More specifically, the 4 → 2 skip shifting may be performed by releasing the operation of the first clutch C1 in the state of 4 speed and operating the third brake B3, and the 5 → 2 skip shifting may be performed in the second state at 5 speed. The operation of the clutch C2 may be canceled and the first brake B1 may be operated. In the six to four skip shifts, the operation of the second clutch C2 may be canceled in the sixth speed state, and the first brake B1 may be released. It works.

In the 7 → 5 skip shifting operation, the first clutch C1 may be canceled in the 7th speed state, and the second clutch C2 may be operated. In the 7 → 4 skip shifting operation, the third brake B3 may be performed in the 7th speed state. In this case, the operation of controlling the operation of one operation element and releasing one operation element enables the skip shift.

In addition, the 5 → 3 skip shift releases the operation of the second clutch C2 and the third brake B3 at the state of 5 speed, and controls the operation of the third clutch C3 and the first brake B1, 6 → 3 skip shifting is performed by releasing the operation of the first clutch C1 and the second clutch C2 in the state of six speeds and controlling the operation of the third clutch C3 and the first brake B1. If the two operating elements are released and the two operating elements are operated and controlled, skip shifting is possible.

In addition, in the above 5 → 3 skip shifting, the operation of the second clutch C2 and the third brake B3 is released in the state of the fifth speed, and the operation of the third clutch C3 and the first brake B1 is controlled. The 6 → 3 skip shift is performed by releasing the operation of the first clutch C1 and the second clutch C2 in the state of 7 speeds and controlling the operation of the third clutch C3 and the first brake B1. Shifting can be achieved, but in this case, the two operating elements must be deactivated and the two operating elements must be operated and controlled. Therefore, it is difficult to control, so 5 → 4 → 3, or 6 → 4 → 3 It would be desirable to allow the shift to occur.

As described above, the power train of the present invention is advantageous in terms of the gear ratio and the short ratio ratio by adding only one clutch to the combination of three single-pinion planetary gear sets of the conventional six-speed power train, which are advantageous in terms of volume and weight. Its performance is improved and seven forward speeds can be realized simply by reducing operating elements when shifting.

In addition, the combination of only a single pinion planetary gear set ensures durability of the planetary gear, ensures productivity and design freedom, and enables skipping within 3 steps in forward 4, 5, 6, and 7 shifts. By improving, the performance of the automatic transmission can be improved.

In addition, it is possible to solve the conventional problem of disposing the position of the third brake to the front to obstruct the flow path for supplying the operating pressure to the first and second clutch when designing the actual layout.

Claims (5)

In a power train of an automatic transmission for an all-wheel drive vehicle formed by combining a first, second, third single-pinion planetary gear set and a plurality of operating elements on an input shaft, The first ring gear and the second planet carrier, the second ring gear and the third planet carrier, the third ring gear and the first planet carrier are fixedly connected, respectively, The first sun gear is selectively connected and fixed between the input shaft and the transmission case via a second clutch operating at fifth and sixth speeds and a first brake operating at first to fourth speeds, respectively. The two-wire gear is fixedly connected to the input shaft so as to operate as an input element at all times. Selectively connected and secured via a third brake operating at seven speeds, The second planetary carrier is selectively connected between the input shaft on the other side via the first clutch operating in the fourth and sixth speeds and the seventh speed, and the third planetary carrier is operated on the reverse side from the other side. Powertrain of a seven-speed automatic transmission for a vehicle, characterized in that the brake is selectively fixed and connected to the transmission case through a two-wheel and a one-way clutch operating at the first speed, and the third ring gear is connected to the output gear on the other side. . The seventh speed vehicle according to claim 1, wherein the third clutch and the second and third brakes are disposed at the front side in the transmission case, and the first, second clutch and the first brake are disposed at the rear side in the transmission case. Power train of automatic transmission. The power train of the seventh speed automatic transmission for a vehicle according to claim 1, wherein the one-way clutch is disposed in parallel with the second brake in a transmission case and connected to the third planet carrier through an inner race. The first brake and the one-way clutch operate at the first speed, the third brake operates at the first speed in the second speed, and the third brake operates at the second speed in the third speed. The third clutch is operated when the brake is released, and the fourth clutch is operated in the fourth speed while the third clutch is released in the third speed state, and in the fifth speed, the first clutch and the third clutch are operated in the fourth speed state. As the first brake is released, the second clutch and the third brake are operated, and in the sixth speed, the first clutch is operated while the third brake is released in the fifth speed, and in the seventh speed, the first clutch is operated. The third brake B3 is operated while the two clutches are released, and only the third clutch and the second brake are operated at the reverse shift stage to shift the vehicle. A. delete

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