JP2007085364A - Seven shift position powertrain for automatic transmission for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a seven sift position automatic transmission capable of realizing forward seven shift position of short overall length and easy layout design. <P>SOLUTION: This powertrain is provided with an input shaft and an output shaft arranged in parallel, a main transmission part having a simple planetary gear set and a complex planetary gear set combined, and having three clutches, two brakes and a one way clutch combined to make three operating elements of a first operation element or a seventh operation element operate as an input element and to make two operation elements operate as reaction elements is arranged on the input shaft, and a sub transmission part composed of a simple planetary gear set and having a clutch, a brake and a one way clutch combined to make one of the operation elements of an eighth operation element or a tenth operation element selectively operate as reaction element and to make one of the operation elements operated as an output element is arranged on the output shaft. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a seven-speed powertrain for a vehicle automatic transmission.

Powertrains for automatic transmissions for vehicles have been developed and applied in different formats by various automobile manufacturers, but currently the most commonly used automatic transmissions are mainly 4-speed and 5-speed transmissions. ing. Recently, a 6-speed automatic transmission has been developed and applied to some vehicles, while a 7-speed automatic transmission is being actively developed.
As an example, as shown in FIG. 5, a single pinion planetary gear set and a lavigne type compound planetary gear set are combined through three clutches and three brakes to enable a seven-speed shift.

More specifically, the single pinion planetary gear set 200 is arranged on the rear side of the compound planetary gear set 202, and the first planet carrier (PC1) of the single pinion planetary gear set 200 is always directly connected to the input shaft 204 so as to operate as an input element. Are connected. Further, the first ring gear (R1) of the single pinion planetary gear set 200 is connected to the third sun gear (S3) of the compound planetary gear set 202 via the first clutch (C1), and at the same time, the second clutch (C2) is interposed. The second planetary gear set 202 is variably connected to the second sun gear (S2).
Here, the side closer to the input is called the front side, and the side closer to the output is called the rear side.

  Then, the third planet carrier (PC3) of the compound planetary gear set 202 is connected to the input shaft 204 via the third clutch (C3) so as to selectively operate as the input element, and at the same time, the second planet carrier on the opposite side is connected. (PC2) is variably connected to the transmission case 206 via the first brake (B1) so as to selectively operate as a reaction force element, and the third ring gear (R3) of the compound planetary gear set 202 is output to the output element. The output gear 208 is connected to operate as follows.

  Further, the second planet carrier (PC2) of the compound planetary gear set 202 is connected to the transmission case 206 with a one-way clutch (OWC) interposed therebetween to prevent reverse rotation. Between the clutch (C2) and the second sun gear (S2) of the compound planetary gear set 202, the second sun gear (S2) of the compound planetary gear set 202 is connected to the transmission case 206 via a second brake (B2). ) Are selectively operated as a reaction force element, and the first sun gear (S1) of the single pinion planetary gear set 200 is connected to the transmission case 206 via the third brake (B3), so that the single pinion planetary gear set 200 is operated. The first sun gear (S1) of the gear set 200 is configured to selectively operate as a reaction force element.

As shown in FIG. 6, the power train configured as described above is operated at the first speed by operating the first clutch (C1) and the first and third brakes (B1, B3), and at the second speed. While the operation of the first brake (B1) is released in the state of the first speed, the second brake (B2) is operated to perform a shift.
At the third speed, the second clutch (C2) is operated while releasing the operation of the second brake (B2) in the second speed state, and the second clutch is operated at the fourth speed. While the operation of (C2) is released, the third clutch (C3) is operated to perform a shift.

At the fifth speed, the second clutch (C2) is operated while the operation of the third brake (B3) is released in the fourth speed state, and the first clutch is operated at the fifth speed at the sixth speed. While the operation of (C1) is released, the third brake (B3) is operated to perform a shift.
At the seventh speed, the second brake (B2) is operated while the operation of the second clutch (C2) is released in the sixth speed state, and a shift is performed. At the reverse speed, the second clutch (C2) and the first clutch The three brakes (B1, B3) are actuated to change the speed.
JP 2005-042790 A JP 2004-168295 A

  However, such a powertrain can achieve 7 forward speeds and 1 reverse speed, but by adding one brake to the existing 6-speed automatic transmission, all parts are long on one axis. Since it is arranged in the direction, there is a problem that the total length becomes long. Further, the increase in gear ratio increases the shared load applied to each planetary gear, clutch, and the like, resulting in a decrease in durability, which is disadvantageous in ensuring design flexibility.

The present invention has been made to solve such problems, and the object of the present invention is to divide and arrange all parts on two axes to shorten the overall length and facilitate layout design. It is an object of the present invention to provide a seven-speed automatic transmission that can realize seven forward speeds.
Another object of the present invention is to enable the load sharing by rotating the sub-transmission unit integrally at each gear stage, and to improve the durability of the planetary gear, and at the same time, the freedom of gear ratio selection. It is an object of the present invention to provide a seven-speed automatic transmission that can improve the performance of an automatic transmission by increasing the speed and enabling skip shift within three stages and improving the response.

  In order to achieve the above object, the present invention includes an input shaft and an output shaft arranged in parallel to each other, and on the input shaft, one simple planetary gear set and one compound planetary gear set are combined with each other. Three clutches, two actuating elements so that three of the first to seventh actuating elements are selectively actuated as input elements and two actuating elements are selectively acted as reaction force elements. A main transmission unit combined with a brake and one one-way clutch is disposed, and is configured by one simple planetary gear set on the output shaft, and operates one of three eighth to tenth operating elements. One clutch, one brake and one one-way clutch are combined so that the element selectively operates as a reaction force element and one actuating element acts as an output element. A sub-transmission unit is disposed, and each of the operating elements of the main transmission unit and the sub-transmission unit is connected to each other through an intermediate gear means so that power can be transmitted from the main transmission unit to the sub-transmission unit. It is characterized by being.

According to the seven-speed power train of the automatic transmission for a vehicle according to the present invention, the total length is shortened by arranging all the parts separately on two axes, and the layout design is easy, and the forward seven-stage is realized. be able to.
Then, the sub-transmission unit is rotated integrally at the forward 4, 5, 6, 7 shift stages to enable load sharing, and the durability of the planetary gear is improved, and at the same time, the degree of freedom of gear ratio selection is increased, Furthermore, the performance of the automatic transmission can be improved by enabling a skip shift within three stages and improving the responsiveness.

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

FIG. 1 is a configuration diagram of a power train according to an embodiment of the present invention, and FIG. 2 is an operation table of a friction element in a shifting process of the power train according to an embodiment of the present invention. The power train according to the embodiment of the present invention includes an input shaft 1 and an output shaft 3 arranged in parallel to each other.
A main transmission unit (A) is disposed on the input shaft 1, and a sub transmission unit (B) is disposed on the output shaft 3. The main transmission unit (A) and the sub transmission unit (B) are connected to each other through the intermediate gear device (C), and the output of the main transmission unit (A) is transmitted to the auxiliary transmission unit (B) through the intermediate gear device (C). Communicated.

The main transmission unit (A) includes one simple planetary gear set (SPG1) composed of a single pinion planetary gear set and one compound planetary gear set (LPG) composed of a ravine type planetary gear set.
The auxiliary transmission unit (B) includes one simple planetary gear set (SPG2) composed of a single pinion planetary gear set.
The power train according to the embodiment of the present invention includes a plurality of friction elements for controlling the operation of the main transmission unit (A) and the sub-transmission unit (B). According to one embodiment of the present invention, the plurality of friction elements include four clutches (C1, C2, C3, C4) and three brakes (B1, B2, B3).

The main transmission unit (A) has seven operating elements in which one simple planetary gear set (SPG1) and one compound planetary gear set (LPG) are combined with each other.
The simple planetary gear set (SPG1) includes a first sun gear (S1), a first ring gear (R1), and a first planetary gear (P1) meshing between the first sun gear (S1) and the first ring gear (R1). A first planet carrier (PC1) which is rotatably supported is included as its operating element.

  The compound planetary gear set (LPG) includes a second sun gear (S2), a second ring gear (R2), a third sun gear (S3), and a second pinion gear that meshes between the second sun gear (S2) and the second ring gear (R2). (P2) and a second planet carrier (PC2) that rotatably supports a third pinion gear (P3) that meshes between the third sun gear (S3) and the second pinion gear (P2) are included as operating elements. .

  Hereinafter, the third sun gear (S3) is set as the first operating element, the second ring gear (R2) is set as the second operating element, the second planet carrier (PC2) is set as the third operating element, and the second The sun gear (S2) is set as the fourth operating element. Then, the first ring gear (R1) is set as the fifth operating element, the first planet carrier (PC1) is set as the sixth operating element, and the first sun gear (S1) is set as the seventh operating element.

The first ring gear (R1) as the fifth operating element is fixedly connected to the input shaft 1 so as to act as an input element in a fixed manner, and the first sun gear (S1) as the seventh operating element is always It is fixedly connected to the transmission case 5 so as to act as a fixing element.
The third sun gear (S3), which is the first operating element, and the second sun gear (S2), which is the fourth operating element, selectively act as the input elements, so that the first planet carrier (PC1) that is the sixth operating element. ) Are variably connected to each other via the first clutch (C1) and the second clutch (C2).

The second planet carrier (PC2), which is the third operating element, is variably connected to the input shaft 1 via a third clutch (C3) so as to selectively act as an input element. On the other hand, the second planet carrier (PC2) is connected to the transmission case 5 via the first brake (B1) and the first one-way clutch (OWC1) arranged in parallel so as to selectively act as a reaction force element. Connected.
Further, the second sun gear (S2) as the fourth operating element is variably connected to the transmission case 5 via the second brake (B2) so as to selectively act as a reaction force element. The second ring gear (R2), which is the second operating element, is connected to the intermediate gear means (C) so as to act as an output element of the main transmission unit (A).

Here, the intermediate gear means (C) includes a transfer drive gear 7 connected to the main transmission unit (A), and a transfer driven gear 9 that meshes with the transfer drive gear 7 and is connected to the auxiliary transmission unit (B). The second ring gear (R2) of the main transmission (A) is fixedly connected to the transfer drive gear 7.
That is, in the main transmission unit (A), three operating elements of the seven operating elements on the input shaft 1 selectively operate as input elements, and two operating elements selectively operate as reaction force elements. Thus, it is combined with three clutches, two brakes, and one one-way clutch (OWC1).

The sub-transmission unit (B) that receives the transmission of power from the main transmission unit (A) is composed of one simple planetary gear set (SPG2) that is disposed on the output shaft 3 that is disposed in parallel with the input shaft 1.
The simple planetary gear set (SPG2) includes a fourth sun gear (S4), a third ring gear (R3), and a fourth pinion gear (P4) engaged between the fourth sun gear (S4) and the third ring gear (R3). A third planet carrier (PC3) which is rotatably supported is included as its operating element.
Hereinafter, the third ring gear (R3) is set as the eighth operating element, the third planet carrier (PC3) is set as the ninth operating element, and the fourth sun gear (S4) is set as the tenth operating element.

  The third ring gear (R3), which is the eighth operating element, is fixedly connected to the transfer driven gear 9 of the intermediate gear means (C) so as to operate as an input element of the auxiliary transmission unit (B). The third planet carrier (PC3), which is the ninth operating element, is fixedly connected to the output shaft 3 so as to always act as an output element, and at the same time, the fourth sun gear (S4), which is the tenth operating element. A fourth clutch (C4) is interposed between the fourth sun gear (S4) and the fourth sun gear (S4) so as to be selectively directly connected. The fourth sun gear (S4) is connected to the transmission case 5 via a third brake (B3) and a second one-way clutch (OWC2) arranged in parallel so as to selectively act as a reaction force element. The

That is, the auxiliary transmission unit (B) is configured such that one of the three operating elements is selectively operated as a reaction force element on the output shaft 3, and one operating element is operated as an output element. It is combined with one clutch, one brake, and one one-way clutch (OWC2).
The shift process of the power train configured as described above can be visually shown as shown in FIGS. 3 and 4 by lever analysis. In the main transmission section (A), there are no components in which at least two or more are fixedly connected to each other. Therefore, the first node (N1) is the third sun gear (S3), and the second node (N2) is the second. The ring gear (R2), the third node (N3) are set by the second planet carrier (PC2), the fourth node (N4) is set by the second sun gear (S2), and the fifth node (N5) is set by the first ring gear (R1). The sixth node (N6) is set by the first planet carrier (PC1), and the seventh node (N7) is set by the first sun gear (S1).

Also, since there is no component in which the two or more auxiliary transmission parts (B) are fixedly connected to each other, the eighth node (N8) is the third ring gear (R3), and the ninth node (N9) is the The third planet carrier (PC3) and the tenth node (N10) are set by the fourth sun gear (S4). Since this node setting is a well-known method well known to those skilled in the art, a detailed description thereof will be omitted.
3 and 4, the main transmission unit (A) and the sub-transmission unit (B) are connected to each other by the transfer drive gear 7 and the transfer-driven gear 9 that are the intermediate gear means (C), so that the sub-transmission unit (B) Are input in the reverse direction, but are shown as being input in the forward direction for convenience of explanation.

As described above, in the power train of the present invention in which each node is set by the lever analysis method, a shift is performed while each friction member is operated as shown in FIG.
More specifically, at the first forward speed, the first clutch (C1) and the first one-way clutch (OWC1) of the main transmission unit (A) operate, and the second one-way clutch (OWC2) of the auxiliary transmission unit (B). ) Is activated.

  In the simple planetary gear set (SPG1) of the main transmission (A), the first sun gear (S1), which is the seventh node, always acts as a fixed element, and the input is always performed through the first ring gear (R1). The carrier (PC1) always rotates at a speed decelerated from the rotational speed of the first ring gear (R1). In such a state, the third sun gear (S3) as the first node (N1) and the first planet carrier (PC1) as the sixth node may transmit power to each other by the operation of the first clutch (C1). The second planet carrier (PC2) which is the third node (N3) is operated as a reaction force element by the operation of the first one-way clutch (OWC1). Therefore, an output in a state where the speed is reduced to the maximum through the second ring gear (R2) which is the second node (N2) is performed.

  The decelerated power is input from the main transmission unit (A) through the third ring gear (R3) which is the eighth node (N8) of the auxiliary transmission unit (B), and the tenth node is operated by the operation of the second one-way clutch (OWC2). The fourth sun gear (S4) which is (N10) acts as a reaction force element. Accordingly, the first forward speed is realized while the output is performed only through D9 in FIG. 3 in the state of being decelerated to the maximum through the ninth node (N9) as the output element.

The second forward speed can be realized by operating the first clutch (C1), the second brake (B2), and the second one-way clutch (OWC2).
For example, if the operation of the first one-way clutch (OWC1) of the main transmission unit (A) is released and the second brake (B2) is controlled to operate in the control state of the first forward speed, the second speed is changed. Can be controlled.
Then, in the main transmission unit (A), the second sun gear (S2) as the fourth node (N4) acts as a reaction force element by the operation of the second brake (B2). Accordingly, output is performed through the second ring gear (R2), which is the second node (N2), in a state where the reduction ratio is smaller than the first forward speed.

  Accordingly, the decelerated power from the main transmission unit (A) is input through the third ring gear (R3), which is the eighth node (N8) of the sub-transmission unit (B), and the second one-way is the same as the first forward speed. The fourth sun gear (S4) as the tenth node (N10) acts as a reaction force element by the operation of the clutch (OWC2). Therefore, the second forward speed is realized while outputting only the D2 in FIG. 3 in which the reduction ratio is smaller than the first forward speed through the ninth node (N9) as the output element.

The third forward speed can be realized by operating the first clutch (C1), the second clutch (C2), and the second one-way clutch (OWC2).
For example, if the operation of the second clutch (C2) is controlled by releasing the operation of the second brake (B2) of the main transmission (A) in the control state of the second forward speed, the gear shift is performed to the third speed. Can be controlled.
Then, the third sun gear (S3), which is the first node, and the second sun gear (S2), which is the fourth node, are simultaneously connected to the first planet carrier (PC1), which is the sixth node, to form a compound planetary gear set (LPG). The whole is directly connected. Therefore, output is performed through the second ring gear (R2), which is the second node (N2), in a state where the reduction ratio is smaller than the second forward speed.

  Accordingly, the decelerated power from the main transmission unit (A) is input through the third ring gear (R3) which is the eighth node (N8) of the sub-transmission unit (B), and similarly to the first forward speed and the second forward speed. As a result of the operation of the second one-way clutch (OWC2), the fourth sun gear (S4) as the tenth node (N10) acts as a reaction force element. Therefore, the third forward speed is realized while outputting only D3 in FIG. 3 in which the reduction ratio is smaller than the second forward speed through the ninth node (N9) as the output element.

The fourth forward speed can be realized by operating the first clutch (C1), the second clutch (C2), and the fourth clutch (C4). For example, if the operation of the fourth clutch (C4) is controlled by releasing the operation of the second one-way clutch (OWC2) of the auxiliary transmission unit (B) in the control state of the third speed, the gear shift is performed to the fourth speed. Can be controlled.
Then, the main transmission unit (A) performs output under the same conditions as the third forward speed, and the sub-transmission unit (B) as a whole is directly connected by the operation of the fourth clutch (C4). Accordingly, the input from the main transmission unit (A) is output as it is through the ninth node (N9) as an output element, and output is performed only for D4 in FIG. 3 in which the reduction ratio is smaller than the third forward speed. The fourth forward speed is realized.

The fifth forward speed can be realized by operating the first clutch (C1), the third clutch (C3), and the fourth clutch (C4). For example, if the operation of the third clutch (C3) is controlled by releasing the operation of the second clutch (C2) of the main transmission unit (A) in the control state of the fourth speed, the gear shift is performed to the fifth speed. Can be controlled.
Then, the third sun gear (S3) that is the first node (N1) rotates at the same speed as the first planet carrier (PC1) that is the sixth node by the operation of the first clutch (C1), and the third node ( The second planet carrier (PC2) that is N3) rotates at the same speed as the input shaft 1 by the operation of the third clutch (C3). Therefore, output is performed through the second ring gear (R2), which is the second node (N2), at a reduction ratio smaller than that in the first, second, third, and fourth speed states.

  Power from the main transmission unit (A) having a rotational speed greater than forward speeds 1, 2, 3, and 4 is input through the third ring gear (R3) that is the eighth node (N8) of the auxiliary transmission unit (B). The sub-transmission unit (B) is brought into a directly connected state as in the fourth forward speed by the operation of the fourth clutch (C4). Therefore, the input from the main transmission unit (A) is output as it is through the ninth node (N9) which is the output element, and only the output D5 in FIG. 4 in which the reduction ratio is smaller than the fourth speed is performed. The fifth forward speed is realized.

The sixth forward speed can be realized by operating the second clutch (C2), the third clutch (C3), and the fourth clutch (C4). For example, if the operation of the first clutch (C1) of the main transmission unit (A) is released and the second clutch (C2) is operated and controlled in the control state of the fifth forward speed, the shift to the sixth speed is performed. Can be controlled.
Then, the second planet carrier (PC2) as the third node (N3) rotates at the same speed as the input shaft 1 by the operation of the third clutch (C3), and the second sun gear (the fourth node (N1)) S2) rotates at the same speed as the first planet carrier (PC1) as the sixth node by the operation of the second clutch (C2). Therefore, the output is performed in the overdrive state where the rotational speed is larger than the input rotational speed through the second ring gear (R2) which is the second node (N2).

Then, like the fourth and fifth forwards, the operation of the fourth clutch (C4) causes the entire sub-transmission unit (B) to be directly connected. Therefore, the input from the main transmission unit (A) is output as it is through the ninth node (N9) which is the output element, and the output is only D6 in FIG. 4 in the overdrive state in which the speed is increased from the rotational speed of the input shaft 1. 6 forward speeds are realized while being performed.
The seventh forward speed can be realized by operating the third clutch (C3), the second brake (B2), and the fourth clutch (C4). If the operation of the second brake (B2) is controlled by releasing the operation of the second clutch (C2) of the main transmission (A) in the control state of the sixth speed, control is performed so that the shift is performed to the seventh speed. be able to.

Then, in the main transmission unit (A), the second planet carrier (PC2), which is the third node (N3), rotates at the same speed as the input shaft 1 by the operation of the third clutch (C3), and the fourth node (N4 The second sun gear (S2) is operated as a reaction force element by the operation of the second brake (B2). Therefore, the output is performed in the overdrive state where the rotational speed is larger than the input rotational speed through the second ring gear (R2) which is the second node (N2).
In such a forward seventh speed state, since both the first clutch (C1) and the second clutch (C2) do not operate, the simple planetary gear set of the main transmission unit (A) is disconnected from the compound planetary gear set. Rotate independently of each other.

As a result of the operation of the fourth clutch (C4), the entire sub-transmission unit (B) is brought into a directly connected state. Accordingly, the input from the main transmission unit (A) is output as it is through the ninth node (N9) which is the output element, and only the output D7 in FIG. 4 in the overdrive state is output, and the seventh forward speed is realized. .
In order to realize the reverse gear, only the second clutch (C2) and the first brake (B1) are controlled in the main transmission (A), and the third brake (B3) is controlled in the auxiliary transmission (B). Only) is controlled.
Then, the second sun gear (S2) as the fourth node (N4) is connected to the first planet carrier (PC1) as the sixth node by the operation of the second clutch (C2).

At this time, the second planet carrier (PC2) which is the third node (N3) acts as a reaction force element by the operation of the first brake (B1). Therefore, reverse rotation output is performed in a state where the vehicle is decelerated through the second node (N2) that is the output element.
The reverse rotation power from the main transmission unit (A) is input through the third ring gear (R3) which is the eighth node (N8) of the sub-transmission unit (B), and the fourth sun gear (S4) which is the tenth node (N10). ) Acts as a reaction force element by actuation of the third brake (B3). Therefore, the reverse shift is performed while the reverse rotation output is performed by R in FIG. 4 in a reduced state through the ninth node (N9) which is the output element.

The following table shows the speed change process as described above, that is, the relationship between the deceleration, the same speed, and the acceleration.

Then, as shown in FIGS. 2 to 4, the skip shift within 3 speeds can be achieved by deactivating one actuating element and controlling one actuating element or deactivating two actuating elements. This can be done by a method of controlling the operation of one or two operating elements, and the shift performance of the automatic transmission can be improved.
More specifically, the 3 → 1 skip shift is performed by releasing the operation of the second clutch (C2) of the main transmission (A) and controlling the operation of the first brake (B1) in the state of the third speed. Can do. The 6 → 4 skip shift can be performed by releasing the operation of the third clutch (C3) of the main transmission unit (A) and controlling the operation of the first clutch (C1) in the sixth speed state. The 7 → 5 skip shift can be performed by releasing the operation of the second brake (B2) of the main transmission unit (A) and controlling the operation of the first clutch (C1) in the seventh speed state. That is, if one operating element is released and the other one operating element is controlled, the skip shift can be performed.

  In the 4 → 2 skip shift, the fourth clutch (C4) of the sub-transmission unit (B) is released in the state of the fourth speed to control the operation of the second one-way clutch (OWC2), and the main transmission unit (A) The second clutch (C2) can be released and the second brake (B2) can be controlled to operate. In the 5 → 3 skip shift, the fourth clutch (C4) of the sub-transmission unit (B) is released to control the operation of the second one-way clutch (OWC2) in the state of the fifth speed, and the second transmission of the main transmission unit (A) is controlled. The operation can be performed by releasing the operation of the third clutch (C3) and controlling the operation of the second clutch (C2).

In the 5 → 2 skip shift, the fourth clutch (C4) of the sub-transmission unit (B) is released to control the operation of the second one-way clutch (OWC2) in the state of the fifth speed, and the main transmission unit (A) The operation can be performed by operating the second brake (B2) by releasing the operation of the third clutch (C3). In the 6 → 3 skip shift, the fourth clutch (C4) of the sub-transmission section (B) is released in the sixth speed state to control the operation of the second one-way clutch (OWC2), and the main transmission section (A) The operation can be performed by operating the first clutch (C1) by releasing the operation of the three clutch (C3). That is, if the two operating elements are released and the two operating elements are controlled, the skip shift can be performed.
In addition, the 7 → 4 skip shift is performed by releasing the operation of the third clutch (C3) and the second brake (B2) and controlling the operation of the first and second clutches (C1, C2) in the seventh speed state. be able to.

1 is a configuration diagram of a power train according to an embodiment of the present invention. FIG. 3 is an operation table of a friction element in a power train shifting process according to an embodiment of the present invention; It is a velocity diagram of the lever analysis method which showed visually the speed-change process from the 1st speed of the powertrain by the embodiment of the present invention to the 4th speed. FIG. 6 is a velocity diagram of a lever analysis method visibly showing the fifth to seventh speeds of the powertrain according to the embodiment of the present invention and the speed change process during reverse travel. It is the block diagram which showed one Embodiment of the conventional 7-speed power train. 6 is an operation table of friction elements for shifting in FIG. 5.

Explanation of symbols

1 Input shaft 3 Output shaft 5 Transmission case 7 Transfer drive gear 9 Transfer driven gear 200 Single pinion planetary gear set 202 Compound planetary gear set 204 Input shaft 206 Transmission case 208 Output gear B1, B2, B3 First, second, third brake C1, C2, C3, C4 First, second, third, fourth clutch OWC1, OWC2 First, second one-way clutch P1, P2, P3 First, second, third planetary gear PC1, PC2, PC3 First, second, third planet carrier R1 , R2, R3 first, second and third ring gears S1, S2, S3 first, second and third sun gear

Claims (10)

Input shaft;
An output shaft arranged parallel to the input shaft;
A compound planetary gear set installed on the input shaft to receive input from the input shaft and including first, second, third, and fourth actuating elements; and fifth, sixth, and A main transmission including a first simple planetary gear set including a seventh actuating element;
A sub-transmission unit including a second simple planetary gear set installed on the output shaft so as to be able to transmit an output to the output shaft and including eighth, ninth, and tenth operating elements; and the main transmission unit Any one of the operating elements of the main transmission unit and any one of the operating elements of the sub transmission unit are coupled so that the power of the engine is transmitted to the sub transmission unit An intermediate gear device,
The first to seventh actuating elements of the main transmission include three clutches such that three actuating elements selectively act as input elements and two actuating elements selectively act as reaction force elements. Combined with each other through two brakes and one one-way clutch
The eighth to tenth actuating elements of the sub-transmission unit include one clutch, one actuating element such that one actuating element selectively operates as a reaction force element and one actuating element operates as an output element. 7. A seven-speed powertrain of an automatic transmission for a vehicle, which is combined with each other through a brake and one one-way clutch. The first simple planetary gear set of the main transmission unit consists of a single pinion planetary gear set, the compound planetary gear set of the main transmission unit consists of a Ravine type planetary gear set,
The first simple planetary gear set includes a first ring gear corresponding to the fifth operating element, a first planet carrier corresponding to the sixth operating element, and a first sun gear corresponding to the seventh operating element,
The compound planetary gear set corresponds to a second sun gear corresponding to the fourth operating element, a third sun gear corresponding to the first operating element, a second ring gear corresponding to the second operating element, and the third operating element. The 7-speed powertrain of the automatic transmission for vehicles according to claim 1, further comprising a second planetary carrier. The fifth actuating element is fixedly connected to the input shaft so as to act as an input element fixedly;
The first and fourth actuating elements are variably coupled with the sixth actuating element via clutches so as to selectively act as input elements;
The third actuating element is variably connected to the input shaft via a clutch so as to selectively act as an input element;
The fourth actuating element is variably connected to the transmission case via a brake so as to selectively act as a reaction force element;
The third operating element is connected to the transmission case via a brake and a one-way clutch arranged in parallel so as to selectively act as a reaction force element,
The seventh actuating element is fixedly connected to the transmission case so as to always act as a fixing element;
The seventh speed of the automatic transmission for a vehicle according to claim 2, wherein the second operating element is connected to the intermediate gear device so as to act as an output element of the main transmission unit. Power train. The second simple planetary gear set of the auxiliary transmission unit comprises a single pinion planetary gear set,
The second simple planetary gear set includes a third ring gear corresponding to an eighth operating element, a third planet carrier corresponding to the ninth operating element, and a fourth sun gear corresponding to the tenth operating element. A seven-speed power train for an automatic transmission for a vehicle according to claim 1. The eighth actuating element is connected to the intermediate gear device so as to act as an input element of the sub-transmission unit;
The ninth actuating element acts as an output element and is coupled to the tenth actuating element via a clutch so as to be selectively coupled directly to the tenth actuating element,
The tenth actuating element is connected to a transmission case via a brake and a one-way clutch arranged in parallel so as to selectively act as a reaction force element. 7-speed powertrain for vehicle automatic transmissions. The intermediate gear device is
A transfer drive gear fixedly connected to the second operating element of the main transmission unit;
The 7-speed power train of an automatic transmission for a vehicle according to claim 1, further comprising: a transfer driven gear that meshes with the transfer drive gear and is fixedly connected to an eighth operating element of the auxiliary transmission unit. Input and output shafts arranged parallel to each other;
A main transmission unit installed on the input shaft so as to receive input from the input shaft;
A sub-transmission unit installed on the output shaft so that output can be transmitted to the output shaft; and the main transmission unit and the main transmission unit so that power of the main transmission unit is transmitted to the sub-transmission unit A medium gear device for connecting the auxiliary transmission unit;
The main transmission unit includes a single planetary gear set including a first sun gear, a first ring gear, and a single pinion planetary gear set including a first planet carrier as an operating element, a second sun gear, a third sun gear, a second ring gear, And a combination with a compound planetary gear set consisting of a ravigne type planetary gear set including the second planet carrier as its operating element,
The first sun gear of the simple planetary gear set is fixedly connected to the transmission case so as to always operate as a fixed element, the first ring gear is fixedly connected to the input shaft, and the third planetary gear set is connected to the third sun gear. The sun gear and the second sun gear are variably connected with the first planet carrier via first and second clutches, respectively, and the second planet carrier has a third clutch interposed with the input shaft. The second sun gear is variably connected to the transmission case via the second brake, and the second sun gear is variably connected to the transmission case via the first brake. The two-ring gear is configured to be connected to the intermediate gear device so as to transmit the output of the main transmission unit to the sub-transmission unit,
The auxiliary transmission unit is composed of one simple planetary gear set composed of a single pinion planetary gear set including a fourth sun gear, a third ring gear, and a third planet carrier as operating elements,
The third ring gear is connected to the intermediate gear device so as to receive the output of the main transmission unit, and the third planet carrier acts as an output element of the auxiliary transmission unit and at the same time is selectively connected directly to the fourth sun gear. The fourth sun gear is connected to the fourth sun gear via a fourth clutch, and the fourth sun gear is variably connected to the transmission case via a third brake. 7-speed powertrain for automatic transmission.   The seven-speed powertrain of the automatic transmission for vehicles according to claim 7, wherein a one-way clutch for preventing reverse rotation is interposed between the second planet carrier and the transmission case.   The seven-speed powertrain of an automatic transmission for vehicles according to claim 7, wherein a one-way clutch for preventing reverse rotation is interposed between the fourth sun gear and the transmission case. The intermediate gear device is
A transfer drive gear fixedly connected to the second ring gear of the main transmission unit;
The 7-speed powertrain of the automatic transmission for vehicles according to claim 7, further comprising: a transfer driven gear that meshes with the transfer drive gear and is fixedly connected to a third ring gear of the auxiliary transmission unit.

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