KR100907069B1 - Gear train of car automatic transmission - Google Patents

Abstract

A gear train of automatic transmission for vehicles is provided to minimize the frictional member by arranging dispersively a plurality of friction members. The input shaft(IS) is directly connected to the second planet carrier(PC2). The second sun gear(S2) is connected to the first planetary carrier(PC1). The first ring gear(R1) is connected to the third ring gear(R3). The second ring gear(R2) is connected to the fourth sun gear(S4). The third planetary carrier(PC3) is changeably connected to the fourth planetary carrier(PC4) by the first clutch(C1). The fourth sun gear is changeably connected to the fourth planetary carrier by the second clutch(C2). The second planet carrier is changeably connected to the third sun gear by the third clutch(C3).

Description

GEAR TRAIN OF AUTOMATIC TRANSMISSION FOR VEHICLES}

The present invention combines four planetary gear sets with three clutches and two brakes to implement eight forward speeds and one reverse speed, thereby increasing the speed transmission performance and reducing fuel economy. It relates to a gear train of a vehicle automatic transmission.

In general, a multi-stage shifting mechanism of an automatic transmission is implemented by combining a plurality of planetary gearsets, and a gear train in which the plurality of planetary gearsets is combined receives a rotational power from a torque converter and shifts it to the output shaft. Will be

In such automatic transmissions, the more transmission stages that can be implemented, the more appropriate the transmission ratio can be designed and the vehicle can be realized in terms of power performance and fuel efficiency. Therefore, there is a demand for an automatic transmission that implements more transmission stages.

And even if the same shift stage is implemented, the durability, power transmission efficiency, size, etc. of the gear train are changed according to the combination method of the planetary gear set, so that a more robust, no power loss, and more compact gear train configuration can be invented. Efforts are ongoing.

In particular, unlike the manual transmission, in which the shifting step is more inconvenient for the driver to shift more frequently, the automatic transmission is shifted by the transmission control unit controlling the operation of the gear train in accordance with the driving state. Efforts are being made to find a configuration of gear trains that can implement a stage.

From this point of view, four-speed and five-speed automatic transmissions are the mainstream automatic transmissions currently in use, but recently, six-speed automatic transmissions have been developed and applied to vehicles, while the development of automatic transmissions of eight or more speeds is active. It's going on.

Accordingly, the present inventors have proposed the present invention in order to meet the development of the automatic transmission as described above, and the object of the present invention is a combination of four planetary gear sets with three clutches and two brakes for eight forward speeds. And it is possible to implement the reverse 1 speed, to provide a gear train of an automatic transmission for a vehicle to improve the power transmission performance and reduce fuel economy.

In order to realize the above object, the present invention, as in claim 1, the first, second, each having three rotating elements (S1 ~ S4), (PC1 ~ PC4), (R1 ~ R4) In combining 3,4 planetary gear sets (SPG1 to SPG4),

The input shaft IS into which the rotational power of the engine is input is directly connected to the second planet carrier PC2 to operate as an input element at all times, and the third planet carrier PC3 can operate as an output element at all times.

The second sun gear S2 is connected to the first planet carrier PC1, the first ring gear R1 is connected to the third ring gear R3, and the second ring gear R2 is connected to the fourth sun gear S4. ) And the third sun gear S3 and the fourth ring gear R4, and the third planet carrier PC3 is variably connected to the fourth planet carrier PC4 through the first clutch C1. The fourth sun gear S4 and the fourth planet carrier PC4 are variably connected via the second clutch C2, and the second planet carrier PC2 is formed through the third clutch C3. In a state in which the three sun gears S3 are variably connected;

The first sun gear S1 is variably connected to the transmission housing H via the first brake B1, and the first planet carrier PC1 is connected to the transmission housing H via the second brake B2. It provides a gear train of an automatic transmission for a vehicle, characterized in that the variable transmission and made.

And as in claim 2, the first planetary gear set PG1 is composed of a double pinion planetary gear set, and the second, third and fourth planetary gear sets PG2, PG3 and PG4 are single pinion planetary planets. It is characterized by consisting of a gear set.

The first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 are arranged in the same axis as in claim 3, but the first, second, third, and third engines are arranged from the engine side. 4 planetary gear sets (PG1) (PG2) (PG3) (PG4) or the first, third, second and fourth planetary gear sets (PG1) (PG3) from the engine side as in claim 4 (PG2) (PG4) is arranged in order.

In arranging the friction member, as in claim 5, the first and second brakes are disposed at the front side of the first planetary gear set PG1, and the third clutch C3 is the second and third planetary gear sets (3). It is arranged between PG2) and PG3, and the first and second clutches C1 and C2 are arranged on the rear side of the fourth planetary gear set PG20.

As described above, four planetary gear sets PG1 to PG4 are combined with three clutches C1, C2 and C3 as friction members and two brakes B1 and B2 to shift eight forward speeds and one reverse speed. By implementing a stage, it is possible to improve power transmission performance and fuel economy.

In addition, by distributing the plurality of friction members, the configuration of the flow path can be facilitated.

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

 1 shows a first embodiment of a gear train according to the present invention, in which the gear train according to the first embodiment of the present invention is arranged on the same axis, and includes the first, second, third and fourth planetary gear sets PG1. PG2, PG3, PG4, clutch means consisting of three clutches C1, C2, and C3, and brake means consisting of two brakes B1 and B2.

The first, second, third and fourth planetary gear sets PG1, PG2, PG3 and PG4 are sequentially arranged from the engine side on the input shaft IS, in which the input shaft IS serves as an input member. It means the turbine shaft of the torque converter, the rotational power from the engine crankshaft is input while the torque conversion through the torque converter is input, and the drive wheels are driven through a known differential device through the output gear (OG) as an output member. .

Wherein the first planetary gear set (PG1) is composed of a double pinion planetary gear set, the second, 3, 4 planetary gear set (PG2) is composed of a single pinion planetary gear set, each sun gear (S1) as known It has three rotating elements consisting of (S2) (S3) (S4), planet carrier (PC1) (PC2) (PC3) (PC4), and ring gear (R1) (R2) (R3) (R4). .

In connecting the rotary elements of the first, second, third, and fourth simple planetary gear sets PG1, PG2, PG3, and PG4 to each other, five power transmission members TS1 to TS5 are directly used. And variablely connected using the variable power transmission members VTS1 to VTS3 including three clutches C1, C2 and C3.

More specifically, the first power transmission member TS1 connects the input shaft IS and the second planet carrier PC2 so that the second planet carrier PC2 always operates as an input element, and a second power transmission. The member TS2 connects the second sun gear S2 and the first planet carrier PC1, and the third power transmission member TS3 connects the first ring gear R1 and the third ring gear R3. The fourth power transmission member TS4 connects the second ring gear R2 and the fourth sun gear S4, and the fifth power transmission member TS5 is the third sun gear S3 and the fourth ring gear R4. ).

In addition, the first variable power transmission member VTS1 including the first clutch C1 is connected to the output gear OG to supply a third planet carrier PC3 that operates as an output element at all times to a fourth planet carrier PC4. And the second variable power transmission member VTS2 including the second clutch C2 to variably connect the fourth sun gear S4 and the fourth planet carrier PC4, and the third clutch C3. The third variable power transmission member VTS3 including) variably connects the second planet carrier PC2 and the third sun gear S3.

In addition, the first sun gear S1 is variably connected to the transmission housing H through the first brake B1, and the first planet carrier PC1 is connected to the transmission housing via the second brake B2. H) has a configuration that is variably connected.

In the above, the friction member composed of the first, second and third clutches C1, C2 and C3 and the first and second brakes B1 and B2 is formed of a multi-plate hydraulic friction engagement unit friction-coupled by hydraulic pressure. It is common.

In the arrangement of the friction member as described above, the first and second brakes B1 and B2 are disposed in front of the first planetary gear set PG1, and the third clutch C3 is the second planetary gear set ( PG2) and the third planetary gear set PG3 are disposed, and the first and second clutches C1 and C2 are disposed at the rear side of the fourth planetary gear set PG4.

By distributing the friction members as described above, the hydraulic flow paths supplied to these friction members are easily formed, and the weight distribution is uniform, so that the overall weight balance of the automatic transmission is improved.

Figure 2 is an operating table showing the friction member, that is, the clutch and the brake to be applied at each shift stage applied to the present invention, the gear train of the present invention is shifted while the three friction members are operated at each shift stage. Able to know.

That is, the third clutch C3 and the first and second brakes B1 and B2 operate at the first forward speed.

At the second forward speed, the second clutch C2 and the first and second brakes B1 and B2 operate.

At the third forward speed, the second and third clutches C2 and C3 and the first brake B1 are operated.

The first and second clutches C1 and C2 and the first brake B1 operate at four forward speeds.

The first and third clutches C1 and C3 and the first brake B1 are operated at five forward speeds,

The first, second and third clutches C1, C2 and C3 operate at 6 forward speeds,

The first and third clutches C1 and C3 and the second brake B2 operate at seventh forward speed.

At the 8th forward speed, the first and second clutches C1 and C2 and the second brake B2 operate.

In reverse, the first clutch C1 and the first and second brakes B1 and B2 are operated to shift.

3 to 11 are views showing the shift process of the gear train according to the present invention, wherein the lower horizontal line represents the rotational speed "0", the upper horizontal line represents the rotational speed "1.0", that is, the input shaft (IS) and It shows the same rotation speed.

The three vertical lines of the first planetary gear set PG1 are set from the first rotating element N1 to the third rotating element N3 in order from the left, and the first rotating element N1 is the first planet carrier PC1. ), The second rotating element (N2) is set to the first ring gear (R1), the third rotating element (N3) is set to the first sun gear (S1), these intervals are each gear ratio of the first planetary gear set (PG1) (Number of teeth of sun gear / number of rings).

The three vertical lines of the second planetary gear set PG2 are set from the fourth rotating element N4 to the sixth rotating element N6 in order from the left, and the fourth rotating element N4 is the second sun gear S2. The fifth rotating element N5 is set to the second planetary carrier PC2 and the sixth rotating element N6 is set to the second ring gear R2, and the spacing is each gear ratio of the second planetary gear set PG2. (Number of teeth of sun gear / number of rings).

The three vertical lines of the fourth planetary gear set PG4 are set from the seventh rotation element N7 to the ninth rotation element N9 in order from the left, and the seventh rotation element N7 is the fourth sun gear S4. The eighth rotary element N8 is set to the fourth planet carrier PC4, and the ninth rotary element N9 is set to the fourth ring gear R4, and the spacing is each gear ratio of the fourth planetary gear set PG4. (Number of teeth of sun gear / number of rings).

The three vertical lines of the third planetary gear set PG3 are set from the tenth rotating element N10 to the twelfth rotating element N12 in order from the left, and the tenth rotating element N10 is the third sun gear S3. The eleventh rotating element N11 is set to the third planet carrier PC3, and the twelfth rotating element N12 is set to the fourth ring gear R4, and the spacing is each gear ratio of the third planetary gear set PG3. (Number of teeth of sun gear / number of rings).

Since the positioning of each rotating element in the above-described shift diagram is well known to those skilled in the art of a gear train, a detailed description thereof will be omitted.

[1st speed forward]

At the first forward speed, as shown in FIG. 2, the third clutch C3 and the first and second brakes B1 and B2 are operated and controlled.

Then, as shown in FIG. 3, the first planetary gear set PG1 is operated by operating the first and second brakes B1 and B2 while an input is made to the second planetary carrier PC2, which is the fifth rotating element N5. While the whole is fixed, the second sun gear S2, which is the fourth rotating element N4, which is directly connected to the first planet carrier PC1, which is its first rotating element N1, operates as the fixing element.

Accordingly, the speed increase output is performed through the second ring gear R2, which is the sixth rotation element N6. At this time, the power of the fifth rotation element N5 is driven by the operation of the third clutch C3 to rotate the ninth rotation. The fourth ring gear R4, which is the element N9, and the third sun gear S3, which is the tenth rotation element N10, are transmitted to each other, and the rotational power of the sixth rotation element N6 is directly connected thereto. It is transmitted to the fourth sun gear S4 which is the rotating element N7.

In this state, the third ring gear R3, which is the twelfth rotating element N12, operates as a fixed element due to the total fixing of the first planetary gear set PG1. And the first shift line SP1 connecting the twelfth rotation element N12 to the D1 through the eleventh rotation element N11, which is an output member, so that the shift of the first forward speed is achieved. .

[2 speed forward]

In the second forward speed, as shown in FIG. 2, the operation of the third clutch C3 operated in the state of the first forward speed is released, and the second clutch C2 is operated and controlled.

Then, as shown in FIG. 4, the first planetary gear set PG1 is fixed as in the first speed, and an input is made to the second planet carrier PC2 that is the fifth rotating element N5 while the third clutch C3 is closed. The deceleration of) causes only the speed increase power of the sixth rotating element N6 to be transmitted to the seventh rotating element N7.

In this state, as the fourth planetary gear set PG4 is directly connected by the operation of the second clutch C2, the speed increase power input is transmitted to the third sun gear S3, which is the tenth operating element N10. The third ring gear R3, which is the twelfth rotating element N12, operates as a fixed element due to the entire fixing of the first planetary gear set PG1. As the second shift line SP2 connecting the 12 rotating elements N12 is formed, the output of the D2 is made through the eleventh rotating element N11, which is an output member, so that the shift in the second forward speed is made.

[3 speed forward]

At the third forward speed, as shown in FIG. 2, the operation of the second brake B2 operated in the second forward speed is released, and the third clutch C3 is operated and controlled.

Then, as shown in FIG. 5, the fourth driving gear R4 and the tenth rotating element, which are the ninth rotating element N9, are driven by the rotational force input to the fifth rotating element N5 by the operation of the third clutch C3. N10) is transferred to the third sun gear S3.

At this time, the fourth planetary gear set PG4 is directly connected by the operation of the second clutch C2. The second planetary gear set PG2 also includes the fifth rotary element N5 and the sixth rotary element N6. Is connected directly to the seventh rotation element N7 and the ninth rotation element N9 of the fourth planetary gear set PG4.

In this state, the rotational power of the second sun gear S2, which is the fourth rotating element N4, is transmitted to the first planet carrier PC1, which is the first rotating element N1. At this time, the operation of the first brake B1 is performed. As the first sun gear S1, which is the third operating element N3, operates as a fixed element, the deceleration output is made through the first ring gear R1 that is the second rotating element N2.

The third sun gear which is the tenth rotating element N1 as described above while the deceleration power of the second rotating element N2 is input to the third ring gear R3 which is the twelfth rotating element N12. 10) the rotational power of the input shaft IS is input as it is, the third transmission line (SP3) connecting the tenth rotating element (N10) and the twelfth rotating element (N12) to form an output member 11 the output of the D3 through the rotating element (N11) is made to be a three-speed forward is made.

[4 forward speed]

In the fourth forward speed, as shown in FIG. 2, the operation of the third clutch C3 operated in the third forward speed is released, and the first clutch C1 is operated and controlled.

Then, as shown in FIG. 6, the fourth planetary gear set PG4 is directly connected by the operation of the first clutch C1, and in this state, the fourth planetary carrier PC4, which is the eighth rotating element N8, The fourth ring gear R4, which is the ninth rotating element N9, is the third planetary carrier PC3, which is the eleventh rotating element N11 of the third planetary gear set PG3, and the tenth rotating element N10. The third planetary gear set PG3 is also directly connected to the three sun gear S3.

In this state, an input is made to the fifth rotating element N5, and the first sun gear S1, which is the third rotating element N3, operates as a fixed element by the operation of the first brake B1. In operation, the second sun gear S2, which is the fourth rotating element N4, and the first planet carrier PC1, which is the first rotating element N1, are accelerated, so that the first ring gear, which is the second rotating element N2, Decelerating output is made via R1).

And while the rotational power of the second rotary element (N2) is transmitted to the third planetary gear set (PG3) of the direct connection state to form a fourth transmission line (SP4) as much as D4 through the eleventh rotary element (N11) As the output is made, the shift in the fourth forward speed is achieved.

[5th forward]

In the fifth forward speed, as shown in FIG. 3, the operation of the second clutch C2 operated in the fourth forward speed is released, and the third clutch C3 is operated and controlled.

Then, as shown in FIG. 7, the first sun gear S1, which is the third rotating element N3, is operated as the fixed element by the operation of the first brake B1 while the input is made to the fifth rotating element N5. The second sun gear S2, which is the fourth rotating element N4, and the first planet carrier PC1, which is the first rotating element N1, are accelerated by the complementary operation. 1 Deceleration output is made through ring gear (R1).

In this state, the rotational power input to the fifth rotating element N5 is the fourth ring gear R4 that is the ninth rotating element N9 and the tenth rotating element N10 by the operation of the third clutch C3. It is transmitted to the third sun gear (S3), the deceleration power of the first ring gear (R1) that is the second rotating element (N2) is transmitted to the third ring gear (R3) that is the twelfth rotating element (N12), While forming the fifth shift line SP5 connecting the tenth rotating element N10 and the twelfth rotating element N12, an output of D5 is made through the eleventh rotating element N11, so that the shift of the fifth forward speed is performed. Will be done.

[6th forward]

At the sixth forward speed, as shown in FIG. 2, the operation of the first brake B1 operating in the fifth forward speed is released, and the second clutch C2 is controlled to operate.

Then, as shown in FIG. 8, all three clutches C1, C2, and C3 operate, and the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 are directly connected to each other. The sixth shift line SP6 is formed in the third planetary gear set PG3 and the output of the sixth speed is made through the eleventh rotation element N11, which is the input as it is. You lose.

[7th forward]

In the seventh forward speed, as shown in FIG. 2, the operation of the second clutch C2 operated in the sixth forward speed is released and the second brake B2 is controlled to operate.

Then, as shown in FIG. 9, when the first rotary element N1 and the fourth rotary element N4 operate as the fixed element by the operation of the second brake B2, the input is input to the fifth rotary element N5. As a result, the speed increase output is made through the second rotating element N2 and the rotational power thereof is transmitted to the third ring gear R3 which is the twelfth rotating element N12.

And the rotational power of the input shaft (IS) is input to the tenth rotating element (N10) by the operation of the third clutch (C3), the seventh connecting the tenth rotating element (N10) and the twelfth rotating element (N12) The shift line SP7 is formed, and as much as D7 is output through the eleventh rotation element N11 which is an output member, the shift of the seventh forward speed is made.

[8th forward]

At 8th forward speed, as shown in FIG. 2, the operation of the third clutch C3 operated in the 7th forward speed is released, and the second brake B2 is operated and controlled.

Then, as shown in FIG. 10, the fourth planetary gear set PG4 is directly connected by the operation of the first clutch C1, and the fourth planetary carrier PC4, which is the eighth rotating element N8, is in this state. The fourth ring gear R4, which is the ninth rotating element N9, is the third planetary carrier PC3, which is the eleventh rotating element N11 of the third planetary gear set PG3, and the tenth rotating element N10. The third planetary gear set PG3 is also directly connected to the three sun gear S3.

In this state, an input is made to the fifth rotating element N5, and the first rotating element N1 and the fourth rotating element N4 operate as fixed elements by the operation of the second brake B2. As a result of the speed increase output through the second rotating element N2, the rotational power thereof is transmitted to the third ring gear R3, which is the twelfth rotating element N12.

Accordingly, since the input is made to the twelfth rotating element N12 in the direct connection state, the output of D8 is increased as it is through the eleventh rotating element N11 which is the output member while the eighth shift line SP8 is formed. It is to be made 8 speed shift is made.

[apse]

In the reverse shift stage, as shown in FIG. 2, the first clutch C1 and the first and second brakes B1 and B2 are operated and controlled.

Then, as shown in FIG. 11, the first planetary gear set PG1 is operated by operating the first and second brakes B1 and B2 in a state where an input is made to the second planetary carrier PC2, which is the fifth rotating element N5. While the whole is fixed, the second sun gear S2, the fourth rotating element N4, which is directly connected to the first planet carrier PC1, which is its first rotating element N1, is operated as the fixing element.

Accordingly, the speed increase output is performed through the second ring gear R2 which is the sixth rotation element N6, and the rotational power thereof is input to the seventh rotation element N4, wherein the first planetary gear set PG2 is used. The third ring gear R3, which is the twelfth rotating element N12, is operated as a fixed element by the fixing of the second rotating element N9 and the tenth rotating element N10 in reverse rotation. The reverse direction is output by forming the line SR and outputting the reverse rotation by RS through the eleventh rotating element N11 serving as the output member.

FIG. 12 shows a gear train of a second embodiment according to the present invention. The configuration of the first, second, third and fourth planetary gear sets PG1 to PG4 is the same as that of the first embodiment. It is different.

That is, in the first embodiment, the first, second, third and fourth planetary gear sets PG1 to PG4 are sequentially disposed from the engine side. In the second embodiment, the first, third, second and fourth engines are arranged from the engine side. The planetary gear sets PG1, PG3, PG2, and PG4 are arranged in this order.

Since the second embodiment differs only in the arrangement order of the second and third planetary gear sets PG2 and PG3, the shift process is the same as the first embodiment, and thus the detailed description thereof will be omitted.

Although a preferred embodiment of the gear 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 the present invention from the embodiment of the present invention. It includes all changes to the extent considered equivalent.

1 is a block diagram of a gear train of a first embodiment according to the present invention;

Figure 2 is a shift-specific operation of the friction member applied to the gear train of the present invention.

3 is a shift diagram at forward 1 speed.

4 is a shift diagram at forward two speeds.

5 is a shift diagram at the third forward speed.

6 is a shift diagram at the fourth forward speed.

7 is a shift diagram at the fifth forward speed.

8 is a shift diagram at sixth forward speed.

9 is a shift diagram at the seventh forward speed.

10 is a shift diagram at eight forward speeds.

11 is a reverse shift diagram.

12 is a configuration diagram of a gear train of a second embodiment according to the present invention.

Claims (5)

In combining the first, second, third and fourth planetary gear sets SPG1 to SPG4 having three rotating elements S1 to S4, PC1 to PC4, and R1 to R4, respectively, The input shaft IS into which the rotational power of the engine is input is directly connected to the second planet carrier PC2 to operate as an input element at all times, and the third planet carrier PC3 can operate as an output element at all times. The second sun gear S2 is connected to the first planet carrier PC1, the first ring gear R1 is connected to the third ring gear R3, and the second ring gear R2 is connected to the fourth sun gear S4. ) And the third sun gear S3 and the fourth ring gear R4, and the third planet carrier PC3 is variably connected to the fourth planet carrier PC4 through the first clutch C1. The fourth sun gear S4 and the fourth planet carrier PC4 are variably connected via the second clutch C2, and the second planet carrier PC2 is formed through the third clutch C3. In a state in which the three sun gears S3 are variably connected; The first sun gear S1 is variably connected to the transmission housing H via the first brake B1, and the first planet carrier PC1 is connected to the transmission housing H via the second brake B2. And a gear train of an automatic transmission for a vehicle, characterized in that the variable transmission is made. 2. The first planetary gear set PG1 is composed of a double pinion planetary gear set, and the second, third and fourth planetary gear sets PG2, PG3 and PG4 are single pinion planetary gear sets. Gear train of an automatic transmission for a vehicle, characterized in that made. The first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 are arranged coaxially, and the first, second, third, and fourth planetary gears from the engine side. Gear train of the automatic transmission for a vehicle, characterized in that arranged in the set (PG1) (PG2) (PG3) (PG4). The first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 are arranged coaxially, and the first, third, second, and fourth planetary gears from the engine side. Gear train of the automatic transmission for a vehicle, characterized in that arranged in the set (PG1) (PG3) (PG2) (PG4). The first and second brakes of claim 1, wherein the first and second brakes are disposed on the front side of the first planetary gear set PG1, and the third clutch C3 is disposed between the second and third planetary gear sets PG2 and PG3. And the first and second clutches C1 and C2 are disposed at the rear side of the fourth planetary gear set PG4.

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