KR100828681B1 - 7 - shift power train in an automatic transmission for vehicles - Google Patents

Abstract

Two single pinion planetary gear sets and one compound planetary gear set sharing a sun gear and a planetary carrier are combined with four clutches and two brakes to implement forward 7th speed and reverse 1 speed, The present invention provides a powertrain of a 7-speed automatic transmission for a vehicle, which is capable of reducing the capacity of the oil pump and increasing the hydraulic control efficiency by allowing the shift element to operate while the friction element is operated.

Planetary gear set. Input element. Output element

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a 7-speed automatic transmission,

1 is a block diagram of a power train according to the present invention;

2 is a table of friction element operating elements of a power train according to the present invention.

3 (A) and 3 (B) are transmission diagrams of forward 1 and 2 speeds.

4 (A) and 4 (B) are transmission diagrams of forward third and fourth speeds.

5 (A) and 5 (B) are forward speed 5 and 6 speed-change diagrams.

6 (A) and (B) are forward speed 7 speeds and reverse speeds.

7 is a block diagram showing an example of a conventional 7-speed power train.

Fig. 8 is a table of operating elements of the friction element for shifting of Fig. 7;

The present invention relates to a powertrain of a 7-speed automatic transmission for a vehicle.

For example, the powertrain of a vehicular automatic transmission has been developed and applied in various forms according to automobile manufacturers. In the currently used automatic transmission, the 4th and 5th speed transmissions are mainstream, but in recent years, And the development of a 7-speed automatic transmission is progressing actively while it is applied to some vehicles.

For example, as shown in Fig. 7 (BENZ 7G-TRONIC 7 speed), two compound planetary gear sets are combined through three clutches, four brakes, and one one-way clutches so as to be capable of 7-speed shift have,

More specifically, the first complex planetary gear set 100 includes a single pinion planetary gear set and a double pinion planetary gear set, wherein the first sun gear 104 and the planetary carrier 102 share the sun gear 104, The first planetary carrier 102, and the first and second ring gears 106,

And the second complex planetary gear set 110 is assembled by combining the two single pinion planetary gear sets and directly connecting the third ring gear 112 and the fourth planetary carrier 114 to the third and fourth sun gears 116 The third planetary carrier 120, the fourth planetary carrier 124, and the fourth ring gear 126, as shown in Fig.

In connecting the respective operating elements of the complex planetary gear set 100 (110), the first planetary carrier 102 is fixedly connected with the fourth ring gear 126 and the one-way clutch F And is connected to the transmission housing 128.

The first sun gear 104 is variably connected to the first ring gear 106 using the first clutch K1 and is variably fixed to the transmission housing 128 via the first brake B1.

The second ring gear 108 is directly connected to the input shaft 130 to operate as an input element and the third ring gear 112 is connected to the input shaft 128 via the second clutch K2, And is variably connected.

The third and fourth sun gears 116 and 118 are variably connected via a third clutch K3 and the third sun gear 116 is connected to the transmission housing 128 via a second brake B2. And is variably connected.

The first ring gear 106 and the fourth planetary carrier 124 are variably connected to the transmission housing 128 through the third and fourth brakes B3 and B4, And is connected to the output shaft 132 to serve as an output element at all times.

8, the seventh-speed power train having the above-described structure is configured such that the third clutch K3, the second and third brakes B2 and B3 in the forward first speed, the third clutch K3 in the forward second speed, The first and second clutches K1 and K2 and the second brake B2 in the forward third speed and the first and second clutches K1 and K2 and the second brake K2 and the second brake B3 in the forward fourth speed, The first and second clutches K1 and K2 and the first and second clutches K2 and K3 in the forward sixth gear and the first and second brakes B1 and B2 in the forward fifth gear, , The three clutches K1 and K3 and the third brake B3 are operated to perform shifting.

The third clutch K3 and the second and fourth brakes B2 and B4 in the first reverse speed and the first and third clutches K1 and K3 and the fourth brake B4 in the reverse second speed and the third brake B4 in the reverse third speed, The clutch K3 and the third and fourth brakes B3 and B4 are operated to perform the reverse shift.

However, in the power train described above, three forward speeds and three reverse speeds can be realized. However, since three friction elements operate at the respective speed change stages, the hydraulic control efficiency deteriorates and, in order to supply the hydraulic pressure to these friction elements, The capacity of the pump must be increased.

Further, by applying four brakes, the size of the automatic transmission becomes large and the configuration becomes complicated.

SUMMARY OF THE INVENTION Accordingly, the present invention has been made keeping in mind the above problems occurring in the prior art, and it is an object of the present invention to provide a planetary gear set having two simple planetary gear sets and a single complex planetary gear set with four clutches and two brakes, Speed power transmission of a seventh-speed automatic transmission for a vehicle which realizes a first speed and allows a shift operation to be performed while two friction elements operate at each speed change stage, thereby reducing the capacity of the oil pump and increasing the hydraulic control efficiency.

In order to achieve the above object, the present invention provides a planetary gear set comprising a first and a second planetary gear set including a single pinion planetary gear set and a third planetary gear set of a rake type that share a sun gear and a planetary carrier,
The sun gear of the first planetary gear set connected to the input shaft and the planetary carrier of the second planetary gear set are directly connected and the planetary carrier of the first planetary gear set connected to the output gear and the planetary carrier of the third planetary gear set 2 With the ring gear directly connected,
The ring gear of the first planetary gear set is connected to the planetary carrier of the third planetary gear set via the first clutch and the planetary carrier of the third planetary gear set is linked to the third planetary gear set via the second and third clutches, The sun gear of the third planetary gear set is connected to the second ring gear of the planetary gear set and the ring gear of the second planetary gear set and is connected to the transmission housing through the first brake, A power train of a 7-speed automatic transmission for a vehicle, which is connected to a transmission housing and connected to a planetary carrier of the second planetary gear set via a fourth clutch, and the sun gear of the second planetary gear set is directly connected to the transmission housing, to provide.
Wherein the first, second and third planetary gear sets are arranged from the engine side in the order of a first planetary gear set, a third planetary gear set and a second planetary gear set, the first clutch being disposed between the first and third planetary gear sets The second clutch is disposed between the third and second planetary gear sets, the third and fourth clutches are disposed on the rear outer side of the second planetary gear set, and the first and second brakes are disposed in the third, And is disposed between the gear sets.

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

FIG. 1 illustrates an embodiment of a powertrain according to the present invention. The powertrain of the present invention includes first, second, and third planetary gear sets PG1, PG2, PC3 disposed on the same axis line, Four clutches C1, C2, C3, and C4, and two brakes B1 and B2.

The first and second planetary gear sets PG1 and PG2 are formed as a single pinion planetary gear set and the third planetary gear set PG3 is formed by combining a single pinion planetary gear set and a double pinion planetary gear set, And a planetary gear set of a rake type that combines a sun gear and a planetary carrier in a shared manner.

In arranging the planetary gear set as described above, the first planetary gearset PG1, the third planetary gearset PG3, and the second planetary gearset PG2 are arranged in this order from the engine side.

The first clutch C1 is disposed between the first and third planetary gear sets PG1 and PG3 and the second clutch C2 and the second clutch C2 are interposed between the third and second planetary gear sets PG3 and PG2. The first and second brakes B1 and B2 are disposed and the third and fourth clutches C3 and C4 are disposed on the outer peripheral side of the rear portion of the second planetary gearset PG2.

The first planetary gearset PG1 includes a first operating element formed of a sun gear S1, a second operating element formed of a planetary carrier PC1, and a third operating element formed of a ring gear R1 .

The second planetary gear set PG2 includes a first operating element formed of a sun gear S2, a third operating element formed of a planetary carrier PC2, and a second operating element formed of a ring gear R2 .

The third planetary gear set PG3 includes a first operating element composed of a sun gear S3 and a second operating element composed of a first ring gear R3 and a third pinion gear P3 supporting a short pinion P1 and a long pinion P2 And a fourth actuating element composed of a second ring gear R3 '.

1, when the first, second, and third planetary gear sets PG1, PG2, and PG3 are combined, the first operating element of the first planetary gearset PG1 is connected to the input shaft IS, (Sun gear S1) and the second operating element of the second planetary gear set PG2 (the planetary carrier PC2 are directly connected and the second operating element of the first planetary gearset PG1 ) And the fourth operating element (second ring gear R3 ') of the third planetary gearset PG3 are directly connected.

The output gear OG is connected to the second operating element (planetary carrier PC1) of the first planetary gear set PG1 so that the output gear OG always operates as an output element. The structure for transmitting the power to the differential gear through the gear is omitted. However, such a structure can be a well-known structure, and even if any structure is used, the object of the present invention can be realized, do.

The third operating element (ring gear R1) of the first planetary gearset PG1 is connected to the third operating element of the third planetary gearset PG3 via the first clutch C1, (Planetary carrier PC3).

The third operating element of the third planetary gearset PG3 (planetary carrier PC3) is connected to the fourth operating element of the third planetary gearset PG3 via the second clutch C2 The second planetary gear set PG2 is variably connected to the transmission housing H through the first brake B1 and is variably connected to the transmission housing H via the third clutch C3. (The ring gear R2).

The first operating element (sun gear S3) of the third planetary gearset PG3 is connected to the transmission housing H through the second brake B2 and is connected to the transmission housing H via the fourth clutch C4. And the first operating element (sun gear S2) of the second planetary gearset PG2 is connected to the transmission housing H and the second operating element of the second planetary gearset PG2, They are directly connected and always operate as fixed elements.

The second operation of the third planetary gearset PG3 (the first ring gear R3) operates only with the idle element in a free state without any function, and the first planetary gear set PG1 is always output through the second operating element (planetary carrier PC2) while the input is made through the first operating element (sun gear S1).

Also, the second planetary gear set PG2 is configured such that the second operating element (planetary carrier PC2) always operates as an input element while the first operating element (sun gear S2) always functions as a stationary element, (Sun gear S3) of the third planetary gear set PG3 or selectively transmits the rotational power of the increased third operating element (ring gear R2) to the third planetary gear set PG3, To the third operating element (planetary carrier PC3) of the set PG3.

The third planetary gear set PG3 is driven by the fourth operating element (the second ring gear PC3) in accordance with the rotational power transmitted to the first operating element (sun gear S3) and the third operating element (planetary carrier PC3) (Planetary carrier PC1) of the first planetary gear set PG1, which is directly connected to the first planetary gear set PG1, while shifting the planetary gear set PG1 and the planetary gear set R3 '.

In the power train according to the present invention, as shown in FIG. 2, the shifting operation is performed while the friction element is operated. The shifting process is performed visually through the lever analysis method as shown in FIGS. 3 to 6 The following is an example.

First, in the three lever nodes on the lever side of the first planetary gearset PG1, the first operating node N1 is connected to the sun gear S1, the second operating node N2 to the planetary carrier PC1, The fourth working node N4 is the sun gear S2 and the fifth working node N5 is the ring gear R1 of the second planetary gear set PG2. The planetary carrier PC2, and the sixth working node N6 are set to the ring gear R2.

And the seventh working node N7 is the sun gear S3 and the eighth working node N8 is the first ring gear R3 and the eighth working node N8 is the third ring gear R3, The operating node N9 is set to the planetary carrier PC3, and the tenth working node N10 is set to the second ring gear R3 '.

In the above description, each operation node on the lever is well known to be set according to the combination configuration of the power train, and can be easily understood by those skilled in the art of powertrain, and a detailed description thereof will be omitted.

[Advancing first gen]

2, the first brake B1 and the first clutch C1 are controlled in operation. At this time, by directly connecting the input shaft IS to the first operating node N1 And the fifth working node N5 always operate as input elements.

In this state, the third operating node N3 and the ninth working node N9 operate as fixed elements by the operation of the first clutch C1 and the first brake B1, and the first planetary gearset PG1 The first and second speed lines SP1-2 and SP1-2 are formed and the outputs of the first and second operation nodes N2 and SP1-2 are connected to each other The forward 1-speed shift is performed.

At this time, in the third planetary gearset PG3, the ninth working node N9 operates as a fixed element, and the second ring gear R3 ', which is the tenth working node N10, is operated by the operation of the first clutch Cl Which is the second actuating node N2, by the action of the first sun gear S3, thereby forming the first-speed line SP1-1.

[Advancing second gen]

2, the operation of the first brake B1 operating in the forward first speed state is released, and the operation of the second brake B2 is controlled.

Then, as shown in FIG. 3B, the first actuating node N1 and the fifth actuating node N5 always act as input elements by direct connection with the input axis IS, as in the forward first gear.

The operation of the first clutch C1 in the state in which the seventh working node N7 is operated as the fixed element by the operation of the second brake B2 in this state allows the ninth working node N9 and the third working node N7 N3 are connected to each other, and the second-speed change line SP2-1 and the second-second speed change line SP2-2 are formed by complementary operation.

As a result, an output of D2 is transmitted through the second operating node N2, which is an output element connected to the tenth operating element N10, so that the shifting of the forward second speed is achieved.

[Three steps forward]

2, the operation of the second brake B2, which was operated in the forward second speed state, is released, and the second clutch C2 is actuated.

Then, as shown in FIG. 4A, the first actuating node N1 and the fifth actuating node N5 always act as input elements by direct connection with the input axis IS, as in the forward second gear.

In this state, the ninth working node N9 and the tenth working node N10 are connected by the operation of the second clutch C2, and the third working node N3 and the third working node N10 are connected by the operation of the third clutch C3. The ninth working node N9 is directly connected to the first and third planetary gear sets PG1 and PG3 so that the third-first speed line SP3-1 and the third-second speed line SP4-2), so that output of the input D3 is made through the second operation node N2, which is an output element, so that the fourth forward speed shift is performed.

[Advance 4th gen]

In the fourth forward speed, as shown in Fig. 2, the operation of the second clutch C2, which was operating in the state of the forward third speed, is released, and the operation of the third clutch C3 is controlled.

Then, as shown in FIG. 4B, the first actuating node N1 and the fifth actuating node N5 always act as input elements by direct connection with the input axis IS, as in the third forward gear.

In this state, by the operation of the first clutch C1, the operation of the third clutch C3 in the state where the third working node N3 and the ninth working node N9 are connected and the sixth working node N6 The ninth working node N9 is connected, and the fourth planetary gear set PG3 is formed with the fourth-speed line SP4-1.

In the first planetary gearset PG1, a fourth-speed change-speed line SP4-2 is formed and a second operation element, which is an output element, is connected to the third operation node N3, The output of D4 is made through the node N2 and the forward fourth-speed shift of the overdrive state is performed.

[Five steps forward]

In the fifth forward speed, as shown in Fig. 2, the operation of the first clutch C1, which was operating in the forward fourth speed state, is released, and the operation of the second clutch C2 is controlled.

Then, as shown in FIG. 5A, the first actuating node N1 and the fifth actuating node N5 always operate as input elements by direct connection with the input shaft IS, as in the forward fourth gear.

In this state, the ninth working node N9 and the tenth working node N10 are connected by the operation of the second clutch C2, and the sixth working node N6 and the sixth working node N6 are connected by the operation of the third clutch C3. The ninth working node N9 is connected so that the increased power of the second planetary gear set PG2 is directly input to the third planetary gear set PG3, -1 speed change line SP5-1 is formed.

And the tenth working node N10 and the second working node N2 are connected to each other so that the fifth planetary gear set PG1 forms the fifth-speed line SP5-2, The output of D5 is made through the node N2, so that the forward 5-speed shift in the overdrive state is performed.

[6 steps forward]

In the sixth forward speed, the operation of the second clutch C2, which was operating in the forward fifth speed state, is released and the fourth clutch C4 is operated as shown in Fig.

Then, as shown in FIG. 5B, the first actuating node N1 and the fifth actuating node N5 always act as input elements by direct connection with the input axis IS, as in the forward fifth gear.

In this state, the sixth operating node N6 and the ninth working node N9 are connected by the operation of the third clutch C3, and the fifth operating element N5 and the fifth operating element N5 are connected by the operation of the fourth clutch C4. 7 operation node N7 is connected, and the sixth planetary gear set PG3 forms the sixth-speed line SP6-1.

In the first planetary gear set PG1, a fifth-speed change-speed line SP6-2 is formed and a second operation element, which is an output element, is connected to the third operation node N3, The output of D6 is made through the node N2, so that the forward 4th-speed shift is performed.

[Advancing seven genus]

As shown in Fig. 2, in the forward speed 7, the operation of the fourth clutch C4 that was operating in the forward sixth speed state is released, and the second brake B2 is actuated.

Then, as shown in FIG. 6A, the first actuating node N1 and the fifth actuating node N5 always operate as input elements by direct connection with the input axis IS, as in the forward fifth gear.

In this state, the sixth working node N6 and the ninth working node N9 are connected by the operation of the third clutch C3, and the seventh working node N7 is operated by the operation of the second brake B2 The seventh speed change line SP7-1 is formed in the third planetary gear set PG3 while operating as a fixed element.

And the tenth working node N10 and the second working node N2 are connected to each other so that the first planetary gear set PG1 forms the seventh speed line SP7-2 and the second operation The output of D6 is made through the node N2, so that the shift of the forward speed 7, which is the maximum speed change stage, is performed.

[apse]

As shown in Fig. 2, the fourth clutch C4 and the first brake B1 are actuated in the backward first speed.

Then, as shown in FIG. 6B, the first actuating node N1 and the fifth actuating node N5 always operate as input elements by direct connection with the input axis IS.

In this state, the fifth working node N5 and the seventh working node N7 are connected by the operation of the fourth clutch C4, and the ninth working node N9 is operated by the operation of the first brake B1 And the reverse first transmission line RS1 is formed in the third planetary gearset PG3 while operating as a fixed element.

And the second operating node N2 is connected to the second operating node N10 and the second operating node N2 is connected to the second operating node N2. The output of the SR is made through the node N2 and the reverse shift is performed.

In addition to the above-described sequential shifting, the present invention may also be applied to a downshift transmission of 7 to 5, 6 to 4, 5 to 3, 4 to 2, 3 to 1, 7 to 4, 6 to 3, 5 to 2, And in the up-skip case, it can be reversed in the above-described manner, which can be accomplished by changing only one of the two friction elements that operate.

In the power train of the present invention in which the shifting is performed as described above, the number of teeth of the sun gear S1 and the ring gear R1 of the first planetary gearset PG1 is set to 30 and 95 and the number of teeth of the sun gear S1 of the second planetary gearset PG2 The number of teeth of the sun gear S2 and the ring gear S2 is 33 and 89 and the number of teeth of the sun gear S3 of the third planetary gearset PG3, the first ring gear R3, As shown in FIG. 2, it was 4.167 in the forward 1, 1.861 in the forward 2, 1.000 in the forward 3, 0.780 in the forward 4, 0.730 in the forward 5, 0.663 in the forward 5, and in the forward 7 0.530, so that the inter-stage ratio of each gear range can be optimized.

While the present invention has been described in connection with what is presently considered to be practical exemplary embodiments, it is to be understood that the invention is not limited to the disclosed embodiments, but, on the contrary, And shall include all modifications of the scope which are deemed to be equivalent.

As described above, according to the present invention, by combining two simple planetary gear sets and one complex planetary gear set with four clutches and two brakes to implement forward seventh speed and reverse one speed, It is possible to reduce the cost.

In addition, the two-speed or three-speed skip control is possible by shifting the two friction elements at the respective speed change stages so that the capacity reduction of the oil pump and the hydraulic control efficiency can be improved.

Claims (13)

delete delete delete delete delete delete delete delete delete A first planetary gear set comprising a single pinion planetary gear set and a third planetary gear set of a rake type which share a sun gear and a planetary carrier, The sun gear of the first planetary gear set connected to the input shaft and the planetary carrier of the second planetary gear set are directly connected and the planetary carrier of the first planetary gear set connected to the output gear and the planetary carrier of the third planetary gear set 2 With the ring gear directly connected, The ring gear of the first planetary gear set is connected to the planetary carrier of the third planetary gear set via the first clutch and the planetary carrier of the third planetary gear set is linked to the third planetary gear set via the second and third clutches, The sun gear of the third planetary gear set is connected to the second ring gear of the planetary gear set and the ring gear of the second planetary gear set and is connected to the transmission housing via a first brake, And the sun gear of the second planetary gear set is directly connected to the transmission housing. The planetary gear set according to claim 1, wherein the planetary carrier of the second planetary gear set is connected to the transmission housing and is connected to the planetary carrier of the second planetary gear set via a fourth clutch, Power train. 11. The automatic transmission as set forth in claim 10, wherein the first, second and third planetary gear sets are arranged from the engine side in the order of the first planetary gear set, the third planetary gear set, and the second planetary gear set Power train. 12. A planetary gear set according to claim 11, wherein the first clutch is disposed between the first and third planetary gear sets, the second clutch is disposed between the third and second planetary gear sets, and the third, And the rear wheels are disposed on the outer peripheral side of the rear portion of the power train. 12. The powertrain of a seven-speed automatic transmission for a vehicle according to claim 11, wherein the first and second brakes are disposed between the third and second planetary gear sets.

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