KR100916782B1 - Gear train in an automatic transmission for vehicles - Google Patents

Abstract

By combining the first planetary gear set consisting of a simple planetary gear set and the second planetary gear set consisting of a combination of two simple planetary gear sets with three clutches and two brakes, six forward speeds and one reverse speed can be realized. In addition, the present invention provides a gear train of an automatic transmission for a vehicle that simplifies the configuration of the automatic transmission, improves power transmission performance, and reduces fuel consumption.

Planetary gear set, sun gear, planet carrier, ring gear, clutch, brake

Description

GEAR TRAIN IN AN AUTOMATIC TRANSMISSION FOR VEHICLES}

The present invention relates to a gear train of an automatic transmission for a vehicle to realize a sixth speed shift stage by combining one simple planetary gear set and one compound planetary gear set into three clutches and two brakes.

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 this automatic transmission, the more gears that can be implemented, the more appropriate the gear ratio can be designed and the vehicle can be realized in terms of power performance and fuel efficiency. .

And even if the same shift stage is implemented, the durability, power transmission efficiency, size, etc. of the gear train vary depending on the combination method of the planetary gear set, and thus invent a more robust, power lossless, and more compact gear train configuration. Efforts are always underway.

In particular, unlike a manual transmission in which a shifting speed is more inconvenient for a driver, the automatic transmission shifts by controlling a gear train in accordance with a driving state. Efforts are being made to find a gear train configuration that can be implemented.

From this point of view, the automatic transmission that is currently used is a four-speed and five-speed automatic transmission is the mainstream, but recently the six-speed automatic transmission has been applied to the vehicle in practical use.

Accordingly, the present inventors have proposed the present invention to meet the development of the automatic transmission as described above, and an object of the present invention consists of a combination of the first planetary gear set consisting of a simple planetary gear set and two simple planetary gear sets. By combining the second planetary gear set with three clutches and two brakes, six forward speeds and one reverse speed can be realized, simplifying the configuration of the automatic transmission, improving power transmission performance, and reducing fuel efficiency. It is to provide a gear train of a vehicle automatic transmission.

In order to realize the above object, the present invention provides a simple planetary gear set having three rotating elements, the first rotating element being fixedly connected to the transmission housing so that it can always operate as a fixed element, and the deceleration output as an output element. A first planetary gear set including a second rotating element formed directly, and a third rotating element directly connected to the input shaft and operating as an input element at all times;

Combination of the first and second simple planetary gear sets each having three rotating elements constitutes four rotating elements,

Any one rotating element of the first simple planetary gear set and any one rotating element of the second simple planetary gear set are formed so as to be selectively integrally or separated by being variablely connected to the second rotating element and at the same time the transmission A fourth rotary element variably connected to the housing, any one rotary element of the first simple planetary gear set, and one rotary element of the second simple planetary gear set are directly connected and variably connected to the input shaft, A fifth rotary element variably connected to the housing, a sixth rotary element connected to an output shaft as the other rotary element of the first simple planetary gear set, and always operated only as an output element, and of the second simple planetary gear set. A second planetary device having a seventh rotating element which is directly connected to the input shaft as the other rotating element and operated as an input element; Including the set provide a gear train of a vehicle automatic transmission according.

Clutch means for variably connecting the rotation elements of the first and second planetary gear set, and brake means for variably connecting the rotation elements with the transmission housing,

A first clutch disposed between two components forming the fourth rotating element, and disposed between the second rotating element and the fourth rotating element, wherein the first simple planetary gear set of the fourth rotating element is configured. A second clutch connected to the element side; A third clutch disposed between the input shaft and the fifth rotating element; A first brake disposed in parallel with the one-way clutch between the fifth rotating element and the transmission housing; And a second brake disposed between the fourth rotating element and the transmission housing.

According to the above configuration, the first clutch and the first brake or the one-way clutch are operated at the first forward speed, the first clutch and the second brake are operated at the second forward speed, and the first clutch and the second clutch are operated at the third forward speed. The first clutch and the third clutch are operated at the fourth forward speed, the second and third clutches are operated at the fifth forward speed, the third clutch and the second brake are operated at the sixth forward speed, The shift is performed while the second clutch and the first brake are operated.

In the first embodiment of the present invention as described above, the first planetary gear set is a single pinion planetary gear set, wherein the first rotating element is the first sun gear, the second rotating element is the first planet carrier, and the third rotating element is the first planetary gear set. 1 ring gear

In the second planetary gear set, the first simple planetary gear set consists of a single pinion planetary gear set, and the second simple planetary gear set consists of a double pinion planetary gear set, wherein the fourth rotating elements are variably connected to each other. The fifth rotating element may include the second planetary carrier and the third ring gear, the sixth rotating element may be the second ring gear, and the seventh rotating element may be the third planetary carrier.

In the second embodiment of the present invention as described above, the first planetary gear set is a double pinion planetary gear set, where the first rotating element is the first sun gear, the second rotating element is the first ring gear, and the third rotating element is Consisting of a first planetary carrier,

In the second planetary gear set, the first simple planetary gear set consists of a single pinion planetary gear set, and the second simple planetary gear set consists of a double pinion planetary gear set, wherein the fourth rotating elements are variably connected to each other. The fifth rotating element may include the second planetary carrier and the third ring gear, the sixth rotating element may be the second ring gear, and the seventh rotating element may be the third planetary carrier.

In the third embodiment of the present invention as described above, the first planetary gear set is a double pinion planetary gear set, wherein the first rotating element is the first sun gear, the second rotating element is the first ring gear, and the third rotating element is the first Consists of 1 planetary carrier,

In the second planetary gear set, the first and second simple planetary gear sets are composed of a single pinion planetary gear set, and the second and third sun gears in which the fourth rotating elements are variably connected to each other, and the fifth rotating elements are the second and third planetary gear sets. The carrier, the sixth rotating element is a second ring gear, the seventh rotating element is characterized in that the third ring gear.

In the fourth embodiment of the present invention as described above, the first planetary gear set is a single pinion planetary gear set, wherein the first rotating element is the first sun gear, the second rotating element is the first planet carrier, and the third rotating element is the first planetary gear set. 1 ring gear

In the second planetary gear set, the first and second simple planetary gear sets are composed of a single pinion planetary gear set, and the second and third sun gears in which the fourth rotating elements are variably connected to each other, and the fifth rotating elements are the second and third planetary gear sets. The carrier, the sixth rotation element is the second ring gear, the seventh rotation element is characterized in that consisting of a third ring gear.

As described above, by combining one simple planetary gear set and one compound planetary gear set with three clutches and two brakes, a shift stage of 6 forward speeds and 1 reverse speed can be realized to improve power transmission performance and improve fuel economy. Will be.

In addition, by distributing the friction elements, the configuration of the flow path is facilitated, and the two friction elements operate at each shift stage, so that the shift is made, thereby reducing the capacity of the oil pump and increasing the hydraulic control efficiency.

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

 1 is a configuration diagram of a power train according to a first embodiment of the present invention, in which a gear train according to the present invention includes first and second planetary gear sets PG1 and PG2 arranged on the same axis, and three clutches. And clutch means composed of (C1) (C2) and C3, and brake means composed of two brakes (B1) and (B2).

Accordingly, a rotation input from the input shaft IS is directly input to the first planetary gear set PG1, and a variable input is performed to the second planetary gear set PG2.

The first planetary gear set PG1 is decelerated and input to the second planetary gear set PG2, and the second planetary gear set PG1 is transmitted from the first planetary gear set PG1. The rotational power and the rotational power selectively input from the input shaft IS are shifted to 6 forward speeds and 1 reverse speed to be output through the output shaft OS.

To this end, the first planetary gear set PG1 is disposed to the engine side, and the second planetary gear set PG2 is sequentially disposed to the rear side thereof.

The input shaft IS refers to the turbine shaft of the torque converter as an input member, which means that the rotational power from the crank shaft of the engine is input while torque conversion is performed through the torque converter, and the output shaft OS is not shown as the output member. The drive wheels are driven by a known differential device via an output gear.

The first planetary gear set PG1 is formed of a simple planetary gear set, and is a single pinion planetary gear set. The first rotational element N1 consisting of the first sun gear S1 and the first planetary carrier path PC1 are provided. It comprises a second rotating element (N2) consisting of, and a third rotating element (N3) consisting of a first ring gear (R1).

The first rotating element {N1; The first sun gear S1} is directly connected to the transmission housing H so that it can always operate as a fixed element.

The second rotating element {N2; The first planet carrier PC1} forms an intermediate output path MOP in which the deceleration output is always performed.

The third rotating element {N3; The first ring gear R1} is directly connected to the input shaft IS so as to operate as an input element at all times to form the first input path IP1.

The second planetary gear set PG2 is formed of a combination of the first and second simple planetary gear sets SPG1 and SPG2. The fourth, fifth, sixth and seventh rotating elements N4, N5, N6, and N7 In the first embodiment of the present invention, the first simple planetary gear set SPG1 is formed of a single pinion planetary gear set, and the second simple planetary gear set SPG2 is formed of a double pinion planetary gear set. .

In the interconnection of the first and second simple planetary gear sets SPG1 and SPG2, the second carrier PC2 and the third ring gear R3 are directly connected to each other, and the second and third wire gears S2 are connected. (S3) was variably connected via the 2nd clutch C2.

Accordingly, the fourth rotating element N4 includes the second and third sun gears S2 and S3, and the fifth rotating element N5 includes the second planet carrier PC2, the third ring gear R3, and the sixth rotating element. N6 is set to the second ring gear R2, and the seventh rotation element N7 is set to the third planet carrier PC3.

The fourth rotating element {N4; The second and third sun gears S2 and S3 are variable by interposing a second rotary element N2 and a second clutch C2 which form an intermediate output path MOP in the first planetary gear set PG1. By connecting to it, the intermediate input path (MIP) is formed and at the same time it is variably connected to the transmission housing (H) via the second brake (B2), thereby operating as an optional fixing element.

The fifth rotating element {N5; The second planetary carrier PC1 and the third ring gear R3} are variably connected via the input shaft IS and the third clutch C3, thereby forming a variable input path VIP, thereby forming an optional input element. At the same time, the first brake B1 and the one-way clutch F arranged in parallel with each other are variably connected to the transmission housing H to operate as an optional fixing element.

The sixth rotating element {N6; Second ring gear (R2)} is connected to the output shaft (OS) to form a final output path (OP), the seventh rotating element (N7; The third planet carrier PC3} is directly connected to the input shaft IS to form a second input path IP2 and to always operate as an input element.

In the above, the first, second and third clutches C1, C2 and C3 and the first and second brakes B1 and B2 are typically made of a multi-plate hydraulic friction engagement unit friction-coupled by hydraulic pressure.

In arranging the friction member, the first clutch C1 is disposed between the first and second planetary gear sets PG1 and PG2, and the first and second brakes B1 and B2 and the one-way clutch are disposed on the outer circumferential side thereof. (F) was placed.

The second clutch C2 is disposed at the front side of the first planetary gear set PG1, and the third clutch C3 is disposed at the rear side of the second planetary gear set PG2, so that a distributed arrangement is achieved.

By distributing the friction members as described above, it is possible to maintain a stable center of gravity, and there is an advantage that it is very convenient to form a flow path for supplying hydraulic pressure to these friction members.

2 is an operation table showing that the friction member, that is, the clutch and the brake applied to the present invention operate at each shift stage, and the power train of the present invention shows that the shift is performed while the two friction members operate at each shift stage. Can be.

That is, the first clutch C1 and the first brake B1 or the one-way clutch F are operated at the first forward speed, and the first clutch C1 and the second brake B2 are operated at the second forward speed. The first clutch C1 and the second clutch C2 are operated at the third speed, and the first clutch C1 and the third clutch C3 are operated at the fourth forward speed, and the second and third clutch C2 are operated at the fifth forward speed. The third clutch C3 and the second brake B2 are operated at the sixth forward speed, and the second clutch C2 and the first brake B1 are operated at the reverse shift stage, thereby shifting. You lose.

3 shows a speed change diagram of the gear train according to the first embodiment of the present invention, in which the horizontal line on the lower side represents the rotational speed "0", and the horizontal line on the upper side represents the rotational speed "1.0", that is, the input shaft IS. It shows the same rotation speed.

The three vertical lines of the first planetary gear set PG1 are sequentially rotated by the first rotating element {N1; First sun gear S1}, second rotating element N2; First planet carrier PC1}, third rotating element {N3; First ring gear (R1)}, and these intervals are determined according to the gear ratio (number of teeth of ring gear / number of ring gears) of the first simple planetary gear set SPG1 forming the first planetary gear set PG1. do.

Four vertical lines of the second planetary gear set PG2 are sequentially rotated from the left by the fourth rotating element {N4; 2nd, 3rd sun gear S2 (S3)}, the fifth rotating element {N5; Second planet carrier PC2 and third ring gear R3}, sixth rotating element {N6; Second ring gear R2}, seventh rotating element {N7; It is set to the third planet carrier PC3, and these intervals are determined according to the gear ratio of the first and second simple planetary gear sets SPG1 and SGP2 (the number of teeth of the sun gear / the number of rings of the ring gear), and the shift diagram as described above. Since is well known to those skilled in the art of gear trains, a detailed description thereof will be omitted.

[1st speed forward]

At the first forward speed, as shown in FIG. 2, the first clutch C1 and the one-way clutch F are controlled to operate.

Accordingly, in the first planetary gear set PG1, as shown in FIG. 3, the first rotary element N1 operates as a fixed element while the second rotary element N1 operates as a fixed element. The deceleration output is made to N2) but is not transmitted to the second planetary gear set PG2.

In addition, in the second planetary gear set PG2, the fourth operating element N4 is operated as a fixed element by the operation of the one-way clutch F while the input is made to the seventh rotary element N7. As the first shift line SP1 connecting the seventh rotation element N7 and the fifth rotation element N5 is formed, as much as D1 is output through the sixth rotation element N6, which is an output element, moving forward. One speed shift will be made.

That is, in the forward 1 speed, the first planetary gear set PG1 is not involved in shifting, and the second planetary gear set PG2 is a rotational power input to the seventh rotation element N7 through the second input path IP2. As the speed is reduced and output by the operation of the fixing element of the fifth rotating element N5, the speed change of the forward 1 speed is achieved.

[2 speed forward]

In the second forward speed, the second brake B2 is operated and controlled in the state of the first forward speed.

Then, while the fixed element is converted to the fourth rotating element N4 in the state of the first forward speed, the second shift line SP2 is formed, and as much as D2 is output through the sixth rotating element N6 as the output element, the forward is made. Two-speed shift will be made.

That is, at the second forward speed, the first planetary gear set PG1 is not involved in the shifting, and the second planetary gear set PG2 is a rotational power input to the seventh rotation element N7 through the second input path IP2. As the speed is reduced and output by the operation of the fixing element of the fifth rotating element N5, the speed change of the forward 1 speed is achieved.

[3 speed forward]

At the third forward speed, as shown in FIG. 2, the second brake B2 is released from the second forward speed, and the second clutch C2 is controlled to operate.

Then, while the rotational power of the input shaft IS is input from the second planetary gear set PG2 to the seventh rotary element N7, the speed is reduced through the second rotary element N2 of the first planetary gear set PG2. The output rotational power is input through the fourth rotating element N4, which is an intermediate input path MOP. As a third shift line SP3 is formed by complementary operation, the sixth rotating element N6, which is an output element, is formed. As much as D3 is output, the speed of 3rd forward is made.

That is, in the third forward speed, the rotational power inputted through the intermediate input path MOP to the second planetary gear set PG1 and the rotational power inputted through the second input path IP2 are shifted to each other in a complementary action, and thus the second input is performed. By shifting and outputting the rotation speed smaller than the rotation speed input through the path (IP2) and larger than the rotation speed input through the intermediate input path (MOP), the third forward speed is made.

[4 forward speed]

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

Then, since the second clutch C2 does not operate, the seventh rotary element (PG2) may operate in the second planetary gear set PG2 while the power transmission path connecting the first and second planetary gear sets PG1 and PG2 is blocked. N7) bar is input to the fifth rotating element N5 by the operation of the third clutch C3, the second planetary gear set (PG2) is in a direct connection state.

Accordingly, in the second planetary gear set PG2, the fourth shift line SP4 is directly connected to the fourth planetary gear set PG2, and the fourth shift line SP4 is output as D4 as it is through the sixth rotation element N6. Will be done.

[5th forward]

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

Then, in the second planetary gear set PG2, the first and second simple planetary planets may be simultaneously inputted through the seventh rotary element N7 and the fifth rotary element N5 due to the release of the first clutch C1. The gear sets SPG1 and SPG2 do not cause mutual interference.

In addition, the second simple planetary gear set SPG2 is directly connected to the second planetary carrier PC2 that forms the fifth rotating element N5 while the second planetary gear set SPG2 is directly connected. The rotational power reduced in PG1 is input to the second sun gear S2 forming the fourth rotating element N4, and thus the fifth shift connecting the fourth rotating element N4 and the fifth rotating element N5 is performed. As the line SP5 is formed, the 5th forward speed shift, which is an overdrive state as much as D5, is performed through the sixth rotating element N6 as the output element.

[6th forward]

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

Then, the second planetary gear set PG2 connects the fourth rotating element N4 and the fifth rotating element N5 while the fourth rotating element N4 is converted into the fixed element in the same state as the fifth forward speed. As the sixth shift line SP6 is formed, the sixth forward speed in the overdrive state as much as D6 is achieved through the sixth rotation element N6 as the output element.

[apse]

In the reverse shift stage, the second clutch C2 and the first brake B1 are operated and controlled as shown in FIG. 2.

Then, the deceleration output of the first planetary gear set PG1 is input to the fourth rotary element N4 of the second planetary gear set PG2 through the intermediate input path MOP by the operation of the second clutch C2. In the state, the fifth rotating element N5 is operated as a fixed element by the operation of the first brake B1. As the reverse shift line SR is formed, as much as RS through the sixth rotating element N6 as an output element. Reverse rotation output will be made.

At this time, even if an input is made through the seventh rotating element N7, the first and second simple planetary gear sets SPG1 and SPG2 do not cause mutual interference due to the deactivation of the first clutch C1. Reverse operation is achieved only by operation of the planetary gear set SPG1.

 In summary, the first planetary gear set PG1 is a simple planetary gear set having three rotating elements, and the first rotating element as a technical gist of the gear train according to the first embodiment of the present invention. N1 is a fixed element, the second rotating element N2 is an intermediate output element, and the third rotating element N3 is formed as an input element.

The second planetary gear set PG2 combines the first and second simple planetary gear sets SPG1 and SPG2 having three rotating elements, respectively, to form four rotating elements.

Fourth rotating element (N4) is formed so as to be selectively connected to one of the rotating elements of the first simple planetary gear set (SPG1) to any one of the rotating elements of the second simple planetary gear set (SPG2) selectively integrated or separated )Wow,

 A fifth rotating element formed by directly connecting one rotating element of the first simple planetary gear set SPG1 with one rotating element of the second simple planetary gear set SPG2;

A sixth rotating element formed of the other rotating element of the first simple planetary gear set SPG1;

The seventh rotary element including the other rotary element of the second simple planetary gear set SPG2 is retained.

In addition, the fourth rotary element N4 is variably connected to the second rotary element N2 of the first planetary gear set PG1 and variably connected to the transmission housing, so that the forward and third speeds and the reverse shift stage are It acts as an intermediate input element and acts as a fixed element at forward 2 and 6 speeds.

The fifth rotating element N5 is variably connected to the input shaft IS and variably connected to the transmission housing to operate as an input element at forward 4, 5, and 6 speeds, and is fixed at the forward 1 speed and reverse shift stages. Will work as

The sixth rotating element N6 is connected to the output shaft OS to operate only as an output element at all times, and the seventh rotating element N7 is directly connected to the input shaft IS so as to be operated at forward 1, 2, 3 and 4 speeds. It acts as an input element.

With the above configuration, as shown in FIG. 3, at the first forward speed, the seventh rotating element N7 operates as an input element while the first clutch C2 operates, and the fifth rotating element is operated by the operation of the one-way clutch F. FIG. (N5 (is a fixed element, shifting takes place.

In the second forward speed, the shift is performed while the fixed element is converted into the fourth rotating element N4 by the operation of the second brake B2 in the first speed state.

In the third forward speed, the second brake B2 is released in the second speed state and the second clutch C2 is operated, whereby the fourth rotary element N4 is inputted to the seventh rotary element N7. As the low deceleration input is made, the shift is made.

At the fourth forward speed, the operation of the second clutch C2 is canceled in the state of the third forward speed, and the third clutch C3 is operated to be in a direct connection state and output at the same speed as the input is achieved.

At the 5th forward speed, the first clutch C1 operated until the 4th forward speed is released, and the second and third sun gears S2 and S3 of the second planetary gear set PG2 are released. An input is made only to the fourth rotating element N4 and an input is made to the fifth rotating element N5, thereby outputting the over driver state.

At the 6th forward speed, the second clutch C2 is released in the state of the 5th forward speed, and the second brake B2 is operated to convert the fixed element into the fourth rotating element N4 and to move forward of the highest speed shift stage. 6 speed output is achieved.

In the reverse shift stage, while the deceleration input is made to the fourth rotary element N4 by the operation of the second clutch N2, the reverse rotation output is performed while the fifth rotary element N5 operates as a fixed element. will be.

In the shifting process as described above, when the operation of the first clutch C1 is released as in the forward 5, 6 speed and reverse shift stages, the second and third sun gears S2 and S3 are released. Even if an input is made to the element, the second planetary gear set PG2 is not directly connected, and thus the shift stage is shifted.

In order to implement the shift stage as described above, the second clutch C2 is connected to the second sun gear when the second rotation element N2 and the fourth rotation element N4 are variably connected using the second clutch C2. It must be configured to connect with (S2).

The gear trains shown in Figures 4-7 illustrate another embodiment that can be included in the shift principle described above.

4 illustrates a second embodiment according to the present invention. In the first embodiment, the first planetary gear set PG1 is applied as a single pinion planetary gear set. It is applied as a pinion planetary gear set.

Accordingly, compared with the first embodiment, the second rotary element N2 is changed from the first planet carrier PC1 to the first ring gear R1, and the third rotary element N3 is changed to the first planet carrier ( PC1).

The second planetary gear set PG2 has the fourth, fifth, sixth and seventh rotating elements N4, N5, N6, and N7 in the same manner as in the first embodiment. Since it is made the same as in Figure 3, a detailed description of the shifting process will be omitted.

FIG. 5 shows a third embodiment according to the present invention. In the second embodiment, the second planetary gear set PG2 is formed of a single pinion planetary gear set, and the first simple planetary gear set SPG1 is doubled. The second simple planetary gear set (SPG2) consisting of a pinion planetary gear set is applied, but in the third embodiment, the second simple planetary gear set (SPG2) is applied as a single pinion planetary gear set.

Accordingly, the fifth rotating element N5 is changed from the second planetary carrier PC2 and the third ring gear R3 to the second and third planetary carriers PC2 and PC3, and the seventh rotating element N7 is changed. The third ring gear R3 is changed from the third planet carrier PC3.

The third embodiment, which is configured as described above, differs only in the components of the fifth and seventh rotating elements N5 and N7 as compared to the second embodiment, and thus the shifting process is performed in the same manner as in FIG. 3. Is omitted.

FIG. 6 shows a fourth embodiment according to the present invention. In the first embodiment, the first simple planetary gear set SPG1 comprising the second planetary gear set PG2 as a single pinion planetary gear set, and a double The second simple planetary gear set (SPG2) consisting of a pinion planetary gear set is applied. However, in the fourth embodiment, the second simple planetary gear set (SPG2) is applied as a single pinion planetary gear set.

Accordingly, the fifth rotating element N5 is changed from the second planetary carrier PC2 and the third ring gear R3 to the second and third planetary carriers PC2 and PC3, and the seventh rotating element N7 is changed. The third ring gear R3 is changed from the third planet carrier PC3.

In the fourth embodiment configured as described above, only the components of the fifth and seventh rotating elements N5 and N7 are changed in comparison with the first embodiment, and thus the shifting process is performed in the same manner as in FIG. 3. Is omitted.

7 shows a fifth embodiment according to the present invention. In the fourth embodiment, the third clutch C3 is disposed on the rear side of the second planetary gear set PG2. By disposing between the planetary gear set PG1 and the first clutch C1, the clutch can be combined to make the configuration compact. Since the shifting process is the same as in FIG. 3, detailed description 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 the present invention can be easily invented by those skilled in the art to which the present invention pertains. 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 of a gear train according to the present invention;

Figure 4 is a block diagram of the gear train of the second embodiment according to the present invention.

5 is a block diagram of a gear train in a third embodiment according to the present invention;

6 is a block diagram of a gear train in a fourth embodiment according to the present invention;

7 is a configuration diagram of a gear train of a fifth embodiment according to the present invention.

Claims (23)

A simple planetary gear set having three rotating elements, comprising: a first rotating element fixedly connected to a transmission housing to operate as a fixed element; a second rotating element having a deceleration output as an output element; A first planetary gear set connected to the third planetary gear set, the first planetary gear set being connected to the first rotary element; Combination of the first and second simple planetary gear sets each having three rotating elements constitutes four rotating elements, Any one rotating element of the first simple planetary gear set and any one rotating element of the second simple planetary gear set are formed so as to be selectively integrally or separated by being variablely connected to the second rotating element and at the same time the transmission A fourth rotary element variably connected to the housing, any one rotary element of the first simple planetary gear set, and one rotary element of the second simple planetary gear set are directly connected and variably connected to the input shaft, A fifth rotary element variably connected to the housing, a sixth rotary element connected to an output shaft as the other rotary element of the first simple planetary gear set, and always operated only as an output element, and of the second simple planetary gear set. A second planetary device having a seventh rotating element which is directly connected to the input shaft as the other rotating element and operated as an input element; Yirueojim characterized automotive gear train of an automatic transmission according to an including a set. According to claim 1, Clutch means for variably connecting the rotation elements of the first and second planetary gear set, and brake means for variably connecting the rotation elements with the transmission housing, A first clutch disposed between two components forming said fourth rotating element, A second clutch disposed between the second rotating element and the fourth rotating element and connected to the component side of the first simple planetary gear set of the fourth rotating element; A third clutch disposed between the input shaft and the fifth rotating element; A first brake disposed in parallel with the one-way clutch between the fifth rotating element and the transmission housing; And a second brake disposed between the fourth rotating element and the transmission housing. The first clutch, the one-way clutch, the first brake, and the second brake are disposed between the first and second planetary gearsets, and the second clutch is the front side of the first planetary gearset. And a third clutch disposed at a rear side of the second planetary gear set. The first and third clutches, a first brake including a one-way clutch, and a second brake are disposed between the first and second planetary gear sets, and the second clutch is disposed in the first clutch. Gear train of an automatic transmission for a vehicle, characterized in that disposed on the front side of the planetary gear set. The method of claim 1 or 2, wherein the first clutch and the first brake or one-way clutch are operated at the first forward speed, The first clutch and the second brake are operated at the second forward speed, The first clutch and the second clutch are operated at three forward speeds, The first clutch and the third clutch are operated at four forward speeds, The second and third clutches are operated at five forward speeds, The third clutch and the second brake are operated at six forward speeds, A gear train of an automatic transmission for a vehicle, characterized in that the shift is performed while the second clutch and the first brake are operated in the reverse shift stage. According to claim 1 or 2, wherein the first forward speed is shifted while the seventh rotary element is operated as an input element while the first clutch is operated and the fifth rotary element is operated as a fixed element by the operation of the one-way clutch. Gear train of an automatic transmission for a vehicle, characterized by output through six rotating elements. The second forward speed is shifted by shifting the seventh rotating element as the input element while the first clutch is operated and the fourth rotating element as the fixed element by the operation of the second brake. Gear train of an automatic transmission for a vehicle, characterized by output through six rotating elements. According to claim 1 or 2, wherein the third forward speed is shifted by the deceleration input to the fourth rotating element by the seventh rotary element is operated as the input element in the state that the first clutch is operating and the second clutch is shifted Gear train of an automatic transmission for a vehicle, characterized by output through six rotating elements. According to claim 1 or 2, wherein the fourth forward speed is the sixth rotation element is the operating state of the seventh rotary element as the input element in the state of operating the first clutch and the second planetary gear set is directly connected by the operation of the third clutch sixth Gear train of an automatic transmission for a vehicle, characterized in that the output is driven at the same speed as the input through the rotating element. The fifth forward speed is set by the operation of the third clutch in a state in which the deceleration input is made to the fourth rotating element by the operation of the second clutch while the operation of the first clutch is released. The gear train of the vehicle automatic transmission characterized in that the input is made to the rotating element is shifted to the overdrive state and output through the sixth rotating element. The sixth forward speed according to claim 1 or 2, wherein the sixth forward speed is over when the sixth rotating element operates as an input element while the first clutch is released and the fourth rotating element operates as a fixed element by the operation of the second brake. The gear train of the automatic transmission for a vehicle which is shifted to a drive state and outputted through a sixth rotating element. The reverse shifting method according to claim 1 or 2, wherein the reverse shift is performed by operating the first brake while the deceleration input is made to the fourth rotating element while the first clutch is released. A gear train of an automatic transmission for a vehicle, characterized in that a reverse rotation output is made through a sixth rotating element during operation. 2. The first planetary gearset of claim 1, wherein the first planetary gearset is a single pinion planetary gearset, wherein the first rotating element comprises a first sun gear, the second rotating element comprises a first planetary carrier, and the third rotating element comprises a first ring gear. , In the second planetary gear set, the first simple planetary gear set consists of a single pinion planetary gear set, and the second simple planetary gear set consists of a double pinion planetary gear set, wherein the fourth rotating elements are variably connected to each other. And a fifth rotary element is formed of the second planetary carrier and the third ring gear, the sixth rotary element is the second ring gear, and the seventh rotary element is the third planetary carrier. 2. The first planetary gearset of claim 1, wherein the first planetary gearset is a double pinion planetary gearset, wherein the first rotating element comprises a first sun gear, the second rotating element comprises a first ring gear, and the third rotating element comprises a first planetary carrier. , In the second planetary gear set, the first simple planetary gear set consists of a single pinion planetary gear set, and the second simple planetary gear set consists of a double pinion planetary gear set, wherein the fourth rotating elements are variably connected to each other. And a fifth rotary element is formed of the second planetary carrier and the third ring gear, the sixth rotary element is the second ring gear, and the seventh rotary element is the third planetary carrier. 2. The first planetary gearset of claim 1, wherein the first planetary gearset is a double pinion planetary gearset, wherein the first rotating element comprises a first sun gear, the second rotating element comprises a first ring gear, and the third rotating element comprises a first planetary carrier. , In the second planetary gear set, the first and second simple planetary gear sets are composed of a single pinion planetary gear set, and the second and third sun gears in which the fourth rotating elements are variably connected to each other, and the fifth rotating elements are the second and third planetary gear sets. A gear train of an automatic transmission for a vehicle, characterized in that the carrier, the sixth rotating element consists of a second ring gear, and the seventh rotating element consists of a third ring gear. 2. The first planetary gearset of claim 1, wherein the first planetary gearset is a single pinion planetary gearset, wherein the first rotating element comprises a first sun gear, the second rotating element comprises a first planetary carrier, and the third rotating element comprises a first ring gear. , In the second planetary gear set, the first and second simple planetary gear sets are composed of a single pinion planetary gear set, and the second and third sun gears in which the fourth rotating elements are variably connected to each other, and the fifth rotating elements are the second and third planetary gear sets. A gear train of a vehicular automatic transmission, characterized in that the carrier, the sixth rotating element consists of the second ring gear, and the seventh rotating element consists of the third ring gear. A single pinion planetary gear set, comprising: a first rotational element comprising a first sun gear fixedly connected to a transmission housing so as to operate as a fixed element at all times; and a second rotation consisting of a first planetary carrier having a deceleration output as an output element at all times. A first planetary gear set including an element and a third rotating element directly connected to the input shaft and always acting as an input element; Combining the first simple planetary gear set, which is a single pinion planetary gear set, and the second simple planetary gear set, which is a double pinion planetary gear set, forms four rotating elements. The second sun gear of the first simple planetary gear set and the second sun gear of the second simple planetary gear set are connected to each other via a first clutch to be selectively integrated or separated, and interposed between the second rotating element and the second clutch. And a fourth rotating element connected to the transmission housing via a first brake in which the original clutch is connected in parallel with the first wheel, and a ring gear of the second planetary carrier of the first simple planetary gear set and the second simple planetary gear set. Is connected directly via an input shaft and a third clutch, and is connected to a fifth rotating element connected to a transmission housing via a second brake, and is connected to an output shaft as a second ring gear of the first simple planetary gear set. A sixth rotating element acting only as an output element and a third planetary carrier of the second simple planetary gearset that is directly connected to the input shaft and operated as an input element And a second planetary gear set having a seventh rotating element. A double pinion planetary gear set comprising: a first rotational element comprising a first sun gear fixedly connected to a transmission housing so as to operate as a fixed element at all times; and a second rotation including a first ring gear having a deceleration output as an output element at all times. A first planetary gear set including an element and a third rotating element directly connected to the input shaft and having a first planetary carrier acting as an input element at all times; Combining the first simple planetary gear set, which is a single pinion planetary gear set, and the second simple planetary gear set, which is a double pinion planetary gear set, forms four rotating elements. The second sun gear of the first simple planetary gear set and the second sun gear of the second simple planetary gear set are connected to each other via a first clutch to be selectively integrated or separated, and interposed between the second rotating element and the second clutch. And a fourth rotating element connected to the transmission housing via a first brake in which the first wheel clutch is connected in parallel with the first wheel, and a ring gear of the second planetary carrier of the first simple planetary gear set and the second simple planetary gear set. Is connected directly via an input shaft and a third clutch, and is connected to a fifth rotating element connected to a transmission housing via a second brake, and is connected to an output shaft as a second ring gear of the first simple planetary gear set. A sixth rotating element acting only as an output element and a third planetary carrier of the second simple planetary gearset that is directly connected to the input shaft and operated as an input element And a second planetary gear set having a seventh rotating element. A double pinion planetary gear set comprising: a first rotational element comprising a first sun gear fixedly connected to a transmission housing so as to operate as a fixed element at all times; and a second rotation including a first ring gear having a deceleration output as an output element at all times. A first planetary gear set including an element and a third rotating element directly connected to the input shaft and having a first planetary carrier acting as an input element at all times; Combining the first and second simple planetary gear sets, which are single pinion planetary gear sets, constitutes four rotating elements, The second sun gear of the first simple planetary gear set and the second sun gear of the second simple planetary gear set are connected to each other via a first clutch to be selectively integrated or separated, and interposed between the second rotating element and the second clutch. And a fourth rotating element connected to the transmission housing via a first brake through which the first wheel clutch is connected in parallel, and the second and third planetary carriers of the first and second simple planetary gear sets are directly connected to each other. A fifth rotating element connected to the transmission housing via a second brake and connected to the third clutch and connected to an output shaft as a second ring gear of the first simple planetary gear set, which is always operated only as an output element; A second planetary gear having a sixth rotating element and a seventh rotating element directly connected to the input shaft as a third ring gear of the second simple planetary gearset to operate as an input element; Gear train of a vehicular automatic transmission, characterized in that it comprises an asset. A single pinion planetary gear set, comprising: a first rotational element comprising a first sun gear fixedly connected to a transmission housing so as to operate as a fixed element at all times; and a second rotation consisting of a first planetary carrier having a deceleration output as an output element at all times. A first planetary gear set including an element and a third rotating element directly connected to the input shaft and always acting as an input element; Combining the first and second simple planetary gear sets, which are single pinion planetary gear sets, constitutes four rotating elements, The second sun gear of the first simple planetary gear set and the second sun gear of the second simple planetary gear set are connected to each other via a first clutch to be selectively integrated or separated, and interposed between the second rotating element and the second clutch. And a fourth rotating element connected to the transmission housing via a first brake through which the first wheel clutch is connected in parallel, and the second and third planetary carriers of the first and second simple planetary gear sets are directly connected to each other. A fifth rotating element connected to the transmission housing via a second brake and connected to the third clutch and connected to an output shaft as a second ring gear of the first simple planetary gear set, which is always operated only as an output element; A second planetary gear having a sixth rotating element and a seventh rotating element directly connected to the input shaft as a third ring gear of the second simple planetary gearset to operate as an input element; Gear train of a vehicular automatic transmission, characterized in that it comprises an asset. 21. The method of claim 17, wherein the first clutch, the one-way clutch, the first brake, and the second brake are disposed between the first and second planetary gearsets, and the second clutch is the first planetary gear. The gear train of the automatic transmission for a vehicle, wherein the third clutch is disposed at the front side of the gear set, and the third clutch is disposed at the rear side of the second planetary gear set. 21. The method according to any one of claims 17 to 20, wherein the first and third clutches, the first brake including the one-way clutch, and the second brake are disposed between the first and second planetary gear sets, and the second A gear train of an automatic transmission for a vehicle, characterized in that the clutch is disposed on the front side of the first planetary gear set. 21. The drive according to any one of claims 17 to 20, wherein the first clutch and the first brake or one-way clutch are actuated at one forward speed, The first clutch and the second brake are operated at the second forward speed, The first clutch and the second clutch are operated at three forward speeds, The first clutch and the third clutch are operated at four forward speeds, The second and third clutches are operated at five forward speeds, The third clutch and the second brake are operated at six forward speeds, A gear train of an automatic transmission for a vehicle, characterized in that the shift is performed while the second clutch and the first brake are operated in the reverse shift stage.

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