KR100623781B1 - A 6th-SPEED POWER TRAIN OF AN AUTOMATIC TRANSMISSION FOR A VEHICLE - Google Patents

Abstract

The present invention applies three single pinion planetary gear sets, which are advantageous in terms of volume and weight, so that the entire single pinion planetary gear sets include a direct connection to each other, thereby improving power transmission efficiency, and at the same time, a part of the high speed stage is used to increase the power of the input shaft. It provides a six-speed power train of an automatic transmission for a six-speed forward and a first-speed vehicle for transmission at a gear ratio to maximize its power transmission efficiency.

Automatic transmission. clutch. Planetary gear set, power train, 6 speed

Description

A 6th-SPEED POWER TRAIN OF AN AUTOMATIC TRANSMISSION FOR A VEHICLE}

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

2 is an operating element table of a power train according to an embodiment of the present invention;

3 is a shift diagram of a power train according to an embodiment of the present invention;

4 is a schematic diagram of a conventional power train,

5 is a table of operating elements of a conventional power train, and

6 is a shift diagram of a conventional power train.

The present invention relates to a six-speed power train of an automatic transmission for a vehicle that is applied to an automatic transmission for a vehicle to realize a sixth forward speed and one reverse speed.

For example, the multi-speed gear mechanism of an automatic transmission is composed of a combination of a plurality of planetary gear sets, and a power train in which the plurality of planet gear sets is combined, when a rotational power is input from a torque converter that converts and transmits engine torque, is transmitted. It performs the function of transmitting to the output side by shifting to multiple stages.

Since the power train of the automatic transmission has more shift stages, it is advantageous in terms of power performance and fuel consumption rate, and thus, a power train capable of implementing more shift stages is required.

Also, even if the same number of gear stages are implemented, durability, power transmission efficiency, size and weight vary greatly depending on the combination method of the planetary gear set. Therefore, the power train can be more robust and compact while minimizing power loss. Efforts for development are ongoing.

Thus, in developing a power train using a planetary gear set, a new planetary gear set is not developed, but a single pinion planetary gear set, a double pinion planetary gear set, or a single and double pinion planetary gear set. How to combine the planetary gear set of the combination type, and the accompanying clutch, brake, and one-way clutch to place a few in any position to implement the desired gear stage and the corresponding gear ratio without possible power loss Various studies are underway with the goal of improving performance.

In particular, in the case of a manual transmission, if there are too many shift stages, the driver should shift frequently. However, in the case of an automatic transmission, the transmission control unit automatically controls the operation of the power train in accordance with the driving state to change the shift. As a result, developing a power train that can implement more shifts is of great value.

In order to cope with this trend, various researches on 4 speed and 5 speed power trains are being conducted. In addition, recently, a power train of an automatic transmission capable of implementing 6 speed forward and 1 speed reverse gears has been provided.

As an example, as shown in FIG. 4, one single pinion planetary gear set (SPG) is combined with one rib type planetary gear set (LPG) in the rear, and a single pinion planetary gear set (SPG) is used. The first sun gear S1 is fixed to the transmission housing 1, and the output gear OUT is mounted on the second ring gear R2 (R3) of the planetary gear set LPG. Will work.

The first ring gear R1 of the single pinion planetary gear set SPG is directly connected to the input shaft 3 and connects the second and third planetary gears P2 and P3 of the planetary gear set LPG. Three planetary carriers PC3 are variably connected to the input shaft 3 via a third clutch C3.

Further, the first planet carrier PC1 connecting the first planetary gear P1 of the single pinion planetary gear set SPG may have a first clutch between the third sun gear S3 of the rib planetary gear set LPG. They are variably connected to each other via (C1), which in turn are variably connected to each other via a second clutch (C2) between the second sun gear (S2).

In addition, the second sun gear S2 is variably fixed to the transmission housing 1 through the second brake B2 and connects only the second planetary gear P2 of the rib planetary gear set LPG. The second planetary carrier PC2 is variably connected to the transmission housing 1 via a first brake B1 disposed in parallel with the second brake B2 in the transmission housing 1.

As illustrated in FIG. 5, the power train operates the first clutch C1 and the first brake B1 at the first forward speed, and the first clutch C1 and the second brake B2 at the second speed. The first clutch C1 and the second clutch C2 operate in the third speed.

In the fourth speed, the first clutch C1 and the third clutch C3 are operated. In the fifth speed, the second and third clutches C2 and C3 are operated. In the sixth speed, the third clutch C3 and the third clutch are operated. The second brake B2 is operated, and the second clutch C2 and the first brake B1 are operated at the reverse shift stage, thereby implementing a shift stage of 6 forward speed and 1 reverse speed as shown in FIG. 6. .

However, in the power train as described above, as shown in FIG. 6, a gear stage in which three planet gears are powered and rotated is one second gear stage, and a gear stage in which two planet gears are powered and rotates is a first gear stage. The fourth gear and the fifth gear are three, and only one planetary gear is powered by two gears, which are rotated while the third gear and the sixth gear are rotated.

In other words, by excluding the gear stages in which all planetary gears are directly connected to each other, in terms of power transmission efficiency of the overall automatic transmission, the power loss due to the cloud efficiency of the gear increases.

In addition, the power transmission of the input shaft 3, which is always decelerated from the single pinion planetary gear set SPG, is transmitted to the planetary gear set LPG in which the output element is implemented. The problem is indicated.

Accordingly, the present invention has been invented to solve the above-mentioned conventional problems, and an object of the present invention is to apply three single pinion planetary gearsets, which are advantageous in terms of volume and weight, so that the entire single pinion planetary gearset includes a direct connection with each other. It is to provide a six-speed power train of an automatic transmission for a six-speed forward and one-speed vehicle to transfer the power of the input shaft to the gear ratio to maximize the power transmission efficiency. .

In order to realize the above object, the six-speed power train of the automatic transmission for a vehicle according to the present invention is a six-speed power train of the automatic transmission for a vehicle formed by combining three planetary gear sets.

The first planetary gear set is a single pinion planetary gear set (SPG) whose sun gear is variably connected to the transmission case via a brake, one side planet carrier is directly connected to the input shaft, and the second planetary gear set is a single pinion planetary gear. The sun gear is variably connected to the other planetary carrier of the first planetary gear set through a mutual clutch, and the planetary carrier of the one side is composed of an output element, and the third planetary gear set is a single pinion planetary gear. The sun gear is directly connected to the ring gear of the first planetary gear set by a set SPG, and is variably connected to the transmission case through a brake, and the one planet carrier is directly connected to the ring gear of the second planetary gear set. And a brake configured in parallel to the transmission case and a one-way clutch, and the other planet carrier is connected to the first planet gear through a clutch. Variablely connected to the other planetary carrier of the set, the ring gear is directly connected to the other planetary carrier of the second planetary gear set, the shift of 6 forward speed and 1 reverse speed by the operation control of the operating element consisting of the clutch and brake Characterized in that they are combined to implement a stage.

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

1 schematically shows an embodiment of a power train according to the present invention, in which the power train of the present invention has a first, second and third planetary gear for an input shaft 3 connected to an engine output side via a torque converter. Sets PG1, PG2, and PG3 are combined to implement shift stages of six forward speeds and one reverse speed.

The first planetary gear set PG1 includes a first sun gear S1, a first ring gear R1, and a first planetary gear meshed between the first sun gear S1 and the first ring gear R1. It consists of a single pinion planetary gear set (DPG) constituting the first planet carrier (PC1) rotatably supporting (P1) on both sides.

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

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

In the arrangement of the first, second and third planetary gear sets PG1 and PG2 and PG3, the first, second and third planetary gear sets PG1 and PG2 and PG3 are sequentially arranged from the front side of the transmission.

First, in the first planetary gear set PG1, the first sun gear S1 is variably connected to the transmission case 1 through a third brake B3 to operate as a variable fixing element, and the first sun gear set PG1 may operate as a variable fixing element. The one planet carrier PC1 is directly connected to the input shaft 3 to operate as an input element at all times.

The second planetary gear set PG2 is connected so that the second sun gear S2 is variably coupled to the other side of the first planetary carrier PC1 through the first clutch C1, and the second planetary carrier PC2) is configured such that the output gear is connected to one side to operate as a constant output element.

In addition, the third planetary gear set PG3 has a third sun gear S3 directly connected to the first ring gear R1 and is fixedly fixed to the transmission case 1 through a second brake B2. To be combined.

One side of the third planet carrier PC3 of the third planetary gear set PG3 is directly connected to the second ring gear R2 of the second planetary gear set PG2, and is parallel to the transmission case 1. It is connected to the first brake (B1) and the one-way clutch (OWC) consisting of a constant fixing in one direction and a variable fixing element for the other direction.

In addition, the third planet carrier PG3 is connected to the other side of the first planet carrier PCG of the first planetary gear set PG1 through the second clutch C2.

The third ring gear R3 of the third planetary gear set PG3 is directly connected to the other side of the second planetary carrier PC2 of the second planetary gear set PG2.

According to the above configuration, the first and second clutches C1 and C2 are positioned together with the output gear OUT between the first planetary gear set PG1 and the second planetary gear set PG2 in the transmission housing 1. do.

In the configuration of the six-speed power train, the first planetary gear set PG1 transfers the power of the input shaft to the second planetary gear set PG2 and the third planetary gear set PG3 through six input paths. Done.

That is, the first input path is operated by only the first clutch C1 for variably connecting the first planet carrier PC1 to the second sun gear S2 at the first speed and the second speed. The power of the input shaft 3 is input at the same speed ratio to the second sun gear S2 through the carrier PC1.

The second input path includes a second clutch C2 for variably connecting the first planetary carrier PC1 to the third planetary carrier PC3 and a first sun gear S1 at a third speed. If the third brake (B3) variablely connected to the) is operated at the same time, the first sun gear (S1) acts as a fixed element to the third sun gear (S3) of the input shaft (1) through the first ring gear (R1) The power is input at a speed ratio, and at the same time, the power of the input shaft 1 is input at the same speed ratio to the third planet carrier PC3 through the first planet carrier PC1.

The third input path includes a first clutch C1 for variably connecting the first planet carrier PC1 to the second sun gear S2 and a first planet carrier PC1 at the fourth speed. The second clutch C2, which is variably connected to the carrier PC3, is operated at the same time so that the second sun gear S2, the third planet carrier PC3, and the second ring gear through the first planet carrier PC1 are operated. At the same time, the power of the input shaft 3 is input at the same speed ratio to R2).

The fourth input path includes a first clutch C1 for variably connecting the first planetary carrier PC1 to the second sun gear S2 and a first sun gear S1 at a fifth speed. The third brake (B3) that is variablely connected to the same time acts as the first sun gear (S1) acts as a fixed element and the first sun gear (S3) of the input shaft (3) through the first ring gear (R1) The power is input at a speed ratio, and at the same time, the power of the input shaft 3 is input at a speed ratio to the third planet carrier PC3 through the first planet carrier PC1.

In the fifth input path, the first sun gear S1 is operated by only the second clutch C2 that variably connects the first planet carrier PC1 to the third planet carrier PC3 at a sixth speed. It operates as a fixed element and inputs the power of the input shaft 3 to the third planet carrier PC3 and the second ring gear R2 at the same speed ratio through the first planet carrier PC1.

In addition, the sixth input path operates the first sun gear S1 as a fixed element by an operation of only the third brake B3 that variably connects the first sun gear S1 to the transmission case 1 at the reverse stage. By inputting the power of the input shaft (3) to the third sun gear (S3) via the first ring gear (R1) as a speed ratio.

As for each brake and each clutch which are the operating elements of the power train comprised as mentioned above, as shown in the operating element table of FIG. 2, the 1st clutch C1 and the one-way clutch OWC are operated-controlled at the 1st speed | speed_speed, In the second speed, the second brake B2 is operated and controlled in the state of the first speed, and in the third speed, the second brake B2 and the first clutch C1 are released in the state of the second speed and the third brake (B1) is released. B3) and the second clutch C2 are controlled to operate.

At the fourth speed, the first clutch C1 is operated and controlled while the third brake B3 is released, and at the fifth speed, the second clutch C2 is released at the fourth speed. The third brake B3 is operated and controlled, and in the sixth speed, the first clutch C1 and the third brake B3 are released in the state of the fifth speed, and the second clutch C2 and the second brake ( B2) is activated.

In addition, the third brake B3 and the first brake B1 operate at the reverse speed stage.

A power train having such a configuration and a table of operating elements combines three single pinion planetary gear sets (SPGs), but includes a second ring gear (R2), a third planet carrier (PC3), and a third ring gear (R3). The second planet carriers PC2 are fixedly connected to each other, and thus apply to seven nodes NODE as shown in FIG. 3.

That is, the first node (N1) is the first sun gear (S1), the second node (N2) is the first planet carrier (PCG1), the third node (N3) is the first ring gear (R1), the fourth node ( N4 is the third sun gear S3, the fifth node N5 is the third planet carrier PC3, the second ring gear R2, and the sixth node N6 is the third ring gear R3 and the second. The planetary carrier PC2 and the seventh node N7 are set to the second sun gear S2.

3 is a diagram illustrating a shift process of the power train of the present invention. As shown in the first forward speed, the first clutch C1 and the one-way clutch OWC operate.

Then, while the input is made through the second node N2 which is the first planetary carrier PC1, the input is made to the seventh node N7 which is the second sun gear S2 at the same speed ratio directly from the second node N2. The fifth node N5 operates as a fixed element, and the first speed line L1 of FIG. 3 and the first speed line L1 of FIG. 3 are complemented by the first, second and third planetary gear sets PG1, PG2, and PG3. The same speed line is formed, and the output is made as much as D1 through the sixth node N6, which is an output element, and the speed change of the forward 1 speed is made.

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

Then, while the input is made through the second node N2 which is the first planetary carrier PC1, the input is made to the seventh node N7 which is the second sun gear S2 at the same speed ratio directly from the second node N2. The fourth node N4 operates as a fixed element, and the second speed line L2 of FIG. 3 is complemented by the first, second and third planetary gear sets PG1, PG2, and PG3. The same speed line is formed, and the output is made as much as D2 through the sixth node N6, which is an output element, and the second forward speed is made.

At the third forward speed, the operation of the first clutch C1 and the second brake B2 is released in the state of the second speed, and the second clutch C2 and the third brake B3 are operated and controlled.

Then, in a state where an input is made through the second node N2 which is the first planetary carrier PC1, the first node N1, which is the first sun gear S1, operates as a fixed element, and the first ring gear R1. The increase ratio is input to the fourth node N4, which is the third sun gear S3, through the third node N3.

The seventh node N7, which is the second sun gear S2, is directly input from the second node N2 at the same speed ratio.

Accordingly, the first, second, and third planetary gear sets PG1, PG2, and PG3 may complement each other to form a speed line as shown in the third speed line L3 of FIG. 3. As the output is made as D3 through the sixth node N6, the third speed is shifted.

At the fourth forward speed, the operation of the third brake B3 is released in the state of the third speed, and the first clutch C1 is operated and controlled.

Then, in the state where the input is made through the second node N2 which is the first planetary carrier PC1, the seventh node N7 which is the second sun gear S2 is directly input from the second node N2 at the same speed ratio. At the same time, the second ring gear R2 and the third planet carrier PC3 are connected to the fifth node N5.

The power of the input shaft 3 is input at the same speed ratio from the second node N2 which is the first planetary carrier PC1.

At this time, the first, second and third planetary gear sets PG1, PG2 and PG3 are rotated integrally in a directly connected state to form a speed line as shown in the fourth speed line L4 of FIG. As the output is made as much as D4 through the sixth node N6, which is an output element, the fourth speed is shifted.

At the fifth forward speed, the second clutch C2 is released from the fourth speed state, and the third brake B3 is controlled to operate.

Then, in a state where an input is made through the second node N2 which is the first planetary carrier PC1, the first node N1, which is the first sun gear S1, operates as a fixed element, and the first ring gear R1. The increase ratio is input to the fourth node N4, which is the third sun gear S3, through the third node N3.

In addition, the seventh node N7, which is the second sun gear S2, is directly input from the second node N2 at the same speed ratio, and the seventh node N7 acts as a driving element that is actually driven, and FIG. The same speed line as that of the fifth speed line L5 is formed, and the output is made as much as D5 through the sixth node N6, which is an output element, and thus the fifth speed is shifted.

At the sixth forward speed, the first clutch C1 and the third brake B3 are released from the fifth speed state, and the second clutch C2 and the second brake B2 are operated and controlled.

Then, while the input is made through the second node N2 which is the first planetary carrier PC1, the second ring gear R2 and the fifth node N5 which is the third planetary carrier PC3 are formed in the fifth node N5. The power of the input shaft 3 is input at the same speed ratio from the second node N2 which is the one planet carrier PC1.

At this time, the fourth node (N4) of the third sun gear (S3) acts as a fixed element to the complementary operation of the first, second, third planetary gear set (PG1) (PG2) (PG3) of FIG. The same speed line as the fourth speed line L6 is formed, and the output is made as much as D5 through the sixth node N6, which is an output element, and the sixth speed is shifted.

In the first speed reverse, the third brake B3 and the first brake B1 are operated and controlled.

Then, while the third sun gear S3 is directly connected to the first ring gear R1, the fifth node N5 is operated as a fixed element in a state in which a speed ratio is input to the fourth node N4.

Accordingly, the second and third planetary gear sets PG2 and PG3 may complement each other to form a speed line, such as the backward line LR of FIG. 3, and form the sixth node N6 as an output element. The output is as much as R through the speed of reverse 1 is achieved.

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

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

As described above, the power train of the present invention, by applying three single pinion planetary gear sets advantageous in terms of volume and weight, so that the power transmission efficiency by including two direct pins operating directly connected to each other. Has the effect of improving.

In addition, the fifth speed, which is part of the high speed stage, transmits the power of the input shaft at an increase ratio, thereby maximizing the power transmission efficiency.

Claims (11)

In the six-speed power train of the automatic transmission for a vehicle made by combining three planetary gear sets, The first planetary gear set is a single-pinion planetary gear set (SPG), the sun gear of the first planetary gear set is variably connected to the transmission case via a brake, and one planetary carrier of the first planetary gear set is directly connected to the input shaft. The second planetary gear set is a single pinion planetary gear set (SPG), and the sun gear of the second planetary gear set is variably connected to the other planet carrier of the first planetary gear set through a mutual clutch, and the second planetary gear set One side of the planetary carrier is composed of output elements, The third planetary gear set is a single-pinion planetary gear set (SPG), the sun gear of the third planetary gear set is directly connected to the ring gear of the first planetary gear set, and is variably connected to the transmission case via a brake. One planetary carrier of the three planetary gear sets is directly connected to the ring gear of the second planetary gear set, and is connected to a brake and a one-way clutch configured in parallel to the transmission case, and the other planetary carrier of the third planetary gear set is An actuating element that is variably connected to the other planetary carrier of the first planetary gearset through a clutch, and the ring gear of the third planetary gearset is directly connected to the other planetary carrier of the second planetary gearset and constitutes the clutch and the brake. The six-speed power train of the automatic transmission for a vehicle, characterized in that it is combined to implement a shift stage of six forward speed and one reverse speed by the operation control of. The sixth speed power of the automatic transmission for a vehicle according to claim 1, wherein the first planetary gear set transmits power of an input shaft to the second planetary gear set and the third planetary gear set through six input paths. Train. The method of claim 2, wherein the input path A first input path for inputting power of an input shaft to the sun gear of the second planetary gearset at a speed ratio through the planetary carrier of the first planetary gearset; The sun gear of the first planetary gear set acts as a fixed element to input the power of the input shaft to the sun gear of the third planetary gear set at a speed increase ratio through the ring gear of the first planetary gear set, and at the same time A second input path for inputting power of an input shaft to the planetary carrier of the third planetary gear set through a planet carrier at a speed ratio; A third input path for simultaneously inputting power of an input shaft to the planetary carrier of the second planetary gearset and the planetary carrier of the third planetary gearset through the planetary carrier of the first planetary gearset at the same speed ratio; The sun gear of the first planetary gear set operates as a fixed element to input the power of the input shaft to the sun gear of the third planetary gear set at a speed increase ratio through the ring gear of the first planetary gear set, and the planetary of the first planetary gear set. A fourth input path through which a power of an input shaft is input at a speed ratio to the planet carrier of the third planetary gear set through a carrier; A fifth input path for inputting power of an input shaft to a ring gear of the third planetary gearset and the planetary carrier of the third planetary gearset through the planetary carrier of the first planetary gearset at a speed ratio; A sixth input path configured to operate the sun gear of the first planetary gear set as a fixed element to input the power of the input shaft to the sun gear of the third planetary gear set at a speed increase ratio through a ring gear of the first planetary gear set; A six-speed power train of an automatic transmission for a vehicle, characterized in that consisting of. The method of claim 3, wherein the first input path A six-speed power train of an automatic transmission for a vehicle, characterized in that at the first speed and the second speed, the clutch only variably connects the planetary carrier of the first planetary gear set to the sun gear of the second planetary gearset. The method of claim 3, wherein the second input path In a third speed, the clutch for variably connecting the planetary carrier of the first planetary gearset to the planetary carrier of the third planetary gearset and the brake for variably connecting the sun gear of the first planetary gearset to the transmission case are operated at the same time. A six-speed power train of an automatic transmission for a vehicle. The method of claim 3, wherein the third input path In a fourth speed, a clutch for variably connecting the planetary carrier of the first planetary gear set to the sun gear of the second planetary gear set, and the planetary carrier of the first planetary gear set to the planetary carrier of the third planetary gear set A six-speed power train of an automatic transmission for a vehicle, characterized in that the clutch is operated at the same time. The method of claim 3, wherein the fourth input path In a fifth speed, the clutch for variably connecting the planet carrier of the first planetary gear set to the sun gear of the second planetary gear set and the brake for variably connecting the sun gear of the first planetary gear set to the transmission case are operated at the same time. A six-speed power train of an automatic transmission for a vehicle. The method of claim 3, wherein the fifth input path At sixth speed, the six-speed power train of the automatic transmission for a vehicle, characterized by the operation of the clutch variably connecting the planetary carrier of the first planetary gearset to the planetary carrier of the third planetary gearset. The method of claim 3, wherein the sixth input path In the reverse stage, the six-speed power train of the automatic transmission for a vehicle, characterized in that made by the operation of the brake variably connects the sun gear of the first planetary gear set to the transmission case. The brake and the clutch of claim 1, wherein each of the actuating elements A clutch connecting the sun gear of the second planetary gear set and the planet carrier of the first planetary gear set is a first clutch, and the planet carrier of the third planet gear set and the planet carrier of the first planet gear set are connected. A second clutch, a brake for variably connecting the planetary carrier of the third planetary gear set to the transmission case as a first brake, and a brake for fixing the sun gear of the third planetary gearset to the transmission case. 2 brakes, and a brake for variably connecting the sun gear of the first planetary gear set to the transmission case as a third brake, In the first speed, the first clutch and the one-way clutch are operated and controlled, and in the second speed, the second brake is operated in the state of the first speed, and in the third speed, the second brake and the first are operated. The third brake and the second clutch are operated and controlled as the clutch is released, and in the fourth speed, the first clutch is operated and controlled as the third brake is released, and at the fifth speed, the fourth clutch is operated and controlled. The third brake is operated and controlled as the second clutch is released from the second clutch. In the sixth speed, the second clutch and the second brake are operated while the first clutch and the third brake are released in the state of the fifth speed. A six-speed power train of an automatic transmission for a vehicle, characterized in that the first brake and the third brake are operated to shift. The method of claim 1, wherein the arrangement of the first, second, third planetary gear set The first planetary gear set PG1 is disposed at the front side of the transmission, and the third planetary gear set PG3 is disposed at the rear side of the transmission, and the second planetary gear set PG2 is disposed therebetween. Six-speed power train with automatic transmission.

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