JP2008075748A - Rolling bearing unit for wheel support - Google Patents

Abstract

In a rolling bearing unit 1a for wheel support in which a pitch circle diameter of balls 4a in an outer row is larger than a pitch circle diameter of balls 4b in an inner row, grease existing in the ball 4b portion in the inner row flows outward in the axial direction. To achieve a structure that is easy to secure and durable.
A slinger 19 is provided between balls 4a and 4b arranged in a double row so that grease existing in the ball 4b portion in the inner row flows outward in the axial direction toward the ball 4a portion in the outer row. To prevent. And it prevents that the grease which exists in the ball | bowl 4b part of this inner side line runs short, and solves the said subject.
[Selection] Figure 1

Description

  The present invention relates to an improvement of a rolling bearing unit for supporting a wheel for rotatably supporting a rotating member for braking such as a wheel and a brake disk of an automobile with respect to a suspension device. In particular, the present invention provides a wheel bearing rolling bearing unit in which the pitch circle diameters of the rolling elements arranged in double rows are different from each other, and realizes a structure that can smoothly lubricate the rolling element portions in the inner row with a small pitch circle diameter. Is intended.

  The wheel of the automobile and the rotating member for braking are rotatably supported with respect to the suspension device by the wheel bearing rolling bearing unit. A large moment is applied to such a wheel-supporting rolling bearing unit when the automobile is turning. Therefore, in order to ensure stability during turning, it is necessary to ensure a large moment rigidity. Therefore, conventionally, as a rolling bearing unit for supporting a wheel, a structure in which rolling elements are arranged in a double row, and a preload and a back combination type (DB type) contact angle are given to the rolling elements in both rows is generally used. Has been used. Furthermore, in recent years, in order to ensure a larger moment rigidity while preventing an increase in size, for example, as described in Patent Documents 1 to 5, the pitch circle diameters and the rolling element diameters of both rolling elements are made different. A proposed structure has been proposed.

  FIG. 6 shows the structure described in Patent Document 4 among them. The wheel support rolling bearing unit 1 includes a hub 2, an outer ring 3, and a plurality of balls 4, 4 each of which is a rolling element. Of these, the hub 2 is formed by combining a hub body 5 and an inner ring 6. Further, the hub 2 is an outer end in the axial direction of the outer peripheral surface (outside with respect to the axial direction means the outer side in the width direction of the vehicle when assembled to the automobile, and the left side of each figure. The right side of each figure is said to be inward with respect to the axial direction.This is the same throughout the present specification and claims.) The mounting flange 7 for supporting the wheel and the rotating member for braking is also placed in the middle. Double row inner ring raceways 8a and 8b are formed on the inner and inner end portions, respectively. Of these inner ring raceways 8a and 8b, the diameter of the inner ring raceway 8a in the axially outer row is larger than the diameter of the inner ring raceway 8b in the inner row. A base end portion of a plurality of studs 9 is fixed to the mounting flange 7 so that a braking rotator such as a disk or a wheel constituting a wheel can be supported and fixed to the mounting flange 7. .

  In order to make the diameters of the inner ring raceways 8a and 8b different from each other, in the structure shown in FIG. 6, the axially intermediate outer peripheral surface of the hub body 5 is slightly closer to the inner side in the axial direction than the inner ring raceway 8a in the outer row. An outer peripheral surface side inclined step portion 10 that is inclined in a direction in which the outer diameter decreases toward the inner side in the axial direction is formed in the portion. Further, a small-diameter step portion 11 is formed at the inner end portion in the axial direction of the hub body 5 which is closer to the inner side in the axial direction than the inclined step portion 10 on the outer peripheral surface side. Then, the inner ring 6 having the inner ring raceway 8b in the axially inner row formed on the outer peripheral surface is externally fitted to the small-diameter stepped part 11, and the caulking part 12 formed on the inner end in the axial direction of the hub body 5 is used. The inner ring 6 is pressed against the stepped surface 13 existing at the outer end in the axial direction of the small-diameter stepped portion 11. In this state, the inner ring 6 is coupled and fixed to the hub body 5. The inner ring raceways 8a and 8b have a circular cross-sectional shape (bus shape), and the outer diameter decreases as they approach each other (as they approach the center in the axial direction of the hub 2).

  The outer ring 3 is provided with double-row outer ring raceways 14a and 14b on the inner peripheral surface and a coupling flange 15 on the outer peripheral surface for coupling and fixing the outer ring 3 to a suspension device. Of the two outer ring raceways 14a and 14b, the diameter of the outer ring raceway 14a on the outer side in the axial direction is larger than the diameter of the outer ring raceway 14b on the inner side. For this reason, in the structure shown in FIG. 6, the inner diameter decreases toward the inner side in the axial direction at a portion closer to the inner side in the axial direction than the outer outer ring raceway 14 a on the inner circumferential surface in the axial direction of the outer ring 3. An inner peripheral surface side inclined step portion 16 that is inclined in the direction is formed. The outer ring raceways 14a and 14b have a circular cross-sectional shape (bus shape), and the inner diameter decreases as they approach each other (as they approach the center in the axial direction of the hub 2).

A plurality of balls 4, 4 are provided between the inner ring raceways 8a, 8b and the outer ring raceways 14a, 14b, respectively, so that they can roll. In this state, each of the balls 4 and 4 arranged in a double row is provided with a back-combined contact angle together with preload. The pitch circle diameters of the balls 4 and 4 in both rows differ from each other in accordance with the difference in diameter between the inner ring raceways 8a and 8b and the outer ring raceways 14a and 14b. That is, the pitch circle diameter PCD _OUT of each ball 4, 4 (outer row) in the axially outer row is larger than the pitch circle diameter PCD _IN of each ball 4, 4 (inner row) in the axially inner row ( PCD _OUT > PCD _IN ).

The structure of the rolling bearing unit for supporting a wheel described in Patent Documents 1 to 5 in which the pitch circle diameters of the rolling elements in both rows are made different is as described above. In the case of such a structure, the moment circle rigidity can be increased as much as the pitch circle diameter PCD _OUT of the outer row can be increased to improve the running stability during turning and the durability of the wheel bearing rolling bearing unit. The design for achieving this becomes easy. On the other hand, since it is not necessary to increase the pitch circle diameter PCD _IN of the inner row, it is not necessary to increase the diameter of a part of the suspension device (knuckle mounting hole). Therefore, the traveling stability and the durability can be improved without particularly increasing the size of the suspension device.

  In the structure shown in FIG. 6 described above, the diameters of the balls 4 and 4 arranged in a double row are made equal. However, like the wheel support rolling bearing unit 1a shown in FIG. A structure in which the diameters of the balls 4a and 4a are smaller than the diameters of the balls 4b and 4b in the inner row is also conventionally known. In the case of the second example of the conventional structure shown in FIG. 7, the number of balls 4a, 4a in the outer row is sufficiently larger than the number of balls 4b, 4b in the inner row, The degree to which the rigidity is higher than the rigidity of the inner row is made more prominent. Furthermore, in each example shown in the figure, balls 4, 4a, and 4b are used as rolling elements. However, in the case of a rolling bearing unit for an automobile that is heavy in weight, a tapered roller may be used as the rolling element.

In the case of the wheel bearing rolling bearing units 1 and 1a as described above, grease is sealed in the internal space 17 in which the balls 4, 4a and 4b are installed, and the rolling surfaces of the balls 4, 4a and 4b are The rolling contact portions between the inner ring raceways 8a and 8b and the outer ring raceways 14a and 14b are lubricated. By the way, in the case of the wheel support rolling bearing units 1 and 1a in which the pitch circle diameter PCD _OUT of the outer row is larger than the pitch circle diameter PCD _IN of the inner row, the diameter of the inner space 17 is smaller on the inner side in the axial direction. It becomes larger outside in the axial direction. For this reason, as the hub 2 rotates, the grease enclosed in the internal space 17 rotates along with the balls 4, 4a, 4b, and when the centrifugal force is applied to the grease, the grease is It flows outward in the axial direction in the internal space 17. As a result, the grease in the axially inner portion of the internal space 17 is reduced, the lubricity of the balls 4, 4b in the inner row is deteriorated, and the durability of the wheel bearing rolling bearing units 1, 1a is improved. It can be damaged.

  On the other hand, as a result of excessive grease collecting in the outer portion of the internal space 17, the grease stirring resistance by the balls 4, 4a in the outer row increases, and the rotational resistance of the wheel bearing rolling bearing units 1, 1a increases. (Dynamic torque) increases. This increase in rotational resistance is not preferable because it causes a reduction in the power performance of the automobile, including fuel efficiency performance and acceleration performance. Further, the grease concentrated on the outer portion of the internal space 17 tends to leak to the outside by pushing away the seal lip of the seal ring 18 closing the outer end portion of the internal space 17. As a result, there is a possibility that the absolute amount of grease existing in the internal space 17 is insufficient and the durability is more deteriorated.

JP 2003-232343 A JP 2004-108449 A JP 2004-345439 A JP 2006-137365 A International Publication WO2005 / 065077

  In view of the circumstances as described above, the present invention is a wheel bearing rolling bearing unit in which the pitch circle diameter of the rolling elements in the outer row is larger than the pitch circle diameter of the rolling elements in the inner row, and is present in the rolling element portion of the inner row. This invention was invented to realize a structure in which the grease to be flowed hardly flows outward in the axial direction toward the rolling element portions of the outer row.

The wheel-supporting rolling bearing unit of the present invention includes an outer ring, a hub, and a plurality of rolling elements, like the conventionally-known wheel-supporting rolling bearing unit.
Among these, the outer ring has a double row outer ring raceway on the inner peripheral surface.
The hub has a mounting flange for supporting and fixing the wheel at the axially outer end portion of the outer peripheral surface, and double row inner ring raceways at the intermediate and inner end portions in the axial direction.
Each of the rolling elements is provided between each of the inner ring raceways and the both outer ring raceways in a state where a plurality of, preferably a rear combination type contact angle is provided for each row.
The pitch circle diameter of the outer row in the axial direction is made larger than the pitch circle diameter of the inner row in the axial direction.

In particular, in the rolling bearing unit for wheel support of the present invention, the grease existing in the rolling element portion in the inner row is directed toward the rolling element portion in the outer row between the rolling elements arranged in the double row. A slinger is provided to suppress movement outward in the axial direction.
When implementing such a wheel-supporting rolling bearing unit of the present invention, for example, as described in claim 2, the outer peripheral edge of the slinger is placed between the outer ring raceways of the double row on the inner peripheral surface of the intermediate part of the outer ring. Support and fix to the part. Then, the inner peripheral edge of the slinger is closely opposed to the portion between the double-row inner ring raceways on the outer peripheral surface of the intermediate portion of the hub over the entire periphery.
Alternatively, as described in claim 3, the inner peripheral edge of the slinger is supported and fixed to a portion between the inner ring tracks of the double row on the outer peripheral surface of the intermediate portion of the hub. Then, the outer peripheral edge of the slinger is brought close to and opposed to the portion between the double row outer ring raceways on the inner peripheral surface of the outer ring over the entire circumference. In this case, it is preferable that a portion near the outer diameter of the slinger is bent or bent inward in the axial direction so that the outer peripheral edge of the slinger is positioned inward in the axial direction from the inner peripheral edge.

  In the case of the rolling bearing unit for supporting a wheel according to the present invention having the above-described configuration, the slinger provided between the rolling elements in both the outer and inner rows is arranged so that the grease existing in the rolling elements in the inner row is outside. Suppresses the flow outward in the axial direction toward the rolling elements of the row. That is, the grease sealed in the internal space in which the rolling elements are installed is rotated by the rolling elements, centrifugal force is applied to the grease, and the grease flows outward in the axial direction in the internal space. Even if it becomes a tendency, this grease is blocked by the slinger and remains in the rolling element portion of the inner row. As a result, it is possible to ensure the lubricity of the rolling elements in the inner row and ensure the durability of the wheel bearing rolling bearing unit.

[First example of embodiment]
FIG. 1 shows a first example of an embodiment of the present invention corresponding to claims 1 and 2. The feature of the present invention including this example is a wheel bearing rolling bearing unit in which the pitch circle diameter of the rolling elements in the outer row is larger than the pitch circle diameter of the rolling elements in the inner row. In order to realize a structure in which the existing grease does not easily flow outward in the axial direction toward the rolling element portions in the outer row, a slinger is provided between the rolling members in both rows. Since the configuration and operation of the other parts are the same as those of the conventional structure shown in FIG. 6 or FIG. 7, the same parts are denoted by the same reference numerals, and redundant description is omitted. The explanation will focus on the part.

  In the case of this example, the slinger 19 is fitted and fixed to the portion between the double row outer ring raceways 14a and 14b on the inner peripheral surface of the intermediate part of the outer ring 3. The slinger 19 is formed by bending a metal plate such as a steel plate or a stainless steel plate to form an entire ring shape with an L-shaped cross section. And a cylindrical portion 21 bent at a right angle on one side of the direction. Such a slinger 19 is supported and fixed to the outer ring 3 by fitting the cylindrical part 21 to the inner peripheral surface of the intermediate part of the outer ring 3 with an interference fit. In this state, the inner peripheral edge of the annular ring portion 20 is close to the cylindrical surface portion 22 provided on a portion of the outer peripheral surface of the hub body 5 adjacent to the inner side in the axial direction of the inner ring raceway 8a. Opposite. When assembling the wheel support rolling bearing unit 1a, the slinger 19 is configured so that the outer ring 3 has an inner peripheral surface before the balls 4a and the seal ring 18 are assembled to the outer peripheral portion of the outer ring 3. It is fixed in the middle part. The axial position of the cylindrical portion 21 with respect to the circular ring portion 20 (whether it is bent inward in the axial direction or conversely bent outward) is not particularly limited. Select design in consideration of installation space. Further, the entire slinger can be formed in a slightly thick annular shape (so as to ensure the width of the fitting portion), and the cylindrical portion can be omitted.

  In the case of the wheel bearing rolling bearing unit 1a of the present example having the above-described configuration, the slinger 19 provided between the balls 4a and 4b in both the outer and inner rows is arranged in the ball 4b portion in the inner row. The existing grease is prevented from flowing outward in the axial direction toward the balls 4a in the outer row. That is, during the operation of the wheel bearing rolling bearing unit 1a, the grease sealed in the internal space 17 in which the balls 4a and 4b are installed is moved in the internal space 17 by the revolving motion of the balls 4a and 4b. It rotates (moves in the circumferential direction of the internal space 17). Along with this rotational movement, centrifugal force is applied to the grease, and the grease tends to flow outward in the axial direction in the internal space 17. Even in this case, the grease is blocked by the ring portion 20 of the slinger 19 and remains in the ball 4b portion of the inner row. As a result, the lubricity of the rolling contact portion between the rolling surface of the balls 4b in the inner row and the inner ring raceway 8b and the outer ring raceway 14b can be ensured, and the durability of the wheel support rolling bearing unit 1a can be ensured. The grease collects in a portion closer to the outer diameter of the inner space 17 (the inner peripheral surface portion of the outer ring 3) based on the centrifugal force. The slinger 19 is fitted into the inner peripheral surface of the outer ring 3 by an interference fit. Therefore, the damming effect of the grease can be sufficiently secured.

  In order to secure the amount of grease existing in the ball 4b portion of the inner row even after the operation of the wheel bearing rolling bearing unit 1a is started while suppressing the total amount of grease sealed in the internal space 17. The slinger 19 is preferably disposed close to the balls 4b in the inner row. Considering this point, it is preferable that the slinger 19 is fitted and fixed to the inner peripheral surface of the shoulder portion 23 adjacent to the outer side in the axial direction of the inner outer ring raceway 14b at the intermediate portion of the inner peripheral surface of the outer ring 3. In this case, the inner peripheral edge of the annular ring portion 20 constituting the slinger 19 is made to face the axially inner portion of the intermediate portion outer peripheral surface of the hub body 5 closer to the axially inner side portion than the outer peripheral surface side inclined step portion 10. Even in such a structure (because the work of connecting and fixing the hub body 5 and the inner ring 6 by the caulking portion 12 is performed after the constituent members are combined in the state shown in FIG. 1), the structure shown in FIG. Similarly, assembly of a wheel bearing rolling bearing unit is possible. Of course, the diameter of the slinger 19 to be used is made smaller than in the case of the structure shown in FIG.

[Second Example of Embodiment]
FIG. 2 also shows a second example of an embodiment of the present invention corresponding to claims 1 and 2. In the case of this example, there is almost no cylindrical surface portion 22 (see FIG. 1) as in the first example of the above-described embodiment on the outer peripheral surface of the intermediate portion of the hub body 5. In other words, the outer diameter of the portion located on the inner diameter side of the slinger 19a described below at the intermediate portion of the hub body 5 is smaller than that in the case of the first example described above. In accordance with this, in the case of this example, the inner diameter of the annular portion 20a constituting the slinger 19a is decreased (the width dimension in the radial direction is increased), and the inner peripheral edge of the annular portion 20a is It is made to face and oppose the intermediate part outer peripheral surface. Since the configuration and operation of the other parts are the same as in the first example of the above-described embodiment, the same parts are denoted by the same reference numerals, and redundant description is omitted.

[Third example of embodiment]
FIG. 3 also shows a third example of an embodiment of the present invention corresponding to claims 1 and 2. In the case of this example, a bank-like projecting portion 24 projecting radially inward is provided over the entire circumference on the outer half portion in the axial direction of the shoulder portion 23 provided on the inner peripheral surface of the intermediate portion of the outer ring 3. ing. An inner diameter R ₂₄ of the protrusion ₂₄ is smaller than an outer diameter D ₆ of the inner end of the inner ring 6 constituting the hub 2 (R ₂₄ <D ₆ ). Then, the cylindrical portion 21a constituting the slinger 19b is fitted and fixed to the bank-like projecting portion 24 by an interference fit, and the inner periphery of the annular portion 20b constituting the slinger 19b constitutes the hub 2. The hub body 5 is made to face and face the outer peripheral surface of the intermediate part over the entire circumference.

  In the case of such a structure of this example, the slinger 19b prevents the grease existing in the inner row of balls 4b from moving outward in the axial direction, and also when the inner row of balls 4b is worn out. The hub 2 can be prevented from coming out from the inner diameter side of the outer ring 3. Since the function of preventing the movement of grease is the same as in the first and second examples described above, the function of preventing the hub 2 from slipping out will be described below.

  Although it is hardly conceivable in a general use state, the diameter of the balls 4b in the inner row becomes small due to wear if used for a long time in a poorly lubricated state. Further, when the cage 25 holding the balls 4b in the inner row is broken, the balls 4b in the inner row may be concentrated on a part in the circumferential direction. When such a state is overlapped and the hub 2 and the outer ring 3 are eccentric in the direction in which the radial thickness of the inner space increases at the portion where the balls 4b are located, the presence of the balls 4b is caused. Regardless, the hub 2 may come out from the inner diameter side of the outer ring 3. There is almost no possibility of such a breakout unless the vehicle is operated in an insane and violent manner, but it is preferable to consider measures. Further, the possibility of the above-mentioned pull-out is not completely impossible even in the case of a general wheel support rolling bearing unit in which the pitch circle diameters are equal to each other in the outer row and the inner row. In such a structure, the pitch circle diameter of the rolling elements in the outer row is larger than the pitch circle diameter of the rolling elements in the inner row, and this is likely to occur (from the possibility of poor lubrication of the balls 4b in the inner row). It is considered a thing.

In view of such circumstances, in the case of this example, the inner diameter R ₂₄ of the protrusion 24 is smaller than the outer diameter D ₆ of the inner end of the inner ring 6 constituting the hub 2 (R ₂₄ <D ₆ ). Thus, the hub 2 is prevented from coming out from the inner diameter side of the outer ring 3 even when the balls 4b in the inner row are worn. Since other configurations and operations are the same as those in the first and second examples of the above-described embodiment, the same parts are denoted by the same reference numerals, and redundant description is omitted.

[Fourth Example of Embodiment]
FIG. 4 shows a fourth example of an embodiment of the present invention corresponding to claims 1 and 3. As described above, the slinger is preferably fitted and fixed to the inner peripheral surface of the outer ring. However, when the inner ring surface of the outer ring 3 cannot be fitted and fixed due to the installation space or the like, the cylindrical portion 21b provided on the inner peripheral edge portion of the slinger 19c is connected to the outer peripheral portion of the hub body 5 as in this example. It can also be externally fixed to the surface. In this case, the outer peripheral edge of the ring portion 20c constituting the slinger 19c is made to face and oppose the inner peripheral surface of the shoulder portion 23 provided on the inner peripheral surface of the intermediate portion of the outer ring 3 over the entire periphery. However, the outer diameter D ₂₀ of the ring portion 20c is set to be equal to or smaller than the diameter D ₄ of the inscribed circle of the outer row of balls 4c (D ₂₀ ≦ D ₄ ), and the slinger 19c is attached to the outer row of the outer row during assembly work. The inner diameter side of the ball 4c is allowed to pass. Since the configuration and operation of the other parts are the same as those in the first and second examples of the above-described embodiment, the same parts are denoted by the same reference numerals, and redundant description is omitted.

[Fifth Example of Embodiment]
FIG. 5 also shows a fifth example of an embodiment of the present invention corresponding to claims 1 and 3. In the case of this example, a portion closer to the outer diameter of the annular portion 20d constituting the slinger 19d is bent inward in the axial direction, and the outer peripheral edge of the slinger 19d is positioned inward in the axial direction from the inner peripheral edge. I am letting. The outer peripheral edge portion of the annular portion 20d is made to face and face the outer ring raceway 14b in the inner row. According to such a structure of this example, the grease that has been moved radially outward based on the centrifugal force while being guided by the axial inner surface of the annular portion 20d can be efficiently applied to the outer ring raceway 14b in the inner row. Returned, the lubricity of the rolling contact portion between the rolling surface of the balls 4b in the inner row and the inner ring raceway 8b and the outer ring raceway 14b is ensured. Since the configuration and operation of the other parts are the same as those in the fourth example of the above-described embodiment, the same parts are denoted by the same reference numerals, and redundant description is omitted.
In addition, although illustration is abbreviate | omitted, the slinger installed between the rolling element of an outer side row | line | column and the rolling element of an inner side row | line | column is not restricted to one, and it shall be two or more (the slinger of each example shown in FIGS. 1-4). Can be combined as appropriate).

FIG. 2 is a half sectional view showing a first example of an embodiment of the present invention. Sectional sectional drawing which shows the 2nd example. Sectional sectional drawing which shows the 3rd example. Sectional sectional drawing which shows the 4th example. Half sectional view showing the fifth example. Sectional drawing which shows the 1st example of a conventional structure. Sectional drawing which shows the 2nd example.

DESCRIPTION OF SYMBOLS 1, 1a Rolling bearing unit for wheel support 2 Hub 3 Outer ring 4, 4a, 4b, 4c Ball 5 Hub main body 6 Inner ring 7 Mounting flange 8a, 8b Inner ring raceway 9 Stud 10 Outer peripheral surface side inclined step part 11 Small diameter step part 12 Caulking part 13 Stepped surfaces 14a, 14b Outer ring raceway 15 Coupling flange 16 Inner peripheral surface side inclined stepped portion 17 Internal space 18 Seal ring 19, 19a, 19b, 19c, 19d Slinger 20, 20a, 20b, 20c, 20d Circular ring portion 21, 21a , 21b Cylindrical part 22 Cylindrical surface part 23 Shoulder part 24 Projection part 25 Cage 26 Bending part

Claims (3)

  An outer ring having a double row outer ring raceway on the inner peripheral surface, a mounting flange for supporting and fixing the wheel on the outer axial end portion of the outer peripheral surface, and a double row inner ring raceway in the middle and inner end portions in the same axial direction. And a plurality of rolling elements provided for each row between the inner ring raceways and the outer ring raceways, and the pitch circle diameter of the outer row in the axial direction is set on the inner side in the axial direction. In the rolling bearing unit for supporting a wheel larger than the pitch circle diameter of the row, the grease existing in the rolling element portion in the inner row is between the rolling elements arranged in the double row in the rolling element portion in the outer row. Rolling bearing unit for wheel support, characterized by the provision of a slinger to prevent it from moving outward in the axial direction.   The outer peripheral edge of the slinger is supported and fixed to the portion between the double row outer ring raceways at the inner peripheral surface of the outer ring, and the inner periphery of the slinger is attached to the portion between the inner ring raceways of the double row at the intermediate outer peripheral surface of the hub. The rolling bearing unit for supporting a wheel according to claim 1, wherein the rolling bearing unit is opposed to the entire circumference. The inner peripheral edge of the slinger is supported and fixed to the portion between the double row inner ring raceways at the outer peripheral surface of the hub, and the outer peripheral edge of the slinger is attached to the portion between the double row outer ring raceways at the inner peripheral surface of the outer ring. The rolling bearing unit for supporting a wheel according to claim 1, wherein the rolling bearing unit is opposed to the entire circumference.

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