JP2016205435A - Double-row ball bearing and shaft support device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make foreign matters contained in a lubricant hardly enter a clearance between balls and a raceway groove while suppressing a cost increase, and to elongate a life of a bearing, in the double-row ball bearing.SOLUTION: A double-row ball bearing comprises: an outer ring 16; an inner ring 15; a plurality of first balls 11 which are arranged at one side in an axial direction, and constitute a first row; a plurality of second balls 12 which are arranged at the other side in the axial direction, and constitute a second row which is smaller than the first row in a pitch circle diameter; an annular first cage 21 having a plurality of pockets 23 for holding the first balls 11; an annular second cage 22 having a plurality of pockets 24 for holding the second balls 12; and an annular flange part 30 which is arranged at a large-diameter shoulder part 20 of one side of the inner ring 15 in the axial direction, and prevents the intrusion of a lubricant containing foreign matters into a clearance between the first cage 21 and the inner ring 15 from the outside of the bearing.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a double row ball bearing. For example, the present invention relates to a double row ball bearing used as a shaft support bearing for a differential gear device or a transaxle device mounted on an automobile or the like. The present invention also relates to a shaft support device including a double row ball bearing.

  As a rolling bearing for supporting the pinion shaft of a differential gear device, a tapered roller bearing having a high load capacity and a high rigidity has been conventionally used. However, in recent years, for the purpose of reducing torque (reducing loss). Double row ball bearings are employed (see, for example, Patent Document 1 and Patent Document 2).

  FIG. 4 is an explanatory view showing a part of the differential gear device in section. The differential gear device includes a case 80, a differential mechanism 81 provided in the case 80 and having a ring gear 82 and a pinion gear 83, a pinion shaft 84 that rotates integrally with the pinion gear 83, and the pinion shaft 84 rotatably supported. A double row ball bearing 90 is provided.

  The double row ball bearing 90 is provided between the outer ring 91, the inner ring 92, the outer ring 91 and the inner ring 92, and a plurality of first balls 93 constituting the first row and a plurality of rows constituting the second row. The second ball 94 is provided. The first ball 93 and the second ball 94 are in angular contact with the raceway grooves of the outer ring 91 and the inner ring 92, and the pitch circle diameter of the first row by the first ball 93 is due to the second ball 94. It is larger than the pitch circle diameter of the second row. And the cyclic | annular 1st holder | retainer 95 hold | maintains the some 1st ball | bowl 93 at equal intervals along the circumferential direction, and the cyclic | annular 2nd holder | retainer 96 holds the some 2nd ball | bowl 94 in the circumferential direction. It is kept at regular intervals along.

  The double row ball bearing 90 is installed in the vicinity of the pinion gear 83 and supports the pinion shaft 84. Further, the ring gear 82 and the pinion gear 83 are lubricated by the lubricating oil (oil) P 1 stored in the case 80, and the lubricating oil P 1 is also used for lubricating the double row ball bearing 90. In addition, the virtual line L1 of FIG. 4 has shown the oil level of the lubricating oil P1.

JP 2006-234100 A JP 2004-2111861 A

  In the differential gear device shown in FIG. 4, the lubricating oil P <b> 1 stored in the case 80 is treated with the processing waste generated during the manufacture of the case 80, the ring gear 82, and the pinion gear 83, and the gear 82 during the operation of the differential mechanism 81. , 83 may contain foreign matter such as wear debris.

  The differential gear device is configured such that the lubricating oil P1 in the case 80 is scraped up by the rotating ring gear 82. The scraped lubricating oil P1 is the large diameter of the inner ring 92 of the double row ball bearing 90. It falls on the side portion (see arrow X1 in FIG. 4). In this case, the foreign matter contained in the lubricating oil P1 may be caught between the raceway groove of the inner ring 92 and the first ball 93 located on the large diameter side. The bearing groove will be peeled off and the bearing life will be reduced.

  In Patent Document 2, seal members are provided on both sides in the axial direction of the annular space formed between the inner ring and the outer ring, and it is possible to prevent the lubricating oil containing foreign matter from entering the bearing. It has become. Each seal member includes an elastic body such as an annular metal core and rubber, and two such seal members are additionally required, leading to an increase in the cost of the bearing.

  Accordingly, an object of the present invention is to increase the bearing life in a double row ball bearing, while suppressing an increase in cost and making it difficult for foreign matter contained in the lubricating oil to enter between the ball and the raceway groove.

  The double-row ball bearing of the present invention includes an outer ring, an inner ring, a plurality of first balls that are provided on one side in the axial direction between the outer ring and the inner ring and that constitute a first row, and the outer ring. A plurality of second balls that are provided on the other side in the axial direction between the inner ring and the inner ring and that constitute a second row having a pitch circle diameter smaller than that of the first row, and hold the first ball A ring-shaped first cage having a plurality of pockets, a ring-shaped second cage having a plurality of pockets for holding the second ball, and a bearing provided on a large-diameter shoulder on one axial side of the inner ring And an annular flange that prevents the lubricating oil containing foreign matter from entering between the first retainer and the inner ring.

  According to the present invention, for example, even if the lubricating oil falls from a gear (outside of the bearing) that exists in the vicinity of one side in the axial direction of the double row ball bearing toward the double row ball bearing, It can be blocked by an annular collar. For this reason, it is difficult for foreign matter contained in the lubricating oil to enter particularly between the raceway groove of the inner ring and the first ball, and as a result, the bearing life can be extended. And in order to suppress intrusion of foreign matter in this way, it is only necessary to provide an annular flange on one side in the axial direction of the inner ring, so that an increase in the cost of the double row ball bearing can be suppressed.

Further, the first retainer has an annular portion provided on one axial side of the first ball, and a pillar portion extending from the annular portion to the other axial side, Preferably, the flange portion is provided to face the annular portion with a gap in the axial direction, and a labyrinth is formed between the flange portion and the annular portion.
In this case, a labyrinth is formed between the flange portion and the annular portion of the first cage, and it is possible to more effectively suppress the entry of foreign matter (lubricating oil) between the inner ring and the first cage. It becomes possible.

  Moreover, although the said collar part may be formed with an inner ring | wheel and may be integral with an inner ring | wheel, it is preferable that the said collar part consists of a ring member which is a different body from the said inner ring | wheel and is attached to the said inner ring | wheel. By forming them separately, it is easy to form the inner ring and the buttocks.

The shaft support device of the present invention includes a case, a gear mechanism having a large-diameter gear and a small-diameter gear provided in the case, a shaft that integrally rotates with the small-diameter gear, and a shaft that rotatably supports the shaft. The double row ball bearing.
According to the present invention, it is difficult for foreign matter contained in the lubricating oil to enter between the raceway groove of the inner ring and the first ball of the double row ball bearing, and the bearing life can be extended. As a result, the life of the shaft support device can be extended. And in order to suppress intrusion of foreign matters in this way, it is only necessary to provide an annular flange on one side in the axial direction of the inner ring, so that an increase in cost can be suppressed.

According to the double row ball bearing of the present invention, it is difficult for foreign matter contained in the lubricating oil to enter the inside of the bearing, and the bearing life can be extended.
In addition, according to the shaft support device of the present invention, it is possible to extend the life of the shaft support device.

It is sectional drawing of the differential gear apparatus provided with the double row ball bearing. It is sectional drawing of a double row ball bearing. It is explanatory drawing which expands and shows a collar part and its periphery. It is explanatory drawing which shows a part of conventional differential gear apparatus in a cross section.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[About shaft support device]
A shaft support device described below is a differential gear device mounted on an automobile or the like. As shown in FIG. 1, a case 50, a differential mechanism (gear mechanism) 51, a pinion shaft 55, and this pinion shaft. And double-row ball bearings 5 and 7 that rotatably support 55.

The differential mechanism 51 includes a ring gear 52 that is a large-diameter gear and a pinion gear 53 that is a small-diameter gear provided in the case 50. The pinion gear 53 and the pinion shaft 55 are integrally formed, and these rotate integrally.
The pinion gear 53 is provided at one end of the pinion shaft 55 and meshes with the ring gear 52. A flange 54 is attached to the other end of the pinion shaft 55, and a drive shaft (not shown) is connected to the flange 54.

  The case 50 accommodates the differential mechanism 51, the pinion shaft 55, and the double row ball bearings 5 and 7. In the case 50, annular walls 50a and 50b are provided. The outer ring 16 of one double row ball bearing 5 is attached to the inner peripheral surface of the annular wall 50a, and the outer ring 26 of the other double row ball bearing 7 is attached to the inner peripheral surface of the annular wall 50b. A cylindrical spacer 6 is provided between the inner ring 15 of the double row ball bearing 5 on the pinion gear 53 side and the inner ring 25 of the double row ball bearing 7 on the flange 54 side.

  Lubricating oil (oil) P1 is stored in the case 50, and the lubricating oil P1 lubricates the ring gear 52 and the pinion gear 53, and this lubrication is used to lubricate the double row ball bearings 5 and 7. Oil P1 is used. In addition, the virtual line L1 of FIG. 1 has shown the oil level of the lubricating oil P1.

  In this differential gear device, the power of the drive shaft (not shown) is transmitted to the differential mechanism 51 via the pinion shaft 55, and the differential mechanism 51 is driven. A wheel shaft is connected to both sides of the differential mechanism 51 via a joint (not shown), and the differential gear device can appropriately adjust the difference in rotational speed between the wheel shafts.

[About double row ball bearings]
The double row ball bearing 5 on the pinion gear 53 side will be described. FIG. 2 is a cross-sectional view of the double row ball bearing 5. 2 is a cross-sectional view of the lower half of the double row ball bearing 5 shown in FIG. The double row ball bearing 5 includes an outer ring 16, an inner ring 15, a plurality of first balls 11, a plurality of second balls 12, an annular first retainer 21, and an annular second retainer 22. It has. Furthermore, the double row ball bearing 5 includes an annular flange 30. Although the collar part 30 will be described later, the collar part 30 of the present embodiment is attached to the inner ring 15 and is a ring member separate from the inner ring 15.

The outer ring 16 and the inner ring 15 are each made of a cylindrical member, and are arranged concentrically with the balls 11 and 12 interposed therebetween.
A plurality of first balls 11 arranged along the circumferential direction constitute a first row (first rolling element row). Moreover, the 2nd row | line | column (2nd rolling element row | line | column) is comprised by the some 2nd ball | bowl 12 arrange | positioned along the circumferential direction.
In the present embodiment, the first ball 11 and the second ball 12 have the same diameter. The outer ring 16, the inner ring 15, and the balls 11 and 12 are made of bearing steel. The first cage 21 and the second cage 22 are made of synthetic resin. In addition, the material of each part may be other than these.

  A first outer ring raceway groove 35 and a second outer ring raceway groove 36 are formed on the inner peripheral surface of the outer ring 16. The first outer ring raceway groove 35 is larger in diameter than the second outer ring raceway groove 36. A first inner ring raceway groove 38 and a second inner ring raceway groove 39 are formed on the outer peripheral surface of the inner ring 15. The first inner ring raceway groove 38 has a larger diameter than the second inner ring raceway groove 39. The first ball 11 contacts the first outer ring raceway groove 35 and the first inner ring raceway groove 38 with a contact angle, and rolls on these raceway grooves 35 and 38. The second ball 12 contacts the second outer ring raceway groove 36 and the second inner ring raceway groove 39 with a contact angle, and rolls on these raceway grooves 36 and 39. As described above, the pitch circle diameter D1 of the second row constituted by the plurality of first balls 11 is larger than the pitch circle diameter D2 of the second row constituted by the plurality of second balls 12. (D1> D2).

The first retainer 21 has an annular shape as a whole, and has an annular outer ring portion 42 located on one axial side of the first ball 11, and from the outer annular portion 42 toward the other axial side. A plurality of pillar portions 44 that extend and an inner annular portion 43 that is an annular shape located on the other axial side of the first ball 11 are included. The plurality of column portions 44 are provided at equal intervals along the circumferential direction, and connect the outer annular portion 42 and the inner annular portion 43.
The second retainer 22 has an annular shape as a whole, and is an annular outer ring portion 45 positioned on the other axial side of the second ball 12, and from the outer annular portion 45 toward the one axial side. It has a plurality of pillar portions 47 that extend, and an inner annular portion 46 that is an annular shape and is located on one side of the second ball 12 in the axial direction. The plurality of column portions 47 are provided at equal intervals along the circumferential direction, and connect the outer annular portion 45 and the inner annular portion 46.

In the first retainer 21 shown on the left side of FIG. 2, the region surrounded by the outer annular portion 42, the inner annular portion 43, and the column portion 44 adjacent in the circumferential direction becomes a pocket 23 that holds the ball 11. One ball 11 is provided in the pocket 23. A plurality of pockets 23 are formed along the circumferential direction, whereby the first cage 21 can hold the plurality of first balls 11 at regular intervals along the circumferential direction.
In the second cage 22 shown on the right side of FIG. 2, the region surrounded by the outer annular portion 45 and the inner annular portion 46 and the column portion 47 adjacent in the circumferential direction becomes the pocket 24 that holds the ball 12, One ball 12 is provided in the pocket 24. A plurality of pockets 24 are formed along the circumferential direction, whereby the second cage 22 can hold the plurality of second balls 12 at regular intervals along the circumferential direction.

  As described above, the plurality of first balls 11 constituting the first row are provided between the outer ring 16 and the inner ring 15 on one side in the axial direction (left side in FIG. 2). The plurality of second balls constituting the ball are provided between the outer ring 16 and the inner ring 15 on the other axial side (the right side in FIG. 2), and these balls 11 and 12 are held by the cages 21 and 22, respectively. Thus, the inner ring 15 and the outer ring 16 are relatively rotatable.

[About the buttocks 30]
Although the collar part 30 of this embodiment consists of an annular ring member and is made of steel, it may be made of resin. As described above, the inner ring 15 is separate and attached to the inner ring 15. The collar portion 30 is provided on the large-diameter shoulder portion 20 located on one side in the axial direction of the inner ring 15. The collar 30 is attached to the shoulder 20 with the inner circumferential surface of the collar 30 in close contact with and fitted to the outer circumferential surface of the shoulder 20. The flange portion 30 prevents, for example, lubricating oil containing foreign matter from entering between the first cage 21 and the inner ring 15 from the outside of the bearing on one axial side.

For this purpose, the collar portion 30 has the following specific configuration.
Here, since the first retainer 21 has an outer annular portion 42 provided on one side in the axial direction of the first ball 11, the flange portion 30 extends axially with the outer annular portion 42. They are provided facing each other with a gap e (see FIG. 3). FIG. 3 is an explanatory diagram showing an enlarged view of the collar 30 shown in FIG. 2 and its surroundings. The outer peripheral surface 30a of the annular collar portion 30 is located radially outside the inner peripheral surface 42b of the outer annular portion 42, and the inner side surface 30c of the collar portion 30 and the outer side surface 42c of the outer annular portion 42. Are opposed to each other with a gap e. As a result, a labyrinth is formed between the inner side surface 30 c of the flange portion 30 and the outer side surface 42 c of the outer annular portion 42. By this labyrinth, it is possible to effectively suppress the entry of foreign matter (lubricating oil) from the outside of the bearing into the space between the inner ring 15 and the first cage 21.

The axial dimension A of the gap e is set to 2 mm or less, for example. Thereby, the penetration | invasion of lubricating oil P1 is suppressed effectively.
Further, a region where the inner side surface 30c of the flange portion 30 and the outer side surface 42c of the outer annular portion 42 overlap in the radial direction (region where the inner side surface 30c and the outer side surface 42c face each other), that is, the length B of the labyrinth (radial direction). Can be set to 1 mm or more. Thereby, the penetration | invasion of lubricating oil P1 is suppressed effectively.

  As described above, according to the double row ball bearing 5 (see FIG. 1) of the present embodiment, the gears 52 and 53 that are present in the vicinity of one side (left side in FIG. 1) of the double row ball bearing 5 in the axial direction. Even when the lubricating oil P1 falls toward the double row ball bearing 5 (see arrow X1), the lubricating oil P1 can be blocked by the annular flange 30. For this reason, the foreign matter contained in the lubricating oil P1 is difficult to enter between the first inner ring raceway groove 38 (see FIG. 2) of the inner ring 15 and the first ball 11, and further the second inner ring raceway groove 39. And the second ball 12 are less likely to enter, and foreign matter is less likely to enter between the raceway grooves 35 and 36 of the outer ring 16 and the balls 11 and 12. As a result, the bearing life can be extended.

And in order to suppress the penetration | invasion of a foreign material in this way, in this embodiment, it is only necessary to provide the ring-shaped collar part 30 which is a simple structure and consists of one member in the axial direction one side of the inner ring | wheel 15. The cost increase of the double row ball bearing 5 can be suppressed.
The flange portion 30 may be formed together with the inner ring 15 and may be integrated with the inner ring 15. However, in this embodiment, the flange portion 30 is separated from the inner ring 15 and is a ring member attached to the inner ring 15. Therefore, the inner ring 15 and the collar part 30 can be easily formed.

  Further, in the present embodiment, the collar portion 30 can reduce the amount of the lubricating oil P1 passing between the outer ring 16 and the inner ring 15, thereby reducing the probability of foreign matter intrusion inside the bearing. It is also possible. Hereinafter, this function will be described.

In FIG. 2, since the pitch circle diameter D1 of the first row by the first ball 11 is larger than the pitch circle diameter D2 of the second row by the second ball 12, as described above, the first ball 11 The diameter of the first outer ring raceway groove 35 of the outer ring 16 on which the outer ring 16 rolls is larger than the diameter of the second outer ring raceway groove 36 of the outer ring 16 on which the second ball 12 rolls. As a whole, the diameter increases toward one side in the axial direction (in FIG. 1, the pinion gear 53 side).
For this reason, when the double row ball bearing 5 rotates, the lubricating oil P1 stored in the case 50 is placed between the outer ring 16 and the inner ring 15 (inside the double row ball bearing 5) on the opposite side of the pinion gear 53 ( A flow of lubricating oil P1 (arrow X2 in FIG. 1) is generated from the right side in FIG. 1 through the inside of the double row ball bearing 5 and discharged from the pinion gear 53 side (left side in FIG. 1).

  In the case of the conventional double row ball bearing 90 (see FIG. 4), the opening K1 between the outer ring 91 and the inner ring 92 and the inflow side of the lubricating oil P1 is wide, and the opening K2 as the outflow side is also formed. wide. In this case, a large amount of the lubricating oil P1 can flow inside the double row ball bearing 90, and when a large amount of the lubricating oil P1 passes through the inside of the bearing, the foreign matter contained in the lubricating oil P1 is in contact with the balls 93 and 94. There is a higher probability of biting between the outer ring 91 and the raceway grooves of the inner ring 92. As a result, the surface of the balls 94 (93) and the raceway grooves are peeled off and the bearing life is reduced.

  On the other hand, in the present embodiment (see FIG. 2), one side in the axial direction between the inner ring 15 and the outer ring 16 becomes the opening k2 on the outflow side of the lubricating oil P1, but the annular flange 30 Functions as a throttle for the opening k2 on the outflow side, and the amount of oil passing between the inner ring 15 and the outer ring 16 can be reduced. As described above, in the present embodiment, it is possible to reduce the probability of entry of foreign matter inside the bearing.

  Further, in the present embodiment, between the first cage 21 and the inner ring 15, the outflow of the lubricating oil P <b> 1 is restricted by the flange portion 30, whereas the first cage 21 and the outer ring 16 are Between, it is in an open state. That is, the space between the inner ring 15 and the outer ring 16 is opened on the outer ring 16 side on one side in the axial direction on the outflow side of the lubricating oil P1. More specifically, the space between the outer ring 16 and the outer annular portion 42 is opened so that the ball 11 can be seen from the outside in the radial direction.

Here, temporarily, on the outflow side of the lubricating oil P1, the space between the inner ring 15 and the outer ring 16 is closed by the flange 30 on the inner ring 15 side, and also on the outer ring 16 side (for example, by the outer ring 16 or other members). In this case, if the lubricating oil P1 flowing in from the other side in the axial direction stays inside the bearing and foreign matter is contained in the staying lubricating oil P1, the foreign matter is between the balls 11, 12 and the inner ring 15 and the outer ring 16. It becomes easy to enter.
Accordingly, it is preferable to provide an outlet for the lubricating oil P1 on one side in the axial direction, which is the outflow side of the lubricating oil P1, and the outer ring 16 is opened between the inner ring 15 and the outer ring 16 as in this embodiment. ing.

  Further, as shown in FIG. 3, the lubricating oil P1 flows out from the gap e of the labyrinth formed between the inner side surface 30c of the flange portion 30 and the outer side surface 42c of the outer annular portion 42, but the gap e is reduced. As a result, the speed of this outflow increases, and the penetration of the lubricating oil P1 from the outside of the bearing is suppressed.

  In the embodiment shown in FIG. 3, the outer peripheral surface 30 a of the flange portion 30 is located radially inward of the outer peripheral surface 42 a of the outer annular portion 42, but the radial dimension of the flange portion 30 is increased. In addition, the outer peripheral surface 30 a of the flange portion 30 may be located on the radially outer side than the outer peripheral surface 42 a of the outer annular portion 42. Thereby, the length B of the labyrinth can be increased.

  In the embodiment shown in FIG. 2, the case where the first retainer 21 includes the outer annular portion 42 has been described, but the outer annular portion 42 is omitted (not shown), and the first retainer 21 is provided. May be a so-called crown-shaped cage composed of an inner annular portion 43 and a plurality of column portions 44. In this case, the collar portion 30 forms a labyrinth with the outer peripheral surface of the ball 11, and even in this case, the collar portion 30 receives lubricating oil containing foreign matter from the outside of the bearing. Intrusion between 21 and the inner ring 15 can be prevented.

  According to the double row ball bearing 5 having the above configuration, the foreign matter contained in the lubricating oil P1 is between the first ball 11, the outer ring 16 and the raceway grooves 35 and 38 of the inner ring 15, and the second. It becomes difficult for the ball 12 to enter between the outer ring 16 and the raceway grooves 36, 39 of the inner ring 15, and the bearing life can be extended. As a result, the lifetime of the differential gear device can be extended.

[Others]
The above description regarding the configuration of the double row ball bearing is the description of the double row ball bearing 5 on the pinion gear 53 side of the differential gear device shown in FIG. 1, but the double row ball bearing 7 on the flange 54 side is also the pinion gear 53. It can have the same configuration as the double-row ball bearing 5 on the side. That is, also in the double-row ball bearing 7 on the flange 54 side, an annular flange 40 is provided on a large-diameter shoulder located on one side of the inner ring 25 in the axial direction. Lubricating oil containing foreign matter can be prevented from entering between the cage and the inner ring 25 from the outside.

Further, the double row ball bearing and the shaft support device of the present invention are not limited to the illustrated form, and may be other forms within the scope of the present invention.
For example, in the above-described embodiment, the case where the double row ball bearing 5 (7) is applied to a differential gear device has been described. However, it can be applied to other shaft support devices.

5: Double row ball bearing 7: Double row ball bearing 11: First ball 12: Second ball 15: Inner ring 16: Outer ring 20: Shoulder 21: First retainer 22: Second retainer 23: Pocket 24 ： Pocket 30: collar 40: collar 42: outer annular part (annular part) 44: pillar part 50: case 51: differential mechanism (gear mechanism) 52: ring gear (large diameter gear)
53: Pinion gear (small diameter gear) 55: Pinion shaft (shaft) Clearance e
P1: Lubricating oil

Claims (4)

Outer ring,
Inner ring,
A plurality of first balls which are provided between the outer ring and the inner ring and which are provided on one side in the axial direction and constitute a first row;
A plurality of second balls which are provided between the outer ring and the inner ring and which are provided on the other side in the axial direction and constitute a second row having a pitch circle diameter smaller than the first row;
An annular first cage having a plurality of pockets for holding the first balls;
An annular second cage having a plurality of pockets for holding the second balls;
An annular flange that is provided on a large-diameter shoulder on one side in the axial direction of the inner ring and prevents lubricant containing foreign matter from entering between the first retainer and the inner ring;
With double row ball bearings. The first retainer has an annular portion provided on one axial side of the first ball, and a pillar portion extending from the annular portion to the other axial side,
The double row ball bearing according to claim 1, wherein the flange portion is provided to face the annular portion with a gap in the axial direction, and a labyrinth is formed between the flange portion and the annular portion. .   The double row ball bearing according to claim 1, wherein the flange portion is a separate member from the inner ring and includes a ring member attached to the inner ring.   4. A case, a gear mechanism having a large-diameter gear and a small-diameter gear provided in the case, a shaft that integrally rotates with the small-diameter gear, and the shaft that rotatably supports the shaft. A shaft support device comprising the double-row ball bearing according to claim.

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