JP2019218975A - Damper device - Google Patents

Abstract

To improve the rigidity of a support part of an input-side side plate for supporting torsion springs, in a damper device.SOLUTION: This device comprises input-side/output-side side plates 11, 12, a hub flange 13, and a plurality of torsion springs 14. The input-side side plate 12 has a plurality of input-side support parts 12b for supporting the torsion springs 14, and receives inputted torque. The input-side support part 12b has an external peripheral side support part 121, an internal peripheral side support part 122 and a curved part 123. The external peripheral side support part 121 is formed by cutting and raising an edge of an opening 120 at the outside of a radial direction. The internal peripheral side support part 122 is formed by cutting and raising an edge of the opening 120 at the inside of the radial direction. The curved part 123 connects both end parts of the opening 120 in a circumferential direction and both end parts of the internal peripheral side support part 122 in the circumferential direction in a curved shape, and is not contact with the torsion springs 14.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a damper device, and more particularly, to a damper device for transmitting torque from a drive source to an output side and attenuating input torque fluctuation.

  A damper device is provided for suppressing vibration transmitted from a drive source such as an engine to a transmission and suppressing abnormal noise. As this kind of damper device, a damper device as shown in Patent Document 1 is provided.

  In the damper device of Patent Literature 1, a window hole is provided in a hub flange as a housing portion for housing a coil spring. Further, a clutch plate and a retaining plate are arranged on both sides in the axial direction of the hub flange, and these plates are formed with windows as supporting portions for supporting the coil spring. The window has a hole penetrating in the axial direction and a support formed along an edge of the hole.

JP 2003-148512 A

  In the device of Patent Document 1, torque is input via a clutch disk fixed to an outer peripheral portion of a clutch plate. The input torque is transmitted to the coil spring via the clutch plate and the retaining plate, and further output from the coil spring to the transmission via the hub flange.

  In transmitting the torque as described above, the windows of the clutch plate and the retaining plate receive torque at circumferential ends that come into contact with the end surfaces of the coil springs. Therefore, stress tends to concentrate on the corner at the circumferential end of the window, and problems such as cracks tend to occur from the corner.

  It is an object of the present invention to improve the strength of a support portion of a plate on a side to which torque is input, of a pair of plates supporting an elastic member, in a damper device.

  (1) A damper device according to the present invention includes an input side plate, an output side plate, a hub flange, and a plurality of elastic members. The input-side side plate has a plurality of input-side support portions having openings that penetrate in the axial direction, and receives a torque. The output side plate has a plurality of output side support portions having openings that penetrate in the axial direction, is opposed to the input side plate in the axial direction, and is fixed so as not to rotate relative to the input side plate. . The hub flange has a flange portion arranged between the input side plate and the output side plate in the axial direction, and the flange portion has a plurality of housing portions at positions corresponding to the input side and the output side support portion. , And can be rotated relative to the input side and output side side plates. The plurality of elastic members are housed in the housing portion, are supported in the axial direction by the input-side and output-side support portions, and can contact the circumferential ends of the openings. The hub flange is elastically connected in the rotation direction.

  The input-side support section has an outer-peripheral-side support section, an inner-peripheral-side support section, and a curved section. The outer peripheral side support portion is formed by cutting and raising a radially outer edge of the opening, and supports the elastic member. The inner peripheral side support portion is formed by cutting and raising a radially inner edge portion of the opening, and supports the elastic member. The curved portion connects between both ends in the circumferential direction of the opening and both ends in the circumferential direction of the inner peripheral side support portion in a curved shape, and is not in contact with the elastic member.

  In this device, the torque from the drive source is input to the input side plate. Then, the input torque is transmitted from the input side and output side side plates to the plurality of elastic members and the hub flange and output.

  During this torque transmission, torque is transmitted between the input-side support portion of the input-side side plate and the elastic member. In the input-side support, the elastic member is axially supported by the outer-peripheral support and the inner-peripheral support. In the input-side support portion, between the circumferential end of the opening that receives the torque and the circumferential end of the inner-side support portion, a curved portion that connects these portions in a curved shape is provided. The curved portion is formed so as not to contact the elastic member. For this reason, even when torque is input from the radially inner side of the input-side support portion in the input-side side plate, stress can be prevented from being concentrated on a part of the input-side support portion, and The strength of the support is improved.

  (2) Preferably, the inner peripheral side support portion extends linearly, and the curved portion is curved so as to expand radially inward.

  (3) Preferably, the apparatus further includes an input member fixed to the input side plate and for inputting torque to the input side plate. Then, torque is input to the input side plate from the radially inner side of the input side support portion.

  Here, the input member is fixed to the input side plate. Then, torque is input from the radially inner side of the input-side support portion via the input member. That is, here, the torque is transmitted from the inner peripheral side to the outer peripheral side in the input side plate.

  In such a torque transmission path, in the input-side support portion, the curved portion is provided at a boundary between the circumferential end portions of the opening and the circumferential end portions of the inner circumferential side support portion, and The curved portion is not in contact with the elastic member. Therefore, the stress at the corners of the input-side support portion is reduced.

  (4) Preferably, it further includes a plurality of first rivets and a plurality of second rivets. The first rivet connects the input-side and output-side side plates at predetermined intervals in the axial direction so as to be immovable in the axial and rotational directions. The second rivet fixes the input member to a side surface of the input side plate. The input member has a plurality of rivet caulking holes at positions corresponding to the plurality of first rivets.

  In this device, the torque from the drive source is input to the input side plate via the input member. Then, the input torque is transmitted from the input side and output side side plates to the plurality of elastic members and the hub flange and output.

  Here, the input member has a rivet caulking hole formed at a position corresponding to the first rivet. Therefore, after the input member is fixed to the side surface of the input side plate, the rivet can be caulked using the rivet caulking hole to connect the input side plate and the output side plate.

  (5) Preferably, the first rivet axially penetrates the inside of the elastic member in the radial direction inside the housing portion.

  Here, the first rivet penetrates a housing portion for housing the elastic member. That is, it is not necessary to form a hole in the flange portion for penetrating the first rivet separately from the accommodation portion. For this reason, the size of the flange portion can be reduced in the radial direction, and a decrease in the strength of the flange portion can be suppressed.

  According to the present invention described above, in the damper device, the strength of the support portion of the input side plate that supports the elastic member can be improved.

1 is a cross-sectional view of a damper device according to an embodiment of the present invention. The front view of FIG. The enlarged front view of a 2nd support part. FIG. 4 is a schematic view showing an arrangement of a housing portion of a hub flange. Enlarged partial view of FIG.

[Constitution]
1 and 2 show a damper device 1 according to an embodiment of the present invention. FIG. 1 is a sectional view of the damper device 1, and FIG. 2 is a front view thereof. Note that FIG. 2 is a view as viewed from the transmission side, and illustrates a part with parts removed. In FIG. 1, OO is the rotation axis of the damper device 1, that is, the rotation center line. A drive source such as an engine or a motor is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of FIG.

  In the following description, “radially outward” and “outer peripheral side” are sides away from the rotation center line of the damper device 1, and “radially inward” and “inner peripheral side” are opposite sides. .

  The damper device 1 transmits torque input from the drive source to the transmission side and attenuates torque fluctuations. The damper device 1 includes an input plate 10 (an example of an input member), a first side plate 11 (an example of an output side plate), a second side plate 12 (an example of an input side plate), a hub flange 13, It has a plurality of torsion springs 14, a stopper mechanism 15, and a hysteresis torque generating mechanism 16.

  The input plate 10 is arranged closest to the drive source of the damper device 1. The input plate 10 is formed in a disk shape, has an opening 10a in the center, and has an engaging portion 10b provided in the outer peripheral portion inclined to the drive source side. More specifically, the inner peripheral end extends further radially inward than the position where the torsion spring 14 is arranged. The outer peripheral end extends radially outward such that the torsion spring 14 and the radial position overlap. The torque from the drive source is input via the engagement portion 10b. A plurality of caulking holes 10c are formed radially inward of the engagement portion 10b.

  The first and second side plates 11 and 12 are arranged facing each other at a predetermined interval in the axial direction. The first side plate 11 and the second side plate 12 are fixed immovably in the axial direction and the rotational direction by caulking a plurality of first rivets 18. The first side plate 11 is arranged on the transmission side, and the second side plate 12 is arranged on the drive source side.

  The first side plate 11 is formed in a disk shape. The first side plate 11 includes an opening 11a formed in the center, a plurality of first support portions 11b (an example of an output side support portion), a plurality of engagement holes 11c, and a plurality of rivet caulking holes 11d. ,have.

  The first support portion 11b is formed in a frame shape. That is, it has an opening that penetrates in the axial direction and extends in the circumferential direction, and an inner-peripheral-side support portion and an outer-peripheral-side support portion formed by cutting and raising the inner and outer edges of the opening. The engaging hole 11c is formed at a radially intermediate portion, and the rivet setting hole 11d is formed at the outer peripheral portion.

  The second side plate 12 is formed in a disk shape, and a radially intermediate portion is fixed to the input plate 10 by a second rivet 19. That is, a part of the input plate 10 is in contact with the side surface on the drive source side of the second side plate 12, and the contact portion is swaged by the second rivet 19, so that the input plate 10 and the second side plate 12 are fixed. The second side plate 12 has an opening 12a formed at the center and a plurality of second support portions 12b (input-side support portions).

  The second support portion 12b is arranged to face the first support portion 11b in the axial direction, and is formed in a frame shape like the first support portion 11b. That is, it has an opening 120 that penetrates in the axial direction and extends in the circumferential direction, and has an outer peripheral side support portion 121, an inner peripheral side support portion 122, and two curved portions 123 as shown in an enlarged manner in FIG. are doing.

  The outer peripheral side support portion 121 is formed by cutting and raising a radially outer edge of the opening 120. The outer peripheral side support portion 121 is formed in a continuous arc shape bulging outward. The outer peripheral side support portion 121 supports a radially outer portion of the torsion spring 14.

  The inner peripheral side support portion 122 is formed by cutting and raising a radially inner edge of the opening 120. The inner peripheral side support portion 122 extends linearly, and has a notch 122a at the center. The notch 122a is formed to avoid interference with the input plate 10. Thus, the radially inner portion of the torsion spring 14 is supported by both ends of the inner peripheral side support portion 122.

  The curved portion 123 is a portion that connects between both ends in the circumferential direction of the opening 120 and both ends in the circumferential direction of the inner peripheral side support portion 122 (that is, a boundary portion) in a curved shape. The curved portion 123 is formed to be curved so as to expand radially inward, and does not contact the torsion spring 14.

  Here, the first support portion 11b and the second support portion 12b are formed radially outside of the second rivet 19 connecting the input plate 10 and the second side plate 12. Therefore, when the torque input to the input plate 10 is transmitted to the torsion spring 14, the torque is transmitted from the inner peripheral side support portion 122 of the second support portion 12 b to the torsion spring 14. Therefore, stress tends to concentrate on both ends of the inner peripheral side support portion 122 of the second support portion 12b (that is, a boundary portion between the both end portions and the circumferential end of the opening 120).

  However, curved portions 123 are formed at both ends of the inner peripheral side support portion 122, respectively. The bending portion 123 is not in contact with the torsion spring 14. For this reason, compared with the conventional structure in which the curved portion 123 is not formed, it is possible to prevent stress from being concentrated on both ends of the inner peripheral side support portion 122.

  The hub flange 13 has a boss 21 and a flange 22. The hub flange 13 is rotatable relative to the first and second side plates 11 and 12 within a predetermined angle range.

  The boss portion 21 extends in the axial direction, and has a spline hole 21a in an inner peripheral portion. An input shaft (not shown) of the transmission can be spline-fitted into the spline hole 21a.

  The flange portion 22 extends radially outward from the boss portion 21 and is disposed between the first and second side plates 11 and 12 in the axial direction. The flange portion 22 has openings as a plurality of storage portions 22a. The accommodation section 22a is formed at a position corresponding to the first and second support sections 11b and 12b of the first and second side plates 11 and 12. As is clear from FIG. 2, the accommodation portion 22a is formed such that the inner peripheral portion extends further inward in the radial direction than the openings of the first and second support portions 11b and 12b. The first rivet 18 for fixing the first and second side plates 11 and 12 passes through the inner peripheral portion of the housing portion 22a.

  The plurality of torsion springs 14 are housed in the housing portion 22a of the hub flange 13, and are supported by the first and second support portions 11b and 12b of the first and second side plates 11 and 12 so as not to move in the axial direction. ing. Further, both end surfaces of the plurality of torsion springs 14 can abut on circumferential ends of the openings of the first and second support portions 11b and 12b. The torsion spring 14 elastically connects the first and second side plates 11 and 12 and the hub flange 13 in the rotational direction.

  FIG. 4 schematically shows the arrangement of the housing portion 22a of the hub flange 13. The torsion spring 14 has two first springs 141 and four second springs. In this embodiment, each spring includes a large-diameter coil spring and a small-diameter coil spring housed therein.

  The two first springs 141 are arranged facing each other at an interval of 180 °. Further, the four second springs 142 are arranged between the two first springs 141 in the circumferential direction. The first spring 141 has a longer spring length than the second spring.

  The accommodation section 22a has two first accommodation sections 221a that accommodate the first spring 141, and four second accommodation sections 222a that accommodate the second spring 142. The circumferential length of the first housing portion 221a is longer than that of the second housing portion 222a.

  Here, as shown by the dashed line in FIG. 4, if the six housing portions 22a are arranged at equal angular intervals (here, 60 ° intervals), the adjacent housing portions 221a and 222a have different lengths so that adjacent housing portions 221a and 222a have different lengths. The intervals between the portions 22a differ. Specifically, the interval between the adjacent first storage portion 221a and the second storage portion 222a is G1, the interval between the adjacent second storage portions 222a is G2, and the interval between G1 is reduced.

  Generally, a member such as a stop pin is arranged between the housing portions 221a and 222a in the circumferential direction, so that it is not preferable that the gap between the housing portions 221a and 222a is widened. The strength of the narrow part will be reduced.

  Thus, here, the second housing portion 222a is separated from the first housing portion 221a, and the two housing portions 222a are arranged closer to each other. That is, the second housing portions 222a are arranged so as to be separated from the first housing portions 221a by an angle θ as compared with the case where the second housing portions 222a are arranged at equal angular intervals. As a result, the distance between the first storage part 221a and the second storage part 222a and the distance between the second storage parts 222a are both G0, and can be equalized.

  As shown in FIG. 2, the stopper mechanism 15 includes a plurality of notches 24 formed in the flange portion 22, a plurality of stoppers 25 formed in the outer peripheral portion of the first side plate 11, and a third rivet 26. Have.

  The notch 24 is formed on the outer peripheral surface of the flange portion 22 with a predetermined length in the circumferential direction and a predetermined width in the radial direction. The stopper 25 includes a stopper body 25a formed by bending a part of an outer peripheral portion of the first side plate 11 toward the second side plate 12, and a fixing portion 25b formed by further bending an end thereof toward the inner peripheral side. And The stopper body 25a passes through the notch 24 in the axial direction, and the fixing portion 25b is fixed to the outer peripheral portion of the second side plate 12 by swaging the third rivet 26.

  With such a configuration, the first and second side plates 11 and 12 and the hub flange 13 can rotate relative to each other within an angle range in which the stopper main body 25a contacts the end face of the notch 24. In other words, the relative rotation between the first and second side plates 11 and 12 and the hub flange 13 is prohibited by the stopper body 25a contacting the end face of the notch 24.

  As shown in FIG. 5, the hysteresis torque generating mechanism 16 has a first friction member 31, a second friction member 32, a friction plate 33, and a cone spring.

  The first friction member 31 is an annular plate, and is arranged on the outer peripheral portion of the boss portion 21 so as to contact the side surface of the inner peripheral portion of the flange portion 22 on the first side plate 11 side. The second friction member 32 is an annular plate, and is arranged between the inner peripheral portion of the flange portion 22 and the inner peripheral portion of the second side plate 12. Friction members 31a and 32a are fixed to both side surfaces of the first and second friction members 31 and 32, respectively.

  The friction plate 33 is arranged on the first side plate 11 side of the first friction member 31, and the cone spring 34 is arranged between the friction plate 33 and the first side plate 11 in a compressed state. A plurality of engagement projections 33a formed by being bent toward the first side plate 11 are formed on an outer peripheral portion of the friction plate 33. The engagement protrusion 33a is engaged with the engagement hole 11c of the first side plate 11. Therefore, the friction plate 33 cannot rotate relative to the first side plate 11.

  In the above configuration, the first friction member 31 is pressed by the flange portion 22 and the friction plate 33 with a predetermined pressing force, and the second friction member 32 is pressed by the flange portion 22 and the second side plate 12 with a predetermined pressing force. Pressed by pressure. Therefore, when relative rotation occurs between the first and second side plates 11, 12 and the hub flange 13, frictional resistance occurs between the first and second friction members 31, 32 and the mating member. . As a result, a hysteresis torque is generated.

[Configuration for lubricating oil supply]
Here, the lubricating oil is supplied to the hysteresis torque generating mechanism 16 from the second side plate 12 on the inner peripheral side of the hub flange 13. The direction in which the lubricating oil is supplied is indicated by an arrow L in FIG. A plurality of oil supply holes 35 penetrating in the axial direction are formed in a portion of the hub flange 13 where the lubricating oil is supplied. Specifically, the oil supply hole 35 is formed at the inner peripheral end of the flange portion 22 of the hub flange 13, and penetrates the first side plate 11 side and the second side plate 12 side in the axial direction. The oil supply hole 35 is formed further radially inside than the inner peripheral ends of the first and second friction members 31 and 32.

  As shown in FIG. 5, a recess 13a that is recessed in the axial direction is formed on a side surface of the hub flange 13 on the second side plate 12 side. The outer diameter of the concave portion 13a substantially coincides with the radially outermost portion of the oil supply hole 35. The outer peripheral side wall 13b of the concave portion 13a has a curved surface as an oil receiving portion.

  Therefore, the lubricating oil supplied from the inner peripheral sides of the input plate 10 and the second side plate 12 is supplied to the inner peripheral portion of the second friction member 32 along the curved surface of the outer peripheral side wall 13b of the concave portion 13a. At the same time, the lubricating oil is also guided to the oil supply hole 35 along the curved surface of the outer peripheral side wall 13b of the recess 13a. The lubricating oil guided to the oil supply hole 35 is supplied to the inner peripheral portion of the first friction member 31 through the oil supply hole 35. Since the oil supply hole 35 is formed radially inward of the inner peripheral ends of the first and second friction members 31 and 32, it is possible to prevent the lubricating oil from flowing into the oil supply hole 35. Further, the lubricating oil is not prevented from flowing out of the oil supply hole 35.

  Thus, the lubricating oil is supplied to the inner peripheral portions of the first and second friction members 31, 32, and further supplied to the outer peripheral friction materials 31a, 32a by centrifugal force.

  Further, the inner diameters of the friction plate 33 and the first side plate 11 are formed smaller than the inner diameter of the first friction member 31. Therefore, the lubricating oil flowing out to the first friction member 31 through the oil supply hole 35 can be further prevented from flowing out to the outside in the axial direction (the right side in FIG. 1) by the plates 33 and 11. That is, the inner diameters of the friction plate 33 and the first side plate 11 restrict the flow of the lubricating oil discharged from the oil supply holes 35 further axially outward (the right side in FIGS. 1 and 3) from the first side plate 11. It functions as a regulation unit. Therefore, lubricating oil can be sufficiently supplied to the first friction member 31.

  Similarly, the inside diameter of the second side plate 12 is formed smaller than the inside diameter of the second friction member 32. Therefore, the lubricating oil supplied to the second friction member 32 from the recess 13a can be further prevented from flowing outward in the axial direction (the left side in FIG. 1) by the second side plate 12. Therefore, the lubricating oil can be sufficiently supplied to the second friction member 32.

  As described above, the lubricating oil is supplied to the first and second friction members 31 and 32 through the oil supply holes 35 and the like. In such a configuration, it is difficult to provide a configuration for radially positioning the first and second friction members 31, 32 on the inner peripheral side of the first and second friction members 31, 32.

  Therefore, annular projecting portions 22b that project in the axial direction are formed on both side surfaces of the flange portion 22. The first and second friction members 31, 32 are positioned in the radial direction by bringing the outer peripheral surfaces of the first and second friction members 31, 32 into contact with the protruding portions 22b.

[Assembly]
Here, when assembling the present apparatus, first, the input plate 10 is fixed to the side surface of the second side plate 12 with the second rivet 19. Thereafter, the hysteresis torque generating mechanism 16 and the torsion spring 14 are assembled to the first side plate 11 and the hub flange 13, and the first side plate 11 and the second side plate 12 are fixed by the first rivet 18 and the third rivet 26. .

  When fixing the first side plate 11 and the second side plate 12, the first rivet 18 is swaged using the swaging hole 10 c formed in the input plate 10, and the first side plate 11 is fixed to the first side plate 11. The third rivet 26 is swaged using the formed swaging hole 11d.

[motion]
When torque is input from the drive source to the input plate 10, the torque is transmitted from the first and second side plates 11 and 12 to the hub flange 13 via the torsion spring 14. The torque transmitted to the hub flange 13 is transmitted to the input shaft of the transmission fitted into the spline hole 21a of the boss 21.

  In the above operation, as described above, when the first and second side plates 11, 12 and the hub flange 13 rotate relative to each other, the friction fixed to both side surfaces of the first and second friction members 31, 32. The members 31a and 32a are in sliding contact with other members, and a frictional resistance is generated. As a result, a hysteresis torque is generated, and the torque fluctuation is attenuated.

  Further, during the above operation, sufficient lubricating oil is stably supplied to the first and second friction members 31 and 32 through the recess 13a and the oil supply hole 35. Therefore, a stable hysteresis torque can be obtained.

  Further, in the support portions 11b and 12b of the first and second side plates 11 and 12, a curved portion 123 is provided in an inner peripheral portion of the second support portion 12b where the stress is highest due to the structure of the present apparatus. Therefore, the strength of the second support portion 12b can be improved.

[Other embodiments]
The present invention is not limited to the above embodiments, and various changes or modifications can be made without departing from the scope of the present invention.

  (A) In the above embodiment, the notch 122a is formed in the inner support portion 122 of the second support portion 12b in order to avoid interference with the input plate 10. If there is no interference, the notch 122a is unnecessary.

  (B) In the above embodiment, the example in which the friction members 31 and 32 are provided on both sides of the flange portion 22 has been described. However, the friction members may be provided only on one side.

DESCRIPTION OF SYMBOLS 1 Damper device 10 Input plate 10b Engaging part 10c Caulking hole 11 First side plate (output side plate)
11b 1st support part (output side support part)
12 Second side plate (input side plate)
12b 2nd support part (input side support part)
120 Opening 121 Outer peripheral side support part 122 Inner peripheral side support part 123 Curved part 13 Hub flange 14 Torsion spring 18 First rivet 19 Second rivet

Claims (5)

An input-side side plate having a plurality of input-side support portions having openings that penetrate in the axial direction, and an input of torque,
An output side plate having a plurality of output side support portions having openings penetrating in the axial direction, facing the input side side plate in the axial direction, and being fixed to the input side plate and relatively non-rotatable. ,
It has a flange portion arranged between the input side plate and the output side plate in the axial direction, and the flange portion has a plurality of housing portions at positions corresponding to the input side and the output side support portion. A hub flange rotatable relative to the input and output side plates,
The input side and the output side plate and the hub are accommodated in the accommodation section, are supported in the axial direction by the input side and the output side support section, and can abut on circumferential ends of the opening. A plurality of elastic members elastically connecting the flange to the rotating direction;
With
The input-side support portion,
An outer peripheral side supporting portion formed by cutting and raising a radially outer edge of the opening, and supporting the elastic member;
An inner peripheral side support portion formed by cutting and raising a radially inner edge of the opening, and supporting the elastic member,
Both ends in the circumferential direction of the opening, and both ends in the circumferential direction of the inner peripheral side support portion, a curved portion that connects between the curvilinear, and non-contact with the elastic member,
Having,
Damper device. The inner peripheral side support portion extends linearly,
The curved portion is curved so as to expand radially inward,
The damper device according to claim 1. An input member fixed to the input side plate, further comprising an input member for inputting torque to the input side plate,
Torque is input to the input side plate from a radially inner side of the input side support portion.
The damper device according to claim 1. A plurality of first rivets for connecting the input side and output side side plates at predetermined intervals in the axial direction and immovably in the axial and rotational directions,
A plurality of second rivets for fixing the input member to a side surface of the input side plate;
Further comprising
The input member has a plurality of rivet caulking holes at positions corresponding to the plurality of first rivets,
The damper device according to claim 3. The first rivet axially penetrates a radially inner side of the elastic member inside the housing portion.
The damper device according to claim 1.

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