JP2018007578A - Double bearing reel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a double bearing reel having a brake device braking a spool, reducing an inertia amount of a spool, and appropriately applying braking force to the spool corresponding to the rotation of the spool.SOLUTION: A double bearing reel body includes a spool shaft 3, a spool 2 and a brake device 5 braking the spool 2. The spool 2 is attached to the spool shaft 3 so as not to be rotatable and includes a spool shank part 11, a first flange part 12, a second flange part and a brim part 14. The first flange part 12 is formed on one end of the spool shank part 11 in a diameter larger than that of the spool shank part 11. The second flange part is formed on another end of the spool shank part 11 in a diameter larger than that of the spool shank part 11. The brim part 14 extends in a direction further from the tip end of the first flange part 12. The brake device 5 has magnets 26 arranged so as to face the inner peripheral surface of the brim part 14 and brakes the spool 2 by magnetic force of the magnets 26 to the brim part 14.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a dual-bearing reel, and more particularly to a dual-bearing reel having a braking device that brakes a spool.

  In the double-bearing reel in which the spool rotates when the fishing line is fed out, the rotation speed of the spool becomes faster than the line feeding speed at the time of casting, so that the fishing line sags and the dandruff occurs, so-called backlash occurs. For this reason, what provided the braking device for providing a braking force to the rotating spool is provided. For example, the brake device of Patent Document 1 applies a braking force to a spool using a magnetic brake.

Japanese Utility Model Publication No. 62-35334

  The brake device of Patent Document 1 brakes the rotation of the spool by causing a magnet constituting the magnetic brake to face the inner peripheral surface of the flange portion of the spool. In this case, in order to further increase the braking force, for example, it is conceivable to increase the thickness of the flange portion of the spool, or to extend the flange portion in the axial direction to expand the facing range of the magnet. However, such a configuration increases the amount of inertia of the spool. If the spool has a large inertia, the spool is difficult to rotate with the throwing of the device, and not only does the flight distance increase, but it is difficult to reduce the speed even when a braking force is applied, and it is difficult to eliminate the backlash.

  An object of the present invention is to reduce the inertia amount of a spool in a dual-bearing reel having a braking device that brakes the spool, and to appropriately apply a braking force according to the rotation of the spool to the spool. is there.

  A dual-bearing reel according to one aspect of the present invention includes a reel body, a spool shaft, a spool, and a braking device that brakes the spool. The spool shaft is rotatably supported by the reel body. The spool is non-rotatably mounted on the spool shaft, and includes a bobbin trunk, a first flange, a second flange, and a flange. The bobbin trunk can wind a fishing line around the outer periphery. The first flange portion is formed at one end of the bobbin trunk with a larger diameter than the bobbin trunk. The second flange portion is formed at the other end of the bobbin trunk with a larger diameter than the bobbin trunk. The collar portion further extends in the axial direction from the tip of only the first flange portion. The braking device includes a magnet disposed to face the inner peripheral surface of the flange portion, and brakes the spool by a magnetic force applied to the flange portion of the magnet.

  In this dual-bearing reel, since the collar portion is formed only at the first flange portion provided at one end of the bobbin trunk portion, an increase in the inertia amount of the spool can be suppressed. Further, since the flange portion away from the center of rotation of the spool is used as the conductor, a greater braking force can be obtained compared to when the conductor is provided near the center of rotation of the spool.

  Preferably, the spool further includes an annular rib that extends in the axial direction from one of the bobbin trunk and the first flange and is formed on the inner peripheral side of the collar. The magnet is disposed between the collar portion and the annular rib. The braking device brakes the spool by the magnetic force applied to the flange portion of the magnet and the annular rib.

  In this case, the magnetic force of the magnet with respect to the collar part and the annular rib can be used as a braking force by using the collar part and the annular rib facing the magnet as the conductor. For this reason, it is possible to increase the braking force while suppressing an increase in the amount of inertia.

  Preferably, the bobbin trunk has a plurality of through holes. Since a braking force is applied using the spool collar as a conductor, a through-hole can be provided as a whole in the bobbin trunk. For this reason, the inertial amount of the spool can be reduced.

  Preferably, the braking device has a magnet attachment member for attaching the magnet.

  Preferably, the braking device relatively moves the magnet mounting member based on the magnetic force, and changes the action of the magnetic force on the spool in accordance with the movement of the magnet mounting member. In this case, the braking force is relatively small when the rotation of the spool is low, and the braking force is large when the spool is high, so that a highly practical braking function can be realized.

  Preferably, the braking device further includes an adjusting member that adjusts the braking force by moving the magnet mounting member in the axial direction. As a result, the braking force can be easily adjusted.

  According to the present invention, it is possible to reduce the inertia amount of the spool and appropriately apply a braking force according to the rotation of the spool to the spool.

1 is a perspective view of a dual-bearing reel in which an embodiment of the present invention is adopted. 1 is a cross-sectional view of a dual-bearing reel in which an embodiment of the present invention is employed. The perspective view of the spool of the double bearing reel by which one Embodiment of this invention was employ | adopted. The expanded sectional view of the braking device of the said double bearing reel. The expansion disassembled perspective view of the principal part of the said braking device. The expanded sectional view of the said braking device when a 2nd cylinder part moves to an axial direction.

<Overall configuration of dual-bearing reel>
1 and 2 are a perspective view and a sectional view of a dual-bearing reel in which an embodiment of the present invention is adopted. The dual-bearing reel includes a reel body 1, a spool 2 disposed inside the reel body 1, a spool shaft 3 rotatably supported on the reel body 1, and a spool disposed on the side of the reel body 1. 2, a rotation handle 4, and a braking device 5 for braking the rotation of the spool 2.

  As shown in FIGS. 1 and 2, the reel unit 1 includes a frame 6, a first side cover 7 and a second side cover 8 that are mounted on both sides of the frame 6, and a frame 6 that is not illustrated. And a thumb rest. The frame 6 has a pair of first side plate 9 and second side plate 10 arranged so as to face each other with a predetermined interval, and a plurality of connecting portions (not shown) that connect these.

  A brake case 20 is fixed to the first side cover 7 (left side in FIG. 2) by a screw member. The second side cover 8 (right side in FIG. 2) is detachably fixed to the second side plate 10 by a screw member. The first side plate 9 is formed with an opening 9a through which the spool 2 can pass.

  As shown in FIG. 4 which is an enlarged view of FIG. 2 and FIG. 2, the brake case 20 is a bottomed cylindrical case member. An inner cylinder portion 20 a that protrudes in a cylindrical shape is formed at the center portion of the brake case 20 on the spool 2 side. A bearing 18a for supporting one end of the spool shaft 3 is disposed on the inner peripheral portion of the inner cylindrical portion 20a. A plurality of through holes 20b penetrating in the axial direction are formed in the inner peripheral portion of the inner cylinder portion 20a.

  As shown in FIGS. 3 and 4, the spool 2 includes a tubular bobbin trunk 11 on which a fishing line can be wound, a first flange portion 12, a second flange portion 13, a flange portion 14, and an annular rib 15. And a cylindrical shaft mounting portion 16 fixed to the spool shaft 3, and a connecting portion 17 that connects the bobbin trunk 11 and the shaft mounting portion 16. The shaft mounting portion 16 and the spool shaft 3 are coupled by, for example, serration so that the spool 2 cannot rotate with respect to the spool shaft 3 penetrating the shaft mounting portion 16. The spool 2 is made of, for example, an aluminum alloy and is a nonmagnetic electric conductor.

  The bobbin trunk 11 is formed to have a space on the inner peripheral side. Further, as shown in FIG. 3, a plurality of circular through-holes 11a and elliptical through-holes 11b are formed in the bobbin trunk 11 at regular intervals in order to reduce the weight of the spool 2. Has been.

  The first flange portion 12 is formed at one end (the left side in FIG. 4) of the bobbin trunk 11 with a diameter larger than the outer diameter of the bobbin trunk 11. The second flange portion 13 is formed at the other end (right side in FIG. 4) of the bobbin trunk 11 with a diameter larger than the outer diameter of the bobbin trunk 11. Here, the outer diameters of the first flange portion 12 and the second flange portion 13 are the same.

  The flange portion 14 is formed to extend further outward in the axial direction (left side in FIG. 4) from the tip of the outer peripheral portion of the first flange portion 12. Further, the flange portion 14 is formed only on the first flange portion 12 in order to suppress an increase in the inertia amount of the spool 2. For this reason, as shown in FIG. 3, the spool 2 has a left-right asymmetric shape.

  The annular rib 15 is formed to further extend from the bobbin trunk 11 to the axially outer side (left side in FIG. 4) on the inner peripheral side of the collar portion 14. A magnet 26 described later is disposed in an annular space A formed between the outer peripheral surface 15a of the annular rib 15 and the inner peripheral surface 14a of the flange portion 14.

  As shown in FIG. 2, one end of the spool shaft 3 is rotatably supported by a bearing 18 a disposed on the inner peripheral side of the brake case 20. The other end of the spool shaft 3 extends through the second side plate 10 to the outside of the second side cover 8, and is freely rotatable by a bearing 18 b disposed on a boss portion 19 formed on the second side cover 8. It is supported by.

  As shown in FIG. 1, the handle 4 is disposed on the side of the second side cover 8, and has a plate-like arm portion 4a and a pair of gripping portions 4b rotatably mounted on both ends of the arm portion 4a. have.

<Configuration of braking device 5>
The braking device 5 applies a force in the direction opposite to the rotation direction to the spool 2 to brake the spool 2. As shown in FIGS. 4 and 5, the braking device 5 includes a support member 22, a magnet attachment member 23, a spring member 24, a retaining member 25, and a magnet 26.

  The support member 22 is attached to the outer peripheral portion of the inner cylindrical portion 20a that protrudes in a cylindrical shape from the central portion of the brake case 20. The support member 22 has an engaged portion 22a on the outer peripheral surface. The engaged portion 22a is a groove formed in a curved shape, and is formed such that the axial engagement position gradually changes in the circumferential direction. More specifically, the engagement position in the axial direction of the engaged portion 22a is formed so as to change suddenly in a part of the circumferential direction. The support member 22 has a female screw portion 22b at the inner peripheral portion of the tip on the spool 2 side (right side in FIG. 4). A flange portion 22 c is formed on the base end side of the support member 22.

  As shown in FIG. 5, the magnet attachment member 23 includes a first tube portion 27 and a second tube portion 28 formed on the inner peripheral side of the first tube portion 27 and having a smaller diameter than the first tube portion 27. Have. The first cylinder part 27 and the second cylinder part 28 are formed integrally. The 1st cylinder part 27 has the some holding part 27a for hold | maintaining a magnet in an outer peripheral part. Here, eight holding portions 27a are formed at equal intervals in the circumferential direction. The 2nd cylinder part 28 has the through-hole 28a penetrated to an axial direction, and the engaging part 28b. The support member 22 is attached to the through hole 28a. Thereby, the magnet attachment member 23 is supported by the support member 22, and can be relatively rotated and moved in the axial direction with respect to the outer peripheral portion of the support member 22.

  The engaging portion 28 b is provided on the inner peripheral portion of the second cylinder portion 28. For example, the engaging portion 28b is a protruding portion that protrudes radially inward. The engaging portion 28b is a portion that engages with the engaged portion 22a. When the engaging portion 28 b is engaged with the engaged portion 22 a and the magnet attachment member 23 rotates with respect to the support member 22, the magnet attachment member 23 moves in the axial direction with respect to the support member 22.

  The spring member 24 is a member for biasing the magnet attachment member 23. Specifically, as shown in FIG. 4, the spring member 24 biases the magnet mounting member 23 toward the brake case 20 (left side in FIG. 4). The spring member 24 is disposed between the magnet attachment member 23 and the retaining member 25. More specifically, one end of the spring member 24 is disposed so as to contact the front end portion 28c on the spool 2 side (right side in FIG. 4) of the second cylindrical portion 28 of the magnet mounting member 23. Further, the other end of the spring member 24 is disposed so as to contact the retaining member 25. The spring member 24 is a conical coil spring. The spring member 24 is formed using a nonmagnetic material such as SUS303 so that the spring member 24 is not attracted by the magnet 26.

  The retaining member 25 is a member for retaining the spring member 24. The retaining member 25 is engaged with the support member 22. Specifically, the retaining member 25 has a male threaded portion 25a protruding at one end (left side in FIG. 5), and the male threaded portion 25a is screwed into the female threaded portion 22b of the supporting member 22, thereby supporting the supporting member. 22 is attached.

  The magnet 26 is fixed by being fitted into the holding portion 27 a of the magnet mounting member 23. The magnet 26 is disposed so as to face the inner peripheral surface 14 a of the flange 14 of the spool 2 and the outer peripheral surface 15 a of the annular rib 15. The magnet 26 is composed of, for example, a permanent magnet, and eight magnets 26 are arranged in the circumferential direction with a constant interval. Here, as shown in FIG. 5, the magnet 26 having a substantially rectangular shape with one surface having an N pole and the other surface having an S pole, the magnetic poles of adjacent magnets 26 are alternately arranged with an N pole and an S pole. It is arranged to be.

<Adjustment member 30>
As shown in FIG. 4, the adjustment member 30 is disposed in contact with the support member 22. The adjustment member 30 adjusts the braking force by moving the support member 22 in the axial direction. As shown in FIG. 4, the adjustment member 30 includes a circular knob portion 30 a and a plurality of pressing portions 30 b. The knob portion 30 a is a portion exposed from the opening portion 7 a formed in the first side cover 7. The plurality of pressing portions 30b are provided to protrude on the spool 2 side (right side in FIG. 4) of the knob portion 30a. The pressing portion 30 b passes through the through hole 20 b formed in the brake case 20 and is in contact with the flange portion 22 c of the support member 22. Thereby, the supporting member 22 can be pressed by the pressing portion 30b.

  The knob part 30a is rotatably supported by the opening part 7a. The operation knob 30 has a cam mechanism (not shown) that converts the rotation of the knob portion 30a into the axial movement of the pressing portion 30b. Here, when the operation knob 30 is rotated clockwise, the magnet attachment member 23 and the magnet 26 are moved in a direction approaching the spool 2 that is a conductor via the support member 22 by a cam action. That is, the magnet 21 approaches the spool 2. As a result, the number of magnetic fluxes passing through the inner peripheral surface 14a of the flange portion 14 of the spool 2 and the outer peripheral surface 15a of the annular rib 15 increases, and the braking force against the spool 2 becomes stronger.

  Further, when the operation knob 30 is turned counterclockwise, the magnet mounting member 23 and the magnet 26 are moved in a direction away from the spool 2 as a conductor via the support member 22 by cam action. That is, the magnet 26 is separated from the spool 2. As a result, the number of magnetic fluxes passing through the inner peripheral surface 14a of the flange 14 of the spool 2 and the outer peripheral surface 15a of the annular rib 15 is reduced, and the braking force on the spool 2 is weakened. Thus, the initial braking force of the spool 2 is set by rotating the operation knob 30.

<Operation of braking device 5 during spool rotation>
The braking device 5 applies a force in the direction opposite to the rotation direction to the spool 2 to brake the spool 2. Specifically, when the spool 2 is rotated, the rotation speed of the spool 2 is increased by the magnetic flux of the magnet 26 facing the inner peripheral surface 14a of the flange 14 of the spool 2 and the outer peripheral surface 15a of the annular rib 15 as a conductor. An eddy current corresponding to Due to the generation of this eddy current, a force in the direction opposite to the rotation direction is applied to the spool 2, and the spool 2 is braked. Here, since the magnetic poles of the adjacent magnets 26 are arranged so as to alternate between the N pole and the S pole, the magnetic field of the magnet 26 spreads toward both sides of the flange 14 and the annular rib 15. For this reason, a larger braking force can be obtained.

  Further, the braking device 5 relatively moves the magnet mounting member 23 based on the magnetic force of the magnet 26, and changes the action of the magnetic force according to the movement. Specifically, in a state where the spool 2 is braked by the generation of eddy current, a reaction force corresponding to the braking force acts on the magnet mounting member 23. That is, a rotational force acts on the magnet attachment member 23. Since the engaging portion 28b of the magnet mounting member 23 is engaged with the engaged portion 22a of the support member 22, the magnet mounting member 23 is guided by the engaged portion 22a and moves in the axial direction. . That is, as shown in FIG. 6, the spring member 24 moves in the contracting direction (right side in FIG. 6) while the magnet attachment member 23 rotates with respect to the support member 22 by the reaction force according to the braking force. For this reason, the magnet attachment member 23 comes closer to the spool, and the area (opposing range) of the magnet 26 facing the inner peripheral surface 14a of the flange portion 14 of the spool 2 and the outer peripheral surface 15a of the annular rib 15 increases. Accordingly, the number of magnetic fluxes acting on the inner peripheral surface 14a of the flange portion 14 of the spool 2 and the outer peripheral surface 15a of the annular rib 15 increases, and the braking force also increases.

  Here, as the rotational speed (rotational speed) of the spool 2 increases, the reaction force corresponding to the braking force also increases. Conversely, as the rotational speed (rotational speed) of the spool 2 decreases, the reaction force corresponding to the braking force also increases. Get smaller. Since the magnet mounting member 23 moves in the axial direction in accordance with the rotation of the spool 2, the braking force of the spool 2 is automatically adjusted. As a result, a braking force corresponding to the rotation of the spool 2 can be appropriately applied to the spool 2.

  Further, since the position in the axial direction of the engaged portion 22a of the support member 22 is formed in a curvilinear shape that gradually changes in the circumferential direction, the magnet mounting member 23 rapidly rotates along the high speed rotation of the spool 2. The movement in the direction can be suppressed. That is, it is possible to prevent the braking force acting on the spool 2 from increasing suddenly.

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

  (A) In the above-described embodiment, the spool 2 is used as a conductor. However, the spool 2 is an example of a conductor, and the inner peripheral surface 14a of the flange 14 facing the magnet 26 and the outer peripheral surface 15b of the annular rib 15. May be used as the conductor.

  (B) In the above-described embodiment, the annular rib 15 is provided on the inner peripheral side of the flange portion 14 of the spool 2, but only the inner peripheral surface 14a of the flange portion 14 is opposed to the magnet 26 without providing the annular rib. Also good. Since the flange portion 14 is located away from the rotation center of the spool 2, it is possible to obtain a greater braking force than when the conductor is provided near the rotation center of the spool 2.

  (C) In the above-described embodiment, the eight magnets 26 are installed at equal intervals in the circumferential direction of the magnet mounting member 23, but the number, interval, and shape of the magnets 26 can be arbitrarily set.

DESCRIPTION OF SYMBOLS 1 Reel main body 2 Spool 3 Spool shaft 5 Braking device 11 Bobbin trunk part 11a, 11b Through-hole 12 1st flange part 13 2nd flange part 14 ridge part 15 Annular rib 23 Magnet attachment member 26 Magnet 30 Adjustment member

Claims (6)

The reel body,
A spool shaft rotatably supported by the reel body;
A bobbin trunk capable of winding a fishing line around its outer periphery, a first flange formed at one end of the bobbin trunk with a larger diameter than the bobbin trunk, and a bobbin trunk at the other end of the bobbin trunk A spool that has a second flange portion that is also formed with a large diameter, and a flange portion that extends further in the axial direction from the tip of only the first flange portion, and is rotatably mounted on the spool shaft;
A braking device having a magnet disposed opposite to the inner peripheral surface of the flange, and braking the spool by a magnetic force of the magnet with respect to the flange;
Double-bearing reel equipped with. The spool further includes an annular rib that extends in the axial direction from one of the bobbin trunk or the first flange and is formed on the inner peripheral side of the flange.
The magnet is disposed between the flange and the annular rib,
The dual-bearing reel according to claim 1, wherein the braking device brakes the spool by a magnetic force applied to the flange portion and the annular rib of the magnet.   The double-bearing reel according to claim 1, wherein the bobbin trunk has a plurality of through holes.   The double-bearing reel according to any one of claims 1 to 3, wherein the braking device includes a magnet mounting member for mounting the magnet.   The double bearing according to claim 4, wherein the braking device relatively moves the magnet mounting member based on the magnetic force, and changes the action of the magnetic force on the spool in accordance with the movement of the magnet mounting member. reel.   The dual-bearing reel according to claim 4, wherein the braking device further includes an adjusting member that adjusts a braking force by moving the magnet mounting member in an axial direction.

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