JP2014200227A - Spool brake device for dual-bearing reel and dual-bearing reel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable a spool brake device for a dual-bearing reel to adjust braking force over a wide range and appropriately apply to a spool a braking force according to the spool rotation.SOLUTION: A spool brake structure 20 comprises a spool brake mechanism 23 having conductor parts 12, 50 rotating interlocked with a spool 12; and a magnet 51 radially opposable to the conductor parts 12, 50. The spool brake mechanism 23 applies brakes to the rotation of the spool 12 on the basis of the magnetic force of the magnet 51 acted on the conductor body 12, 50. A spool braking force adjustment mechanism 64 adjusts the braking force on the spool 12 by the changes of the magnetic force of the magnet 51 acted on the conductor parts 12, 50. In this configuration, at least one of the magnet 51 and the conductor part 12, 50 has magnetic force changing means for changing the magnetic force of the magnet 51 acted on the spool 12, 50 in a move direction in which the magnet 51 moves relative to the spool 12, 50.

Description

  The present invention relates to a spool brake device, and more particularly to a spool brake device for a dual-bearing reel that brakes the rotation of the spool of the dual-bearing reel. The present invention also relates to a dual bearing reel.

  In double-bearing reels used for lure fishing, backlash may occur in which the rotational speed of the spool is faster than the yarn unwinding speed during casting. When backlash occurs, the fishing line sags, or so-called dandruff, which causes thread sag. Therefore, an electromagnetic brake as disclosed in Patent Document 1 is provided. In this electromagnetic brake, it is possible to apply a braking force to the spool and adjust the braking force.

  The electromagnetic brake of Patent Document 1 has a cylindrical magnet support frame. A plurality of magnets are arranged in the circumferential direction on the magnet support frame. The magnetic pole surfaces of the plurality of magnets are arranged at a predetermined distance (opposite) from the side wall of the spool. By moving the magnet support frame in the spool axial direction, the distance between the magnetic pole surface of the magnet and the spool side wall is changed. Thereby, the braking force of the spool is adjusted.

  The axial position of the magnet support frame is determined by a cam groove formed on the outer peripheral surface of the magnet support frame and a guide protrusion that engages with the cam groove. Specifically, the magnet support frame is rotatable within a predetermined angle range, and rotates in accordance with the rotation speed of the spool. This rotation of the magnet support frame is converted into an axial movement of the magnet support frame by the engagement of the cam groove and the guide projection. The distance between the magnetic pole surface of the magnet supported by the magnet support frame and the spool side wall is adjusted by the movement of the magnet support frame in the axial direction. That is, the braking force of the spool is adjusted.

Japanese Examined Patent Publication No. 4-68892

  Since the spool braking device of Patent Document 1 is for adjusting a minute gap between the magnetic pole surface of the magnet and the side wall of the spool that are arranged to face each other, the range in which the braking force can be adjusted is narrow. If the movement stroke of the magnet support frame is increased in order to widen the adjustment range, the apparatus is increased in size. Further, in the configuration for adjusting the braking force shown in Patent Document 1, the magnet support frame easily moves in the axial direction following the high-speed rotation of the spool, and the braking force of the spool increases rapidly. With such a configuration, there is a possibility that the flight distance may not be extended during casting.

  An object of the present invention is to enable a braking force to be adjusted over a wide range in a spool braking device for a dual-bearing reel and to appropriately apply a braking force according to the rotation of the spool to the spool.

  A spool brake device for a dual-bearing reel according to a first aspect is a device that brakes rotation of a spool that is rotatably mounted on a reel body of the dual-bearing reel. This spool braking device includes braking means and braking force adjusting means. The braking means includes a conductor portion that rotates in conjunction with the spool, and a magnet portion that can face the conductor portion in the radial direction. The braking means brakes the rotation of the spool based on the magnetic force of the magnet portion acting on the conductor portion. The braking force adjusting means moves the magnet portion relative to the conductor portion to adjust the braking force against the rotation of the spool. Here, at least one of the magnet part and the conductor part has a magnetic force changing means. The magnetic force changing means changes the magnetic force of the magnet part acting on the conductor part in the moving direction in which the magnet part moves relative to the conductor part.

  In this spool braking device, in the braking means, when the conductor portion rotates in the braking means in a state where the magnet portion and the conductor portion face each other in the radial direction, the magnetic force of the magnet portion acting on the conductor portion The spool rotation is braked. In the braking force adjusting means, the braking force against the rotation of the spool is adjusted by moving the magnet portion relative to the conductor portion. Furthermore, in the magnetic force changing means, the magnetic force of the magnet part acting on the conductor part is changed in the moving direction in which the magnet part moves relative to the conductor part. The magnetic force changing means is included in at least one of the magnet part and the conductor part.

  Thus, in this spool braking device, the magnetic force acting on the conductor portion is changed by moving the magnet portion by the braking force adjusting means, and the braking force of the spool is adjusted. Thereby, in this spool braking device, the braking force of the spool can be adjusted smoothly and in a wide range as compared with the prior art, for example, a device that adjusts the distance between the facing magnet portion and the conductor portion.

  In addition, at least one of the magnet part and the conductor part has a magnetic force change means, and the magnetic force change means has a conductor in the moving direction in which the magnet part moves relative to the conductor part. The magnetic force of the magnet part acting on the part is changed. In this configuration, the braking force can be changed smoothly compared to a configuration in which the change in magnetic force acting on the conductor portion is uniform. For example, even if the rotation of the spool increases, it is possible to suppress a sudden increase in the braking force of the spool. Thus, in the present spool braking device, a braking force according to the rotation of the spool can be appropriately applied to the spool.

  In the spool brake device for a dual-bearing reel according to a second aspect, in the spool brake device according to the first aspect, the magnetic force changing means is provided in the magnet portion. The magnet part has a first magnetic part and a second magnetic part with a small magnetic force generated from the first magnetic part. The first magnet part and the second magnet part are provided along the moving direction.

  In the spool braking device, the first magnetic part and the second magnetic part with a small magnetic force generated from the first magnetic part are provided along the moving direction. Thereby, when the magnet part moves along the moving direction, the magnetic force of the magnet part acting on the conductor part can be changed, so that the braking force can be changed smoothly. For example, as the rotation of the spool increases, the braking force of the spool increases rapidly by changing the magnet portion facing the conductor portion from the first magnetic portion to the first magnetic portion and the second magnetic portion. This can be suppressed. Thus, in the present spool braking device, a braking force according to the rotation of the spool can be appropriately applied to the spool.

  In the spool brake device for a dual-bearing reel according to a third aspect, in the spool brake device according to the first or second aspect, the first magnetic part has a first facing surface that can face the conductive part. The second magnetic part can be opposed to the conductive part and has a second opposing surface that is smaller than the first opposing surface.

  In this spool braking device, when the magnet portion moves in the moving direction, the magnetic force of the magnet portion acting on the conductor portion can be changed, so that the braking force can be changed smoothly. For example, as the rotation of the spool increases, the braking force of the spool increases abruptly by changing the facing surface facing the conductor portion from the first facing surface to the first facing surface and the second facing surface. This can be suppressed. Thus, in the present spool braking device, a braking force according to the rotation of the spool can be appropriately applied to the spool.

A spool brake device for a dual-bearing reel according to a fourth aspect of the present invention is the spool brake device according to any one of the first to third aspects, wherein the magnetic force changing means is provided in the magnet portion, and the magnetic force of the magnet portion moves in the magnetic force changing means. It changes continuously along the direction.
In this spool braking device, in the magnetic force changing means provided in the magnet portion, the magnetic force of the magnet portion changes continuously along the moving direction, so that the braking force can be changed smoothly. For example, when the magnet portion moves as the spool rotates, it is possible to suppress a sudden increase in the braking force of the spool by continuously reducing the magnetic force of the magnet portion. Thus, in the present spool braking device, a braking force according to the rotation of the spool can be appropriately applied to the spool.

A spool brake device for a dual-bearing reel according to a fifth aspect of the present invention is the spool brake device according to any one of the first to fourth aspects, wherein the magnetic force changing means is provided in the conductor portion. The conductor part has a first conductor part and a second conductor part that is less affected by the magnetic force received from the magnet part than the first conductor part. The first conductor portion and the second conductor portion are provided along the moving direction.
In this spool braking device, when the magnet portion moves along the moving direction, the influence of the magnetic force that the conductor portion receives from the magnet portion can be changed when the magnet portion moves along the moving direction. Can be changed smoothly. For example, as the rotation of the spool increases, the spool braking force is rapidly increased by changing the conductor portion facing the magnet portion from the first conductor portion to the first conductor portion and the second conductor portion. Can be suppressed. Thus, in the present spool braking device, a braking force according to the rotation of the spool can be appropriately applied to the spool.

In the spool brake device for a dual-bearing reel according to a sixth aspect, in the spool brake device according to the fifth aspect, the first conductive portion has a third facing surface that can face the magnet portion. Moreover, the 2nd electroconductive part can oppose a magnet part, and has a 4th opposing surface separated from the magnet part from the 3rd opposing surface.
In this spool braking device, when the magnet portion moves along the moving direction, the interval between the magnet portion and the conductor portion can be changed. That is, the influence of the magnetic force that the conductor portion receives from the magnet portion can be changed. Thereby, the braking force can be changed smoothly.
For example, as the rotation of the spool increases, the braking force of the spool increases rapidly by changing the conductor portion facing the magnet portion from the third facing surface to the third facing surface and the fourth facing surface. This can be suppressed. Thus, in the present spool braking device, a braking force according to the rotation of the spool can be appropriately applied to the spool.

In the spool brake device for a dual-bearing reel according to a seventh aspect, in the spool brake device according to the fifth or sixth aspect, the magnetic force changing means is provided in the conductor portion, and the distance from the magnet portion is continuously along the moving direction. To change.
In this spool braking device, the distance between the magnetic force changing means provided in the conductor portion and the magnet portion continuously changes along the moving direction, so that the braking force can be changed smoothly. For example, when the magnet portion moves as the rotation of the spool increases, it is possible to suppress a sudden increase in the braking force of the spool by continuously reducing the distance. Thus, in the present spool braking device, a braking force according to the rotation of the spool can be appropriately applied to the spool.

  According to a spool brake device for a dual-bearing reel according to an eighth aspect of the present invention, in the spool brake device according to any one of the first to seventh aspects, the spool is a conductor portion. The spool is made of metal. In this case, the whole number of parts can be reduced by using the spool itself as the conductor portion.

  The spool brake device for a dual-bearing reel according to a ninth aspect is the spool brake device according to any one of the first to seventh aspects, wherein the conductor is a metal member fixed to the spool. In this case, the conductor portion, that is, the cylindrical member can be easily attached.

  The dual-bearing reel according to the tenth aspect is a dual-bearing reel that is attached to a fishing rod and feeds and winds the fishing line. The double-bearing reel includes a reel body, a spool, and a spool braking device. The reel body is attached to a fishing rod. The spool is rotatably supported by the reel body and winds the fishing line around the outer periphery. The spool braking device is the device described in any one of the first to ninth aspects of the present invention. With this dual-bearing reel, it is possible to obtain the same effects as those shown in the first to ninth aspects of the invention.

  According to the present invention, in the spool braking device for a dual-bearing reel, the braking force can be adjusted over a wide range, and the braking force according to the rotation of the spool can be appropriately applied to the spool.

The perspective view of the double bearing reel which employ | adopted 1st Embodiment of this invention. Sectional drawing which shows the structure inside the reel main body of the said double bearing reel. The expanded sectional view of the spool braking device of the said double bearing reel. The expanded sectional view of the spool braking device when the second cylinder part moves in the axial direction. The expansion exploded perspective view of the important section of the spool braking device. The expansion perspective view of the 1st cylinder part. Curves showing the relationship between the number of rotations of the spool and the spool braking force in each shape of the engaged portion of the first cylindrical portion (note that the present invention is graph A, the second embodiment is graph B, and the third embodiment is An example is shown in graph C). The figure equivalent to FIG. 4 of 2nd Embodiment. The figure equivalent to FIG. 5 of 2nd Embodiment. The figure equivalent to FIG. 3 of 3rd Embodiment. The figure equivalent to FIG. 3 of other embodiment. The figure equivalent to FIG. 3 of other embodiment. The figure equivalent to FIG. 3 of other embodiment.

[First Embodiment]
<Overall configuration of dual-bearing reel>
FIG. 1 shows a dual-bearing reel in which an embodiment of the present invention is adopted. This dual-bearing reel is a bait reel mainly used for lure fishing. The dual-bearing reel includes a reel body 1, a spool rotation handle 2 disposed on the side of the reel body, and a drag drag adjusting star drag 3 disposed on the reel body 1 side of the handle 2. Yes. The handle 2 is a double handle type. The handle 2 has a plate-like arm portion 2a and a pair of handle portions 2b that are rotatably attached to both ends of the arm portion 2a. The outer side surface of the arm portion 2a of the handle 2 is configured with a smooth surface without a joint, and has a shape in which a fishing line is not easily entangled.

  As shown in FIGS. 1 and 2, the reel body 1 includes a frame 5, a first side cover 6 and a second side cover 7 mounted on both sides of the frame 5, and a thumb rest mounted on the upper portion of the frame 5. 10. The frame 5 includes a pair of first side plate 8 and second side plate 9 arranged so as to face each other with a predetermined interval therebetween, and a plurality of unillustrated links that connect the first side plate 8 and the second side plate 9. And a connecting portion.

  The second side cover 7 on the handle 2 side is detachably fixed to the second side plate 9 with screws. An opening 8a through which the spool 12 can pass is formed in the first side plate 8 opposite to the handle 2. A brake case 55 is fixed to the first side cover 6 opposite to the handle 2 by screws.

  As shown in FIG. 2, a spool 12, a level wind mechanism 15, and a clutch operation lever 17 are disposed in the frame 5. The level wind mechanism 15 is a mechanism for uniformly winding the fishing line around the spool 12. The clutch operating lever 17 serves as a thumb rest for summing.

  A gear mechanism 18, a clutch mechanism 13, a clutch engagement / disengagement mechanism 19, a drag mechanism 21, and a casting control mechanism 22 are disposed between the frame 5 and the second side cover 7. . The gear mechanism 18 transmits the rotational force from the handle 2 to the spool 12 and the level wind mechanism 15. The clutch engagement / disengagement mechanism 19 engages / disengages the clutch mechanism 13 in accordance with the operation of the clutch operation lever 17. The drag mechanism 21 brakes the spool 12 when the yarn is fed. The casting control mechanism 22 brakes with the spool shaft 16 sandwiched between both ends. A spool braking structure 20 for suppressing backlash during casting is disposed in the opening 8a.

  The spool 12 is made of, for example, an aluminum alloy and is a nonmagnetic electric conductor. Here, the spool 12 corresponds to a conductor 50 described later. As shown in FIGS. 2 to 4, the spool 12 has dish-shaped flange portions 12 a on both sides. Moreover, the spool 12 has a cylindrical bobbin trunk 12b between both flanges 12a. The spool 12 has a connecting portion 12d that connects the flange portion 12a and the bobbin trunk 12b. The bobbin trunk 12b (an example of the first conductor part) and the connecting part 12d (an example of the second conductor part) constitute magnetic force changing means described later.

  Further, the spool 12 has a cylindrical boss portion 12c integrally formed on the inner peripheral side of the bobbin trunk 12b. The spool 12 is fixed to the spool shaft 16 penetrating the boss portion 12c so as not to rotate, for example, by serration coupling.

  The spool shaft 16 extends through the second side plate 9 to the outside of the second side cover 7. One end of the spool shaft 16 is rotatably supported by a bearing 35 b with respect to a boss portion 29 formed on the second side cover 7. Further, the other end of the spool shaft 16 is rotatably supported by a bearing 35 a in the inner cylinder portion 55 a of the brake case 55.

  As shown in FIG. 2, the level wind mechanism 15 includes a guide cylinder 25 fixed between a pair of the first side plate 8 and the second side plate 9, and a screw shaft 26 rotatably disposed in the guide cylinder 25. And a line guide 27. A gear 28 a constituting the gear mechanism 18 is fixed to the end of the screw shaft 26. The screw shaft 26 is formed with a spiral groove 26a. A line guide 27 is engaged with the spiral groove 26a. For this reason, the line guide 27 is reciprocated by the guide cylinder 25 when the screw shaft 26 is rotated via the gear mechanism 18. A fishing line is inserted into the line guide 27, and the fishing line is uniformly wound around the spool 12.

  The gear mechanism 18 is rotatably mounted on the handle shaft 30 and the rotation of the handle shaft 30 is transmitted via the drag mechanism 21, the cylindrical pinion gear 32 that meshes with the drive gear 31, and the screw described above. A gear 28a fixed to the end of the shaft 26 and a gear 28b fixed to the handle shaft 30 so as not to rotate and meshing with the gear 28a are provided.

  The pinion gear 32 is disposed through the second side plate 9. The pinion gear 32 is a cylindrical member. The spool shaft 16 is inserted through the center of the pinion gear 32. The pinion gear 32 is attached to the spool shaft 16 so as to be movable in the axial direction. The pinion gear 32 has a tooth portion 32a formed on the outer periphery of the right end portion in FIG. 2 and meshing with the drive gear 31, and a meshing portion 32b formed on the other end side. A constricted portion 32c is provided between the tooth portion 32a and the meshing portion 32b.

  The meshing portion 32 b is configured by a concave groove formed on the end surface of the pinion gear 32. A clutch pin 16a that penetrates the spool shaft 16 in the radial direction is connected to the concave groove. Here, when the pinion gear 32 moves outward, the concave groove of the meshing portion 32b and the clutch pin 16a of the spool shaft 16 are disengaged and the connection is released, the rotation from the handle shaft 30 causes the spool shaft 30 to rotate. 12 is not transmitted. The clutch mechanism 13 is configured by the concave groove of the meshing portion 32b and the clutch pin 16a.

  The clutch operating lever 17 is disposed behind the spool 12 at the rear portion between the pair of first side plate 8 and second side plate 9. Long holes (not shown) are formed in the first side plate 8 and the second side plate 9 of the frame 5. A clutch cam (not shown) that fixes the clutch operation lever 17 passes through the long hole. The clutch operating lever 17 slides up and down along the long hole. The clutch engagement / disengagement mechanism 19 has a clutch yoke 40. The clutch engagement / disengagement mechanism 19 moves the clutch yoke 40 in parallel with the axis of the spool shaft by the rotation of the clutch operation lever 17. The clutch engagement / disengagement mechanism 19 moves the clutch yoke 40 so that the clutch mechanism 13 is automatically turned on when the handle shaft 30 rotates in the yarn winding direction.

  In such a configuration, in the normal state, the pinion gear 32 is located at the inner clutch engagement position. At this clutch engagement position, the meshing portion 32b of the pinion gear 32 and the clutch pin 16a of the spool shaft 16 are engaged, and the clutch is on. On the other hand, when the pinion gear 32 is moved outward by the clutch yoke 40, the engagement portion 32b is disengaged from the clutch pin 16a, and the clutch is turned off.

  The casting control mechanism 22 is attached to a bottomed cylindrical cap 45 that is screwed into a male screw portion formed on the outer peripheral side of the boss portion 29, a friction plate 46 attached to the bottom portion of the cap 45, and a brake case 55. The friction plate 47 is provided. The friction plate 46 and the friction plate 47 are in contact with both ends of the spool shaft 16 and sandwich the spool shaft 16. For example, when the cap 45 is rotated, the clamping force generated by the friction plate 46 and the friction plate 47 is adjusted. Thereby, the braking force of the spool 12 is adjusted.

As shown in FIG. 3, the brake case 55 is a bottomed cylindrical case member. The outer periphery of the brake case 55 is attached to the opening 8 a of the first side plate 8 by the bayonet structure 14. At the center of the brake case 55 on the spool 12 side (right side in FIG. 4), there is an inner cylinder portion 55a that protrudes in a cylindrical shape. The 1st cylinder part 60 is mounted | worn with the outer peripheral part of the inner cylinder part 55a. The inner peripheral part of the inner cylinder part 55a supports the outer ring of the bearing 35a. A plurality of through holes 55b are formed in the outer peripheral portion of the base end portion of the inner cylinder portion 55a. A pressing portion 65b (described later) of the operation knob 65 is inserted into the through hole 55b.

  As shown in FIGS. 3 and 4, the operation knob 65 includes a circular knob portion 65a and a plurality of pressing portions 65b. The knob portion 65 a is a portion exposed from the opening 6 a formed in the first side cover 6. The plurality of pressing portions 65b are provided so as to protrude to the spool 12 side (right side in FIGS. 3 and 4) of the knob portion 65a. The pressing portion 65b is inserted through the through hole 55b and abuts on the flange portion 60c of the first cylindrical portion 60 so as to be able to press the first cylindrical portion 60.

  The knob portion 65a is rotatably supported by the opening 6a. The operation knob 65 has a cam mechanism (not shown) that converts the rotation of the knob portion 65a into the axial movement of the pressing portion 65b. Here, when the operation knob 65 is rotated clockwise, a cam action causes a second cylinder portion 61 and a magnet 51 (to be described later) to approach the spool 12 via the first cylinder portion 60 (right side in FIG. 3). Moving. That is, the magnet 51 approaches the spool 12 (conductor 50 described later). As a result, the number of magnetic fluxes passing through the spool 12 increases, and the braking force on the spools 12 and 50 increases.

  Further, when the operation knob 65 is turned counterclockwise, the second cylinder portion 61 and the magnet 51 are moved in the direction away from the spool 12 (left side in FIG. 3) via the first cylinder portion 60 by cam action. . That is, the magnet 51 is separated from the spool 12. As a result, the number of magnetic fluxes passing through the spool 12 is reduced and the overall braking force is weakened.

  Thus, the initial braking force of the spool 12 is set by rotating the operation knob 65.

<Configuration of spool braking structure>
The spool braking structure 20 is for braking the rotation of the spool 12 rotatably mounted on the reel body 1 of the dual-bearing reel. Specifically, the spool braking structure 20 brakes the rotation of the spool 12 based on the magnetic force of a magnet 51 (described later) acting on the spool 12 (corresponding to a conductor 50 described later). As a result, a force (braking force) in the direction opposite to the rotation direction is applied to the spool 12 that is the conductor 50. By braking the spool 12 in this manner, for example, backlash during casting is suppressed.

  As shown in FIGS. 3 and 4, the spool braking structure 20 is disposed on the side of the reel body 1. Specifically, the spool braking structure 20 is disposed in an opening 8 a formed in the first side plate 8 opposite to the handle 2. The spool braking structure 20 includes a spool braking mechanism 23 and a spool braking force adjusting mechanism 64.

<Configuration of spool braking mechanism>
As illustrated in FIGS. 3 to 5, the spool braking mechanism 23 includes a conductor 50 that rotates in conjunction with the spool 12 and a magnet 51 that can face the conductor 50.

  The conductor 50 rotates in conjunction with the spool 12. Here, the conductor 50 corresponds to the spool 12 made of aluminum alloy. Specifically, the inner peripheral portion of the cylindrical bobbin trunk 12 b on the first side plate 8 side (left side in FIG. 3) of the spool 12 mainly corresponds to the conductor 50. Hereinafter, the “conductor 50” is referred to as “spool 12, 50”. The spools 12 and 50 are nonmagnetic electric conductors.

  The conductor 50 has magnetic force changing means that includes a bobbin trunk 12b (an example of a first conductor part) and a connecting part 12d (an example of a second conductor part). The magnetic force changing means 12b and 12d change the magnetic force of the magnet 51 acting on the conductor 50 in the direction in which the magnet 51 moves (moving direction), for example, the direction in which the spool shaft 16 extends. In the magnetic force change means 12b, 12d, the distance from the magnet 51 continuously changes along the moving direction of the magnet 51.

  The bobbin trunk 12b included in the magnetic force changing means is formed in a cylindrical shape. The bobbin trunk 12 b has a facing surface 112 b (an example of a third facing surface) that can face the magnet 51. The facing surface 112b is provided on the inner peripheral surface of the bobbin trunk 12b. The distance between the opposing surface 112b and the magnet 51 is substantially constant.

  The connecting portion 12d included in the magnetic force changing means is formed in a cylindrical shape. The connecting portion 12d is formed integrally with the bobbin trunk 12b. Specifically, the connecting portion 12d is integrally formed with the bobbin trunk 12b so as to increase in diameter from the bobbin trunk 12b toward the opening (flange 12a). In other words, the connecting portion 12d is integrally formed with the bobbin trunk 12b so as to reduce the diameter from the opening (flange portion 12a) toward the bobbin trunk 12b.

  More specifically, the connecting portion 12d has a facing surface 112d (an example of a fourth facing surface) that can face the magnet 51. The opposing surface 112d is provided on the inner peripheral surface of the connecting portion 12d. The distance between the facing surface 112d and the magnet 51 is substantially changed. The facing surface 112d is formed in a curved shape that protrudes toward the spool shaft from the flange portion 12a toward the bobbin trunk 12b. For example, the opposing surface 112d is enlarged in diameter from the bobbin trunk 12b toward the opening (flange 12a). In other words, the opposing surface 112d is reduced in diameter from the opening (flange portion 12a) toward the bobbin trunk 12b. With this configuration, the radial space between the connecting portion 12d and the magnet 51 changes in the moving direction of the magnet 51 (the direction in which the spool shaft 16 extends).

  As shown in FIGS. 3 and 4, the magnet 51 is provided so as to face the spools 12 and 50. The magnet 51 is movable in a direction along the spool shaft 16. The magnet 51 is disposed on the inner peripheral side of the spools 12 and 50. Specifically, the magnet 51 is disposed on the inner peripheral side of the connecting portion 12 d of the spools 12 and 50. Thereby, the magnetic field of the magnet 51 acts on the spools 12 and 50, for example, the connecting portions 12d of the spools 12 and 50. The magnet 51 brakes the rotation of the spools 12 and 50 by applying a magnetic force to the spools 12 and 50.

  As shown in FIG. 5, the magnet 51 is fixed to the outer peripheral portion of the second cylindrical portion 61 described later. The magnet 51 is composed of, for example, eight rectangular plate-shaped permanent magnets. The magnets 51 are arranged at eight locations at equal intervals in the circumferential direction on the outer peripheral portion of the second cylindrical portion 61.

  In this state, when the spools 12 and 50 rotate, an eddy current corresponding to the number of rotations of the spools 12 and 50 is generated. Due to the generation of the eddy current, a force in the direction opposite to the rotation direction is applied to the spools 12 and 50. Thereby, the spools 12 and 50 are braked. That is, when the spools 12 and 50 are rotated in a state where the magnets 51 and the spools 12 and 50 face each other in the radial direction, the spools 12 and 50 are braked.

<Configuration of spool braking force adjustment mechanism>
The spool braking force adjusting mechanism 64 is for adjusting the braking force of the spools 12 and 50 according to the rotation of the spools 12 and 50. The spool braking force adjusting mechanism 64 adjusts the braking force of the spools 12 and 50 by moving the magnet 51 relative to the spools 12 and 50. As a result, the braking force against the rotation of the spools 12 and 50 is adjusted.

  The spool braking force adjusting mechanism 64 includes a cylindrical first cylindrical portion 60, a cylindrical second cylindrical portion 61, a spring member 62, and a retaining member 63.

  As shown in FIGS. 3 to 5, the first cylindrical portion 60 is provided on the reel body 1. Specifically, the first cylinder portion 60 is attached to the outer peripheral portion of the inner cylinder portion 55a of the brake case 55. More specifically, the inner peripheral portion of the first cylindrical portion 60 is attached to the outer peripheral portion of the inner cylindrical portion 55 a of the brake case 55.

  The 1st cylinder part 60 has the to-be-engaged part 60a. The engaged portion 60 a guides the magnet 51 relative to the spools 12 and 50. The engaged portion 60a is formed in a curved shape that gradually changes in the axial direction with respect to changes in the circumferential direction. More specifically, the engaged portion 60a is formed in a curved shape in which the change in the axial direction gradually increases with respect to the change in the circumferential direction. The engaged portion 60a is formed along a multi-degree curve, for example, a quadratic curve. The engaged portion 60a is, for example, a groove formed in a curved shape.

  The multi-order curve is a word meaning a curve having a plurality of orders. The multi-order curve is defined by a first reference axis X that extends in the axial direction on the outer peripheral surface of the first cylindrical portion 60 and a second reference axis Y that extends in the circumferential direction on the outer peripheral surface of the first cylindrical portion 60 (see FIG. 6).

  Moreover, in the 1st cylinder part 60, the internal thread part 60b is formed in the front-end | tip inner peripheral part by the side of the spools 12 and 50 (FIG. 3 right side). A male screw portion 63a formed on the outer periphery of the brake case 55 side (left side in FIG. 3) of the retaining member 63 is screwed into the female screw portion 60b. As a result, the retaining member 63 is attached to the first cylindrical portion 60. A large-diameter flange portion 60c is formed at the end of the first cylinder portion 60 on the brake case 55 side (left side in FIG. 3), and a pressing portion 65b of an operation knob 65 described later is in contact therewith.

  When the second cylindrical portion 61 moves in the axial direction, the magnet 51 is moved away from the non-opposing position (position in FIG. 3) not facing the inner periphery of the bobbin trunk 12b of the spool 12, 50, and the spool 12, It can move between opposing positions (positions in FIG. 4) facing the inner peripheral part of 50 bobbin trunks 12b. Specifically, at the facing position shown in FIG. 4, about 2/3 of the axial length of the magnet 51 faces the inner peripheral portion of the connecting portion 12 d of the spools 12 and 50. A range of about 2/3 of the axial length of the magnet 51 is a range of the portion where the magnet 51 faces the bobbin trunk 12b of the spools 12 and 50 (opposing range; facing area). Therefore, compared with the non-opposing position shown in FIG. 3, the number of magnetic fluxes acting on the spools 12 and 50 is increased at the facing position shown in FIG. 3, and the braking force for braking the rotation of the spools 12 and 50 is large. Become.

  As shown in FIGS. 3 to 6, the second cylindrical portion 61 is attached to the outer peripheral portion of the first cylindrical portion 60 so as to be capable of relative rotation and axial movement. Further, the second cylinder portion 61 is movable in the axial direction in accordance with the rotation with respect to the first cylinder portion 60.

  The second cylinder part 61 has a holding part 61 b for holding the magnet 51. The holding portions 61 b are formed at eight locations on the outer peripheral portion of the second cylinder portion 61. A magnet 51 is attached and fixed to each holding portion 61b. For example, each holding portion 61b is formed so that the outer peripheral surface of the second cylindrical portion 61 and the outer peripheral surface of the magnet 51 are flush with each other. More specifically, each holding portion 61 b is formed in a concave shape so that the outer peripheral surface of the second cylindrical portion 61 becomes a smooth peripheral surface in a state where the magnet 51 is mounted on the second cylindrical portion 61.

  The 2nd cylinder part 61 has the engaging part 61a. The engaging portion 61a is a portion that engages with the engaged portion 60a. The engaging portion 61a is engaged with and guided by the engaged portion 60a so that the second cylindrical portion 61 can rotate relative to the first cylindrical portion 60 and can move in the axial direction.

  The engaging part 61 a is provided on the inner peripheral part of the second cylinder part 61. For example, the engaging portion 61 a is a protruding portion that protrudes inward at the inner peripheral portion of the second cylindrical portion 61 on the spool 12, 50 side (right side in FIG. 3). The engaging portion 61 a (protruding portion) of the second cylindrical portion 61 is engaged with the engaged portion 60 a formed in a quadratic curve shape on the first cylindrical portion 60 according to the rotation of the second cylindrical portion 61. Move while meeting.

  The spring member 62 is a member for biasing the second cylindrical portion 61. Specifically, the spring member 62 urges the second cylindrical portion 61 toward the brake case 55 (left side in FIG. 3) as shown in FIGS. The spring member 62 is disposed so as to come into contact with the tip of the second cylinder portion 61 on the spool 12, 50 side (right side in FIG. 3). The spring member 62 is disposed between the retaining member 63 and the second cylindrical portion 61. Specifically, the spring member 62 is a conical coil spring. The spring member 62 is formed using a nonmagnetic material such as SUS303 so as not to be attracted by the magnet 51.

  The retaining member 63 is a member for retaining the spring member 62. As shown in FIGS. 3 to 5, the retaining member 63 is attached to the distal end portion of the first cylindrical portion 60 on the spool 12, 50 side (right side in FIG. 3). Here, the retaining member 63 is formed by screwing a male threaded portion 63a formed on the outer periphery of the brake case 55 side (left side in FIG. 3) of the retaining member 63 into the female threaded portion 60b of the first cylindrical portion 60. Is attached to the first tube portion 60.

<Operation of double-bearing reel>
Next, the operation of the reel will be described in detail. In a normal state, the clutch yoke 40 is pushed inward and is in a clutch-on state. As a result, the rotational force from the handle 2 is transmitted to the spools 12 and 50 via the handle shaft 30, the drive gear 31, the pinion gear 32, and the spool shaft 16. That is, when the handle 2 is rotated, the spools 12 and 50 are rotated in the yarn winding direction.

  When casting is performed, in order to suppress backlash, the operation knob 65 is rotated to adjust the initial braking force. In order to suppress the entire braking force, the operation knob 65 is turned counterclockwise to move the magnet 51 away from the spools 12 and 50. When the operation knob 65 is rotated counterclockwise, the magnet 51 moves in a direction away from the spools 12 and 50 by the cam action. As a result, the number of magnetic fluxes passing through the spools 12, 50 is reduced, and the overall braking force is weakened.

  On the other hand, when it is desired to increase the overall braking force, the operation knob 65 is turned clockwise to bring the magnet 51 closer to the spools 12 and 50. When the operation knob 65 is rotated clockwise, the magnet 51 moves in a direction approaching the spools 12 and 50 by cam action. As a result, the number of magnetic fluxes passing through the spools 12 and 50 increases, and the overall braking force becomes stronger.

  Subsequently, the clutch operating lever 17 is pushed downward. The movement of the clutch operating lever 17 moves the clutch yoke 40 outward, and the pinion gear 32 moves in the same direction. As a result, the clutch is turned off. In this clutch-off state, the rotation from the handle shaft 30 is not transmitted to the spools 12, 50 and the spool shaft 16, and the spools 12, 50 can freely rotate. In the clutch-off state, the thumb placed on the clutch operating lever 17 is summed with the spool, and when the reel is tilted in the axial direction so that the spool shaft 16 follows the vertical plane, the lure is thrown and the spool 12 is thrown. , 50 rotate in the yarn feeding direction.

  Here, when the spools 51 and 50 are rotated as described above in a state where the magnet 51 is at the facing position (the position in FIG. 4), a braking force is applied to the spools 12 and 50. Thus, in the state in which the spools 12 and 50 are braked, a reaction force corresponding to the braking force acts on the second cylinder portion 61 (magnet 51). By this reaction force, the second cylinder portion 61 and the magnet 51 rotate, and the second cylinder portion 61 and the magnet 51 move in the axial direction toward the spools 12 and 50 (right side in FIG. 4).

  For example, as the number of rotations (rotational speed) of the spools 12 and 50 increases, the reaction force corresponding to the braking force also increases, and the second cylindrical portion 61 is drawn into the inner peripheral portion of the spools 12 and 50. As a result, the number of magnetic fluxes acting on the spools 12 and 50 increases and the braking force becomes stronger. On the other hand, as the rotational speed (rotational speed) of the spools 12 and 50 decreases, the reaction force corresponding to the braking force also decreases. In this case, the second cylinder portion 61 is moved in a direction away from the spools 12 and 50 by the spring member 62. As a result, the number of magnetic fluxes acting on the spools 12, 50 is reduced, and the braking force is weakened. In this manner, the braking force of the spools 12 and 50 is automatically adjusted according to the rotation of the spools 12 and 50.

  As described above, in the double-bearing reel having the spool braking structure 20, the second cylindrical portion 61 rotates by the reaction force corresponding to the braking force of the spools 12 and 50. Then, the engaging part 61a (protrusion part) of the 2nd cylinder part 61 moves along the to-be-engaged part 60a (groove part of a quadratic curve shape) of the 1st cylinder part 60. FIG. Then, the second cylinder part and the magnet 51 move in the axial direction, and the number of magnetic fluxes acting on the spools 12 and 50 changes. In this way, the braking force of the spools 12, 50 is automatically adjusted according to the rotation of the spools 12, 50.

  In the spool braking structure 20 that operates as described above, the braking force of the spools 12 and 50 is adjusted by changing the area of the magnet 51 facing the spools 12 and 50 according to the rotation of the spools 12 and 50. Yes. For this reason, in the spool braking structure 20, the braking force of the spools 12 and 50 can be adjusted smoothly and in a wide range as compared with the prior art. Thereby, a braking force according to the rotation of the spools 12 and 50 can be appropriately applied to the spools 12 and 50.

<Detailed operation of spool braking structure>
The detailed operation of the spool braking structure 20 will be described below. In the spool braking structure 20, when the spools 12 and 50 that face the magnets 51 in the radial direction rotate, the second cylinder part 61 is moved relative to the first cylinder part 60 by the magnetic force of the magnets 51 acting on the spools 12 and 50. Move in the axial direction while rotating. As a result, the area (opposite range) of the portion where the spools 12 and 50 and the magnet 51 face each other in the radial direction changes, and the braking force of the spools 12 and 50 also changes.

  More specifically, when the spools 12 and 50 start rotating at an initial position where an initial braking force acts on the spools 12 and 50, the magnetic force of the magnet 51 acts on the spools 12 and 50, and the spools 12, 50 Braking force is generated. Note that the initial position is set by the operation knob 65 as described above. In the initial position, the magnet 51 faces the connecting portion 12d (see FIG. 3).

  In this state, when a braking force is generated on the spools 12 and 50, a reaction force corresponding to the braking force acts on the second cylindrical portion 61. Due to this reaction force, the second cylindrical portion 61 rotates with respect to the first cylindrical portion 60. In accordance with the rotation of the second cylinder portion 61, the engaging portion 61a moves along the engaged portion 60a. Then, the 2nd cylinder part 61 and the magnet 51 move to an axial direction (FIG. 3 right side). Thereby, the facing range (facing area) in which the magnet 51 faces the connecting portion 12d of the spools 12 and 50 in the radial direction is increased. Here, when the facing range is increased, the space S1 formed in the radial direction between the facing surface 112d of the connecting portion 12d and the magnet 51 is also increased.

  In particular, the opposing surface 112d of the connecting portion 12d is reduced in diameter from the flange portion 12a toward the bobbin trunk portion 12b. That is, when the facing range of the magnet 51 is increased, the distance between the moving direction end of the magnet 51 and the facing surface 112d of the connecting portion 12d is decreased. When the facing range of the magnet 51 is further increased, the end portion on the moving direction side of the magnet 51 reaches the facing surface 112b of the bobbin trunk 12b. Thus, as the facing range of the magnet 51 increases, the enlargement ratio of the space S1 gradually decreases. That is, the rate of change of the number of magnetic fluxes (magnetic force) of the magnet 50 acting on the spools 12 and 50 is suppressed. Here, the enlargement ratio is defined as the rate at which the space S1 changes when the magnet 51 moves in the movement direction (the direction in which the spool shaft 16 extends).

  When the rotation speed (rotational speed) of the spools 12 and 50 is decreased, the second cylindrical portion 61 and the magnet 51 are moved in the direction away from the spools 12 and 50 (left side in FIG. 4) by the spring member 62. As a result, the number of magnetic fluxes acting on the spools 12 and 50 decreases. Thereby, the braking force of the spools 12 and 50 is also reduced.

  Thus, in this spool braking structure 20, since the opposing surface 112d of the connecting portion 12d of the spools 12, 50 is reduced in diameter from the flange portion 12a toward the bobbin trunk 12b, the spools 12, 50 (connecting) When the number of magnetic fluxes acting on the part 12d) increases, the braking force acting on the spools 12, 50 can be gradually increased. For example, even if the rotation of the spool 12 increases, it is possible to suppress a sudden increase in the braking force of the spool 12.

  In addition, the spool braking structure 20 can automatically adjust the braking force of the spools 12 and 50 according to the rotation of the spools 12 and 50. In the spool braking structure 20, the engaged portion 60 a of the first tube portion 60 is formed in a curved shape that gradually increases in the axial direction with respect to the change in the circumferential direction of the first tube portion 60. Thereby, the operation | movement which the 2nd cylinder part 61 and the magnet 51 move to an axial direction rapidly following the high speed rotation of the spools 12 and 50 can be suppressed. That is, it is possible to further prevent the braking force acting on the spools 12 and 50 from rapidly increasing.

  Here, by forming the curve of the engaged portion 60a as a quadratic curve, a braking force close to a centrifugal brake proportional to the square of the rotational speed can be obtained. That is, a braking force according to the rotation of the spool can be appropriately applied to the spool. For example, in the spool braking force adjusting mechanism 64, a braking force as shown in the graph A in FIG. 7 acts on the spools 12 and 50 according to the rotational speed. For example, the braking force with respect to the rotational speed shown in the graph A of FIG. 7 is approximated by a quadratic curve. That is, the spool braking force adjusting mechanism 64 can obtain a braking force close to a centrifugal brake that is proportional to the square of the rotational speed of the spools 12 and 50. Thus, the braking force can be applied to the spools 12 and 50 in a well-balanced manner by forming the engaged portion 60a in a quadratic curve shape.

  On the other hand, when the engaged portion 60a of the first cylindrical portion 60 is formed in a shape (linear shape) defined by a linear equation, the relationship between the rotational speed and the braking force is as shown in the graph B in FIG. Shown in In this graph B, the braking force changes rapidly with respect to the change in the rotational speed. For this reason, when the engaged portion 60a is formed in a straight line, it is difficult for beginners to adjust.

  Further, when the engaged portion 60a is formed in a shape defined by a cubic curve, the relationship between the rotational speed and the braking force is shown as a graph C in FIG. In this graph C, the braking force changes gently with respect to the change in the rotational speed. Therefore, a relatively large braking force acts on the spools 12 and 50 even at a low speed, and the flight distance becomes difficult to be extended, but a characteristic that is easy for beginners to handle can be obtained.

[Second Embodiment]
The configuration of the dual bearing reel of the second embodiment is the same as that of the first embodiment except for the configurations of the spools 12 and 50 and the configuration of the magnet 51. For this reason, description is abbreviate | omitted here about the structure similar to 1st Embodiment. Moreover, in FIG.8 and FIG.9, the same code | symbol is attached | subjected about the structure similar to 1st Embodiment. Further, the description omitted here is in accordance with the description of the first embodiment.

  As shown in FIG. 8, the spools 12 and 50 have dish-shaped flange portions 12a on both sides. Moreover, the spools 12 and 50 have a cylindrical bobbin trunk 12b between both flanges 12a. Further, in the range from the initial position where the initial braking force acts on the spools 12 and 50 (the position corresponding to FIG. 3) to the maximum braking force position shown in FIG. The distance is substantially constant. That is, in this range, the expansion ratio of the space S1 formed in the radial direction between the bobbin trunk 12b and the magnet 51 is substantially constant. In the second embodiment, a portion between the flange portion 12a and the bobbin trunk portion 12b (a portion corresponding to the connecting portion 12d in the first embodiment) is considered to be included in the flange portion a, and is described below. Give an explanation.

  Here, the magnet 51 constitutes a magnetic force changing means. The magnet 51 is formed in a shape in which the magnetic force continuously changes along the moving direction. Thereby, when the magnet 51 moves along the spool shaft 16, the amount of change in the magnetic force acting on the spools 12 and 50 changes. Specifically, as the opposing range (opposing surface) where the magnet 51 moves along the spool shaft 16 and the magnet 51 opposes the spools 12 and 50 in the radial direction increases, the enlargement ratio of the opposing range increases. Becomes smaller.

  As shown in FIG. 9, the magnet 51 is formed in a shape tapered in one direction. The proximal end portion 51 a of the magnet 51 is disposed on the side close to the spools 12 and 50 in the second cylindrical portion 61. A tip 51 b (tapered portion) of the magnet 51 is disposed on the side farther from the spools 12 and 50 in the second cylindrical portion 61. More specifically, the magnet 51 is formed in a triangular plate shape. In the magnet 51, the bottom side 51 a (base end) is disposed on the side close to the spools 12 and 50 in the second cylindrical portion 61. Further, the apex portion 51 b (tip portion, tapered portion) is disposed on the side farther from the spools 12 and 50 in the second cylindrical portion 61. The magnet 51 is composed of eight permanent magnets. The magnets 51 are arranged at eight locations at equal intervals in the circumferential direction on the outer peripheral portion of the second cylindrical portion 61.

Here, the shape of the magnet 51 changes continuously. For this reason, the magnet 51 includes a first magnetic part and a second magnetic part having a small magnetic force generated from the first magnetic part. The first magnetic part and the second magnetic part are specially designed. Not shown in the figure. When the first magnetic part and the second magnetic part are illustrated, the first magnetic part corresponds to the bottom part 51a, and the second magnetic part corresponds to the apex part 51b.
Similarly, in a facing range (facing surface) where the magnet 51 faces the spools 12 and 50, the first magnetic force portion faces the spools 12 and 50, and the second magnetic force portion faces the spools 12 and 50. Although the opposing 2nd opposing surface is contained, these 1st opposing surface and 2nd opposing surface are not specifically illustrated. When considering to define the first facing surface and the second facing surface, the first facing surface corresponds to the facing surface of the first magnetic part (the base 51a), and the first facing surface is the second facing surface. It corresponds to the opposing surface of the magnetic part (vertex part 51b).

  Thus, when the spools 12 and 50 and the magnet 51 are configured, when the second cylindrical portion 61 and the magnet 51 move to the handle 2 side by the reaction force corresponding to the braking force of the spools 12 and 50, the opposing of the magnet 51 is achieved. The range (opposing surface) expands from the base end 51a side (bottom side) toward the tip 51b side (vertex side). That is, as the facing range of the magnet 51 becomes larger, the enlargement ratio of the facing range becomes smaller. Here, the enlargement ratio is defined as the rate at which the facing range (opposing surface) of the magnet 51 changes when the magnet 51 moves in the moving direction (the direction in which the spool shaft 16 extends).

  Thereby, since the change rate of the magnetic flux number (magnetic force) of the magnet 50 which acts on the spools 12 and 50 can be suppressed, the braking force on the spools 12 and 50 can be changed smoothly. For example, even if the rotation of the spools 12 and 50 increases, it is possible to suppress a sudden increase in the braking force of the spools 12 and 50. As described above, a braking force according to the rotation of the spools 12 and 50 can be appropriately applied to the spools 12 and 50.

[Third Embodiment]
The configuration of the dual bearing reel of the third embodiment is the same as that of the first embodiment except for the configuration of the spools 12 and 50. For this reason, description is abbreviate | omitted here about the structure similar to 1st Embodiment. Moreover, in FIG. 10, the same code | symbol is attached | subjected about the structure similar to 1st Embodiment. Further, the description omitted here is in accordance with the description of the first embodiment.

  Here, the spools 12 and 50 constitute magnetic force changing means. As shown in FIG. 10, the spools 12 and 50 have dish-shaped flange portions 12a on both sides. Moreover, the spools 12 and 50 have a cylindrical bobbin trunk 12b between both flanges 12a. Furthermore, the spool 12 has a cylindrical boss portion 12c integrally formed on the inner peripheral side of the bobbin trunk 12b. In the third embodiment, the portion between the flange portion 12a and the bobbin trunk portion 12b (the portion corresponding to the connecting portion 12d in the first embodiment) is considered to be included in the flange portion 12a, and is described below. Give an explanation.

  Between the initial position where the initial braking force acts on the spools 12 and 50 (the position shown in FIG. 10) and the maximum braking force position (the position corresponding to FIG. 4), between the bobbin trunk 12b and the magnet 51. The distance is substantially constant. That is, in this range, the expansion rate of the space formed in the radial direction between the bobbin trunk 12b and the magnet 51 is substantially constant.

  The spools 12 and 50 are formed of a plurality of materials having different electrical conductivities along the axial direction. At least a part of the spools 12 and 50, for example, the part where the spools 12 and 50 are opposed to the magnet 51, is made of a plurality of materials having different electrical conductivities. For example, the flange portion 12a (an example of the first conductor portion) facing the magnet 51 is formed by the first conductive member having the first conductivity, and the bobbin trunk portion 12b (an example of the second conductor portion) is It is formed by a second conductive member having two conductivity. Specifically, the material of the first conductive member is made of, for example, aluminum. The material of the second conductive member is made of, for example, stainless steel having a lower electrical conductivity such as aluminum. Here, an example in which the material of the first conductive member is aluminum or the like and the material of the second conductive member is stainless steel or the like has been shown, but the conductivity of the second conductive member (second conductive material). Other materials may be used as long as the ratio is smaller than the conductivity (first conductivity) of the first conductive member.

  In this way, when the spools 12 and 50 are configured, when the second cylindrical portion 61 and the magnet 51 move to the handle 2 side by the reaction force corresponding to the braking force of the spools 12 and 50, the magnet 51 is moved to the flange portion 12a ( The facing state changes from the state facing the first conductive member) to the state where the magnet 51 faces the flange 12a and the bobbin trunk 12b (second conductive member). That is, the state changes from a state where the first conductivity is mainly dominant to a state where the first conductivity and the second conductivity are mixed.

  In this case, as the facing range of the magnet 51 increases, the rate of increase of the magnetic flux lines acting on the spools 12 and 50 decreases, so that the braking force can be changed smoothly. For example, even if the rotation of the spools 12 and 50 increases, it is possible to suppress a sudden increase in the braking force of the spools 12 and 50. As described above, a braking force according to the rotation of the spools 12 and 50 can be appropriately applied to the spools 12 and 50. Here, the increasing rate is defined as the rate at which the magnetic flux lines change when the magnet 51 moves in the moving direction (the direction in which the spool shaft 16 extends).

[Other Embodiments]
(A) In the first to third embodiments, the engaged portion 60 a is a groove formed in a concave shape on the outer peripheral portion of the first cylindrical portion 60, and the engaging portion 61 a is the second cylindrical portion 61. The example in the case of the protrusion part protruded and formed in the inner peripheral part was shown. Instead, as shown in FIG. 11, the engaged portion 60 a is protruded from the outer peripheral portion of the first cylindrical portion 60 to form a protruding portion, and the engaging portion 61 a is set inside the second cylindrical portion 61. It is good also as a groove part by forming in a concave shape in a surrounding part. In this case, the protruding portion that is the engaged portion 60 a is formed in a curved shape that suddenly changes in the axial direction with respect to the change in the circumferential direction of the first tube portion 60. Even if comprised in this way, the effect similar to the said embodiment can be acquired.

  (B) In the first to third embodiments, the example in which the conductor 50 is the spool 12 has been described. Instead of this, as shown in FIGS. 12 and 13, a metal cylindrical member fixed to the spool 12 or the spool shaft 16 may be used as the conductor 50. In FIG. 12 and FIG. 13, an example in which the spool 12 does not have the connecting portion 12d is used. The description omitted here is the same as the description of the first embodiment.

  (C) In the first to third embodiments, the magnets 51 are arranged at eight positions on the outer peripheral portion of the second cylindrical portion 61 at equal intervals in the circumferential direction. However, the number and interval of the magnets 51 can be arbitrarily set. is there.

  (D) In the first to third embodiments, the example in which the initial braking force is set by moving the first cylindrical portion 60 by the cam mechanism (not shown) has been described. Instead of this, for example, by extending the internal thread portion 60b of the first tube portion 60 to the inner periphery of the first tube portion 60 and screwing it to the external thread portion provided on the outer periphery of the inner tube portion 55a, the initial braking force is increased. It may be settable. In this case, when the operation knob 65 is turned clockwise, the first cylinder part 60, the second cylinder part 61, and the magnet 51 move in a direction approaching the spools 12 and 50. On the other hand, when the operation knob 65 is turned counterclockwise, the first cylinder portion 60, the second cylinder portion 61, and the magnet 51 are moved away from the spools 12 and 50.

  (E) In the first to third embodiments, an example in which the spring member 62 is a conical coil spring has been shown in order to ensure a sufficient amount of movement of the second cylindrical portion 61 in the axial direction. The spring member 62 may be a coil spring having a constant outer shape.

  (F) In the first embodiment, the example in which the connecting portion 12d is provided only on one side of the spools 12 and 50 has been described. However, the connecting portions 12d may be provided on both sides of the spools 12 and 50. In this case, the spools 12, 50 can be easily molded. Further, in this case, the fishing line can be easily wound around the bobbin trunk 12b in the left and right directions.

  (G) In the said 2nd Embodiment, although the case where the shape of the magnet 51 changed continuously was shown as an example, you may comprise the magnet 51 so that the shape of the magnet 51 may change intermittently. For example, the magnet 51 may be configured such that the magnet 51 has a first magnetic part and a second magnetic part having an area facing the spools 12 and 50 that is smaller than the first magnetic part. Even in this case, it is possible to obtain the same effect as in the above embodiment.

  (H) In the third embodiment, an example in which the spools 12 and 50 are formed of the first conductive member and the second conductive member has been described. However, the number of members constituting the spools 12 and 50 ( The number of materials) may be three or more. In this case, the braking force can be changed more smoothly. For example, even if the rotation of the spools 12 and 50 is increased, it is possible to more reliably suppress a sudden increase in the braking force of the spools 12 and 50.

  (I) In the third embodiment, the braking force can be changed smoothly by changing the conductivity of the spool 12 in the axial direction, but the conductivity is not changed, and the thickness of the spool 12 is changed in the axial direction. The braking force can also be changed smoothly by changing to. For example, even if the spool 12 is configured such that the thickness of the flange portion 12a and / or the bobbin trunk portion 12b on the flange portion side gradually decreases as the distance from the flange portion 12a increases, the braking force can be changed smoothly. Can do.

  The present invention can be widely applied to spool braking devices.

1 Reel body 2 Handle 12 Spool (an example of a conductor)
12b Bobbin trunk 112b Opposing surface (an example of a third opposing surface)
12d connecting portion 112d facing surface (an example of a fourth facing surface)
16 Spool shaft 20 Spool braking structure (an example of a spool braking device)
23 Spool braking mechanism (an example of braking means)
50 Conductor (an example of a conductor part)
51 Magnet 51a Bottom part (an example of a first magnetic part)
51b Apex part (an example of the second magnetic part)
60 first cylinder part 60a engaged part 61 second cylinder part 61a engagement part 62 spring member 63 retaining member 64 spool braking force adjusting mechanism (an example of braking force adjusting means)
65 Operation knob 65a Knob section 65b Press section

Claims (10)

A spool brake device for a dual-bearing reel that brakes rotation of a spool that is rotatably mounted on a reel body of the dual-bearing reel,
A conductor portion that rotates in conjunction with the spool, and a magnet portion that can be opposed to the conductor portion in the radial direction, and the spool is rotated based on the magnetic force of the magnet portion acting on the conductor portion. Braking means for braking;
Braking force adjusting means for adjusting the braking force against rotation of the spool by moving the magnet portion relative to the conductor portion;
With
At least one of the magnet part and the conductor part changes a magnetic force of the magnet part acting on the conductor part in a moving direction in which the magnet part moves relative to the conductor part. Having magnetic force change means,
Spool braking device for double-bearing reels. The magnetic force changing means is provided in the magnet part,
The magnet part includes a first magnetic part and a second magnetic part having a small magnetic force generated from the first magnetic part,
The first magnet part and the second magnet part are provided along the moving direction.
The spool brake device for a double-bearing reel according to claim 1. The first magnetic part has a first facing surface that can face the conductive part,
The second magnetic part can be opposed to the conductive part and has a second opposing surface that is smaller than the first opposing surface.
3. A spool brake device for a dual-bearing reel according to claim 2. The magnetic force changing means is provided in the magnet portion, and the magnetic force of the magnet portion continuously changes along the moving direction.
The spool braking device for a dual-bearing reel according to any one of claims 1 to 3. The magnetic force change means is provided in the conductor portion,
The conductor portion includes a first conductor portion and a second conductor portion whose magnetic force received from the magnet portion is smaller than the first conductor portion. The first conductor portion and the second conductor portion. The conductor portion is provided along the moving direction.
The spool braking device for a double-bearing reel according to any one of claims 1 to 4. The first conductor portion has a third facing surface that can face the magnet portion,
The second conductive portion can be opposed to the magnet portion, and has a fourth opposing surface that is further away from the magnet portion than the third opposing surface.
6. A spool brake device for a double-bearing reel according to claim 5. The magnetic force changing means is provided in the conductor portion, and the distance from the magnet portion continuously changes along the moving direction.
The spool braking device for a dual-bearing reel according to any one of claims 5 and 6. The conductor portion is the spool;
The spool is made of metal.
The spool braking device for a double-bearing reel according to any one of claims 1 to 7. The conductor portion is a metal member fixed to the spool.
The spool braking device for a double-bearing reel according to any one of claims 1 to 7. A dual-bearing reel that is attached to a fishing rod and feeds and winds the fishing line,
A reel body mounted on the fishing rod;
A spool that is rotatably supported by the reel body, and winds the fishing line around an outer periphery;
The spool braking device according to claim 1,
Double-bearing reel equipped with.

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