JP2001017044A - Brake for reel supported with bearings at both ends - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable a second moving member to smoothly move even in a state that the second moving member is into contact with a taper-shaped surface in a reel brake. SOLUTION: A brake mechanism 23 for a reel supported with bearings at both ends is equipped with a taper-shaped surface 45, a first moving member 46, a second moving member 47, a coil spring 48 and a braking means 49. The surface 45 is the inner surface of a spool 12 in which the distance from a spool shaft 16 becomes longer as going outward from the rotating shaft, and has a friction-adjusting member 44 on a region contacting with the member 47. The member 46 interlocks with the spool. The member 47 is attached to the member 46 so as to be able to contact with the surface 45 and moves the member 46 outward from the rotating shaft when the member comes into contact with the surface 45 by centrifugal force. The coil spring 48 energizes the member 46 inward toward the rotating shaft. The braking means 49 brakes the spool 12 by the movement of the member 46.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a centrifugal braking device and, more particularly, to a dual bearing reel braking device for braking a spool rotatably provided on a reel body.

[0002]

2. Description of the Related Art In a dual-bearing reel called bait reel, which is mainly used for lure fishing, a braking force is applied to the spool so as to prevent a backlash in which the rotation speed of the spool becomes faster than the line payout speed during casting. Is commonly done. As this type of brake mechanism, a brake mechanism using centrifugal force and magnetic force is disclosed in Japanese Patent Application Laid-Open No. 10-309158.

In this brake mechanism, a conductor rotating in conjunction with a spool is moved in the axial direction of the spool using centrifugal force to increase or decrease the magnetic force acting on the conductor from a magnet mounted on the reel body. . In order to move the conductor in the axial direction of the spool using centrifugal force, a tapered surface having a large diameter on the reel body side is provided on the inner peripheral side of the spool or a rotating member that rotates in conjunction with the spool. . A first moving member is provided on the spool or the rotating member so as to be movable in the axial direction of the spool, and a second moving member that is movable in the radial direction so as to be able to contact the tapered surface is provided on the first moving member. Is provided. The first moving member is urged by the urging member in a direction away from the reel body. Further, braking means for braking the spool in accordance with the movement of the first moving member is provided. The braking means has a cylindrical conductor provided on the first moving member, and a pair of magnets provided on the reel body so as to be able to face the inner and outer circumferences of the conductor.

In the brake mechanism having such a configuration, when the spool rotates, the second moving member comes into contact with the tapered surface due to the centrifugal force, and when the urging force due to the centrifugal force becomes larger than the urging force of the urging member, the reel further moves. The spool is moved outward in the spool axial direction and radial direction along the tapered surface toward the main body to urge the first moving member toward the reel main body. When the first moving member moves toward the reel body, the conductor moves to a position facing the magnet, and the conductor crosses the magnetic force of the magnet, thereby generating an eddy current and braking the spool. The braking force of this spool changes according to the magnitude of the centrifugal force, that is, the axial position of the conductor that varies depending on the magnitude of the rotation speed, and the overall braking force changes to the opposing position of a pair of magnets to reduce the magnetic force. It can be adjusted by adjusting.

[0005]

In the conventional brake mechanism, the centrifugal force acting on the second moving member is converted into a force in the axial direction of the spool by using the tapered surface, and the second moving member is moved to the second moving member. One moving member is urged toward the reel body.
That is, when the second moving member comes into contact with the inner peripheral surface of the tapered shape due to centrifugal force, a pressing force in the spool axial direction is generated from the inner peripheral surface of the tapered shape and presses the second moving member. It moves in the spool axis direction while contacting the inner peripheral surface. For this reason, unless the tapered surface is finished to a smooth surface, the second moving member cannot move smoothly along the tapered surface. If the second moving member does not move smoothly along the tapered surface, it becomes difficult to perform braking at a desired timing. Also, depending on the material of the second moving member, the tapered inner peripheral surface may be damaged, and the corrosion resistance of the spool or the rotating member may be impaired.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a braking device for a dual-bearing reel that can smoothly move even if the second moving member moves in contact with the tapered surface.

[0007]

A braking device for a dual-bearing reel according to a first aspect of the present invention is a device for operating a spool rotatably provided on a reel body by centrifugal force to brake the spool.
It has a tapered surface, a first moving member, a second moving member, an urging member, and a braking means. The tapered surface is
A surface provided on the inner peripheral surface of the spool or a rotating member that rotates in conjunction with the spool such that the distance from the axis of the rotation shaft of the spool becomes longer as going outward in the rotation axis direction, at least. A friction adjusting member is provided at a contact portion with the second moving member. The first moving member is a member that is provided movably in the direction of the rotation axis with respect to the tapered surface and is interlocked with the spool. The second moving member is provided movably in the radial direction on the first moving member so as to contact the tapered surface, and moves along the tapered surface when the first moving member comes into contact with the tapered surface by centrifugal force. It is a member that moves outward in the rotation axis direction. The urging member is a member that urges the first moving member inward in the rotation axis direction. The braking means is means for braking the spool by moving the first moving member.

In this braking device, when the centrifugal force acts on the second moving member by rotating the spool, the second moving member comes into contact with the friction adjusting member provided on the tapered surface, and the spool shaft generated by the tapered surface is generated. A directional force acts on the second moving member. When this force becomes stronger than the urging force of the urging member,
The second moving member moves outward in the rotation axis direction along the friction adjusting member, the first moving member also moves outward in the rotation axis direction, and the spool is braked by the braking means. Also, when the force in the spool axial direction due to the centrifugal force is weaker than the urging force of the urging member,
The first moving member moves inward in the rotation axis direction by the urging force of the urging member, and the braking is released. Here, a friction adjusting member capable of maintaining a low frictional force is provided at a contact portion between the second moving member and the tapered surface, so that the second moving member moves to the tapered side by centrifugal force. Then, it always contacts the friction adjusting member. For this reason, the movement of the moving member becomes smooth, a desired braking timing is easily obtained, and the second moving member is less likely to be damaged.

A braking device for a dual-bearing reel according to a second aspect of the present invention includes:
In the apparatus according to the first aspect, the spool is made of a magnesium alloy, the tapered surface is formed on a part of the inner peripheral surface of the spool over the entire circumference, and the friction adjusting member is provided on the entire tapered surface. . In this case, since the friction adjustment member is provided on the inner peripheral surface of the magnesium alloy spool that is light and can greatly extend the flight distance of the device, the magnesium alloy spool is less likely to be damaged and Corrosion is less likely to occur. Further, since the taper-shaped surface is directly provided on the spool, the inertia of the portion that rotates in conjunction with the spool can be kept small, and a compact shape can be maintained. Therefore, the flight distance can be further increased.

A braking device for a dual-bearing reel according to a third aspect of the present invention includes:
In the device according to the first or second aspect, the friction adjusting member may be
It is formed in a layer on the tapered surface. In this case,
Since the friction adjusting member is formed in a layer shape by a processing method such as resin coating, the thickness of the friction adjusting member becomes uniform. A braking device for a dual bearing reel according to a fourth aspect of the present invention is the braking device according to the first or second aspect, wherein the friction adjusting member is fixed to the tapered surface. In this case, since the friction adjusting member is fixed to the tapered surface by an appropriate fixing means such as adhesion, welding, or bolt fixing, the friction adjusting member is not easily detached from the tapered surface.

A dual-bearing reel braking device according to a fifth aspect of the present invention includes:
In the apparatus according to the fourth aspect, the friction adjusting member is made of a hard synthetic resin having a smooth surface. In this case, the friction adjusting member can be easily formed and can be easily fixed to the tapered surface. A braking device for a dual-bearing reel according to a sixth aspect of the present invention is the braking device according to any one of the first to fifth aspects, wherein the braking means faces a contact portion provided on the reel body side of the first moving member. And a braking member provided non-rotatably and axially movable on the reel body and capable of contacting the contact portion, and brakes the spool by a frictional force generated by the contact between the contact portion and the braking member. In this case, when the spool rotates, the first moving member moves to the reel body side, and the contact portion contacts the braking member to brake the spool. Here, the spool is braked by frictional force that changes due to centrifugal force.

A braking device for a dual-bearing reel according to a seventh aspect of the present invention includes:
In the apparatus according to any one of the first to fifth aspects, the braking means may include a conductor provided on one of the first moving member and the reel body, and the first moving member and the first moving member configured to apply a magnetic force to the conductor. A magnet provided on one of the other sides of the reel body, and the spool is braked by an electromagnetic force generated by an eddy current generated by a magnetic force of the magnet acting on the conductor. In this case, when the spool rotates, the first moving member moves to the reel body side, the conductor is disposed between the opposed magnets, the lines of magnetic force are cut off, and an eddy current is generated to brake the spool. Here, the spool is braked by an electromagnetic force that changes due to centrifugal force.

[0013]

FIG. 1 is a plan view of a dual bearing reel to which an embodiment of the present invention is mounted. The dual-bearing reel shown in the drawing is a bait reel mainly used for lure fishing, and includes a reel body 1 and a spool rotation handle 2 disposed on the side of the reel body, and a spool rotation handle 2 disposed on the reel body 1 side of the handle 2. And a star drag 3 for drag adjustment. The handle 2 is of a double handle type having a plate-like arm portion 2a and handle portions 2b rotatably mounted on both ends of the arm portion 2a. The outer surface of the arm portion 2a of the handle 2 is formed of a smooth surface without any seams, and has a structure in which the fishing line is hardly entangled.

As shown in FIG. 2, the reel body 1 is mounted on a frame 5, a first side cover 6 and a second side cover 7 mounted on both sides of the frame 5, and a front part of the frame 5. And a front cover 10. The frame 5 includes a pair of side plates 8 and 9 arranged to face each other at a predetermined interval, and a plurality of connecting portions (not shown) connecting these side plates 8 and 9. I have.

The second side cover 7 on the handle 2 side is detachably fixed to the side plate 9 by screws. The first side cover 6 opposite to the handle 2 is detachably attached to the side plate 8 of the frame 5 by a bayonet structure 14. Handle 2
The side plate 8 on the opposite side has an opening 8 through which the spool 12 can pass.
a is formed. A spool 12 is provided in the frame 5.
And a level wind mechanism 15 for evenly winding the fishing line in the spool 12 and a clutch lever 17 to be applied to the thumb when performing the summing.
Between the frame 5 and the second side cover 7, the rotational force from the handle 2 is applied to the spool 12 and the level wind mechanism 15.
Gear mechanism 18 for transmitting to the clutch mechanism 13,
A clutch engaging / disengaging mechanism 19 for engaging and disengaging the clutch mechanism 13 in accordance with an operation of the clutch lever 17, a drag mechanism 21 for braking the spool 12 at the time of thread feeding, and a casting control for braking the spool shaft 16 at both ends. A mechanism 22 is provided. Also, frame 5
A brake mechanism 23 for suppressing backlash during casting is disposed between the first cover 6 and the first side cover 6.

The spool 12 is a generally cylindrical member with a flange made of a magnesium alloy, and has an anodic oxide film formed on the surface thereof to prevent corrosion. As shown in FIG. 3, the spool 12 has a pair of dish-shaped flange portions 12a at both ends, and has a generally cylindrical bobbin trunk portion 12b between the two flange portions 12a. The bobbin trunk 12b includes a cylindrical tubular portion 12d, and a
and a tapered cylindrical portion 12e having a tapered shape that gradually increases in diameter toward “a”. A tapered surface 45 constituting the brake mechanism 23 is formed on the inner peripheral surface of the tapered cylindrical portion 12e on the left side (the side plate 8 side) in FIG. The spool 12 has a cylindrical boss portion 12c integrally formed on the inner peripheral side of the cylindrical portion 12d of the bobbin trunk portion 12b. The spool 12 is, for example, serrated with a spool shaft 16 passing through the boss portion 12c. Is fixed so that it cannot rotate.

The spool shaft 16 extends through the side plate 9 and
It extends outside the side cover 7. Its extended end is the second
A boss 29 formed on the side cover 7 is rotatably supported by a bearing 35b. The other end of the spool shaft 16 is rotatably supported in the brake mechanism 23 by a bearing 35a. The level wind mechanism 15 includes a guide tube 25 fixed between the pair of side plates 8 and 9, and a guide tube 25.
A worm shaft 26 rotatably disposed therein, and a line guide 27. Worm shaft 26
Is fixed to an end of the gear mechanism 18. The worm shaft 26 has a spiral groove 2.
6a are formed, and the line guide 27 meshes with the spiral groove 26a. Therefore, the worm shaft 26 is rotated via the gear mechanism 18, so that the line guide 27 reciprocates by the guide cylinder 25. The fishing line is inserted into the line guide 27, and the fishing line is uniformly wound around the spool 12.

The gear mechanism 18 includes a main gear 31 fixed to the handle shaft 30, a cylindrical pinion gear 32 meshing with the main gear 31, a gear 28a fixed to the end of the worm shaft 26, and a handle shaft. 30 and a gear 28b that is non-rotatably fixed to the gear 30 and meshes with the gear 28a. The pinion gear 32 is a cylindrical member that is disposed outside the side plate 9 and through which the spool shaft 16 passes, and is mounted on 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 main 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 32b is formed by a concave groove formed on the end face of the pinion gear 32, and a clutch pin 16a that penetrates the spool shaft 16 in the radial direction is locked therein. Here, when the pinion gear 32 moves outward and the concave groove of the meshing portion 32b is disengaged from the clutch pin 16a of the spool shaft 16, the rotation from the handle shaft 30 is not transmitted to the spool 12. The groove of the engagement portion 32b and the clutch pin 1
6a constitute the clutch mechanism 13.

As shown in FIG. 2, the clutch lever 17 is disposed rearward of the spool 12 at a rear portion between the pair of side plates 8, 9. A long hole (not shown) is formed in the side plates 8, 9 of the frame 5, and a clutch cam (not shown) for fixing the clutch lever 17 passes through the long hole. The clutch 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 moving the clutch lever 17. When the handle shaft 30 rotates in the line winding direction, the clutch mechanism 13 is automatically turned on.
The clutch yoke 40 is moved so that is turned on.

In such a configuration, in a normal state,
The pinion gear 32 is located at an inner clutch engagement position, and the meshing portion 32b and the clutch pin 16a of the spool shaft 16 are engaged to be in a clutch-on state. On the other hand, the pinion gear 3 is
When 2 moves outward, the engagement between the engagement portion 32b and the clutch pin 16a is released, and the clutch is turned off.

[Structure of brake mechanism] Brake mechanism 23
Is a mechanism for braking the spool by centrifugal force, as shown in FIG. The brake mechanism 23 includes a tapered surface 45 formed on the inner peripheral surface of the bobbin trunk 12b of the spool 12.
And a first moving member 46 provided on a rotating member 51 that rotates in conjunction with the spool 12 so as to be movable in the spool axial direction.
And a second moving member 47 provided on the first moving member 46 so as to be movable in the radial direction. Also, brake mechanism 2
3 further includes a coil spring 48 for urging the first moving member 46 in a direction away from the side plate 8 and a braking means 49 for braking the spool 12 by the movement of the first moving member 46.

The rotating member 51 is a cylindrical member, and is fixed to the spool shaft 16 so as to be non-rotatable and axially immovable by appropriate fixing means such as serrations. Rotating member 5
1, a flange portion 51a having a larger diameter than the other portion is provided at the left end portion in FIG.
Are formed. The flange portion 51a is provided to lock one end of the coil spring 48. The right end of the rotating member 51 in FIG. 3 has a retaining ring 51 for restricting the movement of the first moving member 46 inward in the spool axial direction (rightward in FIG. 3).
b is attached. On the outer peripheral surface of the rotating member 51, parallel chamfers (not shown) are formed.

The tapered surface 45 of the bobbin trunk 12b is formed so that the distance from the axis of the spool shaft 16 becomes longer toward the outside in the spool axial direction (toward the first side cover 6 of the reel body 1). A frustoconical shape is formed on the inner peripheral surface. The tapered surface 45 has a friction adjusting member 44 fixed to smooth the movement of the second moving member 47. The friction adjusting member 44 is a frustoconical cylindrical member formed over the entire circumference and made of a hard synthetic resin such as a tetrafluoroethylene resin or a nylon resin, for example. It is fixed by fixing means. The inner peripheral surface of the friction adjusting member 44 is a very smooth tapered surface, and the friction coefficient is maintained at a very low value.

The first moving member 46 is mounted on the rotating member 51 so as to be axially movable and non-rotatable. The first moving member 46 is a frusto-conical member that expands outward in the spool axial direction (leftward in FIG. 3) approaching the first side cover 6, and the first moving member 46 is disposed on the outer peripheral side of the large-diameter end surface. A ring-shaped contact portion 46a protruding toward the cover 6 is formed. In the first moving member, for example, four guide holes 46b are formed radially so as to open on the peripheral surface. The guide hole 46b is, for example, a hole having a circular cross section, and a second moving member 47 is mounted in the guide hole 46b so as to be movable in the radial direction. An oval hole is formed in the inner peripheral surface of the first moving member 46 to engage with a chamfer formed on the inner peripheral surface of the rotating member 51. By this engagement, the first moving member 46 is mounted on the rotating member 51 so as to be non-rotatable and movable in the axial direction.

The second moving member 47 is a rod-shaped member mounted in the guide hole 46b, and has a slanted cut surface 47a at its tip which can be in contact with the friction adjusting member 44 of the tapered surface 45. I have. When the second moving member 47 comes into contact with the friction adjusting member 44 of the tapered surface 45 by centrifugal force, the second moving member 47 moves along the tapered surface 45 to the reel body 1 side, and moves the first moving member 46 to the first side of the reel body 1. Cover 6
Move to the side.

The coil spring 48 is connected to the flange 5 of the rotating member 51.
It is arranged in a compressed state between 1a and the end face of the first moving member 46, and urges the first moving member 46 inward in the spool axial direction (rightward in FIG. 3). The urging force of the coil spring 48 is, for example, weaker than the component force acting on the first moving member 46 outward in the spool axial direction due to the centrifugal force when the centrifugal force acts on the second moving member 47 at the time of thread feeding. It is larger than the component force acting at the time of winding the thread outward in the spool axial direction.

The braking means 49 includes a contact portion 46a of the first moving member 46 and a braking member 53 which can contact the contact portion 46a.
A biasing member 54 for biasing the braking member 53 toward the first moving member 46; a regulating member 55 for regulating movement of the braking member 53 toward the first moving member 46; and a biasing force of the biasing member 54. And an urging force adjusting mechanism 56 for adjusting the force. As shown in FIGS. 3 and 4, the braking member 53 is provided so as to be freely movable in the axial direction of the spool 12 with respect to the reel body 1 and is not rotatable. It is a contactable washer-shaped member. Specifically, the braking member 53 is mounted on the brake case 50 constituting the reel body 1 so as to be non-rotatable and movable in the spool axial direction.

The brake case 50 is a short cylindrical member with a bottom, and has a cylindrical bearing housing 50a projecting inward at the center of the bottom. The spool shaft 1
6, a friction plate of the casting control mechanism 22 is mounted, and a braking member 53 is mounted on the outer periphery so as to be non-rotatable and axially movable.

The brake case 50 includes a screw 60 (FIG. 2).
To the first side cover 6. That is, the brake case 50 constitutes a part of the reel body 1.
Also, at the outer periphery of the tip (the right end in FIG. 3) of the bearing housing portion 50a,
A pair of concave grooves 50b are formed along the axial direction. The concave groove 50b is provided to lock the braking member 53 so that it cannot rotate. An annular groove 50c is provided at the tip of the concave groove 50b.
Is formed, and a regulating member 55 is mounted in the annular groove 50c. The regulating member 55 is, for example, a member made of a ring-shaped elastic wire with a part of the circumference cut out,
As described above, the movement of the braking member 53 toward the first moving member 46 is restricted. The braking member 53 has an inner peripheral portion supported by the bearing housing portion 50a so as to be movable in the axial direction, and a pair of locking projections 53a that are locked by the concave groove 50b are formed on the inner peripheral portion.

On the outer peripheral surface of the brake case 50, three projections 14a forming the bayonet structure 14 are formed at intervals in the circumferential direction. In the opening 8a, a locking claw 14b is formed at a position facing the projection 14a. The locking claw 14b is formed to protrude outward from the opening 8a. One end of the urging member 54 has the braking member 53.
And the braking member 53 side is a large diameter conical spring.
The urging member 54 includes a braking member 53 and a pressing member 58 described later.
And in a compressed state. The pressing member 5
The biasing member 54 may have a free length when 8 is retracted most.

The urging force adjusting mechanism 56 includes the brake case 5
0, an operation member 59 rotatably mounted on the outside of the brake case 50, and an operation member 59 rotatably mounted on the outside of the brake case 50. Cam mechanism 61 for converting the movement in the direction
And The pressing member 58 includes an inner peripheral portion 58a supported in the bearing housing portion 50a so as to be movable in the axial direction, an outer peripheral portion 58b mounted in the inner peripheral surface of the brake case 50 so as to be movable in the axial direction and non-rotatably. Part 58a and outer peripheral part 58b
And a bottom portion 58c connecting the two. Outer periphery 58b
A pair of locking pins 62 protruding in the radial direction is formed on the outer peripheral surface of. The pair of locking pins 62 are formed on the inner peripheral surface of the brake case 50 along the spool axial direction.
The pressing member 58 is locked to the brake case 50 so as not to rotate. A cam mechanism 61 is provided on the outer peripheral surface of the outer peripheral portion 58b.
The first cam 63 is formed. The first cam 63 is a substantially triangular cam. A step 58d is formed on the inner wall of the bottom 58c, and the urging member 54 is attached to the step 58d.
Is locked at the other end.

The operating member 59 is a substantially ring-shaped member rotatably mounted on the outer surface of the brake case 50.
A knob 59a is formed on the outer peripheral portion of the outer surface of the operation member 59. The knob 59a is formed to protrude outward in the spool axial direction. At the center of the outer surface of the knob 59a, a projection 59c is further provided along the radial direction.
It is formed so as to protrude from the surface of the side cover 6, and indicates, for example, characters (not shown) of 0 to 5 indicating the braking force displayed on the surface of the first side cover 6. Further, a pair of rotation restricting recesses 59b for restricting the rotation range are formed on the inner peripheral surface. Operation member 59
Is provided with a positioning mechanism 70 for positioning the rotation angle with respect to the brake case 50 at six positions.

The positioning mechanism 70 includes a positioning pin 70a movably mounted on the operation member 59 in the spool axial direction.
And a coil spring 70b for urging the positioning pin 70a toward the brake case 50, and six positioning recesses 70c formed on the outer side surface of the brake case 50 at intervals in the circumferential direction. A second cam 64 constituting the cam mechanism 61 is provided on the right side surface of the operation member 59 in FIG. The second cams 64 are formed at positions facing the first cams 63, and each form a triangular hypotenuse cam. By the action of the two cams 63 and 64, the rotation of the operation member 59 is converted into the movement of the pressing member 58 in the direction approaching the braking member 53. The brake case 50 has an arc-shaped cam groove 5 through which the second cam 64 passes.
0f is provided as a pair.

The operating member 59 is pressed against the brake case 50 by a pressing plate 75. The holding plate 75 is provided with a screwing portion 50 formed on the outer surface of the brake case 50.
The operation member 59 is pressed by being screwed into d. The screwing portion 50d protrudes radially outward, and the operation member 59
The rotation angle is restricted to a predetermined range by locking the rotation restricting recess 59b to the screwing portion 50d.

The urging force adjusting mechanism 56 thus configured
Then, the knob 59a is pinched to move the operation member 59 to the arrow A.
When rotated in the direction, the pressing member 58 moves forward in a direction approaching the braking member 53 by the action of the first cam 63 and the second cam 64. As a result, the urging force on the braking member 53 is increased, the reaction force when the first moving member 46 contacts the braking member 53 is increased, and the braking force is increased. on the other hand,
When the operation member 59 is moved in the direction of arrow B, the urging member 5 is moved.
The urging force of No. 4 causes the pressing member 58 to retreat in a direction away from the braking member 53, so that the urging force acting on the braking member 53 is weakened and the braking force is reduced. When the vehicle retreats most, the braking force becomes the weakest. At four intermediate positions therebetween, the reaction force gradually becomes weaker, and the braking force gradually becomes weaker.

Here, since the braking force is adjusted by changing the urging force of the urging member 54, the braking force can be easily adjusted, and a clear difference in the braking force can be obtained by adjusting the urging force. Can be. Further, since the friction adjusting member 44 having the tapered surface 45 fixed is provided, the movement of the second moving member 47 becomes smooth. Therefore, the second moving member 4 is brought into contact with the spool 12 made of a magnesium alloy.
Even if 7 is arranged, the spool 12 will not be easily damaged.

[Reel Operation] In a normal state, the clutch yoke 40 is pushed inward and the clutch is on. As a result, the rotational force from the handle 2 is transmitted to the spool 12 via the handle shaft 30, the main gear 31, the pinion gear 32 and the spool shaft 16, and
Rotates in the line winding direction.

When performing the casting, the knob 59a is pinched to suppress the backlash, and the braking force is adjusted by the operation member 59. Arrow A on the operating member 59
When the pressing member 58 is caused to approach the braking member 53 by rotating in the direction, the urging force of the urging member 54 increases, and the braking force increases. Subsequently, the clutch lever 17 is pushed downward.
Here, the clutch lever 17 moves to the lower disengagement position along the flow of the side plates 8 and 9. Clutch lever 17
, The clutch yoke 40 moves 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 spool 12 and the spool shaft 16, and the spool 12 enters a free rotation state. When the fishing rod is tilted by tilting the reel in the axial direction so that the spool shaft 16 is along the vertical plane while the spool is being thumbed with the thumb placed on the clutch lever 17 in the clutch off state, the lure is thrown, and the spool 12 moves in the line payout direction. Rotate vigorously.

In such a state, the rotation of the spool 12 causes the spool shaft 16 to rotate in the line payout direction, and the rotation is transmitted to the rotating member 51. When the rotating member 51 rotates, a centrifugal force acts on the second moving member 47. When a centrifugal force acts on the second moving member 47, the second moving member 47
Is moved radially outward by centrifugal force and the tapered surface 4
5 comes in contact with the friction adjusting member 44. When the second moving member 47 comes into contact with the friction adjusting member 44, when the component force in the spool axial direction caused by the centrifugal force becomes larger than the urging force of the coil spring 48, the first moving member 46 and the spool axially outward ( (Left in FIG. 3). At this time, since the tapered surface 45 has the friction adjusting member 44, when the second moving member 47 comes into contact with the friction adjusting member 44, it is easy to move along the friction adjusting member 44. As a result, the first
The contact portion 46a of the moving member 46 contacts the braking member 53 to brake the spool 12. When the component force due to the centrifugal force becomes weaker than the urging force, the first moving member 46
To separate from the braking member 53.

When the yarn is rotated at a lower speed than when the yarn is unwound, as in the case of winding the yarn, the component force generated by the centrifugal force is weaker than the urging force of the coil spring 48.
2 is not braked. For this reason, the spool 12 can be selectively braked at the time of yarn winding and at the time of yarn feeding. Further, at the time of casting, the first moving member 46 comes into sliding contact with the braking member 53, and the spool 12 is braked by the brake mechanism 23, so that backlash can be prevented.

Even if a backlash occurs in the spool 12, the first side cover 6 can be easily attached and detached by the bayonet structure 14, so that the backlash can be easily eliminated. When replacing the lure with a different weight, the knob 59a is pinched according to the weight of the lure, the operating member 59 is rotated, and the urging force acting on the braking member 53 is adjusted to adjust the braking force. Here, the braking force due to the centrifugal force can be easily adjusted only by rotating the operation member 59 by grasping the knob portion 59a exposed to the outside. Adjusting the braking force makes the difference in the braking force clear. Moreover, since the friction adjusting member 44 is provided on the tapered surface 45, the movement of the second moving member 47 becomes smooth.

[Other Embodiments] (a) In the above embodiment, the pressing member 58 is moved by the cam mechanism 61, but the pressing member 58 may be moved by another conversion mechanism such as a screw. (B) In the above embodiment, the braking means 49 is configured to use the frictional force that changes due to the centrifugal force, but may be configured to use the electromagnetic force that changes due to the centrifugal force. As shown in FIG. 5, the braking means 49 using the electromagnetic force includes a washer-shaped conductor 80 made of a nonmagnetic metal such as an aluminum alloy or a copper alloy and fixed to the tip of the first moving member 46. A plurality of magnets 81 are provided facing the body 80 and arranged at intervals in the circumferential direction. The magnets 81 are arranged at intervals in the circumferential direction on the wall surface of the adjusting member 82 having substantially the same configuration as the pressing member 58 of the embodiment and opposed to the first moving member 46. The adjusting member 82 is moved by the cam mechanism 61 in a direction approaching the conductor 80, and the urging member 83 including a coil spring mounted in a compressed state on the spool 12 side of the adjusting member 82 and the cam mechanism 61 allow the adjusting member 82 to move. It moves in a direction away from the conductor 80. Other structures such as a moving mechanism of the adjustment member 82 are the same as those in the above-described embodiment, and thus description thereof is omitted here.

In the braking means 49 having such a structure, the spool 12 rotates at a high speed and the second moving member 47 moves in the radial direction by centrifugal force.
When an axial force larger than the urging force is applied, the first moving member 46 moves in a direction approaching the magnet 81. When the first moving member 46 approaches the magnet 81, the area of the conductor 80 crossing the magnetic flux of the magnet 81 gradually increases, and the magnitude of the eddy current generated in the conductor 80 acting by the magnetic force of the magnet 81 gradually increases. To increase. The magnitude of the eddy current increases even when the rotation speed of the conductor 80, that is, the rotation speed of the spool 12 increases. Since the braking force is proportional to the magnitude of the eddy current, the braking force gradually increases according to the area where the conductor 80 crosses the magnetic flux and the rotation speed of the spool 12. When the overall braking force is changed, the knob 59a is pinched to rotate the operation member 59 to change the distance between the magnet 81 and the conductor 80 to adjust the braking force.

Even in such an embodiment, since the second moving member 47 contacts the friction adjusting member 44 provided on the tapered surface 45, the movement along the tapered surface 45 becomes smooth. Note that the arrangement of the magnet 81 and the conductor 80 may be reversed, and the magnet 81 may be arranged on the first moving member, and the conductor 80 may be arranged on the adjustment member 82. Further, the arrangement of the magnets 81 may be such that the magnets 81 are arranged on opposed inner and outer peripheral surfaces of a double cylindrical member arranged concentrically. In this case, the conductor 80 may be formed in a cylindrical shape so as to be inserted between the opposed magnets 81.

(C) In the above embodiment, the first moving member 4
Although 6 is mounted on the rotating member 51 which rotates in conjunction with the spool 12, it may be mounted directly on the spool 12 or mounted on the spool shaft 16. (D) In the above embodiment, the friction adjusting member 44 is fixed to the entire tapered surface 45. However, the friction adjusting member 44 may be fixed only to a portion where the second moving member 47 contacts.

(E) In the above embodiment, the friction adjusting member 44 separate from the spool 12 is attached to the spool 1 by bonding or the like.
Although it is fixed to 2, the tapered surface 45 may be formed into a layer by various coating methods such as an ion plating method and an evaporation method. (F) In the above embodiment, the tapered surface is formed directly on the spool 12 in order to reduce the inertia and reduce the size. However, the tapered surface is formed on another member that rotates in conjunction with the spool 12. You may.

[0047]

According to the present invention, a friction adjusting member capable of maintaining a low frictional force is provided at a contact portion between the second moving member and the tapered surface. When it moves to the tapered side by centrifugal force, it always contacts the friction adjusting member. For this reason, the movement of the moving member becomes smooth, and it becomes easy to obtain a desired braking timing.
The second moving member is less likely to be damaged.

[Brief description of the drawings]

FIG. 1 is a plan view of a dual-bearing reel employing an embodiment of the present invention.

FIG. 2 is a sectional view thereof.

FIG. 3 is an enlarged sectional view of a brake mechanism.

FIG. 4 is an exploded perspective view of a brake mechanism.

FIG. 5 is a diagram corresponding to FIG. 3 of another embodiment.

[Explanation of symbols]

 Reference Signs List 1 reel body 12 spool 23 brake mechanism 44 friction adjusting member 45 tapered surface 46 first moving member 46a contact portion 47 second moving member 48 coil spring 51 rotating member 53 braking member 80 conductor 81 magnet

Claims (7)

[Claims] 1. A dual-bearing reel braking device for braking a spool rotatably provided on a reel body by a centrifugal force, the inner periphery of the spool or a rotating member rotating in conjunction with the spool. A tapered surface provided on the surface so that the distance from the axis of the rotation shaft of the spool increases toward the outside in the rotation axis direction; and in the rotation shaft direction with respect to the tapered surface. A first moving member movably provided and interlocking with the spool; a first moving member movably provided in a radial direction so as to be able to contact the tapered surface, and contacting the tapered surface by centrifugal force; A second moving member that moves along the tapered surface to move the first moving member outward in the rotation axis direction, and a biasing member that biases the first movement member inward in the rotation axis direction. The said And a braking means for braking the spool by the movement of the moving member, wherein the tapered surface has a friction member contacting portion of at least the second moving member, a braking device for a dual bearing reel. 2. The spool is made of a magnesium alloy, the tapered surface is formed on a part of an inner peripheral surface of the spool over the entire circumference, and the friction adjusting member is provided on the entire tapered surface. The braking device for a dual-bearing reel according to claim 1, wherein the braking device is provided. 3. The braking device for a dual-bearing reel according to claim 1, wherein the friction adjusting member is formed in a layer on the tapered surface. 4. The braking device for a dual bearing reel according to claim 1, wherein the friction adjusting member is fixed to the tapered surface. 5. A braking device for a dual bearing reel according to claim 4, wherein said friction adjusting member is made of a hard synthetic resin having a smooth surface. 6. A contact portion provided on a side of the first moving member away from the tapered surface, and a non-rotatable and axially movable member on the reel body opposed to the contact portion. A braking member provided to the contact portion and capable of contacting the contact portion, wherein the spool is braked by a frictional force generated by contact between the contact portion and the braking member.
The braking device for a dual-bearing reel according to any one of the above. 7. The braking means comprises: a conductor provided on one of the first moving member and the reel body; and the first moving member and the reel body so as to apply a magnetic force to the conductor. And a magnet provided on one of the other members, wherein the spool is braked by an electromagnetic force generated by an eddy current generated by a magnetic force generated by the magnet acting on the conductor. A braking device for a dual-bearing reel according to claim 1.