JPH10327722A - Braking apparatus for double-bearing reel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a contact-type brake mechanism to enable light winding of a fishing line. SOLUTION: A 2nd casting control mechanism 24 of a double-bearing reel brakes a spool 12 by friction and is provided with a brake liner 84, a magnetic material 80 and a one-way clutch 1O. The brake liner 84 is fixed to a brake case 65 which is fixed to the 2nd side-cover 6 of the reel main body. The magnetic material 80 is fixed to a rotary part 66. The one-way clutch 70 is placed between a spool shaft 16 and the rotary part 66 and transmits the rotation of the spool shaft 16 to the rotary part exclusively when the shaft is rotated in the line-delivery direction.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a braking device,
The present invention relates to a dual-bearing reel braking device that brakes a spool by friction.

[0002]

2. Description of the Related Art In a dual-bearing reel, it is common practice to apply a braking force to a spool in casting (during yarn feeding) so that a backlash in which the rotation speed of the spool is faster than the yarn feeding speed does not occur. Have been done. This type of brake mechanism includes a magnetic brake mechanism using eddy current generated by a magnetic force, a centrifugal brake mechanism that brakes a spool using centrifugal force, and a contact brake that directly brakes a spool or a spool shaft using frictional force. There is a mechanism. Of these, the contact brake mechanism is easy for beginners to easily prevent backlash and use.

[0003] In general, a beginner is likely to hit a device on the water surface or cast upward during casting. As described above, if a situation occurs in which the spool is rotating at a high speed while the speed of the device is low, backlash is likely to occur. The contact-type brake mechanism using the friction force stops the rotation of the spool when the tension higher than the braking force does not act, so that the above-mentioned situation is less likely to occur and even a beginner can easily prevent backlash.

[0004] The contact-type brake mechanism generally brakes the spool by bringing a fixed member fixed to the reel body into contact with a rotating member that rotates in conjunction with the spool, such as a spool shaft. Specifically, for example,
A wear-resistant metal plate is placed in contact with both ends of the spool shaft, and the braking force is adjusted by moving one of the metal plates in the axial direction.

[0005]

In the conventional contact-type brake mechanism, it is possible to prevent backlash by adjusting the braking force during casting. However, the contact-type brake mechanism applies a braking force regardless of the rotation speed.Therefore, if the brake mechanism is adjusted to a braking force that can prevent backlash, the braking force will be applied even when winding the yarn at a low rotation speed, and the steering wheel The rotation becomes heavy, and the fishing line cannot be wound up lightly.

An object of the present invention is to make it possible to wind up fishing line lightly in a contact brake mechanism.

[0007]

A dual-bearing reel braking device according to a first aspect of the present invention is a device for braking a spool by friction, and includes a fixed member, a contact member, and a one-way clutch. The contact member is a member that is provided on the rotating member that is linked to the spool and that can be pressed against the fixed member. The one-way clutch is interposed between the contact member and the rotating member, and connects the contact member and the rotating member when the rotating member rotates in the line unwinding direction, and shuts off the two members when rotated in the line winding direction.

In this braking device, when the spool rotates in the line payout direction as in the case of casting, the rotating member rotates in the line payout direction in conjunction with the spool, and the contact member and the rotating member are connected by the one-way clutch. Therefore, the contact member rotates and presses against the fixed member to generate a braking force, and the braking force acts on the spool. But,
When the rotating member rotates in the line winding direction, the rotating member and the contact member are shut off, so that the contact member does not rotate and no braking force is generated. Therefore, no braking force acts on the spool when the line is wound, and the fishing line can be wound lightly.

A braking device for a dual-bearing reel according to a second aspect of the present invention includes:
The device according to the first aspect of the present invention further includes an adjusting member that adjusts a pressing force between the contact member and the fixed member. In this case, the braking force can be freely adjusted according to the skill and preference of the angler. The braking device for a dual-bearing reel according to the third aspect of the present invention provides the braking device of the first aspect.
Or the rotating member is a spool shaft non-rotatably connected to the spool, and the contact member is connected to the spool shaft via a one-way clutch.
In this case, when the spool rotates in the line pay-out direction, the spool shaft also rotates in the same direction, and the rotation is transmitted to the contact member, and the braking force acts on the spool. Further, when the spool shaft rotates in the line winding direction, the contact member does not rotate and the braking force does not act on the spool, so that the fishing line can be wound lightly.

A braking device for a dual-bearing reel according to a fourth aspect of the present invention includes:
In the apparatus according to the first or second aspect, the rotating member is a spool, and the contact member is connected to the spool via a one-way clutch. In this case, when the spool rotates in the line payout direction, the rotation is transmitted to the contact member, and the braking force acts on the spool. When the spool rotates in the line winding direction, the contact member does not rotate and the braking force does not act on the spool, so that the fishing line can be wound lightly.

A dual-bearing reel braking device according to a fifth aspect of the present invention includes:
In the device according to any one of the inventions 2 to 4, the contact member includes a magnetic member, and the adjusting member adjusts the pressure contact force between the contact member and the rotating member by changing the number of magnetic fluxes acting on the magnetic member. In this case, the braking force can be finely adjusted by changing the number of magnetic fluxes. A braking device for a dual-bearing reel according to a sixth aspect of the present invention is the device according to any of the first to fifth aspects, wherein the holding member interlocked with the spool and the holding member are supported by the holding member so as to be movable substantially in the radial direction of the spool. A slider and a tubular member arranged outside the slider so as to be able to contact the slider, and the slider moves in the radial direction by centrifugal force to contact the cylindrical member. A centrifugal braking mechanism that brakes the spool is further provided, and the contact member is held by a holding body. In this case, at the time of casting, the spool is braked by the frictional force between the slider and the cylindrical member in addition to the frictional force between the contact member and the fixed member, so that a stronger braking force can be obtained. In addition, since the holding member of the centrifugal braking mechanism holds the contact member, the holding member does not rotate when winding the line. For this reason, the braking force does not act on the spool when the line is wound, and the fishing line can be wound lightly.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1 FIG. 1 is a plan view of a dual bearing reel according to an embodiment of the present invention. The dual-bearing reel shown in the drawing is a bait reel, which includes a reel body 1, a spool rotation handle 2 arranged on the side of the reel body 1, and a drag adjustment arranged on the reel body 1 side of the handle 2. A star drag 3 is provided. The handle 2 is of a double handle type having a plate-shaped arm portion 2a and handles 2b rotatably mounted on both ends of the arm portion 2a. The outer surface of the arm portion 2a is formed of a smooth surface with no seams, and has a structure in which the fishing line is not easily entangled.

As shown in FIG. 2, the reel body 1 has 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 and rear side of the frame 5 which is openably and closably mounted. And a front cover 10. The frame 5 has a pair of side plates 8 and 9 arranged to face each other at a predetermined interval, and a plurality of connecting portions 11 connecting these side plates 8 and 9.

The second side cover 7 on the handle 2 side is detachably fixed to the side plate 9 with 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 mechanism 14. The side plate 8 opposite to the handle 2 is provided with a spool 12 as shown in FIG.
An opening 8a is formed through which the hole 8a can pass. Opening 8
A long hole 8b for attaching the front cover 10 to be openable and closable is formed in front of "a". The long hole 8b is formed obliquely in front of the opening 8a, and a similar long hole (not shown) is formed in the side plate 9 on the handle 2 side at a position facing the long hole 8b. .

As shown in FIGS. 1 and 4, the front cover 10 includes a cover body 10a formed of a smooth curve continuous with the side covers 6 and 7, and the cover body 10a is connected to the side plates 8 and 9.
And a mounting leg portion 10b for mounting on the vehicle. An opening 10d through which a line guide 27 of the level wind mechanism 15 described later can move is formed on the front surface of the cover body 10a. An engagement piece 10e that engages with the side plates 8, 9 is formed at a lower front portion of the front cover 10. This engagement piece 10
A semispherical projection 10f is formed at the tip of e, and the projection 10f can move through a concave hole (not shown) formed on the inner surface of the side plates 8, 9.

The mounting leg 10b is a U-shaped member as viewed from the front, and a shaft 10c (only the side plate 8 side is shown in FIG. 4) protrudes outward from both ends. The shaft portion 10c is provided with a side plate 8,
9 and is movable in the longitudinal direction of the long hole.
The shaft portion 10c on the side plate 8 side further projects outward from the side plate 8. Such a front cover 10 can be freely opened and closed with respect to the side plates 8 and 9 between an open position shown by a two-dot chain line and a closed position shown by a solid line in FIG.

In the frame 5, there are arranged a spool 12, a level wind mechanism 15 for uniformly winding fishing line in the spool 12, and a thumb rest 17 to be applied to a thumb when performing summing. A gear mechanism 18 for transmitting the rotational force from the handle 2 to the spool 12 and the level wind mechanism 15, a clutch mechanism 13, and a clutch in accordance with the operation of the thumb rest 17 are provided between the frame 5 and the second side cover 7. A clutch engaging / disengaging mechanism 19 for engaging and disengaging the mechanism 13, a drag mechanism 21, and a first casting control mechanism 22 are arranged. Also,
A centrifugal brake mechanism 23 for suppressing backlash during casting and a second casting control mechanism 24 are arranged between the frame 5 and the first side cover 6.

The spool 12 has a dish-shaped flange portion 12a on both sides, and a cylindrical bobbin trunk 12b between both flange portions 12a. Also, the spool 12
Has a cylindrical boss portion 12c integrally formed substantially at the central portion in the axial direction on the inner peripheral side of the bobbin trunk portion, and is connected to a spool shaft 16 passing through the boss portion 12c by, for example, serration connection. It is fixed so that it cannot rotate. This fixing method is not limited to serration connection, and various connection methods such as key connection and spline connection can be used.

As shown in FIG. 3, the spool shaft 16 extends through the side plate 9 to the outside of the second side cover 7. The extended one end is formed on the boss 2 formed on the second side cover 7.
9 is rotatably supported by a bearing 35b. The other end of the spool shaft 16 is rotatably supported by a bearing 35a in the centrifugal brake mechanism 23. These bearings are sealed ball bearings. Spool shaft 16
Is a large-diameter portion 16a at the center where the spool 12 is fixed.
And two small diameter portions 16b, 16 formed at both ends thereof.
c.

The large diameter portion 16a is arranged in a space inside the bobbin trunk 12b of the spool 12, and a serration 16d for fixing the spool 12 is formed on the outer peripheral surface of the central portion. At the right end of the large-diameter portion 16a in FIG.
Are formed. The small diameter portion 16c on the left side is further reduced in diameter in two steps in a stepwise manner, and the tip is supported by the brake case 65 by the bearing 35. A pinion gear 32 is supported by the small diameter portion 16b on the right side so as to be movable in the axial direction. The distal end of the small diameter portion is rotatably supported by a bearing 35a. Note that both ends of the spool shaft 16 have spherical surfaces in order to suppress an increase in rotation resistance.

The level wind mechanism 15 is shown in FIGS.
As shown in FIG. 1, the guide tube 25 includes a guide tube 25 fixed between the pair of side plates 8 and 9, a worm shaft 26 rotatably supported in the guide tube 25, and a line guide 27. A long groove is formed in the outer peripheral surface of the guide cylinder 25 in the axial direction, and a locking portion 27 d attached to the line guide 27 extends from the groove toward the worm shaft 26. A gear 28a constituting the gear mechanism 18 is fixed to an end of the worm shaft 26. A helical groove 26a is formed in the worm shaft 26, and the locking portion 27d is engaged with the helical groove 26a. Therefore, the worm shaft 26 is rotated via the gear mechanism 18, so that the line guide 27 reciprocates along 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. A hard ring 27a for guiding the fishing line is fitted on the upper part of the line guide 27.

As shown in FIG. 2, the gear mechanism 18 is fixed to a main gear 31 fixed to the handle shaft 30, a cylindrical pinion gear 32 meshing with the main gear 31, and an end of the worm shaft 26 described above. Gear 28a and a gear 28b that is fixed to the handle shaft 30 so as not to rotate and that meshes with the gear 28a. As shown in FIG. 3, the pinion gear 32 is a tubular member that is disposed outside the side plate 9 and through which the spool shaft 16 penetrates at the center, and is mounted on the spool shaft 16 so as to be movable in the axial direction. Pinion gear 32
3 is a toothed portion 32a formed on the outer peripheral portion on the right end side of FIG. 3 and meshing with the main gear 31, and a meshing portion 32 formed on the other end side.
b, and a constricted portion 32c formed between the tooth portion 32a and the meshing portion 32b. Meshing part 32b
Consists of an oval concave hole formed on the end face of the pinion gear 32, and a chamfered part 16e formed at the end of the large diameter part 16a of the spool shaft 16 is locked therein. Here, the pinion gear 32 moves outward and its meshing portion 32b
When the chamfered portion 16 e of the spool shaft 16 is separated from the concave hole of the spool shaft 16, the rotational force from the handle shaft 30 is not transmitted to the spool 12. The concave hole of the engaging portion 32b and the chamfered portion 16
e constitutes the clutch mechanism 13.

As shown in FIG. 2, the thumb rest 17
A rear portion between the pair of side plates 8 and 9 is disposed behind the spool 12, and also serves as a clutch operation lever. Frame 5
Elongated holes (not shown) are formed in the side plates 8 and 9.
The rotation shaft 17a of the thumb rest 17 is rotatably supported by the elongated hole. For this reason, the thumb rest 17 can be slid up and down along the long hole.

The clutch engagement / disengagement mechanism 19 has a clutch yoke 40 as shown in FIG. The clutch engagement / disengagement mechanism 19 moves the clutch yoke 40 in parallel with the axis of the spool shaft 16 by rotating the thumb rest 17. Further, when the handle shaft 30 rotates in the line winding direction, the clutch yoke 40 is moved so that the clutch mechanism 13 is automatically turned on. The clutch yoke 40 is arranged on the outer peripheral side of the spool shaft 16, and is supported by two pins 41 (only one is shown) so as to be movable in parallel with the axis of the spool shaft 16. The spool shaft 16 can rotate relative to the clutch yoke 40. That is, even if the spool shaft 16 rotates, the clutch yoke 40 does not rotate. Also, the clutch yoke 40
Has an engaging portion 40a at the center thereof for engaging with the constricted portion 32c of the pinion gear 32. Further, the outer circumference of each pin 41 supporting the clutch yoke 40, the clutch yoke 4
A spring 42 is arranged between the first cover 0 and the second side cover 7, and the clutch yoke 40 is constantly biased inward (toward the clutch engagement side) by the spring 42.

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 chamfered portion 16e of the spool shaft 16 are engaged to be in a clutch-on state.
On the other hand, when the pinion gear 32 is moved outward by the clutch yoke 40, the engagement between the meshing portion 32b and the chamfered portion 16e is released, and the clutch is turned off.

As shown in FIG. 2, the drag mechanism 21 is provided for pressing the friction plate 45 against the main gear 31 with a predetermined force by rotating the star drag 3 and the friction plate 45 pressed against the main gear 31. Press plate 46
And As shown in FIG. 3, the first casting control mechanism 22 includes a plurality of friction plates 51 disposed so as to sandwich both ends of the spool shaft 16, and a cap for adjusting the force of holding the spool shaft 16 by the friction plates 51. 52. The left friction plate 51 is mounted in the brake case 65. The cap 52 is embedded in the boss portion 29 and cannot be operated unless a special tool is used. The first casting control mechanism 22 is used for reducing the backlash in the axial direction of the spool shaft 16 for the purpose of adjusting the braking force. Therefore, in this embodiment, the first casting control mechanism 22 hardly applies a braking force to the spool 12.

As shown in FIG. 3, the centrifugal brake mechanism 23 includes a brake case 65, a rotating portion 66 provided in the brake case 65, and a radially arranged Slider 67 movably mounted
And a cylindrical brake liner 68 fixed to the inner peripheral surface of the brake case. Brake case 65
Is a short cylindrical member with a bottom, and a bearing housing portion 65a protruding outward is formed at the center of the bottom. Here, a bearing 35a for supporting the spool shaft 16 is housed, and a friction plate 51 of the first casting control mechanism 22 is mounted on a bottom surface thereof. The brake case 65
It is fixed to the first side cover 6 by two screws 69a and 69b. On the outer peripheral surface of the brake case 65, 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 in an L-shape.

As shown in FIG. 4, a detent protrusion 65b is formed on the outer peripheral surface of the brake case 65 so as to be in contact with the peripheral surface of the shaft portion 10c of the front cover 10. The detent protrusion 65b is provided to stop the first side cover 6 by abutting on the shaft portion 10c when the front cover 10 is at the closed position. That is, the shaft portion 10c of the front cover 10 realizes the function of preventing the first side cover 6 from rotating. As described above, the first side cover 6 is prevented from rotating by the front cover 10 that covers the front portion of the frame 5 so as to be openable and closable, so that the first side cover 6 can be prevented from rotating without providing a dedicated rotation preventing member.

The rotating portion 66 is a disk-shaped member, and has a plurality of concave portions 66a formed in the outer peripheral portion at intervals in the circumferential direction as shown in FIG. A guide shaft 66b is provided upright along the radial direction in the concave portion 66a. Rotating part 66
Is axially movably connected to the spool shaft 16 by a one-way clutch 70 disposed on the small diameter portion 16c of the spool shaft 16. Further, the rotating portion 66 is urged toward the spool 12 by a pressing spring 71 disposed on the outer peripheral side of the small diameter portion 16c of the spool shaft 16. The one-way clutch 70 includes an inner race 70a connected to the spool shaft 16 so as to be non-rotatable and non-movable in the axial direction, an outer race 70b non-rotatably connected to the rotating part 66 so as to be axially movable, and an inner race 7
0a and rolling element 70 arranged so as to be able to contact outer ring 70b
c, for example, is an outer ring idle-type roller clutch. A plurality of rolling elements 70c are provided at intervals in the circumferential direction by a retainer (not shown). This rolling element 70c
Is biased in one direction by a spring (not shown). When the spool shaft 16 rotates in the line unwinding direction, the one-way clutch 70 rotates the rotating portion 66 and the spool shaft 1.
6 are connected to each other, and when they are rotated in the yarn winding direction, both are shut off. For this reason, the centrifugal brake mechanism 23 and a second casting control mechanism 24 described later brake the spool 12 only at the time of thread feeding, and do not brake at the time of thread winding.

The slider 67 is movably supported by a plurality of guide shafts 66a provided upright in the concave portion 66a of the rotating portion 66. The slider 67 moves radially outward by centrifugal force and slides on the brake liner 68 in the brake case 65 to brake the spool 12. Here, since the centrifugal force increases in proportion to the square of the rotation speed, the braking force of the centrifugal brake mechanism 23 increases in proportion to the square of the rotation speed.

Second casting control mechanism 24
Is arranged in the brake case 65 as shown in FIGS. 3 and 5. The second casting control mechanism 24 includes a magnetic plate 80 fixed to the end face of the rotating portion 66.
And a swing arm 83 for braking having two magnets 81 and 82 for attracting the magnetic plate 80, and a brake liner 84 disposed on the brake case 65 so as to face the magnetic plate 80.
And a braking adjustment unit 85 for adjusting the braking force by swinging the swing arm 83. The second casting control mechanism 24 adjusts the braking force by changing the number of magnetic fluxes acting on the magnetic plate 80.

The magnetic plate 80 is a soft iron disk-shaped member, and is fixed to the end face of the rotating portion 66 by a suitable fixing means such as an adhesive. When the magnetic plate 80 is attracted by the magnets 81 and 82, the rotating portion 66 to which the magnetic plate 80 is fixed moves outward in the axial direction, and the magnetic plate 80 contacts the brake liner 84. The swing arm 83 is an arm that swings between a maximum braking position shown by a solid line in FIG. 5 and a minimum braking position shown by a two-dot chain line, and holds the two magnets 81 and 82 at an interval. Arm 83a and a swing shaft 83b non-rotatably mounted at the base end of the magnet holding arm 83a
And an operation arm 83c whose base end is non-rotatably mounted on the swing shaft 83b. The magnet holding arm 83a is
It is an arc-shaped arm member, and holds two magnets 81, 82 at the distal end and near the proximal end in the longitudinal direction. Here, when the swing arm 83 is disposed at the maximum braking position, 2
The two magnets 81 and 82 are arranged at substantially symmetric positions facing the magnetic plate 80 with the spool shaft 16 interposed therebetween. Swing axis 8
3b is rotatably supported on the bottom surface of the brake case 65. The magnet holding arm 83a is mounted on one end of the arm, and the operation arm 83c is mounted on the other end of the arm so as not to rotate. The operation arm 83c is an arc-shaped arm member having a long hole 83d formed at the tip. When the operation arm 83c swings, the magnet holding arm 83a swings via the swing shaft 83b, so that the area of the magnets 81 and 82 facing the magnetic plate 80 changes, and the magnets 81 and 82 pass through the magnetic plate 80. The magnetic flux density changes. As a result, the force for attracting the magnetic plate 80 changes, and the frictional force between the magnetic plate 80 and the brake liner 84 changes to change the braking force.

The brake liner 84 is provided with an intermediate plate 90 disposed parallel to and spaced from the bottom of the brake case 65.
Are mounted non-rotatably at the center of the shaft. The brake liner 84 is made of an abrasion-resistant nylon resin such as a polyslider (trade name) and is used to brake the spool 12 by contacting the magnetic plate 80.

The braking adjustment section 85 includes a guide member 91 fixed obliquely to the inner surface of the first side cover 6 and a guide member 91.
And a positioning mechanism 93 for positioning the handle member 92. The guide member 91 is disposed along a guide hole 95 formed obliquely in the first side cover 6 and guides the handle member 92 in the longitudinal direction. The handle member 92 has a photographing portion 92 a exposed to the outside of the first side cover 6 and a link shaft portion 92 b protruding inward of the first side cover 6. The link shaft portion 92b is
The operation arm 83c is locked by a long hole 83d formed at the tip of the operation arm 83c. As a result, when the handle member 92 moves between the maximum braking position shown by the solid line and the minimum braking position shown by the two-dot chain line, the link shaft 92b moves between the upper end and the lower end of the elongated hole 83d, and the operating arm 83c swings between the maximum braking position and the minimum braking position. The positioning mechanism 93 has a positioning spring 96 fixed to the photographing section 92 a and a positioning metal fitting 97 for positioning the positioning spring 96 in the moving direction of the handle member 92. The positioning spring 96
It is a leaf spring bent in a mountain shape, and its vertex is bent in an arc shape. An arc-shaped unevenness 97 a having a shape along the arc portion of the positioning spring 96 is formed on the positioning fitting 97. Therefore, when the handle member 92 moves, the positioning spring 96 comes into contact with the unevenness 97a of the positioning fitting 97, and the handle member 92 is positioned. As a result, the handle member 92 is positioned at a plurality of positions between the maximum braking position and the minimum braking position, and the braking force can be adjusted in multiple stages.

Next, the operation of the reel will be described. In a normal state, the clutch yoke 40 is pushed inward (leftward in FIG. 3) by the spring 42, whereby the pinion gear 32 is moved to the engagement position. In this state, the meshing portion 32b of the pinion gear 32 meshes with the chamfered portion 16e of the spool shaft 16, and the clutch is turned on. The rotational force from the handle 2 is applied to the handle shaft 30, the main gear 31, the pinion gear 32, The power is transmitted to the spool 12 via the spool shaft 16, and the spool 12 rotates in the line winding direction. At this time, since the one-way clutch 70 is mounted, the rotation is not transmitted from the spool shaft 16 rotating in the line winding direction to the rotating unit 66, and the rotating unit 66 is braked by the centrifugal brake mechanism 23 and the second casting control mechanism 24. Even if it is performed, the spool 12 is not braked. For this reason, when winding the fishing line, no matter how the braking force of the centrifugal brake mechanism 23 or the second casting control mechanism 24 is adjusted, the braking force does not act, and the fishing line can be wound lightly.

When performing casting, the braking force is adjusted by the handle member 92 to suppress backlash. Then, the thumb rest 17 is pushed downward. Here, the thumb rest 17 moves to the lower detached position along the long holes of the side plates 8 and 9. The movement of the thumb rest 17 causes the clutch yoke 40 to move outward, and the pinion gear 32 engaged with the clutch yoke 40 to move in the same direction. As a result, the meshing portion 3 of the pinion gear 32
The engagement between 2b and the chamfered portion 16e of the spool shaft 16 is released, and the clutch is turned off. In this clutch state, 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. With the clutch off, spool the spool shaft 1 while thumbing the spool with the thumb resting on the thumb rest 17.
When the fishing rod is shaken while tilting the reel in the axial direction so that 6 is along the vertical plane, a lure is thrown and the spool 12 rotates vigorously in the line feeding direction.

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 section 66 via the one-way clutch 70. When the rotating part 66 rotates, the slider 67 slides on the brake liner 68 to brake the spool 12 by the centrifugal brake mechanism 23. On the other hand, the magnetic plate 80 is attracted to the magnets 81 and 82 in accordance with the swing position of the swing arm 83, and moves to the brake liner 84 side together with the rotating portion 66 against the urging force of the pressing spring 71. Contacts the brake liner 84 with an attraction force corresponding to the swing position of the swing arm 83. As a result, the spool 12 is braked with a desired braking force by the frictional force between the magnetic plate 80 and the brake liner 84, and troubles such as backlash are reduced.

Further, even if a backlash occurs in the spool 12, the first side cover 6 can be easily attached and detached by the bayonet mechanism 14, so that the backlash can be easily eliminated. The procedure for attaching and detaching the first side cover 6 will be described below. In a normal state, the front cover 10 is located at the closed position shown in FIG. At this time, the shaft portion 10c of the front cover 10
Is arranged at the lower end of the elongated hole 8b. The rotation preventing projection 65b fixed to the brake case 65 abuts on the shaft portion 10c, so that the first side cover 6 to which the brake case 65 is fixed cannot rotate counterclockwise in FIG.

When removing the first side cover 6 from the side plate 8 to take out the spool 12, the front cover 10 is pulled out to the open position as shown in FIG. Front cover 10
Is pulled out, the shaft 10c of the front cover 10 is guided by the elongated hole 8b and moves to the upper end. Then, the shaft portion 10c is disengaged from the rotation preventing protrusion 65b, and the first side cover 6 can be rotated counterclockwise in FIG. When the first side cover 6 is rotated counterclockwise in this state, the projections 14a come off from the locking claws 14b provided on the side plate 8, and the first side cover 6 can be removed from the side plate 8. First side cover 6
When the spool 12 is braked by the second casting control mechanism 24, the magnetic plate 80 is attracted to the magnets 81 and 82 and can be removed together with the side cover 6. When the brake is not applied, the opening 8
a.

Embodiment 2 In the above embodiment, the spool 12 is fixed to the spool shaft 16, but the present invention can be applied to a case where the spool 12 is rotatably supported by the spool shaft 16. In the following description, the same or similar components are denoted by the same reference numerals. Further, only the points that are significantly different from the first embodiment in the configuration and operation will be described.

Referring to FIG. 8, in a bait reel employing another embodiment of the present invention, bearing mounting portions 12d and 12e are formed on the inner peripheral side of the spool 12, and the bearing 2 is provided there.
0a and 20b are mounted. This makes the spool 1
2 is rotatably supported on the spool shaft 16 by two bearings 20a and 20b. The pinion gear 32 is rotatably supported on the side plate 9 by a bearing 35c.
Further, the pinion gear 32 and the spool 12 are engaged and disengaged by the clutch mechanism 13.

First casting control mechanism 22
As shown in FIG. 9, a plurality of friction plates 51 arranged so as to sandwich both ends of the spool shaft 16, a cap 52 for adjusting the braking force of the spool shaft 16 by the friction plate 51, 9 has a bottomed cylindrical pressing cap 53 over the other end (left side in FIG. 9), and a braking member 54 that can contact and separate from the pressing cap 53. A female screw is formed on the inner peripheral portion of the cap 52 and is screwed to a male screw formed on the boss portion 29 of the second side cover 7.

The pressing cap 53 is provided on the spool shaft 16 so as to be relatively movable in the axial direction, and the bottom portion is in contact with the left friction plate 51. A bearing 35 a that supports the spool shaft 16 is arranged on the outer periphery of the end of the pressing cap 53. The spool shaft 16 is provided inside the pressing cap 53.
A space 53a is formed between the pressure spring 55 and the end face of the pressure spring 55, and the pressing spring 55 is disposed in a compressed state in the space 53a.
The pressing spring 55 urges the pressing cap 53 and the spool shaft 16 in a direction away from each other. The braking member 54 is a disk-shaped member, and includes a rotating portion 66 of a centrifugal braking mechanism 23 described later.
Are formed integrally with the rotating portion 66 on the inner peripheral portion of the rotating member. The braking member 54 brakes the spool 12 by being pressed by the pressing cap 53 and clamped between the bearing 20a locked by the annular projection 16f.

In the first casting control mechanism 22, when the cap 52 is screwed, the spool shaft 16
Moves in a direction (left side in FIG. 9) approaching the pressing cap 53. At the same time, the spool 12 moves in the same direction, so that the pressing cap 53 comes into contact with the braking member 54 and the bearing 20a
Thus, the braking member 54 is sandwiched and the spool 12 is braked. When the cap 52 is loosened, the spool shaft 16 is pressed by the pressing spring 55, and moves in a direction away from the pressing cap 53. When the braking member 54 is the pressing cap 5
When it is separated from 3, the braking on the spool 12 is released.

The centrifugal brake mechanism 23 includes a brake case 65 and a rotating portion 66 provided in the brake case 65.
And a slider 67 which is arranged on the rotating portion 66 at a distance in the circumferential direction and is movably mounted in the radial direction. At the center of the brake case 65, a cylindrical bearing housing portion 65a for mounting the bearing 35a is formed. Further, a friction plate 51 of the first casting control mechanism 22 is disposed at the center thereof. A brake liner 68 is provided on the inner periphery of the periphery of the brake case 65. The rotating part 66 is connected to the bearing mounting part 12 e of the spool 12 via a one-way clutch 70. The one-way clutch 70 connects the spool 12 and the rotating part 66 when the spool 12 rotates in the line pay-out direction, and releases the connection when the spool 12 rotates in the line winding direction. The slider 67 slides on the liner 68 in the brake case 65 by centrifugal force. As a result, the first casting control mechanism 22 and the centrifugal brake mechanism 23 brake the spool 12 only at the time of thread feeding,
No braking when winding the line.

Next, the operation will be described. In a normal state, the clutch yoke 40 is pushed inward by the spring 42, whereby the pinion gear 32 is moved to the engagement position. In this state, the pinion gear 3
2 is engaged with the spool 12 and the spool 12 is in a clutch engaged state. The rotational force in the line winding direction from the handle 2 is reduced by the handle shaft 30 and the main gear 31.
And transmitted to the spool 12 via the pinion gear 32. At the time of this line winding, the one-way clutch 70 does not transmit the rotation to the rotating section 66 because the spool 12 rotates in the line winding direction. For this reason, since the braking force by the first casting control mechanism 22 and the centrifugal brake mechanism 23 does not act on the spool 12, the fishing line can be lightly wound by that much.

When performing the casting, it is possible to adjust the braking force when the spool 12 is fed by adjusting the tightening amount of the cap 52 of the first casting control mechanism 22. Cap 5
9 and move the spool shaft 16 to the left in FIG.
The annular projection 16f contacts the inner ring of the bearing 29a and the spool 1
9 moves to the right in FIG. 9 and is pressed by the pressing cap 53 so that the braking member 54 is pressed by the pressing cap 53 and the bearing 20a.
Between the outer ring. As a result, the spool 12 is braked according to the pressing force. Conversely, if you loosen the cap 52,
The spool shaft 16 is biased by the pressing spring 55 and moves rightward in FIG. As a result, there is a gap between the pressing cap 53 and the braking member 54.

As described above, since the pinion gear 32 is rotatably supported by the side plate 9, the spool shaft 16 is
, The deflection of the spool shaft 16 is not so large, and the spool touch phenomenon hardly occurs. Therefore, the rotation of the spool 12 becomes smooth even during a load operation such as a drag operation or a winding operation. After adjusting the braking force, the thumb rest 17 is pushed downward. Here, the thumb rest 17 moves to the lower detached position along the long holes of the side plates 8 and 9. The movement of the thumb rest 17 causes the clutch yoke 40 to move outward, and the clutch yoke 40
Is also moved in the same direction. In this state, the engagement between the pinion gear 32 and the spool 12 is released, and the clutch is released. In this state, 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. With the clutch disengaged, spool the spool shaft 16 while thumbing the spool with the thumb resting on the thumb rest.
When the fishing rod is shaken while tilting the reel in the axial direction so as to be along the vertical plane, a lure is thrown and the spool 12 rotates vigorously in the line payout direction.

In this state, since the spool 12 rotates in the line pay-out direction, the spool 12 is braked by the first casting control mechanism 22 and the centrifugal brake 23 and thereafter, and backlash is less likely to occur. In addition, since both the spool shaft 16 and the spool 12 are supported by the rolling bearings 20a, 20b, 35a, and 35b, the rotation efficiency does not easily decrease even when the spool 12 rotates at high speed, and the lure jumps out vigorously. Then, just before the landing, the summing is stopped and the handle 2 is rotated. Thereby, the clutch mechanism 13 is automatically engaged. Then, the lure is retrieved by manipulating the rods and reels and waiting for a hit.

[Other Embodiments] (a) In the first embodiment, the braking force of the first casting control mechanism 22 acts on the spool 12 at the time of winding the yarn. Is connected by a one-way clutch, it is possible to prevent the braking force of the first casting control mechanism 22 from acting on the spool when winding the line.

(B) The mounting location of the one-way latch is
The present invention is not limited to the above-described two embodiments, and may be mounted at any place between the rotating member interlocking with the spool and a contact member that can be pressed against a fixed member such as a reel body. (C) The form of the one-way clutch is not limited to the roller clutch, but may be another type of clutch such as a pawl type or a type using a coil spring.

[0052]

According to the present invention, when the spool rotates in the line payout direction as in the case of casting,
The rotating member rotates in the line payout direction in conjunction with the spool, and the contact member and the rotating member are connected by the one-way clutch.The contact member rotates and presses against the fixed member to generate a braking force. A braking force acts. However, when the rotating member rotates in the line winding direction, the rotating member and the contact member are shut off, so that the contact member does not rotate and no braking force is generated. Therefore, no braking force acts on the spool when the line is wound, and the fishing line can be wound lightly.

[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 plan view thereof.

FIG. 3 is an enlarged sectional view of the periphery of the spool.

FIG. 4 is a side cutaway view thereof.

FIG. 5 is a side cutaway view thereof.

FIG. 6 is a cross-sectional side view when the front cover is in a closed position.

FIG. 7 is a cross-sectional side view with the front cover in an open position.

FIG. 8 is a view corresponding to FIG. 2 of another embodiment.

FIG. 9 is a view corresponding to FIG. 3 of another embodiment.

[Explanation of symbols]

 Reference Signs List 1 reel body 12 spool 16 spool shaft 23 centrifugal brake mechanism 24 second casting control mechanism 66 rotating section 67 slider 68 brake liner 70 one-way clutch 80 magnetic plate 84 brake liner 85 brake adjusting section

Claims (6)

[Claims] 1. A braking device for a dual-bearing reel that brakes a spool by friction, comprising: a fixed member; a contact member provided on a rotating member interlocked with the spool and capable of pressing against the fixed member; A one-way clutch interposed between the rotating member and a one-way clutch that connects the contact member and the rotating member when the rotating member rotates in the line unwinding direction and disconnects the contact member when the rotating member rotates in the line winding direction. Braking device. 2. The braking device for a dual-bearing reel according to claim 1, further comprising an adjusting member for adjusting a pressure contact force between the contact member and the fixed member. 3. The spool member according to claim 1, wherein the rotating member is a spool shaft non-rotatably connected to the spool, and the contact member is connected to the spool shaft via the one-way clutch. Dual bearing reel braking device. 4. The braking device for a dual-bearing reel according to claim 1, wherein the rotating member is the spool, and the contact member is connected to the spool via the one-way clutch. 5. The contact member includes a magnetic member, and the adjusting member adjusts the pressure contact force between the contact member and the rotating member by changing the number of magnetic fluxes acting on the magnetic member. The braking device for a dual-bearing reel according to any one of the above. 6. A slider interlocked with said spool, a slider supported by said holder so as to be movable substantially in the radial direction of said spool, and said slider located outside said slider. And a cylindrical member arranged so as to be able to contact, further comprising a centrifugal braking mechanism that brakes the spool by moving the slider in the radial direction by centrifugal force and contacting the cylindrical member, The said contact member is hold | maintained by the said holding body.
6. The braking device for a dual-bearing reel according to any one of claims 1 to 5.