JPH10271939A - Centrifugal brake device for double bearing reel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable the easy practice of regulating operations of a braking force. SOLUTION: This centrifugal brake device 23 for a double bearing reel is capable of braking a spool 12 freely and ratably supported on a reel body by a centrifugal force and is equipped with a cylindrical brake case 65, a rotating part 66, plural sliding pieces 67, plural locking members and plural operating members 73. The brake case 65 is provided in the reel body and has a liner 68 on the inner peripheral side. The rotating part 66 is arranged on the inside of the liner 68 and interlockingly rotated with the spool 12. The plural sliding pieces 67 are supported on the rotating part 66 freely movably in the radial direction and moved to the outside of the rotating part 66 according to the rotation of the rotating part 66 and can be brought into contact with the liner 68. The plural locking members are capable of respectively regulating the movement of each sliding piece 67 to the liner 68. The plural operating members 73 are capable of respectively operating each locking member from the side of the spool 12.

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 centrifugal braking device for braking a spool rotatably supported on a reel body by centrifugal force.

[0002]

2. Description of the Related Art Generally, a dual bearing reel includes a reel body, a spool rotatably mounted on the reel body, and a handle for rotating the spool. The reel body has a pair of side plates arranged so as to face each other at a predetermined interval, and a side cover that covers the outside of each side plate. A spool shaft passes through the spool, the spool is fixed to the spool shaft, and the spool shaft is rotatably supported by the reel body. A dual-bearing reel equipped with a centrifugal braking device for braking the spool is known.

A centrifugal braking device generally includes a cylindrical sliding portion detachably provided on a side plate opposite to a handle of a reel body and having a sliding surface on an inner peripheral side, a rotating member, and a plurality of guide members. And a plurality of sliders. The rotating member rotates in conjunction with the spool. The guide members are provided at intervals in the circumferential direction of the rotating member, and are arranged along the radial direction. The slider is a member that is movably supported in the radial direction by the guide member and can abut on the sliding surface. In this centrifugal braking device, when the spool rotates, the slider moves radially outward due to centrifugal force, and contacts the sliding surface to brake the spool. Since this centrifugal force increases in proportion to the square of the speed, when the spool rotates at a low speed as in the case of winding the yarn, the braking force does not act much and the rotation of the spool does not become heavy. On the other hand, when the spool rotates at a high speed as in the case of casting, a large braking force acts, and it is easy to prevent backlash of the fishing line.

In this type of centrifugal braking device, the number of sliders moving in the radial direction is changed in order to adjust the braking force. For this purpose, the centrifugal braking device is provided with a lock mechanism for switching the slider between an operation position where it can contact the sliding surface and a non-operation position where it cannot contact the sliding surface. In order to operate this lock mechanism, conventionally, the side cover of the reel body is opened, and one or a plurality of sliders are manually switched to the operation position or the non-operation position.

[0005]

For example, when lures of different weights, such as plugs and worms, are used during lure fishing, if the braking force is constant, casting is performed according to the weight of the lures. The flight distance fluctuates. For this reason, in such a case, it is better to change the number of the sliders in order to adjust the braking force when lures having different weights are mounted. However, in the above-described conventional configuration, each time the braking force is adjusted, the side cover opposite to the handle must be opened to change the number of the sliders arranged in the operation position. troublesome.

An object of the present invention is to make it possible to easily adjust a braking force in a centrifugal braking device for a dual-bearing reel.

[0007]

A centrifugal braking device for a dual-bearing reel according to a first aspect of the present invention is a device for braking a spool rotatably supported on a reel body by a centrifugal force. A member, a rotating member, one or a plurality of sliders, one or a plurality of locking members, and one or a plurality of operating members. The cylindrical sliding portion is provided on the reel body, and has a sliding surface on the inner peripheral side. The rotating member is disposed inside the sliding portion, and rotates in conjunction with the spool. The one or more sliders are movably supported by the rotating member, and can move to the outside of the rotating member in accordance with the rotation of the rotating member and contact the sliding surface. The one or more lock members regulate the movement of the slider to the sliding surface side. One or a plurality of operation members can operate the lock member from the spool side of the spool.

In this centrifugal braking device, when the spool rotates, the rotating body rotates in conjunction therewith, and the slider moves outward due to centrifugal force. When the slider comes into contact with the sliding surface of the sliding portion, a braking force acts on the rotating body due to friction, and the spool is braked. This braking force is proportional to the number of sliders that contact the sliding surface. When changing the number of sliders in contact with the sliding surface, the operating member is operated from the spool side of the spool, and the movement of the slider to the sliding surface side is regulated by the lock member. Since the slider whose movement is restricted does not come into contact with the sliding surface, the braking force is reduced by the number of sliders whose movement is restricted. Here, a plurality of braking states from a maximum braking state in which all the sliders abut on the sliding surface to a non-braking state in which all the sliders are prevented from abutting are adjusted in a stepwise manner. Since the operation can be performed from the spool side of the spool, the operation of adjusting the braking force can be easily performed without opening the side cover.

A centrifugal braking device for a dual bearing reel according to a second aspect of the present invention is the device according to the first aspect, wherein the rotating member comprises a plurality of guide members provided at intervals in a circumferential direction and arranged along a radial direction. And a plurality of sliders, which are supported movably in the radial direction by a guide member. In this case,
Since the slider moves in the radial direction, the slider moves efficiently to the sliding surface side due to centrifugal force, and when it comes into contact, the force is efficiently transmitted to the sliding surface, improving braking efficiency. I do.

A centrifugal braking device for a dual bearing reel according to a third aspect of the present invention is the device according to the first or second aspect, wherein the spool comprises:
A support portion including a tubular portion through which the spool shaft passes, and flange portions formed at both ends of the tubular portion and having openings near the outer peripheral portion, wherein the operating member is movably supported by the rotating member at two radial positions. And an operating portion formed integrally with the support portion and provided to face the opening of the flange portion of the spool, wherein the slider has a flange portion locked by the lock member, and the lock member is It has a locking portion for locking the flange, and moves in the radial direction integrally with the operation member. In this case, when the operating member is moved to the radially inward position by the operating portion provided facing the opening of the flange portion of the spool, the locking member locks the flange portion of the slider in conjunction therewith. The locking portion of the member moves radially inward. As a result, the slider cannot contact the sliding surface. On the other hand, when the operation member is moved to the position radially outward by the operation portion, the locking portion moves radially outward in conjunction with the operation member. As a result, the slider can contact the sliding surface. Here, the movement of the slider can be easily restricted by the operation of moving the operation portion radially inward from the spool side of the spool.

A centrifugal braking device for a dual-bearing reel according to a fourth aspect of the present invention is the device according to the first or second aspect, wherein the spool comprises:
A tubular portion through which the spool shaft passes, and a flange portion formed at both ends of the tubular portion and having an opening near the outer peripheral portion, wherein the operating member is supported by the rotating member so as to be swingable, An operating portion formed integrally and facing the opening of the flange portion of the spool, the slider has a flange portion locked by a lock member, and the lock member locks the flange portion. And has a locking portion that moves in the radial direction according to the swing of the operation member.
In this case, when the operation member is swung by the operation portion provided facing the opening of the flange portion of the spool, the locking portion of the lock member that locks the flange portion of the slider in conjunction therewith is pivoted. Move radially inward or outward. When the locking portion moves inward in the radial direction, the slider cannot contact the sliding surface. on the other hand,
When the locking portion moves radially outward, the slider can contact the sliding surface. Here, the movement of the slider can be easily restricted by the swinging operation of the operation section from the spool side of the spool.

[0012]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiment 1 FIG. 1 is a plan view of a dual-bearing reel employing 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 includes a plate-like arm portion 2a,
It is a double handle type having grips 2b rotatably attached to both ends of the arm 2a. Arm part 2a
The outer surface of is made 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 unit 1 has a frame 5 and first and second side covers 6 and 7 mounted on both sides of the frame 5. 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 10 connecting these side plates 8 and 9. On the inner surfaces of the side plates 8 and 9 facing each other, columnar spool storage spaces 14 are respectively formed. The side plate 8 has a circular opening 8a for attaching and detaching the spool 12. The first side cover 6 is attached to the side plate 8 by a swing shaft 11 arranged at the front end of the side plate 8 so as to be freely swingable and movable by a predetermined distance in the axial direction. Thereby, the first side cover 6 can be freely opened and closed with respect to the side plate 8. The first side cover 6 is
It is urged by the coil spring 4 in a direction away from the side plate 8. The first side cover 6 is locked and unlocked with respect to the side plate 8 by a bayonet structure provided in a brake case 65 of the centrifugal brake mechanism 23 described later.

In the pair of frames 5, a spool 12 is provided.
And a level wind mechanism 15 for uniformly winding the fishing line in the spool 12 and a thumb rest 17 which also serves as a clutch lever and serves as a contact for a thumb when performing summing. Between the frame 5 and the second cover 7, a gear mechanism 18 for transmitting the rotational force from the handle 2 to the spool 12 and the level wind mechanism 15, and a clutch disengaging mechanism 19 for disengaging and disengaging the clutch. And a disengagement control mechanism 20 for controlling engagement and disengagement of the clutch in accordance with an operation of the thumb rest 17, a drag mechanism 21, and a casting control mechanism 22 for adjusting a resistance force when the spool 12 rotates. Have been. Further, a centrifugal brake mechanism 23 for suppressing backlash during casting is arranged between the frame 5 and the first cover 6.

The spool 12 has a dish-shaped flange portion 12a on both sides, and a cylindrical bobbin trunk 12b between the flange portions 12a. Also, the spool 12
Has a cylindrical boss 12c integrally formed on the inner peripheral side of the bobbin trunk, and is non-rotatably fixed to a spool shaft 16 passing through the boss 12c, for example, by serration coupling. 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 peripheral edge of the flange portion 12a is disposed at the inner peripheral portion of the spool storage space 14 with a gap C1 therebetween. This gap C1 is, for example, 0.2
mm, the periphery of the flange portion 12a is covered by the spool storage space 14 with a small gap C1 from the outside in the radial direction, so that fishing line does not easily enter the spool shaft 16 from the spool 12, and The fishing line is less likely to become entangled with the shaft 16. In addition, six rectangular notches 12e are formed in the peripheral portion of the flange portion 12a on the left side in FIG. 3 at equal intervals in the circumferential direction.

The bobbin trunk 12b is provided with a plurality of holes 12d for weight reduction. The hole 12d is, for example, a circular hole, and is formed on two circumferences of the bobbin trunk 12b that are spaced apart in the axial direction with a space in the circumferential direction. By reducing the weight of the spool 12, the rotation efficiency of the spool during free rotation is improved. The spool shaft 16 extends outside the second side cover 7 through the side plate 9. The extended one end is rotatably supported by a bearing 24a on a boss 29 formed on the second side cover 7. The other end of the spool shaft 16 is rotatably supported by a bearing 35 in the centrifugal brake mechanism 23. These bearings are sealed ball bearings.
The spool shaft 16 has a large-diameter portion 16a at the center to which the spool 12 is fixed, and two small-diameter portions 16b and 16c formed at both ends.

The large diameter portion 16a is disposed in a space 12e 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. Further, a serration 16e is formed on the outer peripheral surface of the left end in FIG. 3 for connecting the rotating part 66 of the centrifugal brake mechanism 23 so as not to rotate. The right end in FIG. 3 of the large diameter portion 16a is disposed close to the boss portion 12c of the spool 12, and an engaging pin 16f constituting a clutch mechanism is fixed thereto. The engagement pin 16f penetrates the large diameter portion 16a along the diameter, and both ends protrude in the radial direction.

The small diameter portion 16c on the left side is supported by a brake case 65 by a bearing 35. Two small steps 16g and 16h are formed in the small diameter portion 16b on the right side in a stepwise manner. The left side of the step portion 16g is a large diameter portion 16i of the small diameter portion 16b, the right side is a middle diameter portion 16j, and the right side of the step portion 16h is a small diameter portion 16k. The right side of the small diameter portion 16k is a large diameter shaft support portion 16l, which is supported by a bearing 24a. This shaft support 16l
Is shorter than the axial length of the bearing 24a so as to reduce the rotational resistance. On the right side of the shaft support 161 are a small-diameter groove portion 16m for preventing falling off and a locking portion 16n having a larger diameter than that. Groove 16m
A ring-shaped spring member 29a is arranged on the inner peripheral portion of the boss portion 29 around. The inner diameter of the spring member 29a is smaller than the locking portion 16n, and when the spool shaft 12 moves in the axial direction, the spring member 29a is locked to the locking portion 16n. Thereby, when the side cover 6 is opened, the spool 12 and the spool shaft 16 do not immediately fall off. Note that both ends of the spool shaft 16 have spherical surfaces in order to suppress an increase in rotation resistance.

As shown in FIG. 2, the level wind mechanism 15 includes a guide cylinder 25 fixed between the pair of side plates 8 and 9.
, A worm shaft 26 rotatably supported in the guide cylinder 25, and a line guide 27. A gear 28a constituting the gear mechanism 18 is fixed to an end of the worm shaft 26. Worm shaft 2
6, a spiral groove 26a is formed, and a part of the line guide 27 meshes with the spiral groove 26a.
For this reason, the worm shaft 26
Is rotated, the line guide 27 reciprocates along the guide tube 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 and meshes with the gear 28a. As shown in FIG. 3, the pinion gear 32 is a tubular member that extends inward from the outside of the side plate 9 and has a spool shaft 16 penetrating at the center thereof. I have. The pinion gear 32 is rotatably and axially movably supported on the side plate 9 by a bearing 24b. This bearing 24b is also a shield ball bearing. The pinion gear 32 is formed on the outer peripheral portion on the right end side in FIG. 3 and meshes with the main gear 31, a meshing portion 32b formed on the other end side, and is formed between the tooth portion 32a and the meshing portion 32b. It has a constricted portion 32c. The meshing portion 32b is formed by a concave groove formed along the end face of the pinion gear 32 along the diameter, and the engaging pin 16f fixed through the spool shaft 16 is locked therein. Here, the pinion gear 32 moves outward, and the engagement portion 32 b and the engagement pin 16 of the spool shaft 16 are moved.
When f is separated, the rotational force from the handle shaft 30 is not transmitted to the spool 12. The engagement mechanism 32b and the engagement pin 16f constitute a clutch mechanism. Here, since the clutch mechanism is disposed near the boss portion 12c of the spool 12, when the rotational force is transmitted from the pinion gear 32 to the spool 12 via the spool shaft 16, the twist of the spool shaft 16 is reduced. As a result, the rotation transmission efficiency is improved, and the rotation feeling is improved.

On the inner peripheral surface of the pinion gear 32, two steps 32d and 32e are formed. The left side of the step portion 32d on the left side in FIG. 4 is a large-diameter inner surface 32f, and the right side is a medium-diameter inner surface 32g. The right side of the step portion 32e is a small-diameter inner surface 32h. Here, the pinion gear 3
The medium-diameter inner surface 32g of the spool shaft 16 has a small-diameter portion 16
b can contact the outer peripheral surface of the large diameter portion 16i, and the small diameter inner surface 32h can contact the outer peripheral surface of the middle diameter portion 16j. The length of the large-diameter inner surface 32f is shorter than that of the large-diameter portion 16i, and the length of the medium-diameter inner surface 32g is substantially the same as that of the medium-diameter portion 16j.

On the other hand, the meshing portion 32 of the pinion gear 32
On the outer peripheral surface on the b side, a shaft support portion 32 that can contact the bearing 24b is provided.
i and a separating portion 32j slightly smaller in diameter than the shaft supporting portion 32i. A step of C2 is formed between the separation part 32j and the shaft support part 32i. Therefore, the bearing 2
A gap C2 is formed between 4b and the separation part 32j. The gap C2 is, for example, about 0.1 mm, and is smaller than the gap C1 of the flange portion 12a of the spool 12. The separation part 32j is formed on the outer peripheral surface facing the bearing 24b when the clutch is on.

Thus, in the clutch-on state in which the engagement portion 32b is engaged with the engagement pin 16f, as shown in FIG. 4A, the inner surface 32g of the medium diameter comes into contact with the outer surface of the large-diameter portion 16i, and The inner surface 32h contacts the outer peripheral surface of the middle diameter portion 16j. Further, as shown in FIG.
2 and the bearing 24b, a gap C2 is formed,
The pinion gear 32 is supported by the spool shaft 16 so as to be rotatable and movable in the axial direction. Here, spool shaft 1
Since the pinion gears 32 are supported at two positions with respect to 6, the pinion gears 32 do not tilt even if a force is applied during the winding rotation, and poor contact with the main gear 31 hardly occurs.

On the other hand, in the clutch-off state in which the pinion gear 32 moves rightward in FIG. 4 and the engagement portion 32b is disengaged from the engagement pin 16f, as shown in FIG. 16i, separated from the outer peripheral surface,
2h is separated from the outer peripheral surface of the middle diameter portion 16j. For this reason,
The pinion gear 32 separates from the spool shaft 16 and is not supported by the spool shaft 16. But at this time,
As shown in FIG. 5B, the shaft support portion 32i on the outer peripheral surface contacts the bearing 24b, and the pinion gear 32 is rotatably and axially movable by the bearing 24b. For this reason,
During free rotation, the pinion gear 32 does not tilt and break, and does not contact the spool shaft 16. Therefore, the rotation resistance does not increase due to the contact between the pinion gear 32 and the spool shaft 16 during free rotation.

Even if the spool shaft 16 bends due to the force acting on the spool 12 during winding, the pinion gear 32 is supported by the pinion gear 32 when it comes into contact with the bearing 24b.
As described above, the spool shaft 16 does not bend. This gap C2
Is smaller than the gap C1, the spool touch phenomenon in which the flange portion 12a comes into contact with the end face of the flange accommodating portion 14 even when a force acts on the spool 12 does not easily occur.

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. Slots (not shown) in side plates 8 and 9 of frame 5
Are formed, and the rotating 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 yoke 40 is arranged on the outer peripheral side of the spool shaft 16, and
The number of pins 41 (only one is shown) allows the spool shaft 16
Is supported so as to be movable in parallel with the axis of the. 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. 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. Also, on the outer periphery of each pin 41 supporting the clutch yoke 40,
A spring 42 is disposed between the clutch yoke 40 and the second cover 7, and the clutch yoke 40 is constantly urged inward by the spring 42.

With such a configuration, in the normal state, the pinion gear 32 is located at the inner clutch engagement position.
The engagement pin 32 of the spool shaft 16 is engaged with the engagement portion 32b.
f is 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 and the engagement pin 16f
Is disengaged and the clutch is turned off.

As shown in FIG. 2, the drag mechanism 21 presses 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 Casting control mechanism 22
Has a plurality of friction plates 51 arranged so as to sandwich both ends of the spool shaft 16 and a cap 52 for adjusting a clamping force of the spool shaft 16 by the friction plates 51, as shown in FIG. I have. Left friction plate 51
Are mounted in the brake case 65.

As shown in FIG. 3, the centrifugal brake mechanism 23 includes a brake case 65, a rotating part 66 provided in the brake case 65, and guide members arranged at intervals in a circumferential direction of the rotating part 66. 71, a slider 67 movably supported in the radial direction by the guide member 71, and a slider 67
A lock member 72 for restricting the movement of the lock member 72 toward the brake case 65, and an operation member 73 for operating the lock member 72
And

The brake case 65 is a cylindrical member having a bottom and is removably attached to the opening 8a of the side plate 8 by a bayonet structure. The brake case 65 is urged outward from the first side cover 6 by the conical coil spring 4b, as shown in FIG. The brake case 65 is fixed to a detachable handle 69 exposed outside the first side cover 6. By rotating the detachable handle 69, the brake case 65 is detached from the side plate 8 and jumps out to the left side in FIG. 2 together with the first side cover 6. When the first side cover 8 is swung in this state, the spool 12 can be taken out together with the spool shaft 16. At the center of the brake case 65, a cylindrical bearing mounting portion 65a for mounting the bearing 35 is provided.
Are formed. The friction plate 5 of the casting control mechanism 22 is provided at the bottom of the bearing mounting portion 65a.
1 is arranged. Further, a cylindrical liner 68 for braking is mounted on the inner periphery of the periphery of the brake case 65.

The rotating part 66 includes a disk part 66a and a disk part 6
Cylindrical guide mounting portion 6 integrally formed on the outer surface of 6a
6b. The disk portion 66a is non-rotatably connected to the spool shaft 16 by serration coupling.
The guide mounting portion 66b is arranged on the outer peripheral side of the bearing mounting portion 65a. A ring-shaped stepped portion 66c is formed on the outer peripheral side of the guide attachment portion 66b of the disk portion 66a. A ring-shaped lid member 7 is formed so as to cover this step 66c.
4 is attached to the disk portion 66a by bolts. As shown in FIG. 4, on the side surface of the lid member 74, six bow tie-shaped openings 74a are formed at intervals in the circumferential direction.

The guide members 71 are provided at equal intervals in the circumferential direction at, for example, six locations on the outer peripheral surface of the guide mounting portion 66b. The guide member 71 is a rod-shaped member arranged along the radial direction, and its tip is arranged at an interval from the liner 68. The number of guide members 71 may be any number as long as it is one or more. The slider 67 is a cylindrical member having a flange 67a on the center side of the spool shaft, and is supported movably in the radial direction by a guide member 71 penetrating the center. The tip of the slider 67 can abut the liner 68, and the abutment with the liner 68 generates a braking force by friction.

As shown in FIGS. 4 and 5, the lock member 72 is formed integrally with the operation member 73. The lock member 72 is a fork-shaped member that extends bifurcated outward from the lower end of the operation member 73, and locks the flange 67 a of the slider 67 so that the slider 67 faces the liner 68. Restrict movement to. The lock member 72 extends around the slider 67 through the opening 74 a of the lid member 74.

The operation member 73 is a plate-shaped member, and the tip portion 73a for performing the operation is provided at the flange portion 1 of the spool 12.
It is bent inward and extends from a rectangular notch 12e formed in 2a. The proximal end 73b of the operation member 73 is disposed movably in the radial direction in the stepped portion 66c, and is wider than the distal end 73a in the middle thereof. Protrusions 75 for positioning and holding the operation member 73 between the operating position and the non-operating position are provided on both sides of the wide portion at an interval above and below in FIG. A holding member 76 made of an elastic resin is disposed in the opening 74 a so as to face the projection 75. The holding member 76 is a linear member that is bent in a symmetrical hairpin shape, and is urged toward the protrusion 75. On both inner surfaces of the holding member 76 opposed to the projections 75, for example, two projections 7 for locking the projections 75 are provided.
6a are respectively formed. When the protrusion 75 is fitted between the protrusions 76a, the operation member 73 is disposed at the operation position and the non-operation position. And the operation member 73
Is located at the upper working position in FIG.
And the slider 67 can be brought into contact with the liner 68. When the operating member 73 is located at the non-operating position on the lower side in FIG. 4, the lock member 72 also moves down, and the slider 67 whose flange 67a is locked to the lock member 72 moves toward the liner 68. Is restricted and the liner 68 cannot be contacted. Here, since the distal end portion 73a of the operating member 73 can be operated from the spool 12, the braking force can be easily adjusted by adjusting the number of the contactable sliders 67 without removing the side cover 8.

Next, the operation 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 engaging pin 16f of the spool shaft 16, and the clutch is turned on.
Main gear 31, pinion gear 32 and spool shaft 16
Through the spool 12. At this time, by adjusting the tightening amount of the cap 52 of the casting control mechanism 22, it is possible to adjust the resistance force when the spool shaft 16 rotates. When the handle 2 is rotated in this state, the rotation is transmitted to the spool 12 via the gear mechanism 18, and the spool 12 rotates. However, since the rotation speed at this time is relatively low, the braking force by the centrifugal brake mechanism 23 is small.

When casting is performed, the braking force is adjusted by the centrifugal brake mechanism 23 in consideration of the weight of the lure and the like in order to suppress the crash. When adjusting the braking force, the operating member 73 is moved to the radially outward working position or the inner non-working position by vertically operating the tip portion 73a by hand. When the operation member 73 is located at the operation position,
The restriction by the lock member 72 is released, and the slider 67 can contact the liner 68. On the other hand, when the operation member 73 is located at the non-operating position, the lock member 72
The flange 67a is locked to restrict the movement of the slider 67 in the radial direction, so that the slider 67 does not hit the liner 68. Therefore, to maximize the braking force, 6
When all the operating members 73 are arranged at the operation positions, and when braking is not performed, all the six operation members 73 are arranged at the non-operation positions. When it is desired to obtain an intermediate braking force, one or more of the six operating members 73 are arranged at the operation position, and the rest are arranged at the non-operation position. Thereby, the spool 1
The operation of adjusting the braking force to seven braking states including the non-braking state by the operation from the two sides can be easily performed.

After adjusting the braking force, the thumb rest 17
Press down. Here, the thumb rest 17 is attached to the side plate 8,
It moves to the lower release position along the slot 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. In this state, the engagement between the engagement portion 32b of the pinion gear 32 and the engagement pin 16f of the spool shaft 16 is released, and the clutch is turned off. In this state, the rotation from the handle shaft 30 is not transmitted to the spool 12 and the spool shaft 16,
Is in a free rotation state. When the clutch is off and the spool is tilted in the axial direction so that the spool shaft 16 is along the vertical plane while the spool is being thumbed on the thumb rest 17 and the fishing rod is shaken, the lure is thrown and the spool 1
2 rotates vigorously in the line feeding direction. At this time, by optimally adjusting the braking force, the occurrence of backlash can be suppressed as much as possible, and the flight distance can be optimized.

Embodiment 2 In the above embodiment, the sliding member is locked by moving the operating member in the radial direction. In the second embodiment, the sliding member is locked by swinging the operating member. The difference from the above embodiment is only the rotating part 66 of the centrifugal brake mechanism 23, the lock member 72, and the operation member 73, and the description of the other parts is omitted.

As shown in FIGS. 6 and 7, the rotating portion 66 has a disk portion 66a and a cylindrical guide mounting portion 66b integrally formed on the outer surface of the disk portion 66a. . The disk portion 66a is connected to the spool shaft 16 by serration coupling.
Are non-rotatably connected. The guide mounting portion 66b
It is arranged on the outer peripheral side of the bearing mounting portion 65a. Disk part 6
A step portion 66d is formed on the side surface of the spool 6a on the spool 12 side. For example, six swing pins 66 are provided on the stepped portion 66d toward the spool 12 at intervals in the circumferential direction.
e is formed. Further, six openings 66f are formed radially outward from the swing pin 66e. further,
As shown in FIGS. 8 and 9, two positioning pins 66 g and 66 h protruding toward the spool 12 are formed on the peripheral edge.

The guide members 71 are provided at equal intervals in the circumferential direction at, for example, six locations on the outer peripheral surface of the guide mounting portion 66b. The guide member 71 is a rod-shaped member arranged along the radial direction, and its tip is arranged at an interval from the liner 68. The number of guide members 71 may be any number as long as it is one or more. The slider 67 is a cylindrical member having a flange 67a on the center side of the spool shaft, and is supported movably in the radial direction by a guide member 71 penetrating the center. The tip of the slider 67 can abut the liner 68, and the abutment with the liner 68 generates a braking force by friction.

As shown in FIGS. 8 and 9, the lock member 72 is a member made of an elastic resin formed integrally with the operation member 73. The lock member 72 is a fork-shaped member that extends outward from the middle of the operation member 73 and is bifurcated and extends in the circumferential direction. The locking member 72 locks the flange 67 a of the The movement of the 67 toward the liner 68 is restricted. The lock member 72 extends around the slider 67 through the opening 66f of the disk portion 66a.

The operating member 73 is a cross-shaped member, and a tip portion 73a for performing an operation extends inward from a rectangular notch 12e formed in the flange portion 12a of the spool 12. The proximal end 73 b of the operation member 73 is
e is swingably supported. Further, locking recesses 73d are formed on both left and right sides of the intersecting portion in the middle to be elastically locked by the positioning pins 66g and 66h. The operating member 73 is positioned and held between the operating position and the non-operating position by elastically locking the locking concave portion 73d to one of the positioning pins. Here, in the operation position shown in FIGS. 8 and 9 in which the operation member 73 is locked to the positioning pin 66g, the slider 67 can contact the liner 68.
In the non-operation position where the slider 67 is locked by the positioning pin 66h, the movement of the slider 67 toward the liner 68 is restricted.
It cannot abut the liner 68. The other operations are the same as those of the above-described embodiment, and the description will not be repeated.

In the second embodiment, the distal end portion 73a
Can be swung from the spool 12 side, so that the braking force can be easily adjusted without removing the side cover 8. [Other Embodiments] (a) Instead of forming the operation member and the lock member integrally, they may be formed separately.

(B) The number of sliders may be any number as long as it is one or more. Also, the number of operating members and lock members may be any number as long as it is one or more. Moreover, when the number of operation members is smaller than the number of lock members and sliders, the lock members may be arranged so that a plurality of sliders are operated by one operation member. (C) The support structure of the slider is not limited to the structure supported by the guide member so as to be movable in the radial direction. Any support structure may be used as long as the structure can be freely supported, such as a structure that comes into contact with an outer sliding portion by rotation of the rotating portion.

[0047]

According to the present invention, there are a plurality of brakes from a maximum braking state in which all the sliders are brought into contact with the sliding surface to a non-braking state in which all the sliders are restricted from being brought into contact. Since the operation for adjusting the braking state stepwise can be performed from the spool side, the adjustment operation of the braking force can be easily performed without opening the side cover.

[Brief description of the drawings]

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

FIG. 2 is a cross-sectional view thereof.

FIG. 3 is an enlarged cross-sectional view of the spool shaft portion.

FIG. 4 is a front view of a centrifugal brake mechanism.

FIG. 5 is a partial perspective view thereof.

FIG. 6 is a diagram corresponding to FIG. 2 of the second embodiment.

FIG. 7 is a view corresponding to FIG. 3;

FIG. 8 is a diagram corresponding to FIG. 4;

FIG. 9 is a diagram corresponding to FIG. 5;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Reel main body 2 Handle 12 Spool 12a Flange part 12b Pin winding trunk part 16 Spool shaft 23 Centrifugal brake mechanism 65 Brake case 66 Rotating part 67 Slider 67a Flange part 68 Liner 71 Guide member 72 Lock member 73 Operating member 73a Tip part 73b Base edge

Claims (4)

[Claims] 1. A dual-bearing reel centrifugal braking device for braking a spool rotatably supported on a reel body by centrifugal force, the centrifugal braking device being provided on the reel body and having a sliding surface on an inner peripheral side. A cylindrical sliding portion, a rotating member disposed inside the sliding portion and rotating in conjunction with the spool, movably supported by the rotating member, and responsive to rotation of the rotating member, One or more sliders that move outward of the rotating member and can contact the sliding surface; and one or more locking members that regulate the movement of the slider toward the sliding surface. A dual-bearing reel centrifugal braking device, comprising: one or a plurality of operating members capable of operating the lock member from the spool side of the spool. 2. The rotating member includes a plurality of guide members provided at intervals in a circumferential direction and arranged in a radial direction, wherein the plurality of sliders are plural, and The centrifugal braking device for a dual-bearing reel according to claim 1, which is supported movably in a radial direction. 3. The spool includes a tubular portion through which a spool shaft passes, and flange portions formed at both ends of the tubular portion and having openings near the outer periphery. A support portion movably supported at two positions, and an operation portion formed integrally with the support portion and provided to face an opening of a flange portion of the spool; 3. The lock member according to claim 1, further comprising a flange portion locked to a member, wherein the lock member has a lock portion locking the flange portion, and moves in the radial direction integrally with the operation member. 4. Centrifugal braking device for dual bearing reel. 4. The spool includes a tubular portion through which a spool shaft passes, and flange portions formed at both ends of the tubular portion and having openings near outer peripheral portions, wherein the operating member is swingable by the rotating member. And a control unit formed integrally with the support unit and facing the opening of the flange of the spool. The slider is locked by the lock member. 3. The lock member according to claim 1, wherein the lock member has a locking portion that locks the flange portion, and moves in the radial direction according to the swing of the operation member. 4. Centrifugal braking device for bearing reel.