JP2001299164A - Spool shaft of double bearing reel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent rotation performance of a spool shaft from lowering in light load even when the spool shaft is inclined. SOLUTION: This spool shaft 20 of double bearing reel is a shaft to which a spool 12 is unrotatably attached and a pinion gear 32 for transmitting rotation is attached at an interval from the spool and the spool shaft 20 is equipped with a pair of first rotation supporting parts 20a and a second rotation supporting part 20b. The pair of first rotation supporting parts 20a are supported by a pair of bearings 26a mounted at an interval from a reel body 1 and installed in both ends of the shaft body. The second rotation supporting part 20b is arranged at a space from inner peripheral surface of the bearing at a position opposite to a bearing 26b attached to the reel body 1 and protrusively installed in cyclic state in a length L1 in axial direction shorter than a length L2 in axial direction of bearing between a part to which the spool and the gear member are attached.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a spool shaft, and more particularly to a dual-bearing reel which is rotatably mounted on a reel body.
The present invention relates to a dual-bearing reel spool shaft to which a spool is mounted so as not to rotate and a rotation transmitting gear member is mounted at a distance from the spool.

[0002]

2. Description of the Related Art A dual bearing reel generally has a reel body mounted on a fishing rod, a spool rotatably mounted on the reel body, and a handle for rotating the spool. The spool is non-rotatably mounted on a spool shaft passing through its center.

[0003] A rotation transmitting mechanism for transmitting rotation of the handle to the spool is provided between the handle and the spool. The rotation transmission mechanism has a handle shaft with a handle mounted at the end so that the handle cannot rotate, a main gear to which rotation is transmitted from the handle shaft via a drag mechanism, and a pinion gear that meshes with the main gear. The pinion gear also serves as a clutch mechanism for connecting and disconnecting the handle and the spool, and is mounted on the spool shaft so as to be movable in the axial direction and rotatable. The pinion gear moves axially between a clutch-on position where it engages with the spool shaft and a clutch-off position where it disengages.

[0004] In this type of dual-bearing reel, when the clutch is turned off and the spool is freely rotated to perform casting, the rotational performance of the spool in the line let-out direction is set so that the device can be cast farther. There is a demand for enhancement. For this reason, both ends of the spool shaft are rotatably supported by ball bearings. Also,
The spool is supported by a ball bearing between the spool and the pinion gear so that the winding efficiency is not impaired even when a large object is applied to the spool and a large bending moment is applied. Furthermore, by providing a small gap between the inner ring of the ball bearing and the outer peripheral surface of the spool shaft in this portion, the inner ring and the spool shaft do not contact during light load casting,
I try not to give resistance to rotation.

[0005]

In the above-mentioned conventional configuration,
Both ends are supported by bearings, and the bearing between the spool and the pinion gear is brought into contact with the spool shaft only under heavy load. However, when the mounting position of the bearings at both ends is shifted due to manufacturing errors or other causes and the spool shaft is tilted, this part will contact the spool shaft and give resistance to rotation even under a light load. There is.

[0006] It is an object of the present invention to prevent the rotation performance of the spool shaft from deteriorating under a light load even if the spool shaft is inclined.

[0007]

The spool shaft of the dual-bearing reel according to the first aspect of the present invention is rotatably mounted on the reel body of the dual-bearing reel, and the spool is non-rotatably mounted and spaced apart from the spool. A shaft on which a gear member for transmitting rotation is mounted, comprising a shaft main body, a pair of first rotation support portions, and a second rotation support portion. The shaft body has a spool and a gear member mounted thereon. The pair of first rotation support portions are supported by a pair of first bearings mounted on the reel body at an interval, and are provided at both ends of the shaft body. The second rotation support portion is arranged at a position facing the second bearing mounted on the reel body with a gap between the inner peripheral surface of the second bearing and a portion between the portion where the spool of the shaft body and the gear member are mounted. The second bearing has an axial length shorter than the axial length of the second bearing and is annularly projected.

[0008] In this spool shaft, the spool shaft is provided between the first rotation support portion provided at both ends and the second rotation support portion disposed between the spool and the gear member via first and second bearings. It is rotatably supported by the reel body. Here, the second rotation support portion is provided to protrude annularly with a length shorter than the axial length of the second bearing, and is arranged with a gap from the inner peripheral surface of the second bearing. Is arranged so as to face only a part of the inner periphery in the axial direction, and usually does not contact the inner periphery of the second bearing. For this reason, even when the spool shaft is tilted at a light load, the tilt angle until it contacts the inner peripheral surface of the bearing increases, and the allowable amount of tilt of the spool shaft increases. Therefore, even when the spool shaft is inclined, the rotation performance is less likely to be reduced at light load.

The spool shaft of the dual-bearing reel according to the second aspect of the present invention is the spool shaft according to the first aspect, wherein the axial length of the second rotation supporting portion is 10 to 35 times the axial length of the second bearing.
% Range. In this case, the axial length of the second rotation support portion is considerably shorter than the axial length of the second bearing, so that even when the spool shaft is inclined, it becomes more difficult to hinder rotation at light load.

According to a third aspect of the present invention, in the spool shaft of the dual bearing reel according to the first or second aspect, the outer diameter of the second rotation supporting portion is in the range of 95 to 99% of the inner diameter of the second bearing. . In this case, since the gap between the second rotation support portion and the second bearing is not so large, the spool shaft is reliably supported even if the spool shaft is bent by a heavy load. Invention 4
The spool shaft of the dual-bearing reel according to any one of the first to third aspects of the invention, wherein the first rotation support portion has an axial length shorter than the axial length of the first bearing at both ends of the shaft body. And protrude annularly. In this case, since the first rotary support portion is also shorter than the axial length of the first bearing, like the second rotary support portion, the contact area between the first bearing and the first rotary support portion is reduced, and the light load is reduced. Can further improve the rotation performance.

The spool shaft of the dual-bearing reel according to a fifth aspect of the present invention is the spool shaft according to the fourth aspect, wherein the axial length of the first rotation support portion is 15 to 40 times the axial length of the first bearing.
% Range. In this case, the axial length of the first rotation support portion is considerably shorter than that of the first bearing, but it is sufficient for the support of the spool shaft.

[0012]

1 to 3, a dual bearing reel adopting an embodiment of the present invention is a round reel for bait casting. This reel is a reel body 1
And a spool rotation handle 2 arranged on the side of the reel body 1 and a drag adjustment star drag 3 arranged on the reel body 1 side of the handle 2.

[Structure of Reel Body] The reel body 1 is a member made of an aluminum alloy, and includes a frame 5, a first side cover 6 and a second side cover 7, which are detachably fixed to both sides of the frame 5. And a mechanism mounting plate 11 detachably fixed to the second side cover 7. A spool 12 for winding a bobbin is rotatably and detachably mounted via a spool shaft 16 inside the reel body 1.

As shown in FIG. 3, a spool 12, a clutch operating lever 17 to be applied to a thumb for performing thumbing, and a level wind mechanism for uniformly winding fishing line in the spool 12 are provided in the frame 5. 18 are arranged. Also, between the frame 5 and the second side cover 7,
A rotation transmission mechanism 19 for transmitting the rotational force from the handle 2 to the spool 12 and the level wind mechanism 18, a clutch mechanism 21, and a clutch control mechanism 22 for controlling the clutch mechanism 21 in accordance with the operation of the clutch operation lever 17. And a drag mechanism 23 for braking the spool 12, a casting control mechanism 24 for adjusting a resistance force when the spool 12 rotates, and a centrifugal brake mechanism 25 for suppressing backlash during casting. .

The frame 5 has a pair of side plates 8, 9 arranged to face each other at a predetermined interval, and upper and lower connecting portions 10a, 1 for integrally connecting these side plates 8, 9 together.
0b. Each of the side plates 8 and 9 is a flat bottomed cylindrical member having a space inside which is circular when viewed from the spool axis direction. Slightly above the center of the side plate 9, a spool 12
There is formed a circular opening 9a for attaching and detaching. A rod mounting leg 4 for mounting a reel to a fishing rod is integrally formed with the lower connecting portion 10b.

The first side cover 6 is a member formed by pressing a metal having a flat bottomed cylindrical shape slightly curved outwardly. Most of the surface of the first side cover 6 is shown in FIG.
As shown in FIG. 5, the first surface portion 6a has a bright surface formed by cutting. On a part of the first surface portion 6a, there are scattered second surface portions 6b formed of various patterns such as characters and designs formed by pressing. The second surface portion 6b has a matte surface formed by shot blasting. At the center of the second side cover 6, a nameplate 6c is attached. This nameplate 6c
It is also a member for attaching and detaching the first side cover 6. As shown in FIG. 8, a corrosion-resistant layer 6 d made of an alumite film is formed on the front and back surfaces of the first side cover 6.

The first side cover 6 is manufactured by a process as shown in FIG. In step S1, first, a thin plate made of an aluminum alloy is prepared. In step S2, the prepared thin plate material is press-molded to obtain a desired flat-bottomed cylindrical pressed product. In step S3, a second surface portion 6b having a concave pattern is formed on the surface of the press-formed press product. This pattern may be a design or a character. In step S4, a matte surface is formed on the surface of the pressed product on which the pattern is formed, for example, by a shot blast method. As a result, the entire surface of the first side cover 6 becomes a matte surface. In step S5, the surface of the pressed product on which the matte surface has been formed is cut by, for example, a lathe, leaving the matte surface only on the second surface portion 6b, and forming a bright surface on the other portion, that is, the first surface portion 6a. I do. As a result, the first surface portion 6a becomes a glittering surface, and the second surface portion 6b formed of a concave pattern becomes a matte surface. In step S6, the obtained pressed product is processed by an anodizing method to form a corrosion-resistant layer made of an alumite film on the front and back surfaces. Thereby, the corrosion resistance of the first side cover 6 is improved.
The first side cover 6 is fixed to the side plate 8 with a nameplate 6c from inside by screws.

The second side cover 7 is also a flat-bottomed cylindrical press-formed product made of, for example, an aluminum alloy. The second side cover is entirely a bright surface, and does not perform the pattern pressing step shown in step S3 of FIG. 9 or the matte ground forming step shown in step S4. The second side cover 7 is detachably fixed to the side plate 9 of the frame 5 by two screws 13 (only one is shown in FIG. 2). This screw 13
It has a head that can be turned by hand. For this reason, the second side cover 7 can be easily attached and detached without using a tool such as a screwdriver.

The mechanism mounting plate 11 includes a clutch control mechanism 2
2 and a mechanism such as a rotation transmission mechanism 19 are mounted. The mechanism mounting plate 11 is provided so that each mechanism mounted therein can be integrally attached to and detached from the second side cover 7.
The mechanism mounting plate 11 is detachably fixed to the second side cover 7 with screws 14. This screw 14 is, for example,
Round head screw that can be turned by a tool. The mechanism mounting plate 11 is arranged in contact with the outer surface of the side plate 9.

[Structure of Spool and Spool Shaft] As shown in FIG. 3, the spool 12 has a dish-shaped flange portion 12a on both sides, and a cylindrical bobbin trunk portion between both flange portions 12a. 12b. The spool 12 is non-rotatably fixed to a spool shaft 16 that passes through the bobbin trunk 12b, 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.

The spool shaft 16 extends outside the second side cover 7 through the side plate 9 as shown in FIGS. The spool shaft 16 is provided at a rod-shaped shaft main body 20 and at both ends of the shaft main body 20, and is provided with a pair of ball bearings 26a, 26a.
And has a pair of first rotation support portions 20a protruding in an annular shape supported by the first rotation support portion 20a. Further, the spool shaft 16 is provided in the vicinity of the mounting portion of the spool 12 of the shaft main body 20, and has an annularly projecting second rotation support portion 20b supported by a ball bearing 26b. Further, a spool mounting portion 20c composed of a serration for mounting the spool 12,
A brake mounting portion 20d made of serrations for mounting the centrifugal brake mechanism 25 and a second rotation support portion 20b
And a gear mounting portion 20e for mounting a pinion gear (described later) between the first rotation support portion 20a and the second rotation support portion 20b on the right side. One end of the spool shaft 16 passes through the side plate 9 and
Projecting outward from the boss 7b fixed to the boss.

The ball bearing 26a on the right side of FIG. 3 is mounted on the boss 7b, and the ball bearing 26a on the left side is mounted on the side plate 8. The intermediate ball bearing 26b is mounted on a boss 11b formed on the mechanism mounting plate 11, as shown in FIG. Here, as shown in FIG. 6, the axial length L1 of the protruding first rotation support portion 20a is shorter than the axial length L2 of the inner race of the ball bearing 26a, for example, the axial length L
1 is in the range of 15 to 40% of the axial length L2. In addition, there is a gap between the outer peripheral surface of the first rotation support portion 20a and the inner ring of the ball bearing 26a. For example, the outer diameter of the first rotation support portion 20a is 98 to 99.5 of the inner diameter of the inner ring. % Range. The axial length L3 of the protruding second rotation support portion 20b is equal to the axial length L4 of the inner race of the ball bearing 26b.
Shorter, for example, the axial length L3 is the axial length L4
In the range of 10 to 35%. Also, the second rotation support 2
0b and the inner ring of the ball bearing 26b, there is a gap, for example, the outer diameter of the second rotation support portion 20b is
It is in the range of 95 to 99% of the inner diameter of the inner ring. Here, the gap between the ball bearing and the first rotary support portion 20a is set smaller than that of the second rotary support portion 20b, and the axial length of the second rotary support portion 20b is smaller than that of the bearing. It is set small.

As described above, the two rotation supporting portions 20a, 20b
Is set for the ball bearings 26a and 26b, even if the spool shaft 16 is tilted due to a manufacturing error or the like, it is difficult for the ball bearing 26b to contact both ends of the second rotation support portion 20b, and rotation of the ball bearing 26b is prevented. It is hard to be hindered. For this reason, even if the spool shaft 16 is inclined, the rotation performance under a light load is not easily reduced.

On the right side of the second rotation support portion 20b of the spool shaft 16, an engagement pin 21a constituting the clutch mechanism 21 is provided.
Has been fixed. The engagement pin 21a penetrates the spool shaft 16 along the diameter, and both ends protrude in the radial direction. As shown in FIG. 3, the clutch operation lever 17 is disposed behind the spool 12 at a rear portion between the pair of side plates 8 and 9. The clutch operation lever 17 slides vertically between the side plates 8 and 9. On the handle mounting side of the clutch operating lever 17, an engaging shaft 17a penetrating the side plate 9 is integrally formed by insert molding. The engagement shaft 17a is engaged with the clutch control mechanism 22. The tip of the engagement shaft 17a is close to the mechanism mounting plate 11. A long groove 11a is formed in the mechanism mounting plate 11 along the moving range of the engagement shaft 17a. By forming such a long groove 11a, even if the tip of the engaging shaft 17a is cut off to form a convex portion, the contact with the mechanism mounting plate 11 can be prevented by the long groove 11a. For this reason, it is not necessary to remove the convex portion in the post-processing, and the processing cost of the engagement shaft 17a can be reduced.

[Configuration of Rotation Transmission Mechanism] Rotation transmission mechanism 19
Has a handle shaft 30, a master gear 31 mounted on the handle shaft 30, and a cylindrical pinion gear 32 meshing with the master gear 31. The handle shaft 30 is rotatably mounted on the side plate 9 and the second side cover 7,
The rotation (reverse rotation) in the line pay-out direction is prohibited by the roller type one-way clutch 86 and the claw type one-way clutch 87.

As shown in FIG. 4, the one-way clutch 87 has a ratchet wheel 88 non-rotatably mounted on the handle shaft 30 and a ratchet claw 89 pivotally mounted on the mechanism mounting plate 11. I have. On the outer peripheral portion of the ratchet wheel 88, ratchet teeth 88a projecting in a substantially parallelogram shape are arranged at intervals in the circumferential direction, and the ratchet pawl 89 meshes with the ratchet teeth 88a, so that the handle shaft 30 is Rotation in the line feeding direction is prohibited. The ratchet claw 89 has a control piece 89a at its distal end for sandwiching the ratchet wheel 88 from both sides. The control piece 89a separates the ratchet pawl 89 from the ratchet wheel 88 during rotation in the yarn winding direction, and approaches the same during rotation in the yarn payout direction.

The master gear 31, as shown in FIG.
It is rotatably mounted on the handle shaft 30 and is connected to the handle shaft 30 via the drag mechanism 23. The drag mechanism 23 includes a star drag 3 and a drag plate 35 whose pressing force against the master gear 31 is changed by the star drag 3.
, A disc spring 36 for adjustment disposed between the star drag 3 and the one-way clutch 86, and a drag spacer 37 interposed between the disc spring 36 and the star drag 3. The drag spacer 37 is a molybdenum-containing nylon washer-shaped member.
The outer peripheral portion is engaged and fitted. A hole having an inner diameter larger than the outer diameter of the handle shaft 30 is formed in the inner peripheral portion.

The pinion gear 32 is, as shown in FIG.
It is a cylindrical member that extends inward from the outside of the side plate 9 and has a spool shaft 16 penetrating at the center, and is mounted on a gear mounting portion 20e of the spool shaft 16 so as to be movable and rotatable in the axial direction. An engagement pin 21a is provided at the left end of the pinion gear 32 in FIG.
Is formed with an engaging groove 32a. The clutch mechanism 21 is constituted by the engagement groove 32a and the engagement pin 21a. Also, a constricted portion 32b is provided in the middle part,
A gear portion 32c that meshes with the master gear 31 is formed at the right end.

[Structure of Clutch Control Mechanism] As shown in FIGS. 4 to 7, the clutch control mechanism 22 includes a clutch plate 55 that engages with the engagement shaft 17a,
The clutch cam 56 is engaged with the clutch cam 5 and rotates around the spool shaft 16, and the clutch cam 56 moves the clutch yoke 57 along the spool shaft 16. Further, the clutch control mechanism 22 has a clutch return mechanism 58 that turns on the clutch mechanism 21 in conjunction with the rotation of the spool 12 in the line winding direction.

The clutch plate 55 is a plate-like member formed in a fan shape, and is guided in a rotational direction by a guide portion (not shown) formed on the mechanism mounting plate 11. One end of the clutch plate 55 extends to a position in contact with the lower end of the engagement shaft 17a of the clutch operation lever 17 so as to move counterclockwise in FIG. 4 in conjunction with the downward movement of the clutch operation lever 17. The other end of the clutch plate 55 has a U-shaped locking portion 55 locked to the clutch cam 56.
a (FIG. 7) is formed, and the clutch plate 55 and the clutch cam 56 rotate around the spool shaft 16 in conjunction with each other.

The clutch cam 56 is a substantially ring-shaped member made of, for example, a synthetic resin such as polyacetal resin, and is rotatably mounted around the spool shaft 16 on the outer peripheral surface of a boss portion 11b formed on the mechanism mounting plate 11. Have been. The clutch cam 56 is prevented from coming off by a holding plate 60 screwed to the tip of the boss 11b. The holding plate 60 guides the clutch yoke 57 in the spool axial direction.
The pair of guide portions 60a, 60a are formed by bending.

The spool shaft 1 on the outer surface of the clutch cam 56
6, a pair of inclined cams 56a,
56a are formed. Also, the tilt cams 56a, 56
a of the inclined cams 57b, 5 of the clutch yoke 57 adjacent to
Depressions 56b, 56b in which 7b (described later) are stored are formed. An engagement pin 56c that engages with the locking portion 55a of the clutch plate 55 is formed on an outer peripheral portion of the clutch cam 56. Further, a protrusion 56d is formed on the outer peripheral portion of the clutch cam 56, and a return member 59 constituting the clutch return mechanism 58 is swingably mounted on the mechanism mounting plate 11 side of the protrusion 56d. Projection 56d
6, has a thickness that fills a gap between the mechanism mounting plate 11 and the second side cover 7, as shown in FIG. A connection hole 56e into which the connection pin 63 can be inserted is formed in the protrusion 56d in parallel with the spool shaft.

The connecting pin 63 is a member made of a synthetic resin such as polyacetal resin mixed with glass fiber, for example, and has a flange 63a for swingably connecting the return member 59. The flange 63a includes the mechanism mounting plate 11 and the return member 5
9 and the connecting pin 6
3 is retained. Thus, the protrusion 56d is provided with a thickness that fills the gap, and the return member 59 is connected to the protrusion 5d.
6d and the mechanism mounting plate 11, the return member 5
Even if a load is applied to 9, the clutch cam 56 is less likely to be deformed, and the return member 59 is less likely to float.

The clutch yoke 57 includes a clutch cam 56
Are arranged facing outward in the axial direction. The clutch yoke 57 includes two guide portions 60 erected between the mechanism mounting plate 11 and the second side cover 7 with the spool shaft 16 interposed therebetween.
a and 60a so as to be movable in the direction of the spool shaft 16. Further, the second side cover 7 and the clutch yoke 5
7 is urged axially inward (leftward in FIG. 6) by a coil spring 61 arranged in a compressed state on the outer peripheral side of the guide portions 60a, 60a.

The clutch yoke 57 includes a pinion gear 32
A semicircular engaging portion 57a is formed to engage with the constricted portion 32b. Clutch cam 5 of clutch yoke 57
6 are formed on the side surface facing the inclined cams 56a, 56b. The clutch cams 56 rotate counterclockwise in FIG.
When the inclined cams 57b, 57b ride on the a, 56a,
The clutch yoke 57 moves to the clutch off position on the right side in FIG. Further, the tilt cams 57b, 57b are
When the vehicle descends from a and 56a, it is urged by the coil spring 61 to return to the clutch-on position. This clutch yoke 57
The pinion gear 32 moves in the spool axis direction in conjunction with the movement of the clutch mechanism 21, and the clutch mechanism 21 switches between a clutch-off state and a clutch-on state. A step D is formed between the tip of the inclined cam 57b and the engaging portion 57a. By forming such a step D, the clutch cam 56 and the clutch yoke 57 when in the clutch-on position are provided.
And the thickness of the reel in the spool axial direction can be reduced.

The clutch return mechanism 58 includes a ratchet wheel 88 that rotates in association with the handlebar 2, the clutch cam 56 that rotates in association with the clutch operation lever 17,
Return member 59 swingably connected to clutch cam 56
A connecting pin 63 for swingably connecting the return member 59 and the clutch cam 56; and a toggle spring 62 for urging the return member 59.

The return member 59 is a plate member made of a metal such as a stainless alloy, and is swingably connected to the clutch cam 56 by a connection pin 63. The return member 59 is
The rotation of the clutch cam 56 causes the ratchet wheel 88 to rotate.
Move to an engagement position (FIG. 5) in contact with the ratchet teeth 88a of FIG. At the tip of the return member 59, an engaging claw 59a that contacts the ratchet teeth 88a and a guide claw 59b that is guided by an elongated guide groove 11c formed on the mechanism mounting plate 11 are formed by bending. At its base end, a connection hole 59c that is swingably connected to the clutch cam 56 by a connection pin 63 and a locking hole 59d for locking the toggle spring 62 are formed.

The toggle spring 62 comprises a torsion coil spring having one end locked to the return member 59 and the other end rotatably locked to the mechanism mounting plate 11. The toggle spring 62 distributes and urges the return member 59 to two positions, an engagement position and a non-engagement position, and holds the return member 59 at both positions. In the clutch return mechanism 58, when the clutch mechanism 21 is brought into the clutch off state by the pressing operation of the clutch operation lever 17, the clutch cam 56 rotates counterclockwise to move from the disengaged position shown in FIG. Ratchet teeth 88a shown
The return member 59 moves forward to the engagement position where it comes into contact with. At this time, until the toggle spring 62 exceeds the dead point, the return claw 59b is guided toward the ratchet wheel 88 by the guide claw 59b being guided by the outer edge of the guide groove 11c against the urging force of the toggle spring 62. When the robot moves forward and exceeds the dead center, it rotates counterclockwise and is guided by the inner edge of the guide groove 11c to move to the engagement position.

When the handle shaft 30 is rotated in the line winding direction by operating the handle 2 in a state where the return member 59 is in the engagement position, the engagement claws 59a of the return member 59 are pressed by the ratchet teeth 88a and are not engaged. Return to position. At the same time, the clutch cam 56 is rotated clockwise in FIG.
The clutch mechanism 21 is returned to the clutch-on state. [Structure of Centrifugal Brake Mechanism] As shown in FIG. 6, the centrifugal brake mechanism 25 includes a brake mounting base 70 made of a synthetic resin molded article non-rotatably mounted on the brake mounting portion 20d of the spool shaft 16, and a brake mounting base. Six guide shafts 71 erected radially on 70, six brake collars 72 movably mounted on the guide shafts 71, and a brake pipe 73 disposed on the outer peripheral side of the brake collar 72. Have.

The brake mounting base 70 is a thick disk-shaped member made of synthetic resin, and has concave portions 70a for accommodating the brake collar 72 at six locations in the circumferential direction. A guide shaft 71 erected radially in the recess 70a.
Are integrally formed. As shown in FIG. 10, the guide shaft 71 has a substantially oval cross section and is formed in a rod shape. The curvature radius R1 of the outer peripheral surface 71a on the upper side of FIG.
Is smaller than the radius of curvature R2 of the lower outer peripheral surface 71b. As a result, a step 75 is formed at the connection between the outer peripheral surfaces 71a and 71b. This connection part becomes a part (partition line) of the mold at the time of molding. Here step 75
By forming, burrs are less likely to occur during resin molding, and it is not necessary to perform deburring after molding.

The brake collar 72 is a member made of a synthetic resin having a substantially flanged cylindrical shape, and the flange can be locked to two projections (not shown) formed in the recess 70a at an interval in the radial direction. It is. Thereby, the brake collar 72 can be switched between a position where it can contact the brake pipe 73 and a position where it cannot contact the brake pipe 73. The brake pipe 73 is a thin cylindrical member made of metal, and is fixed to the mechanism mounting plate 11 by an appropriate fixing means such as adhesion.

[Operation of Dual Bearing Reel] When performing casting, the clutch operating lever 17 is pressed downward. Then, the clutch plate 55 moves counterclockwise in FIG. When the clutch plate 55 moves, the clutch cam 56 rotates counterclockwise in conjunction therewith, and the clutch yoke 57 moves to the clutch off position on the right side in FIG. As a result, the pinion gear 32 constituting the clutch mechanism 21 moves outward in the axial direction, and enters the clutch off state. In this clutch-off state, the spool 12 is in a free rotation state, and when casting is performed, the fishing line is vigorously fed out of the spool 12 due to the weight of the tackle.
At this time, even if the spool shaft 16 is inclined due to a manufacturing error or the like, the axial length of the second rotation support portion 20b is short, so that the spool shaft 16 does not easily come into contact with the ball bearing 26b, and the rotation performance does not easily decrease. .

When the device has landed, the handle 2 is rotated in the line winding direction. Then, the ratchet wheel 88 rotates in the yarn winding direction (clockwise in FIG. 5), and the ratchet pawl 8
9 is a ratchet wheel 88 by the action of the control piece 89a.
Rocks out of the As a result, the ratchet claw 89 does not come into contact with the ratchet wheel 88 at the time of winding the yarn, and the click sound due to the contact between the ratchet wheel 88 and the yarn at the time of winding the yarn does not occur. Further, when the ratchet wheel 88 rotates in the line winding direction, the ratchet teeth 88a abut on the engaging claws 59a at the tip of the return member 59, and press the return member 59 backward. Then, the return member 59 retreats beyond the dead center of the toggle spring 62 and is urged by the toggle spring 62 toward the non-engagement position.
In conjunction with this movement, the clutch cam 56 rotates clockwise in FIG. 5, the clutch yoke 57 moves to the clutch-on position by the urging force of the coil spring 61, and the clutch mechanism 21 enters the clutch-on state. Thus, the rotation of the handle 2 is transmitted to the spool 12, and the spool 12 rotates in the line winding direction.

When the handle shaft 30 rotates in the line winding direction, the rotation is transmitted to the level wind mechanism 18 and the fishing line is uniformly wound on the spool 12. [Other Embodiments] (a) In the above embodiment, a round dual-bearing reel has been described as an example. However, the spool is non-rotatably mounted on the spool shaft, the pinion gear is mounted, and
The present invention can be applied to all dual-bearing reels supported at different locations.

(B) In the above-described embodiment, the first rotation support portion 20a is constituted by an annular protrusion similar to the second rotation support portion, but need not be constituted by an annular protrusion.

[0046]

According to the present invention, the second rotation supporting portion is provided to protrude annularly with a length shorter than the axial length of the second bearing, and is arranged with a gap from the inner peripheral surface of the second bearing. Therefore, it is arranged so as to face only a part of the inner periphery of the second bearing in the axial direction, and usually does not contact the inner peripheral surface of the second bearing. For this reason, even when the spool shaft is tilted at a light load, the tilt angle until it contacts the inner peripheral surface of the bearing increases, and the allowable amount of tilt of the spool shaft increases. Therefore, even when the spool shaft is inclined at a light load, the rotation performance is not easily reduced.

[Brief description of the drawings]

FIG. 1 is a perspective view of a dual-bearing reel adopting an embodiment of the present invention, on a side opposite to a handle.

FIG. 2 is a perspective view of a handle side of the dual-bearing reel.

FIG. 3 is a longitudinal sectional view thereof.

FIG. 4 is a side view showing a state where a side cover is removed when a clutch is on.

FIG. 5 is a side view showing a state where a side cover is removed when a clutch is off.

FIG. 6 is an enlarged sectional view of the clutch control mechanism.

FIG. 7 is an exploded perspective view of a clutch control mechanism.

FIG. 8 is a schematic sectional view of a first side cover.

FIG. 9 is a flowchart showing a manufacturing process of the first side cover.

FIG. 10 is an enlarged view of a centrifugal brake mechanism.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Reel main body 2 Handle 12 Spool 16 Spool shaft 20 Shaft main body 20a 1st rotation support part 20b 2nd rotation support part 26a, 26b Ball bearing

Claims (5)

[Claims] A spool of a dual-bearing reel, which is rotatably mounted on a reel body of the dual-bearing reel, is non-rotatably mounted on the spool, and has a rotation transmitting gear member mounted at an interval from the spool. A shaft, on which the spool and the gear member are mounted, supported by a pair of first bearings mounted on the reel body at intervals, and provided at both ends of the shaft body. One
A pair of first rotation support portions, and a gap between the first rotation support portion and an inner peripheral surface of the second bearing at a position facing the second bearing mounted on the reel body, and the spool of the shaft body and the gear member And a second rotation support portion provided between the parts where the second bearing is mounted and having a length in the axial direction shorter than the length of the second bearing in the axial direction. 2. The dual-bearing reel spool shaft according to claim 1, wherein the axial length of the second rotation supporting portion is in the range of 10 to 35% of the axial length of the second bearing. 3. An outer diameter of the second rotation supporting portion is in a range of 95% to 99% of an inner diameter of the second bearing.
The spool shaft of the dual-bearing reel described in the above item. 4. The device according to claim 1, wherein the first rotation support portion is provided at both ends of the shaft main body so as to protrude annularly with an axial length shorter than the axial length of the first bearing. The spool shaft of the dual-bearing reel according to any one of the above. 5. The spool shaft of a dual-bearing reel according to claim 4, wherein an axial length of said first rotation supporting portion is in a range of 15 to 40% of an axial length of said first bearing.