JPH10271938A - Double bearing reel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the transmission efficiency of a torque from a pinion gear to a spool. SOLUTION: This double bearing reel comprises a reel body, a spool shaft 16, a spool 12, a clutch mechanism, a thumb rest and a handle. The spool shaft 16 is freely rotatably supported on the reel body and is equipped with a boss part 12c fixed to the spool shaft 12, a cylindrical line winding drum part 12b, formed on the peripheral side of the boss part 12c and capable of winding a fishing line, an inner space 12e formed adjacently to the boss part 12c on the inner peripheral side of the line winding drum side 12b and dishlike flange parts 12a formed at both ends of the line winding drum part 12b. The pinion gear 32 is a cylindrical gear through which the spool shaft 16 passes. The clutch mechanism is provided adjacently to the boss part 12c in the space 12e in the interior of the spool 12 and is capable of engaging and disengaging the spool shaft 16 from the pinion gear 32 by movement in the shaft direction.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dual-bearing reel, and more particularly to a dual-bearing reel having a spool shaft rotatably supported on a reel body.

[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 pair of side covers that cover the side plates from outside. The spool has a bobbin trunk portion to which a spool shaft is fixed penetrating the center, and flange portions formed at both ends of the bobbin trunk portion in a dish shape. The spool shaft is rotatably supported by the reel body, and one end of the spool shaft extends outward from the side plate. Between the handle and the spool, a rotation transmission mechanism consisting of a main gear and a pinion gear for transmitting the torque from the handle to the spool, and a clutch mechanism for transmitting and breaking the torque between the pinion gear and the spool shaft. Are provided.

[0003] The main gear is provided on the rotating shaft of the handle. The pinion gear meshes with the main gear, and a spool shaft extending outward from the side plate passes through the center of the pinion gear. The pinion gear is disposed concentrically with the spool shaft, and is supported by the spool shaft so as to be axially movable and rotatable. A clutch mechanism is constituted by an engagement concave portion provided at the tip of the pinion gear and an engagement convex portion provided on the outer peripheral portion of the spool shaft. The engaging projection is usually provided outside the flange portion of the spool, and is further provided outside the bearing in the configuration in which the spool shaft is supported by the side plate. The pinion gear is moved in the axial direction of the spool shaft by the clutch lever, and the engaging concave portion and the engaging convex portion are engaged and disengaged, whereby the rotational force is transmitted and interrupted.

In such a dual-bearing reel, when performing casting, the pinion gear is disengaged from the spool shaft by the clutch lever so that the spool can freely rotate. Then, the fishing rod is thrown and the fishing line is paid out from the spool by the weight of the device. When winding the fishing line, the pinion gear is engaged with the spool shaft to transmit the rotation of the handle to the spool.

[0005]

In the above-mentioned conventional configuration,
If the engaging projection and the engaging recess are engaged to transmit torque from the pinion gear to the spool shaft to rotate the spool in the winding direction, it is difficult to efficiently transmit the winding torque. This is because when the engaging protrusion provided outside the flange portion is separated from the fixed portion of the spool, a relatively small diameter spool shaft transmits the winding torque from the engaging protrusion to the fixed portion of the spool. It is thought that this is because it is easily twisted. If the winding torque is not efficiently transmitted as described above, the operation feeling when the spool is rotated in the winding direction by the handle is reduced.

An object of the present invention is to improve the efficiency of transmitting torque from a pinion gear to a spool.

[0007]

A dual-bearing reel according to a first aspect of the present invention includes a reel body, a spool shaft, a spool, a clutch engaging portion, a clutch operating member, and a handle. The spool shaft is rotatably supported by the reel body. The spool has a fixed portion fixed to the spool shaft, a cylindrical bobbin trunk formed on the outer peripheral side of the fixed portion and around which the fishing line is wound, and an inner peripheral side of the bobbin trunk formed adjacent to the fixed portion. It has an internal space and dish-shaped flanges formed at both ends of the bobbin trunk. The pinion gear is a cylindrical gear through which a spool shaft passes. The clutch engagement portion is provided in the internal space of the spool near the fixed portion, and is capable of engaging and disengaging the spool shaft and the pinion gear by moving in the axial direction. The clutch operation member is a member for operating the clutch engagement portion.
The handle is for rotating the pinion gear.

In this dual bearing reel, when the handle is rotated in a state where the spool shaft and the pinion gear are engaged by the clutch engaging portion, the rotation of the handle is transferred from the pinion gear to the spool shaft via the clutch engaging portion. It is transmitted and the spool rotates. Further, when the spool shaft and the pinion gear are separated, the spool can freely rotate. As described above, since the rotation of the pinion gear is transmitted to the spool shaft via the clutch engagement portion provided in the vicinity of the fixed portion of the spool, the rotation transmitting portion from the pinion gear to the spool shaft fixes the rotation of the spool. In this case, the spool shaft is less likely to be twisted and the torque transmission efficiency from the pinion gear to the spool is improved.

A dual-bearing reel according to a second aspect of the present invention is the reel according to the first aspect, wherein the fixed portion is formed substantially at a central portion in the axial direction of the bobbin trunk. In this case, since the positions of the fixed portions are well balanced, the efficiency of transmitting torque from the spool shaft to the spool is improved. A dual-bearing reel according to a third aspect of the present invention is the reel according to the first or second aspect, wherein the pinion gear is movable in the axial direction of the spool shaft, and the first clutch engaging portion is formed on the outer periphery of the spool shaft. An engaging portion, and a second engaging portion formed at the tip of the pinion gear and capable of engaging and disengaging from the first engaging portion by axial movement of the pinion gear. In this case, when the two engaging portions are engaged, torque is directly transmitted from the pinion gear having a larger diameter than the spool shaft to the spool shaft, so that the torsional deformation is further reduced and the torque transmission efficiency is further improved.

A dual bearing reel according to a fourth aspect of the present invention is the reel of the third aspect, wherein the handle has a handle body, a handle shaft interlocked with the handle body, and a main gear interlocked with the handle shaft and meshing with the pinion gear. The pinion gear includes a second engagement portion, a tooth portion meshing with the main gear, and a shaft supported by the reel body between the second engagement portion and the tooth portion so as to be rotatable and axially movable by a bearing. And a branch. In this case, since the pinion gear is supported by the reel body between the second engagement portion and the tooth portion, the rotation of the pinion gear becomes smooth, and even if the spool shaft bends when the clutch is engaged, The pinion gear does not tilt and the engagement with the pinion gear does not change significantly.

A dual bearing reel according to a fifth aspect of the present invention is the reel according to the fourth aspect, wherein the teeth are provided so as to be separated from the shaft support in the axial direction. In this case, since the teeth and the shaft support are formed separately, the bearing accuracy of the shaft support is increased. Further, since the teeth are not necessarily formed in the second engaging portion on the distal end side from the shaft supporting portion, the thickness of the portion can be increased, and the strength is improved.

[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 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 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. This allows
The first side cover 6 is openable and closable with respect to the side plate 8. The first side cover 6 is urged by the coil spring 4 in a direction away from the side plate 8. The first side cover 6
Is a brake case 6 of a centrifugal brake mechanism 23 described later.
Locking and unlocking with respect to the side plate 8 are performed by the bayonet structure provided in 5.

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. Further, between the frame 5 and the second cover 7, the gear mechanism 18 for transmitting the rotational force from the handle 2 to the spool 12 and the level wind mechanism 15, the clutch mechanism 13, and the clutch mechanism 13 are disengaged. Disengagement control mechanism 20 for controlling engagement and disengagement of clutch mechanism 13 in accordance with operation of thumb rest 17, drag mechanism 21, and resistance force during rotation of spool 12. And a casting control mechanism 22 are arranged. 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 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 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. A plurality of holes 12d are formed in the bobbin trunk 12b 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 through the side plate 9 and
It extends outside the side cover 7. 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 12c of the spool 12, and an engaging pin 16f constituting the clutch mechanism 13 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 steps of the steps 16g and 16h are, for example, in the range of 0.1 mm to 0.3 mm. Step 16
The left side of g is the large diameter part 16i of the small diameter part 16b, the right side is the middle diameter part 16j, and the right side of the step part 16h is the small diameter part 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. The axial length of the shaft support 16l is equal to the length of the bearing 24.
The length a is shorter than the length in the axial direction, and the rotational resistance is reduced. 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. A ring-shaped spring member 29a is arranged on the inner periphery of the boss 29 around the groove 16m. 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 between an outer peripheral portion on the right end side in FIG. 3 and meshing with the main gear 31, an engaging portion 32b formed on the other end side, and a portion between the tooth portion 32a and the engaging portion 32b. And a constricted portion 32c formed at the bottom. The meshing portion 32b is formed by a concave groove 33 formed on 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, when the pinion gear 32 moves outward and the concave groove 33 of the meshing portion 32b is disengaged from the engagement pin 16f of the spool shaft 16, the rotational force from the handle shaft 30 is not transmitted to the spool 12. The clutch mechanism 13 is constituted by the concave groove 33 of the meshing portion 32b and the engaging pin 16f. Here, since the clutch mechanism 13 is disposed near the boss portion 12c of the spool 12, when the torque 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. The torque transmission efficiency is improved, and the operation feeling is improved. In addition, the engagement pin 16f and the concave groove 3
When engaged with 3, the torque is transmitted directly from the pinion gear 32 having a larger diameter than the spool shaft 16 to the spool shaft 16, so that the torsional deformation is further reduced and the torque transmission efficiency is further 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
As shown in FIG. 5, a shaft support portion 32i that can contact the bearing 24b and a separation portion 32j having a diameter slightly smaller than the shaft support portion 32i are formed on the outer peripheral surface on the side b. Separation part 32j,
A step is formed between the shaft support 32i and the shaft support 32i by C2. Therefore, a gap C2 is formed between the bearing 24b and the separation part 32j. This gap C2 is, for example,
0.1 mm, and the flange 12 of the spool 12
a is smaller than the gap C1. The separation part 32j is formed on the outer peripheral surface facing the bearing 24b when the clutch is on. Here, since the teeth 32a and the shaft support 32i are formed separately, the bearing accuracy of the shaft support 32i is increased.
In addition, the engaging portion 32b located on the tip side from the shaft support portion 32i.
Since the teeth are not necessarily formed in the first portion, the thickness of the portion can be increased, and the strength of the engaging portion 32b is improved.

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 contacts 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, since the gap C2 is formed between the pinion gear 32 and the bearing 24b, the pinion gear 32 is supported by the spool shaft 16 so as to be rotatable and axially movable. Here, since the pinion gears 32 are supported at two positions with respect to the spool shaft 16, the pinion gears 32 do not tilt even when a force is applied at the time of hoisting rotation or the like. Is unlikely to occur.

On the other hand, in the clutch-off state in which the pinion gear 32 moves rightward in FIG. 4 and the meshing portion 32b is disengaged from the engaging 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,
The bearing portion 32i on the outer peripheral surface contacts the bearing 24b,
The pinion gear 32 is rotatably and axially supported by b. Therefore, the pinion gear 32 does not tilt and break during free rotation, and does not contact the spool shaft 16. Therefore, during free rotation, the pinion gear 32
And the spool shaft 16 do not come into contact with each other to increase the rotational resistance.

Even if the spool shaft 16 bends due to a 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 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 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 portion 66 provided in the brake case 65, and a radially arranged Slider 67 movably mounted
And The brake case 65 is detachably mounted in a circular opening 8a formed in the side plate 8 by a bayonet structure. Also, the brake case 65 is shown in FIG.
As shown in (1), the conical coil spring 4b urges the outer side of the first side cover 6. The brake case 65
It is fixed to the detachable handle 69 exposed to the outside of the first side cover 6, is detached from the side plate 8 by rotating the detachable handle 69, 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, the bearing 3
5 is formed with a cylindrical bearing mounting portion 65a. Further, a friction plate 51 of the casting control mechanism 22 is disposed at the center thereof. A liner 68 for braking is provided on the inner periphery of the periphery of the brake case 65.
Is provided. The rotating portion 66 is non-rotatably connected to the spool shaft 16 by serration coupling, and rotates integrally with the spool shaft 16. The slider 67 slides on the liner 68 in the brake case 65 by centrifugal force.

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 as shown in FIG. I have. In this state, the engagement portion 32b of the pinion gear 32 and the engagement pin 16f of the spool shaft 16 are engaged with each other, 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 And transmitted to the spool 12 via the spool shaft 16. At this time, the casting control mechanism 22
By adjusting the tightening amount of the cap 52, it is possible to adjust the resistance when the spool shaft 16 rotates.

In this clutch-on state, the medium-diameter inner surface 32
g contacts the outer peripheral surface of the large diameter portion 16i, and the small diameter inner surface 32h contacts the outer peripheral surface of the middle diameter portion 16j. Further, since the gap C2 is formed between the pinion gear 32 and the bearing 24b, the pinion gear 32 is supported by the spool shaft 16 so as to be rotatable and movable in the axial direction. Here, since the pinion gears 32 are supported at two positions with respect to the spool shaft 16, the pinion gears 32 do not tilt even when a force is applied at the time of hoisting rotation or the like. Is unlikely to occur. When the clutch 12 is wound up in a clutch-on state, a force is applied to the spool 12 and
Even when the pin 6 is bent, when the pinion gear 32 comes into contact with the bearing 24b, the pinion gear 32 is supported by the pinion gear 32, and the spool shaft 16 hardly bends beyond the gap C2. 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. In addition, since the clutch mechanism 13 is disposed near the boss 12c of the spool 12, the spool shaft 1
When the rotational force is transmitted to the spool 16 via the spool 6, the twist of the spool shaft 16 is reduced, the torque transmission efficiency is improved, and the operation feeling is improved.

When performing casting, the braking force is adjusted by the cap 52 in order 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. 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, 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 turned off, the reel is tilted in the axial direction so that the spool shaft 16 is aligned with the vertical plane while the spool is being thumbed with the thumb resting on the thumb rest 17, and the fishing rod is shaken. The lure is thrown and the spool 12 moves in the line payout direction. Rotate vigorously.

In such a state, as shown in FIG. 4B, the inner surface 32g of the middle diameter separates from the outer peripheral surface of the large diameter portion 16i, and the inner surface 32h of the small diameter separates from the outer peripheral surface of the medium 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, the shaft support portion 32i on the outer peripheral surface comes into contact with the bearing 24b, and the pinion gear 32 is supported by the bearing 24b so as to be rotatable and movable in the axial direction. Therefore, the pinion gear 32 does not tilt and break during free rotation, 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.

[Other Embodiments] (a) The configuration of the clutch mechanism is not limited to the engagement pin and the concave groove. The pinion gear and the spool shaft are non-rotatably engaged by the axial movement of the pinion gear. Any configuration may be used as long as it is rotatably detachable. (B) The clutch mechanism may be composed of a separate member from the spool shaft and the pinion gear. For example, a clutch cylinder may be provided on the spool shaft so as to be movable in the axial direction, and the pinion gear and the spool shaft may be engaged / disengaged by moving the clutch cylinder in the axial direction.

[0039]

According to the present invention, since the rotation of the pinion gear is transmitted to the spool shaft via the clutch engaging portion provided near the fixed portion of the spool, the rotation from the pinion gear to the spool shaft is transmitted. The rotation transmitting portion is close to the fixed portion of the spool, so that the spool shaft is less likely to be twisted, and the efficiency of transmitting torque from the pinion gear to the spool is improved.

[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 partial cross-sectional view of a spool shaft end during a clutch operation.

DESCRIPTION OF REFERENCE NUMERALS 1 reel body 2 handle 12 spool 12a flange 12b thread winding body 12c boss 12e internal space 13 clutch mechanism 16 spool shaft 16f engagement pin 17 thumb rest 30 handle shaft 31 main gear 32 pinion gear 32a tooth portion 32b Meshing portion 32i Shaft support portion 33 Groove

Claims (5)

[Claims] A reel body, a spool shaft rotatably supported by the reel body, a fixed portion fixed to the spool shaft, and a cylindrical portion formed on the outer peripheral side of the fixed portion and around which a fishing line is wound. A spool having a bobbin trunk, an internal space formed on the inner peripheral side of the bobbin trunk adjacent to the fixing portion, and a dish-shaped flange formed at both ends of the bobbin trunk; A cylindrical pinion gear through which the spool shaft penetrates; provided in the interior space of the spool in close proximity to the fixed portion, and capable of engaging and disengaging the spool shaft and the pinion gear by axial movement. A dual bearing reel comprising: a clutch engaging portion; a clutch operating member for operating the clutch engaging portion; and a handle for rotating the pinion gear. 2. The dual-bearing reel according to claim 1, wherein the fixing portion is formed substantially at a central portion in the axial direction of the bobbin trunk. 3. The pinion gear is movable in the axial direction of the spool shaft, the clutch engaging portion includes a first engaging portion formed on an outer periphery of the spool shaft, and a tip of the pinion gear. 3. The dual bearing reel according to claim 1, further comprising: a second engaging portion formed on the first engaging portion, the second engaging portion being capable of engaging with and disengaging from the first engaging portion by axial movement of the pinion gear. 4. The handle has a handle main body, a handle shaft interlocked with the handle main body, and a main gear interlocked with the handle shaft and meshing with the pinion gear, wherein the pinion gear includes the second engagement portion. And a tooth portion meshed with the main gear, and a shaft support portion rotatably and axially supported by the bearing on the reel body between the second engagement portion and the tooth portion. A dual bearing reel as described in 1. 5. The dual-bearing reel according to claim 4, wherein the tooth portion is provided so as to be axially separated from the shaft support portion.