阅读说明：本技术 双轴承渔线轮的卷线筒及双轴承渔线轮 (Spool of dual-bearing reel and dual-bearing reel ) 是由 大古濑广树 新妻翔 于 2019-12-10 设计创作，主要内容包括：本发明涉及一种双轴承渔线轮的卷线筒及双轴承渔线轮。卷线筒(4)具有卷线主体部(21)、一对凸缘部(24)和圆筒部(25、26)。一对凸缘部(24)从卷线主体部(21)的两端向卷线筒(4)的旋转轴(A)的径向外侧延伸。一对凸缘部(24)不具有沿旋转轴(A)的轴向贯通的通孔。圆筒部(25、26)从一对凸缘部(24)的顶端部向旋转轴(A)的轴向外侧延伸。一对凸缘部(24)具有第一锥部(27a、28a),随着该第一锥部(27a、28a)向径向外侧延伸其壁厚变薄。第一锥部彼此之间的平均宽度(AW)为圆筒部的外径(D2)的60％以下。根据该发明,能够抑制卷线筒的弯曲强度的下降,并且降低卷线筒的惯性。(The present invention relates to a spool of a dual-bearing reel and a dual-bearing reel. The spool (4) has a spool body (21), a pair of flange portions (24), and cylindrical portions (25, 26). The pair of flange sections (24) extend from both ends of the spool body section (21) radially outward of the rotation axis (A) of the spool (4). The pair of flange sections (24) do not have through holes that penetrate in the axial direction of the rotating shaft (A). The cylindrical sections (25, 26) extend axially outward of the rotating shaft (A) from the distal ends of the pair of flange sections (24). The pair of flange sections (24) have first tapered sections (27a, 28a), and the thickness of the first tapered sections (27a, 28a) decreases as the sections extend radially outward. The Average Width (AW) between the first tapered portions is 60% or less of the outer diameter (D2) of the cylindrical portion. According to the present invention, the inertia of the spool can be reduced while suppressing a decrease in the bending strength of the spool.)

1. A spool for a dual-bearing reel is characterized in that,

has a winding main body, a pair of flange portions and a cylindrical portion,

the pair of flange portions extend from both ends of the spool body portion radially outward of a rotation shaft of the spool, and do not have through holes that penetrate in an axial direction of the rotation shaft;

the cylindrical portion extends from the distal end portions of the pair of flange portions to the outside in the axial direction of the rotating shaft,

the pair of flange portions have tapered portions whose wall thickness becomes thinner as the tapered portions extend outward in the radial direction,

the average width between the tapered portions is 60% or less of the outer diameter of the cylindrical portion.

2. The spool for a dual-bearing reel of claim 1,

the minimum diameter of the winding body is 60% or less of the outer diameter of the cylindrical portion.

3. The spool of the dual-bearing reel according to claim 1 or 2,

the tapered portion has a wall thickness that decreases at a taper rate of 0.3% to 1% as it extends radially outward.

4. The spool for a dual-bearing reel according to any one of claims 1 to 3, wherein,

the thickness of the distal end portion of the tapered portion is equal to or greater than the thickness of the cylindrical portion.

5. The spool for a dual-bearing reel according to any one of claims 1 to 4, wherein,

the thickness of the thickest part of the tapered part is 0.4mm to 0.6 mm.

6. The spool for a dual-bearing reel according to any one of claims 1 to 5, wherein,

and a connecting wall portion formed in a disc shape on an inner peripheral portion of a central portion of the winding main body portion,

the winding wire main body portion has a through hole formed only in a portion of the winding wire main body portion connected to the connecting wall portion,

the thickness of the winding main body is 0.4mm to 0.5 mm.

7. A dual-bearing reel is characterized in that,

a fishing reel having a reel unit, a handle, and the spool according to any one of claims 1 to 6,

the handle is rotatably disposed on the reel unit;

the spool is rotatably disposed in the reel unit.

Technical Field

The present invention relates to a spool for double-bearing reel and a double-bearing reel.

Background

In a dual-bearing reel, in order to throw a sufficient throwing distance with a light weight bait (lure), it is required to reduce the inertia of a spool. In order to reduce the inertia of a spool, for example, a spool of a dual-bearing reel is known, which is reduced in weight by providing a through hole in a flange portion or a spool body portion of the spool (see patent documents 1 and 2). [ Prior art documents ]

[ patent document ]

Patent document 1: japanese patent laid-open publication No. 2017-127234

Patent document 2: japanese patent laid-open publication No. 5779516

Disclosure of Invention

[ technical problem to be solved by the invention ]

In the case where the through-hole is provided in the flange portion of the spool or the spool body portion, since the bending strength around the through-hole is reduced, it is necessary to increase the thickness of the flange portion or the spool body portion to compensate for the reduction in the bending strength of the spool. Therefore, it is difficult to greatly reduce the inertia while maintaining the bending strength of the spool.

The invention aims to reduce inertia of a spool while suppressing a decrease in bending strength of the spool.

[ technical means for solving problems ]

A spool of a dual-bearing reel according to an aspect of the present invention includes a spool body, a pair of flange portions, and a cylindrical portion. The pair of flange portions extend radially outward of the rotation shaft of the spool from both ends of the spool body. The pair of flange portions do not have through holes that penetrate in the axial direction of the rotating shaft. The cylindrical portion extends axially outward of the rotating shaft from the distal ends of the pair of flange portions. The pair of flange portions have tapered portions, and the thickness of the tapered portions becomes thinner as the tapered portions extend radially outward. The average width between the tapered portions is 60% or less of the outer diameter of the cylindrical portion.

In the spool of the dual-bearing reel, since the through-hole is not provided in the pair of flange portions, it is possible to reduce the weight of the spool by reducing the thickness of the pair of flange portions while suppressing a decrease in the bending strength of the pair of flange portions. Further, since the thickness of the pair of flange portions increases as it approaches the winding main body portion, it is possible to effectively suppress a decrease in the bending strength of the pair of flange portions and to reduce the weight of the pair of flange portions. Further, since the average width between the tapered portions is 60% or less of the outer diameter of the cylindrical portion, the distance from the center of the spool body to the pair of flange portions is shorter than the distance on the conventional spool, and the Bending moment (Bending moment) acting on the spool body can be reduced. Accordingly, even when the thickness of the winding main body is reduced to reduce the weight, for example, sufficient bending strength can be maintained in the winding main body.

Preferably, the smallest diameter of the wire winding body is 60% or less of the outer diameter of the cylindrical portion. In this case, since the distance between the spool body and the rotation axis of the spool becomes short, the distance from the center of gravity of the fishing line to the rotation axis becomes short when the fishing line is wound around the spool. Thus, the inertia of the spool during bait throwing can be reduced. In addition, the amount of winding on the spool can be suppressed from being greatly reduced.

Preferably, the tapered portion has a wall thickness that becomes thinner by a taper rate (rateof taper) of 0.3% or more and 1% or less as it extends radially outward. In this case, the inertia of the spool can be reduced while effectively suppressing a decrease in the bending strength of the pair of flange portions.

Preferably, the thickness of the distal end portion of the tapered portion is equal to or greater than the thickness of the cylindrical portion. In this case, the operation of a so-called thumb wire (thumb) for bringing a finger into contact with the tip end portion of the tapered portion to suppress the rotation of the spool can be stably performed. Further, since the thickness of the cylindrical portion is equal to or less than the thickness of the tapered portion at the distal end, the spool can be reduced in weight.

Preferably, the thickness of the thickest part of the tapered part is 0.4mm to 0.6 mm. In this case, the inertia of the spool can be greatly reduced while effectively suppressing a decrease in the bending strength of the pair of flange portions.

Preferably, the spool further includes a connecting wall portion formed in a disc shape on an inner peripheral portion of a central portion of the spool body portion, the spool body portion includes a through hole formed only in a portion of the spool body portion connected to the connecting wall portion, and a wall thickness of the spool body portion is 0.4mm to 0.5 mm. In this case, since the through-hole is formed only in the portion of the winding main body portion connected to the connecting wall portion, even if the thickness of the winding main body portion is set to 0.4mm or more and 0.5mm or less, the winding main body portion can be made lightweight while maintaining sufficient bending strength.

A dual-bearing reel according to an aspect of the present invention includes a reel unit, a handle (handle) and the spool described above, wherein the handle is rotatably disposed on the reel unit; the spool is rotatably disposed in the reel unit. In this case, in the dual-bearing reel, the inertia of the spool can be reduced while suppressing a decrease in the bending strength of the spool.

[ Effect of the invention ]

According to the present invention, the inertia of the spool can be reduced while suppressing a decrease in the bending strength of the spool.

Drawings

Fig. 1 is a perspective view of a dual-bearing reel.

Fig. 2 is a sectional view ii-ii of fig. 1.

Figure 3 is a half cross-sectional view of a spool with a spool shaft mounted.

Fig. 4 is a right side view of the spool with the spool shaft installed.

Fig. 5 is a partially enlarged view of fig. 2.

[ description of reference ]

3: a handle; 4: a spool; 21: a winding main body part; 21 a: a first through hole; 23: a connecting wall portion; 24: a pair of flange portions; 25: a cylindrical portion; 26: a cylindrical portion; 27 a: a first taper portion; 28 a: a first taper portion; 100: a dual-bearing fishing reel; a: a rotating shaft; AW: the average width.

Detailed Description

Fig. 1 is a perspective view of a dual-bearing reel 100 according to an embodiment of the present invention. Fig. 2 is a sectional view taken along line ii-ii of fig. 1. The dual-bearing Reel 100 is, for example, a small-sized Bait-casting Reel (bail-casting Reel) and can Reel out a fishing line forward. The dual-bearing reel 100 includes a reel unit 2, a handle 3, and a spool 4. The dual-bearing reel 100 includes a rotation transmission mechanism 10, a clutch mechanism 11, a bait casting control mechanism 12, a spool brake mechanism 13, a drag mechanism (not shown), and the like, wherein the rotation transmission mechanism 10 transmits the rotation of the handle 3 to the spool 4.

In the following description, the fishing line is cast in a direction called front and the reverse direction called rear. The left and right sides are left and right when the dual-bearing reel 100 is viewed from the rear. The direction in which the spool shaft 14 (see fig. 2) extends is referred to as "axial direction", the direction perpendicular to the spool shaft 14 is referred to as "radial direction", and the direction of rotation around the spool shaft 14 is referred to as "circumferential direction".

The reel unit 2 has a frame 6, a right cover 7 and a left cover 8, wherein the right cover 7 covers the right side of the frame 6; the left cover 8 covers the left side of the frame 6. The frame 6 has a first side plate 6a, a second side plate 6b, and a plurality of connecting portions 6c, wherein the second side plate 6b is disposed at intervals from the first side plate 6a in the axial direction; the plurality of coupling portions 6c couple the first side plate 6a and the second side plate 6 b.

The handle 3 is rotatably attached to the side of the reel unit 2. In the present embodiment, the handle 3 is attached to the right side of the reel unit 2.

The spool 4 is made of, for example, an aluminum alloy, and is rotatably supported by the reel unit 2 between the first side plate 6a and the second side plate 6 b. More specifically, the spool 4 is fixed to a spool shaft 14, and is rotatably supported by the reel unit 2 via the spool shaft 14, wherein the spool shaft 14 is rotatably supported by the reel unit 2. In the present embodiment, the rotation axis a of the spool 4 coincides with the axial center of the spool shaft 14.

Fig. 3 is a half sectional view of the spool 4 with the spool shaft 14 attached. As shown in fig. 2 and 3, the spool 4 includes a spool body 21, a shaft mounting portion 22, a connecting wall portion 23, a pair of flange portions 24, and cylindrical portions 25 and 26.

The spool body 21 is substantially cylindrical, and a fishing line is wound around the outer periphery thereof. The outer peripheral surface of the winding main body 21 is inclined such that the distance from the axis of rotation a gradually decreases as the winding main body 21 approaches the center C in the axial direction. Therefore, in the present embodiment, the diameter of the central portion of the bobbin main body 21 is the minimum diameter D1 of the bobbin main body 21.

Preferably, the minimum diameter D1 of the wire winding body 21 is 60% or less of the outer diameter D2 of the cylindrical portions 25, 26. More preferably, the minimum diameter D1 of the wire winding body 21 is 50% to 60% of the outer diameter D2 of the cylindrical portions 25 and 26. The minimum diameter D1 of the cord winding main body 21 in the present embodiment is, for example, about 56% of the outer diameter D2 of the cylindrical portions 25, 26. Both ends of the winding main body 21 are bent outward in the radial direction and smoothly connected to the pair of flange portions 24.

Preferably, the thickness T1 of the winding main body 21 is 0.4mm to 0.5 mm. The thickness T1 of the winding main body 21 in the present embodiment is, for example, 0.45 mm.

The winding main body 21 has a plurality of first through holes 21a penetrating in the radial direction. The first through hole 21a is a substantially circular hole and is centered on a center portion C of the cord winding main body 21 in the axial direction. The center of the first through hole 21a is arranged at a position overlapping the connecting wall portion 23 in the radial direction. The first through holes 21a are formed at positions overlapping the connecting wall portions 23 in the radial direction, with intervals in the circumferential direction of the bobbin trunk 21. The diameter of the first through hole 21a is slightly larger than the wall thickness of the connecting wall portion 23. The first through hole 21a is formed only in a portion of the winding main body 21 connected to the connecting wall portion 23.

The shaft mounting portion 22 is disposed on the inner peripheral side of the bobbin trunk 21. The shaft mounting portion 22 has a through hole 22a penetrating in the axial direction. The spool shaft 14 is press-fitted into and fixed to the through hole 22a, whereby the spool 4 and the spool shaft 14 rotate integrally.

The connecting wall 23 connects the winding main body 21 and the shaft mounting portion 22. The connecting wall portion 23 is substantially disc-shaped, and extends radially inward from an inner peripheral portion of a central portion C of the bobbin trunk 21 in the axial direction toward the shaft attachment portion 22. The connecting wall portion 23 has a larger thickness in the vicinity of the outer end connected to the cord winding main body portion 21 than the other portion of the connecting wall portion 23.

Fig. 4 is a right side view of the spool 4 with the spool shaft 14 installed. As shown in fig. 4, the connecting wall portion 23 has a plurality of second through holes 23a penetrating in the axial direction. The second through holes 23a are formed at intervals in the circumferential direction. The second through hole 23a is formed near the outer end of the connecting wall portion 23 so as to be continuous with the first through hole 21 a. Therefore, the same number of second through holes 23a as the first through holes 21a are formed in the connecting wall portion 23.

The pair of flanges 24 are substantially disc-shaped and extend radially outward from both ends of the winding main body 21. The pair of flange portions 24 are inclined so as to expand outward in the axial direction as they extend outward in the radial direction. The pair of flanges 24 are inclined so that the diameters thereof become smaller as they approach the center C of the bobbin trunk 21 in the axial direction. As shown in fig. 4, the pair of flange portions 24 do not have through holes penetrating in the axial direction.

The pair of flange portions 24 has a first flange portion 27 and a second flange portion 28. The first flange 27 extends radially outward from the right end of the bobbin trunk 21. The first flange portion 27 includes a first tapered portion 27a and a second tapered portion 27 b.

The first tapered portion 27a extends radially outward from the right end of the bobbin trunk 21. The first tapered portion 27a is formed to be thinner as it extends radially outward.

In detail, the first tapered portion 27a includes a first end portion 31 and a second end portion 32. The first end 31 is connected to the right end of the winding main body 21. In the first tapered portion 27a, the first end portion 31 has the thickest wall thickness. Preferably, the thickness T2 of the first end 31 is 0.4mm or more and 0.6mm or less. More preferably, the thickness T2 of the first end 31 is 0.4mm or more and 0.5mm or less. The thickness T2 in the present embodiment is, for example, 0.45 mm.

The second end portion 32 is connected to the second taper portion 27 b. In the first tapered portion 27a, the wall thickness of the second end portion 32 is thinnest. Preferably, the thickness T3 of the second end portion 32 is 0.3mm or more and 0.4mm or less. The wall thickness T3 of the second end portion 32 in the present embodiment is, for example, 0.35 mm.

Preferably, the first tapered portion 27a has a wall thickness that becomes thinner at a taper rate of 0.3% to 1% as it extends radially outward. More preferably, the first tapered portion 27a has a thickness that becomes thinner at a taper rate of 0.3% to 0.7% as it extends radially outward. The taper rate of the first tapered portion 27a in the present embodiment is, for example, about 0.34%. Here, for example, when the taper ratio is T, the length from the first end portion 31 to the second end portion 32 is L, the thickness of the first end portion 31 is T2, and the thickness of the second end portion 32 is T3, the taper ratio T can be calculated by the following equation (1).

T＝(T2-T3)/L×100···(1)

Fig. 5 is a partially enlarged view of fig. 2, and is an enlarged sectional view of the periphery of the cylindrical portion 25. The second tapered portion 27b extends further axially outward from the second end portion 32 of the first tapered portion 27 a. The second tapered portion 27b is inclined more gently than the first tapered portion 27 a. The boundary between the second tapered portion 27b and the first tapered portion 27a is a reference of the maximum winding position of the fishing line on the spool 4. The wall thickness T4 of the second tapered portion 27b is formed uniformly. Further, it is preferable that the wall thickness T4 of the second tapered portion 27b is approximately the same as the wall thickness T3 of the second end portion 32. The thickness T4 of the second tapered portion 27b in the present embodiment is, for example, 0.36mm and slightly larger than the thickness T3 of the second end portion 32.

The second flange portion 28 extends radially outward from the left end of the bobbin trunk 21. The second flange portion 28 includes a first tapered portion 28a and a second tapered portion 28 b. The first conical portion 28a includes a first end portion 33 and a second end portion 34. The first end portion 33 is connected to the left end of the winding main body 21. The second end portion 34 is connected to the second tapered portion 28 b. The second flange portion 28 is formed symmetrically with respect to the first flange portion 27 across the center portion C of the cord main body 21 in the axial direction, and therefore, a detailed description thereof will be omitted.

Preferably, the average width AW between the first tapered portion 27a and the first tapered portion 28a is 60% or less of the outer diameter D2 of the cylindrical portions 25, 26. More preferably, the average width AW is 50% to 55% of the outer diameter D2 of the cylindrical portions 25, 26. The average width AW in the present embodiment is, for example, about 53% of the outer diameter D2 of the cylindrical portions 25, 26. For example, when the width between the outer peripheral portion of the first end portion 31 and the outer peripheral portion of the first end portion 33 is W1 and the width between the outer peripheral portion of the second end portion 32 and the outer peripheral portion of the second end portion 34 is W2, the average width AW can be calculated using the following formula (2).

AW＝(W1+W2)/2···(2)

The cylindrical portions 25, 26 extend in a substantially cylindrical shape from the distal ends of the pair of flange portions 24 to the outside in the axial direction. The cylindrical portions 25 and 26 are provided to increase the strength of the pair of flange portions 24 and to prevent the fishing line from entering through a gap between the frame 6 and the spool 4. Here, the thickness of the thinnest portion of the first tapered portion 27a, i.e., the thickness T3 of the second end portion 32 is preferably equal to or greater than the thickness T5 of the cylindrical portions 25, 26. Preferably, the thickness T4 of the second tapered portion 27b is equal to or greater than the thickness T5 of the cylindrical portions 25 and 26. The thickness T5 of the cylindrical portions 25 and 26 in the present embodiment is, for example, 0.3 mm.

As shown in fig. 2, the outer peripheral surface of the cylindrical portion 25 is disposed to face the inner peripheral surface of the first side plate 6 a. A slight gap is provided between the outer peripheral surface of the cylindrical portion 25 and the inner peripheral surface of the first side plate 6 a. The outer peripheral surface of the cylindrical portion 26 is disposed to face the inner peripheral surface of the second side plate 6 b. A slight gap is provided between the outer peripheral surface of the cylindrical portion 26 and the inner peripheral surface of the first side plate 6 a.

As shown in fig. 3, the width W3 of the cylindrical portion 25 in the axial direction is smaller than the width W4 of the cylindrical portion 26 in the axial direction. Therefore, as shown in fig. 2, the range in which the outer peripheral surface of the cylindrical portion 26 radially overlaps the inner peripheral surface of the first side plate 6a is smaller than the range in which the outer peripheral surface of the cylindrical portion 25 radially overlaps the inner peripheral surface of the first side plate 6 a.

Here, as shown in fig. 1, the bait casting control mechanism 12 brakes the rotation of the spool 4 by pressing the spool shaft 14 in the axial direction. The braking force of the bait casting control mechanism 12 is adjusted by a rotational operation of a knob member 40 provided on the handle 3 side. A first friction member 41 is disposed inside the knob member 40, and the first friction member 41 can be in contact with one end of the spool shaft 14. The first friction member 41 moves in the axial direction in response to the rotational operation of the knob member 40. Further, a second friction member 42 is disposed on the other end side of the spool shaft 14 so as not to be movable in the axial direction, and the second friction member 42 can contact the other end of the spool shaft 14.

For example, when the knob member 40 is rotated and the first friction member 41 is moved in a direction away from the spool shaft 14 (rightward in fig. 2), the spool shaft 14 is moved rightward in the axial direction from the position shown in fig. 2, and a gap between the cylindrical portion 26 and the second side plate 6b in the axial direction may be generated. On the other hand, even when the spool shaft 14 moves to the axial right side from the position shown in fig. 2, the cylindrical portion 25 does not have a fear of generating a gap between the cylindrical portion 25 and the first side plate 6a in the axial direction. Therefore, the width W3 of the cylindrical portion 25 in the axial direction can be formed smaller than the width W4 of the cylindrical portion 26 in the axial direction. Accordingly, the weight of the spool 4 can be reduced.

In the dual-bearing reel 100 configured as described above, since the pair of flange portions 24 of the spool 4 are not provided with through holes that penetrate in the axial direction, it is possible to reduce the weight of the spool 4 by reducing the thickness of the pair of flange portions 24 while suppressing a decrease in the bending strength of the pair of flange portions 24. Further, since the thickness of the pair of flanges 24 increases as it approaches the cord winding main body 21, it is possible to effectively suppress a decrease in the bending strength of the pair of flanges 24 and to reduce the weight of the pair of flanges 24. Further, since the average width AW between the first tapered portions 27a and the first tapered portions 28a is 60% or less of the outer diameter D2 of the cylindrical portions 25 and 26, the distance from the center portion C of the spool body 21 in the axial direction to the pair of flange portions 24 is shorter than that of the conventional spool, and the bending moment acting on the spool body 21 can be reduced. Accordingly, even when the thickness of the winding main body 21 is reduced to reduce the weight, a sufficient bending strength can be maintained in the winding main body 21.

< other embodiment >

While the embodiment of the present invention and the modification thereof have been described above, the present invention is not limited to the embodiment and the modification, and various modifications can be made without departing from the scope of the invention. In particular, the embodiments and the plurality of modifications described in the present specification can be arbitrarily combined as needed.

(a) In the above embodiment, the spool 4 is fixed to the spool shaft 14, but the spool 4 may be supported by the reel unit 2 so as to be rotatable with respect to the spool shaft 14, for example.

(b) In the above embodiment, the outer peripheral surface of the winding main body 21 is inclined so that the distance from the rotation axis a gradually decreases as it approaches the center C of the winding main body 21 in the axial direction, but the outer peripheral surface of the winding main body 21 is not necessarily inclined. The second tapered portion 27b of the first flange portion 27 and the second tapered portion 27b of the second flange portion 28 may be omitted.