JP2001095437A - Double-bearing reel for fishing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a double-bearing reel for fishing capable of keeping high gear ratio and reducing the size of the reel even by decreasing the depth of spool and ensuring the sufficient line capacity of the spool. SOLUTION: The outer diameter A of the reel main body is set to 35-70 mm, the outer diameter B of the spool 3 is set to 30-50 mm, the gear ratio S2/S1 is set to 3.5-7.5 (S1 is the number of teeth of a pinion gear 6 and S2 is the number of teeth of a drive gear 7 engaging with the pinion gear 6) and the module of both gears 6, 7 is set to 0.3-0.4.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a double-bearing type fishing reel.

[0002]

2. Description of the Related Art Generally, a dual-bearing reel for fishing comprises a spool on which a fishing line is wound and a reel body rotatably supporting the spool. The reel body includes left and right frames that support the spool, and side plates attached to the sides of each frame.

[0003] Further, dual-bearing type reels are generally classified into a so-called round type in which the outer side plate of the reel body is formed in a circular shape, and a so-called round type having a different shape from the circular type. For example, Utility Model Registration No. 2552677 discloses a round bait casting reel.

In the bait casting reel, attempts have been made in recent years to reduce the inertia weight of the spool by forming the groove of the spool to be shallow, thereby reducing the fishing line release resistance and extending the flight distance of the tackle. ing.
In many cases, the gear ratio is set to a high value in order to improve hand return. In addition, the reel body has been made compact for the purpose of good operability and weight reduction. Further, it is desired that the spool has a sufficient winding capacity.

[0005]

As described above, the fact that the groove of the spool is shallow, the gear ratio is high, the reel body is compact, and the spool has a sufficient bobbin capacity is particularly a bait casting reel. Is important in That is, it can be said that it is the most desirable form that the bait casting reel has all of these conditions. However, in practice, it is difficult to satisfy all of these conditions, and in general, giving priority to one condition results in impairing the other conditions.

That is, if the outer diameter of the reel is set to be small to achieve compactness, the maximum outer diameter of the spool may have to be reduced. in this case,
Especially when the groove of the spool is shallow, it is difficult to secure a sufficient spool capacity. On the other hand, when trying to increase the bobbin capacity, the outer diameter of a spool having a particularly shallow groove becomes large, and the outer diameter of the reel body may have to be increased. That is, it is difficult to reduce the size of the reel body. If the reel body is large, the feel when gripping the reel is deteriorated, and it is not possible to avoid the increase in weight. Therefore, if throwing is repeated all day, the user becomes very tired.

[0007] Of course, the problem of making the reel compact is not caused only by the size of the spool. For example,
The outer diameter of a round bait casting reel is determined by the size of the gear of the winding drive mechanism provided between the spool and the handle, and the maximum outer diameter of the spool. Therefore, if the outer diameter of the gear is reduced, the reel can be made compact without reducing the size of the spool.

[0008] However, the winding drive mechanism is configured by meshing a drive gear attached to a handle shaft and a pinion gear attached to a spool shaft. In some cases, a high gear ratio cannot be obtained between the gear and the pinion gear. In addition, especially in the case of the pinion gear, since the spool shaft is supported by a light supporting force, if the pinion gear is reduced, the support of the pinion gear becomes insufficient, and the distortion of the spool shaft causes the pinion gear to separate from the drive gear. There is a risk of slipping, slipping, or tilting.

The present invention has been made in view of the above circumstances, and an object of the present invention is to maintain a high gear ratio even if a sufficient thread winding capacity is secured in the spool while making the groove of the spool shallow. Another object of the present invention is to provide a double-bearing fishing reel which can make the reel body compact.

[0010]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, the present invention provides a spool around which a fishing line is wound, a spool shaft that rotates integrally with the spool, and a reel body that rotatably supports the spool shaft. A pinion gear attached to the spool shaft and rotatable integrally with the spool shaft, a handle shaft rotatably attached to the reel body, and attached to the handle shaft to rotate integrally with the handle shaft and mesh with the pinion gear A dual-bearing fishing reel comprising a drive gear, and operating a handle provided on the handle shaft to rotate the handle shaft and rotate the spool via a pinion gear meshing with the drive gear. The outer diameter of the reel body is set in a range of 35 mm to 70 mm, and the outer diameter of the spool is 30 mm to Together are set to 0mm range, the number of teeth of the pinion gear S1, when and S2 the number of teeth of the drive gear meshing with the pinion gear, the gear ratio S2
/ S1 is set in the range of 3.5 to 7.5, and the modules of both gears are set in the range of 0.3 to 0.4.

[0011]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 to FIG. 5 show a first embodiment of the present invention. As shown in FIGS. 1 and 2, a dual-bearing fishing reel 1 according to the present embodiment is a so-called round reel, which rotatably supports a spool 3 around which a fishing line is wound and a spool 3. It consists of a reel body. The reel body includes left and right circular frames 2a, 2 supporting the spool 3.
b, and circular side plates 1a, 1b attached to the sides of the frames 2a, 2b. A side plate (hereinafter, referred to as a support side plate) 1b located on the right side in the drawing.
Supports a winding drive unit (described later) 30 that rotationally drives the spool 3.

The support side plate 1b is fastened and fixed to the right frame 2b by a plurality of screws 40 screwed into the peripheral edge thereof. In addition, the ring-shaped cover member 32b covers the screw 40 exposed on the outer surface of the support side plate 1b, and covers the periphery of the support side plate 1b where the screw 40 is located so that the screw 40 is not exposed to the outside. Are attached and fixed to the supporting side plate 1b. Also, a cover member 32a as a decorative plate is attached to the peripheral edge of the side plate 1a located on the left side so that the reel can be gripped without discomfort by eliminating surface irregularities.

A certain space is formed between the right frame 2b and the supporting side plate 1b, and various mechanisms such as a driving force transmission system and a drag system described later are accommodated in this space.

A spool shaft 5 is rotatably supported between the left and right frames 2a and 2b via bearings 10 and 10, and a spool 3 around which a fishing line is wound is integrally fixed to the spool shaft 5. Have been.

An annular groove 55 is formed on the outer peripheral surface of the spool shaft 5 to which the spool 3 is attached and fixed. As described above, when the spool shaft 5 is cut out in a groove shape to provide a lightening portion on the spool shaft 5, the spool shaft 5
(Assembly composed of spool shaft 5 and spool 3)
The casting performance can be improved because of the weight reduction, and fatigue can be reduced even when thrown all day. Further, when the spool 3 is bonded and fixed to the spool shaft 5, the concave groove 55 functions as an adhesive reservoir, so that the fixing strength between the spool 3 and the spool shaft 5 is increased. Note that the groove 55 may be formed over a wide range so as to straddle a portion of the spool shaft 5 to which the spool 3 is attached and fixed. That is, the groove 55 may be formed across the receiving portion and the non-receiving portion of the spool shaft 5 that receives the spool 3. If the groove 55 is formed over a wide range as described above, the adhesive can be applied through the groove 55 after the spool 3 is positioned with respect to the spool shaft 5. Therefore, the use of the instant adhesive becomes possible. Further, when the spool shaft 5 is insert-molded on the spool 3, the groove 55 increases the anti-rotation strength and is more resistant to deformation in the axial direction due to the thread winding operation, so that further reduction in thickness and weight can be achieved. .

Spool shaft 5 projecting from right frame 2b
A pinion gear 6 movable along the axial direction of the spool shaft 5 is attached to an end of the shaft. Specifically, the pinion gear 6 is movably attached to a pinion shaft 5 a integral with the spool shaft 5, with both end portions rotatably supported by bearings 39, 39. Also,
The pinion gear 6 turns on / off a clutch mechanism described later.
By performing the F operation, the engagement position at which the spool shaft 5 is engaged and rotated integrally with the spool shaft 5,
It is possible to move between a non-engaged position where the engagement state with is released. Specifically, the yoke 8 engaged with the circumferential groove 6a formed in the pinion gear 6
The pinion gear 7 moves along the pinion shaft 5a in conjunction with the ON / OFF operation of the clutch mechanism, so that the pinion gear 6 is engaged (the fishing line can be wound; the clutch is ON).
And disengaged position (spool free rotation; clutch OF
F).

The pinion gear 6 has a pinion shaft 5a.
And it may be formed integrally. In that case, both ends (or one end) of the pinion shaft 5 a supporting the pinion gear 6 or the vicinity thereof are rotatably supported by bearings 90, 90. Further, in the present embodiment, both ends of the pinion gear 6 are supported by the bearings 39, 39. However, for example, one end of the pinion gear 6 may be supported by a bearing having a wide supporting width. Similar effects can be obtained. Of course, it is needless to say that a mode in which both end portions of the pinion gear 6 are supported as in the present embodiment is more preferable.

The pinion gear 6 has a drive gear 7.
Are engaged. These drive gears 7 are supported by a handle shaft 8 that constitutes the winding drive unit 30. In this case, both ends of the handle shaft 8 are rotatably supported by bearings 38 provided on the right frame 2b and the support side plate 1b.

At the outer end of the handle shaft 8, a handle 12 which constitutes a winding drive unit 30 together with the handle shaft 8 is attached. Therefore, the handle 12
, The spool shaft 5 is driven to rotate via the drive gear 7 and the pinion gear 6, and the spool 3 is rotated accordingly. Note that knobs 12 a are provided at both ends of the handle 12.

A one-way clutch 23 is provided in the middle of the handle shaft 8 to allow rotation of the handle shaft 8 in only one direction, and a friction plate engaged with the drive gear 7 is provided at an inner end of the handle shaft 8. 25 (drag mechanism) is pivotally supported.
The friction plate 25 is pressed in the axial direction by the rotation of the drag operation member 27 attached to the handle 12 and frictionally engages with the drive gear 7 to provide a drag action.

A clutch return gear 82 and a gear 28 are supported at the inner end of the handle shaft 8 to prevent rotation. The gear 28 is connected to the drive gear 7, rotates integrally with the drive gear 7, and meshes with the gear 11 that drives the worm shaft 33 of the level wind mechanism 15 disposed on the front side of the spool 3. Level wind mechanism 15
Has a traverse groove formed on the outer peripheral surface and a gear 1 at the end.
A worm shaft 33 to which the worm shaft 1 is attached, a cylindrical body 17 accommodating the worm shaft 33, and an engaging element 18 which engages with the traverse groove and slides left and right along the cylindrical body 17 by rotation of the worm shaft 33. And guides the fishing line wound around the spool 3 through a hole formed in the engagement element 18. Therefore, when the handle 12 is rotated, the fishing line is evenly wound around the spool 3 by the rotation of the spool 3 and the sliding of the engagement element 18 left and right.

At the end of the spool shaft 5 protruding from the left frame 2a, excessive rotation of the spool shaft 5 is prevented.
A backlash prevention mechanism 73 for preventing backlash when the fishing line is released is provided.

FIG. 3 shows the structure of the clutch mechanism viewed from the handle 12 when the handle 12 and the right side plate 1b are removed. As shown in the drawing, the clutch mechanism includes a clutch lever 88 that can be manually turned on / off by a clutch, a clutch plate 85 that rotates in conjunction with the on / off operation of the clutch lever 88, A yoke 87 which moves in conjunction with the rotation of the clutch 85;
And a return operation piece 81 that engages with the clutch return gear 82 when the switch is made.

The return operating piece 81 is provided with a guide shaft 95.
It is arranged so as to be swingable about A. The return operation piece 81 is provided with an engagement portion 96 that can be engaged with the clutch return gear 82. By pivoting the return operation piece 81 about the guide shaft 95A, this engagement is performed. The joint 96 can be engaged with the clutch return gear 82.

In order to hold the clutch plate 85 at the clutch ON position and the clutch OFF position during the clutch ON / OFF operation, a hold spring 93 is provided in the clutch mechanism. One end of the hold spring 93 is supported by the support piece 85a of the clutch plate 85, and the other end is
Is supported by a support pin 92 attached to the flange 90 of the second member.

The clutch mechanism includes a return operating piece 8.
When the first engaging portion 96 is engaged with the clutch return gear 82, an urging spring 97 for applying a desired engaging force to the engaging portion 96 of the return operating piece 81 is provided. One end of the biasing spring 97 is locked to the return operating piece 81,
The other end is locked by a locking pin 98 attached to the flange 90 of the right frame 2b. The urging spring 97 constantly urges the return operating piece 81 in a direction in which the engaging portion 96 is engaged with the clutch returning gear 82.

In such a rotary clutch mechanism,
When the clutch lever 88 is switched to the ON position indicated by the solid line in the figure, the clutch plate 85 is moved to the pinion shaft 5a.
Around the center. At this time, the yoke 87 is moved toward the clutch plate 85 along the guide shafts 95A and 95B by the urging force of an urging spring (not shown). Thus, the pinion gear 6 connected to the yoke 87 via the circumferential groove 6a
Engages with the spool shaft 5.

When the clutch is switched from the clutch ON state to the clutch OFF state, the clutch plate 85 rotates and the yoke 87 is pressed and moved in a direction away from the clutch plate 85. As a result, the engagement state between the pinion gear 6 and the spool shaft 5 is released, and the return operation piece 8
1 is engaged with the clutch return gear 82. Then, when the handle 12 is rotated in the yarn winding direction from this state, the clutch is automatically returned to the ON state again by the action of the return operating piece 81 and the clutch return gear 82.

In this embodiment, when the number of teeth of the pinion gear 6 is S1 and the number of teeth of the drive gear 7 meshing with the pinion gear 6 is S2, the gear ratio S2 / S1 is 3.5 to 7.5. And the module of both gears 6 and 7 is 0.4 or less, preferably 0.3
It is set in the range of ~ 0.4. As described above, even if the gear ratio S2 / S1 is set to a high value of 3.5 to 7.5 (or the number of teeth of both gears 6 and 7 is the same as the conventional one),
If the outer diameter of the gears 6 and 7 is reduced by setting the module to 0.4 or less, it is possible to reduce the size of the reel body.

That is, if the outer diameter of the pinion gear 6 is reduced by setting the module to 0.4 or less, the handle shaft 8 can be moved to the pinion gear 6 side.
Even if the outside diameter of the spool 3 is set to be large to ensure sufficient winding capacity (the case where the outside diameter of the spool 3 is set to be large in order to secure the winding capacity while making the groove of the spool 3 shallow) Also, it is possible to reduce the size of the reel body while maintaining the gear ratio sufficiently high. Therefore, the reel 1 can be easily gripped, the operability of the reel 1 is improved, and the weight of the reel 1 can be reduced. Therefore, even if thrown repeatedly throughout the day, it is hard to be tired.

If the outer diameter of the pinion gear 6 is reduced, the outer diameter of the drive gear 7 can be increased without increasing the outer diameter of the reel body, so that the gear ratio can be increased. . That is, the range of selection of the gear ratio is larger than that of the related art.

Incidentally, the outer diameter B of the spool 3 is 30 m.
Even if it is in the range of m to 50 mm, if the modules of the gears 6 and 7 are set in the range of 0.3 to 0.4, the gear ratio S2 /
While setting S1 to a high value of 3.5 to 7.5, the outer diameter of the circular side plate (the outer diameter of the reel body) A
In the range of 35 mm to 70 mm, the reel 1 can be made compact.

In order to reduce the outer diameters of the gears 6 and 7 by reducing the size of the modules of the gears 6 and 7 as described above, the supporting accuracy of the gears 6 and 7 is improved as compared with the conventional case (the gears 6 and 7). 7 must be strongly supported). For this reason, in the present embodiment, both ends of the pinion gear 6 are mounted on the bearings 39 and 3.
9, both ends of a handle shaft 8 that rotatably supports the drive gear 7 and bearings 38, 38.
It is rotatably supported by. As described above, if the gears 6 and 7 are firmly supported, even if the gears 6 and 7 are small, the gears 6 and 7 may separate from each other, or the gears 6 and 7 may slip or tilt due to some external force. Disappears. That is, the modules of the gears 6 and 7 can be set low without any trouble, and the outer diameter of the gears 6 and 7 can be sufficiently reduced.

Note that the modules of the gears 6 and 7 are set larger than in the present embodiment (since the gear support accuracy is lower than in the present embodiment, the modules cannot be set smaller than in the present embodiment. 4) Conventional form is shown in FIG.
Is shown in Further, in order to compare the present embodiment with the conventional embodiment shown in FIG. 4, the conventional gears 6, 7 and the reel body are shown by two-dot chain lines in FIGS. As can be seen from these figures, the conventional gears 6, 7
Since the module could not be reduced to 0.4 or less, the outer diameter was larger than that of this embodiment when compared with the same number of teeth. Therefore, the size of the reel 1 cannot be reduced to the extent of the present embodiment.

FIGS. 6 to 8 show a second embodiment of the present invention. In the above-described first embodiment, the present invention is applied to a round dual-bearing type reel, but in the second embodiment, the present invention is applied to a dual-bearing type reel having a different shape.

As shown in FIG. 6, the dual-bearing type reel 1A according to the present embodiment comprises left and right frames 102a and 102b.
And a reel including a frame 102 having a rod mounting portion (not shown) integrally formed at the center of the left and right frames 102a and 102b, and left and right side plates 103a and 103b mounted on the left and right frames 102a and 102b, respectively. It has a main body 104.

A spool shaft 106 is rotatably supported between left and right frames 102a and 102b (left and right side plates 103a and 103b) via bearings 107a and 107b. A fishing line is wound around the spool shaft 106. A spool 106a is attached.

A through hole 195 is formed on the outer peripheral surface of the portion of the spool shaft 106 to which the spool 106a is attached and fixed, for the same purpose as the groove 55 in the first embodiment.

The spool 106a is configured to be rotatable by rotating the handle 110, and the handle 110 is attached to an end of a handle shaft 110a protruding from the left side plate 103a. Note that knobs 192 are provided at both ends of the handle 110.

The handle shaft 110a is connected to the spool shaft 106
And is rotatably supported via a bearing 190 between the left frame 102a and the left side plate 103a.
The one-way clutch 112 is configured to be rotatable only in the fishing line winding direction.

Between the left frame 102a and the left side plate 103a, the rotational movement of the handle 110 is applied to the spool shaft 106.
A drive mechanism 114 for transmitting to the spool 106a when the fishing line is unwound from the spool 106a during fishing.
And a drag mechanism 116 for applying a predetermined drag force to the power supply.

The drive mechanism 114 includes a drive gear 118 rotatably supported by the handle shaft 110a, and a pinion gear 120 meshing with the drive gear 118. The pinion gear 20 is connected to the drive gear 114 via bearings 191 and 191. And is rotatably supported by the left frame 102a and the left side plate 103a.

In the fishing reel of the present invention, the drive gear 118 and the pinion gear 120 transmit the rotational movement of the handle 110 to the spool shaft 106, and drive the spool 106a together with the spool shaft 106 to rotate. The spool drive system is accommodated between the left frame 102a and the left plate 103a.

The circumferential groove 1 is formed on the outer periphery of the pinion gear 120.
20a is formed, and a clutch plate 124 slidable in the axial direction by a clutch operating member 122 (see FIGS. 7 and 8) is engaged with the circumferential groove 120a. In this case, if the clutch operation member 122 slides the clutch plate 124 to move the pinion gear 120 in the axial direction, the driving force transmission state (clutch ON state) as shown in FIG. It is possible to switch to a spool free rotation state (clutch OFF state) in which the gear 120 is disengaged.

It should be noted that the clutch O
As a method of returning to the N state, there is a method of automatically returning by a winding operation of the handle 110, other than a method of returning the clutch operation member 122.

The drag mechanism 116 includes a brake plate 126, a lining material 128, and the like.
26 and the lining material 128 are pressed against the drive gear 118 with a predetermined pressing force by rotating a drag operation member 130 attached to the handle shaft 110a. The pressing force at this time is such that the ratchet plate 1 rotates integrally with the handle shaft 110a.
By acting on the drive shaft 32, a predetermined drag force can be generated between the handle shaft 110a and the drive gear 118.

The spool shaft 106 absorbs backlash of the spool shaft 106 in the thrust direction.
A pressing mechanism that applies a braking force to the rotation of the spool shaft 106 is engaged. The pressing mechanism includes a thrust shaft 134 inserted into the pinion gear 120 and abutting on the end surface of the spool shaft 106, and a thrust shaft 134. And a cap 136 for pressing the cap 134 in the thrust direction. In this configuration, when the cap 136 is tightened, the thrust shaft 134 is pressed against the end surface of the spool shaft 106 in accordance with the tightening amount. As a result, the play of the spool shaft 106 in the thrust direction is eliminated, and the desired frictional force is reduced. Provided to the spool shaft 106.

A level wind device 138 is provided between the left and right frames 102a and 102b.
The level wind device 138 includes a guide tube 140 having a long hole 140a formed in the left-right direction,
Worm shaft 142 rotatably supported within 40
And a slot 14 attached around the guide cylinder 140.
0a, and a fishing line guide member 144 engaged with the worm shaft 142 via the fishing line guide member 144.
Is formed with a fishing line guide hole (not shown) through which the fishing line is inserted.

The worm shaft 142 is connected to the spool shaft 1
It is arranged on the front side (on the fishing line payout direction side) with respect to 06. A worm shaft driving gear 146 is attached to the worm shaft 142. The worm shaft driving gear 146 is connected to a drive gear via a plurality (two in the present embodiment) of intermediate gears 148 and 150. 118 (see FIG. 7).

The worm shaft driving gear 14
6, the intermediate gears 148 and 150, and the drive gear 118
A rotational drive of the handle 110 is transmitted to the worm shaft 142 to rotate the worm shaft 142 and reciprocate the fishing line guide member 144 (hereinafter, referred to as a level wind drive system). The level wind drive system includes the left frame 102a and the left plate 103a together with the spool drive system described above.
And is housed between.

In the configuration described above, the handle 1
When the drive gear 118 is rotated by the rotation operation of 10, the rotational motion is transmitted to the pinion gear 120 and to the worm shaft driving gear 146 via the intermediate gears 148 and 150. At this time, the rotation of the pinion gear 120 causes the spool shaft 10 to rotate.
6 rotates to rotate the spool 106a in the fishing line winding direction. At the same time, the rotation of the worm shaft driving gear 146 causes the worm shaft 142 to rotate,
The fishing line guide member 144 is reciprocated in the left-right direction. As a result, the fishing line is wound around the spool 106a at a predetermined winding angle via the fishing line guide hole of the fishing line guide member 144, and is uniformly wound on the spool 106a at a predetermined density without offset.

A backlash prevention mechanism is provided between the right frame 102b and the right side plate 103b to prevent the spool 106a from rotating excessively when the fishing line is fed. In the present embodiment, a magnetic brake device 152 is applied to the backlash prevention mechanism.

As shown in FIG. 6, the brake device 15
2 is fixed to the spool shaft 106 and the spool shaft 10
6, an annular conductive member 154 formed concentrically
A first annular magnet 156 formed concentrically opposite the inside of the annular conductive member 154 and arranged at a predetermined gap from the annular conductive member 154; and an outside of the annular conductive member 154. A second annular magnet 158 which is formed concentrically and faces a predetermined distance from the annular conductive member 154, and relatively moves the first and second annular magnets 156 and 158. And an operation knob unit 160 to be operated.

According to such a brake device 152,
By operating the operation knob unit 160, the first and second
By changing the facing magnetic poles of the annular magnets 156, 158, the braking force applied to the spool 106a can be adjusted.

By the way, also in this embodiment, if the number of teeth of the pinion gear 120 is S1 and the number of teeth of the drive gear 118 meshing with the pinion gear 120 is S2, the gear ratio S2 / S1 is 3.5 to 7.5. , And the module of both gears 118 and 120 is set to 0.4 or less, preferably, in the range of 0.3 to 0.4. Therefore, the same operation and effect as in the first embodiment can be obtained. In the present embodiment, the gears 146, 148, and 150 that mesh with the drive gear 118 also have a module of 0.4 or less, preferably 0.3 to
It is set in the range of 0.4. Gears 118, 120,
146, 148, and 150 modules are set to be larger than in the present embodiment (the module cannot be set as small as in the present embodiment because the gear support accuracy is lower than in the present embodiment). FIGS. 7 and 8 show a conventional gear 11 for comparison with the present embodiment.
8, 120, 146, 148, 150 and the reel body are shown by two-dot chain lines. As can be seen from these figures, the conventional gears 118, 120, 146, 148, 15
In the case of 0, since the module could not be reduced to 0.4 or less, when compared with the same number of teeth, the outer diameter was larger than that of the present embodiment. Therefore, the size of the reel 1A cannot be reduced to the extent of the present embodiment.

FIG. 9 shows a knob 12a (19) provided on the handle 12 (110) of the first and second embodiments.
2) is shown enlarged. Knob 12a (192)
Is formed of a metal material such as an aluminum alloy or a copper alloy, and has a concave portion 200 for obtaining a good grip feeling. The surface of the concave portion 200 is provided with a laser engraving 202 for preventing slippage. The laser engraving 202
Are shown in FIGS. 10 and 11.

[0058]

As described above, according to the dual bearing reel for fishing of the present invention, the gear ratio can be maintained high even if the spool has a sufficient groove capacity while the groove of the spool is made shallow. Thus, the reel body can be made compact.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view of a double-bearing fishing reel according to a first embodiment of the present invention.

FIG. 2 is an enlarged sectional view of a main part of the dual-bearing fishing reel of FIG. 1;

FIG. 3 is a sectional view taken along line AA of FIG. 1;

FIG. 4 is a sectional view corresponding to FIG. 3 of a conventional double-bearing fishing reel.

FIG. 5 is a cross-sectional view showing an engaged state of a pinion gear and a drive gear of the dual-bearing fishing reel of FIG. 1;

FIG. 6 is a sectional view of a double-bearing fishing reel according to a second embodiment of the present invention.

7 is a side view showing a configuration of a spool drive system and a level wind drive system provided in the main body of the fishing dual-bearing reel of FIG. 6;

FIG. 8 is a cross-sectional view showing a meshing state of gears constituting a spool drive system and a level wind drive system.

FIG. 9 is a side view showing a first example of a handle knob.

FIG. 10 is a side view showing a second example of the handle knob.

FIG. 11 is a side view showing a third example of the handle knob.

[Explanation of symbols]

 1, 1A: Double-bearing reel for fishing 3: Spool 5: Spool shaft 6: Pinion gear 7: Drive gear 8: Handle shaft 12: Handle

Claims (2)

[Claims] 1. A spool on which a fishing line is wound, a spool shaft rotating integrally with the spool, a reel body rotatably supporting the spool shaft, and a pinion mounted on the spool shaft and rotatable integrally with the spool shaft. A gear, a handle shaft rotatably attached to the reel body, and a drive gear attached to the handle shaft and rotating integrally with the handle shaft and meshing with the pinion gear, to operate a handle provided on the handle shaft. Thereby, the outer diameter of the reel body is set in the range of 35 mm to 70 mm in the dual bearing reel for fishing configured to rotate the handle shaft and rotate the spool via the pinion gear meshing with the drive gear. The outer diameter of the spool is set in the range of 30 mm to 50 mm, and the teeth of the pinion gear are set. If the number of teeth of the drive gear meshing with the pinion gear is S2, the gear ratio S2
/ S1 is set in the range of 3.5 to 7.5, and the module of both gears is set in the range of 0.3 to 0.4. 2. An end portion of a handle shaft is rotatably supported by a bearing, and an end portion of a pinion gear or an end portion of a shaft portion supporting the pinion gear is rotatably supported by a bearing. The dual-bearing fishing reel according to claim 1, wherein: