JP2021073955A - Fishing reel - Google Patents

Abstract

To provide a fishing reel which can achieve an optimal fishing operation by utilizing a clutch mechanism.SOLUTION: A fishing reel of the present invention includes: a spool 6 around which fishing line is wound; a drive gear 11 that rotates by a rotational operation of a handle; and a clutch mechanism 20 which switches the spool between a power transmission state and a cut-off state by sliding a pinion gear 21 in an engaged state with the drive gear 11 by an operation of a switching member 24 so as to integrally engage/detach with the spool 6. A switching member 24 is provided on a spool rear side of the reel body in a vertically movable manner. The spool 6 radially projects on both sides of a line winding part 6a around which the fishing line is wound, has a flange part 6b whose outer diameter is set at 20 mm to 50 mm. A power transmission of the clutch mechanism 20 is ON/OFF controlled under an engagement condition in which a torsion angle beta of the drive gear 11 and the pinion gear 21 is set at 5 degrees≤beta≤25 degrees, and a pressure angle alpha is set at 3 degrees≤alpha≤16 degrees.SELECTED DRAWING: Figure 2

Description

The present invention relates to a fishing reel, and more particularly to a fishing reel characterized by a drive gear constituting a drive gear that is rotationally driven by a winding operation of a handle and a pinion gear that meshes with the drive gear.

Among the fishing reels, for example, both bearing reels have a take-up drive mechanism that transmits the rotation of the handle to the spool that is rotatably supported by the reel body, and a power transmission path of the take-up drive mechanism to transfer the fishing thread to the spool. It is equipped with a power transmission state that enables winding and a clutch mechanism that switches the spool to a free rotation state and a power cutoff state that enables the release of fishing thread.

The above-mentioned double bearing reel has a structure suitable for casting a device such as a lure. For example, in order to improve casting performance, the spool is made lighter (thin wall shape, a plurality of through holes). Is known to reduce inertia and improve the flight distance of the tackle (Patent Documents 1 and 2).

Japanese Patent Application Laid-Open No. 10-165057 JP 2013-192507

When the casting operation is performed using the above-mentioned known double-bearing reels, after adjusting the length of the tackle hanging from the rod tip, the spool is summed at the same time as the clutch disengagement operation while holding the reel body by hand. Casting operation toward the point of. Then, the clutch is engaged (handle winding operation or clutch operating member operation) together with the spool summing operation at the timing of the water landing of the device, and a series of operations such as guiding and winding the device are repeatedly performed. ..

The clutch mechanism for actual fishing of such casting reels is each operation of "ON to OFF clutch disengagement operation", "OFF to ON clutch engagement operation", and "Clutch winding operation maintaining ON state". Reliable performance without hindrance and efficiency of rework are required in the process of this series of continuous fishing operations. That is, the quality of this series of operations affects the fishing results and is an important factor that affects the casting performance.
Although the above-mentioned public literature describes that the flight distance is improved by reducing the spool inertia, it does not smoothly and reliably perform a series of continuous operations from the release operation of the device to the guidance / winding operation, and casting. It is not possible to sufficiently improve the performance.

The present invention has been made by paying attention to the above-mentioned problems, and is for fishing that can realize the optimum fishing operation (clutch disengagement operability, clutch winding operability, clutch engagement operability) by making full use of the clutch mechanism. The purpose is to provide reels.

In order to achieve the above object, the present invention meshes with a spool rotatably provided between the left and right side plates of the reel body, a drive gear that rotates by rotating a handle provided on one side plate, and the drive gear. The switching member is provided with a clutch mechanism that switches the spool between a power transmission state and a cutoff state by sliding the pinion gear in the state of being in the state by operating an external switching member and integrally engaging and disengaging with the spool. In a fishing reel provided so as to be movable up and down behind the spool of the reel body, the spool is radially projected on both sides of a thread winding body around which a fishing thread is wound, and has an outer diameter of 20 mm to 50 mm. The clutch mechanism has a flange portion to be set, and the clutch mechanism is set under meshing conditions in which the twist angle β of the drive gear and the pinion gear is set to 5 ° ≤ β ≤ 25 ° and the pressure angle α is set to 3 ° ≤ α ≤ 16 °. It is characterized in that the power transmission of the above is controlled ON / OFF.

The twist angle β of the pinion gear incorporated in the fishing reel having the above configuration is set to an optimum angle according to the application in consideration of the rotational feeling and the ease of disengaging the clutch. Then, in such a meshing relationship between the drive gear and the pinion gear, by setting the pressure angle α to 3 ° ≤ α ≤ 16 °, the action of acting in the direction perpendicular to the tooth surfaces of both gears in the meshed state. The force in the linear direction can be reduced, which also reduces the resistance force when the pinion gear slides in the axial direction, makes it easier to disengage the clutch mechanism, stabilizes the clutch engaged state, and has good winding performance. Can be maintained. That is, while maintaining a good rotational feeling during the winding operation, a series of continuous operations of shifting from the fishing line release operation of the casting operation to the fishing line winding can be performed lightly and surely.

According to the present invention, it is possible to obtain a fishing reel capable of realizing an optimum fishing operation (clutch disengagement operability, clutch winding operability, clutch engagement operability) by making full use of the clutch mechanism.

The plan view which shows 1st Embodiment of the fishing reel (both bearing reel) which concerns on this invention. The figure which shows the main part of the winding drive mechanism of the fishing reel shown in FIG. 1 (clutch ON state). The figure which shows the main part of the winding drive mechanism of the fishing reel shown in FIG. 1 (clutch OFF state). Enlarged view of the drive gear incorporated in the take-up drive mechanism. (A) is a perspective view showing an engaging wall portion of the engaging pin and the pinion gear, and (b) is a cross-sectional view showing a state in which the engaging pin is engaged with the engaging wall portion. An enlarged view showing a modified example of the pinion gear. The schematic diagram which showed the state which the gears mesh with each other and transmit the power. The plan view which shows the 2nd Embodiment of the fishing reel (both bearing reel) which concerns on this invention.

First, with reference to FIGS. 1 to 3, the fishing reel according to the embodiment of the present invention will be described by exemplifying both bearing reels.
In the case of a double-bearing reel, the present invention includes a type suitable for various fishing methods such as for boat fishing and lure fishing, but the configuration is particularly suitable for lure fishing. ..

As shown in FIGS. 1 to 3, the reel bodies 1 of both bearing reels are mounted on the left and right frames 2a and 2b and the left and right frames 2a and 2b with a predetermined space, respectively, via a sealing material. It is provided with side plates 3a and 3b. The left and right frames 2a and 2b are integrated via a plurality of columns, and the reel body 1 is attached to a reel seat (not shown) of a fishing rod by a reel leg (not shown) provided on the lower column.

A spool shaft 5 is rotatably supported between the left and right frames 2a and 2b (left and right side plates 3a and 3b) via bearings 4A and 4B, and a spool 6 is attached to the spool shaft 5. The spool 6 is formed with a fishing line winding body (thread winding body) 6a around which the fishing line is wound and flanges 6b and 6b on both the left and right sides, and the fishing line is formed by the flanges 6b and 6b on both the left and right sides. It is regulated and wound around the fishing line winding body 6a.

In the spool 6 of the present embodiment, the spool shaft 5 is prevented from rotating and fitted to the inner center portion of the fishing line winding body portion 6a via a disc-shaped connecting portion 6c so as to reduce the weight. It is provided with a support portion 6d through which the fishing line is inserted, and has a structure in which a hollow portion (gap) S is formed between the fishing line winding body portion 6a and the spool shaft 5. That is, the spool 6 is configured so that the inertial force can be reduced, the impact is mitigated, and the clutch engagement operability is improved. In this case, the spool 6 may be made of a lightweight metal such as an aluminum alloy or a magnesium alloy so as to reduce the weight, and an opening may be formed if necessary.

The size of the spool 6 is specified by the outer diameter of the flange portion 6b. As described above, the double-bearing reel in the present invention is configured to be suitable for lure fishing, and is in a state where the reel body is gripped together with the fishing rod, particularly, the side plate on the anti-handle side is gripped and held together with the fishing rod. , A small type is considered so that the above series of operations can be performed without any trouble (without getting tired). Therefore, the outer diameter D of the flange portion 6b of the spool 6 is in the range of 20 mm to 50 mm, and the reel body is miniaturized according to the size of the spool. Further, as the side plates 3a and 3b of the reel body of the present embodiment, circular ones are used in the side view, but a spool having an outer diameter D of the flange portion 6b in the range of 20 mm to 50 mm is incorporated and gripped. As long as it is easy to hold, its shape is not limited.

The spool 6 having the above configuration is rotated by rotating the handle 10 attached to the end of the handle shaft 7 protruding from the right side plate 3b. The winding operation of the handle 10 is transmitted to the spool 6 via the winding drive mechanism described below.

The handle shaft 7 is rotatably supported between the right frame 2b and the right side plate 3b via a bearing (not shown), and the fishing thread is wound by a one-way clutch (not shown) interposed between the right frame 2b and the right side plate 3b. It is configured to be rotatable only in the direction.

A drive gear 11 rotatably supported by the handle shaft 7 to transmit the rotational movement of the handle 10 to the spool shaft 5 side is provided between the right frame 2b and the right plate 3b, and the rotation of the handle 10 is provided. A known drag mechanism 12 that engages with the drive gear 11 that rotates by operation to apply a predetermined drag force to the spool 6 is housed. The drag mechanism 12 is adapted to apply a predetermined drag force to the spool 6 when the fishing line is unwound from the spool 6 during fishing, and includes a plurality of friction plates 12a that come into contact with the drive gear 11. In such a drag mechanism 12, the pressure contact force with respect to the drive gear 11 is adjusted by rotating the operating member 13 arranged at the end of the handle shaft 7, and the drag with respect to the spool 6 is adjusted. It is configured so that the force can be adjusted.

A part of the clutch mechanism 20 is formed in the teeth 11A of the drive gear 11, and the pinion gear 21 (the teeth 21A of the pinion gear 21) as a power transmission member is meshed with the teeth 11A. The pinion gear 21 is a member that transmits the rotation of the drive gear 11 to the spool 6 (spool shaft 5), and a central hole 21a penetrating in the axial direction is formed, and the spool shaft 5 (or spool shaft 5) is formed in the center hole 21a. A support shaft that abuts on the end face of 5) is penetrated.

In the present embodiment, the right end side of the spool shaft 5 abuts on the large diameter portion 5A, the small diameter portion 5B continuous with the large diameter portion 5A, and the end surface of the shaft portion 5C (or the small diameter portion 5B) extending from the small diameter portion 5B. It may be a separate support shaft), and the shaft portion 5C is inserted into the central hole 21a of the pinion gear 21 as described above. Further, the spool shaft 5 is a shaft provided inside an adjusting member 60 (dial operating body) in which the right end surface 5a (of the shaft portion 5C) is screwed into the support portion 3ba of the reel body 1 (right side plate 3b). By hitting the direction regulating unit 62, the movement in the axial direction is regulated. The adjusting member 60 constitutes an operating member of the spool braking mechanism 70 that applies a braking force to the free rotation of the spool. By rotating the adjusting member 60, a predetermined push is applied to the spool shaft 5. Pressure is applied as braking force.

A circumferential groove 21b is formed in a part of the pinion gear 21 along the circumferential direction, and the clutch member 23 constituting the clutch mechanism 20 is engaged with the circumferential groove 21b. The clutch mechanism 20 slides the pinion gear 21 by operating a clutch operating member (switching member) 24 arranged so as to be vertically movable behind the spool, and powers the spool by engaging and disengaging integrally with the spool 6. It is a mechanism that switches between a state and a cutoff state. As is known, a cam 24b formed on a cam member 24a movably supported on the right frame (sliding movement or rotational movement) can be engaged with the clutch member 23, and the left and right frames 2a The clutch member 23 is moved by the cam 24b of the moving cam member 24a by the downward movement operation (switching operation from the clutch ON state to the clutch OFF state) of the clutch operating member 24 arranged so as to be movable up and down behind the spool between 2b. , It is driven toward the right side in the figure against the urging force of the urging member 90. That is, the pinion gear 21 is moved to the right along the spool shaft 5 via the cam member 24a by the push-down operation (clutch OFF operation) of the clutch operating member 24, and is engaged with the spool shaft as described later. The clutch is disengaged and the clutch is turned off.

The cam member 24a described above is preferably made of a resin having good operating efficiency in order to reduce the sliding frictional resistance between the right frame 2b and the clutch member 23.
As described above, the clutch operating member 24 is arranged at the rear position of the spool so that it can be easily disengaged while holding the reel body 1, so that the principle of leverage and the reduction of frictional resistance are good. The clutch OFF operation can be smoothly performed by the combination with the cam member 24a and the organic coupling relationship between the drive gear and the pressure angle of the pinion gear, which will be described later.

In the pinion gear 21, both sides of the teeth 21A that mesh with the drive gear 11 in the axial direction (both sides of the teeth 21A that mesh with the drive gear 11 on the spool 6 side and the side plate 3b side) are the reel body 1 (right frame 2b, right side plate). It is supported by the bearings 24A and 24B provided in 3b) via the collar C (resin material), and can be rotated with respect to the inner peripheral surface of the inner ring of the bearings 24A and 24B and can be moved in the axial direction on the reel body. It is supported. That is, the side of the pinion gear 21 connected to the spool 6 is supported by the first bearing 24A, and the side opposite to the side connected to the spool 6 is supported by the second bearing 24B. The collar C may be deleted and the bearings 24A and 24B may directly support both sides of the pinion gear 21.

At the left end of the pinion gear 21 on the spool 6 side, a recess 25a that can be engaged with and disengaged from the engaging pin 5b provided at the right end (small diameter portion 5B) of the spool shaft 5 is provided. In this case, the engaging pin 5b is projected in the diametrical direction of the spool shaft 5, and the recess 25a is formed along the diametrical direction on the end face of the pinion gear so that the engaging pin 5b fits. (See Fig. 5). As shown in FIG. 2, the state in which the engaging pin 5b of the spool shaft 5 is engaged with the recess 25a is the clutch ON state, and as shown in FIG. 3, the clutch mechanism 20 (clutch member 23) is used. The clutch OFF state is a state in which the pinion gear 21 is moved toward the right side in the drawing and the engagement pin 5b is disengaged from the recess 25a (a state in which the engagement state between the two is released).

The pinion gear 21 can be automatically returned from the clutch OFF state to the clutch ON state by a known automatic return mechanism when the clutch operating member 24 is returned or when the handle 10 is wound up. ing.

A level wind device 50 is provided between the left and right frames 2a and 2b of the reel body 1, and the level wind device 50 is shown in the guide cylinder 51 and rotatably supported in the guide cylinder 51. It includes a worm shaft that does not, an engaging member 53 having a pin (not shown) that engages with the worm shaft, and a fishing line guide portion 54 attached to the engaging member 53. Further, a gear (not shown) is attached to the right side plate side of the worm shaft, and this gear meshes with a gear (not shown) that rotates integrally with the drive gear 11 or the handle shaft 7. ..

In the double bearing reel configured as described above, when the handle 10 is rotationally operated in the clutch ON state shown in FIGS. 1 and 2, the rotational motion is transmitted to the level wind device side and the level wind device side via the take-up drive mechanism. It is transmitted to the spool side.
That is, the rotation of the handle 10 is transmitted from the handle shaft 7 to the drive gear 11 and the gear via the drag mechanism 12, and then transmitted to the worm shaft of the level wind device 50 via the gear, and causes the worm shaft to move. Rotate. At this time, the engaging member 53 of the level wind device 50 slides left and right according to the rotational movement of the worm shaft, so that the fishing line is evenly wound around the spool 6 via the fishing line guide portion 54 of the engaging member 53. It is turned.

Further, the rotational driving force transmitted to the drive gear 11 by the rotational operation of the handle 10 is transmitted to the pinion gear 21, and is transmitted to the spool shaft 5 via the engaging pin 5b engaged with the recess 25a of the pinion gear 21. Be transmitted. As a result, the spool 6 is rotationally driven.

Then, when the clutch operating member 24 is moved (pushed down from the clutch ON state to the clutch OFF state) from the clutch ON state (fishing thread winding state) shown in FIGS. 1 and 2, the clutch member 23 is moved. , The pinion gear 21 engaged with the clutch member 23 is moved toward the right side in the drawing against the urging force of the urging member 90 via the cam 24b of the cam member 24a. As a result, as shown in FIG. 3, the engagement of the recess 25a of the pinion gear 21 with the engagement pin 5b of the spool shaft 5 is released. Therefore, the spool 6 is in a free-rotating state (fishing line feeding state) in which transmission of rotational power from the drive gear is cut off.

At this time, the teeth 11A of the drive gear 11 and the teeth 21A of the pinion gear 21 are always in a meshing relationship, and therefore, the tooth surface 21F of the pinion gear 21 (see FIG. 5A) and the tooth surface of the drive gear 11 The 11F (see FIG. 4) slides in a meshed contact state.

After that, when the handle 10 is rotated or the clutch operating member 24 is operated, the clutch mechanism 20 is returned from the clutch OFF state to the clutch ON state, and the pinion gear 21 is moved to the spool shaft 5 side (left side). .. As a result, the end face of the pinion gear 21 comes into contact with the engaging pin 5b of the spool shaft 5 while rotating in the direction of the arrow in FIG. 5A. The end face of the pinion gear 21 is formed so that the end portion 25f1 side is high and the end portion 25f2 side is low along the circumferential direction, and the engagement pin 5b is in contact with the end portion 25f1 side of the engagement wall portion 25e and is recessed. It fits into 25a and engages with the engaging wall portion 25e in the rotational direction (see FIG. 5B).

As shown in FIG. 5A, the recess 25a of the present embodiment is formed on the end face of the pinion gear along the radial direction so that the engaging pin 5b is fitted, and is formed in the axial direction of the spool shaft 5. It is provided with an engaging wall portion 25e parallel to the above. By forming the engaging wall portion 25e so as to be parallel to the axial direction of the spool shaft 5 in this way, as shown in FIG. 5B, when the engaging pin 5b is fitted into the recess 25a, it engages. A stable contact surface can be secured between the wall portion 25e and an unnecessary gap, whereby the engaging pin 5b can be inadvertently disengaged from the recess 25a or rattled. It is suppressed, the clutch engagement operability and the meshing state with the drive gear are stable, and the winding operability (clutch winding operability) is improved.
The recess 25a into which the engaging pin 5b fits may be formed in the cross direction as shown in FIG.

The above-mentioned drive gear 11 and pinion gear 21 (collectively referred to as drive gears) are always in a meshing relationship, and in a fishing reel, the tooth surface of the pinion gear 21 is operated when the clutch is turned on / off. The 21F and the tooth surface 11F of the drive gear 11 have a peculiarity of sliding in a contact state. In addition, in power transmission by meshing gears of fishing reels, when the handle is wound up, the meshing is as smooth as possible and noise is not generated. It has been adopted. That is, as shown in FIG. 4, the drive gear 11 is formed so that the teeth 11A (tooth surface 11F) continuously formed in the circumferential direction are twisted, and the teeth 21A (tooth surface 21F) of the pinion gear 21 are formed. Also, as shown in FIG. 5A, it is formed so as to be twisted.

Here, the twist angle (β) of the drive gear in the present invention will be described.
The twist angle is an angle that specifies how much the tooth (tooth muscle) 21e is twisted with respect to the axis X of the gear, and the twist angle is 0 °. If so, it is a meshing relationship between spur gears. As described above, in the fishing reel, the meshing relationship of the drive gear is set to have a certain degree of twist angle so that the meshing is smooth and noise is not generated.

In the drive gear incorporated in the fishing reel according to the present invention, the twist angle (β) is set to 5 ° ≦ β ≦ 25 °.
The twist angle becomes a factor that hinders the sliding of the pinion gear 21 toward the right side plate against the urging force of the urging member 90 by pushing down the clutch operating member 24, and the twist angle is small. For example, the pinion gear 21 becomes easy to slide. However, if the twist angle is set too small, the smoothness of rotation is lowered and noise is likely to be generated, and further, it is easy to slide, which causes a problem that the engagement with the spool side is easily disengaged. .. Specifically, in the power transmission state (clutch ON state), the force of the gear tooth surface to press against the spool side becomes weak, and when a strong load is applied to the fishing line, the pinion gear 21 slides with the spool. Problems such as easy disengagement and erroneous recovery even when the clutch is off occur. In particular, if the engaging wall portion 25e of the recess 25a formed at the end portion of the pinion gear 21 is tilted so as to correspond to the twist angle, such a problem is likely to occur.

The lower limit of the twist angle is set to 5 °, which is such that the above-mentioned problem does not occur remarkably (no inconvenience occurs during use). Further, if the twist angle is set large, the smoothness is improved and the noise is reduced, and the pinion gear can be prevented from malfunctioning. However, if the twist angle is set too large, the clutch operating member 24 is pressed when the clutch is disengaged. It becomes difficult to push down. Specifically, when the temperature exceeds 20 °, the pushing-down operation tends to be difficult, and when the temperature exceeds 25 °, considerable resistance acts on the pushing-down operation. Therefore, the upper limit of the twist angle is 25. It is preferable to set it to °.
In this case, with a small casting reel that is gripped and held together with the fishing rod (as shown in FIG. 1, a reel incorporating a spool having an outer diameter D of the flange portion of 20 mm to 50 mm), the clutch is turned on during actual fishing. Since it is used to frequently repeat the OFF operation, casting operation, clutch ON operation, and handle winding operation, the rewinding operation can be performed smoothly, and even if such operations are repeated for a long time, it will not get tired. Is desirable. That is, in such a type of fishing reel, the upper limit of the twist angle is preferably set to 20 °, preferably 18 °.

In fact, when various commercially available double-bearing reels are verified, the twist angle of the drive gear differs depending on the application, but it is generally set within the range of 5 ° ≤ β ≤ 20 °. That is, for jigging and boat fishing, the noise at the time of winding the fishing line is not so much a concern, and smooth rotation performance is not required so much. Therefore, the twist angle is set to a relatively small angle within the above range. , In a casting reel using a lure or the like, the twist angle is set to a relatively large angle within the above range because a frequent rewinding operation and a delicate winding operation are performed. In particular, in a reel incorporating a spool 6 having a small diameter as shown in FIG. 1, the twist angle β can be set in the range of 15 ° to 20 ° so that the meshing ratio can be increased and smooth rotation can be obtained. preferable.

As described above, in the case of a small reel, particularly a reel used for lure casting, it is considered preferable to set the twist angle to a certain extent, but if it is set too large, a strong tension acts on the fishing line. At that time, the clutch mechanism cannot be quickly turned off.
In the present invention, the pressure angle of the drive gear is adjusted so that the clutch disengagement operation can be smoothly performed even under such a situation, and further, a series of clutch engagement operation and clutch winding operation can be smoothly performed without any trouble. I am paying attention.

Here, the pressure angle (α) of the drive gear incorporated in the fishing reel will be described with reference to the schematic diagram of FIG. 7.
The teeth 11A and 21A in which the drive gear 11 and the pinion gear 21 mesh with each other are formed in an involute tooth profile. In the figure, when the radius of the base circle of each gear (the circle that is the base of the involute gear) is indicated by R11 and R21, the involute tooth profile of each tooth is assumed to have a thread wound around the base circle, and the thread is in a tense state. It is defined by the curve drawn by the tip when solved by. Further, the angle α formed by the common tangent line L of each base circle of both gears and the common tangent line L1 at the contact point (pitch point P) of the reference circles (circles indicated by radii R11a and R21a) of both gears is the pressure angle. ..

That is, the pressure angle is defined in the direction orthogonal to the tooth surface in the involute tooth profile, and the force Fn acting in this direction becomes the force to transmit the force (force to push the tooth surface; normal force at each tooth surface). In this case, if the tooth surface is formed so that the pressure angle α becomes small, the base circles R11 and R21 of each gear become large. Therefore, considering the transmission of force with the same torque, the normal force Fn at each tooth surface (By setting the pressure angle small, the normal force Fn on each tooth surface can be reduced).

As described above, the pinion gear 21 slides in the axial direction while meshing with the drive gear due to the action of the clutch mechanism, but since this sliding direction is orthogonal to the paper surface of FIG. 7, the above The smaller the vertical drag force Fn acting on the clutched tooth surface, the easier it is for the pinion gear 21 to slide. That is, as the pressure angle α becomes smaller, the frictional resistance when the pinion gear 21 slides in the axial direction is reduced, and the clutch is easily disengaged.

Currently, a standard standard rack tooth profile (JIS B 1701-1 2012; standard involute tooth profile) is used for the tool (hobbing) that forms the involute tooth surface of the gear incorporated in the fishing reel, and the pressure angle α is The one that becomes 20 ° is adopted. In this case, even if such a tool is used, it is possible to form a gear having a pressure angle in the range of 17 ° to 19 ° depending on the amount of dislocation. As described above, it is considered advantageous to make the pressure angle α smaller than the conventional general angle of 20 ° in consideration of the operability of the clutch mechanism, etc., but the present inventors have set the pressure angle. An evaluation test (sensory test) was conducted to determine how small the clutch should be to improve operability, including the ease of disengaging the clutch.

The evaluation test is conducted by five testers, and a small double-screw reel for lure fishing is used so that a series of operations such as clutch disengagement operability, clutch engagement operability, and clutch winding operability can be comprehensively evaluated. I went there. That is, in lure fishing, the above operation is frequently repeated, and in the winding operation, it is easy to grasp a subtle difference. Therefore, among the two bearing reels, a small casting reel was used for evaluation. For evaluation, multiple bearing reels of the same size with different twist angle and pressure angle settings of the drive gear built into the reel body were prepared, and each tester performed the above-mentioned series of operations on each reel. A comprehensive evaluation was performed by repeating the process. Specifically, the reels used were evaluated on a three-point scale, with 3 points if they felt very good, 1 point if they felt good, and 0 points if they were the same as before, and 5 testers. When the total score was 12 points or more, it was evaluated as ⊚, when it was 8 points or more, it was evaluated as 〇, when it was 4 points or more, it was evaluated as Δ, and when it was 3 points or less, it was evaluated as ×.

Further, in the double bearing reels used, the outer diameter D of the flange portion 6b shown in FIG. 1 is 34 mm, the shaft core of the drive gear 11 (the central shaft of the handle shaft 7) and the shaft core of the pinion gear 21 (spool shaft 5). A small one having an inter-core distance Ld of 22.6 mm and being able to be held and held together with a fishing rod, and having a drive gear 11 and 21 with a gear ratio of 6.3 was used. Further, the turning radius of the handle 10 is 45 mm, and the engaging pin 5b is provided for the recess 25a in which the engaging pin 5b of the spool shaft formed at the end of the pinion gear 21 can be engaged and disengaged. The engaging wall portions 25e and 25e that are engaged and on which the contact load in the rotational direction acts are formed so as to be parallel to the spool shaft (axis center X) in the axial direction (see FIGS. 2 and 5). The end surface of the pinion gear 21 is formed on an inclined surface so that one edge portion 25f2 side is lower than the other edge portion 25f1 side, and the engagement wall portion of the pinion gear 21 on which the engagement pin 5b rotates. It is configured so that it can be easily contacted and engaged with the 25e.

Then, in the reel of the above-described form, the twist angles β are formed at 5 °, 10 °, 15 °, 20 °, and 25 °, and the pressure angles α are formed at 14 °, 16 °, 18 °, and 20 °, respectively. I prepared the one that incorporated the drive gear that was used. In this case, the pressure angle of 20 ° is a drive gear incorporated in a conventional double bearing reel.
The results of the evaluation test are shown in Table 1 below.

According to the results of the evaluation test described above, when the pressure angle was 18 °, the overall evaluation of all testers did not give a feeling that the pressure was improved so much with the conventional 20 ° reel. When the angle is set as small as 16 ° and further as 14 °, the overall evaluation of the entire tester tends to be improved. Therefore, it can be said that it is preferable to set the pressure angle to 16 ° or less. That is, by setting the pressure angle to 16 ° or less in the range of the twist angle of 5 ° ≦ β ≦ 25 °, the above-mentioned series of operability is improved.

Further, as the pressure angle is reduced, the involute tooth surface gradually becomes steep, which causes a problem of undercutting the tooth root. Therefore, the lower limit of the pressure angle is related to the number of teeth (gear ratio) of the drive gear and the module, but the angle at which undercut does not occur when cutting the tooth surface, specifically, 3 ° It may be set to (preferably 5 °) or more. That is, in the present invention, the pressure angle of the drive gear may be set in the range of 3 ° ≤ α ≤ 16 °.

The normal force (surface pressure) Fn acting on the tooth surface when the gear is rotationally driven changes depending on the pressure angle α. As described above, the normal force Fn is reduced by reducing the pressure angle, but at the same time, the strength of the tooth root side is reduced by undercutting. That is, when the pressure angle is reduced in order to reduce the normal force, the tooth surface tends to be gradually sharpened, the tooth root is more likely to be scraped and undercut, and the strength resistance of the gear is lowered. In particular, in a fishing reel in which the clutch mechanism is continuously turned ON / OFF by sliding in a state where the gears are meshed with each other, a decrease in the strength of the gears cannot stably maintain good clutch performance during actual fishing. Therefore, the surface pressure (maximum surface pressure) that can be tolerated for the drive gear is specified, and the strength of the gear is analyzed for the relationship between the torsion angle (β) and the pressure angle (α) for each surface pressure. Using analysis software, we also analyzed the permissible value of the pressure angle for each twist angle that can withstand each surface pressure.
In this analysis, when a constant surface pressure is applied to the tooth surface of the drive gear, the surface pressure can be tolerated for each twist angle of 5 °, 10 °, 15 °, 20 °, 25 °, and 30 °. The minimum and maximum values of the pressure angle to be applied were obtained. As for the drive gears to be meshed, the distance between the cores was 22.6 mm, the gear ratio was 6.3, and the module was arbitrary.
The analysis results are shown in Table 2 below.

In the above table, in the case where the surface pressure is 800 MPa, the case where a material having a relatively high strength and a high yield strength is used as the drive gear corresponds to the case. Considering such materials, the minimum pressure angle can be set to 6 °. That is, if it is set in the range of 6 ° ≤ α ≤ 16 °, if a material with high proof stress (material strength proof stress 400 to 600 MPa) is used, the tooth strength is sufficient even if the pressure angle is formed at 6 °. It is possible to maintain. In the table, the case where the maximum surface pressure is 450 MPa is also analyzed, but this corresponds to the case where a material having a low yield strength of the material strength is used as the drive gear. Even when the drive gear is formed of such a material, it is possible to maintain the strength of the teeth by setting the pressure angle to 11 ° or more. That is, if the pressure angle is set in the range of 11 ° ≤ α ≤ 16 °, it is possible to maintain sufficient tooth strength even if the drive gear is formed using a material having a low yield strength. Is.

As described above, in the meshing relationship between the drive gear 11 and the pinion gear 21, the twist angle β is 5 ° ≤ β ≤ 25 ° and the pressure angle α is 3 ° ≤ α ≤ 16 ° (preferably 6 ° ≤ α ≤ 16). By controlling the power transmission of the clutch mechanism ON / OFF under the meshing conditions set to °, more preferably 11 ° ≤ α ≤ 16 °), the reel body was gripped and held together with the fishing rod during actual fishing. In this state, the clutch can be turned on and off smoothly. Further, even when tension is applied to the fishing line, the clutch operating member 24 installed on the rear side of the spool can be easily pushed down while maintaining the gripping and holding state, so that the clutch OFF operation can be performed quickly. It can be easily done. That is, a series of continuous operations (clutch winding operability, clutch disengagement operability, clutch engaging operability) in which the casting operation shifts from the fishing line release to the fishing line winding while maintaining a good rotational feeling during the winding operation. ) Can be done lightly and surely.

Further, in a small reel suitable for casting operation, as described above, it is preferable to form the twist angle β so as to be relatively large (15 ° to 20 °), and thus the twist angle β can be increased. For example, since a large sliding resistance is generated when the clutch is switched from ON to OFF, it is preferable to set the pressure angle α small within the above range. Specifically, if the twist angle β is 15 ° ≤ β ≤ 20 °, the pressure angle α can be set in the range of 6 ° ≤ α ≤ 16 ° and further 6 ° ≤ α ≤ 12 °. preferable.

Further, the engaging wall portion 25e formed at the end of the pinion gear 21 and engaged with the engaging pin 5b provided on the support shaft of the spool in the rotational direction is parallel to the axial direction of the spool shaft. Since the meshing state of the pinion gear 21 and the drive gear 11 is also stable, the take-up rotation performance (clutch engagement operability and clutch take-up operability) can be improved. In this case, as in the prior art, the engaging wall portion of the engaging groove of the pinion gear that engages with the engaging pin of the spool shaft needs to be precisely processed so as to be in the inclined direction of the tooth. Instead, the clutch OFF operation can be easily performed by simply forming the engaging wall portion parallel to the axial direction and cutting the tooth surface so as to have a predetermined pressure angle. Therefore, the processing process is not complicated, and high-precision processing is not required, so that the manufacturing cost does not increase.

Further, as described above, the spool 6 of the present embodiment has a hollow portion (gap) S formed between the fishing line winding body portion 6a and the spool shaft 5 to reduce the weight. In such a spool, when the spool rotates freely during casting, the inertial force is reduced, and when the clutch is turned on, the impact on the recess 25a of the engaging pin 5b is alleviated, so that the clutch can be turned on reliably. It becomes possible.

Further, since the pinion gear 21 is supported by the reel body so that both sides of the teeth 21A meshing with the drive gear can be rotated and moved axially by the bearings 24A and 24B, the pinion gear 21 slides in the axial direction. Is stable, the engagement pin 5b fits into the recess 25a when the clutch is ON, and the engagement pin 5b disengages from the recess 25a when the clutch is OFF, so that optimum clutch performance can be exhibited.

As described above, it is effective to apply the fishing reel incorporating the above-mentioned drive gear (meshing system) to a small reel such as lure fishing. For example, in the double-bearing reel of the second embodiment shown in FIG. 8, the miniaturized spool 6 described above is incorporated, and the left and right side plates 3a and 3b of the reel body 1A are formed in a circular shape in a side view, and one of them is formed. The shape of the side plate (left side plate 3a on the anti-handle side) is formed to have a smaller diameter in the radial direction than the other side plate (right side plate 3b on the handle side).

In this way, by making the left and right side plates of the reel body different in size (different shape), the side plate side in which the take-up drive mechanism is housed is enlarged to secure sufficient space, while the fishing rod is used during actual fishing. At the same time, the reel body can be easily gripped and held, and the above-mentioned series of operability can be further improved. In this case, by setting the distance Ld between the shaft cores of the drive gear and the pinion gear within the range of 15 mm to 30 mm, the configuration of the spool 6 described above (the outer diameter of the flange portion 6b is set to 20 mm to 50 mm). In combination with this, a small reel body is constructed, and a double-bearing reel with good casting operability can be obtained.

Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments and can be variously modified.
In the miniaturized double bearing reel described above, it is preferable that the turning radius of the handle is set to 30 mm to 80 mm. That is, with such a turning radius, in addition to a good rotation feeling, it becomes possible to perform a small induction winding operation of the mechanism.

Further, it is preferable that the spool 6 can be driven by winding at the ratio of the number of teeth of the drive gear 11 and the pinion gear 21 (gear ratio is 1: 6 or more) so that the spool 6 rotates 6 or more times with one rotation of the handle. .. According to such a gear ratio, it is possible to quickly shift to the winding state by rotating the handle while the spool is rotating in the feeding direction at the time of landing in the casting operation to prevent unnecessary subsidence of the mechanism. And it is possible to quickly collect the device.

Further, in the above-mentioned engaging wall portion, in addition to the portion where the engaging pin abuts in the rotational direction is parallel to the axial direction of the spool shaft, the engaging wall portion is inclined with respect to the axial direction or tapered to the opening edge. Etc. may be formed. Further, the fishing reel according to the present invention can be appropriately deformed in terms of constituent members such as the shape of the side plate, and can be applied to a single bearing reel in addition to the double bearing reel.

1 Reel body 5 Spool shaft 5b Engagement pin 6 Spool 10 Handle 11 Drive gear 11A Tooth 20 Clutch mechanism 21 Pinion gear 21A Tooth 24A, 24B Bearing 25a Recess

Claims (5)

A spool that is rotatably provided between the left and right side plates of the reel body, a drive gear that rotates by rotating the handle provided on one side plate, and a pinion gear that is in mesh with the drive gear can be operated by an external switching member. It is provided with a clutch mechanism that switches the spool between a power transmission state and a cutoff state by sliding and integrally engaging with the spool.
In a fishing reel in which the switching member is provided behind the spool of the reel body so as to be movable up and down.
The spool has flanges that are radially projected on both sides of the bobbin body around which the fishing line is wound and whose outer diameter is set to 20 mm to 50 mm.
The power transmission of the clutch mechanism was controlled to be ON / OFF under the meshing conditions in which the twist angle β of the drive gear and the pinion gear was set to 5 ° ≦ β ≦ 25 ° and the pressure angle α was set to 3 ° ≦ α ≦ 16 °. A fishing reel that features this. The spool is formed in a disk shape at the inner center portion of the spool body portion, and includes a support portion through which the spool shaft holding the spool penetrates.
The fishing reel according to claim 1, wherein a hollow portion is formed between the spool body portion and the spool shaft. The first or second aspect of the present invention, wherein the distance between the shaft cores of the drive gear and the pinion gear is set to 15 mm to 30 mm, and the shape of the other side plate is formed to have a smaller diameter in the radial direction than the one side plate. Fishing reel. The pinion gear is any one of claims 1 to 3, wherein both sides of the teeth meshing with the drive gear are supported by the reel body so as to be rotatable and axially movable by bearings. The fishing reel described in. The fish fishing according to any one of claims 1 to 4, wherein when the twist angle β is 15 ° ≤ β ≤ 20 °, the pressure angle α is set to 6 ° ≤ α ≤ 12 °. reel.

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