JP2021052676A - Fishing reel and drive gear thereof - Google Patents

Abstract

To provide a fishing reel that can simplify gear manufacture, and can achieve optimal fishing operation making full use of a clutch mechanism (clutch winding operability, clutch-off operability, and clutch-on operability).SOLUTION: A fishing reel of the present invention includes: a drive gear 11 rotated by the rotating operation of a handle 10; a pinion gear 21 co-rotatably engaged and disengaged to/from a spool 6 supported in a reel body rotatably; and a clutch mechanism 20 for switching a spool 6 between a power transmission state and a power cut-off state by sliding the pinion gear 21 using external operation while being engaged with the drive gear 11. The power transmission of the clutch mechanism 20 is controlled on/off by engagement conditions where a torsion angle β of the drive gear 11 and the pinion gear 21 is set in 5°≤β≤25°, and a pressure angle α is set in 3°≤α≤16°, respectively.SELECTED DRAWING: Figure 1

Description

The present invention relates to a fishing reel and its drive gear, 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. ..

Normally, fishing reels such as double-bearing reels and single-bearing reels have a take-up drive mechanism that transmits the rotation of the handle to a spool that rotatably supports the reel body, and a reel that transmits the power transmission path of the take-up drive mechanism. Equipped with a clutch mechanism that switches between a power transmission state that allows the fishing thread to be wound around the spool by external operation of the switching member attached to the main body and a power cutoff state that allows the spool to rotate freely and release the fishing thread. There is.

The take-up drive mechanism includes a drive gear provided on the handle shaft and a pinion gear that meshes with the drive gear. In order to improve rotational performance and strength, a helical tooth gear is generally adopted. ing. Further, in the clutch mechanism, the engaging portion on the pinion gear side is engaged with the engaging portion on the spool shaft side (spool side) by an external operation, and the pinion gear is engaged with the drive gear in the axial direction. Therefore, a special power transmission path peculiar to the fishing reel that switches between the power transmission state and the power cutoff state is configured. Furthermore, during the winding operation where a load is applied during actual fishing, the clutch engaging part on the pinion gear side does not come off from the clutch engaging part on the spool side and winding becomes impossible, and the meshing state with the drive gear does not deteriorate. , The inclination direction of the tooth gear is set so that the urging force acts in the direction in which the pinion gear is engaged with the spool shaft side.

In the case of a pinion gear, the inclination direction of the helical gear defines a twist angle with respect to the axial direction, and this twist angle has a great influence on the ease of disengagement, strength, and rotational feeling of the clutch. There is. That is, in the conventional double-bearing type reel, the optimum twist angle is selected according to the gear system of the take-up drive mechanism in consideration of the fishing method, the target fish, etc., and if the twist angle is small, The clutch is easier to disengage, but the rotational feeling is reduced, and if the twist angle is large, the clutch mechanism becomes difficult to disengage, but the rotational feeling is improved. It has meshing characteristics.

When using a double-bearing reel that can be cast during actual fishing, the clutch mechanism that switches the spool rotatably supported by the reel body between the power transmission state (clutch ON) and the power cutoff state (clutch OFF) is loaded. Stable winding operation can be performed while maintaining the power transmission state even during taking (clutch winding operability), and the clutch is used when adjusting the length of the device hanging from the rod tip or when switching to release the device to a predetermined point. The OFF operation can be easily performed (clutch disengagement operability), the device during casting operation prevents unnecessary sinking of the device from the water surface at the time of landing, and the device quickly shifts to the winding state to efficiently invite the device. It is required to have various functions related to the clutch, such as what can be done (operability with clutch).

During actual fishing operation, the clutch mechanism may be switched to the power cutoff state (clutch OFF) while tension is applied to the fishing thread, and the feeding state of the fishing thread may be controlled by summing operation, but tension is applied to the fishing thread. In this case, the clutch OFF operation becomes difficult to be performed quickly and easily due to the influence of the urging force acting when the helical gears are engaged (the pinion gear is urged toward the spool side).
Therefore, the wall of the engagement groove of the pinion gear that engages with the engagement pin of the spool shaft is provided so that the clutch OFF operation can be performed quickly even if a strong load acts on the clutch mechanism (a strong tension acts on the fishing thread). Patent Document 1 knows that the helical gear is in the same direction as the inclination direction.

Patent No. 6407578

The double-bearing reel disclosed in Patent Document 1 pays attention to the wall portion of the engaging groove of the pinion gear so that the wall portion is oriented in the same direction as the twisting direction of the pinion gear. It is necessary to accurately align the directionality of the wall portion of the engaging groove and the tooth surface, and the processing is not easy. That is, while the tooth surface is cut by an involute milling cutter (hob), the wall part of the engaging groove needs to be machined using another cutting tool, which complicates the machining process and performs highly accurate machining. It is difficult to achieve and the manufacturing cost is high.

Furthermore, in terms of the function of the clutch, the clutch is easily disengaged (clutch disengagement operability), but on the other hand, the clutch engaging portion is easily separated due to the influence of the inclined wall of the pinion gear during the winding operation when tension is applied to the fishing thread. Therefore, the meshing state with the drive gear is unstable and the take-up rotation performance (clutch take-up operability) is inferior. In addition, when the spool is rotating in the feeding direction at the time of landing in the casting operation and the handle is rotated to quickly shift to the winding state to prevent unnecessary sinking of the mechanism, the spool shaft side The engagement pin comes into contact with the inclined wall of the engagement groove of the pinion gear and easily escapes to the outside, and problems such as the clutch cannot be reliably moved to the winding state (clutch engagement operation) are likely to occur during actual fishing. ..

The present invention has been made by paying attention to the above-mentioned problems, and the gear manufacturing can be simplified, and the optimum fishing operation (clutch winding operability, clutch disengagement operability, clutch engagement operability) making full use of the clutch mechanism can be achieved. ), And its drive gear.

As described above, the clutch mechanism of the fishing reel has a drive gear and a pinion gear that mesh with each other, and when the clutch mechanism is switched between a power transmission state and a power cutoff state, one pinion gear maintains the meshing state. There is a peculiarity of moving the clutch in the axial direction with sliding resistance acting on the tooth surface. The present invention pays attention to the peculiarity of the clutch mechanism peculiar to the fishing reel, and does not separately process the tooth surface and the engagement groove of the pinion gear as in the above-mentioned conventional technique, but the drive gear and the engagement groove. Provided is a meshing system that constitutes an optimum clutch mechanism that effectively suppresses sliding resistance when forming a tooth surface of a pinion gear.

In order to achieve the above object, the present invention meshes with a drive gear that rotates by rotating a handle, a pinion gear that rotatably engages and disengages with a spool that is rotatably supported by a reel body, and the drive gear. In a fishing reel equipped with a clutch mechanism that switches the spool to a power transmission state and a power cutoff state by sliding the pinion gear by an external operation in this state, the twist angle β of the drive gear and the pinion gear is set to 5 °. It is characterized in that the power transmission of the clutch mechanism is ON / OFF controlled under the meshing conditions in which the pressure angle α is set to ≦ β ≦ 25 ° and the pressure angle α is set to 3 ° ≦ α ≦ 16 °.

According to the fishing reel having the above configuration, the twist angle β of the pinion gear is set to the optimum angle according to the application in consideration of the rotation 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. Further, in such a configuration, when the hob forming the tooth surface is cut, the pressure angle for effectively suppressing the sliding resistance can be formed, so that the gear constituting the clutch mechanism can be easily manufactured. Cost reduction is also possible.

According to the present invention, a fishing reel in which gear manufacturing can be simplified and a series of fishing operability of a clutch mechanism for clutch winding operation, clutch disengaging operation, and clutch engaging operation is optimized, and A drive gear is obtained.

The plan view which shows one 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. Enlarged view of the pinion gear that meshes with the drive gear. The schematic diagram which showed the state which the gears mesh with each other and transmit the power.

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. However, the double-bearing reel shown in the figure is used for lure fishing. The type of thing is illustrated.

As shown in FIGS. 1 to 3, the reel main 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 thread winding body portion 6a around which the fishing thread is wound and flange portions 6b and 6b on both the left and right sides, and the fishing thread is regulated by the flange portions 6b and 6b on both the left and right sides to wind the fishing thread. It is wound around the rotating body portion 6a.

The spool 6 is configured to be rotated by rotating the handle 10, and the handle 10 is 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 side plate 3b. It is configured to be rotatable only in the direction.

A drive gear 11 is provided between the right frame 2b and the right plate 3b so as to be rotatably supported by the handle shaft 7 and to transmit the rotational movement of the handle 10 to the spool shaft 5 side. A known drag mechanism 12 that engages with the drive gear 11 that rotates by the rotation operation of 10 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 thread 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 has a central hole 21a that penetrates in the axial direction. The spool shaft 5 (or the spool shaft 5) is formed in the center hole 21a. It may be a support shaft that abuts on the end face of the spool shaft 5).

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. As is known, the clutch member 23 resists the urging force of the urging member 90 by pushing down the clutch operating member 24 arranged between the left and right frames 2a and 2b (operating from the clutch ON state to the clutch OFF state). Then, it is driven toward the right side in the drawing, whereby the pinion gear 21 is moved to the right side along the spool shaft 5.

In this case, both sides of the pinion gear 21 (both sides of the spool 6 side and the side plate 3b side of the teeth 21A meshing with the drive gear 11) are provided on the reel body 1 (right frame 2b, right side plate 3b, see FIG. 1). The bearings 24A and 24B are supported by the collar C (resin material), and are in axially movable and rotatably in contact with the inner peripheral surfaces of the inner rings of the bearings 24A and 24B. 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, recesses 25a that can be engaged with and disengaged from the engaging pins 5b and 5b provided at the right end (small diameter portion 5B) of the spool shaft 5 are provided. In this case, the engaging pins 5b and 5b are projected in the radial direction of the spool shaft 5, and the recess 25a is provided along the radial direction on the end face of the pinion gear so that the engaging pins 5b are fitted. It is formed (see FIG. 5). As shown in FIG. 2, the state in which the engaging protrusions 5b and 5b of the spool shaft 5 are engaged with the recess 25a is the clutch ON state, and as shown in FIG. 3, the clutch mechanism 20 (clutch member). The clutch OFF state is a state in which the pinion gear 21 is moved toward the right side in the drawing by 23) and the engaging pins 5b and 5b are disengaged from the recess 25a (a state in which the engaging states of the two are 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 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 thread 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, after being transmitted from the handle shaft 7 to the drive gear 11 and the gear via the drag mechanism 12, it is transmitted to the worm shaft 52 of the level wind device 50 via the gear, and the worm shaft is rotated. 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 thread is evenly wound around the spool 6 via the fishing thread guide portion 54 of the engaging member 53. It is turned.

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

Then, when the clutch operating member 24 is moved (operated 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 attached. Driven toward the right side in the figure against the urging force of the force member 90, the pinion gear 21 is moved toward the right side in the figure, thereby engaging the spool shaft 5 as shown in FIG. The engagement of the recess 25a of the pinion gear 21 with the portions 5b and 5b is released. Therefore, the spool 6 is in a free rotatable state (fishing thread 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. 5) and the tooth surface 11F of the drive gear 11 (FIG. 5). 4) slides in contact with each other.

After that, when the handle 10 is rotated or the clutch operating member 24 is operated again, 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). To. As a result, the end faces of the pinion gears 21 come into contact with the engaging protrusions 5b and 5b of the spool shaft 5 while rotating, and the engaging protrusions 5b and 5b of the spool shaft 5 are fitted into the recesses 25a of the pinion gear 21 to enter the wall. It is in a state of abutting and engaging with the portion 25e in the rotational direction (fishing thread winding state) (see FIGS. 1 and 2), and the rotational driving force of the handle 10 is transmitted from the pinion gear 21 to the spool shaft 5. Even when the clutch is returned to the ON state, the tooth surface 21F of the pinion gear 21 and the tooth surface 11F of the drive gear 11 slide in contact with each other.

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, both gears remain meshed when the clutch is turned on / off. There is a peculiarity that the tooth surfaces slide with each other. 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. 5, 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 if the twist angle is 0 °, the twist angle will be described. 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 thread, the pinion gear 21 slides with the spool. Problems such as easy disengagement and erroneous recovery even when the clutch is off occur.

The lower limit of the twist angle is set to 5 ° or more, 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, a small casting reel that is gripped and held together with a fishing rod is used so that the clutch ON to OFF operation, casting operation, clutch ON operation, and handle winding operation are frequently repeated during actual fishing. Therefore, it is desirable that the reworking operation can be performed smoothly and that the person does not get tired even if such an operation is repeated for a long time. 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 thread 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 frequent rewinding operations and delicate winding operations are performed.

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 thread. 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.
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 power (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. 6, 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 size should be to improve operability.

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 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 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 25g of the recess 25a is formed on an inclined surface so that one edge side with respect to the wall portion 25e that abuts and engages in the rotation direction is lower than the other edge side, and the engagement pin 5b rotates. It is easy to abut and engage with the wall portion 25e of the pinion gear 21.

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 yield strength (400 to 600 MPa) is used, sufficient tooth strength can be maintained even if the pressure angle is formed at 6 °. Is possible. 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 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 system of 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 clutch can be smoothly turned ON / OFF during actual fishing. Therefore, even when tension is applied to the fishing thread, the clutch OFF operation can be performed quickly and easily. That is, it is possible to realize the optimum fishing operation (clutch winding operability, clutch disengagement operability, clutch engagement operability) by making full use of the clutch mechanism.

Further, a wall portion formed at the end of the pinion gear 21 and engaging with the engaging pin provided on the support shaft of the spool in the rotational direction is formed parallel to the axial direction of the support shaft of the spool. By doing so, the meshing state of the pinion gear and the drive gear is also stabilized, so that the take-up rotation performance (clutch engagement operability and clutch take-up operability) can be improved. In this case, unlike the conventional technique, it is not necessary to perform precision processing such that the wall portion of the engaging groove of the pinion gear that engages with the engaging pin of the spool shaft is in the inclined direction of the screw tooth, and simply Since the clutch OFF operation can be easily performed only by forming the tooth surface (cutting so as to have a predetermined pressure angle), the machining process is not complicated and the machining is highly accurate. Since it is not required, the manufacturing cost will not be high.

The fishing reel incorporating the drive gear (meshing system) as described above can be applied to various types of double bearing reels and single bearing reels, but is applied to small reels such as lure fishing. Is more effective. Specifically, the distance between the core of a small fishing reel or drive gear in which the outer diameter D of both flanges 6b of the spool 6 is set to 20 mm to 50 mm and the core of the pinion gear is It is preferable to apply it to a small fishing reel set to 15 mm to 30 mm or a small reel set to a handle turning radius of 30 mm to 80 mm. That is, it is possible to repeat the delicate winding operation without getting tired when the rewinding operation is frequently performed and the delicate winding operation is performed.

Further, 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 so that the spool 6 rotates 6 or more times with one rotation of the handle (gear ratio is 1: 6 or more). In the casting operation, while the spool is rotating in the feeding direction at the time of landing, the handle can be rotated to quickly shift to the winding state to prevent unnecessary sinking of the gimmick, and the gimmick can be quickly collected. It becomes possible to do. Even in such a case, the engaging pin of the spool shaft can be securely engaged with the engaging groove of the pinion gear, so that the clutch can be reliably moved to the winding state and the spool can be rotated quickly. It becomes possible to make it.

Although the embodiment of the present invention has been described above, the fishing reel according to the present invention can be applied to a single bearing reel in addition to the double bearing reel.

1 Reel body 5 Spool shaft 6 Spool 10 Handle 11 Drive gear 11A Tooth 20 Clutch mechanism 21 Pinion gear 21A Tooth

Claims (5)

A drive gear that rotates by rotating the handle, a pinion gear that rotatably engages and disengages with a spool that is rotatably supported by the reel body, and the pinion gear that slides by external operation while meshing with the drive gear. In a fishing reel equipped with a clutch mechanism that switches the spool between a power transmission state and a power cutoff state.
The power transmission of the clutch mechanism was controlled to be ON / OFF under 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 reel for fishing that is characterized by that. At the end of the pinion gear, a wall portion on which an engaging pin provided on the support shaft of the spool abuts and engages in the rotational direction is formed parallel to the axial direction of the support shaft of the spool. The fishing reel according to claim 1. The spool is rotatably bored between the side plates of the reel body via a support shaft, and flange portions are formed on both sides of a bobbin body around which the fishing thread is wound.
The fishing reel according to claim 1 or 2, wherein the outer diameters of both flange portions are set to 20 mm to 50 mm. The fishing reel according to claim 2 or 3, wherein the spool is driven by winding at a gear ratio of a drive gear and a pinion gear that rotate 6 or more times with one rotation of the handle. A drive gear used for the winding drive mechanism of fishing reels.
The drive gear is a drive gear for a fishing reel, wherein the twist angle β is set to 5 ° ≤ β ≤ 25 ° and the pressure angle α is set to 3 ° ≤ α ≤ 16 °, respectively.

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