JP2012120444A - Rotation transmission mechanism of fishing reel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve rotation feeling when winding a fishing reel stably and without raising shape accuracy of a gear tooth superfluously.SOLUTION: A rotation transmission mechanism 20 of a double bearing reel is a mechanism in which a spool 15 is rotated by rotation of a handle 2 of the double bearing reel. The rotation transmission mechanism 20 includes a pinion gear 32 and a drive gear 31. The pinion gear 32 can rotate around a shaft of the spool 15. The drive gear 31 can integrally rotate with a handle 2, engages with the pinion gear 32, a number of teeth is at least 100 and at most 500.

Description

  The present invention relates to a rotation transmission mechanism, and more particularly to a rotation transmission mechanism for a fishing reel that operates a spool by rotating a handle of the fishing reel.

  In fishing reels such as dual-bearing reels and spinning reels, a fishing line is wound around the spool by a rotation transmission mechanism that accelerates and transmits the rotation of the handle. The rotation transmission mechanism has a large-diameter drive gear that rotates in conjunction with the rotation of the handle, and a pinion gear that meshes with the drive gear. For example, in a dual-bearing reel, a drive gear is rotated by rotation of a handle, a spool is rotated by a pinion gear, and a fishing line is wound around the spool (for example, refer to Patent Document 1). In a spinning reel, a drive gear using a face gear is rotated by rotating a handle, a rotor is rotated by a pinion gear, and a spool is reciprocated back and forth to wind a fishing line around the spool (for example, Patent Documents). 2).

JP 2000-069889 A JP 2000-125713 A

  In such a fishing reel that rotates the handle to wind up the fishing line, it is important to improve the rotational feeling when the handle is wound up. Gear noise is greatly involved in the rotational feeling. Conventionally, gear noise is reduced by applying a lubricant to the drive gear or processing the shape of the gear teeth of the drive gear with high accuracy. In the method using a lubricant, the effect is not stable due to aging or outflow of the lubricant on the tooth surface. Although it is necessary to improve the accuracy of the housing and gear teeth, there are limitations depending on the processing machine and structure, and human fingertips can detect vibration due to slight processing errors.

  An object of the present invention is to improve the rotational feeling at the time of winding a fishing reel stably without increasing the gear tooth shape accuracy excessively.

A fishing reel rotation transmission mechanism according to a first aspect of the present invention is a mechanism that operates a spool by rotation of a fishing reel handle. The fishing reel is a dual bearing reel. The rotation transmission mechanism includes a pinion gear and a drive gear. The pinion gear is rotatable around the spool axis. The drive gear can rotate integrally with the handle, meshes with the pinion gear, and has 100 to 500 teeth.

  The present inventors conducted various experiments on the drive gear of the fishing reel in order to improve the rotational feeling. In particular, in the case of a dual-bearing reel, it has been found that by increasing the number of teeth of the drive gear to 100 or more, the sense of gear noise is suppressed and the rotational feeling is improved.

  First, we examined the limit of the amplitude per frequency that humans feel by vibrating the handle handle of the fishing reel. Next, for each frequency, the limit of the amplitude at which the gear noise generated on the fishing reel does not feel bad is examined. It has been found that a spinning fisher can tolerate even a relatively large amplitude in a spinning reel having a long distance from the reel mounting leg as a support point to the center of rotation of the handle. Further, it has been found that in a double-bearing reel having a short distance from the reel mounting leg to the center of rotation of the handle, the angler recognizes it as an unpleasant noise even with a relatively small amplitude. Furthermore, it has been found that anglers catch noise particularly severely with small double-bearing reels that hold the reel body through palming.

  Accordingly, the handle handle was vibrated with vibration patterns of five types of vibration A to vibration E that reproduced the noise of various fishing reels, and the minimum amplitude that the operator actually felt as a good / bad limit was investigated. FIG. 1 shows vibration E on a large spinning reel (the distance from the reel mounting leg to the center of rotation of the handle is 85 mm or more), vibration D on a medium / small spinning reel (85 mm or less), and a medium-sized dual-bearing reel. Amplitude felt as good / bad limits for vibration pattern of vibration C (maximum diameter of spool flange 45 mm to 60 mm or less) and vibration B of small dual-bearing reel (maximum diameter of spool flange 45 mm or less) The change of is shown in the table. The vibration A is a minute vibration at a level that does not exist in the current reel, and was performed in order to grasp the limit at which vibration can be perceived. This is shown in a line graph in FIG. In FIG. 2, the vertical axis represents amplitude (μm), and the horizontal axis represents frequency. All the scales are logarithmic scales.

  According to FIG. 2, for example, in vibration D, the smallest amplitude is felt between 70 and 100 Hz. Therefore, it was thought that if the vibration was avoided while avoiding these areas, the sense of gear noise would be suppressed even with relatively large gear noise.

  The angler turns the steering wheel at a speed of at least two revolutions per second on average during normal hoisting, that is, when he is strongly aware of gear noise. However, as the turning radius of the handle increases, the rotation speed decreases and the handle can only be turned about 1.5 turns per second. Note that the faster the rotation speed, the greater the amplitude of the gear noise due to the contact speed between the gears. In addition, gear noise is small when the handle is slowly rotated to wait for the hit, and the angler is not very aware of gear noise while winding the fish.

  Therefore, in the case of a double bearing reel of a medium size (spool diameter of 45 mm or more and 65 mm or less), in order to generate a vibration of 200 Hz or more by avoiding the region of 100 to 200 Hz from the vibration C, the number of teeth is set to 100 or more. It turns out that it only has to be set.

  Here, since the number of teeth of the drive gear is 100 or more, vibration with a frequency of 200 Hz or more can be generated during normal handle winding. This increases the number of teeth, but does not require excessive accuracy on the shape of the gear teeth of the drive gear. For this reason, the sense of gear noise at the time of winding of the double-bearing reel can be stably suppressed without excessively increasing the gear tooth shape accuracy.

  In addition, since it is thought that the angler cannot recognize a sensory difference in vibrations of 1000 Hz or higher, it is not practical to set the number of teeth to 500 or higher in view of the balance of time, cost, and effect required for manufacturing.

  The rotation transmission mechanism for a fishing reel according to a second aspect is the mechanism according to the first aspect, wherein the number of teeth of the drive gear is set according to the maximum diameter of the flange of the spool. In this case, when the maximum diameter of the flange is small, the reel main body is wrapped with the angler's palm by palming, and thus gear noise with a small amplitude is severely captured. For this reason, it is preferable to increase the frequency by increasing the number of teeth more than 100.

  In the mechanism for transmitting rotation of a fishing reel according to a third aspect of the invention, the number of teeth of the drive gear is 150 or more and 500 or less when the maximum diameter of the flange of the spool is 45 mm or less.

  In the vibration B of the small double-bearing reel in FIG. 2 described above, the noise of the smallest amplitude is felt at a frequency of 70 Hz to 300 Hz. Therefore, if the number of teeth is 150 or more, a frequency of 300 Hz or more can be obtained, and the amplitude perceived as the limit can be increased.

  The rotation transmission mechanism for a fishing reel according to a fourth aspect of the present invention is the mechanism according to any one of the first to third aspects, wherein the number of teeth of the drive gear is set according to the rotation radius of the handle. In this case, when the turning radius of the handle is large, it is difficult to turn the handle quickly. Therefore, it is easier to obtain vibration of 200 Hz or more when the number of teeth is as large as possible. Further, when the turning radius of the handle is small, it is easy to turn the handle quickly, so that vibration of 200 Hz or more can be obtained even if the number of teeth is somewhat small.

  The rotation transmission mechanism for a fishing reel according to a fifth aspect of the present invention is the mechanism according to the fourth aspect, wherein the number of teeth of the drive gear is not less than 1.33 times the set lower limit when the rotation radius is not less than 75 mm and not more than 120 mm. It is as follows. In this case, since the turning radius is large, there may occur a case where the handle can be rotated only about 1.5 turns per minute. Even in such a case, vibrations of 200 Hz or less to 300 Hz or less can be avoided.

  A fishing reel rotation transmission mechanism according to a sixth aspect of the invention is a mechanism for operating a spool by rotation of a fishing reel handle. The fishing reel is a spinning reel. The rotation transmission mechanism includes a pinion gear and a drive gear. The pinion gear is rotatable around the spool axis. The drive gear can rotate integrally with the handle, meshes with the pinion gear, and has a number of teeth of 50 to 667.

  In FIG. 2 described above, when the vibration E and vibration D of the spinning reel are seen, it can be seen that when the vibration exceeds 100 Hz, the amplitude that a person feels as the limit of good / bad gradually increases. For this reason, if the number of teeth is 50 or more, if the handle is rotated twice or more per minute as described above, vibration of 100 Hz can be obtained. For this reason, it is possible to suppress the feeling of gear noise when the spinning reel is wound up, and to improve the rotation feeling without increasing the shape accuracy of the gear teeth stably. In addition, since the face gear and hypoid gear which are drive gears of a spinning reel can be manufactured by injection molding or forging using a mold, the time and cost required for manufacturing do not increase extremely by increasing the number of teeth. However, as described above, since it seems that the user will not recognize the difference when the frequency is 1000 Hz or higher, it is meaningless to set the frequency to 667 or higher.

  The rotation transmission mechanism for a fishing reel according to a seventh aspect is the mechanism according to the sixth aspect, wherein the number of teeth of the drive gear is set according to the mounting distance from the fishing rod mounting position of the spinning reel to the rotation center of the handle. Thereby, if the mounting distance from the fishing rod mounting position to the rotation center of the handle is large, the amplitude of vibration increases. For this reason, the vibration of a frequency can be generated by changing the number of teeth according to these.

  In the rotation transmission mechanism for a fishing reel according to an eighth aspect, in the structure according to the seventh aspect, the number of teeth of the drive gear is 60 or more and 667 or less when the mounting distance is less than 85 mm. In the case of a spinning reel, the distance from the fishing rod mounting position to the rotation center of the handle is larger than that of the dual-bearing reel. Therefore, a sensory test as shown in FIGS. 3 and 4 was performed. In FIG. 3, the sensory test which changed the number of teeth of a drive gear into 10 steps | paragraphs and gave the order regarding the rotation feeling of each step | paragraph was performed by six test subjects of AF. The graph which shows the average value of this result is shown in FIG. In FIG. 4, the vertical axis represents the ranking and the horizontal axis represents the frequency. The distance from the fishing rod mounting position to the handle rotation center is less than 85 mm. In this case, as shown in FIG. 4, it was found that the average ranking of the rotational feeling was worst at around 100 Hz to 120 Hz. For this reason, in such a condition, when the number of teeth is 60 or less, vibration in the vicinity of 100 Hz to 120 Hz cannot be avoided, so the number of teeth needs to be 60 or more. Here, since the number of teeth is set to 60 or more, vibration from 100 Hz to 120 Hz is hardly generated, and the sense of gear noise can be suppressed.

  In the rotation transmission mechanism for a fishing reel according to a ninth aspect, in the structure according to the sixth to eighth aspects, the number of teeth of the drive gear is set according to the rotation radius of the handle. In this case, even when the turning radius of the handle is large and it is difficult to turn the handle quickly, the number of teeth can be increased to obtain a frequency of 100 Hz to 120 Hz or more, and the sense of gear noise can be suppressed.

  In the rotation transmission mechanism for a fishing reel according to a tenth aspect, in the structure according to the ninth aspect, the number of teeth of the drive gear is 66 or more and 667 or less when the rotation radius is 85 mm or more. In this case, since the rotation radius is large, the rotation speed is about 1.5 rotations per rotation. For this reason, by making the number of teeth 1.33 times or more, vibrations of 100 Hz to 120 Hz or less are less likely to occur, and the sense of gear noise can be suppressed.

  According to the present invention, since the number of teeth of the drive gear of the dual-bearing reel is 100 or more, vibration with a frequency of 200 Hz or more can be generated during normal handle winding. As a result, the number of teeth increases, but less precision is required for the shape of the gear teeth of the drive gear. For this reason, the sense of gear noise at the time of winding of the double-bearing reel can be stably suppressed without excessively increasing the gear tooth shape accuracy.

  According to another aspect of the present invention, since the number of teeth of the driving gear of the spinning reel is 50 or more, vibration with a frequency of 100 Hz or more can be generated during normal handle winding. This increases the number of teeth, but the accuracy of the shape of the gear teeth of the drive gear is not excessively necessary. For this reason, the sense of gear noise at the time of winding the spinning reel can be suppressed stably without excessively increasing the gear tooth shape accuracy.

A table showing the relationship between the amplitude and frequency of the limit vibration that is acceptable or unacceptable when a vibration pattern is applied The line graph which shows the test result of FIG. The table | surface which shows the sensory test result which investigated the order | rank of the rotation feeling for every frequency of a spinning reel. The line graph which shows the test result of FIG. The perspective view of the double bearing reel which employ | adopted one Embodiment of this invention. FIG. Rotation transmission mechanism and surrounding exploded perspective view The side sectional view of the spinning reel which adopted one embodiment of the present invention. XX sectional drawing of FIG. The side view of a rotation transmission mechanism.

<First Embodiment>
<Overall configuration>
In FIG. 5, a dual-bearing reel employing an embodiment of the present invention is, for example, a medium-sized round reel used for jigging. The round reel includes a reel body 1, a spool rotating handle 2 disposed on the side of the reel body 1, and a star drag 3 disposed on the reel body 1 side of the handle 2. A spool 15 is rotatably mounted on the reel body 1. The reel body 1 can be attached to the fishing rod R via the fishing rod mounting leg 4.

  As shown in FIG. 6, the reel body 1 includes a frame 5, a first side cover 13, a second side cover 14, and a mechanism mounting plate 16. The frame 5 includes a first side plate 10 and a second side plate 11 that are arranged at a predetermined interval, and a plurality of connecting members 12 that connect the first side plate 10 and the second side plate 11. The first side cover 13 is integrally formed with the first side plate so as to cover the outside of the first side plate 10. The second side cover 14 is fixed to the second side plate 11 so as to cover the outside of the second side plate 11. The mechanism mounting plate 16 is disposed on the second side plate 11, and a space for storing various mechanisms described later is formed between the mechanism mounting plate 16 and the second side cover 14.

  The frame 5 is obtained by die casting, and the second side cover 14 is obtained by press-molding a thin metal plate. The first side plate 10, the second side plate 11, and the first side cover 13 each have a circular shape when viewed from the side, and the outer peripheral surface is machined using, for example, a lathe. As shown in FIGS. 5 and 7, the second side cover 14 and the mechanism mounting plate 16 have a shape in which a part of a circle protrudes in the radial direction when viewed from the side. The second side cover 14 also bulges outward in the axial direction around a mounting portion of a handle shaft 30 (described later).

  The plurality of connecting members 12 are plate-like members formed integrally with the first side plate 10 and the second side plate 11 in a shape along the outer peripheries of the first side plate 10 and the second side plate 11. The plurality of connecting members 12 connect the first side plate 10 and the second side plate 11 at, for example, three locations of the rear portion, the lower portion, and the front portion of the reel body 1. Thus, by forming the first side plate 10 and the second side plate 11 and the plurality of connecting members 12 integrally, even if a large load is applied to the reel body 1, deformation such as bending hardly occurs, and the winding efficiency is improved. Reduction is suppressed. The outer peripheral portion of the connecting member 12 is also machined integrally with the first side plate 10, the second side plate 11, and the first side cover 13.

  A fishing rod mounting leg 4 is fixed to the lower connecting member 12. The fishing rod mounting leg 4 is disposed in the front-rear direction along the center position C <b> 1 between the first side plate 10 and the second side plate 11 of the frame 5. The center position C1 is also the center position of the spool portion of the spool 15. A synthetic resin thumb rest 17 for holding the reel together with the fishing rod R is attached to the rear connecting member 12.

  The thumb rest 17 is formed so as to be in contact with the upper part and the rear part of the connecting member 12, and the rear part protrudes radially outward from the first side plate 10 and the second side plate 11, that is, rearward. The upper surface rear portion of the thumb rest 17 is inclined while curving convexly downward. Further, the left end and the right end of the rear portion of the upper surface of the thumb rest 17 are gradually decreased as the rearward protruding amount goes to the left side.

  The thumb rest 17 having such a shape is provided, and the thumb rod 17 is placed on the thumb rest 17 and the fishing rod R is grasped with another finger and the reel is held together with the fishing rod R, so that the fishing rod R can be securely held together with the reel during vertical jigging. Can hold.

  6 and 7, the handle 2 includes a crank arm 6 that is non-rotatably attached to the tip of the handle shaft 30, and a handle shaft C3 that is perpendicular to one end of the crank arm 6 at one end of the crank arm 6. A handle handle 7 is rotatably mounted around the handle. In the handle 2, the rotation plane of the base end portion of the handle handle 7 is closer to the reel body 1 side than the rotation plane of the fixed portion of the crank arm 6 to the handle shaft 30. As a result, the distance between the handle grip 7 and the fishing rod R becomes shorter than before, the torque around the shaft of the fishing rod R when the handle grip 7 is turned to wind up the fishing line is reduced, and the handle winding efficiency is reduced. It can be effectively suppressed. Further, the rotation radius R1 of the handle 2, which is the distance between the handle shaft core C2 of the handle shaft 30 and the handle shaft core C3 of the handle handle 7, is, for example, 73 mm.

  As shown in FIG. 6, the spool 15 is rotatably disposed between the first side plate 10 and the second side plate 11. The spool 15 includes a bobbin trunk 15a around which a fishing line is wound, and a pair of flanges 15b disposed on both sides of the bobbin trunk 15a. A spool shaft 25 penetrates and is fixed to the center of the bobbin trunk 15a. The spool shaft 25 is rotatably supported by the first side cover 13 and the mechanism mounting plate 16 via bearings 26a and 26b. Casting control mechanisms 36 are disposed at both ends of the spool shaft 25. The maximum flange diameter of the spool is 49 mm.

  In a space between the mechanism mounting plate 16 and the second side cover 14, a rotation transmission mechanism 20 for transmitting torque from the handle 2 to the spool 15, a clutch mechanism 21 provided in the rotation transmission mechanism 20, and a clutch A clutch operating mechanism 22 for turning on and off the mechanism 21 is disposed.

<Configuration of rotation transmission mechanism>
The rotation transmission mechanism 20 includes a rotation control mechanism 23 for regulating torque when torque is transmitted from the spool 15 to the handle 2 side. In addition, a centrifugal brake mechanism 24 for braking the spool 15 that freely rotates in the yarn feeding direction is disposed at the center of the second side plate 11. Inside the first side cover 13 outside the first side plate 10, there is a sound generation mechanism for generating sound when the spool 15 rotates, a lock mechanism for completely locking the spool 15 and making it easy to break the thread when rooted, etc. Has been placed.

  As shown in FIG. 7, the rotation transmission mechanism 20 includes a handle shaft 30 having the handle 2 fixed to one end, a drive gear 31 connected to the other end of the handle shaft 30 via a rotation control mechanism 23, and a drive gear. And a pinion gear 32 that meshes with 31. The drive gear 31 can be connected to one end side of the handle shaft 30 via the rotation control mechanism 23 so as to handle the integral rotation.

  The handle shaft 30 is disposed in parallel with the spool shaft 25. One end of the handle shaft 30 is rotatably supported by the mechanism mounting plate 16 via a bearing 35a, and an intermediate portion is rotatably supported by the first boss portion 14a of the second side cover 14 via a bearing 35b. .

  The drive gear 31 has a large number of gear teeth 31 a on the outer periphery and is rotatably attached to the handle shaft 30. The number of teeth of the gear teeth 31a of the drive gear 31 is, for example, “115”. When the maximum outer diameter of the flange 15b of the spool 15 is 45 mm or more and 65 mm or less and the rotation radius R1 is 30 mm or more and less than 75 mm, the number of teeth is preferably 100 or more and 500 or less. Here, in the case of the drive gear 31 of the double-bearing reel, if the number of teeth exceeds 500, it takes time and cost for gear cutting. Also, it is difficult to feel the difference in effect from 500 or less.

  The drive gear 31 is a helical gear with a torsion angle of less than 20 degrees, its pitch circle diameter is approximately 42 mm, and the module is 0.35.

  The pinion gear 32 constitutes the rotation transmission mechanism 20 and also functions as the clutch mechanism 21. The pinion gear 32 is formed at a cross engagement groove 32a formed at one end, a constricted portion 32b formed in the middle, a large number of gear teeth 32c formed adjacent to the constricted portion 32b, and the other end. And a bearing support portion 32d. The gear teeth 32 c mesh with the gear teeth 31 a of the drive gear 31. The number of teeth of the gear teeth 32c is, for example, “18”. In FIG. 7, the number of teeth is not drawn accurately.

  Since the pinion gear 32 has a large number of teeth, the gear teeth 32c have a low tooth height. For this reason, high meshing accuracy is required for the pinion gear 32. In order to realize this, both ends of the pinion gear 32 are supported by the reel body 1. Specifically, one end of the pinion gear 32 in which the engagement groove 32a is formed and the other end in which the bearing support portion 32d is formed are connected to the mechanism mounting plate 16 through the bearing 27a and the bearing 27a via the bearing 27b. The second boss portion 14b of the second side cover 14 is individually supported rotatably. Further, the pinion gear 32 is reciprocally movable in the spool axis direction to a clutch-on position shown on the lower side of the spool axis C4 in FIG. 7 and a clutch-off position shown on the upper side of the spool axis C4.

  In such a configuration, the torque from the handle 2 is directly transmitted to the spool 15 when the clutch mechanism 21 is turned on.

  The clutch mechanism 21 includes a cylindrical pinion gear 32 slidably mounted on the outer periphery of the spool shaft 25, a meshing groove 32 a disposed in a part of the pinion gear 32, and a clutch pin disposed on the spool shaft 25. 33. When the pinion gear 32 is slid along the spool shaft 25 and the meshing groove 32 a is engaged with the clutch pin 33, the rotational force is transmitted between the spool shaft 25 and the pinion gear 32. This state is a connected state (clutch on state). If the engagement between the engagement groove 32 a and the clutch pin 33 is disengaged, the rotational force is not transmitted between the spool shaft 25 and the pinion gear 32. This state is a disconnected state (clutch off state). In the clutch-off state, the spool 15 rotates freely. The pinion gear 32 is biased by the clutch operating mechanism 22 in the direction in which the meshing groove 32a and the clutch pin 33 are engaged, that is, in the clutch-on state.

  The rotation control mechanism 23 includes a roller-type one-way clutch 55 that rotates the handle shaft 30 only in the yarn winding direction (inhibiting rotation in the yarn unwinding direction), a drag mechanism 57, and a claw-type one-way clutch 60. is doing. The drag mechanism 57 is a mechanism for applying a set braking force to the rotation of the spool 15 in the yarn unwinding direction. The drag mechanism 57 can adjust the drag force by the star drag 3. As shown in FIG. 7, the drag mechanism 57 has a plurality of drag washers 57 a attached to the handle shaft 30. A part of the drag washer 57 a is attached to the handle shaft 30 so as to be integrally rotatable, and the rest is attached to the handle shaft 30 so as to be rotatable.

  The claw-type one-way clutch 60 rotates the handle shaft 30 only in the yarn winding direction. As shown in FIGS. 6 and 7, the claw-type one-way clutch 60 includes a ratchet wheel 61 that is rotatably attached to the handle shaft 30 and a ratchet claw 62 that can mesh with the ratchet wheel 61. Yes. The ratchet pawl 62 is biased toward the ratchet wheel 61 side.

  If only the reverse rotation of the handle shaft 30 (rotation in the thread drawing direction) is prohibited, only the claw-type one-way clutch 60 may be provided and the roller-type one-way clutch 55 may be omitted. However, the one-way clutch 60 takes a certain amount of time for the operation in which the ratchet pawl 62 is engaged with or disengaged from the ratchet wheel 61. The roller-type one-way clutch 55 described above is preferable in order to perform the quick and smooth reverse rotation prohibition operation required for the fishing operation, and the claw-type one-way clutch 60 has an excessive force that cannot be borne by the one-way clutch 55. It is effective to pay by

  The clutch operation mechanism 22 has a clutch operation lever 40 for performing clutch on and clutch off operations of the clutch mechanism 21, and the pinion gear 32 is moved between the clutch on position and the clutch off position in conjunction with the operation of the clutch operation lever 40. Move.

<Operation of double-bearing reel>
Next, the operation of the round reel during jigging will be described.

  When the fishing line is fed out, the clutch operating lever 40 is operated to bring the clutch mechanism 21 into the clutch-off state. As a result, the spool 15 is in a freely rotating state, the spool 15 rotates in the line feeding direction by the weight of the jig (device), and the fishing line is fed out from the spool 15.

  When the jig reaches the seabed, the vertical jigging is started by rotating the handle 2 in the yarn winding direction. When the handle 2 is rotated in the yarn winding direction, the clutch mechanism 21 is turned on by the action of a clutch return mechanism (not shown). The rotation of the handle 2 is transmitted from the drive gear 31 to the spool 15 via the pinion gear 32, and the spool 15 rotates in the yarn winding direction. At this time, the one-way clutch 55 and the claw-type one-way clutch 60 are allowed to rotate because the rotation is in the yarn winding direction. Further, since the number of teeth of the drive gear 31 is 100 or more (specifically 115), the number of times the drive gear 31 meshes with the pinion gear 32 is 200 times or more when the handle 2 is rotated twice per minute. Thus, the handle 2 vibrates at 200 Hz or higher. For this reason, as shown in FIG. 2, even if the amplitude increases, it becomes difficult to feel it uncomfortable, the sense of gear noise is suppressed, and the rotational feeling is improved.

  When performing vertical jigging, for example, the rear end (not shown) of the fishing rod R is sandwiched between the left side, the thumb of the left hand is placed on the thumb rest 17 fixed to the rear of the reel body 1, and the fishing rod R is grasped with the remaining fingers. While holding the reel and the fishing rod R, the pumping operation of pinching the fishing rod R with the left hand and pinching the handle handle 7 of the handle 2 with the right hand and rotating the handle shaft 30 at high speed is repeated. In this case, since the rotation speed of the handle 2 is further increased, it is more difficult to feel the amplitude, the sense of gear noise is further suppressed, and the rotational feeling is improved.

  When the handle 2 is rotated in the yarn winding direction, the rotation of the handle 2 is transmitted as it is from the handle shaft 30 to the drive gear 31 via the one-way clutch 55 and the drag mechanism 57. At this time, since the clutch mechanism 21 is in the clutch-on state, the rotation of the drive gear 31 is transmitted from the pinion gear 32 to the spool 15 and the fishing line is wound up.

  Next, when the fishing line is fed out by pulling a fish or the like, the rotation of the spool 15 is transmitted to the drive gear 31 and transmitted to the handle shaft 30 and the one-way clutch 55 via the drag mechanism 57. In the one-way clutch 55, the reverse rotation of the handle shaft 30 is prohibited. If the fish pull is weak, the spool 15 does not rotate and the fishing line is not pulled out. When the fish pull becomes strong and the rotational force of the spool 15 increases, the transmitted rotational force exceeds the set rotational resistance force of the drag mechanism 57. Then, since slip occurs in the drag mechanism 57, the spool 15 side including the drive gear 31 starts to rotate. At this time, a constant resistance force, that is, a drag force is always applied to the spool 15 from the drag mechanism 57. At this time, a strong reaction force acts on the pinion gear 32 in the radial direction. However, since the pinion gear 32 is supported at both ends by the bearing 27a and the bearing 27b, the pinion gear 32 does not escape in the radial direction, and the drive gear The meshing with 31 is maintained.

Second Embodiment
In the first embodiment, the rotation transmission mechanism according to the first embodiment of the present invention has been described by taking a double-bearing reel as an example. In the second embodiment, the rotation transmission mechanism of the spinning reel will be described.

<Configuration of spinning reel>
The spinning reel adopting the second embodiment of the present invention is a medium-sized spinning reel. As shown in FIG. 8, a handle 101, a reel body 102 that rotatably supports the handle 101, a rotor 103, and a spool 104 are provided. The rotor 103 is rotatably supported at the front portion of the reel body 102. The spool 104 winds the fishing line around the outer peripheral surface, and is disposed at the front portion of the rotor 103 so as to be movable back and forth. The handle 101 can be mounted on either the left or right side of the reel body 102.

  As shown in FIGS. 8 and 9, the handle 101 includes a handle shaft 101a, a handle arm 101b extending in a radial direction from the handle shaft 101a, and a handle grip 101c rotatably provided at the tip of the handle arm 101b. Have.

  The reel body 102 includes a reel body 102a having a storage space with an open side, and a lid member 102b (FIG. 9) that is detachably attached to the reel body 102a to close the storage space of the reel body 102a. Have. The reel main body 102 has a main body guard 126 that covers the rear portions of the reel body 102a and the lid member 102b.

  The reel body 102a is made of, for example, a light alloy such as a magnesium alloy or an aluminum alloy, and a T-shaped fishing rod mounting leg 102c extending in the front-rear direction is integrally formed at an upper portion. At the upper part of the fishing rod mounting leg 102c, a mounting seat 102d to which the fishing rod R is mounted is forwardly lowered and disposed in the front-rear direction (left-right direction in FIG. 8). The mounting seat 102d has a transverse section curved in an arc shape and is recessed. A mounting distance L1 which is a distance between the mounting seat 102d which is the fishing rod mounting position and the handle shaft core C5 of the handle 101 is, for example, 90 mm. Further, the rotation radius R2 that is the distance between the handle shaft core C5 and the handle shaft core C6 of the handle handle 101c is, for example, 45 mm.

  As shown in FIG. 8, a rotor drive mechanism 105 and an oscillating mechanism 106 are provided in the storage space of the reel body 102a.

<Rotor drive mechanism>
A rotor drive mechanism 105 (an example of a rotation transmission mechanism) transmits the rotation of the handle 101 to the rotor 103 and also to the spool 104. The rotor drive mechanism 105 rotates the rotor 103 in conjunction with the rotation of the handle 101 and reciprocates the spool 104 back and forth. As shown in FIGS. 9 and 10, the rotor drive mechanism 105 includes a drive gear 111 including a face gear that rotates together with a drive gear shaft 110 that is coupled to a handle shaft 101 a of the handle 101 so as to be integrally rotatable, and the drive gear 111. And a pinion gear 112 meshing with each other.

  As shown in FIG. 9, the drive gear 111 is formed integrally or separately from the drive gear shaft 110 (in this embodiment). The drive gear shaft 110 is coupled to the handle shaft 101a so as to be integrally rotatable by screw coupling or non-circular engagement (screw coupling in this embodiment). The drive gear shaft 110 is rotatably mounted on the reel body 102 by a bearing 127a mounted on the lid member 102b and a bearing 127b mounted on the reel body 102a. A left female screw portion 110a and a right female screw portion 110b that are screwed to the handle shaft 101a are formed on the inner peripheral surfaces of both ends of the drive gear shaft 110. Here, the left female screw portion 110a on the side close to the drive gear 111 is a left screw, and the right female screw portion 110b on the side away from the drive gear 111 is a right screw. Therefore, two types of handle shafts 101a for right-handed screws and left-handed screws are prepared.

  As shown in FIGS. 9 and 10, the drive gear 111 includes a disk portion 111a formed integrally with the drive gear shaft 110, and a face gear formed in a ring shape on the outer peripheral side of one side surface of the disk portion 111a. Part 111b. The face gear portion 111b has a plurality of face gear teeth 111c formed at intervals in the circumferential direction on the outer peripheral side of one side surface of the disc portion 111a.

  The drive gear 111 is formed by forging, for example, an aluminum alloy together with the drive gear shaft 110. The specifications of the drive gear 111 are as follows: the number of teeth is “59”, the outer diameter is 25.9 mm, the inner diameter is 21.4 mm, and the reference offset amount OS is 6.5 mm. In the case of a spinning reel, when the rotation radius R5 of the handle 101 is 30 mm or more and less than 50 mm and the mounting distance L1 is 85 mm or more, the number of teeth is preferably 55 or more and 400 or less. Here, in the case of the spinning reel drive gear 111, if the number of teeth exceeds 400, the face gear teeth have a reduced tooth depth and are difficult to mesh with the pinion gear 112.

  As shown in FIG. 10, the pinion gear 112 has a cylindrical gear main body 112a and a gear portion 112b having helical teeth 112c formed on the rear outer peripheral surface of the gear main body 112a. The gear body 112a is rotatably mounted on the reel body 102a around an axis that is different from the handle shaft 101a (around the spool shaft 115). As shown in FIG. 8, the gear body 112a is rotatably supported by the reel body 102a by a front bearing 114a and a rear bearing 114b before and after the gear portion 112b. A spool shaft 115 can pass through the center of the gear body 112a. A nut 113 for fixing the rotor 103 is screwed to the outer peripheral surface of the front end of the gear body 112a. The rotor 103 is connected to the front outer peripheral surface of the gear body 112a so as to be integrally rotatable.

  The drive gear 111 and the pinion gear 112 are designed to mesh at a reference mesh height. The pinion gear 112 is arranged offset from the rotation center of the drive gear 111 by a reference offset amount. The pitch circle of the drive gear 111 is a distance from the tooth tip of the drive gear 111 to the tooth tip of the pitch circle diameter of the pinion gear 112 (tooth tip diameter−pitch circle diameter) / 2). Therefore, the pitch circle of the pinion gear 112 matches the pitch circle of the drive gear 111 at the reference meshing height. The reference offset amount OS is defined by the distance from the rotation center of the drive gear 111 to the rotation center of the pinion gear 112, as shown in FIG.

  As shown in FIGS. 8 and 9, the oscillating mechanism 106 moves the spool shaft 115 connected to the center portion of the spool 104 via the drag mechanism 160 in the front-rear direction to reciprocate the spool 104 in the same direction. Mechanism. The oscillating mechanism 106 includes a traverse cam shaft 121 arranged in parallel below the spool shaft 115, a slider 122 guided to the reel body 102 a in the front-rear direction along the traverse cam shaft 121, and the tip of the traverse cam shaft 121. And an intermediate gear 123 fixed to the motor. A rear end of the spool shaft 115 is fixed to the slider 122 so as not to rotate. The intermediate gear 123 meshes with the pinion gear 112.

  As shown in FIG. 8, the rotor 103 is made of a light alloy such as a magnesium alloy or an aluminum alloy, is non-rotatably connected to the pinion gear 112, and is rotatable with respect to the reel body 102. The rotor 103 includes a cylindrical portion 130 that is coupled to the pinion gear 112 so as to be integrally rotatable, a first rotor arm 131 that is connected to a position facing the rear portion of the cylindrical portion 130 and that extends forward with a space from the cylindrical portion 130. 2 rotor arms 132.

  The cylindrical portion 130 has a disk-shaped wall portion 130d on the inner peripheral side of the front portion, and an annular boss portion 130e that is connected to the pinion gear 112 so as to be integrally rotatable is formed at the center portion of the wall portion 130d. . The front portion of the pinion gear 112 passes through the inner peripheral portion of the boss portion 130e, and the boss portion 130e is locked to the front portion of the pinion gear 112 so as to be integrally rotatable. In this state, the rotor 103 is fixed to the pinion gear 112 by screwing the nut 113 into the pinion gear 112. A bail arm 144 for guiding the fishing line to the spool 104 is mounted on the outer peripheral side of the tip of the first rotor arm 131 so as to be swingable between a line releasing position and a line winding position.

  Inside the cylinder portion 130 of the rotor 103, a reverse rotation prevention mechanism 150 for prohibiting / releasing the reverse rotation of the rotor 103 is disposed. The reverse rotation prevention mechanism 150 includes a roller-type one-way clutch 151 in which an inner ring rotates freely, and a switching lever 152 that switches the one-way clutch 151 between an operation state (reverse rotation prohibited state) and a non-operation state (reverse rotation permission state). Yes. The switching lever 152 is swingably attached to the reel body 102a. A cam (not shown) is provided at the tip of the switching lever 152. When the switching lever 152 is swung, the one-way clutch 511 is switched between an operating state and a non-operating state by the cam.

  As shown in FIG. 8, the spool 104 is disposed between the first rotor arm 131 and the second rotor arm 132 of the rotor 103, and is attached to the tip of the spool shaft 115 via the drag mechanism 160. . The spool 104 is provided at a front end of the bobbin trunk 104a, a bobbin trunk 104a around which the fishing line is wound, a cylindrical skirt 104b integrally formed with the bobbin trunk 104a behind the bobbin trunk 104a, and the bobbin trunk 104a. And a large-diameter flange portion 104c.

  The drag mechanism 160 brakes the rotation of the spool 104, and includes a drag adjustment knob 161 that is screwed to the tip of the spool shaft 115 and a brake portion 162 that is pressed by the drag adjustment knob 161 to brake the spool 104. is doing.

<Operation of spinning reel>
In the spinning reel configured as described above, the bale arm 144 is in a line releasing posture, and casting is performed by hooking the fishing line on the tip of the index finger. When the device comes into contact with water after casting and the handle 101 is operated in the yarn winding direction, the bail arm 144 returns to the yarn winding posture by a bale reversing mechanism (not shown).

  When the bail arm 144 returns to the yarn guiding posture and the angler rotates the handle 101 in the yarn winding direction, the rotation causes the drive gear 111 to rotate, and the pinion gear 112 that meshes with the drive gear 111 rotates. As a result, the rotor 103 rotates in the line winding direction, the spool 104 reciprocates back and forth, and the fed fishing line is wound around the spool 104. At this time, since the number of teeth of the face gear teeth 111c of the drive gear 111 is 59, the frequency of vibration by the face gear teeth 111c becomes 118 Hz or more by rotating the handle 101 twice or more per minute. For this reason, even if the amplitude of the vibration felt in the handle grip 101c is increased, it is difficult to feel the vibration, the sense of gear noise is suppressed, and the rotational feeling is improved.

<Other embodiments>
As mentioned above, although one Embodiment of this invention was described, this invention is not limited to the said embodiment, A various change is possible in the range which does not deviate from the summary of invention.

  (A) In the first embodiment, the number of teeth of the drive gear 31 of the dual-bearing reel is “115” and the number of teeth of the pinion gear 32 is “18”, but the present invention is not limited to this. In the case of a dual-bearing reel, the number of teeth may be set according to the rotational speed for changing the rotational speed when the handle 2 is wound according to the rotational radius R1 of the handle 2. In any case, the vibration generated by the rotation of the handle 2 may not be 100 Hz or less.

  When the turning radius R1 of the handle 2 is 30 mm or more and less than 75 mm, the number of teeth is preferably 100 or more and 500 or less. When the rotation radius R1 is 75 mm or more and 120 mm or less, the number of teeth is preferably 134 or more and 500 or less.

  (B) In the second embodiment, the number of teeth of the spinning reel drive gear 111 is “59” and the number of teeth of the pinion gear 32 is “11”, but the present invention is not limited to this. In the case of the spinning reel, the rotation speed of the handle changes depending on the rotation radius R2 of the handle 101, and the amplitude changes depending on the fishing rod mounting position of the fishing rod mounting leg 102c. For this reason, the number of teeth may be set by the rotation radius R2 of the handle 101 and the mounting distance L1.

  When the rotation radius R2 is 30 mm or more and less than 50 mm and the mounting distance L1 is less than 85 mm, the number of teeth of the face gear teeth 111c may be 60 or more and 667 or less. Further, when the rotation radius R2 is 50 mm or more and 85 mm or less and the mounting distance L1 is 85 mm or less, the number of teeth may be 80 or more and 667 or less. Further, when the rotation radius R2 is 30 mm or more and less than 50 mm and the mounting distance L1 is less than 85 mm, it is preferably 60 or more and 667 or less.

(C) In the first embodiment, the present invention has been described by taking a star drag type double bearing reel as an example, but the double bearing reel can also be applied to, for example, a lever drag type dual bearing reel. In the second embodiment, the present invention has been described by taking a front drag type spinning reel as an example. However, the present invention can also be applied to a lever brake type spinning reel and a rear drag type spinning reel. Further, the present invention is not limited thereto, and the present invention can be applied to all fishing reels that operate a spool by a drive gear and a pinion gear.
<Features>
(A) The dual-bearing reel rotation transmission mechanism 20 is a mechanism that rotates the spool 15 by the rotation of the handle 2 of the dual-bearing reel. The rotation transmission mechanism 20 includes a pinion gear 32 and a drive gear 31. The pinion gear 32 can rotate around the axis of the spool 15. The drive gear 31 can rotate integrally with the handle 2, meshes with the pinion gear 32, and has 100 to 500 teeth.

  During normal hoisting, that is, when the gear noise is strongly conscious, on average, the angler turns the handle at a speed of 2 or more revolutions per second. However, as the turning radius of the handle 2 increases, the rotation speed decreases and the handle can only be turned about 1.5 turns per second.

  Therefore, in the case of a dual-bearing reel, it can be seen that the number of teeth may be set to 100 or more in order to generate a vibration of 200 Hz or more from the vibration C of FIG.

  Here, since the number of teeth of the drive gear is 100 or more, vibration with a frequency of 200 Hz or more can be generated during normal handle winding. As a result, the number of teeth increases, but excessive accuracy is not necessary for the shape of the gear teeth 31a of the drive gear 31. For this reason, the sense of gear noise at the time of winding of both bearing reels can be suppressed, and the rotational feeling can be improved stably without excessively increasing the shape accuracy of the gear teeth 31a.

(B) In the rotation transmission mechanism 20, the number of teeth of the drive gear 31 is set according to the maximum diameter of the flange 15 b of the spool 15. In this case, when the maximum diameter of the flange 15b is small, the reel main body is wrapped with the angler's palm by palming, and thus gear noise with a small amplitude is severely captured. For this reason, it is preferable to increase the frequency by increasing the number of teeth more than 100.
8 (C) In the rotation transmission mechanism 20, the number of teeth of the drive gear 31 is 150 or more and 500 or less when the maximum diameter of the flange 15b of the spool 15 is 45 mm or less.

  In the vibration B of the small double-bearing reel in FIG. 3 described above, the noise of the smallest amplitude is felt at a frequency of 70 Hz to 300 Hz. Therefore, if the number of teeth is 150 or more, a frequency of 300 Hz or more can be obtained, and the amplitude perceived as the limit can be increased.

  (D) In the rotation transmission mechanism 20, the number of gear teeth 31 a of the drive gear 31 is set according to the rotation radius R 1 of the handle 2. In this case, when the turning radius R1 of the handle 2 is large, it is difficult to turn the handle 2 quickly. Therefore, it is easier to obtain vibrations of 200 Hz or more when the number of teeth is larger than when the turning radius R1 is small. Further, when the turning radius of the handle 1 is small, it is easy to turn the handle 1 quickly, so that vibration of 200 Hz or more can be obtained even if the number of teeth is somewhat small.

  (E) In the rotation transmission mechanism 20, the number of teeth of the drive gear 31 is 1.33 times or more and 500 or less of the lower limit set in each claim when the rotation radius R1 is 75 mm or more and 120 mm or less. In this case, since the turning radius is large, there may occur a case where the handle can be rotated only about 1.5 turns per minute. Even in such a case, vibrations of 200 Hz or less to 300 Hz or less can be avoided.

  (F) The spinning reel rotor driving mechanism 105 is a mechanism for moving the spool 104 back and forth by the rotation of the spinning reel handle 101. The rotor drive mechanism 105 includes a pinion gear 112 and a drive gear 111. The pinion gear 112 and the spool shaft 115 can be rotated. The drive gear can rotate integrally with the handle 101, meshes with the pinion gear 112, and has a number of teeth of 50 or more and 667 or less.

  In FIG. 2 described above, when the vibration A and vibration B of the spinning reel are seen, it can be seen that when the vibration exceeds 100 Hz, the amplitude that a person feels as the limit of good / bad gradually increases. For this reason, if the number of teeth is 50 or more, if the handle is rotated twice or more per minute as described above, vibration of 100 Hz or more is obtained. Therefore, it is possible to suppress the feeling of gear noise when the spinning reel is wound up, and to improve the rotation feeling without increasing the shape accuracy of the face gear teeth 111c stably.

  (G) In the rotor drive mechanism 105, the number of teeth of the drive gear 111 is set according to the mounting distance L1 from the mounting seat 102d which is the fishing rod mounting position of the spinning reel to the rotation center C5 of the handle 101. Thereby, when the mounting distance L1 from the fishing rod mounting position to the rotation center C5 of the handle 102 is large, the amplitude of vibration increases. For this reason, the vibration of a frequency can be generated by changing the number of teeth according to these.

  (H) In the rotor drive mechanism 105, the number of teeth of the drive gear 111 is 60 or more and 667 or less when the mounting distance is less than 85 mm. In the case of the spinning reel, the distance from the fishing rod mounting position to the rotation center C5 of the handle 101 is larger than that of the dual-bearing reel. Therefore, a sensory test as shown in FIGS. 3 and 4 was performed. In FIG. 3, the number of teeth of the drive gear 31 was changed to 10 stages, and a sensory test for ranking the rotational feeling in each stage was performed by 6 subjects A to F. The graph which shows the average value of this result is shown in FIG. In FIG. 4, the vertical axis represents the ranking and the horizontal axis represents the frequency. The distance L1 from the fishing rod mounting position to the rotation center C5 of the handle 1 is less than 85 mm. In this case, as shown in FIG. 4, it was found that the average ranking of the rotational feeling was worst at around 100 Hz to 120 Hz. For this reason, in such a condition, when the number of teeth is 60 or less, vibration in the vicinity of 100 Hz to 120 Hz cannot be avoided, so the number of teeth needs to be 60 or more. Here, since the number of teeth is set to 60 or more, vibration from 100 Hz to 120 Hz is hardly generated, and the sense of gear noise can be suppressed.

  (I) In the rotor drive mechanism 105, the number of teeth of the drive gear 31 is set according to the rotation radius C5 of the handle. In this case, even when the turning radius C5 of the handle 101 is large and it is difficult to turn the handle 101 quickly, the number of teeth can be increased to obtain a frequency of 100 Hz to 120 Hz or more, and the sense of gear noise can be suppressed.

  (J) In the rotor drive mechanism 105, the number of teeth of the drive gear 111 is 66 or more and 667 or less when the rotation radius C5 is 85 mm or more. In this case, since the rotation radius C5 is large, the rotation speed is about 1.5 rotations per rotation. For this reason, by making the number of teeth of the drive gear 111 1.33 times or more of 50, vibrations of 100 Hz to 120 Hz or less are less likely to occur, and the sense of gear noise can be suppressed.

2 Handle 4 Fishing rod mounting leg 15 Spool 15b Flange 20 Rotation transmission mechanism 30 Handle shaft 31 Drive gear 31a Gear teeth 32 Pinion gear 101 Handle 101a Handle shaft 104 Spool 111 Drive gear 111a Disk portion 111c Face gear teeth 112 Pinion gear 112c Lotus tooth

Claims (10)

A fishing reel rotation transmission mechanism that operates a spool by rotation of a fishing reel handle,
The fishing reel is a dual-bearing reel,
A pinion gear rotatable around the axis of the spool;
A drive gear that is integrally rotatable with the handle, meshes with the pinion gear, and has a number of teeth of 100 to 500;
Rotation transmission mechanism for fishing reel with   The rotation transmission mechanism of the fishing reel according to claim 1, wherein the number of teeth of the drive gear is set according to a maximum diameter of a flange of the spool.   3. The rotation transmission mechanism of a fishing reel according to claim 2, wherein the number of teeth of the drive gear is 150 to 500 when the maximum diameter of the flange of the spool is 45 mm or less.   The rotation transmission mechanism of the fishing reel according to claim 1, wherein the number of teeth of the drive gear is set according to a rotation radius of the handle.   5. The drive gear according to claim 4, wherein the number of teeth of the drive gear is 1.33 times or more and 500 or less of a lower limit set in each claim when the turning radius of the handle is 75 mm or more and 120 mm or less. Fishing reel rotation transmission mechanism. A fishing reel rotation transmission mechanism that operates a spool by rotation of a fishing reel handle,
The fishing reel is a spinning reel;
A pinion gear rotatable around the axis of the spool;
A drive gear capable of rotating integrally with the handle, meshing with the pinion gear and having a number of teeth of 50 to 667;
Rotation transmission mechanism for fishing reel with   The rotation transmission mechanism of the fishing reel according to claim 6, wherein the number of teeth of the drive gear is set according to a mounting distance from a fishing rod mounting position of the spinning reel to a rotation center of the handle.   The rotation transmission mechanism of the fishing reel according to claim 7, wherein the number of teeth of the drive gear is 60 or more and 667 or less when the mounting distance is less than 85 mm.   The rotation transmission mechanism of the fishing reel according to claim 6, wherein the number of teeth of the drive gear is set according to a rotation radius of the handle.   10. The fishing reel according to claim 9, wherein the number of teeth of the drive gear is 1.33 times or more and 667 or less of a lower limit value set in each claim when the turning radius is 50 mm or more and 85 mm or less. Rotation transmission mechanism.

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