JP7436173B2 - Fishing reel and its driving gear - Google Patents

Description

The present invention relates to a fishing reel and its drive gear, and particularly relates to a fishing reel having features in a drive gear that constitutes a drive gear that is rotationally driven by a reeling operation of a handle, and a pinion gear that meshes with the drive gear. .

Usually, 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 is rotatably supported on the reel body, and a power transmission path for the take-up drive mechanism that is connected to the reel. A clutch mechanism that switches between a power transmission state in which the fishing line can be wound onto the spool by external operation of a switching member attached to the main body and a power cut-off state in which the spool is in a free rotation state and the fishing line can be released. There is.

The winding drive mechanism includes a drive gear provided on the handle shaft and a pinion gear that meshes with the drive gear, and generally a helical gear is used to improve rotational performance and strength. ing. Further, the clutch mechanism is capable of engaging and disengaging the engaging part on the pinion gear side in the axial direction with the engaging part on the spool shaft side (spool side) by an external operation while the pinion gear remains in the engaged state with the drive gear. This constitutes a special power transmission path unique to fishing reels that switches between a power transmission state and a power cutoff state. Furthermore, during the winding operation where loads are applied during actual fishing, the clutch engagement part on the pinion gear side becomes detached from the clutch engagement part on the spool side, making it impossible to wind up, and the meshing condition with the drive gear is prevented from deteriorating. The inclination direction of the helical gear is set so that a biasing force acts in a direction that engages the pinion gear with the spool shaft.

In addition, in the case of a pinion gear, the direction of inclination of a helical gear determines the helix angle with respect to the axial direction, and this helix angle has a large effect on the ease of disengaging the clutch, its strength, and the rotational feeling. There is. In other words, with conventional double-bearing type reels, the optimum helix angle is selected according to the gear system of the take-up drive mechanism, taking into account the fishing method and the target fish, etc., and if the helix angle is small, The clutch becomes easier to disengage, but the rotational feeling deteriorates, and if the torsion angle is large, the clutch mechanism becomes difficult to disengage, but the rotational feeling improves. It has interlocking characteristics.

When using a double-bearing reel that allows casting operations during actual fishing, the clutch mechanism that switches the spool rotatably supported on the reel body between a power transmission state (clutch ON) and a power cutoff state (clutch OFF) is equipped with a load winding. It is possible to maintain stable winding operation by maintaining the power transmission state even when reeling (clutch winding operability), and when adjusting the length of the hook hanging from the rod tip or switching operation to release the hook to a predetermined point, etc. The OFF operation can be easily performed (clutch release operability), prevents unnecessary sinking of the device from the water surface when the device lands on the water during casting operation, and quickly shifts to the reeling state to efficiently lure the device. It is required to be equipped with various functions related to clutches, such as what it can do (clutch engagement operability).

During actual fishing operations, the clutch mechanism may be switched to the power cut-off state (clutch OFF) while tension is applied to the fishing line, and the feeding state of the fishing line may be controlled by a summing operation. In this case, the clutch OFF operation becomes difficult to perform quickly and easily due to the influence of the biasing force that acts when the helical gears mesh (the pinion gear is biased toward the spool side).
Therefore, in order to quickly turn off the clutch even when a strong load is applied to the clutch mechanism (strong tension is applied to the fishing line), the wall of the engagement groove of the pinion gear that engages with the engagement pin of the spool shaft is A device in which the helical gear is inclined in the same direction as that of the helical gear is known from Patent Document 1.

Patent No. 6407578

The double-bearing reel disclosed in Patent Document 1 focuses on the wall of the engagement groove of the pinion gear, and makes the wall part of the engagement groove of the pinion gear align in the same direction as the twisting direction of the pinion gear. Machining is not easy because it is necessary to precisely align the directionality of the wall of the engagement groove and the tooth surface. In other words, while the tooth surface is cut with an involute milling cutter (hob), the walls of the engagement groove need to be machined using a separate cutting tool, which complicates the machining process and requires high-precision machining. This is difficult to achieve and increases manufacturing costs.

Furthermore, in terms of clutch functionality, while the clutch becomes easier to disengage (clutch disengagement operability), the clutch engagement part tends to separate due to the influence of the inclined wall of the pinion gear during winding operations when tension is applied to the fishing line. As a result, the meshing state with the drive gear is unstable and the winding rotation performance (clutch winding operability) is poor. In addition, if you try to quickly shift to the winding state by rotating the handle while the spool is rotating in the direction of feeding out when landing on water during a casting operation to prevent unnecessary sinking of the device, the spool shaft side The engagement pin comes into contact with the inclined wall of the engagement groove of the pinion gear and tends to escape outward, which can cause problems such as the inability to reliably shift the clutch to the winding state (clutch engagement operation) during actual fishing. .

The present invention has been made by focusing on the above-mentioned problems, and it is possible to simplify gear manufacturing and optimize fishing operations (clutch winding operability, clutch disengagement operability, clutch engagement operability) by making full use of the clutch mechanism. ), and to provide a fishing reel and its driving gear.

As mentioned above, the clutch mechanism of a fishing reel involves a drive gear and a pinion gear that mesh with each other. It has the special feature of moving in the axial direction with sliding resistance acting on the tooth surface. The present invention focuses on the special characteristics of the clutch mechanism unique to fishing reels, and instead of separately machining the tooth surface and the engagement groove of the pinion gear as in the above-mentioned prior art, To provide a meshing system constituting an optimal 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 provides a drive gear that rotates when a handle is rotated, a pinion gear that is rotatably engaged with and disengaged from a spool that is rotatably supported on a reel body, and a pinion gear that meshes with the drive gear. In the fishing reel, the torsion angle β between the drive gear and the pinion gear is set to 5°. The present invention is characterized in that the power transmission of the clutch mechanism is ON/OFF controlled under 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 configured as described above, the torsion angle β of the pinion gear is set to an optimum angle depending on the application, taking into consideration rotational feeling and ease of clutch disengagement. In this meshing relationship between the drive gear and pinion gear, by setting the pressure angle α to 3°≦α≦16°, the action that acts perpendicularly to the tooth surfaces of both gears in the meshing state can be achieved. The force in the linear direction can be reduced, which also reduces the resistance force when the pinion gear slides in the axial direction, making it easier to disengage the clutch mechanism and stabilizing the clutch engagement state, resulting in good winding performance. It becomes possible to maintain In addition, with such a configuration, it is possible to form a pressure angle that effectively suppresses sliding resistance as described above during cutting of the hob that forms the tooth surface, so the gear that constitutes the clutch mechanism can be easily manufactured. Cost reduction is also possible.

According to the present invention, there is provided a fishing reel in which gear manufacturing is simplified and a series of fishing operability of a clutch mechanism including a clutch winding operation, a clutch disengaging operation, and a clutch engaging operation are optimized; A driving gear is obtained.

FIG. 1 is a plan view showing an embodiment of a fishing reel (double bearing reel) according to the present invention. FIG. 2 is a diagram showing the main parts of the reel drive mechanism of the fishing reel shown in FIG. 1 (clutch ON state). FIG. 2 is a diagram showing the main parts of the reel drive mechanism of the fishing reel shown in FIG. 1 (clutch OFF state). FIG. 3 is an enlarged view of a drive gear incorporated in the take-up drive mechanism. An enlarged view of the pinion gear that meshes with the drive gear. A schematic diagram showing a state in which gears mesh with each other to transmit power.

First, with reference to FIGS. 1 to 3, a fishing reel according to an embodiment of the present invention will be described by exemplifying a double bearing reel.
The present invention includes double-bearing reels that are suitable for various fishing methods such as boat fishing and lure fishing, but the double-bearing reel shown in the figure is suitable for use in lure fishing. Examples of the types that can be used are shown below.

As shown in FIGS. 1 to 3, the reel body 1 of the double-bearing reel has left and right frames 2a and 2b, and left and right frames that are attached to these left and right frames 2a and 2b with a predetermined space apart through sealing materials, respectively. It includes side plates 3a and 3b. The left and right frames 2a, 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 means of reel legs (not shown) provided on the lower columns.

A spool shaft 5 is rotatably supported between the left and right frames 2a, 2b (left and right side plates 3a, 3b) via bearings 4A, 4B, and a spool 6 is attached to this spool shaft 5. The spool 6 has a fishing line winding trunk 6a around which the fishing line is wound, and flanges 6b, 6b on both left and right sides. It is wound around the rotation drum part 6a.

The spool 6 is configured to be rotated by rotating a 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 a 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 is used for winding the fishing line by a one-way clutch (not shown) interposed between the right side plate 3b and the right side plate 3b. It is configured to be rotatable only in this direction.

A drive gear 11 is provided between the right frame 2b and the right side plate 3b, and is rotatably supported by the handle shaft 7 to transmit the rotational motion of the handle 10 to the spool shaft 5 side. A known drag mechanism 12 is housed therein, which engages with this drive gear 11 which is rotated by a rotation operation of 10 to apply a predetermined drag force to the spool 6. The drag mechanism 12 applies a predetermined drag force to the spool 6 when the fishing line is let out 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 against the drive gear 11 is adjusted by rotating an operating member 13 disposed at the end of the handle shaft 7. Constructed to adjust force.

A pinion gear 21 (teeth 21A of the pinion gear 21), which constitutes a part of the clutch mechanism 20 and serves as a power transmission member, meshes with the teeth 11A of the drive gear 11. This pinion gear 21 is a member that transmits the rotation of the drive gear 11 to the spool 6 (spool shaft 5), and is formed with a center hole 21a penetrating in the axial direction. A support shaft (which may be a support shaft that comes into contact with the end surface of the spool shaft 5) passes through the shaft.

In the present embodiment, the right end side of the spool shaft 5 includes a large diameter portion 5A, a small diameter portion 5B continuous to the large diameter portion 5A, and a shaft portion 5C extending from the small diameter portion 5B (or contacting the end surface of the small diameter portion 5B). The shaft portion 5C is inserted into the center hole 21a of the pinion gear 21 as described above. Further, the spool shaft 5 is a shaft provided inside an adjustment member 60 (dial operating body) whose 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). Movement in the axial direction is regulated by abutting against the direction regulating portion 62 . This adjustment member 60 constitutes an operation member of a spool braking mechanism 70 that applies a braking force to the free rotation of the spool. Pressure is applied as a braking force.

A circumferential groove 21b is formed in a part of the pinion gear 21 along the circumferential direction, and a clutch member 23 forming the clutch mechanism 20 is engaged with the circumferential groove 21b. As is well known, the clutch member 23 resists the biasing force of the biasing member 90 by pushing down the clutch operating member 24 (operating from the clutch ON state to the clutch OFF state), which is disposed between the left and right frames 2a and 2b. The pinion gear 21 is driven rightward in the figure, thereby moving the pinion gear 21 to the right along the spool shaft 5.

In this case, both sides of the pinion gear 21 (both sides of the tooth 21A that meshes with the drive gear 11 on the spool 6 side and on the side plate 3b side) are installed in the reel body 1 (right frame 2b, right side plate 3b, see FIG. 1). It is supported by bearings 24A, 24B via a collar C (resin material), and is movably in the axial direction and rotatably in contact with the inner peripheral surface of the inner ring of the bearings 24A, 24B. That is, the pinion gear 21 has a side connected to the spool 6 supported by a first bearing 24A, and a side opposite to the side connected to the spool 6 supported by a second bearing 24B. Note that the collar C may be deleted and both sides of the pinion gear 21 may be directly supported by the bearings 24A and 24B.

The left end of the pinion gear 21 on the spool 6 side is provided with a recess 25a that can be engaged with and detached from the engagement pins 5b, 5b provided on the right end (small diameter portion 5B) of the spool shaft 5. In this case, the engagement pins 5b, 5b are provided to protrude in the diametrical direction of the spool shaft 5, and the recess 25a is formed along the diametrical direction on the end surface of the pinion gear so that each engagement pin 5b fits therein. (See Figure 5). As shown in FIG. 2, the state in which the engaging protrusions 5b, 5b of the spool shaft 5 are engaged with the recess 25a is the clutch ON state, and as shown in FIG. 23), the state in which the pinion gear 21 is moved toward the right side in the figure and the engagement pins 5b, 5b are disengaged from the recess 25a (the state in which both are disengaged) is the clutch OFF state.

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 operated to return or when the handle 10 is operated to wind 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 includes a guide tube 51 and a rotatable roller rotatably supported within the guide tube 51. The fishing rod includes a worm shaft that does not have a worm shaft, an engaging member 53 having a pin (not shown) that engages with the worm shaft, and a fishing line guide section 54 attached to the engaging member 53. Further, a gear (not shown) is attached to the right 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 rotated with the clutch ON as shown in FIGS. 1 and 2, the rotational movement is transmitted to the level wind device side and It is transmitted to the spool side.
That is, the signal is transmitted from the handle shaft 7 via the drag mechanism 12 to the drive gear 11 and the gear, and then via the gear to the worm shaft 52 of the level wind device 50, and this 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 line is evenly wound around the spool 6 via the fishing line guide portion 54 of the engaging member 53. It is passed around.

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

When the clutch operating member 24 is operated to move from the clutch ON state (fishline winding state) shown in FIGS. 1 and 2 (operated from the clutch ON state to the clutch OFF state), the clutch member 23 is moved. The pinion gear 21 is driven toward the right side in the figure against the biasing force of the biasing member 90, and thereby the engagement protrusion of the spool shaft 5 is moved as shown in FIG. The engagement of the recessed portion 25a of the pinion gear 21 with the portions 5b, 5b is released. Therefore, the spool 6 becomes in a freely rotatable state (fishing line payout 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, so that the tooth surface 21F of the pinion gear 21 (see FIG. 5) and the tooth surface 11F of the drive gear 11 (see FIG. 4) slides while in contact.

Thereafter, 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). Ru. As a result, the end face of the pinion gear 21 comes into contact with the engagement protrusions 5b, 5b of the spool shaft 5 while rotating, and the engagement protrusions 5b, 5b of the spool shaft 5 fit into the recess 25a of the pinion gear 21, causing the wall The fishing line winding state is brought into contact with the portion 25e in the rotational direction (fishline 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. Note that 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 while remaining in contact.

The drive gear 11 and pinion gear 21 (also collectively referred to as drive gears) described above are always in mesh with each other, and in a fishing reel, both gears remain in mesh when the clutch is turned ON/OFF. It has a special feature in that the tooth surfaces slide against each other. In addition, when power is transmitted by meshing the gears of a fishing reel, in order to ensure that the meshing is as smooth as possible and does not generate noise when the handle is retracted, helical teeth are used to increase the meshing ratio. 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 twisted. Also, as shown in FIG. 5, it is formed to be twisted.

Here, the torsion angle (β) of the drive gear in the present invention will be explained.
The torsion angle, explained with reference to the pinion gear 21 in FIG. 5, is an angle that specifies how much the teeth (tooth traces) 21e are twisted with respect to the axis X of the gear, and if the torsion angle is 0°, This is the meshing relationship between spur gears. As described above, in a fishing reel, the meshing relationship of the drive gear is set to have a certain degree of helix angle so that the meshing is smooth and no noise is generated.

In the drive gear incorporated in the fishing reel according to the present invention, the helix angle (β) is set to 5°≦β≦25°.
The torsion angle becomes a factor that hinders the sliding when the clutch operating member 24 is pushed down and the pinion gear 21 is slid toward the right side plate against the biasing force of the biasing member 90. For example, the pinion gear 21 can easily slide. However, if the helix angle is set too small, the smoothness of the rotation will decrease, making noise more likely to occur, and furthermore, it will become easier to slide, causing the problem of easy disengagement from the spool side. . Specifically, in the power transmission state (clutch ON state), when the pressing force on the spool side by the tooth surface of the gear becomes weak and a strong load is applied to the fishing line, the pinion gear 21 slides and becomes disconnected from the spool. Problems arise such as the clutch becoming easily disengaged and erroneously returning even when the clutch is OFF.

The lower limit of the twist angle is set to 5° or more, which is such that the above-mentioned problems do not occur significantly (no inconvenience occurs during use). Furthermore, if the torsion angle is set large, smoothness will be improved, noise will be reduced, and pinion gear malfunctions can be prevented. However, if the torsion angle is set too large, the clutch operating member 24 will be It becomes difficult to press down. Specifically, when the angle is 20 degrees or more, it tends to be difficult to press down, and when it exceeds 25 degrees, there is considerable resistance to the downward operation, so the upper limit of the twist angle is 25 degrees. It is preferable to set it to .
In this case, the small casting reel that is held and held together with the fishing rod is used in such a way that the clutch ON/OFF operation, casting operation, clutch ON operation, and handle rewinding operation are frequently repeated during actual fishing. Therefore, it is desirable to be able to perform rework operations smoothly and not get tired even if such operations are repeated for a long time. That is, in this type of fishing reel, the upper limit of the helix angle is preferably set to 20 degrees, preferably 18 degrees.

In fact, when examining various commercially available double-bearing reels, the torsion angle of the drive gear differs depending on the application, but it is generally set within the range of 5°≦β≦20°. In other words, for jigging and boat fishing, the noise when winding the fishing line is not a big concern, and smooth rotation performance is not so required, so the helix angle is set to a relatively small angle within the above range. In a casting reel using a lure or the like, the helix angle is set to a relatively large angle within the above-mentioned range because frequent turning operations and delicate winding operations are performed.

As mentioned above, in the case of small reels, especially reels used for lure casting, it is considered preferable to set the helix angle to a certain degree, but if it is set too large, strong tension will be applied to the fishing line. In this case, the clutch mechanism cannot be turned off quickly.
In the present invention, even under such circumstances, the pressure angle of the drive gear is adjusted so that the clutch disengagement operation can be performed smoothly, and furthermore, the clutch engagement operation and clutch winding operation can be performed smoothly without any problems. I'm paying attention.

Here, the pressure angle (α) of the drive gear incorporated in the fishing reel will be explained with reference to the schematic diagram of FIG. 6.
The meshing teeth 11A and 21A of the drive gear 11 and pinion gear 21 are formed with an involute tooth profile. In the figure, if 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 calculated by assuming that the thread is wound around the base circle and the thread is in tension. It is defined by the curve drawn by the tip when solved. In addition, the angle α formed by the common tangent L of each base circle of both gears and the common tangent L1 at the contact point (pitch point P) of the reference circle of both gears (circles indicated by radii R11a and R21a) is the pressure angle. .

That is, the pressure angle is defined in the direction perpendicular to the tooth flank in the involute tooth profile, and the force Fn acting in this direction becomes the force for transmitting power (force pushing the tooth flank; normal force on each tooth flank). In this case, if the tooth flanks are formed so that the pressure angle α is small, the base circles R11 and R21 of each gear will become larger. Therefore, when considering force transmission with the same torque, the normal force Fn on each tooth flank becomes small (by setting the pressure angle small, the normal force Fn on each tooth surface can be made small).

As described above, due to the action of the clutch mechanism, the pinion gear 21 slides in the axial direction while being engaged with the drive gear, but since this sliding direction is perpendicular to the paper surface of FIG. If the normal force Fn acting on the tooth surface becomes smaller, the pinion gear 21 will slide more easily. 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 becomes easier to disengage.

Currently, the standard reference rack tooth profile (JIS B 1701-1 2012; standard involute tooth profile) is used for the tool (hob) that forms the involute tooth surface of the gear incorporated in a fishing reel, and the pressure angle α is A type with an angle of 20° has been adopted. In this case, even if such a tool is used, it is possible to form a gear with a pressure angle in the range of 17° to 19° depending on the amount of dislocation. Regarding the pressure angle α, as mentioned above, it is considered advantageous to make it smaller than the conventional general angle of 20°, considering the operability of the clutch mechanism, etc., but the present inventors An evaluation test (sensory test) was conducted to determine how small the size should be to improve operability.

The evaluation test was conducted by five testers, and a small double-shaft reel for lure fishing was used in order to comprehensively evaluate the series of operations including clutch release operability, clutch engagement operability, and clutch winding operability. So I went. That is, in lure fishing, the above-mentioned operations are frequently repeated, and subtle differences are easy to understand in the reeling operation, so among the double-bearing reels, a small casting reel was used for evaluation. For the evaluation, we prepared multiple double-bearing reels of the same size with different settings for the torsion angle and pressure angle of the drive gear built into the reel body, and each tester performed the above series of operations on each reel many times. Comprehensive evaluation was performed repeatedly. Specifically, the five testers evaluated the reels they used on three levels: 3 points if they felt it was very good, 1 point if they felt it was good, and 0 points if it was the same as before. When the total score was 12 points or more, it was evaluated as ◎, when it was 8 points or more, it was evaluated as ○, when it was 4 points or more, it was △, and when it was 3 points or less, it was evaluated as ×.

In addition, the double-bearing reel used had an outer diameter D of 34 mm of the flange portion 6b shown in FIG. The rod has a center-to-center distance Ld of 22.6 mm, can be gripped and held together with a fishing rod, and has a gear ratio of drive gears 11 and 21 of 6.3. In addition, the rotation radius of the handle 10 is 45 mm, and the recess 25a formed at the end of the pinion gear 21 into which the engagement pin 5b of the spool shaft can be engaged and detached has the engagement pin 5b. The wall portions 25e, 25e that engage and are subjected to a contact load in the rotational direction are formed to be parallel to the spool shaft (axis center X) in the axial direction (see FIGS. 2 and 5). Note that the end surface 25g of the recess 25a is formed into an inclined surface such that one edge side with respect to the wall portion 25e that abuts and engages in the rotational direction is lower than the other edge side, and the engagement pin 5b rotates. It is designed so that it can easily come into contact with the wall portion 25e of the pinion gear 21.

In the reel having the above configuration, the twist angles β are formed at 5°, 10°, 15°, 20°, and 25°, and the respective pressure angles α are formed at 14°, 16°, 18°, and 20°. We have prepared a model that incorporates the drive gear that was used. In this case, the pressure angle of 20° is a drive gear built into 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 there was much improvement between the pressure angle reel and the conventional 20° reel. When the angle was set as small as 16° and further as 14°, the overall evaluation of the tester as a whole tended to improve, so 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 degrees or less in the range where the torsion angle is 5 degrees≦β≦25 degrees, the series of operability described above is improved.

Further, as the pressure angle is reduced, the involute tooth surface becomes gradually steeper, causing the problem of undercut at the tooth root. For this reason, 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 lower limit of the pressure angle is the angle at which undercut does not occur when cutting the tooth surface, specifically 3 degrees. (preferably 5°) or more. That is, in the present invention, the pressure angle of the drive gear may be set within the range of 3°≦α≦16°.

Note that when the gear is rotationally driven, the normal force (surface pressure) Fn that acts on the tooth surface 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 on the dedendum side is reduced due to the undercut. That is, when the pressure angle is reduced in order to reduce the normal force, the tooth surface tends to gradually become steeper, and the root of the tooth is more likely to be ground and undercut, reducing the strength of the gear. Particularly in a fishing reel in which the clutch mechanism is continuously turned on and off by sliding gears in mesh with each other, a decrease in the strength of the gears makes it impossible to stably maintain good clutch performance during actual fishing. Therefore, we identify the allowable surface pressure (maximum surface pressure) for the drive gear, and analyze the strength of the gear with respect to the relationship between the helix angle (β) and pressure angle (α) for each surface pressure. Using analysis software, we also analyzed the allowable pressure angle for each torsion angle that can withstand each surface pressure.
In this analysis, when a constant surface pressure acts on the tooth surface of the drive gear, the surface pressure can be tolerated for each helix angle of 5°, 10°, 15°, 20°, 25°, and 30°. The minimum and maximum values of the pressure angle were determined. In addition, for the driving gears that mesh with each other, the center-to-center distance 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, the case where the surface pressure is 800 MPa corresponds to the case where a material with relatively high strength and high yield strength is used as the drive gear. Considering such materials, the minimum value of the pressure angle can be set at 6°. In other words, if the pressure angle is set within the range of 6°≦α≦16°, and a material with high yield strength (400 to 600 MPa) is used, the strength of the tooth can be maintained sufficiently even if the pressure angle is formed at 6°. is possible. Note that the table also analyzes the case where the maximum surface pressure is 450 MPa, but this corresponds to the case where a material with low yield strength is used as the drive gear. Even when the drive gear is formed of such a material, the strength of the teeth can be maintained by setting the pressure angle to 11° or more. In other words, if the pressure angle is set within the range of 11°≦α≦16°, it is possible to maintain sufficient tooth strength even if the drive gear is made of a material with low yield strength. It is.

As described above, in the meshing system of the drive gear 11 and pinion gear 21, the torsion 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 11°≦α≦16°, the ON/OFF operation of the clutch can be performed smoothly during actual fishing. This makes it possible to quickly and easily turn off the clutch even when tension is applied to the fishing line. In other words, it is possible to realize optimal fishing operations (clutch winding operability, clutch disengagement operability, clutch engagement operability) making full use of the clutch mechanism.

In addition, a wall portion formed at the end of the pinion gear 21, which engages an engagement pin provided on the spool spindle and abuts and engages in the rotational direction, is formed parallel to the axial direction of the spool spindle. By doing so, the meshing state between the pinion gear and the drive gear is stabilized, so that the winding rotation performance (clutch engagement operability and clutch winding operability) can be improved. In this case, unlike the prior art, there is no need to perform precise machining such as making the wall of the engagement groove of the pinion gear that engages with the engagement pin of the spool shaft in the direction of the helical tooth inclination. , it is possible to easily turn off the clutch by simply forming the tooth surface (cutting to achieve a predetermined pressure angle), so the machining process does not become complicated and high-precision machining is possible. Since the manufacturing cost is not required, the manufacturing cost does not increase.

Fishing reels incorporating the drive gear (meshing system) as described above can be applied to various forms of double-bearing reels and single-bearing reels, but they cannot be applied to small reels such as lure fishing. It is more effective. Specifically, in a small fishing reel in which the outer diameter D of both flange portions 6b of the spool 6 is set to 20 mm to 50 mm, the center-to-center distance between the axis of the drive gear and the axis of the pinion gear is It is preferable to apply the present invention to a small fishing reel whose diameter is set to 15 mm to 30 mm, or a small reel whose handle has a rotation radius set to 30 mm to 80 mm. That is, when performing frequent rewinding operations and delicate winding operations, it becomes possible to repeatedly perform delicate winding operations without getting tired.

In addition, by making it possible to drive the spool 6 for winding with the tooth ratio of the drive gear 11 and pinion gear 21 (gear ratio is 1:6 or more) so that the spool 6 rotates six times or more with one rotation of the handle, During casting operations, when the spool is rotating in the payout direction when landing on the water, the handle can be rotated to quickly shift to the winding state, preventing unnecessary sinking of the bait and quickly recovering the bait. It becomes possible to do so. Even in such cases, the engagement pin of the spool shaft can be reliably engaged with the engagement groove of the pinion gear, so the clutch can be reliably shifted to the winding state without any trouble and the spool can be rotated quickly. It becomes possible to do so.

Although the embodiments of the present invention have been described above, the fishing reel according to the present invention can be applied to a single-bearing reel as well as a double-bearing reel.

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

Claims (2)

A drive gear that rotates when a handle is rotated, a pinion gear that rotatably engages and disengages from a spool that is rotatably supported on a reel body, and the pinion gear that is meshed with the drive gear and is slid by an external operation. A fishing reel equipped with a clutch mechanism that switches the spool between a power transmission state and a power cutoff state,
The drive gear and pinion gear are made of a material with a yield strength of 400 to 600 MPa, and are meshed with a helix angle β of 5°≦β≦25° and a pressure angle α of 6° ≦α≦16°. ON/OFF control of power transmission of the clutch mechanism under conditions ;
A wall portion is formed at an end of the pinion gear in parallel to the axial direction of the spool support shaft, with which an engagement pin provided on the spool support shaft abuts and engages in the rotational direction,
The spool is rotatably supported between the side plates of the reel body via a support shaft, and has flanges formed on both sides of the bobbin trunk around which the fishing line is wound.
A fishing reel characterized in that the outer diameters of both flanges are set to 20 mm to 50 mm . 2. The fishing reel according to claim 1, wherein the spool is wound and driven with a tooth ratio of a drive gear and a pinion gear that rotate at least 6 times per rotation of the handle.