Electric fishing reel

Abstract

To increase a degree of freedom of a component layout and prevent an increase in size of a reel body.SOLUTION: A clutch mechanism 20 has a clutch actuation member 23 rotated by an operation of a clutch lever 21 and brought into a driving force cut-off state. A return mechanism 40 for returning the clutch mechanism 20 brought into the driving force cut-off state to a driving force transmission state includes: a gear 41 for return provided on a motor shaft of an electric motor 6; a rotation body 42 for clutch return for meshing with the gear 41 for return and rotating; and a kick member 43 rotatably supported by the clutch actuation member 23, engaged with or disengaged from the rotation body 42 for clutch return by rotating in interlock with the rotation of the clutch actuation member 23, and returning the clutch actuation member 23 brought into the driving force cut-off state to the driving force transmission state. The rotation body 42 for clutch return and the kick member 43 are disposed between a spool shaft and the motor shaft.SELECTED DRAWING: Figure 3A

Description

Technical Field

[0001] The present invention relates to an electric fishing reel.

Background Art

[0002] Conventionally, as an electric fishing reel, for example, the one disclosed in Patent Document 1 is known. In the electric fishing reel of Patent Document 1, a clutch mechanism for switching the power transmission state to the spool is provided in the frame of the reel body. The clutch mechanism includes an operation lever, and is configured to be switched from the clutch-on position in the driving force transmission state to the clutch-off position in the driving force cutoff state by operating this operation lever. Further, the electric fishing reel includes a return mechanism that uses the driving force of an electric motor to return the clutch mechanism in the driving force cutoff state to the driving force transmission state.

[0003] The clutch mechanism includes a slide plate that moves from the clutch-on position to the clutch-off position by operating the operation lever, and a contact piece that protrudes from the slide plate. On the other hand, the return mechanism includes a return gear driven by the reverse rotation of the electric motor, and a protrusion that contacts the contact piece of the slide plate.

[0004] In such a configuration, when the operation lever is operated to switch the clutch mechanism to the driving force cutoff state, the slide plate slides from the clutch-on position to the clutch-off position, and in the process of this movement, the contact piece enters a position where it contacts the protrusion of the return gear. When the electric motor is reversely rotated in such a driving force cutoff state, the protrusion of the clutch return gear contacts the contact piece of the slide plate, and the slide plate is pushed up by the contact force. As a result, the slide plate is returned from the clutch-off position to the clutch-on position, and the clutch mechanism is returned to the driving force transmission state.

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0006] Patent Document 1 has a structure in which the slide plate slides linearly from the clutch-on position to the clutch-off position, and moreover, the contact piece of the slide plate directly contacts the protrusion of the clutch return gear. For this reason, it is necessary to widely secure the slide space of the slide plate in the frame of the reel body, and there is a risk that the degree of freedom in the layout of the components will be reduced. In particular, since an electric fishing reel has more components than a fishing reel without an electric motor, there is a risk that the reel body will be enlarged by securing the slide space of the slide plate.

[0007] The present invention was created to solve such problems, and an object thereof is to provide an electric fishing reel that can increase the degree of freedom in the layout of components and prevent the enlargement of the reel body.

Means for Solving the Problems

[0008] The electric fishing reel of the present invention that solves such problems is provided between the frames of the reel body, and includes a spool that is provided between the frames of the reel body and rotates at least receiving the driving force of an electric motor, and a clutch mechanism that is provided on one side of the frame to which a handle shaft is attached and switches the spool between a driving force transmission state and a driving force cutoff state, and a return mechanism that is provided on one side of the frame and returns the clutch mechanism in the driving force cutoff state to the driving force transmission state. The clutch mechanism has a clutch operating member that rotates by the operation of a clutch lever and is in a driving force cutoff state. The return mechanism includes a return gear provided on the motor shaft of the electric motor, a rotation body for clutch return (gear B) that meshes with the return gear and rotates, and a kick member that is rotatably supported by the clutch operating member and engages and disengages with the rotation body for clutch return by rotating in conjunction with the rotation of the clutch operating member, and returns the clutch operating member in the driving force cutoff state to the driving force transmission state. The rotation body for clutch return and the kick member are arranged between the spool shaft that supports the spool and the motor shaft. The rotary body for clutch return includes an engagement claw that engages with the kick member and a biasing member. The engagement claw is capable of changing its position around the axis of the rotary body for clutch return, and is configured to be able to take a first position moved in the rotational direction of the rotary body for clutch return and a second position moved in the opposite direction thereto, and is biased from the second position toward the first position by the biasing force of the biasing member.

[0009] According to this electric fishing reel, since the kick member is rotatably supported by the frame and engages and disengages with the rotation body for clutch return by rotating in conjunction with the clutch operating member, compared with a configuration in which a return member engages and disengages by a linear sliding movement as in the prior art, the degree of freedom in the layout of the components can be increased, and an increase in the size of the reel body can be prevented. In addition, since the rotation body for clutch return and the kick member can be provided with high space efficiency between the spool shaft and the motor shaft, the degree of freedom in the layout of the components can be increased, and an increase in the size of the reel body can be prevented.

[0011] Also, against the biasing force of the biasing member, the engaging claw is movable in a direction opposite to the rotational direction of the rotary body for clutch return. Therefore, even when the kick member engages and interferes with the engaging claw and engages so as to push the engaging claw in a direction opposite to the rotational direction of the rotary body for clutch return, the engaging claw is pushed by the kick member and moves flexibly in the reverse direction. As a result, the engagement state between the kick member and the engaging claw is maintained well. Therefore, the clutch mechanism can be quickly returned from the driving force interruption state to the driving force transmission state, and the responsiveness of the return mechanism is excellent.

[0012] Also, since the engagement state is maintained well even when the kick member interferes with the engaging claw during engagement of the kick member, there is no need to manage the stop position of the engaging claw for the next return, and there is no need to provide a sensor for detecting the stop position of the engaging claw or control means for adjusting the position of the engaging claw. Therefore, it is possible to reduce the cost while preventing the enlargement of the reel body.

[0013] Moreover, it is preferable to provide a handle operation return mechanism for returning the clutch mechanism, which has been brought into the driving force interruption state by a rotational operation of the handle, to the driving force transmission state. In this case, it is preferable that the handle operation return mechanism includes a ratchet attached to the handle shaft and a handle interlocking kick member that engages with and disengages from the ratchet and returns the clutch operating member, which has been brought into the driving force interruption state, to the driving force transmission state.

[0014] With this configuration, since the clutch mechanism, which has been brought into the driving force interruption state by a rotational operation of the handle, can be returned to the driving force transmission state, a fishing electric reel with good usability and excellent fishing operability can be obtained.

[0015] Also, a drive control unit that drives and controls the electric motor in the forward rotation direction or the reverse rotation direction, a detection unit that detects that the clutch mechanism is in a driving force cutoff state, a calculation unit that calculates the rotational speed of the spool accompanying the payout of the fishing line and calculates the payout amount of the fishing line, a rotational speed determination unit that determines whether or not the rotational speed of the spool calculated by the calculation unit satisfies a predetermined condition, and a payout amount determination unit that determines whether or not the payout amount of the fishing line calculated by the calculation unit has reached a preset payout amount of the fishing line are preferably provided. In this case, when the detection unit detects that the clutch mechanism is in a driving force cutoff state and the rotational speed determination unit determines that the rotational speed of the spool satisfies a predetermined condition, or when the payout amount determination unit determines that the payout amount of the fishing line has reached a preset payout amount of the fishing line, it is preferable that the drive control unit drives and controls the electric motor in the reverse rotation direction and brings the engaging claw of the rotary body for clutch return into contact with the kick member.

[0016] In this configuration, when the clutch mechanism is in a driving force cutoff state and the rotational speed of the spool satisfies a predetermined condition, or when the payout amount of the fishing line has reached a preset payout amount of the fishing line, the clutch mechanism in the driving force cutoff state can be automatically restored to the driving force transmission state. Therefore, an electric fishing reel that is easy to use and excellent in fishing operation performance can be obtained.

Advantages of the Invention

[0017] According to the present invention, an electric fishing reel capable of preventing the enlargement and weight increase of the reel body can be obtained.

Brief Description of the Drawings

[0018]

Figure 1

Figure 2

Figure 3A

Figure 3B

Figure 4

Figure 5A

Figure 5B

Figure 5C

Figure 5D

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10

Figure 11A

Figure 11B

Figure 11C

Figure 11D

Figure 11E

Figure 12

Figure 13

Mode for Carrying Out the Invention

[0019] Hereinafter, embodiments of an electric fishing reel according to the present invention will be described with reference to the drawings. In the following description, when referring to "front-rear", "left-right", and "up-down", the directions shown in FIG. 1 are used as a reference.

[0020] As shown in FIG. 1, the electric fishing reel 100 has a reel body 1 including left and right frames 2, 2 and left and right side plates 3, 3 (only the right side plate is shown) disposed so as to cover the left and right frames 2, 2. A counter case 4 as a display means is arranged at the front part of the upper surface of the reel body 1. The counter case 4 has control means for controlling the operation of the electric motor 6 inside.

[0021] The left and right frames 2, 2 are parts forming the skeleton of the reel body 1 and are integrated left and right via columns. A reel leg 2a to be attached to a reel seat of a fishing rod (not shown) is provided on the lower column. The left and right frames 2, 2 are formed of a metal material such as an aluminum alloy or a magnesium alloy, for example. Between the left and right frames 2, 2, a spool 5 around which a fishing line is wound is rotatably supported. Also, in front of the spool 5, an electric motor 6 is supported by the left and right frames 2, 2.

[0022] The electric motor 6 is provided with a drive shaft (not shown) that extends toward the left and right frames 2, 2. A drive reduction mechanism that reduces the rotational driving force of the electric motor 6 and transmits it to the spool 5 side is connected to the drive shaft extending toward the left frame 2 side. Further, a return reduction mechanism 6a that reduces the rotational driving force of the electric motor 6 and transmits it to a second return mechanism 40 described later is connected to the drive shaft extending toward the right frame 2 side.

[0023] The left and right side plates 3, 3 are the parts (the parts that the angler's hand contacts) that are held or gripped by the angler's hand. The left and right side plates 3, 3 are integrally formed individually and are respectively attached to the left and right frames 2, 2. The right side plate 3 is provided with a handle shaft 7 to which a manual handle is attached. The spool 5 is rotationally driven in the fishing line winding direction via a driving force transmission mechanism by the driving force from the winding operation of the manual handle and the rotational driving force of the electric motor 6. The driving force transmission mechanism by the electric motor 6 is provided on the left frame 2 side.

[0024] As shown in FIGS. 2, 3A, and 3B, the right frame 2 is provided with a driving force transmission mechanism 10 that transmits the driving force of the manual handle to the spool 5, a clutch mechanism 20 that switches the spool 5 between a driving force transmission state and a driving force cutoff state, and a return mechanism that returns the clutch mechanism 20 in the driving force cutoff state to the driving force transmission state. Among these, the return mechanism includes a first return mechanism 30 that returns to the driving force transmission state using the rotational driving force of the handle (handle shaft 7), and a second return mechanism 40 that returns to the driving force transmission state using the rotational driving force of the electric motor 6. That is, the electric fishing reel 100 of the present embodiment is provided with two return mechanisms, manual and electric. Details of the first return mechanism 30 and the second return mechanism 40 will be described later.

[0025] As shown in Fig. 3A, the driving force transmission mechanism 10 includes a drive gear 11 supported by the steering shaft 7 and a pinion 12 meshing with the drive gear 11. The drive gear 11 rotates integrally with the steering shaft 7 and transmits the driving force generated by the rotational operation of the manual steering wheel to the pinion 12. The pinion 12 is provided on a pinion shaft (not shown) that is rotatably supported by the right side plate 3 via a bearing. The pinion shaft extends coaxially with a spool shaft (not shown). A yoke 24 (to be described later) of the clutch mechanism 20 is engaged with the pinion 12. The pinion 12 is configured to be axially movable along the pinion shaft by the action of the yoke 24 (to be described later).

[0026] The pinion 12 has a fitting portion that fits onto the spool shaft. When the pinion 12 is moved toward the spool 5 side by the yoke 24, the fitting portion fits onto the spool shaft, putting the mechanism in a state where the driving force of the drive gear 11 is transmitted to the spool shaft (spool 5) (driving force transmission state (fishing line winding possible state)). When the pinion 12 is moved toward the right side plate 3 side by the yoke 24, the fitting portion disengages from the spool shaft, putting the mechanism in a state where the driving force of the drive gear 11 is not transmitted to the spool shaft (spool 5) (driving force cutoff state (fishing line releasing possible state)).

[0027] The clutch mechanism 20 includes a clutch lever 21, a clutch frame 22, a clutch operating member 23, and a yoke 24. The clutch lever 21 is disposed between the rear ends of the left and right frames 2, 2 behind the spool 5 so that it can be operated while holding the spool 5. The clutch lever 21 is a member that switches the clutch mechanism 20 from the driving force transmission state to the driving force cutoff state by placing the thumb on it and pushing it downward.

[0028] The clutch frame 22 is a metal member that supports the clutch lever 21. The clutch frame 22 is fitted into a fitting recess 23b (see FIG. 4) formed on the right side surface of the clutch operating member 23 and is integrally attached to the clutch operating member 23. An arm portion 23a for supporting the clutch lever 21 is provided at the rear end portion of the clutch frame 22. As shown in FIG. 3A, the arm portion 23a is movable in the vertical direction along a communication hole 2b formed at the rear end portion of the right frame 2.

[0029] The clutch operating member 23 is an annular rotating body that is rotatable about a spool shaft (pinion shaft). The clutch operating member 23 is formed of a material having high strength and excellent wear resistance, for example, polyacetal (POM). The clutch operating member 23 has a pair of cam portions 23k, 23k (see FIG. 4) that can engage with the yoke 24. The cam portions 23k, 23k engage with and disengage from the yoke 24 as the clutch operating member 23 rotates, and move the yoke 24 along the pinion shaft.

[0030] As shown in FIG. 3B, a long hole 27 extending in the circumferential direction is formed at the rear portion of the clutch operating member 23. A boss portion (pin) (not shown) protruding from the right frame 2 is engaged with the long hole 27, and the engagement of this boss portion defines the rotation range of the clutch operating member 23. A screw member 27a is screwed into the boss portion from the right side of the clutch frame 22.

[0031] The clutch operating member 23 is elastically sorted between a driving force transmission state, which is the clutch-on position, and a driving force cutoff state, which is the clutch-off position, by a sorting spring member 28 interposed between the clutch operating member 23 and the right frame 2. A torsion spring is used as the sorting spring member 28.

[0032] The yoke 24 is a member that moves in the left - right direction along the pinion shaft in conjunction with the rotational movement of the clutch operating member 23. The yoke 24 fits into a circumferential groove (not shown) of the pinion 12 over approximately 180° and has a pair of arm portions 24a, 24a that extend in the radial direction. The yoke 24 is held by support pins 25, 25 protruding from the right frame 2, and each arm portion 24a, 24a is constantly biased toward the clutch operating member 23 by spring members (not shown) disposed on each support pin 25, 25.

[0033] As described above, the first return mechanism 30 is a handle - operated return mechanism that uses the rotational driving force of the handle (handle shaft 7) to return the clutch mechanism 20 to the driving - force transmission state. The first return mechanism 30 includes a ratchet 31 and a first kick member 32 as a handle - interlocking kick member. The ratchet 31 is rotationally fixed to the handle shaft 7 and rotates integrally with the handle shaft 7.

[0034] The first kick member 32 is disposed on the side surface of the right frame 2 below the pinion 12 (pinion shaft) in a side view and has a substantially rectangular plate shape. The first kick member 32 has an elongated hole 32a through which one support pin 25 is inserted, a square regulating hole 32b through which a regulating projection 33 provided on the side surface of the right frame 2 is inserted, and an engaging portion 32c that engages with the ratchet 31. A coil spring 34 (see FIGS. 3A and 3B) that biases the engaging portion 32c toward the ratchet 31 is attached in the vicinity of the engaging portion 32c. In FIGS. 4, 11A - 11E below, the coil spring 34 is omitted for simplicity.

[0035] In the driving - force transmission state shown in FIG. 3A, the first kick member 32 is pressed by the rotation of the clutch operating member 23 and is disposed at a position where it rotates clockwise with the support pin 25 as a fulcrum. As a result, in the driving - force transmission state, the engaging portion 32c is disposed at a position where it is disengaged from the ratchet 31. On the one hand, when the first kick member 32 is switched from the driving force transmission state to the driving force interruption state, as shown in FIG. 3B, the engaging portion 32c moves into the rotation orbit of the ratchet 31. Thereby, when the handle is rotated in the driving force interruption state, the first kick member 32 abuts on the ratchet 31 (is kicked) and moves obliquely upward backward. By this movement, the tip portion 32e of the first kick member 32 abuts on the concave portion 23j (see FIG. 4) of the clutch operating member 23, and the clutch operating member 23 is rotated in the clockwise direction. Thereby, the clutch mechanism 20 is restored from the driving force interruption state to the driving force transmission state. It should be noted that the restoration of the clutch mechanism 20 can also be performed by pushing up the clutch lever 21.

[0036] As described above, the second restoration mechanism 40 is a mechanism that uses the rotational driving force of the electric motor 6 to restore the clutch mechanism 20 to the driving force transmission state. As shown in FIG. 3A, the second restoration mechanism 40 includes a return gear 41, an engaging gear 42 that functions as a clutch return rotating body, and a second kick member 43. The engaging gear 42 and the second kick member 43 are arranged between the spool shaft (pinion shaft) and the output shaft 6b (see FIG. 3A, motor shaft) of the return reduction mechanism 6a. Here, the second restoration mechanism 40 is driven by the control of the control unit 60 as a control means as shown in FIG. 13.

[0037] As shown in FIG. 13, the control unit 60 includes a detection unit 61, a calculation unit 62, a rotation speed determination unit 63, a feed amount determination unit 64, and a drive control unit 65. The detection unit 61 detects that the clutch mechanism 20 is in the driving force interruption state. A position sensor 66 for detecting the position of the clutch operating member 23 is connected to the detection unit 61. When the detection unit 61 inputs a detection signal from the position sensor 66, it detects that the clutch mechanism 20 is in the driving force interruption state, and outputs the detection signal to the drive control unit 65. The position sensor 66 can be composed of, for example, a magnetic sensor provided on the right frame 2 side and a magnet provided on the clutch operating member 23 side.

[0038] The calculation unit 62 calculates the rotational speed of the spool 5 as the fishing line is paid out, and also calculates the amount of fishing line paid out. A rotation detection sensor 67 that detects the rotation of the spool 5 is connected to the calculation unit 62. The calculation unit 62 calculates the rotational speed of the spool 5 based on the rotation signal of the spool 5 input from the rotation detection sensor 67, and outputs the calculated value to the rotational speed determination unit 63. Further, the calculation unit 62 calculates the amount of fishing line paid out based on the calculated rotational speed of the spool 5, and outputs the calculated value to the payout amount determination unit 64.

[0039] The rotational speed determination unit 63 determines whether the value of the rotational speed of the spool 5 calculated by the calculation unit 62 satisfies a predetermined condition set in advance. Then, when the rotational speed determination unit 63 determines that the value of the rotational speed of the spool 5 satisfies the predetermined condition set in advance, it outputs the determination result to the drive control unit 65. Note that the predetermined condition for the rotational speed of the spool 5 can be appropriately set by selecting the functions provided in the counter case 4 (see FIG. 1).

[0040] The payout amount determination unit 64 determines whether the amount of fishing line paid out calculated by the calculation unit 62 has reached a preset amount of fishing line paid out. Then, when the payout amount determination unit 64 determines that the calculated value of the amount of fishing line paid out has reached the preset amount of fishing line paid out, it outputs the determination result to the drive control unit 65. Note that the setting of the amount of fishing line paid out (for example, setting to stop the payout at a predetermined shelf (water depth) by stopping the rotation of the spool 5, etc.) can be appropriately performed by selecting the functions provided in the counter case 4 (see FIG. 1).

[0041] The drive control unit 65 controls the driving of the electric motor 6 in the forward rotation direction or the reverse rotation direction. When the detection unit 61 detects that the clutch mechanism 20 is in the driving force cutoff state, and the rotation speed determination unit 63 determines that the rotation speed of the spool 5 satisfies a predetermined condition, or when the payout amount determination unit 64 determines that the payout amount of the fishing line has reached a preset fishing line payout amount, the drive control unit 65 controls the driving of the electric motor 6 in the reverse rotation direction. That is, in addition to normal winding control, the drive control unit 65 has a return control function for returning the clutch mechanism 20 from the driving force cutoff state to the driving force transmission state.

[0042] Next, each component of the second return mechanism 40 will be described in detail. As shown in FIGS. 3A and 3B, the return gear 41 of the second return mechanism 40 is attached to the output shaft 6b of the return reduction mechanism 6a connected to the electric motor 6, and is configured to rotate in the clockwise direction when the electric motor 6 is driven in reverse rotation by the drive control of the control unit 60. Note that the return gear 41 is configured not to rotate in the counterclockwise direction by the return reduction mechanism 6a and a one-way clutch incorporated separately therefrom.

[0043] The engaging gear 42 meshes with the return gear 41 and has the effect of pushing the second kick member 43 downward (returning from the driving force cutoff state to the driving force transmission state) by receiving the rotational driving force of the return gear 41. The second kick member 43 is a member for returning the clutch operating member 23 in the driving force cutoff state to the driving force transmission state. The second kick member 43 is configured to engage and disengage with the engaging gear 42 by rotating in conjunction with the rotation of the clutch operating member 23. The second kick member 43 is retained by a retaining plate 50 for fixing the handle shaft 7 to the right frame 2. The second kick member 43 is formed of a stainless steel material having strength and excellent wear resistance.

[0044] As shown in FIG. 5A, the engaging gear 42 includes a gear body 421 and a claw portion 426 rotatably assembled to the gear body 421.

[0045] As shown in FIGS. 5A and 5B, the gear body 421 includes a cylindrical base portion 422 and a tooth portion 423 integrally formed on the right side portion of the base portion 422. The base portion 422 is non-rotatably fixed to the output shaft 6b (see FIG. 3A) of the return speed reduction mechanism 6a. As shown in FIG. 5B, a stepped cylindrical inner surface portion 422a into which the insertion portion 427 of the claw portion 426 is inserted is formed inside the base portion 422. Further, as shown in FIG. 5C, a protruding portion 422b protruding radially inward is formed inside the base portion 422. The protruding portion 422b has a substantially triangular cross-sectional shape, and a total of four are formed at intervals of 90 degrees in the circumferential direction of the inner surface of the base portion 422. A rotation space portion 422e for ensuring the rotation of the claw portion 426 is formed between adjacent protruding portions 422b. Each protruding portion 422b includes a right-angle surface 422c extending in the axial direction and an inclined surface 422d extending in the axial direction, and supports the insertion portion 427 of the claw portion 426 rotatably at each vertex portion.

[0046] As shown in FIG. 5B, the claw portion 426 includes a cylindrical insertion portion 427 inserted into the inner surface portion 422a of the base portion 422 and a substantially cylindrical large-diameter portion 428 continuous with the left side of the insertion portion 427. A gap portion 424 is formed between the right side portion of the large-diameter portion 428 and the left side portion of the base portion 422 facing the same, and a spring member 425 is disposed therein. The spring member 425 functions as a biasing member that biases the claw portion 426 counterclockwise (in the direction of arrow X1 in FIG. 5C) with respect to the base portion 422. Two engaging claws 429, 429 (only one is shown) are protruding and formed on the outer peripheral surface of the large-diameter portion 428 at intervals of 180 degrees in the circumferential direction. Each engaging claw 429 includes an engaging surface 429a that rises substantially perpendicular to the radial direction (see FIG. 12).

[0047] As shown in FIG. 5C, a regulating protrusion 426a protruding radially outward is formed on the outer peripheral surface of the insertion portion 427 of the claw portion 426. The regulating protrusion 426a has a substantially square cross-section and a total of four are formed at intervals of 90 degrees in the circumferential direction of the outer peripheral surface of the insertion portion 427. Each regulating protrusion 426a is disposed in each rotation space portion 422e of the base portion 422 and can rotate in the clockwise direction (see arrow X2 in FIG. 5D) against the biasing force of the spring member 425 within the range partitioned in the circumferential direction by the right-angle surface 422c and the inclined surface 422d of the adjacent protrusions 422b, 422b (within the range of the circumferential dimension of the rotation space portion 422e). That is, the engaging claw 429 of the claw portion 426 is configured to be able to take a first position (the position shown in FIG. 5C) moved in the rotation direction of the engaging gear 42 and a second position (the position shown in FIG. 5D) moved in the opposite direction thereto, and is biased from the second position toward the first position by the biasing force of the spring member 425. The rotation angle of each regulating protrusion 426a is represented by an angle θ1 defined by the inclined surface 422d and the opposing surface of the regulating protrusion 426a opposing thereto, as shown in FIG. 5D. The angle θ1 is set to a size that allows a sliding distance L1 (see FIG. 12), which will be described later, when the second kick member 43 abuts against the large-diameter portion 428 of the engaging gear 42.

[0048] As shown in FIGS. 8(a) and 8(b), the second kick member 43 includes a rotation support portion 431, a spring locking portion 437 extending rearward from the rotation support portion 431, an engaging protrusion 433 extending upward from the rotation support portion 431, and a guide portion 435 extending forward and downward from the rotation support portion 431.

[0049] In the central portion of the swing support portion 431, a support hole 432 through which the swing support shaft 23d (see FIG. 7) of the clutch operating member 23 is inserted is formed. A locking hole 438 is formed at the rear end portion of the spring locking portion 437. The engaging projection 433 is a portion that abuts against the engaging claw 429 of the engaging gear 42, and has a contact portion 434 at its tip. The contact portion 434 is formed by bending the upper end portion of the engaging projection 433 substantially at a right angle to the left. As shown in FIG. 8(b), the contact portion 434 is disposed somewhat on the front side in a side view with respect to the support hole 432. The guide portion 435 is curved in a substantially U shape in a side view and the tip portion faces rearward and downward. A guide projection 436 is provided at the tip portion of the guide portion 435. The guide projection 436 is formed by bending the tip portion of the guide portion 435 substantially at a right angle to the right.

[0050] As shown in FIG. 4, the second kick member 43 is attached to the front end portion 23c of the clutch operating member 23. The front end portion 23c has a substantially rectangular flat plate shape in a side view as shown in FIG. 7, and extends forward of the clutch operating member 23. An attachment seat 23e on which the second kick member 43 is disposed is formed at the lower front side of the front end portion 23c. The outer contour of the attachment seat 23e is formed in a circular shape corresponding to the circular shape of the swing support portion 431 of the second kick member 43. A swing support shaft 23d inserted through the support hole 432 of the second kick member 43 projects from the attachment seat 23e.

[0051] On the other hand, a holding projection 23f for holding the second kick member 43 in an upright posture (a posture in which the contact portion 434 faces directly upward) is formed at the upper front side of the front end portion 23c. The holding projection 23f projects toward the right side of the front end portion 23c and abuts against the rear portion of the engaging projection 433 of the second kick member 43 to hold the posture of the second kick member 43.

[0052] At the rear of the front end portion 23c, a locking hole 23g is formed. The rear end portion of the spring member 29 connected to the second kick member 43 is locked in the locking hole 23g. The rear end portion of the spring member 29 is inserted into the locking hole 23g from the right side, and is covered by the upper portion 52a of the rear portion 52 of the fixing plate 50 from the right side and is retained to prevent it from coming off. The spring member 29 functions as a distribution spring that elastically distributes the engagement and disengagement of the second kick member 43 with respect to the engagement gear 42. In the present embodiment, a torsion spring is used as the spring member 29. In the driving force transmission state of the clutch mechanism 20, the second kick member 43 is distributed and held in a non-engaged state in which the engaging protrusion 433 abuts against the holding protrusion 23f by the spring member 29. Further, in the driving force cut-off state of the clutch mechanism 20, the second kick member 43 is distributed and held in an engaged state in which it abuts against the claw portion 426 of the engagement gear 42 and can engage with the engaging claw 429 by the spring member 29.

[0053] As described above, the fixing plate 50 mainly has two functions: a function of fixing the handle shaft 7 to the right frame 2 and a function of retaining the second kick member 43 to prevent it from coming off. Further, the fixing plate 50 covers a part of the front side of the clutch operating member 23 and also has a function of holding the front side of the clutch operating member 23. The fixing plate 50, like the second kick member 43, is formed of a stainless steel material having strength and excellent wear resistance.

[0054] As shown in FIGS. 6(a) and 6(b), the fixing plate 50 includes a central portion 51, a rear portion 52 continuous with the rear side of the central portion 51, and a front portion 53 continuous with the front side of the central portion 51. A groove portion 56 extending in the vertical direction and having a substantially U-shaped side view is formed between the rear portion 52 and the front portion 53. The handle shaft 7 is inserted inside the fixing plate 50 through the lower end portion of the groove portion 56 and is attached to the right frame 2 (see FIG. 2). Here, a one-way clutch (not shown) or a known drag mechanism 7a as shown in FIG. 10 is disposed on the handle shaft 7. The drag mechanism 7a applies a drag force to the rotation of the spool 5 when fishing line is paid out from the spool 5 during fishing. A star-shaped drag adjustment knob (star drag) for adjusting the drag force by the drag mechanism 7a is provided between the reel body 1 and the handle. The drag mechanism 7a includes a plurality of braking members (friction plates, washers, etc.) 7b disposed in the recess 11b of the drive gear 11. The drag mechanism 7a has a function of adjusting the pressing force of the pressing member 7c against the braking member 7b by rotating the drag adjustment knob, and adjusting the rotational frictional force (drag force) of the drive gear 11 with respect to the handle shaft 7.

[0055] As shown in FIGS. 4, 6(a) and 6(b), the rear portion 52 of the fixed plate 50 covers a part of the front portion of the clutch operating member 23 and rotatably holds the front portion of the clutch operating member 23. The upper portion 52a of the rear portion 52 extends upward so as to cover the locking hole 23g of the front end portion 23c of the clutch operating member 23, and holds the rear end portion of the spring member 29 so as to prevent it from coming off throughout the rotation of the clutch operating member 23. An extending portion 52b extending rearward is formed at the lower portion of the rear portion 52. As shown in FIG. 4, the extending portion 52b extends so as to cover a part of the first kick member 32, and abuts on the first kick member 32 from the right side to support the first kick member 32.

[0056] As shown in FIGS. 4, 6(a) and 6(b), the front portion 53 of the fixed plate 50 faces the rear portion 52 with the groove portion 56 interposed therebetween, and is provided with a substantially triangular guide hole 55 that opens in the vertical direction. The guide hole 55 functions as a regulation hole for regulating the rotational position of the second kick member 43 with respect to the engaging claw 429 of the engaging gear 42. A guide protrusion 436 of the second kick member 43 is inserted into the guide hole 55. The upper portion 53a of the front portion 53 holds the rotation support shaft 23d (the rotation support portion 431 of the second kick member 43) throughout the movement of the second kick member 43 accompanying the rotation of the clutch operating member 23.

[0057] In addition, at the lower part of the front portion 53, there is provided an attachment portion 54 to which the front end portion of the coil spring 34 (see FIG. 3A) is attached.

[0058] As shown in FIG. 9, the guide hole 55 includes an upper edge portion 55a, a front upper edge portion 55b continuous with the front side of the upper edge portion 55a, a front lower edge portion 55c continuous with the lower side of the front upper edge portion 55b, a lower edge portion 55d continuous with the lower side of the front lower edge portion 55c, a rear lower edge portion 55e continuous with the rear side of the lower edge portion 55d, and a rear upper edge portion 55f continuous with the upper side of the rear lower edge portion 55e and connected to the rear side of the upper edge portion 55a. The upper edge portion 55a and the lower edge portion 55d are substantially parallel to each other. The front upper edge portion 55b is inclined forward and downward from the front end portion of the upper edge portion 55a. The front lower edge portion 55c is inclined rearward and downward from the lower end portion of the front upper edge portion 55b and is recessed in a gently arcuate shape toward the front as a whole. The rear lower edge portion 55e is inclined forward and upward from the rear end portion of the lower edge portion 55d. The rear upper edge portion 55f is inclined rearward and upward from the upper end portion of the rear lower edge portion 55e and is connected to the rear end portion of the upper edge portion 55a.

[0059] Next, the positional relationship between the guide protrusion 436 of the second kick member 43 and each edge portion of the guide hole 55 will be described with reference to FIGS. 4, 11A to 11E while referring to FIG. 9. As shown in FIG. 4, when the clutch mechanism 20 is in the clutch-on position (driving force transmission state), as shown in FIG. 9, the guide protrusion 436 is disposed at a first position P1 within a region surrounded by the front lower edge portion 55c, the lower edge portion 55d, and the rear lower edge portion 55e, which is the lower region of the guide hole 55.

[0060] From this state, as shown in FIG. 11A, when the clutch lever 21 of the clutch mechanism 20 is pushed down with a finger, the clutch operating member 23 rotates counterclockwise about the rotation axis O1, and the second kick member 43 moves upward from the position shown in FIG. 4. At this time, as shown in FIG. 9, the guide projection 436 of the second kick member 43 moves upward along the front lower edge portion 55c from the lower end position of the front lower edge portion 55c of the guide hole 55 and moves to the second position P2 where it abuts near the lower end portion of the front upper edge portion 55b. Note that the engaging projection 433 of the second kick member 43 remains in contact with the holding projection 23f at the front end portion 23c of the clutch operating member 23.

[0061] Then, when the clutch lever 21 is continuously pushed down, as shown in FIG. 11B, the clutch mechanism 20 rotates counterclockwise beyond the dead point of the switching spring member 28. At this time, as shown in FIG. 9, the guide projection 436 of the second kick member 43 moves from the second position P2 to the third position P3 near the upper end portion of the front upper edge portion 55b. Along with this movement, the second kick member 43 rotates clockwise about the rotation support shaft 23d as shown in FIG. 11B and reaches the dead point by the spring member 29. As a result, the engaging projection 433 of the second kick member 43 separates from the holding projection 23f and takes an upright posture.

[0062] After that, when the clutch lever 21 is further pushed down, as shown in FIG. 11C, the clutch mechanism 20 is brought into a driving force cutoff state. At this time, as shown in FIG. 9, the guide projection 436 of the second kick member 43 moves along the upper edge portion 55a from the third position P3, and then moves to the fourth position P4 near the corner (corner portion) between the upper edge portion 55a and the rear upper edge portion 55f. Along with this movement, the second kick member 43 rapidly rotates clockwise beyond the dead point as shown in FIG. 11C. As a result, in the driving force cutoff state, the engaging projection 433 of the second kick member 43 comes into contact with the outer peripheral surface of the large diameter portion 428 of the return gear 41 (a state in which it can engage with the engaging claw 429).

[0063] Here, the second kick member 43 is configured to rotate toward the engagement gear 42 while moving upward as the clutch operating member 23 rotates. As a result, when the engagement protrusion 433 abuts against the large-diameter portion 428 of the engagement gear 42, it comes into contact while sliding upward on the outer peripheral surface of the large-diameter portion 428.

[0064] Next, the operation when returning from the driving force cutoff state to the driving force transmission state will be described. When the electric motor 6 is driven in reverse rotation by the drive control of the control unit 60 in the driving force cutoff state, the engagement gear 42 rotates counterclockwise via the return gear 41. Then, as shown in FIG. 11D, the engagement claw 429 abuts against the engagement protrusion 433 of the second kick member 43 on the large-diameter portion 428 of the return gear 41, and then, as shown in FIG. 11E, the engagement claw 429 pushes down the second kick member 43. At this time, as shown in FIG. 9, the guide protrusion 436 of the second kick member 43 moves downward along the rear upper edge portion 55f and the rear lower edge portion 55e from the fourth position P4 and returns to the first position P1. By this movement, the second kick member 43 pushes the front end portion 23c of the clutch operating member 23 downward and rotates the clutch operating member 23 in the clockwise direction. By this rotation of the clutch operating member 23, the clutch mechanism 20 returns from the driving force cutoff state to the driving force transmission state.

[0065] Next, the action when the engagement claw 429 is in a positional relationship interfering with the engagement protrusion 433 during sliding when the engagement protrusion 433 abuts against the large-diameter portion 428 will be described with reference to FIG. 12. In FIG. 12, the symbol PT1 indicates the initial contact position where the engagement protrusion 433 of the second kick member 43 abuts against the large-diameter portion 428 of the engagement gear 42, the symbol PT2 indicates the position after sliding after the engagement protrusion 433 slides on the outer peripheral surface of the large-diameter portion 428, and the symbol L1 indicates the sliding distance. Note that the engagement claw 429 of the engagement gear 42 stops at an arbitrary position in the circumferential direction, and control of the stop position is not performed. FIG. 12 shows a case where the engagement claw 429 indicated by a dashed line is located on the side in the sliding direction of the initial contact position PT1 of the engagement protrusion 433.

[0066] As shown in Fig. 12, the engaging protrusion 433 of the second kick member 43 contacts the outer peripheral surface of the large-diameter portion 428 at the initial contact position PT1 of the outer peripheral surface of the large-diameter portion 428, and then moves a sliding distance L1 to reach the position PT2 after sliding. In the process of this movement, the engaging protrusion 433 contacts the engaging claw 429 and presses the engaging claw 429 in the clockwise direction. Then, the large-diameter portion 428 rotates in the clockwise direction against the biasing force of the spring member 425, allowing the sliding of the engaging protrusion 433. As a result, even when the engaging claw 429 is located in the sliding direction, the engaging claw 429 does not get in the way, and the engaging protrusion 433 can engage with the engaging claw 429 preferably.

[0067] According to the present embodiment described above, since the second kick member 43 is rotatably supported by the right frame 2 and engages with and disengages from the engaging gear 42 by rotating in conjunction with the clutch operating member 23, compared with a configuration in which a return member engages and disengages by a linear sliding movement as in the prior art, the degree of freedom in the layout of the component parts can be increased, and an increase in the size of the reel body 1 can be prevented. In addition, since the engaging gear 42 and the second kick member 43 can be provided with good space efficiency between the spool shaft and the motor shaft, the degree of freedom in the layout of the component parts can be increased, and an increase in the size of the reel body 1 can be prevented.

[0068] Further, since the engaging claw 429 can move in the direction opposite to the rotation direction of the engaging gear 42 against the biasing force of the spring member 425, even when the second kick member 43 engages and presses the engaging claw 429 in the direction opposite to the rotation direction of the engaging gear 42 by interfering with the engaging claw 429 when the second kick member 43 engages, the engaging claw 429 is pushed by the second kick member 43 and moves flexibly in the reverse direction. As a result, the engagement state between the second kick member 43 and the engaging claw 429 is maintained well. Therefore, the clutch mechanism 20 can be quickly returned from the driving force cutoff state to the driving force transmission state, and the responsiveness of the return mechanism is excellent.

[0069] In addition, when the second kick member 43 engages, even if the second kick member 43 interferes with the engagement claw 429, the engaged state is maintained well. Therefore, it is not necessary to manage the stop position of the engagement claw 429 for the next return, and it is not necessary to provide a sensor or the like for detecting the stop position of the engagement claw 429 or control means for adjusting the position of the engagement claw 429. Accordingly, it is possible to reduce costs while preventing the reel body 1 from becoming large.

[0070] In addition, since the first return mechanism 30 can return the clutch mechanism 20, which has been brought into a driving force cutoff state by the rotation operation of the handle, to a driving force transmission state, a fishing electric reel 100 that is easy to use and excellent in fishing operability can be obtained.

[0071] In addition, since the control unit 60 is provided, when the clutch mechanism 20 is in a driving force cutoff state and the rotational speed of the spool 5 satisfies a predetermined condition, or when the amount of fishing line paid out reaches a preset amount of fishing line paid out, the clutch mechanism 20 in the driving force cutoff state can be automatically returned to the driving force transmission state. Accordingly, a fishing electric reel 100 that is easy to use and excellent in fishing operability can be obtained.

[0072] As described above, the embodiments of the present invention have been described. However, the present invention is not limited to the above-described embodiments and can be variously modified. For example, in the above embodiment, the engagement gear 42 and the second kick member 43 are arranged in the upper region of the right frame 2 between the spool shaft and the motor shaft, but the present invention is not limited to this, and they may be arranged in the lower region of the right frame 2 between the spool shaft and the motor shaft. Further, they may be arranged in a region overlapping the drive gear 11 or the like of the handle shaft 7.

[0073] In the above embodiment, the guide hole 55 provided in the fixed plate 50 constitutes the restricting portion. However, the present invention is not limited to this, and the second kick member 43 may be configured to be guided by using the edge portion or the like of the fixed plate 50. Further, although the fixed plate 50 is shown as being composed of a single plate, it may be configured by combining a plurality of plates.

[0074] Further, the second kick member 43 is not limited to being disposed between the right frame 2 and the fixed plate 50, and may be disposed at a position deviated from the fixed plate 50.

[0075] In addition, the fixed plate 50 is configured to retain the sorting spring member 28 to prevent it from coming off. However, the present invention is not limited to this, and the sorting spring member 28 may be exposed to reduce the size.

Explanation of Reference Numerals

[0076] 1 Reel body 2 Frame 3 Side plate 5 Spool 6 Electric motor 7 Handle shaft 20 Clutch mechanism 21 Clutch lever 23 Clutch operating member 31 Ratchet 32 First kick member (handle interlocking kick member) 30 First return mechanism (handle operation return mechanism) 40 Second return mechanism (return mechanism) 41 Return gear 42 Engaging gear (rotating body for clutch return) 43 Second kick member (kick member) 61 Detection unit 62 Calculation unit 63 Rotation speed determination unit 64 Pay-out amount determination unit 65 Drive control unit 100 Electric fishing reel 425 Spring member (biasing member) 429 engaging claws

Claims

1. A spool provided between frames of a reel body and rotating at least under the driving force of an electric motor, a clutch mechanism provided on one frame side to which a handle shaft is attached and switching the spool between a driving force transmission state and a driving force interruption state, a return mechanism provided on one frame side for returning the clutch mechanism in the driving force interruption state to the driving force transmission state, the electric fishing reel comprising: the clutch mechanism having a clutch operating member that rotates by an operation of a clutch lever and is in a driving force interruption state, the return mechanism including: a return gear provided on a motor shaft of the electric motor, a clutch return rotating body that meshes with the return gear and rotates, a kick member rotatably supported by the clutch operating member and engaging and disengaging with the clutch return rotating body by rotating in conjunction with the rotation of the clutch operating member to return the clutch operating member in the driving force interruption state to the driving force transmission state, the clutch return rotating body and the kick member being disposed between a spool shaft that supports the spool and the motor shaft, the clutch return rotating body including an engaging claw that engages with the kick member and a biasing member, the engaging claw being: capable of changing its position around the axis of the clutch return rotating body, configured to be able to take a first position moved in the rotation direction of the clutch return rotating body and a second position moved in the opposite direction thereto, the electric fishing reel characterized in that it is biased from the second position toward the first position by the biasing force of the biasing member.

2. A handle operation return mechanism for returning the clutch mechanism in the driving force interruption state to the driving force transmission state by a rotational operation of a handle, the handle operation return mechanism including: a ratchet attached to the handle shaft, a handle interlocking kick member that engages and disengages with the ratchet and returns the clutch operating member in the driving force interruption state to the driving force transmission state, the electric fishing reel according to claim 1, characterized in that it comprises the same.

3. a drive control unit for driving and controlling the electric motor in a forward rotation direction or a reverse rotation direction, a detection unit for detecting that the clutch mechanism is in a driving force interruption state, a calculation unit for calculating the rotational speed of the spool accompanying the payout of fishing line and calculating the amount of fishing line paid out A rotational speed determination unit that determines whether or not the rotational speed of the spool calculated by the calculation unit satisfies a predetermined condition; A payout amount determination unit that determines whether or not the payout amount of the fishing line calculated by the calculation unit has reached a preset payout amount of the fishing line, and comprising: The drive control unit When it is detected by the detection unit that the clutch mechanism is in a driving force cut-off state, and it is determined by the rotational speed determination unit that the rotational speed of the spool satisfies a predetermined condition, or when it is determined by the payout amount determination unit that the payout amount of the fishing line has reached a preset payout amount of the fishing line, The electric fishing reel according to claim 1, wherein the electric motor is driven and controlled in the reverse rotation direction to bring the engaging claw of the rotary body for clutch return into contact with the kick member.

Images