JP4785372B2 - Fishing reel one-way clutch - Google Patents

Description

  The present invention relates to a one-way clutch, and more particularly to a fishing reel one-way clutch that prohibits rotation in one direction of a rotating shaft rotatably mounted on a reel body of a fishing reel.

  Generally, an electric reel is a reel that can be driven to rotate at least a spool in a yarn winding direction by a motor, and is widely used when fishing a fish having a depth of 50 m or more from a ship. A conventional electric reel includes a reel body having a handle, a spool rotatably mounted on the reel body, a motor for rotating the spool, and a rotation transmission mechanism including a planetary gear mechanism for transmitting the rotation of the motor to the spool. And. A clutch mechanism capable of turning on and off the spool in a freely rotatable state and a yarn winding enabled state; a clutch switching mechanism that switches the clutch mechanism between a clutch off state and a clutch on state; and a clutch operating member that operates the clutch switching mechanism; It has. The handle shaft and the motor on which the handle is mounted are prohibited from rotating (reversely rotating) in the yarn drawing direction.

  In this type of electric reel, an electric reel is known in which the clutch mechanism is returned from the clutch-off state to the clutch-on state by reverse rotation of the motor (see, for example, Patent Document 1).

  The conventional electric reel that returns the clutch mechanism to the clutch-on state by such a motor is linked to a one-way clutch that can be switched between a reverse rotation prohibited state that prohibits the reverse rotation of the motor and a reverse rotation permitted state that is permitted, and the clutch switching mechanism. And an interlocking mechanism that moves between the first position and the second position, and a pressing member that is mounted on the output shaft of the motor via a one-way clutch. The interlocking mechanism is located at the first position when the clutch is on, and moves to the second position when the clutch is turned off by clutch operation. When the second position is moved, the one-way clutch for prohibiting the reverse rotation of the motor is switched to the reverse rotation permitted state by the movement. The pressing member is attached to the output shaft of the motor via a one-way clutch for clutch return. When the motor rotates in the reverse direction, the pressing member presses the interlock mechanism and moves it from the second position to the first position for clutch-on.

  In the electric reel having such a configuration, when the clutch lever is clutch-off operated, the clutch switching mechanism switches the clutch mechanism to the clutch-off state, and the one-way clutch is allowed to rotate in reverse by the interlocking mechanism in conjunction with the clutch switching mechanism. When the motor is reversed in this state, the interlocking mechanism is pressed by the pressing member, the clutch switching mechanism returns to the clutch-on state, and the clutch mechanism returns to the clutch-on state. Thereby, feeding of a fishing line can be stopped.

The one-way clutch used in this type of electric reel is attached to a ratchet wheel that is non-rotatably attached to the output shaft of the motor, a ratchet pawl that contacts and separates from the ratchet wheel, and the ratchet pawl toward the ratchet wheel. And a cam mechanism for swinging the ratchet pawl from the ratchet wheel to a position where the ratchet pawl is displaced when the motor rotates forward in the yarn winding direction. The cam mechanism has a wire-like question mark type spring member that is mounted in pressure contact with the outer peripheral surface of the motor output shaft, and a pressing cam that is connected to the tip of the spring member and swings the ratchet pawl. Yes. Here, the pressing cam is swung from the ratchet wheel to a position where the spring cam is rotated forward by the frictional force generated by pressing the spring member against the output shaft of the motor.
JP-A-11-341939 (FIG. 20)

  In the electric reel in which the clutch mechanism is returned to the clutch-on state by the conventional motor, for example, the clutch mechanism can be returned to the clutch-on state even when the clutch mechanism has less grease or the clutch mechanism is salted. Therefore, it is required to increase the operating force of the pressing cam. The one-way clutch used in such an electric reel generates a frictional force by winding a wire-like question mark type spring member around the output shaft of the motor and pressing it. For this reason, in order to increase the operating force of the pressing cam, it is necessary to increase the frictional force of the spring member against the output shaft of the motor.

  However, in general, since the wire-like spring member has a small contact area with the output shaft of the motor, it is difficult to obtain a large frictional force. Furthermore, since the rotation shaft of the motor rotates at a high speed, if the question mark type spring member repeatedly rotates, the inner peripheral portion attached to the output shaft of the motor wears, and the frictional force on the output shaft of the motor is reduced. There is a risk of decline.

  An object of the present invention is to increase the frictional force of a cam mechanism while improving the wear resistance of the cam mechanism in a one-way clutch of a fishing reel.

  A one-way clutch according to a first aspect of the present invention is a fishing reel one-way clutch that prohibits rotation in one direction of a rotation shaft that is rotatably mounted on a reel body of a fishing reel, and includes a ratchet wheel, a ratchet pawl, One urging member and a cam mechanism are provided. The ratchet wheel is interlocked with the rotation shaft, and has serrated teeth on the outer periphery thereof spaced apart in the circumferential direction. The ratchet pawl is swingably mounted on the reel body, and its tip contacts the tooth portion to prohibit rotation in one direction of the rotation shaft. The first urging member urges the ratchet pawl in a direction in contact with the tooth portion. The cam mechanism is mounted on the outer peripheral surface of the rotating shaft, and is attached to the outer periphery of the ring portion, which is mounted on the outer peripheral surface of the rotating shaft and has a first divided piece and a second divided piece that are divided at intervals in the circumferential direction. A second urging member that presses the first divided piece and the second divided piece against the rotation shaft, and a protruding portion that protrudes from the outer peripheral portion of the first divided piece and lifts the ratchet claw away from the tooth portion. The ratchet pawl is separated from the tooth portion against the biasing force of the first biasing member in conjunction with rotation in the other direction of the rotation shaft.

  In this one-way clutch, the ring portion of the cam mechanism is made of metal. Therefore, compared to the case where a wire-like question mark type spring member is used as the conventional cam mechanism or the ring portion is made of synthetic resin. Thus, the wear resistance can be remarkably improved. Moreover, since the ring part has the 1st division piece and the 2nd division piece which were divided | segmented at intervals in the circumferential direction, while mounting | wearing with a ring part becomes easy, the 2nd urging | biasing attached to outer periphery The frictional force with respect to the rotating shaft can be increased by pressing the member.

  A one-way clutch according to a second aspect is the one-way clutch according to the first aspect, wherein the ring portion is formed along a circumferential direction of the outer peripheral portion, and has an annular mounting groove in which the second urging member is mounted. In this case, the second urging member can be easily attached and the second urging member can be prevented from coming off.

  The one-way clutch according to a third aspect is the one-way clutch according to the second aspect, wherein the second urging member is a C-shaped spring member that can be mounted in the mounting groove. In this case, since a large urging force can be obtained with a simple configuration by using a metal C-shaped spring member as the second urging member, the frictional force on the rotating shaft can be increased with an inexpensive configuration.

  The one-way clutch according to a fourth aspect is the one-way clutch according to the third aspect, wherein the second urging member is mounted such that the outer peripheral portion is positioned inside the mounting groove. The cam mechanism further includes a cylindrical member attached to the outer peripheral portion of the second urging member. In this case, by attaching the cylindrical member attached to the outer peripheral portion of the second urging member, it is possible to reliably prevent the second urging member from coming off.

  A one-way clutch according to a fifth aspect is the one-way clutch according to any one of the first to fourth aspects, wherein the first divided piece and the second divided piece are divided at a position passing through the axis of the rotation shaft. In this case, since the ring portions of the first divided piece and the second divided piece can be formed symmetrically, the first divided piece and the second divided piece can be easily formed.

  A one-way clutch according to a sixth aspect is the one-way clutch according to any one of the first to fourth aspects, wherein the first divided piece and the second divided piece are divided at a position eccentric from the axis of the rotating shaft toward the second divided piece. Yes. In this case, since the ring portion of the first divided piece is formed to be longer than the ring portion of the second divided piece, the protrusion formed on the first divided piece causes the first divided piece by an impact when lifting the ratchet claw. The amount by which the piece moves can be regulated.

  A one-way clutch according to a seventh aspect is the one-way clutch according to any one of the first to sixth aspects, wherein the fishing reel is an electric reel that rotates a spool that is rotatably supported by the reel body by a motor. The rotating shaft is an output shaft of the motor. In this case, the frictional force with respect to the output shaft of the motor can be increased while improving the wear resistance of the cam mechanism of the electric reel.

  According to the present invention, in the one-way clutch of a fishing reel, the ring portion of the cam mechanism is formed of metal and has a first divided piece and a second divided piece that are divided at intervals in the circumferential direction. Therefore, the frictional force of the cam mechanism can be increased while improving the wear resistance of the cam mechanism.

〔overall structure〕
As shown in FIG. 1, an electric reel according to an embodiment of the present invention mainly includes a reel body 2 to which a handle 1 is attached, a spool 3 that is rotatably attached to the reel body 2, and an inside of the spool 3. The motor 4 is provided. A counter 5 for displaying a water depth or the like is mounted on the top of the reel body 2. As shown in FIG. 2, a rotation transmission mechanism 6 that transmits the rotation of the handle 1 to the spool 3 and transmits the rotation of the motor 4 to the spool 3 and a rotation transmission mechanism 6 are provided inside the reel body 2. The clutch mechanism 7, the clutch switching mechanism 8 for switching the clutch mechanism 7 (see FIG. 5 ), the first one-way clutch 9 for prohibiting the reverse rotation of the handle 1 in the thread unwinding direction, and the reverse rotation of the motor 4 in the thread unwinding direction. The second one-way clutch 10 to be prohibited, the first clutch return mechanism 11 that returns the clutch mechanism 7 to the clutch-on state by the reverse rotation of the motor 4, and the first clutch mechanism 7 that returns to the clutch-on state by the rotation of the handle 1 in the yarn winding direction. And a two-clutch return mechanism 12 (see FIG. 5 ).

[Reel body configuration]
As shown in FIG. 2, the reel body 2 includes a frame 13, and a first side cover 14 and a second side cover 15 that cover both sides of the frame 13. As shown in FIG. 2, the frame 13 is an integrally formed member of aluminum alloy die casting, and includes a pair of left and right first side plates 16 and second side plates 17, and a plurality of first side plates 16 and second side plates 17. And a connecting member 18 to be connected. A rod mounting leg 19 for mounting a fishing rod is mounted on the lower connecting member 18.

  The second side cover 15 is fastened to the second side plate 17 with bolts. A fixed frame 20 for mounting the rotation transmission mechanism 6 and the like is fastened to the second side cover 15 with bolts. Therefore, when the second side cover 15 is removed from the second side plate 17, the fixed frame 20 is also detached from the second side plate 17 together with a part of the rotation transmission mechanism 6 and the second side cover 15.

  The first side cover 14 is fastened to the first side plate 16 with bolts. The first side cover 14 is provided with a connector portion 14a (see FIG. 1) for a power cable for connecting to a power source such as a storage battery provided outside and projecting obliquely at the front portion.

  The first side plate 16 is a plate-shaped member made of synthetic resin having a rib on the peripheral edge, and a bulging portion 27 for mounting the motor 4 is formed on the center portion so as to protrude outward. A cover member 28 for covering a protruding portion of an output shaft 30 (described later) of the motor 4 is mounted on the outer side of the bulging portion 27 on the first side cover 14 side.

  The cover member 28 is a cap member made of synthetic resin, and is detachably attached to the bulging portion 27 by a plurality of screw members 14c. The cover member 28 is formed so as to penetrate the through hole 14b of the first side cover 14 and protrude outward when the cover member 28 is attached to the bulging portion 27. Inside the cover member 28, a claw control mechanism 84, a roller clutch 90, a pressing member 91, and the like, which will be described later, mounted on the protruding portion of the output shaft 30 are disposed.

[Spool configuration]
The spool 3 includes a cylindrical bobbin trunk 3a capable of accommodating the motor 4 therein, and a pair of left and right flanges 3b formed on the outer periphery of the bobbin trunk 3a with a space therebetween. One end of the spool 3 extends outward from the flange portion 3b, and a bearing 25 is disposed on the inner peripheral surface of the extended end portion. A gear plate 3 c is fixed to the other end of the spool 3. The gear plate 3c is provided to transmit the rotation of the spool 3 to a level wind mechanism (not shown). A bearing 26 is mounted between the gear plate 3c and the fixed frame 20 on the spool center side portion of the gear plate 3c. The spool 3 is rotatably supported by the reel body 2 by the two bearings 25 and 26.

[Motor configuration]
As shown in FIG. 3, the motor 4 functions as a driving body for winding the spool 3, for feeding the yarn, and for operating the first clutch return mechanism 11. The motor 4 is rotatable to a bottomed cylindrical case member 31 whose base end is open, a cap member 32 fixed to the base end of the case member 31 to close the opening, and the case member 31 and the cap member 32. And an attached output shaft 30. The case member 31 is a bottomed cylindrical member, and rotatably supports the output shaft 30 at the bottom.

  As shown in FIG. 4, a field 67 having permanent magnets, an armature 68 having coils, a commutator 69, and a brush 70 are disposed inside the case member 31. The case member 31 is a metal member that is deep-drawn press-molded, and the output shaft 30 is rotatably supported at the bottom thereof via a bearing 76b. The cap member 32 is a disk-shaped metal member, and is fixed to the case member 31 by caulking. The output shaft 30 is rotatably supported by the cap member 32 via a bearing 76a. The bearings 76a and 76b are sliding bearings made of, for example, brass having a spherical outer peripheral surface.

  The output shaft 30 is rotatably mounted on the case member 31 and the cap member 32. The left end of the output shaft 30 protrudes from the cap member 32. A serration 30a is formed there, and the mechanism mounting shaft 75 is fixed to be non-rotatable by, for example, serration coupling. The right end 30b of the output shaft 30 protrudes from the tip of the case member 31 as shown in FIG. A two-stage reduction planetary gear mechanism 40 constituting the rotation transmission mechanism 6 is attached to the protruding tip.

  As shown in FIG. 4, the field magnet 67 is fixed to the inner peripheral surface of the case member 31, and is a cylindrical anisotropic magnet obtained by sintering and solidifying rare earth alloy powder into a cylindrical shape, for example. It is.

  The armature 68 is disposed to face the inner peripheral surface of the field magnet 67. The armature 68 includes an armature core 77 having, for example, five pole portions protruding radially, and a coil 78 wound around the pole portion of the armature core 77. The armature core 77 is formed by stacking thin plates made of amorphous silicon alloy and has a high magnetic permeability with little hysteresis loss.

  The commutator 69 is a conductor formed by being divided into five in the circumferential direction on the outer peripheral surface of a cylindrical insulating member 69 a that is electrically insulated and fixed to the output shaft 30. The commutator 69 is electrically connected to the brush 70.

  The brush 70 is fixed to an attachment member 70 a made of an insulator mounted on the cap member 32, and is electrically connected to the commutator 69 on the circumferential surface facing the commutator 69. The brush 70 is electrically connected to two terminals 70b disposed so as to penetrate the pair of extraction grooves 32a of the cap member 32 and protrude outside. A gap between the take-out groove 32a and the terminal 70b is sealed with, for example, an instantaneous adhesive. This prevents the liquid from entering the motor 4.

  As shown in FIG. 3, the output shaft 30 is rotatably mounted on a case member 31 and a cap member 32. The left end of the output shaft 30 protrudes from the cap member 32. A serration 30a is formed there, and the mechanism mounting shaft 75 is fixed to be non-rotatable by, for example, serration coupling. The right end 30b of the output shaft 30 protrudes from the tip of the case member 31 as shown in FIG. A two-stage reduction planetary gear mechanism 40 constituting the rotation transmission mechanism 6 is attached to the protruding tip.

  As shown in FIG. 8, the mechanism mounting shaft 75 has a large-diameter first shaft portion 75a having a circular cross section on the base end side, and a chamfered portion 75c parallel to each other, and a smaller diameter than the first shaft portion 75a. The second shaft portion 75b and a third shaft portion 75d having a circular cross section and a smaller diameter than the second shaft portion 75b. Further, a larger-diameter bearing support portion 75e is provided on the base end side. The bearing support portion 75e is rotatably supported by a bearing 24 (see FIG. 3) attached to the bulging portion 27.

[Counter configuration]
The counter 5 is provided for controlling the motor 4 while displaying the water depth of the device attached to the tip of the fishing line. As shown in FIG. 1, the counter 5 includes a water depth display unit 98 composed of a liquid crystal display for displaying the water depth data LX and the shelf position of the device on the basis of two criteria from the water surface and from the bottom, and a water depth display unit. An operation key unit 99 composed of a plurality of switches arranged around 98 is provided.

  As shown in FIG. 12, the operation key section 99 includes a shelf memo button TB for shelf memos arranged on the right and left sides of the water depth display section 98, and a fast winding button for fast winding that rotates the spool 3 at the highest speed. It has HB, menu button MB arranged side by side on the lower side of water depth display section 98, and decision button DB. The shelf memo button TB is a button for setting the device water depth when operated as a shelf position. The fast winding button HB is a button that is used when the spool 3 is rotated in the winding direction at a high speed when collecting the device. The menu button MB is a button used for selecting a display item in the water depth display unit 98. The decision button DB is a button for confirming and setting the selection result. Further, when the decision button DB is pressed and held for 3 seconds or longer, for example, a zero set process in which the water depth data LX at that time is set as the reference position of the water depth 0 can be performed. Thereafter, the water depth data LX is displayed with the yarn length from the set reference position. In addition, the angler usually presses the enter button and sets it to 0 when the device reaches the sea surface. Further, a thread winding learning mode for learning the relationship between the spool rotation speed and the thread length can be entered by simultaneously pressing the shelf memo button TB and the fast winding button HB at a water depth of 6 m or less.

  Further, as shown in FIG. 12, a reel control unit 100 including a water depth display unit 98 and a microcomputer for controlling the motor 4 is provided inside the counter 5. The reel control unit 100 includes an operation key unit 99, an adjustment lever 101 that is swingably attached to the second side cover 15 and adjusts the spool speed and fishing line tension, and the rotation speed and rotation direction of the spool 3. For example, a spool sensor 102 that detects two Hall elements arranged side by side in the rotation direction, a power supply voltage sensor 106 that detects a voltage of a power supply connected to the electric reel, and various notification buzzers 103; The water depth display unit 98, the PWM drive circuit 105 that drives the motor 4 with a duty ratio obtained by pulse width modulation (PWM), and other input / output units are connected. The reel control unit 100 controls the speed and torque of the motor 4 according to the operation amount of the adjustment lever 101. Further, the water depth of the device attached to the tip of the fishing line is calculated from the output of the spool sensor 102 and displayed on the water depth display unit 98. Furthermore, when the bottom position and the shelf position are set by operating the operation key unit 99, the calculated depth of water coincides with the set bottom position and the shelf position, and the device reaches the shelf position or the bottom position. Then, the motor 4 is reversely rotated to operate the clutch switching mechanism 8 via the first clutch return mechanism 11 to return the clutch mechanism 7 to the clutch-on state. Thereby, the device is arranged at that position.

  In the clutch returning operation by the reverse rotation of the motor 4, the duty ratio DR (for example, the duty ratio DR = 50% when the power supply voltage is 11V) is set so that the current value becomes a constant value (for example, about 10A). I have control. When the power supply voltage PV becomes 15 volts using a lithium battery, the duty ratio is corrected to a value of 11/15, for example, so as to correct the increase of the power supply voltage PV. Thus, even when a storage battery having a higher power supply voltage than that of a lead battery such as a lithium battery or a nickel metal hydride battery is used, the current value applied to the motor 4 during reverse rotation is less likely to fluctuate.

[Configuration of rotation transmission mechanism]
As shown in FIG. 2, the rotation transmission mechanism 6 includes a handle shaft 33 on which the handle 1 is rotatably mounted, a main gear 34 that is rotatably mounted on the handle shaft 33, and a pinion gear 35 that meshes with the main gear 34. And a drag mechanism 36 disposed around the handle shaft 33 and a planetary gear mechanism 40 that decelerates the rotation of the motor 4 in two stages.

  The handle shaft 33 is rotatably supported on the fixed frame 20 by a bearing 37 and a roller clutch 38 that prohibits rotation of the handle shaft 33 in the thread drawing direction. The handle 1 is non-rotatably attached to the tip of the handle shaft 33, and the star drag 39 of the drag mechanism 36 is screwed inside.

  The rotation of the handle shaft 33 is transmitted to the main gear 34 via the drag mechanism 36. The pinion gear 35 is attached to a pinion gear shaft 47 erected on the second side cover 15 so as to be rotatable and axially movable. The pinion gear shaft 47 is disposed concentrically with the output shaft 30 of the motor 4. An engagement recess 35 a is formed at the left end of the pinion gear 35 in FIG. 2, and a tooth portion 35 b that meshes with the main gear 34 is formed at the right end. A small-diameter constricted portion 35c is formed between them. The engagement recess 35a engages with an engagement protrusion 46a formed at the tip (right end in FIG. 2) of the planetary gear mechanism 40, which will be described later, in a non-rotatable manner. The clutch mechanism 7 is composed of the engagement concave portion 35a and the engagement convex portion 46a. The pinion gear 35 is moved in the axial direction of the pinion gear shaft 47 by the clutch switching mechanism 8 engaged with the constricted portion 35c.

  The drag mechanism 36 brakes the rotation of the spool 3 in the yarn unwinding direction. The drag mechanism 36 includes a star drag 39 and a drag disk 48 in which a pressing force (drag force) on the main gear 34 is changed by the star drag 39. Mechanism.

  As shown in FIG. 3, the planetary gear mechanism 40 is engaged with the first sun gear 41 fixed to the output shaft 30 on the right side of FIG. 3 of the motor 4 and the first sun gear 41, for example, at equal intervals on the circumference. Three first planetary gears 43 arranged, a first carrier 45 rotatably supporting the first planetary gear 43, a second sun gear 42 fixed to the first carrier 45, and a second sun gear 42 For example, it includes three second planetary gears 44 that are arranged at regular intervals on the circumference, for example, and a second carrier 46 that rotatably supports the second planetary gear 44. The first planetary gear 43 and the second planetary gear 44 mesh with an internal gear 3 d formed on the inner peripheral surface of the spool 3. The first carrier 45 and the second carrier 46 are cylindrical shafts, through which the output shaft 30 of the motor 4 passes. The second sun gear 42 and the second carrier 46 are provided to be rotatable relative to the output shaft 30. The second carrier 46 is rotatably mounted on the gear plate 3c. Between the second planetary gear 44 and the first carrier 45, a washer member 29 made of synthetic resin having a slippery property is mounted. When such a washer member 29 is mounted, the play of the first carrier 45 is reduced, and the noise of the planetary gear mechanism 40 can be reduced.

[Configuration of clutch mechanism]
The clutch mechanism 7 is a mechanism capable of switching the spool 3 between a yarn winding-capable state and a free-rotatable state. As shown in FIG. 2, the clutch mechanism 7 is configured by the engagement concave portion 35 a of the pinion gear 35 and the engagement convex portion 46 a of the second carrier 46 as described above. The state in which the pinion gear 35 moves to the left and engages with the engagement recess 35a and the engagement protrusion 46a of the second carrier 46 is the clutch-on state, and the separated state is the clutch-off state. In the clutch-on state, the spool 3 is in a yarn winding-capable state, and in the clutch-on state, the spool 3 is in a freely rotatable state. If the motor 4 is turned in the yarn winding direction in the clutch-off state, the frictional resistance of the planetary gear mechanism 40 is reduced. As a result, the free rotation speed of the spool 3 increases, and the device can be quickly lowered to the shelf position. This is the yarn feeding process.

[Configuration of clutch switching mechanism]
The clutch switching mechanism 8 switches the on / off state of the clutch mechanism 7. As shown in FIGS. 5 and 6, the clutch switching mechanism 8 includes a clutch operating lever 50 that is swingably mounted on the second side cover 15, and rotates around the pinion gear shaft 47 by the swing of the clutch operating lever 50. A clutch cam 51 that moves, and a clutch yoke 52 that moves in the direction of the pinion gear shaft 47 as the clutch cam 51 rotates are provided.

  The clutch operating lever 50 is swingably attached to the second side cover 15 behind and above the spool 3. The clutch operation lever 50 is swingable between a clutch-on position shown in FIG. 5 and a clutch-off position shown in FIG.

  The clutch cam 51 is a member that rotates around the pinion gear shaft 47 when the clutch operation lever 50 swings, and moves the clutch yoke 52 outward of the spool shaft by rotation. The clutch cam 51 includes a rotating portion 55 that is rotatably mounted around the pinion gear shaft 47, a first projecting portion 56a that extends from the rotating portion 55 toward the clutch operation lever 50, and a front side from the rotating portion 55. It has a second projecting portion 56 b that extends, a third projecting portion 56 c that extends rearward from the rotating portion 55, and a pair of cam protrusions 57 a and 57 b that are formed of inclined cams formed on the side surfaces of the rotating portion 55. Yes. At both ends of the clutch yoke 52 facing the cam protrusions 57a and 57b, cam receivers (not shown) that ride on the cam protrusions 57a and 57b are formed.

  The rotating portion 55 is formed in a ring shape and is disposed between the clutch yoke 52 and the fixed frame 20. The rotating part 55 is rotatably supported by the fixed frame 20.

  The first projecting portion 56 a extends upward and rearward from the rotating portion 55, and the tip is divided into two portions and is engaged with the clutch operation lever 50. The first protrusion 56 a is provided to rotate the clutch cam 51 in response to the swing of the clutch operation lever 50.

  The second projecting portion 56 b is provided for interlocking the clutch switching mechanism 8 with the second clutch return mechanism 12. The second projecting portion 56b extends forward of the reel, and extends outward of the ratchet wheel 62 of the first one-way clutch 9 disposed between the main gear 34 and the fixed frame 20. A first toggle spring 65 made of a torsion coil spring is engaged with the second protrusion 56b. The other end of the first toggle spring 65 is locked to the fixed frame 20. By the first toggle spring 65, the clutch cam 51 is held at the clutch-on position shown in FIG. 5 and the clutch-off position shown in FIG. A swing shaft 51a is mounted on the second protrusion 56b, and an engagement member 61 of the second clutch return mechanism 12 is swingably mounted on the swing shaft 51a.

  The third projecting portion 56 c is provided for interlocking the clutch switching mechanism 8 with the first clutch return mechanism 11. The third protrusion 56c extends rearward and downward of the reel, and the first clutch return mechanism 11 is connected to the tip of the third protrusion 56c.

  The cam protrusions 57a and 57b are provided to press the clutch yoke 52 outward in the spool axial direction. That is, when the clutch cam 51 rotates from the clutch-on position shown in FIG. 5 to the clutch-off position shown in FIG. 6, the clutch yoke 52 rides on the cam protrusions 57a and 57b and moves outward in the spool axial direction (see FIG. 5 and FIG. 6). Move forward).

  The clutch yoke 52 is disposed on the outer peripheral side of the pinion gear shaft 47, and is supported by two guide shafts 53 so as to be movable in parallel with the axis of the pinion gear shaft 47. The clutch yoke 52 has a semicircular arc engaging portion 52a that engages with the constricted portion 35c of the pinion gear 35 at the center thereof. In addition, a coil spring 54 is disposed in a compressed state on the outer periphery of the guide shaft 53 that supports the clutch yoke 52 and between the clutch yoke 52 and the second side cover 15. (Second side plate 17 side) is biased.

  In such a configuration, in a normal state, the pinion gear 35 is located at the inner clutch engagement position, and the engagement concave portion 35a and the engagement convex portion 46a of the second carrier 46 are engaged with each other to provide a clutch mechanism. 7 is in a clutch-on state. On the other hand, when the pinion gear 35 is moved outward by the clutch yoke 52, the engagement concave portion 35a and the engagement convex portion 46a are disengaged, and the clutch is turned off.

[Configuration of the first one-way clutch]
The first one-way clutch 9 is provided to prevent the handle 1 from rotating when the motor 4 is driven, by prohibiting the handle shaft 33 from rotating in the yarn drawing direction. The first one-way clutch 9 includes a ratchet wheel 62 that is non-rotatably mounted on the handle shaft 33, a ratchet pawl 71, and a clamping member 72.

  The ratchet wheel 62 is non-rotatably mounted on the handle shaft 33 between the main gear 34 and the fixed frame 20. On the outer peripheral side of the ratchet wheel 62, serrated ratchet teeth 62a are formed.

  The ratchet pawl 71 is rotatably mounted on the second side plate 17. The clamping member 72 is attached to the tip of the ratchet pawl 71 and can clamp the outer peripheral surface of the ratchet wheel 62. Due to the friction between the pinching member 72 and the ratchet wheel 62, the ratchet pawl 71 is separated to a position where it does not interfere with the ratchet teeth 62a when the ratchet wheel 62 rotates clockwise (yarn winding direction). The ratchet pawl 71 does not come into contact with each other at the time of rotation, and noise can be reduced. On the other hand, when rotating counterclockwise (yarn feeding direction), the ratchet pawl 71 is pulled to a position where it interferes with the ratchet teeth 62a, and rotation in the yarn drawing direction is prohibited. In this electric reel, in addition to the first one-way clutch 9, a roller clutch 38 that instantaneously inhibits the reverse rotation of the handle shaft 33 is disposed between the second side cover 15 and the handle shaft 33. Yes.

[Configuration of the second one-way clutch]
The second one-way clutch 10 is provided to prevent the planetary gear mechanism 40 from operating due to the reverse rotation of the motor 4 when the handle 1 is operated. As shown in FIGS. 7 and 8, the second one-way clutch 10 has a claw wheel 81 (an example of a ratchet wheel) that is non-rotatably mounted on the second shaft portion 75 b of the mechanism mounting shaft 75, and a claw wheel 81. A swinging claw 82 (an example of a ratchet claw) that contacts and separates, a torsion coil spring 83 (an example of a first biasing member) that biases the swinging claw 82 toward the claw wheel 81, and the motor 4. A claw control mechanism 84 (an example of a cam mechanism) that controls the swing claw 82 during normal rotation in the yarn winding direction.

  The claw wheel 81 has an oval hole 81b that engages with a chamfered portion 75c formed in the second shaft portion 75b of the mechanism mounting shaft 75 in a non-rotatable manner at the center. Moreover, it has two claw parts 81a (an example of a tooth | gear part) formed in the outer periphery so that it might protrude in radial direction.

  The swinging claw 82 has a proximal end mounted on a swinging shaft 80 erected on the bulging portion 27 of the first side plate 16 so as to be swingable. A protruding portion 82a is formed at the tip of the swinging claw 82 so as to protrude to the back side in FIG. The protruding portion 82a contacts the claw portion 81a of the claw wheel 81 to prevent reverse rotation of the claw wheel 81 (the output shaft 30), and contacts a silent cam 85 (to be described later) of the claw control mechanism 84 to dodge the claw portion 81a. It is provided to swing the swinging claw 82 to the position.

  The swinging claw 82 is always disposed at the reverse rotation prohibition position where it can come into contact with the claw portion 81a shown in FIGS. 9 and 10, but as shown in FIG. 11, the claw portion 81a of the claw wheel 81 is rotated during the forward rotation of the motor 4. Rocks clockwise slightly to the position where it is The swinging claw 82 is formed with a notch 82b for dodging an advance / retreat member 96 described later.

  The claw control mechanism 84 is a mechanism for swinging the swing claw 82 to the reverse rotation permission position side to a position where the claw portion 81a of the claw wheel 81 is displaced when the motor 4 rotates forward. The claw control mechanism 84 is rotatably mounted on the first shaft portion 75a of the mechanism mounting shaft 75 and has a silent arc-shaped pressing portion 85a for pressing the swinging claw 82 toward the reverse rotation prohibiting position on the outer periphery. A cam 85 and a rotation restricting portion 86 for restricting the rotation range of the silent cam 85 are provided.

  The silent cam 85 includes a metal cam body 85b (an example of a ring portion) having a pressing portion 85a (an example of a protruding portion) on the outer periphery and a non-rotatably mounted cam body 85b on the outer periphery of the cam body 85b. A C-shaped spring member 85c (an example of a second urging member) that presses against the first shaft portion 75a of the mechanism mounting shaft 75, and an annular member 85e (an example of a cylindrical member) that is mounted on the outer periphery of the spring member 85c. And have.

  The cam body 85b has a storage groove 85d in which the spring member 85c is stored in a non-rotatable manner on the end surface and a locking piece 86a described later, and is frictionally engaged with the mechanism mounting shaft 75 via the spring member 85c. The mechanism mounting shaft 75 rotates in the same direction in conjunction with the rotation of the mechanism mounting shaft 75, and the mechanism mounting shaft 75 can rotate even if the rotation of the silent cam 85 is restricted by the rotation restricting portion 86. The pressing portion 85a is formed in an arc shape on the outer peripheral surface of the cam main body portion 85b so as to press the swinging claw 82 in a pressing range wider than the interval between projections 91b of the pressing member 91 described later.

  As shown in FIGS. 8, 16, and 17, the cam body 85b is rotatably mounted on the outer peripheral surface of the mechanism mounting shaft 75, and is divided into first divided pieces 85f that are divided at intervals in the circumferential direction. It is a metal ring member having the second divided piece 85g. The first divided piece 85f and the second divided piece 85g are divided so that the center is located at a position that passes through the axis of the mechanism mounting shaft 75 when the first divided piece 85f and the second divided piece 85g are attached. Yes. A pressing portion 85a protrudes from the outer peripheral portion of the front end of the first divided piece 85f, and the center is positioned at a position eccentric from the center of the pressing portion 85a in the outer peripheral portion of the front end of the second divided piece 85g. A protruding locking piece 86a is provided. A storage groove 85d to which the spring member 85c is attached is formed along the circumferential direction on the outer peripheral portion of the rear end of the first divided piece 85f and the second divided piece 85g. The spring member 85c is mounted such that the outer peripheral portion is positioned inside the storage groove 85d, and the first split piece 85f and the second split piece 85g sandwich the mechanism mounting shaft 75 by the pressure contact force of the spring member 85c. Is engaged by friction. Further, an annular member 85e is press-fitted into the outer peripheral portion of the rear end of the first divided piece 85f and the second divided piece 85g at the outer peripheral portion of the spring member 85c, thereby preventing the spring member 85c from coming off.

  The rotation restricting portion 86 includes a locking piece 86 a that is integrally formed so as to protrude in the radial direction on the cam main body portion 85 b of the silent cam 85, and a locking piece that is provided on the outer surface of the bulging portion 27 inside the cover member 28. It has a pair of boss portions 86b and 86c to which 86a is locked. The boss portion 86b is a restricting portion on the reverse rotation (counterclockwise in FIG. 7) side, and the boss portion 86c is a restricting portion on the normal rotation (clockwise in FIG. 7) side. As shown in FIG. 9, when the silent cam 85 is arranged so that the locking piece 86 a contacts the reverse boss 86 b, the swinging claw 82 can contact the claw wheel 81 and prohibit the reverse rotation of the motor 4. become. As shown in FIG. 11, when the silent cam 85 is disposed so that the locking piece 86a contacts the forward boss 86c, the swinging claw 82 is pressed by the pressing portion 85a, and the pressing member 91 is pressed. It is arrange | positioned in the position which dodges the nail | claw part 81a of the claw wheel 81 in the range wider than the space | interval of the projection part 91b. A washer 87 is mounted between the silent cam 85 and the claw wheel 81.

[Configuration of first clutch return mechanism]
The first clutch return mechanism 11 returns the clutch mechanism 7 from the clutch-off state to the clutch-on state via the clutch switching mechanism 8 by the reverse rotation of the motor 4. As shown in FIGS. 5 to 8, the first clutch return mechanism 11 is mounted on the mechanism mounting shaft 75 side by side with the ratchet wheel 81, and rotates together with at least the reverse rotation of the motor 4 and the clutch switching mechanism 8. And an interlocking mechanism 89 that operates.

  The pressing mechanism 88 is arranged on the third shaft portion 75 d of the mechanism mounting shaft 75 side by side with the claw wheel 81, and rotates according to the reverse rotation of the motor 4. The pressing mechanism 88 includes a roller clutch 90 mounted on the third shaft portion 75d and a pressing member 91 mounted non-rotatably on the outer peripheral side of the roller clutch 90. The roller clutch 90 is an outer ring idle type one-way clutch having an outer ring 90a and a plurality of rollers 90b housed in the outer ring 90a. The inner ring is integrated with the third shaft portion 75d of the mechanism mounting shaft 75. The roller clutch 90 transmits only the reverse rotation of the motor 4 to the pressing member 91. Here, the roller clutch 90 is attached to the pressing member 91 when the interlocking mechanism 89 is close to the pressing member 91 and the motor 4 is rotated forward in the clutch-off state. This is to prevent a problem from occurring even if contact is made.

  When the motor 4 rotates in the reverse direction, the rotation of the pressing member 91 is transmitted via the roller clutch 90 and rotates. The pressing member 91 includes, for example, five cylindrical portions 91a that are non-rotatably attached to the outer ring 90a of the roller clutch 90, and are formed on the outer peripheral side of the cylindrical portion 91a in the radial direction and spaced apart in the circumferential direction. And a protrusion 91b. The protrusion 91b is a protrusion formed in, for example, a sawtooth shape capable of pressing the interlocking mechanism 89. The number of protrusions 91 b of the pressing member 91 is not limited to five, but it is better that the number of protrusions 91 b is larger than the number of claw portions 81 a of the claw wheel 81.

  The interlocking mechanism 89 operates in conjunction with the operation of the clutch switching mechanism 8. When the clutch mechanism 7 is switched to the clutch-off state by the clutch switching mechanism 8, the interlocking mechanism 89 can be pressed from a locking position where pressing by the pressing mechanism 88 is impossible. Move to the pressing position. In addition, the interlock mechanism 89 is pressed by the pressing mechanism 88 and returns to the locking position when the motor 4 is rotated in the reverse state.

  The interlocking mechanism 89 includes a connecting shaft 93 that passes through the first side plate 16 and the second side plate 17 and is rotatably mounted on the first side plate 16 and the second side plate 17. The first lever member 94 (see FIG. 5) and the second lever member 95 that are non-rotatably attached to both ends of the connecting shaft 93, and the advance / retreat member 96 connected to the tip of the second lever member 95 are provided. Yes.

The connecting shaft 93 is a shaft member that is rotatably attached to the first side plate 16 and the second side plate 17 and has one end protruding outward of the fixed frame 20 and the other end protruding outward of the first side plate 16. Chamfered portions 93a and 93b that are parallel to each other for mounting the first lever member 94 and the second lever member 95 in a non-rotatable manner are formed at the protruding ends of the connecting shaft 93. The first lever member 94 has a base The end is a member that is non-rotatably attached to the chamfered portion 93 a of the connecting shaft 93 on the fixed frame 20 side. The distal end of the first lever member 94 is locked to the distal end of the third projecting portion 56c of the clutch cam 51 constituting the clutch switching mechanism 8 so as to be rotatable and movable for a predetermined distance. Thereby, the rotation of the clutch cam 51 is transmitted to the first clutch return mechanism 11, and the return operation of the first clutch return mechanism 11 is transmitted to the clutch cam 51 and the clutch switching mechanism 8 can be operated.

  The second lever member 95 is a member whose base end is non-rotatably mounted on the chamfered portion 93 b of the connecting shaft 93 on the first side plate 16 side. The distal end of the second lever member 95 is locked to the proximal end of the advance / retreat member 96 so as to be rotatable and movable for a predetermined distance. As a result, the advance / retreat member 96 advances and retracts in conjunction with the operation of the clutch switching mechanism 8, and the clutch changeover mechanism 8 operates in the clutch-off direction by the backward operation of the advance / retreat member 96.

  The advancing / retracting member 96 is guided by the pair of guide portions 22 and 23 formed on the bulging portion 27 so as to be linearly movable toward the swinging claw 82 and the pressing mechanism 88. The advancing / retracting member 96 is a plate-like member in which the second lever member 95 is connected to the base end so as to be rotatable and movable within a predetermined range. The advancing / retracting member 96 has a contact portion 96a bent from the tip toward the pressing member 91. The front surface of the contact portion 96 a is a pressing surface 96 b that is pressed by the pressing member 91. The advancing / retracting member 96 is straight between the pressing position shown in FIG. 10 where the contact portion 96a can be pressed by the pressing member 91 and the locking position shown in FIG. 9 where the pressing portion 91 cannot be pressed by the pressing member 91. Freely movable. Specifically, when the clutch switching mechanism 8 moves from the clutch-off position to the clutch-on position side, the first lever member 94 and the second lever member 95 swing and the advance / retreat member 96 advances to the pressing position, and the motor 4 When it is pressed by the pressing member 91 due to the reverse rotation, it moves backward to the locking position. As a result, the clutch cam 51 rotates in the clutch-on direction via the first lever member 94 and the second lever member 95, the clutch operation lever 50 returns to the clutch-on position, and the clutch mechanism 7 enters the clutch-on state.

[Configuration of second clutch return mechanism]
The second clutch return mechanism 12 returns the clutch cam 51 disposed at the clutch-off position to the clutch-on position in accordance with the rotation of the handle 1 in the yarn winding direction, and returns the clutch mechanism 7 to the clutch-on state. The cam 51 returns the clutch operation lever 50 from the clutch-off position to the clutch-on position. The second clutch return mechanism 12 urges the engagement member 61, the ratchet wheel 62 having ratchet teeth 62a formed on the outer periphery thereof, and the engagement member 61 to be distributed toward the engagement position and the non-engagement position. And a second toggle spring 66. As described above, the engaging member 61 is swingably supported by the second projecting portion 56b of the clutch cam 51, and has a first protrusion 61a that engages with the ratchet teeth 62a of the ratchet wheel 62, and a first protrusion 61a. The first protrusion 61a has a second protrusion 61b extending to the left in FIG.

  The first protrusion 61a is bent toward the outside of the ratchet wheel 62, and the second protrusion 61b is bent to the opposite side to the fixed frame 20 side. The fixed frame 20 is formed with a deformed trapezoidal guide protrusion 20a that engages with the second protrusion 61b. The guide protrusion 20a is provided to control the swinging direction of the engaging member 61 by engaging with the second protrusion 61b.

  When the engaging member 61 is disposed at the engaging position, the first protrusion 61a is located on the inner peripheral side from the outer periphery of the ratchet wheel 62 and can be locked to the ratchet teeth 62a, and is disposed at the non-engaging position. Then, the first protrusion 61 a is located at a position slightly separated from the outer periphery of the ratchet wheel 62. The engaging member 61 is disposed in front of and above the axis of the ratchet wheel 62. For this reason, the space on the rear side of the ratchet wheel 62 can be small as compared with the conventional example disposed behind the ratchet wheel 62. The first protrusion 61a of the engagement member 61 is pulled by the ratchet teeth 62a and rotates from the engagement position shown in FIG. 6 to the non-engagement position shown in FIG.

  Since the level wind mechanism and the casting control mechanism have the same configuration as a conventionally known electric reel, description thereof is omitted.

[Clutch switching operation]
Next, the clutch switching operation of the electric reel will be described.

  In a normal state, the clutch yoke 52 is pushed inward in the pinion gear axial direction by the coil spring 54, whereby the pinion gear 35 is moved to the clutch-on position. In this state, the engagement concave portion 35a of the pinion gear 35 and the engagement convex portion 46a of the second carrier 46 are engaged with each other and the clutch is on.

  When putting the device, the clutch operating lever 50 is swung to the clutch-off position shown in FIG. When the clutch operating lever 50 swings from the clutch-on position shown in FIG. 5 to the clutch-off position shown in FIG. 6, the clutch cam 51 rotates counterclockwise in FIG. As a result, the clutch yoke 52 rides on the cam protrusions 57a and 57b of the clutch cam 51, and the clutch yoke 52 is moved outward in the pinion gear axial direction. Since the clutch yoke 52 is engaged with the constricted portion 35c of the pinion gear 35, the pinion gear 35 is also moved in the same direction as the clutch yoke 52 moves outward. In this state, the engagement concave portion 35a of the pinion gear 35 and the engagement convex portion 46a of the second carrier 46 are disengaged, and the clutch is turned off. In this clutch-off state, the spool 3 is in a freely rotatable state. As a result, the fishing line is unwound from the spool 3 due to the weight of the device.

  In the yarn feed mode, for example, when the feed amount exceeds a predetermined amount (for example, the water depth indication of the device is 6 m) or the rotation speed of the spool 3 exceeds the predetermined speed, the motor 4 rotates in the yarn winding direction. . Since the second carrier 46 rotates in the clutch-off state, the planetary gear mechanism 40 does not decelerate even when the motor 4 is rotated forward, but the friction between the planetary gear mechanism 40 and the spool 3 is reduced, and the spool 3 is free. Rotates in the yarn unwinding direction at a higher speed than the rotating state.

  Further, when the clutch cam 51 rotates to the clutch-off position, the engaging member 61 of the second clutch return mechanism 12 is guided by the guide protrusion 20a and swings in the clockwise direction. The spring 66 biases the ratchet wheel 62 inward. As a result, the engaging member 61 is disposed at an engaging position where the engaging member 61 is locked to the ratchet teeth 62a.

  Further, when the clutch cam 51 rotates to the clutch-off position, the advance / retreat member 96 of the interlocking mechanism 89 of the first clutch return mechanism 11 advances from the locking position shown in FIG. 9 to the pressing position shown in FIG. When the advance / retreat member 96 advances to the pressing position, the contact portion 96a is disposed at a position where the protrusion 91b of the pressing member 91 can be pressed.

  Here, when the advance / retreat member 96 moves from the released position to the locked position during the clutch-off operation, the swinging claw 82 is not changed from the reverse rotation prohibition state to the reverse rotation permission state in conjunction with the movement. It can be done with power.

  When the device is arranged on a predetermined shelf, the motor 4 is rotated in the reverse direction, the handle 1 is rotated in the yarn winding direction, or the clutch operating lever 50 is swung to the clutch-on position to stop the thread feeding of the spool 3. . In the automatic shelf stop mode, the reeling out of the spool 3 is automatically stopped at the shelf position by the reverse rotation of the motor 4.

  When the clutch mechanism 7 is turned on by rotating the motor 4 in the reverse direction, the motor 4 is slightly rotated forward before the reverse rotation. When the motor 4 is rotated slightly forward, the back surface 91c of the protrusion 91b of the pressing member 91 comes into contact with the back surface 96c of the pressing surface 96b of the contact portion 96a of the advance / retreat member 96, as shown in FIG. The rotational phase is positioned at a position where the protruding portion 91b is greatly separated from the pressing surface 96b. Further, when the motor 4 is slightly rotated forward, the silent cam 85 of the claw control mechanism 84 is rotated forward together with the motor 4 and is positioned on the forward rotation side by the rotation restricting portion 86. When the silent cam 85 rotates in the forward direction, the pressing portion 85a presses the swinging claw 82 to a position where the claw portion 81a of the claw wheel 81 is displaced. Further, when the silent cam 85 is positioned on the forward rotation side, the pressing range of the pressing portion 85a has a wider interval between the protruding portions 91b of the pressing member 91. As a result of the reverse rotation, the pressing member 91 can press the advance / retreat member 96.

  When the motor 4 is reversely rotated in this state, the first clutch return mechanism 11 returns to the clutch-on state. Specifically, when the motor 4 is reversed, as shown in FIG. 10, the pressing member 91 is reversed (clockwise rotation in FIG. 10), and any one of the five protrusions 91 b is the contact portion 96 a of the advance / retreat member 96. The pressing surface 96b is pressed, and the advance / retreat member 96 is retracted from the pressing position toward the locking position. Then, the clutch cam 51 connected to the first lever member 94 via the second lever member 95 and the connecting shaft 93 rotates clockwise in FIG. At this time, when the dead point of the first toggle spring 65 is exceeded, the clutch cam 51 returns to the clutch-on position, whereby the advance / retreat member 96 also returns to the locking position. Further, when the clutch cam 51 rotates clockwise toward the clutch on position, the clutch yoke 52 riding on the cam protrusions 57a and 57b of the clutch cam 51 descends from the cam protrusions 57a and 57b, and the coil spring 54 is attached. It moves inward in the spool axial direction by the force. As a result, the pinion gear 35 also moves inward in the spool axial direction and is disposed at the clutch-on position. When the clutch cam 51 rotates clockwise in FIG. 6, the clutch operation lever 50 locked to the first protrusion 56a also swings to the clutch-on position. Thereby, the clutch mechanism 7 can be changed from the clutch-off state to the clutch-on state without operating the clutch operation lever 50. Further, when the motor 4 rotates in the reverse direction, the silent cam 85 is regulated on the reverse side, the pressing by the pressing portion 85a is released, and the swinging claw 82 biased by the torsion coil spring 83 returns to the reverse rotation prohibiting position. 1 The one-way clutch 9 is in the reverse rotation prohibition state, and the reverse rotation of the motor 4 is prohibited.

  During the reverse rotation of the motor 4, the pressing member 91 mounted on the mechanism mounting shaft 75 via the roller clutch 90 collides with the contact portion 96 a of the advance / retreat member 96 and presses it. At this time, an impact acts on the pressing member 91, and the torque caused thereby acts on the serration 30 a of the fixed portion between the mechanism mounting shaft 75 and the output shaft 30. Since this portion has a small diameter, the force in the tangential direction increases, and if the maximum current value is applied to the motor 4 as it is, there is a possibility that the portion may idle. Therefore, in the present embodiment, the duty ratio DR is controlled so that the current value of the motor 4 is constant. As a result, the torque when the pressing member 91 collides with the advancing / retracting member 96 at the start of reverse rotation is reduced, and the drive components mounted on the output shaft 30 such as the mechanism mounting shaft 75 mounted with the pressing member 91 are less likely to idle. .

  In this embodiment, the forward rotation operation is performed before the reverse rotation. If any of the protrusions 91b of the pressing member 91 is disposed near the advance / retreat member 96 during the reverse rotation, the advance / retreat member 96 cannot be pressed with a sufficient force including the inertial force, and the clutch is turned on. The return operation may become unstable. Therefore, in the present embodiment, the motor 4 is rotated forward for a short time before the reverse rotation, and as shown in FIG. 11, the back surface 91d different from the back surface 91c of the five protrusions 91b is brought into contact with the contact portion 96a of the advance / retreat member 96. Is positioned so that the rotational phase of the pressing member 91 before reverse rotation is constant. As a result, any one of the protrusions 91b of the pressing member 91 is disposed at a position far away from the contact portion 96a of the advance / retreat member 96, so that the inertia force is greatly increased when the motor 4 is reversed. The pressing member 91 can press the advance / retreat member 96. For this reason, the interlocking mechanism 89 can be pressed by the pressing member 91 with a sufficient force including the inertial force, and the return operation can be performed reliably. The forward rotation operation of the motor 4 is an extremely short time of about 0.03 seconds to 0.1 seconds, for example, and the duty ratio is set so that the torque of the motor 4 is constant, and the power supply voltage is 11 volts. Control within a range of 10% to 30%.

  When the handle 1 is rotated in the yarn winding direction, the second clutch return mechanism 12 returns to the clutch-on state. When the handle 1 is rotated in the yarn winding direction, the handle shaft 33 rotates clockwise in FIG. Accordingly, the ratchet wheel 62 fixed to the handle shaft 33 so as not to rotate is also rotated clockwise. When the ratchet wheel 62 rotates clockwise, the first protrusion 61a of the engaging member is caught by the ratchet teeth 62a, and the engaging member 61 is pulled.

  When the engaging member 61 is pulled, the engaging member 61 is guided by the guide protrusion 20 a and swings counterclockwise. When the engaging member 61 exceeds the dead point of the second toggle spring 66, the engaging member 61 is moved to the ratchet wheel 62. Is energized outward. Then, the engaging member 61 swings outward toward the non-engaging position where the ratchet wheel 62 is not engaged.

  When the engaging member 61 is pulled, the clutch cam 51 connected to the engaging member 61 rotates clockwise in FIG. 6 and returns to the clutch-on position as described above. Thereby, also here, the clutch mechanism 7 can be changed from the clutch-off state to the clutch-on state without operating the clutch operation lever 50.

  The engagement member 61 of the second clutch return mechanism 12 is disposed on the upper front side of the handle shaft 33. The upper front position of the handle shaft 33 is an empty space when the counter 5 is provided. When the engaging member 61 is provided in this vacant space, the bulge of the reel main body can be reduced as compared with a configuration in which the engaging member is disposed behind and below the handle shaft as in the prior art.

  The first clutch return mechanism 11 and the second clutch return mechanism 12 are configured such that, even when the clutch operating lever 50 is operated from the clutch-off position to the clutch-on position, the advance / retreat member 96 returns to the locking position and the engagement member 61 Needless to say, it returns to the disengaged position.

  When the fish is caught in the clutch in the clutch-on state, the spool 3 is rotated in the line winding direction by the rotation drive of the handle 1 or the motor 4, and the fishing line is wound up.

  At the time of manual winding, rotation of the handle 1 in the yarn winding direction (clockwise rotation in FIG. 5) is accelerated and transmitted to the spool 3 via the handle shaft 33, the main gear 34, the pinion gear 35, and the planetary gear mechanism 40. Is done. At this time, the reverse rotation of the motor 4 (counterclockwise rotation when viewed from the right side of FIG. 3) is prohibited by the second one-way clutch 10. For this reason, the first sun gear 41 of the planetary gear mechanism 40 does not reverse, and the second planetary gear 44 and the first carrier rotate from the second carrier 46 that rotates in the yarn winding direction (clockwise rotation as viewed from the right side in FIG. 3). The rotation is transmitted to the internal gear 3d via the first planetary gear 43, and the spool 3 is driven to increase in the yarn winding direction.

  When the motor is driven, the rotation of the motor 4 that normally rotates (clockwise rotation as viewed from the right side in FIG. 3) is transmitted to the spool 3 via the planetary gear mechanism 40. At this time, the rotation of the handle shaft 33 in the yarn feeding direction (counterclockwise rotation when viewed from the right side in FIG. 3) is prohibited by the first one-way clutch 9, so that the second carrier 46 is reversely rotated (as viewed from the right side in FIG. 3). (Clockwise rotation) is prohibited. For this reason, the rotation of the decelerated second sun gear 42 is transmitted to the internal gear 3d via the second planetary gear 44, and the spool 3 is driven to decelerate.

  As shown in FIG. 11, when the motor 4 rotates in the forward direction (counterclockwise rotation in FIG. 11) in the clutch-on state, the silent cam 85 of the pawl control mechanism 84 rotates in the same direction, and the rotation restricting portion 86. Thus, the protrusion 82a of the swinging claw 82 stops at the position where the pressing portion 85a presses. At this time, since the silent cam 85 is merely frictionally engaged with the mechanism mounting shaft 75, the motor 4 rotates as it is. As a result, the swinging claw 82 is pressed by the pressing portion 85 a and swings to the reverse rotation permission position side to the position where the claw portion 81 a of the claw wheel 81 is dominated, so that the claw wheel 81 does not contact the swinging claw 82. For this reason, when the motor 4 rotates in the forward direction, the click sound due to the swinging claw 82 of the first one-way clutch 9 repeatedly contacting the claw wheel 81 is not generated, and the noise can be reduced.

  When the motor 4 rotates in the reverse direction, the silent cam 85 also rotates in the same direction, and as shown in FIG. 9, the rotation restricting portion 86 stops at a position where the pressing portion 85a is disengaged from the protruding portion 82a. The coil spring 83 is biased to return to the reverse rotation prohibited position.

  Further, when the motor 4 rotates in the forward direction in the clutch-off state as in the yarn feed mode, the silent cam 85 can also rotate in the same direction to achieve noise reduction. At this time, since the pressing member 91 is mounted on the mechanism mounting shaft 75 via the roller clutch 90 that transmits only the reverse rotation of the motor 4, the rotation of the mechanism mounting shaft 75 is not transmitted to the pressing member 91. For this reason, even if the advancing / retracting member 96 is disposed so as to be in contact with the pressing member 91 in the clutch-off state, the pressing member 91 does not press the advancing / retreating member 96, and there is no problem due to this.

[Operation of reel control unit]
Next, specific control processing performed by the reel control unit 100 will be described with reference to the control flowchart of FIG.

  When an external power source is connected to the electric reel, initial setting is performed in step S1 of FIG. In this initial setting, the count value of the spool rotation number is reset, various variables and flags are reset, and the gear position is set to the first speed. In step S2, the power supply voltage PV detected by the power supply voltage sensor 106 is captured. In step S3, it is determined whether or not the power supply voltage PV is higher than 11 volts, that is, whether or not a type of storage battery having a higher power supply voltage than the lead storage battery is connected to the reel. When a battery of a type having a high power supply voltage PV (for example, a lithium battery or a nickel metal hydride battery) is connected, the process proceeds from step S3 to step S4 and the duty ratio DR at the time of motor reverse rotation is detected as the detected power supply voltage PV. Correct accordingly. Specifically, a value obtained by multiplying the basic duty ratio DR by a value (11 / PV) obtained by dividing 11 by the power supply voltage PV is set as a new duty ratio DR. Thereby, even if the power supply voltage PV fluctuates, the current value applied to the motor 4 at the time of reverse rotation is less likely to fluctuate. In this embodiment, the power supply voltage is determined only once after the initial setting for connecting the power supply. However, the determination may be performed a plurality of times after the power supply is connected.

  In step S5, display processing is performed. In the display process, various display processes such as water depth display are performed. In step S6, it is determined whether any switch of the operation key unit 99 or the adjustment lever 101 is operated. In step S7, it is determined whether or not the spool 3 is rotating. This determination is made based on the output of the spool sensor 102. In step S8, it is determined whether or not the water depth LX calculated from the output of the spool sensor 102 is 6 m or more. In step S9, it is determined whether any other command or input has been made.

  When key input is performed by the operation key unit 99 or the adjustment lever 101, the process proceeds from step S6 to step S10, and key input processing is executed. In this key input process, when the power switch SW is operated, the forward rotation of the motor 4 is turned on / off. When the adjustment lever 101 is operated, the motor 4 is increased or decreased or the torque of the motor 4 is increased or decreased according to the accuracy of the swing. Further, when the fishing mode setting switch LF is operated, a line feed mode, a shelf stop mode, and the like are set.

  When the rotation of the spool 3 is detected, the process proceeds from step S7 to step S11. In step S11, each operation mode process described later is executed. When the water depth LX is 6 m or more, the process proceeds from step S8 to step S12. In step S12, it is determined whether or not the device stop time at the water depth LX is 6 seconds or more. In the case of 6 seconds or more, it is considered that the device has stopped the shelf, so the process proceeds to step S13 and the water depth LX is set at the shelf position M. If any other command or input is made, the process proceeds from step S9 to step S14 to execute other processes.

  In each operation mode process in step S11, it is determined in step S21 in FIG. 15 whether or not the rotation direction of the spool 3 is the yarn feeding direction. This determination is made based on which reed switch of the spool sensor 102 has issued a pulse first. When the rotation direction of the spool 3 is determined to be the yarn feeding direction, the process proceeds from step S21 to step S22. In step S22, every time the count value of the pulse output from the spool sensor 102 decreases, data indicating the relationship between the water depth and the count value stored in the reel control unit 100 is read based on the count value and the water depth LX is calculated. . This water depth is displayed in the display process of step S2.

  In step S23, it is determined whether or not the yarn feeding mode is set. In step S24, it is determined whether or not the shelf stop mode. In step S25, it is determined whether the mode is another mode. If it is not in another mode, each operation mode process is terminated and the process returns to the main routine.

  In the yarn feed mode, the process proceeds from step S23 to step S26. In step S26, it is determined whether the water depth LX is 6 m or more. In the line feed mode, the motor 4 is not normally rotated from the beginning, but waits for the fishing line to be fed to a water depth at which it can be determined that the fishing line has been reliably fed. When the water depth LX is 6 m or more, the process proceeds to step S27 and the motor 4 is rotated forward. As a result, as described above, the friction between the planetary gear mechanism 40 and the spool 3 is reduced, and the spool 3 rotates in the yarn unwinding direction at a higher speed. When the water depth LX is less than 6 m, step S27 is skipped.

  The process proceeds from step S24 for determining the shelf stop mode to step S28. In step S28, it is determined whether or not the obtained water depth LX matches the value (M-α) before the shelf position M, that is, whether the device has reached αm before the shelf. The numerical value α is a value determined in consideration of control response time, stop time, and the like, and is usually a value of 0.5 m to 1 m. The shelf position M is set by pressing the position setting switch MS when the device reaches the shelf, in addition to the above-described automatic setting by stopping for a predetermined time or more. When the mechanism reaches the numerical value (M−α), the process proceeds from step S28 to step S29. In step S29, the buzzer 103 is sounded to notify that the device is on the shelf.

  In step S30, the motor 4 is rotated forward at a duty ratio of 10% to 30% for a predetermined time. As a result, as described above, the back surface 91d of the protrusion 91b of the pressing member comes into contact with the back surface 96c of the pressing surface 96b of the contact portion 96a of the advance / retreat member 96, and the rotational phase is positioned. As a result, the protrusion 91b of the pressing member 91 and the contact portion 96a of the advance / retreat member 96 are greatly separated from each other, and the press member 91 pushes the advance / retreat member 96 in a state where the inertial force is large when the motor 4 is reversed. It becomes possible to press. For this reason, the interlocking mechanism 89 can be pressed by the pressing member 91 with a sufficient force including the inertial force, and the clutch return operation can be reliably performed.

  The silent cam 85 rotates forward until the locking piece 86a contacts the boss portion 86c together with the motor 4, and the swinging claw 82 is pressed by the pressing portion 85a of the silent cam 85 to a position where the claw portion 81a of the ratchet wheel 81 is displaced. Being away from the claw wheel. As a result, the reverse rotation of the motor 4 is permitted. At this time, since the claw wheel 81 rotates in the forward direction, even if the swinging claw 82 bites into the claw part 81a, it is separated from the claw part 81a, so that the pressing part 85a can easily press the swinging claw 82.

  In step S31, the motor 4 is reversely rotated for a predetermined time. At this time, the duty ratio DR is controlled so that the current value becomes constant. As a result, excessive torque due to impact is less likely to act on the mechanism mounting shaft 75, and the mechanism mounting shaft 75 mounted on the output shaft 30 of the motor 4 is less likely to idle. Due to the reverse rotation of the motor 4, the clutch mechanism 7 is returned to the clutch-on state by the first clutch return mechanism 11 via the clutch switching mechanism 8 in the above-described operation. As a result, the rotation of the spool in the yarn unwinding direction stops. When the motor 4 is reversed, the silent cam 85 is rotated together with the motor 4 until the locking piece 86 a comes into contact with the boss portion 86 c, the pressing by the pressing portion 85 a is released, and the urging force of the torsion coil spring 83 is used. The swinging claw 82 returns to a position where it contacts the claw portion 81a of 81. As a result, the reverse rotation of the motor 4 is prohibited by the second one-way clutch 10.

  If the water depth LX has not reached the shelf position M, steps S29 to S31 are skipped. If it is determined that the mode is another mode, the process proceeds from step S25 to step S32, and the set other mode processing is executed.

  When the rotation of the spool 3 is determined to be the yarn winding direction, the process proceeds from step S21 to step S33. In step S32, every time the count value of the spool sensor 102 increases, the data stored in the reel control unit 100 is read and the water depth LX is calculated. This water depth is displayed in the display process of step S2. In step S34, it is determined whether or not the water depth matches the ship edge stop position. If it has not been wound up to the ship edge stop position, it returns to the main routine. When the ship edge stop position is reached, the process proceeds from step S34 to step S35. In step S35, the buzzer 103 is sounded to notify that the device is on the shore. In step S36, the motor 4 is turned off. As a result, the fish is arranged at a position where it can be easily taken when the fish is caught. This ship edge stop position is set when, for example, the water depth is less than 6 m and the spool 3 is stopped for a predetermined time or more.

  In such an electric reel, the cam main body 85b constituting the silent cam 85 of the claw control mechanism 84 is formed of metal, and therefore, a wire-like question mark type spring member is used as a conventional claw control mechanism. Compared to the above, the wear resistance can be remarkably improved. Further, the cam body 85b has the first divided piece 85f and the second divided piece 85g that are divided at intervals in the circumferential direction, so that the claw control is performed by the pressure contact of the spring member 85c attached to the outer periphery. The frictional force of the mechanism 84 with respect to the mechanism mounting shaft 75 can be increased.

[Other Embodiments]
(A) In the above embodiment, the one-way clutch that prohibits the rotation of the output shaft of the electric reel motor in one direction has been described as an example. However, the present invention also applies to a one-way clutch that prohibits the reverse rotation of the spinning reel rotor, for example. Can be applied.

  (B) In the above-described embodiment, the motor 4 for rotating the spool of the electric reel is rotated forward before being reversed. However, the reverse rotation may be performed without the normal rotation before the reverse rotation. In this case, it is preferable to use a stepping motor or the like as the motor, and to stop the motor so that the claw portion 81a is farthest from the locking position of the swing claw 82.

  (C) In the above embodiment, the motor 4 is disposed in the spool 3, but the present invention can also be applied to an electric reel in which the motor 4 is disposed outside the spool 3. In this case as well, the clutch-off operation can be performed with a light force as in the above embodiment.

  (D) In the above embodiment, the cam body 85b of the silent cam 85 has the pressing portion 85a provided on the first divided piece 85f and the locking piece 86a provided on the second divided piece 85g. The shape and position of the 85a and the locking piece 86a can be set to arbitrary positions. For example, both the pressing portion 85a and the locking piece 86a are provided on one or both of the first divided piece 85f and the second divided piece 85g. Also good.

  (E) In the above embodiment, the first divided piece 85f and the second divided piece 85g are centered at a position that passes through the axis of the mechanism mounting shaft 75 when the first divided piece 85f and the second divided piece 85g are attached. However, as shown in FIG. 18, it may be divided at a position eccentric from the axis of the mechanism mounting shaft 75 toward the second divided piece 85g.

  (F) In the embodiment, the first divided piece 85f and the second divided piece 85g are pressed against the mechanism mounting shaft 75 by the C-shaped spring member 85c, but the first divided piece 85f and the second divided piece 85g are used. The means for press-contacting is not limited to this.

  (G) As shown in FIG. 19, the first one-way clutch 9 includes a metal ratchet pawl 120 and a metal first spring member 121 that biases the ratchet pawl 120 toward the ratchet wheel 62. The ratchet pawl 120 may be retained by the first spring member 121 by extending the tip of the one spring member 121 and fixing it with the bolt member 123. Further, a metal second spring member 122 that connects the back cover portion 5a made of aluminum alloy provided at the bottom portion of the counter 5 and the first spring member 121 is further provided, and is grounded from an electric component inside the counter 5. The back cover 5a may be configured to release static electricity to the handle 1. Here, the back cover 5a of the counter 5, the second spring member 122, the first spring member 121, the ratchet pawl 120, the ratchet wheel 62, the main gear 34, the handle shaft 33, and the handle 1 are electrically connected in this order. Even when the fixed frame 20 or the like is formed of a synthetic resin, static electricity can be easily released with an inexpensive configuration. In addition, the front-end | tip part of the 1st spring member 121 and the 2nd spring member 122 is bent and formed in hook shape, and the bolt-shaped part of the hook-shaped part of the 1st spring member 121 and the 2nd spring member 122 is one bolt member 123. As a result, the total number of parts can be reduced.

  (H) As shown in FIG. 20, the cover member 28 includes a first opening 28 a in which a part of the side portion is open, and a protrusion that is formed at the end of the first opening 28 a and protrudes toward the bulging portion 27. Part 28b and a second opening 28c with a part of the side opening on the opposite side of the first opening 28a across the protruding part 28b. The bulging part 27 has a tip end surface of the protruding part 28b. The rib 27a protrudes toward the cover member 28 so as to face at least a part of the end surface and the inner surface of the second opening 28c, and the lead wire 110 electrically connected to the motor 4 protrudes from the rib 27a. Wiring may be performed outside the cover member 28 through the second opening 28c from the space surrounded by the portion 28b. In this case, the lead wire 110 is guided by the rib 27a and the protruding portion 28b, so that the lead wire 110 is moved to each member such as the claw control mechanism 84, the roller clutch 90, and the pressing member 91 disposed inside the cover member 28. Contact can be prevented.

The perspective view of the electric reel by one Embodiment of this invention. FIG. The cross-sectional enlarged view of a motor mounting part. The exploded perspective view of a motor. The side view of the state which removed the side cover by the side of a handle at the time of clutch on. The side view of the state which removed the side cover by the side of a handle at the time of clutch off. The side view of the state which removed the side cover on the opposite side to the handle at the time of clutch-on. The disassembled perspective view centering on a 1st clutch return mechanism. The side surface enlarged view centering on the 1st one-way clutch and the 1st clutch return mechanism at the time of a clutch-on. The side surface enlarged view centering on the 1st one-way clutch and the 1st clutch return mechanism at the time of clutch-off. The side surface enlarged view centering on the 1st one-way clutch and the 1st clutch return mechanism at the time of motor forward rotation. The plane enlarged view of a counter. The block diagram which shows the structure of the control system of a reel. The control flowchart of the main routine of a reel control part. 7 is a control flowchart of each operation mode process of the reel control unit. The front view of a nail | claw control mechanism. The side view of the said nail | claw control mechanism. The figure equivalent to FIG. 16 of other embodiment. The figure equivalent to FIG. 5 of other embodiment. The figure equivalent to FIG. 3 of other embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Handle 2 Reel body 3 Spool 4 Motor 7 Clutch mechanism 8 Clutch switching mechanism 9 1st one way clutch 10 2nd one way clutch 11 1st clutch return mechanism 12 2nd clutch return mechanism 30 Output shaft 75 Mechanism mounting shaft 81 Claw wheel 81a Claw Part 82 Oscillating claw 84 Claw control mechanism 85 Silent cam 85a Pressing part 85b Cam body part 85c Spring member 85d Storage groove 85e Annular member 85f First divided piece 85g Second divided piece 86 Rotation restricting mechanism 86a Locking piece 86b, 86c Boss part 88 Pressing mechanism 89 Interlocking mechanism 91 Pressing member 91b Protruding part 93 Connecting shaft 94 First lever member 95 Second lever member 96 Advance / Retreat member 96a Contact part 98 Water depth display part 100 Reel control part

Claims (7)

A fishing reel one-way clutch that prohibits rotation in one direction of a rotating shaft rotatably mounted on a reel body of a fishing reel,
In conjunction with the rotating shaft, a ratchet wheel in which serrated teeth are formed on the outer periphery at intervals in the circumferential direction;
A ratchet claw that is swingably mounted on the reel body, the tip of which contacts the tooth portion and prohibits rotation of the rotating shaft in the one direction;
A first biasing member that biases the ratchet pawl in a direction in contact with the tooth portion;
A metal ring portion having a first divided piece and a second divided piece that are rotatably attached to an outer peripheral surface of the rotating shaft and divided at intervals in the circumferential direction, and an outer periphery of the ring portion that is attached to the outer periphery of the ring portion. A second urging member that presses the first divided piece and the second divided piece against the rotation shaft, and a protrusion that is provided on the outer peripheral portion of the first divided piece, and lifts the ratchet pawl away from the tooth portion. And a cam mechanism that separates the ratchet pawl from the tooth portion against the biasing force of the first biasing member in conjunction with rotation in the other direction of the rotation shaft.
One-way clutch for fishing reels with   The fishing ring one-way clutch according to claim 1, wherein the ring portion is formed along a circumferential direction of an outer peripheral portion and has an annular mounting groove on which the second urging member is mounted.   The fishing reel one-way clutch according to claim 2, wherein the second urging member is a C-shaped spring member that can be mounted in the mounting groove. The second urging member is mounted such that an outer peripheral portion is positioned inside the mounting groove,
The fishing cam one-way clutch according to claim 3, wherein the cam mechanism further includes a cylindrical member attached to an outer peripheral portion of the second urging member.   5. The fishing reel one-way clutch according to claim 1, wherein the first divided piece and the second divided piece are divided at a position passing through an axis of the rotating shaft. 6.   The fishing according to any one of claims 1 to 4, wherein the first divided piece and the second divided piece are divided at a position eccentric to the second divided piece side from the axis of the rotating shaft. One-way clutch for reels. The fishing reel is an electric reel that rotates a spool rotatably supported by the reel body by a motor,
The one-way clutch of a fishing reel according to any one of claims 1 to 6, wherein the rotating shaft is an output shaft of the motor.

Images