JP2023106872A - electric fishing reel - Google Patents

Abstract

To provide an electric fishing reel capable of enlarging a speed difference between high-speed rotation and low-speed rotation and further increasing a hoisting torque, while retaining a maximum speed.SOLUTION: An electric fishing reel comprises a first planetary gear 22 to be meshed with a first sun gear 21 non-rotatably fixed to an input shaft, a first ring gear 23 to be meshed with the first planetary gear 22, a first carrier 24 for supporting the first planetary gear 22, a second ring gear 25 provided integrally with the first carrier 24, a second planetary gear 26 to be meshed with the second ring gear 25, a second sun gear 27 fixed to an output shaft 29 and being meshed with the second planetary gear 26, and a second carrier 28 for supporting the second planetary gear 26. The second planetary gear 26 consists of a first pinion 26A to be meshed with the second ring gear 25, and a second pinion 26B to be meshed with the second sun gear 27. The electric fishing reel includes a changeover part for selectively changing over the rotation of the second carrier 28 around a motor shaft between a locked state and an unlocked state.SELECTED DRAWING: Figure 3

Description

The present invention relates to an electric fishing reel.

Conventionally, an electric reel used for fishing is equipped with a speed change mechanism for an electric reel that changes the rotation speed from a motor and transmits it to a spool for the purpose of performing a winding operation according to the fishing situation ( For example, see Patent Document 1). As such a speed change mechanism, an electric speed change device is generally known that controls the amount of current supplied to the motor to increase or decrease the motor output, thereby changing the rotational speed of the spool.

On the other hand, by turning ON/OFF a portion of the drive system of the reduction mechanism consisting of planetary gears that reduce the rotation of the motor by external operation to change the gear ratio of the meshing gears, the rotational speed of the spool can be mechanically changed. A mechanical transmission that switches between two stages of low-speed rotation and high-speed rotation is also known.

JP 2006-174825 A

However, in the transmission mechanism of the conventional electric reel as shown in the above-mentioned Patent Document 1, depending on whether the gear ratio of the meshing gears is set to a high speed state or a low speed state, torque may be insufficient at low speed rotation, The high-speed winding performance was degraded. That is, it is required to obtain high-torque and high-speed winding performance. For example, in the case of a system in which the sun gear is fixed, although the motor does not stop when switching, it is difficult to increase the difference in speed between high-speed and low-speed rotation. There was a problem that the goal of speed could not be achieved.

The present invention has been made in consideration of such circumstances, and its object is to increase the speed difference between high-speed rotation and low-speed rotation, and to increase the hoisting torque while maintaining the maximum speed. To provide an electric reel for fishing.

(1) An electric fishing reel according to the present invention is an electric fishing reel provided with a speed change mechanism for switching the rotation speed of a spool between high speed rotation and low speed rotation, and the speed change mechanism is connected to a motor input side. a first power transmission gear mechanism arranged; and a second power transmission gear mechanism connected to the first power transmission gear mechanism and arranged on the motor output side, wherein the first power transmission gear mechanism has an input shaft a first sun gear non-rotatably fixed to the body, a first planetary gear meshing with the first sun gear, a first ring gear fixed to the reel body and meshing with the first planetary gear, and the first planetary gear a first carrier that supports the second power transmission gear mechanism, the second power transmission gear mechanism including: a second ring gear integrally provided with the first carrier; a second planetary gear meshing with the second ring gear; a second sun gear that is fixed to a shaft and meshes with the second planetary gear; and a second carrier that supports the second planetary gear, the second planetary gear being a pair of pinions that mesh with each other; The pair of pinions consists of a first pinion that meshes with the second ring gear and a second pinion that meshes with the second sun gear, and the rotation of the second carrier about the motor shaft is fixed or released. It is characterized in that a switching unit for selectively switching is provided.

According to the electric fishing reel of the present invention, the second planetary gear supported by the second carrier in the second power transmission gear mechanism is a double pinion, one of which the first pinion meshes with the second ring gear, and the other of which meshes with the second ring gear. The second pinion meshes with the second sun gear, and the second carrier can be switched between a rotatable state and a non-rotatable state by the switching portion. Thereby, when the second carrier is fixed by the switching unit to be in a non-rotatable state, the rotation speed of the input shaft for rotation of the motor is reduced by the first power transmission gear mechanism, and the reduced rotation speed is It is transmitted from the transmitted second ring gear to the second planetary gear. At this time, the rotation speed of the second planetary gear increases. That is, the second planetary gear forming the double pinion rotates at a speed higher than that of the second ring gear because the second carrier is fixed so as not to rotate and does not revolve. Specifically, the second planetary gear, which forms a double pinion, transmits the rotational force from the second ring gear to the second sun gear, and the rotational speed is determined by the gear ratio due to the difference in the number of teeth between the second ring gear and the second sun gear. speed up. As a result, the rotational force of the second sun gear is transmitted to the output shaft fixed to the second sun gear at high speed without being decelerated. In the present invention, by mechanically fixing the second carrier in a non-rotatable state by the switching portion, it is possible to increase the hoisting torque while maintaining the maximum speed of high-speed rotation, thereby improving the operability of fishing. be able to.

Further, when the second carrier is made rotatable by the switching unit, the rotation speed of the input shaft for rotation of the motor is reduced by the first power transmission gear mechanism, and the reduced rotation speed is transmitted to the second carrier. It is transmitted from the 2nd ring gear to the 2nd planetary gear. At this time, the rotation speed of the second planetary gear increases. Since the second carrier is rotatable, the rotation of the first and second pinions is transmitted to the second planetary gear that constitutes the double pinion, and the second planetary gear revolves along the second ring gear. , rotate at the same rotational speed as the second ring gear. Then, the rotational force of the second planetary gear is not reduced by the second carrier, but reduced to approximately the same rotational speed and transmitted to the second sun gear meshing with the second pinion. As a result, the rotational force of the second sun gear is transmitted to the output shaft fixed to the second sun gear at low speed.
Thus, in the present invention, the speed difference between high-speed rotation and low-speed rotation can be increased by making the second planetary gear of the second power transmission gear mechanism a double pinion.

(2) The switching unit and the switching operation unit for operating the switching unit are connected using a level wind shaft of a level wind mechanism for uniformly winding the fishing line in the spool. may be

In this case, by also using the level wind shaft as the connecting shaft that connects the switching section and the switching operation section for operating the switching section, restrictions on the arrangement and shape of the connecting shaft in the electric fishing reel are eliminated. It is possible to suppress the reception and improve the space efficiency.

(3) A switching operation section for operating the switching section may be provided on a speed adjusting member of the driving motor.

In this case, since the switching operation part for operating the switching part is mounted on the speed adjusting member of the drive motor, it is possible to achieve commonality and improve space efficiency.

According to the electric fishing reel of the present invention, the speed difference between high-speed rotation and low-speed rotation can be increased, and the hoisting torque can be increased while maintaining the maximum speed.

1 is a partially omitted perspective view showing the overall configuration of an electric reel according to an embodiment of the present invention; FIG. 1 is a longitudinal sectional view of a transmission mechanism provided with a motor; FIG. FIG. 3 is an enlarged view of a main part of the transmission mechanism shown in FIG. 2; It is a perspective view which shows the structure of a stopper fixing base. It is the perspective view which looked at the transmission mechanism shown in FIG. 2 from the diagonal left. FIG. 6 is a view taken along the line AA shown in FIG. 5; FIG. 6 is a cross-sectional view taken along line BB shown in FIG. 5 and is a cross-sectional perspective view of the transmission mechanism; FIG. 3 is a perspective view showing the relationship between a transmission mechanism, a transmission switching mechanism, and a spool; FIG. 3 is a partially cutaway perspective view showing the configuration of the shift switching mechanism; FIG. 3 is a perspective view showing the configuration of a shift change operation switch of the shift change mechanism; FIG. 2 is a schematic diagram that simplifies rotational force transmission paths in high-speed rotation and low-speed rotation; FIG. 5 is a diagram showing an example of changes in the number of revolutions of the first planetary gear and the second planetary gear during high-speed rotation by the speed change mechanism; FIG. 5 is a diagram showing an example of changes in the number of rotations of the first planetary gear and the second planetary gear during low-speed rotation by the speed change mechanism;

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of an electric fishing reel according to the present invention will be described below with reference to the drawings. In addition, in each drawing, the scale of each component may be appropriately changed as necessary in order to make each component visible.

As shown in FIGS. 1 and 2, the electric fishing reel of this embodiment (hereinafter simply referred to as the electric reel 1) is driven by electric power supplied from an external power source and used as a hand-wound dual-bearing reel. It has a power supply inside.

The electric reel 1 includes a reel body 10 that can be attached to a fishing rod, a handle (not shown) attached to the reel body 10 so as to be rotatable about a handle shaft 14 , and a handle shaft 14 parallel to the reel body 10 . A spool 3 which is rotatable around an axis and on which a fishing line (not shown) is wound, a motor 4 which is provided in the reel body 10 and which transmits rotational driving force to the spool 3, and a connection state in which the spool 3 and the handle are connected and disconnected. It comprises a clutch mechanism 5 capable of switching between disengaged states, and a speed change mechanism 20 (see FIG. 2) that decelerates the rotational driving force of the motor 4 and transmits it to the spool 3 . The torque of the handle is directly transmitted to the spool 3 when the clutch mechanism 5 is clutched on.

Here, in the present embodiment, the handle shaft 14, the rotation shaft of the spool 3, and the motor rotation shaft 41 (motor shaft O, see FIG. 2) of the motor 4 are provided in parallel with each other. , and a direction perpendicular to the left-right direction X1 and along the direction in which the fishing line wound around the spool 3 is let out is defined as the front-rear direction X2. Further, in the front-rear direction X2, the direction in which the fishing line is paid out from the spool 3 is defined as the front, and the opposite direction is defined as the rear. Note that FIG. 1 is a perspective view of the electric reel 1 as seen obliquely from above.

(reel body)
The reel body 10 includes a body frame 11, a cover (not shown) that covers a part of the body frame 11, and a liquid crystal display located above the body frame 11 and capable of displaying the water depth of a tackle that can be attached to the tip of a fishing line. and a water depth display unit 17 having

The body frame 11 is, for example, an integrally formed member made of synthetic resin or metal. The body frame 11 has a right side plate 11A and a left side plate 11B arranged at a predetermined interval in the left-right direction X1, and a plurality of connecting members 11C connecting the right side plate 11A and the left side plate 11B. The right cover is integrally formed with the right side plate 11A so as to cover the outside of the right side plate 11A. The left cover is fixed to the left side plate 11B so as to cover the outside of the left side plate 11B. A space is formed between the right side plate 11A and the right side cover to accommodate various mechanisms to be described later.
The ends of a spool rotating shaft (not shown) of the spool 3 are rotatably supported on the right side plate 11A and the left side plate 11B.

The connecting member 11C has a plate shape and connects the lower portions of the right side plate 11A and the left side plate 11B. One of the connecting members 11C is provided with a fishing rod attachment portion 15 for attachment to a fishing rod at a substantially central portion in the left-right direction X1.
The plurality of connecting members 11C are plate-shaped members integrally formed with the right side plate 11A and the left side plate 11B, and connect the right side plate 11A and the left side plate 11B at three points of the upper part, the lower part and the rear part of the reel body 10. there is By providing such a connecting member 11C, even if a large load is applied to the reel body 10, deformation such as deflection is unlikely to occur, and a decrease in winding efficiency is suppressed. A rod mounting leg is fixed to the lower connecting member 11C, and the rear connecting member 11C is equipped with a synthetic resin thumb rest for holding the reel together with the fishing rod.

When viewed from the side, the right side plate 11A and the right cover have a substantially elliptical shape that bulges outward in the axial direction around the mounting portion of the main gear shaft (not shown). The left plate 11B and the left cover have a circular shape when viewed from the side.
The right cover covers the right side plate 11A with a predetermined accommodation space, and is screwed, for example, to the outer edge of the right side plate 11A. The left cover covers the left side plate 11B with a predetermined accommodation space, and is screwed, for example, to the outer edge of the left side plate 11B.

(spool)
The spool 3 is rotatably provided between the right side plate 11A and the left side plate 11B via bearings (not shown). The spool 3 includes a rotatable cylindrical bobbin trunk portion 32 and flange portions 33 formed at both ends of the bobbin trunk portion 32 and expanding in diameter outward in the radial direction. The spool 3 is arranged so that its rotation center is parallel to the output shaft 29 and the motor rotation shaft 41 shown in FIG. there is A drive gear 34 (see FIG. 8) that transmits power to an output shaft 29 of a transmission mechanism 20 (described later) is non-rotatably fitted to one end of the spool 3 .

When the motor 4 is driven and the motor rotating shaft 41 is rotated, the spool 3 is rotationally driven from the output shaft 29 (described later) of the transmission mechanism 20 through the spool driving mechanism (driving gear 34, etc.). , and the clutch mechanism 5 driven by the clutch operating member 50 is interlocked. That is, the rotational force of the motor 4 is changed by the speed change mechanism 20 to rotate the spool 3 .

(clutch mechanism)
The clutch mechanism 5 can be switched between a clutch-on state in which rotation of the handle can be transmitted to the spool 3 and a clutch-off state in which rotation of the handle can not be transmitted to the spool 3 by operating the clutch operating member 50 . At the clutch-on position, the rotation of the pinion gear is transmitted to the spool 3, the clutch is turned on, and the pinion gear and the spool 3 can rotate integrally. At the clutch-off position, the rotation of the pinion gear is not transmitted to the spool 3, so the clutch is off and the spool 3 can rotate freely.

(Clutch operating member)
The clutch operation member 50 is for switching the clutch mechanism 5 between a clutch-on state and a clutch-off state, as shown in FIG. The clutch operating member 50 is provided at the rear portion of the reel body 10 between the right side plate 11A and the left side plate 11B so as to be movable in directions approaching and separating from the fishing rod mounting portion 15. .

(Spool drive mechanism)
The spool driving mechanism described above drives the spool 3 in the line winding direction, and generates a drag force (not shown) on the spool 3 during winding to prevent the fishing line from being cut.
The drag is provided coaxially with the handle shaft 14 between the handle arm of the handle and the right cover. The spool drive mechanism includes the motor 4, whose rotation in the line winding direction is prohibited by a reverse rotation preventing portion in the form of a roller clutch 24A, which will be described later, and the rotation of the motor 4, which is decelerated and transmitted to the spool 3, and the rotation of the handle. and a rotation transmission mechanism that accelerates and transmits to the spool 3.

(motor)
As shown in FIG. 1, the motor 4 is arranged in front of the spool 3 (see FIG. 1) in the front portion of the electric reel 1 and housed in a cylindrical motor housing 40 (see FIG. 2). The motor 4 has a motor rotating shaft 41 , a motor body 42 having a housing, and a motor case 43 that houses the motor body 42 . Note that the laminated core (coil) of the motor 4 is omitted in FIG.
The rotational force of the motor rotating shaft 41 of the motor 4 is transmitted to the output shaft 29 connected to the spool 3 via the transmission mechanism 20 which will be described later. That is, the output shaft 29 is rotationally driven by obtaining rotational force from the motor 4 .

As shown in FIG. 2, the motor rotating shaft 41 passes through the center of the motor main body 42 in the direction of the motor shaft O, and includes a shaft tip portion 41a at one end (left side of the paper surface) and the other end (right side of the paper surface) of the motor rotating shaft 41. are rotatably supported by the motor case 43 via bearings 45 . The motor 4 is closed inside a motor case 43 .
Here, in the motor shaft O, the shaft distal end portion 41a side of the motor rotating shaft 41 is defined as the distal end side, and the shaft proximal end portion 41b side is defined as the proximal end side.

A first sun gear 21, which will be described later, is fixed to the shaft tip portion 41a of the motor rotating shaft 41 in a non-rotatable state. A carrier bearing portion 245 that rotatably supports the first carrier 24 is provided between the shaft tip portion 41 a of the motor rotating shaft 41 that protrudes further from the first sun gear 21 and the inner peripheral surface of the first carrier 24 . It is Furthermore, the tip of the motor rotating shaft 41 is connected to the output shaft 29 via a bearing. In other words, the motor rotating shaft 41 and the output shaft 29 are not integral but rotate at different rotational speeds.

(transmission mechanism)
As shown in FIG. 3, the transmission mechanism 20 decelerates the rotational driving force of the motor 4 and transmits it to the spool 3, thereby switching the rotational speed of the spool 3 (see FIG. 1) between high speed rotation and low speed rotation. is.
The transmission mechanism 20 includes a first power transmission gear mechanism 20A arranged on the motor input side, and a second power transmission gear mechanism 20B connected to the first power transmission gear mechanism 20A and arranged on the motor output side. there is

The first power transmission gear mechanism 20A includes a first sun gear 21 fixed to the motor rotation shaft 41 which is the input shaft, a first planetary gear 22 meshing with the first sun gear 21, and a first power transmission gear mechanism fixed to the reel body 10. It has a first ring gear 23 that meshes with the planetary gears 22 and a first carrier 24 that supports the first planetary gears 22 .

The first sun gear 21 is coaxially fixed to the shaft tip portion 41 a of the motor rotating shaft 41 . Three first planetary gears 22 mesh with the first sun gear 21 .

One end 221a of each planetary gear support shaft 221 of the first planetary gear 22 is supported by the first carrier 24 . These first planetary gears 22 are rotatably provided around planetary gear support shafts 221 via bearings 223 . Also, these three first planetary gears 22 mesh with the inner peripheral gear 231 of the first ring gear 23 .

The first ring gear 23 is provided coaxially with the motor rotation shaft 41 and has an inner peripheral gear 231 that meshes with the three first planetary gears 22 on the inner peripheral surface of the ring. The first ring gear 23 is non-rotatably fitted to the motor housing 40 (see FIG. 1). Accordingly, the first planetary gears 22 are rotated by the rotation of the first sun gear 21 and circulated along the inner peripheral gear 231 .

The first carrier 24 supports the planetary gear support shafts 221 of the three first planetary gears 22, and rotates the motor rotating shaft 41 as the first planetary gears 22 move around along the first ring gear 23 with which the first planetary gears 22 mesh. It rotates around the center and transmits rotational driving force to the second ring gear 25 .
The first carrier 24 includes a support wall 241 , a tubular portion 242 and a flange portion 243 to form a truncated tubular shape. The first carrier 24 is arranged such that a support wall 241 forming a disk-shaped top wall faces the motor 4 side, and the center of the support wall 241 is coaxial with the motor rotation shaft 41 .

The support wall 241 is provided with a shaft hole 241 a in the center, and the shaft hole 241 a is rotatably supported with respect to the motor rotation shaft 41 via a carrier bearing portion 245 . The first carrier 24 is rotated at a speed different from that of the first sun gear 21 . The support wall 241 supports the planetary gear support shafts 221 of the three first planetary gears 22 . The planetary gear support shafts 221 are arranged at equal intervals in the circumferential direction of the circular support wall 241 . The first planetary gears 22 supported by the planetary gear support shaft 221 are supported around the first sun gear 21 at regular intervals. The tubular portion 242 extends leftward from the outer peripheral edge of the support wall 241 and is fitted with a tubular body to which the output shaft 29 is fitted. The flange portion 243 has a ring shape when viewed in the axial direction, and protrudes radially outward from the entire circumference of the left end portion of the tubular portion 242 . The outer peripheral portion of the flange portion 243 is integrally connected to the second ring gear 25 which will be described later. That is, the rotation of the first carrier 24 is transmitted to the second ring gear 25 at the same rotational speed.

As shown in FIGS. 2 and 3, the roller clutch 24A is housed in a state of being press-fitted into the first carrier 24, and is configured to transmit power in one direction between the first carrier 24 and the output shaft 29. It is That is, the roller clutch 24A is configured to unidirectionally transmit power between the motor rotating shaft 41 and the output shaft 29 .
When the output shaft 29 slows down due to the load applied by the rotation of the spool 3 in the fishing line payout direction, power is transmitted to the output shaft 29 and the second sun gear 27 via the roller clutch 24A. As a result, the spool 3 does not rotate in the fishing line payout direction. On the other hand, when the spool 3 rotates in the fishing line winding direction, the roller clutch 24</b>A does not transmit power between the first carrier 24 and the output shaft 29 . As a result, the spool 3 rotates in the fishing line winding direction.

The reverse rotation prevention in the form of roller clutch 246 will now be described. As shown in FIGS. 3 and 4, the left side surface 23b of the first ring gear 23 is provided with a stopper fixing base 44. As shown in FIGS. The stopper fixing base 44 has a ring shape with an inner diameter smaller than that of the first ring gear 23 and is fitted to the outside of the cylindrical portion 242 of the first carrier 24 . A rotatable stopper claw 441 is provided on the left surface 44 a of the stopper fixing base 44 . The stopper claw 441 engages with the outer peripheral surface of the cylindrical portion 242 of the first carrier 24 when it rotates toward the inner space side of the stopper fixing base 44 , so that it can rotate integrally with the first carrier 24 . By providing the stopper fixing base 44, the movement of the first ring gear 23 in the left-right direction X1 is restricted. Three concave portions 44c are formed along the outer diameter of the first planetary gear 22 so that the tooth tips of the three first planetary gears 22 do not interfere with each other. By providing the concave portion 44c in this manner, the thickness of the stopper fixing base 44 can be ensured, so that the stopper claw 441 can be incorporated into the left surface 44a.

As shown in FIGS. 3 and 5 to 7, the second power transmission gear mechanism 20B includes a second ring gear 25 provided integrally with the first carrier 24 and a plurality of sets (here, a second planetary gear 26, a second sun gear 27 fixed to the output shaft and meshing with the second planetary gear 26, and a second carrier 28 supporting the second planetary gear 26. . Note that the laminated core (coil) of the motor 4 is omitted in FIG.

The second sun gear 27 is coaxially fixed to the shaft intermediate portion 29b of the output shaft 29 in a non-rotatable state. Three sets of second planetary gears 26 mesh with the second sun gear 27 .

The second ring gear 25 is provided coaxially with the output shaft 29 (the same applies to the motor rotation shaft 41), and has an inner peripheral gear 251 that meshes with the three sets of second planetary gears 26 on the inner peripheral surface of the ring. The front end portion of the second ring gear 25 is integrally fixed to the outer peripheral portion of the flange portion 243 of the first carrier 24 in a non-rotatable state. As a result, the second planetary gears 26 are rotated along the inner peripheral gear 251 while rotating.

Both ends of each planetary gear support shaft 261 of the second planetary gear 26 are supported by the second carrier 28 . These second planetary gears 26 are rotatably provided around planetary gear support shafts 261 via bearings 263 . Also, these three sets of second planetary gears 26 mesh with the inner peripheral gear 251 of the second ring gear 25 .

The second planetary gear 26 is composed of a pair of pinions 26A and 26B that mesh with each other. The pair of pinions consists of a first pinion 26A meshing with the second sun gear 27 and a second pinion 26B meshing with the second ring gear 25. As shown in FIG. The first pinion 26A and the second pinion 26B are set to have the same outer diameter (same gear ratio).

The second carrier 28 supports the planetary gear support shafts 261 of the first pinions 26A and the second pinions 26B of the three sets of second planetary gears 26, and the first pinions 26A of the respective second planetary gears 26 mesh with each other. Rotational driving force is transmitted to the second sun gear 27 as it revolves around the output shaft 29 along the second ring gear 25 . The second carrier 28 is rotated at a speed different from that of the second sun gear 27 .

As shown in FIG. 3 , the second carrier 28 has a pair of support walls 281 and 282 and a tubular portion 283 . The second carrier 28 has a pair of disk-shaped support walls 281 and 282 facing the motor 4 side (first power transmission gear mechanism 20A side), and the centers of the pair of support walls 281 and 282 are coaxial with the output shaft 29. are arranged so that

The first support wall 281 and the second support wall 282 are each formed in a ring shape when viewed from the axial direction. The first support wall 281 is provided at the front end of the tubular portion 283 . The second support wall 282 is fixed to the first support wall 281 via the planetary gear support shaft 261 and is arranged in parallel to the front of the first support wall 281 with a space therebetween. The first support wall 281 and the second support wall 282 are integrally connected by six planetary gear support shafts 261 .

A second planetary gear 26 is arranged between the first support wall 281 and the second support wall 282 . A set of two planetary gear support shafts 261 are arranged at equal intervals in the circumferential direction of each of the circular first support wall 281 and the circular second support wall 282 . The second planetary gears 26 supported by the planetary gear support shaft 261 are supported around the second sun gear 27 at regular intervals. The second planetary gears 26 (first pinion 26A, second pinion 26B) are rotatably supported by bearings 263 on each planetary gear support shaft 261 . The tubular portion 283 extends rearward from the inner peripheral edge of the first support wall 281 and is rotatably provided by bearings 291 and 292 interposed between the tubular portion 283 and the output shaft 29 .
Here, the output shaft 29 protrudes from a ring plate 61 to be described later and transmits rotation to the spool 3 .

(Speed changeover mechanism)
As shown in FIGS. 3, 8 and 9, the transmission mechanism 20 according to this embodiment has a transmission switching mechanism 6 that switches the rotation of the second carrier 28 between high speed rotation and low speed rotation. That is, the transmission mechanism 20 rotates at a high speed when the second carrier 28 is fixed and stops rotating, and rotates at a low speed when the second carrier 28 is unlocked and is rotatable.

The gear changeover mechanism 6 includes a ring plate 61 which is non-rotatably fitted in the distal end portion of the tubular portion 283 of the second carrier 28 and has ratchet pawl teeth 61a (see FIG. 8) notched on the outer peripheral surface thereof. , a switching stopper 62 (switching portion) that can be locked by meshing with the ratchet pawl teeth 61a; (switching operation portion, see FIG. 8), and a connecting shaft 64 that connects the switching stopper 62 and the shift switching operation switch 63 .

The ring plate 61 is provided coaxially with the second carrier 28 and integrally rotatable together with the second carrier 28 . When the switching stopper 62 engages with the ratchet pawl tooth 61a, the rotation of the second carrier 28 together with the ring plate 61 is stopped. The second carrier 28 rotates together with the ring plate 61 when the switching stopper 62 is disengaged from the ratchet pawl tooth 61a.

As shown in FIGS. 8 and 10, the speed change operation switch 63 is arranged outside the right cover of the reel body 10, and is used to adjust the speed of the motor 4. It is mounted in a state of being fitted to the shape part.
The lever switch 46 is arranged in front of the right side plate 11A (see FIG. 1) on the handle side and is rotatable within a predetermined range of rotation angle. A change in the resistance value of the potentiometer due to the rotation of the lever switch 46 is input to a control unit (not shown) of the reel body 10 . The motor output of the motor 4 can be continuously increased or decreased from the motor stop state to a high output value according to the operation amount of the lever switch 46 .

The shift change operation switch 63 is of a rotary type and can be selectively switched between a locked position and a released position. The shift change operation switch 63 is fixed to one end 64a of the connecting shaft 64 at a portion spaced radially outward from the center of rotation.
Alternatively, the shift switching operation switch 63 may be provided with a notch, for example, and the switching mode (rotational speed of the motor 4) of the transmission mechanism 20 may be displayed (for example, high-speed rotation, low-speed rotation, etc.) from the notch. good.

A switching cam 66 projecting radially outward of the connecting shaft 64 is fixed to the other end 64 b of the connecting shaft 64 .
Here, the connecting shaft 64 of this embodiment commonly uses the level wind shaft of the level wind mechanism for uniformly winding the fishing line in the spool 3 . It should be noted that the connecting shaft of the speed change switching mechanism 6 may be provided separately from the level wind shaft.

As shown in FIGS. 8 and 9, the switching stopper 62 is arranged outside the ring plate 61 and supported by a fixed plate 65 so as to be rotatable around a rotation center axis (rotational axis 62a) parallel to the output shaft 29. there is The fixed plate 65 is a disc-shaped member fixed to the left side plate 11B of the reel body 10 . The switching stopper 62 has a ratchet pawl portion 621 that engages with the ratchet pawl tooth 61a on one side of the rotating shaft 62a, and a pressed portion 622 that faces the rotating direction of the switching stopper 62 on the other side. The switching stopper 62 is held by the ring plate 61 by being biased in a direction in which the ratchet pawl portion 621 is engaged with the ratchet pawl teeth 61 a by, for example, a spring member (not shown).
The pushed-in portion 622 is pushed in when the switching cam 66 provided on the connecting shaft 64 is rotated by the speed change operation switch 63 .

The switching stopper 62 is at a position where the switching cam 66 is separated from the pushed-in portion 622 when the speed change operation switch 63 is in one position (high speed mode in this case), and the ratchet pawl portion 621 is engaged with the ratchet pawl tooth 61a. Then, the ring plate 61 is fixed. That is, the second carrier 28 is fixed together with the ring plate 61 (unrotatable state), and the output shaft 29 rotates at high speed.

The switching stopper 62 is pushed in the rotational direction by the switching cam 66 whose push-in portion 622 rotates when the speed change operation switch 63 is in the other position (here, low speed mode), and the ratchet pawl portion 621 is pushed in the direction of rotation. The ring plate 61 becomes rotatable after being removed from the pawl teeth 61a. That is, the second carrier 28 becomes rotatable together with the ring plate 61, and the output shaft 29 rotates at a low speed.

Next, the operation of the transmission mechanism 20 of the electric reel 1 configured as described above will be described in detail with reference to the drawings. Specifically, the transmission mechanism 20 can be switched between high-speed rotation and low-speed rotation, and the operation in the case of high-speed rotation and the operation in the case of low-speed rotation will be described.
FIG. 11 is a simplified diagram of the rotational force transmission path K (K1, K2) in high-speed rotation and low-speed rotation. The rotational force transmission path K becomes the same first transmission path (K1) for both high-speed rotation and low-speed rotation under no load, and the second transmission path K2 for low-speed rotation under load.

First, the case of high-speed rotation will be described.
As shown in FIGS. 8 and 9, the speed change operation switch 63 is manually switched to the high speed rotation mode. At this time, the switching stopper 62 is at a position where the switching cam 66 is separated from the pressed portion 622, the ratchet pawl portion 621 is engaged with the ratchet pawl tooth 61a, and the ring plate 61 is fixed. That is, the second carrier 28 is fixed together with the ring plate 61 (unrotatable state).

As shown in FIGS. 3 and 11, in the case of no load, when the motor 4 is rotationally driven and the motor rotating shaft 41 rotates, in the first power transmission gear mechanism 20A, the first power transmission gear mechanism 20A fixed to the motor rotating shaft 41 rotates. 1 sun gear 21 rotates at the same rotational speed as motor rotating shaft 41 . The rotation of the first sun gear 21 is transmitted to the three first planetary gears 22 meshing with the first sun gear 21, and the first planetary gears 22 rotate on their own axes, and the internal teeth of the non-rotatable first ring gear 23 rotate. Engage and revolve. The first carrier 24 supporting the three first planetary gears 22 also rotates as the first planetary gears 22 revolve. That is, the rotational force of the motor rotating shaft 41 is reduced and transmitted to the first carrier 24 that supports the three first planetary gears 22 .

Next, the second ring gear 25 provided integrally with the first carrier 24 rotates at the same speed as the first carrier 24 in the second power transmission gear mechanism 20B. The rotational force of the second ring gear 25 is transmitted to the second planetary gear 26 composed of three double pinions that mesh with the inner peripheral gear 251 of the second ring gear 25 . Specifically, in the second planetary gear 26, a first pinion 26A and a second pinion 26B meshing with the second ring gear 25 rotate. At this time, the rotational speed of the first pinion 26A and the second pinion 26B increases from the rotational speed of the second ring gear 25 to a high speed.

Here, in the case of high-speed rotation, the second planetary gear 26 does not revolve because the second carrier 28 is in a non-rotatable and fixed state. That is, since the first pinion 26A and the second pinion 26B mesh with the same number of teeth, the rotation speed of the second pinion 26B is the same as that of the first pinion 26A and is faster than the rotation speed of the second ring gear 25. Rotate with the The second planetary gear 26, which forms a double pinion, transmits the rotational force from the second ring gear 25 to the second sun gear 27, and the rotational speed is controlled by the gear ratio due to the difference in the number of teeth between the second ring gear 25 and the second sun gear 27. speed up. As a result, the rotational force of the second sun gear 27 is transmitted to the output shaft 29 fixed to the second sun gear 27 without being decelerated. In this way, the rotational force of the motor rotating shaft 41 is reduced by the first power transmission gear mechanism 20A and then output to the output shaft 29 by high-speed rotation accelerated by the second power transmission gear mechanism 20B. That is, in FIG. 11, the transmission path of rotational force in the first power transmission gear mechanism 20A and the second power transmission gear mechanism 20B during high-speed rotation is the first transmission path K1.
Since the speed of the second sun gear 27 is also accelerated when rotating at high speed under load, the roller clutch 24A idles and becomes the first transmission path K1.

FIG. 12 shows an example of changes in the number of revolutions of the first planetary gear 22 and the second planetary gear 26 during high-speed rotation by the transmission mechanism 20 . In FIG. 12, the horizontal axis is the radial distance from the motor shaft, the 0 side is the motor shaft, and the vertical axis is the number of revolutions (rpm).
In the first planetary gear 22 indicated by the dotted line in FIG. 12, the symbol P1 is the input rotation speed (=approximately 38000 rpm) of the motor rotating shaft 41 (first sun gear 21). Symbol P2 indicates the rotational speed (=0 rpm) of the first ring gear 23 which is fixed and cannot rotate. Reference P3 indicates the rotation speed of the first carrier 24 (=approximately 7000 rpm).

In the second planetary gear 26 indicated by the solid line in FIG. 12, the symbol P3 is the rotational speed (=approximately 7000 rpm) of the second ring gear 25 that rotates integrally with the first carrier 24 . Reference P4 indicates the rotational speed (=0 rpm) of the second carrier 28 which is fixed and cannot rotate. Symbol P5 indicates the rotation speed (=approximately 22000 rpm) of the output shaft 29 (second sun gear 27). In this way, during high-speed rotation, the rotation speed of the output shaft 29 (=approximately 22000 rpm) is lower than the input rotation speed (=approximately 38000 rpm), but the rotation speed of the first carrier 24 (=approximately 7000 rpm) is reduced. ).

Next, the case of low speed rotation will be described.
As shown in FIGS. 8 and 9, the speed change operation switch 63 is manually switched to the low speed rotation mode. At this time, the switching stopper 62 is pushed in the rotational direction by the switching cam 66 whose pushed-in portion 622 rotates, and the ratchet pawl portion 621 is disengaged from the ratchet pawl tooth 61a to allow the ring plate 61 to rotate. That is, the second carrier 28 becomes rotatable together with the ring plate 61 .

As shown in FIGS. 3 and 11, in the case of no load, when the motor 4 is rotationally driven and the motor rotating shaft 41 rotates, in the first power transmission gear mechanism 20A, the first power transmission gear mechanism 20A fixed to the motor rotating shaft 41 rotates. 1 sun gear 21 rotates at the same rotational speed as motor rotating shaft 41 . The rotation of the first sun gear 21 is transmitted to the three first planetary gears 22 meshing with the first sun gear 21, and the first planetary gears 22 rotate on their own axes, and the internal teeth of the non-rotatable first ring gear 23 rotate. Engage and revolve. The first carrier 24 supporting the three first planetary gears 22 also rotates as the first planetary gears 22 revolve. That is, the rotational force of the motor rotating shaft 41 is reduced and transmitted to the first carrier 24 that supports the three first planetary gears 22 .

Next, the second ring gear 25 provided integrally with the first carrier 24 rotates at the same speed as the first carrier 24 in the second power transmission gear mechanism 20B. The rotational force of the second ring gear 25 is transmitted to the second planetary gear 26 composed of three double pinions that mesh with the inner peripheral gear 251 of the second ring gear 25 . Specifically, in the second planetary gear 26, a first pinion 26A and a second pinion that mesh with the internal teeth of the second ring gear 25 rotate. At this time, the rotational speed of the first pinion 26A and the second pinion 26B increases from the rotation speed of the second ring gear 25. As shown in FIG.

Here, in the case of low speed rotation under no load, the second carrier 28 is in a rotatable state, so the rotation of the second pinion 26B is transmitted to the second carrier 28, and the second carrier 28 rotates. do. Accordingly, the second planetary gear 26 revolves along the inner peripheral gear 251 of the second ring gear 25 . That is, the rotation of the second planetary gear 26 is transmitted to the second carrier 28 while being decelerated. Then, the rotational force of the second planetary gear 26 decelerated by the rotation of the second carrier 28 is transmitted to the second sun gear 27 from the second pinion 26B. During low-speed rotation, the second ring gear 25, the second planetary gear 26, and the second sun gear 27 all rotate at approximately the same rotational speed, and the rotational force of the motor rotating shaft 41 is transferred from the output shaft 29 to the first power transmission. It is output at a rotational speed reduced by the gear mechanism 20A. That is, in FIG. 11, the rotational force transmission path in the first power transmission gear mechanism 20A and the second power transmission gear mechanism 20B during low speed rotation and no load is the same first transmission path K1 as during high speed rotation. Thus, when the spool 3 rotates in the fishing line winding direction, the roller clutch 24A does not transmit power between the first carrier 24 and the output shaft 29, so the spool 3 rotates in the fishing line winding direction.

On the other hand, in the case of low speed rotation, when the output shaft 29 slows down due to the load applied by the rotation of the spool 3 in the fishing line payout direction, power is applied to the output shaft 29 and the second sun gear 27 via the roller clutch 24A. transmitted. That is, in FIG. 11, the second transmission path K2 is the transmission path of the torque in the first power transmission gear mechanism 20A and the second power transmission gear mechanism 20B when rotating at low speed and under load. As a result, the spool 3 does not rotate in the fishing line payout direction.
In this embodiment, the roller clutch 24A is provided between the first carrier 24 and the output shaft 29, but the roller clutch 24A may be omitted. If the roller clutch 24A were not provided, the second sun gear 27 would stop due to the load and the second carrier 28 would idle during low speed rotation.

FIG. 13 shows an example of changes in the number of revolutions of the first planetary gear 22 and the second planetary gear 26 when the speed change mechanism 20 rotates at a low speed. In FIG. 13, the horizontal axis is the radial distance from the motor shaft, the 0 side is the motor shaft, and the vertical axis is the number of revolutions (rpm).
In the first planetary gear 22 indicated by the dotted line in FIG. 13, the symbol P1 is the input rotation speed (=approximately 38000 rpm) of the motor rotation shaft 41 (first sun gear 21). Symbol P2 indicates the rotational speed (=0 rpm) of the first ring gear 23 which is fixed and cannot rotate. Reference P3 indicates the rotation speed of the first carrier 24 (=approximately 7000 rpm).

In the second planetary gear 26 indicated by the solid line in FIG. 13, the symbol P3 is the rotational speed (=approximately 7000 rpm) of the second ring gear 25 that rotates integrally with the first carrier 24 . Reference P4 indicates the number of rotations of the rotatable second carrier 28 (=approximately 7000 rpm). Symbol P5 indicates the rotation speed (=approximately 7000 rpm) of the output shaft 29 (second sun gear 27). In this way, during low-speed rotation, the rotation speed of the output shaft 29 (=approximately 7000 rpm) is much reduced than the input rotation speed (=approximately 38000 rpm), and the rotation speed of the first carrier 24 (=approximately 7000 rpm) is reduced. It can be seen that the rotational speeds are the same.

Next, the operation of the electric reel 1 configured as described above will be described in detail with reference to the drawings.

In the electric fishing reel according to this embodiment, as shown in FIG. 3, the second planetary gear 26 supported by the second carrier 28 in the second power transmission gear mechanism 20B is a double pinion, and one of the first pinions 26A. meshes with the second ring gear 25, the other second pinion 26B meshes with the second sun gear 27, and furthermore, the second carrier 28 is switched between a rotatable state and a non-rotatable state by the shift changeover mechanism 6. can be done. As a result, when the second carrier 28 is fixed by the speed change switching mechanism 6 to be in a non-rotatable state, the rotation speed of the input shaft (motor rotation shaft 41) of the rotation of the motor 4 is changed to the first power transmission gear mechanism 20A. and the reduced rotational speed is transmitted from the second ring gear 25 to the second planetary gear 26 .

At this time, the rotation speed of the second planetary gear 26 increases. Since the second carrier 28 is fixed so that the second planetary gear 26 forming a double pinion cannot rotate, the rotation of the first pinion 26A and the second pinion 26B is not transmitted, and the second planetary gear 26 revolves. Therefore, the second ring gear 25 rotates at a speed higher than that of the second ring gear 25 . The rotational force of the second planetary gear 26 is transmitted to the second sun gear 27 meshing with the second pinion 26B at substantially the same rotational speed without being decelerated by the second carrier 28 . As a result, the rotational force of the second sun gear 27 is transmitted to the output shaft 29 fixed to the second sun gear 27 at high speed without being decelerated.

As described above, in this embodiment, by mechanically fixing the second carrier 28 in a non-rotatable state by the speed change mechanism 6, the hoisting torque can be increased while maintaining the maximum speed of high-speed rotation. , can improve the operability of fishing.

Further, when the second carrier 28 is made rotatable by the gear changeover mechanism 6, the rotation speed of the input shaft (motor rotation shaft 41) of the rotation of the motor 4 is reduced by the first power transmission gear mechanism 20A, The reduced rotational speed is transmitted from the second ring gear 25 to the second planetary gear 26 . At this time, the rotation speed of the second planetary gear 26 increases. Since the second carrier 28 is rotatable in the second planetary gear 26 forming a double pinion, the rotation of the first pinion 26A and the second pinion 26B is transmitted, and the second planetary gear 26 is rotated by the second ring gear 25. Since it revolves along , it rotates in a state equivalent to the rotation speed of the second ring gear 25 . The rotational force of the second planetary gear 26 is not decelerated by the second carrier 28, but is decelerated to substantially the same rotational speed and transmitted to the second sun gear 27 meshing with the second pinion 26B. As a result, the rotational force of the second sun gear 27 is transmitted to the output shaft 29 fixed to the second sun gear 27 at low speed.
As described above, in the present embodiment, the second planetary gear 26 of the second power transmission gear mechanism 20B is a double pinion, thereby increasing the speed difference between high-speed rotation and low-speed rotation.

In this embodiment, as shown in FIG. 8, a connecting shaft 64 that connects a switching stopper 62 of the gear switching mechanism 6 and a gear switching operation switch 63 for operating the switching stopper 62 also serves as a level wind shaft. Thus, it is possible to suppress restrictions on the arrangement and shape of the connecting shaft 64 in the electric reel 1, and to improve space efficiency.

In this embodiment, since the shift changeover operation switch 63 for operating the changeover stopper 62 is mounted near the lever switch 46 of the motor 4, space efficiency can be improved.

The electric fishing reel according to the present embodiment configured as described above can increase the speed difference between the high-speed rotation and the low-speed rotation, and can increase the hoisting torque while maintaining the maximum speed.

Although the embodiments of the electric fishing reel according to the present invention have been described above, these embodiments are presented as examples and are not intended to limit the scope of the invention. Embodiments can be implemented in various other forms, and various omissions, replacements, and modifications can be made without departing from the scope of the invention. Embodiments and modifications thereof include, for example, those that can be easily imagined by those skilled in the art, those that are substantially the same, and those within an equivalent range.

For example, in this embodiment, the switching stopper 62 (switching portion) and the speed change switching operation switch (switching operation portion) for operating the switching stopper 62 are connected as a connecting shaft 64 for uniformly winding the fishing line in the spool 3. Although the level wind shaft of the level wind mechanism is used, it is not limited to using the level wind shaft.

Further, in the present embodiment, the shift switching operation switch (switching operation portion) for operating the switching stopper 62 is provided on the lever switch 46 (speed adjusting member) of the motor 4, but the position where the switching operation portion is provided is is not limited to being shared with the speed adjusting member.

1 electric reel (electric reel for fishing)
3 spool 4 motor 5 clutch mechanism 50 clutch operating member 41 motor rotating shaft 46 lever switch (speed adjusting member)
6 transmission switching mechanism 62 switching stopper (switching portion)
63 gear change operation switch (switch operation part)
64 connecting shaft 10 reel body 20 transmission mechanism 20A first power transmission gear mechanism 20B second power transmission gear mechanism 21 first sun gear 22 first planetary gear 23 first ring gear 24 first carrier 25 second ring gear 26 second second Planetary gear 26A First pinion 26B Second pinion 27 Second sun gear 28 Second carrier 29 Output shaft

Claims (3)

An electric fishing reel equipped with a transmission mechanism for changing the rotation speed of a motor to switch the rotation speed of a spool between high speed rotation and low speed rotation,
The speed change mechanism is
a first power transmission gear mechanism disposed on the motor input side;
a second power transmission gear mechanism connected to the first power transmission gear mechanism and arranged on the motor output side;
The first power transmission gear mechanism includes a first sun gear non-rotatably fixed to the input shaft, a first planetary gear meshing with the first sun gear, and a first planetary gear fixed to the reel body and meshing with the first planetary gear. 1 ring gear and a first carrier that supports the first planetary gear,
The second power transmission gear mechanism includes a second ring gear that is integrally provided with the first carrier, a second planetary gear that meshes with the second ring gear, and a second planetary gear that is fixed to an output shaft and meshes with the second planetary gear. a second sun gear and a second carrier supporting the second planetary gear;
The second planetary gear is a pair of pinions that mesh with each other,
the pair of pinions includes a first pinion that meshes with the second ring gear and a second pinion that meshes with the second sun gear;
An electric fishing reel provided with a switching portion for selectively switching rotation of the second carrier about the motor shaft between a fixed state and a released state. The switching part and the switching operation part for operating the switching part are connected using a level wind shaft of a level wind mechanism for uniformly winding the fishing line in the spool. fishing electric reel. 3. The electric fishing reel according to claim 1, wherein a switching operation portion for operating said switching portion is provided on a speed adjusting member of a driving motor.

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