Electric fishing reel

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

[Technical Field]

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

[0002] Conventionally, electric reels used in fishing have been equipped with a speed change mechanism that changes the rotation speed from the motor and transmits it to the spool in order to perform winding operations according to the fishing conditions (see, for example, Patent Document 1). A commonly known example of such a speed change mechanism is an electric speed change device that controls the amount of current to the motor to increase or decrease motor output, thereby changing the rotation speed of the spool.

[0003] On the other hand, a mechanical transmission is also known in which the rotational speed of the spool is mechanically switched between two stages, low speed and high speed, by externally turning on / off part of the drive system of a reduction mechanism consisting of planetary gears that slows down the rotation of the motor, thereby changing the gear ratio of the meshing gears. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Application Laid-Open No. 2006-174825 Summary of the Invention [Problem to be solved by the invention]

[0005] However, in the conventional speed change mechanism of an electric reel such as that shown in Patent Document 1, depending on whether the gear ratio of the meshing gears is set to a high speed or a low speed, torque is insufficient during low-speed rotation or high-speed reeling performance is reduced. In other words, there is a demand for high torque and high-speed reeling 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 speed difference between high-speed and low-speed rotation, which poses a problem that the above-mentioned goal of high torque and high speed cannot be achieved.

[0006] The present invention was made in consideration of these circumstances, and its purpose is to provide an electric fishing reel that can increase the speed difference between high and low rotation speeds, and can increase winding torque while maintaining maximum speed. [Means for solving the problem]

[0007] (1) An electric fishing reel according to the present invention is an electric fishing reel equipped with a speed change mechanism that changes the rotation speed of a spool between high speed and low speed, the speed change mechanism comprising a first power transmission gear mechanism disposed on the motor input side, and a second power transmission gear mechanism connected to the first power transmission gear mechanism and disposed on the motor output side, the first power transmission gear mechanism comprising a first sun gear fixed to the input shaft so as not to rotate, 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 a first carrier supporting the first planetary gear, The second power transmission gear mechanism has a second ring gear integrally formed with the first carrier, a second planetary gear that meshes with the second ring gear, a second sun gear fixed to the output shaft and that meshes with the second planetary gear, and a second carrier that supports the second planetary gear, wherein the second planetary gear is a pair of pinions that mesh with each other, the pair of pinions consisting of a first pinion that meshes with the second ring gear and a second pinion that meshes with the second sun gear, and is characterized by being provided with a switching unit that selectively switches the rotation of the second carrier around the motor shaft between a fixed state and a released state.

[0008] In the electric fishing reel according to the present invention, the second planetary gear supported by the second carrier in the second power transmission gear mechanism is a double pinion, with one first pinion meshing with the second ring gear and the other second pinion meshing with the second sun gear. Furthermore, the second carrier can be switched between a rotatable state and a non-rotatable state by a switching unit. When the switching unit fixes the second carrier and sets it in a non-rotatable state, the rotational speed of the input shaft of the motor is reduced by the first power transmission gear mechanism, and the reduced rotational speed is transmitted from the second ring gear to the second planetary gear. At this time, the rotational speed of the second planetary gear increases. In other words, because the second carrier is fixed and non-rotatable, the second planetary gear forming the double pinion rotates at a speed faster than the rotational speed of the second ring gear. Specifically, the second planetary gear, which forms a double pinion, transmits rotational force from the second ring gear to the second sun gear, increasing the rotational speed according to the gear ratio determined by the difference in the number of teeth between the second ring gear and the second sun gear. 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 slowed down. In this invention, by mechanically fixing the second carrier in an unrotatable state using the switching unit, it is possible to increase the winding torque while maintaining the maximum high-speed rotation speed, thereby improving fishing operability.

[0009] Furthermore, when the switching unit enables the second carrier to rotate, the rotational speed of the motor's input shaft is reduced by the first power transmission gear mechanism, and the reduced rotational speed is transmitted from the second ring gear to the second planetary gear. At this time, the rotational speed of the second planetary gear increases. Since the second carrier is rotatable, the second planetary gear, which forms a double pinion, receives the rotation of the first and second pinions and revolves around the second ring gear, rotating at a speed equivalent to that of the second ring gear. The rotational force of the second planetary gear is not reduced by the second carrier, but is transmitted to the second sun gear meshing with the second pinion at approximately the same rotational speed. As a result, the rotational force of the second sun gear is transmitted to the output shaft fixed to the second sun gear at a low rotational speed. In this way, in the present invention, by configuring the second planetary gear of the second power transmission gear mechanism as a double pinion, it is possible to increase the speed difference between high speed rotation and low speed rotation.

[0010] (2) The switching unit and the switching operating unit for operating the switching unit may be connected using a level wind shaft of a level wind mechanism for winding the fishing line evenly around the spool.

[0011] In this case, by using the level wind shaft as the connecting shaft that connects the switching unit and the switching operating unit for operating the switching unit, it is possible to reduce restrictions on the arrangement and shape of the connecting shaft within the electric fishing reel, and to improve space efficiency.

[0012] (3) A switching operation unit for operating the switching unit may be provided on a speed adjusting member of the drive motor.

[0013] In this case, since the speed adjusting member of the drive motor is equipped with a switching operation unit for operating the switching unit, it is possible to share the same and improve space efficiency. [Effects of the Invention]

[0014] 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 winding torque can be increased while maintaining the maximum speed. [Brief explanation of the drawings]

[0015] [Figure 1] 1 is a partially omitted perspective view showing the overall configuration of an electric reel according to an embodiment of the present invention. [Figure 2] FIG. 2 is a vertical cross-sectional view of a transmission mechanism equipped with a motor. [Figure 3] FIG. 3 is an enlarged view of a main part of the speed change mechanism shown in FIG. 2. [Figure 4] FIG. 2 is a perspective view showing the configuration of a stopper fixing base. [Figure 5] FIG. 3 is a perspective view of the speed change mechanism shown in FIG. 2, seen obliquely from the left. [Figure 6] FIG. 6 is a view taken along the line AA in FIG. 5. [Figure 7] FIG. 6 is a cross-sectional view taken along line BB shown in FIG. 5, and is a cross-sectional perspective view of the speed change mechanism. [Figure 8] FIG. 2 is a perspective view showing the relationship between a speed change mechanism, a speed change switching mechanism, and a spool. [Figure 9] FIG. 2 is a partially cutaway perspective view showing the configuration of a gear changeover mechanism. [Figure 10] FIG. 4 is a perspective view showing the configuration of a gear change operation switch of the gear change mechanism. [Figure 11] 1 is a simplified schematic diagram of a rotational force transmission path at high and low rotation speeds. FIG. [Figure 12] 4 is a diagram showing an example of changes in the rotation speed of a first planetary gear and a second planetary gear during high-speed rotation by a transmission mechanism. FIG. [Figure 13] 4 is a diagram showing an example of changes in the rotation speed of the first planetary gear and the second planetary gear during low-speed rotation by the transmission mechanism. FIG. DETAILED DESCRIPTION OF THE INVENTION

[0016] Hereinafter, an embodiment of an electric fishing reel according to the present invention will be described with reference to the drawings. Note that in each drawing, the scale of each component may be changed as necessary to make each component large enough to be visible.

[0017] As shown in Figures 1 and 2, the electric fishing reel of this embodiment (hereinafter simply referred to as electric reel 1) is driven by power supplied from an external power source and has an internal power source when used as a manual dual-bearing reel.

[0018] The electric reel 1 comprises a reel body 10 that can be attached to a fishing rod, a handle (not shown) that is attached to the reel body 10 so as to be rotatable about a handle shaft 14, a spool 3 that is rotatable about an axis parallel to the handle shaft 14 with respect to the reel body 10 and around which a fishing line (not shown) is wound, a motor 4 that is provided in the reel body 10 and transmits a rotational driving force to the spool 3, a clutch mechanism 5 that can switch between a connected state that connects the spool 3 and the handle and a disconnected state that disconnects them, and a speed change mechanism 20 (see FIG. 2) that reduces the rotational driving force of the motor 4 and transmits it to the spool 3. When the clutch mechanism 5 is in the clutch-on state, the torque of the handle is transmitted directly to the spool 3.

[0019] In this 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 arranged parallel to one another, and these directions are defined as the left-right direction X1 as necessary, and a direction perpendicular to the left-right direction X1 and along the direction in which the fishing line wound on the spool 3 is let out is defined as the front-to-rear direction X2. In addition, in the front-to-rear direction X2, the direction in which the fishing line is let out from the spool 3 is defined as the front, and the opposite direction is defined as the rear, and left and right are defined from the perspective of the electric reel 1 as seen from the rear. Note that FIG. 1 is a perspective view of the electric reel 1 as seen diagonally from above and behind.

[0020] (reel body) The reel body 10 comprises a main body frame 11, a cover (not shown) that covers part of the main body frame 11, and a water depth display unit 17 located on the upper side of the main body frame 11 and having an LCD display that can display the water depth of a fishing tackle that can be attached to the end of a fishing line.

[0021] The main body frame 11 is an integrally formed member made of, for example, synthetic resin or metal. The main 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 side cover is integrally formed with the right side plate 11A so as to cover the outside of the right side plate 11A. The left side 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, which will be described later. An end of a spool rotation shaft (not shown) of the spool 3 is rotatably supported and attached to the right side plate 11A and the left side plate 11B.

[0022] The connecting members 11C are plate-shaped and connect the lower parts of the right side plate 11A and the left side plate 11B. One of the connecting members 11C has a fishing rod attachment part 15 attached to it at approximately the center in the left-right direction X1. The multiple connecting members 11C are plate-like members formed integrally with the right side plate 11A and the left side plate 11B, and connect them to the right side plate 11A and the left side plate 11B at three locations: the top, bottom, and rear of the reel body 10. By providing these connecting members 11C, deformation such as bending is less likely to occur even when a large load is applied to the reel body 10, and a decrease in winding efficiency is suppressed. A rod mounting leg is fixed to the lower connecting member 11C, and a thumb rest made of synthetic resin is attached to the rear connecting member 11C to hold the reel together with the fishing rod.

[0023] The right side plate 11A and the right side cover have a generally elliptical shape when viewed from the side, bulging outward in the axial direction from the mounting portion of the main gear shaft (not shown). The left side plate 11B and the left side cover have a circular shape when viewed from the side. The right cover covers the right side plate 11A, providing a predetermined storage space, and is fastened to the outer edge of the right side plate 11A with screws, for example. The left cover covers the left side plate 11B, providing a predetermined storage space, and is fastened to the outer edge of the left side plate 11B with screws, for example.

[0024] (spool) The spool 3 is rotatably mounted 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 32 and flanges 33 that expand radially outward at both ends of the bobbin trunk 32. The spool 3 is positioned with its center of rotation parallel to the output shaft 29 and the motor rotary shaft 41 shown in FIG. 2, and is supported separately by the right side plate 11A and the left side plate 11B via bearings so as to be rotatable together with the bobbin trunk 32. A drive gear 34 (see FIG. 8), which transmits power to the output shaft 29 of the speed change mechanism 20 (described later), is non-rotatably fitted to one end of the spool 3.

[0025] When the motor 4 is driven and the motor rotary shaft 41 is rotated, the rotational force of the motor 4 is transmitted from the output shaft 29 (described later) of the speed change mechanism 20 to the spool drive mechanism (drive gear 34, etc.), and the clutch mechanism 5, which is driven by the clutch operating member 50, is engaged. In other words, the rotational force of the motor 4 is changed in speed by the speed change mechanism 20 to rotate the spool 3.

[0026] (clutch mechanism) The clutch mechanism 5 can be switched between a clutch-on state in which the rotation of the handle can be transmitted to the spool 3 and a clutch-off state in which the rotation of the handle cannot be transmitted to the spool 3 by operating the clutch operating member 50. In the clutch-on position, the rotation of the pinion gear is transmitted to the spool 3, resulting in the clutch-on state, allowing the pinion gear and spool 3 to rotate integrally. In the clutch-off position, the rotation of the pinion gear is not transmitted to the spool 3, resulting in the clutch-off state, allowing the spool 3 to rotate freely.

[0027] (Clutch operating member) 1, the clutch operating member 50 is used to switch the clutch mechanism 5 between a clutch-on state and a clutch-off state. The clutch operating member 50 is provided at the rear of the reel body 10, between the right side plate 11A and the left side plate 11B, so as to be movable toward and away from the fishing rod attachment portion 15.

[0028] (Spool drive mechanism) The spool drive mechanism described above drives the spool 3 in the line-winding direction, and generates a drag force by a drag (not shown) on the spool 3 during winding to prevent the fishing line from breaking. The drag is mounted coaxially on 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 prevention part in the form of a roller clutch 24A (described later), and a rotation transmission mechanism that reduces the rotation of the motor 4 and transmits it to the spool 3, or increases the rotation of the handle and transmits it to the spool 3.

[0029] (Motor) As shown in Figure 1, the motor 4 is located in front of the spool 3 (see Figure 1) at the front of the electric reel 1, and is housed in a cylindrical motor housing 40 (see Figure 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 from Figure 2. 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. In other words, the output shaft 29 receives the rotational force from the motor 4 and is driven to rotate.

[0030] 2, the motor rotary shaft 41 penetrates the center of the motor body 42 in the direction of the motor axis O, and a shaft tip portion 41a at one end (left side of the drawing) of the motor rotary shaft 41 and a shaft base portion 41b at the other end (right side of the drawing) are each rotatably supported by a motor case 43 via bearings 45. The motor 4 is enclosed inside the motor case 43. Here, in the motor shaft O, the shaft tip end 41a side of the motor rotary shaft 41 is referred to as the tip side, and the shaft base end 41b side is referred to as the base side in the following description.

[0031] The first sun gear 21, which will be described later, is fixedly inserted into and non-rotatable on a shaft tip 41a of the motor rotary shaft 41. A carrier bearing 245 that rotatably supports the first carrier 24 is provided between the shaft tip 41a of the motor rotary shaft 41, which protrudes further than the first sun gear 21, and the inner circumferential surface of the first carrier 24. Furthermore, the tip of the motor rotary shaft 41 is connected to the output shaft 29 via a bearing. In other words, the motor rotary shaft 41 and the output shaft 29 do not rotate integrally but at different rotation speeds.

[0032] (Transmission mechanism) As shown in FIG. 3, the speed change mechanism 20 reduces the rotational drive 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 and low speed. The speed change 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.

[0033] The first power transmission gear mechanism 20A has a first sun gear 21 fixed to the motor rotating shaft 41, which is the input shaft, a first planetary gear 22 meshing with the first sun gear 21, a first ring gear 23 fixed to the reel body 10 and meshing with the first planetary gear 22, and a first carrier 24 supporting the first planetary gear 22.

[0034] The first sun gear 21 is coaxially fixed to a shaft tip portion 41a of the motor rotary shaft 41. The first sun gear 21 is meshed with three first planetary gears 22.

[0035] The first planetary gears 22 have one end 221a of a planetary gear support shaft 221 supported by the first carrier 24. These first planetary gears 22 are rotatable around the planetary gear support shaft 221 via bearings 223. Furthermore, these three first planetary gears 22 are in mesh with an internal gear 231 of the first ring gear 23.

[0036] The first ring gear 23 is provided coaxially with the motor rotary 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 fitted into the motor housing 40 (see FIG. 1) in a non-rotatable state. As a result, the first planetary gears 22 move around along the inner peripheral gear 231 while rotating on their own axes due to the rotation of the first sun gear 21.

[0037] The first carrier 24 supports the planetary gear support shafts 221 of the three first planetary gears 22, and rotates around the motor rotating shaft 41 as it moves around the first ring gear 23 with which the first planetary gears 22 mesh, transmitting rotational driving force to the second ring gear 25. The first carrier 24 has a cylindrical shape with a top and is made up of a support wall 241, a cylindrical portion 242, and a flange portion 243. The first carrier 24 is disposed so that the support wall 241, which forms the 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.

[0038] The support wall 241 has a shaft hole 241a formed in its center, and the shaft hole 241a is rotatably supported on the motor rotary shaft 41 via a carrier bearing portion 245. The first carrier 24 rotates at a rotation speed different from that of the first sun gear 21. The support wall 241 supports planetary gear support shafts 221 of the three first planetary gears 22. The planetary gear support shafts 221 are arranged at equal intervals around the circumferential direction of the circular support wall 241. The first planetary gears 22 supported by the planetary gear support shafts 221 are supported at equal intervals around the first sun gear 21. The cylindrical portion 242 extends leftward from the outer circumferential edge of the support wall 241 and is fitted with a cylindrical body that is fitted with the output shaft 29. The flange portion 243 is ring-shaped when viewed axially and protrudes radially outward from the entire circumference of the left end of the cylindrical portion 242. The outer periphery of the flange portion 243 is integrally connected to a 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.

[0039] 2 and 3, roller clutch 24A is housed in a press-fit state in first carrier 24 and is configured to transmit power in one direction between first carrier 24 and output shaft 29. In other words, roller clutch 24A is configured to transmit power in one direction between motor rotating shaft 41 and output shaft 29. When a load is applied due to rotation of the spool 3 in the line-releasing direction, causing the output shaft 29 to slow down, power is transmitted to the output shaft 29 and second sun gear 27 via the roller clutch 24A. This prevents the spool 3 from rotating in the line-releasing direction. On the other hand, when the spool 3 rotates in the line-reeling direction, the roller clutch 24A does not transmit power between the first carrier 24 and the output shaft 29. As a result, the spool 3 rotates in the line-reeling direction.

[0040] Here, a reverse rotation preventive portion in the form of the roller clutch 246 will be described. As shown in FIGS. 3 and 4, a stopper fixing base 44 is provided on the left side surface 23b of the first ring gear 23. The stopper fixing base 44 is ring-shaped with an inner diameter smaller than that of the first ring gear 23, and is fitted onto the outside of the tubular portion 242 of the first carrier 24. A rotatable stopper claw 441 is provided on the left side 44a of the stopper fixing base 44. When the stopper claw 441 rotates toward the interior of the stopper fixing base 44, it engages with the outer peripheral surface of the tubular portion 242 of the first carrier 24, and becomes rotatable integrally with the first carrier 24. The provision of the stopper fixing base 44 restricts movement of the first ring gear 23 in the left-right direction X1. Three recesses 44c are formed on the inner peripheral surface 44b of the stopper fixing base 44 along the outer diameter of the first planetary gear 22 so as to prevent interference with the tooth tips of the three first planetary gears 22. By providing the recesses 44c in this manner, the thickness of the stopper fixing base 44 can be ensured, and this makes it possible to incorporate the stopper claw 441 into the left surface 44a.

[0041] 3 and 5 to 7, the second power transmission gear mechanism 20B has a second ring gear 25 provided integrally with the first carrier 24, multiple sets (three sets in this case) of second planetary gears 26 that mesh with the second ring gear 25, a second sun gear 27 fixed to the output shaft and meshing with the second planetary gears 26, and a second carrier 28 that supports the second planetary gears 26. Note that the laminated core (coils) of the motor 4 is omitted from FIG. 7.

[0042] The second sun gear 27 is fixed coaxially and non-rotatably to a shaft intermediate portion 29b of the output shaft 29. The second sun gear 27 is meshed with three sets of second planetary gears .

[0043] The second ring gear 25 is provided coaxially with the output shaft 29 (as well as the motor rotary shaft 41), and has an inner peripheral gear 251 that meshes with three sets of second planetary gears 26 on the inner peripheral surface of the ring. The front end of the second ring gear 25 is integrally fixed to the outer periphery of the flange portion 243 of the first carrier 24 in a non-rotatable state. As a result, the second planetary gears 26 move orbitally along the inner peripheral gear 251 while rotating on their own axes.

[0044] The second planetary gears 26 are supported by the second carrier 28 at both ends of the planetary gear support shaft 261. These second planetary gears 26 are rotatable around the planetary gear support shaft 261 via bearings 263. Furthermore, these three sets of second planetary gears 26 are in mesh with the internal gear 251 of the second ring gear 25.

[0045] The second planetary gear 26 is composed of a pair of pinions 26A, 26B that mesh with each other. The pair of pinions consists of a first pinion 26A that meshes with the second sun gear 27 and a second pinion 26B that meshes with the second ring gear 25. The first pinion 26A and the second pinion 26B are set to have the same outer diameter (the same gear ratio).

[0046] The second carrier 28 supports the planet gear support shafts 261 of the first pinions 26A and second pinions 26B of the three sets of second planetary gears 26, and transmits rotational driving force to the second sun gear 27 as it moves around the output shaft 29 along the second ring gear 25 with which the first pinions 26A of each second planetary gear 26 mesh. The second carrier 28 rotates at a different rotation speed from that of the second sun gear 27.

[0047] 3, second carrier 28 includes a pair of support walls 281, 282 and a cylindrical portion 283. Second carrier 28 is disposed so that the pair of disk-shaped support walls 281, 282 face the motor 4 side (first power transmission gear mechanism 20A side) and the centers of the pair of support walls 281, 282 are coaxial with output shaft 29.

[0048] The first support wall 281 and the second support wall 282 are each formed in a ring shape when viewed in the axial direction. The first support wall 281 is provided at the front end of the cylindrical portion 283. The second support wall 282 is fixed to the first support wall 281 via planetary gear support shafts 261, and is disposed in front of and parallel to the first support wall 281 with a gap therebetween. The first support wall 281 and the second support wall 282 are integrally connected by six planetary gear support shafts 261.

[0049] The second planetary gear 26 is disposed between the first support wall 281 and the second support wall 282. A pair of planetary gear support shafts 261 are disposed at equal intervals in the circumferential direction of each of the circular first support wall 281 and the second support wall 282. The second planetary gears 26 supported by the planetary gear support shafts 261 are supported at equal intervals around the second sun gear 27. The second planetary gears 26 (first pinion 26A, second pinion 26B) are rotatably supported on each planetary gear support shaft 261 by a bearing 263. The cylindrical portion 283 extends rearward from the inner circumferential edge of the first support wall 281 and is rotatably provided by bearings 291 and 292 interposed between the cylindrical portion 283 and the output shaft 29. Here, the output shaft 29 projects from a ring plate 61 (described later) and transmits rotation to the spool 3.

[0050] (gear change mechanism) 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 and low speed. That is, in the transmission mechanism 20, the second carrier 28 rotates at a high speed when it is fixed and stopped from rotating, and rotates at a low speed when it is released and freely rotatable.

[0051] The gear shift switching mechanism 6 includes a ring plate 61 that is non-rotatably fitted into the tip of the cylindrical portion 283 of the second carrier 28 and has ratchet pawl teeth 61a (see Figure 8) cut out on its outer peripheral surface, a switching stopper 62 (switching unit) that can be engaged by meshing with the ratchet pawl teeth 61a, a gear shift switching operation switch 63 (switching operation unit, see Figure 8) that switches the switching stopper 62 between an engaged position and a released position with respect to the ratchet pawl teeth 61a, and a connecting shaft 64 that connects the switching stopper 62 and the gear shift switching operation switch 63.

[0052] The ring plate 61 is provided coaxially with the second carrier 28 and can rotate integrally with the second carrier 28. When the switching stopper 62 engages with the ratchet pawl teeth 61a, the rotation of the second carrier 28 is stopped together with the ring plate 61. When the switching stopper 62 disengages from the ratchet pawl teeth 61a, the second carrier 28 rotates together with the ring plate 61.

[0053] As shown in Figures 8 and 10, the speed change switch 63 is located on the outside of the right cover of the reel body 10 and is mounted in a state where it is fitted into the shaft-shaped portion of the lever switch 46 (speed adjustment member) for operating the speed adjustment of the motor 4. The lever switch 46 is located in front of the right side plate 11A (see Figure 1) on the handle side and is provided so as to be rotatable within a predetermined rotation angle range. The lever switch 46 changes the resistance value of a potentiometer as a result of rotation, and this change 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 a motor stopped state to a high output value according to the amount of operation of the lever switch 46.

[0054] The gear changeover operation switch 63 is a rotary type that can be selectively switched between a locked position and a released position. The gear changeover operation switch 63 is fixed to one end 64a of the connecting shaft 64 at a portion radially outward from the center of rotation. The speed changeover operation switch 63 may be provided with a notch, for example, and the changeover mode (rotational speed of the motor 4) by the speed change mechanism 20 may be displayed from the notch (for example, high speed rotation, low speed rotation, etc.).

[0055] A switching cam 66 that protrudes radially outward from the connecting shaft 64 is fixed to the other end 64b of the connecting shaft 64. Here, the connecting shaft 64 in this embodiment is commonly used as the level wind shaft of the level wind mechanism for winding the fishing line evenly around the spool 3. The connecting shaft of the speed changeover mechanism 6 may be provided separately from the level wind shaft.

[0056] As shown in Figures 8 and 9, the switching stopper 62 is disposed on the outside of the ring plate 61 and is supported by a fixed plate 65 so as to be rotatable about a rotation center axis (rotation axis 62a) parallel to the output shaft 29. The fixed plate 65 is a disk-shaped member fixed to the left side plate 11B of the reel body 10. The switching stopper 62 is provided with a ratchet pawl portion 621 that engages with the ratchet pawl teeth 61a on one side across the rotation axis 62a, and with a pressed portion 622 that faces in the rotation direction of the switching stopper 62 on the other side. The switching stopper 62 is biased by, for example, a spring member (not shown) in a direction in which the ratchet pawl portion 621 engages with the ratchet pawl teeth 61a, and is held by the ring plate 61. The pressed portion 622 is a portion that is pressed when the switching cam 66 provided on the connecting shaft 64 is rotated by the speed change switching operation switch 63 .

[0057] When the speed changeover operation switch 63 is in one position (high-speed mode in this case), the switching stopper 62 is in 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 teeth 61a, and the ring plate 61 is fixed. In other words, the second carrier 28 is fixed (unrotatable) together with the ring plate 61, and the output shaft 29 rotates at high speed.

[0058] Furthermore, when the speed changeover operation switch 63 is in the other position (here, low-speed mode), the pressed portion 622 of the switching stopper 62 is pushed in the rotational direction by the rotating switching cam 66, and the ratchet pawl portion 621 is disengaged from the ratchet pawl teeth 61a, allowing the ring plate 61 to rotate. In other words, the second carrier 28 becomes rotatable together with the ring plate 61, and the output shaft 29 rotates at a low speed.

[0059] Next, the operation of the speed change mechanism 20 of the electric reel 1 configured as described above will be explained in detail with reference to the drawings. Specifically, the speed change mechanism 20 is switchable 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 explained. 11 is a simplified diagram of the rotational force transmission path K (K1, K2) at high and low rotation speeds. When there is no load, the rotational force transmission path K becomes the same first transmission path (K1) at both high and low rotation speeds, and when there is a load, the low rotation speed becomes the second transmission path indicated by K2.

[0060] First, the case of high speed rotation will be described. 8 and 9, the speed changeover operation switch 63 is manually switched to the high-speed rotation mode. At this time, the switching stopper 62 is in 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 teeth 61a, and the ring plate 61 is fixed. In other words, the second carrier 28 is fixed (unrotatable) together with the ring plate 61.

[0061] 3 and 11, when there is no load, when the motor 4 is driven to rotate and the motor rotating shaft 41 rotates, the first sun gear 21 fixed to the motor rotating shaft 41 in the first power transmission gear mechanism 20A rotates at the same rotational speed as the motor rotating shaft 41. The rotation of the first sun gear 21 is then transmitted to the three first planetary gears 22 that mesh with the first sun gear 21, and the first planetary gears 22 rotate on their own axes and revolve while meshing with the internal teeth of the non-rotatable first ring gear 23. The first carrier 24 that supports the three first planetary gears 22 also rotates together with the revolution of the first planetary gears 22. In other words, 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.

[0062] Next, in the second power transmission gear mechanism 20B, the second ring gear 25, which is integral with the first carrier 24, rotates at the same speed as the first carrier 24. The rotational force of the second ring gear 25 is transmitted to the second planetary gear 26, which is made up of three double pinions meshing with the inner peripheral gear 251 of the second ring gear 25. Specifically, the second planetary gear 26 has a first pinion 26A and a second pinion 26B meshing with the second ring gear 25, which each rotate on their own axis. 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.

[0063] During high-speed rotation, the second carrier 28 is fixed and unable to rotate, so the second planetary gear 26 does not revolve. In other words, because the first pinion 26A and the second pinion 26B are meshed with each other with the same number of teeth, the second pinion 26B also rotates at the same rotational speed as the first pinion 26A, but at a speed faster than the rotational speed of the second ring gear 25. The second planetary gear 26, which forms a double pinion, transmits rotational force from the second ring gear 25 to the second sun gear 27, and the rotational speed is increased by the gear ratio determined by the difference in the number of teeth between the second ring gear 25 and the second sun gear 27. As a result, the rotational force of the second sun gear 27 is transmitted to the output shaft 29, which is fixed to the second sun gear 27, without being reduced in speed. Thus, the rotational force of the motor rotating shaft 41 is reduced in speed by the first power transmission gear mechanism 20A and then output to the output shaft 29 at a high speed increased by the second power transmission gear mechanism 20B. That is, in FIG. 11, the transmission path of the 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. Furthermore, since the second sun gear 27 also increases in speed during high-speed rotation under load, the roller clutch 24A rotates freely, forming the first transmission path K1.

[0064] Fig. 12 shows an example of changes in the rotation speed 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 represents the radial distance from the motor shaft, with the zero side representing the motor shaft, and the vertical axis represents the rotation speed (rpm). In the first planetary gear 22 indicated by the dotted line in Fig. 12, symbol P1 indicates the rotation speed (= approximately 38,000 rpm) of the input motor rotating shaft 41 (first sun gear 21). Symbol P2 indicates the rotation speed (= 0 rpm) of the fixed and unrotatable first ring gear 23. Symbol P3 indicates the rotation speed (= approximately 7,000 rpm) of the first carrier 24.

[0065] In the second planetary gear 26 indicated by the solid line in FIG. 12, symbol P3 indicates the rotation speed (= approximately 7000 rpm) of the second ring gear 25 that rotates integrally with the first carrier 24. Symbol P4 indicates the rotation speed (= 0 rpm) of the second carrier 28 that is fixed and cannot rotate. Symbol P5 indicates the rotation speed (= approximately 22000 rpm) of the output shaft 29 (second sun gear 27). As such, it can be seen that during high-speed rotation, the rotation speed (= approximately 22000 rpm) of the output shaft 29 is slower than the input rotation speed (= approximately 38000 rpm), but is faster than the rotation speed (= approximately 7000 rpm) of the first carrier 24.

[0066] Next, the case of low speed rotation will be described. 8 and 9, the speed changeover operation switch 63 is manually switched to the low-speed rotation mode. At this time, the switching stopper 62 is pushed in the rotation direction by the switching cam 66, whose pushed portion 622 rotates, and the ratchet pawl portion 621 disengages from the ratchet pawl teeth 61a, allowing the ring plate 61 to rotate. In other words, the second carrier 28 becomes rotatable together with the ring plate 61.

[0067] 3 and 11, when there is no load, when the motor 4 is driven to rotate and the motor rotating shaft 41 rotates, the first sun gear 21 fixed to the motor rotating shaft 41 in the first power transmission gear mechanism 20A rotates at the same rotational speed as the motor rotating shaft 41. The rotation of the first sun gear 21 is then transmitted to the three first planetary gears 22 that mesh with the first sun gear 21, and the first planetary gears 22 rotate on their own axes and revolve while meshing with the internal teeth of the non-rotatable first ring gear 23. The first carrier 24 that supports the three first planetary gears 22 also rotates together with the revolution of the first planetary gears 22. In other words, 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.

[0068] Next, in the second power transmission gear mechanism 20B, the second ring gear 25, which is integral with the first carrier 24, rotates at the same speed as the first carrier 24. The rotational force of the second ring gear 25 is transmitted to the second planetary gear 26, which is made up of three double pinions that mesh with the internal gear 251 of the second ring gear 25. Specifically, the second planetary gear 26 has a first pinion 26A and a second pinion that mesh with the internal teeth of the second ring gear 25, which each rotate on their own axis. 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.

[0069] Here, during low-speed rotation without load, the second carrier 28 is rotatable, so the rotation of the second pinion 26B is transmitted to the second carrier 28, causing the second carrier 28 to rotate. 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, which has been decelerated by the rotation of the second carrier 28, is transmitted from the second pinion 26B to the second sun gear 27. 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 rotation shaft 41 is output at a rotational speed obtained by decelerating the output shaft 29 by the first power transmission gear mechanism 20A. 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 as that during high-speed rotation, that is, the first transmission path K1. Thus, when the spool 3 rotates in the fishing line reeling 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 reeling direction.

[0070] On the other hand, during low-speed rotation, when a load is applied due to rotation of the spool 3 in the fishing line reeling direction, slowing down the output shaft 29, power is transmitted to the output shaft 29 and second sun gear 27 via the roller clutch 24A. In other words, in Figure 11, the transmission path for rotational force in the first power transmission gear mechanism 20A and the second power transmission gear mechanism 20B during low-speed rotation and under load is the second transmission path K2. As a result, the spool 3 does not rotate in the fishing line reeling 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 can be omitted. If the roller clutch 24A is not provided, the second sun gear 27 will stop due to the load during low-speed rotation, and the second carrier 28 will rotate freely.

[0071] Fig. 13 shows an example of changes in the rotation speed of the first planetary gear 22 and the second planetary gear 26 during low-speed rotation by the transmission mechanism 20. In Fig. 13, the horizontal axis represents the radial distance from the motor shaft, with the zero side representing the motor shaft, and the vertical axis represents the rotation speed (rpm). In the first planetary gear 22 indicated by the dotted line in Fig. 13, symbol P1 indicates the rotation speed (= approximately 38,000 rpm) of the input motor rotating shaft 41 (first sun gear 21). Symbol P2 indicates the rotation speed (= 0 rpm) of the fixed and unrotatable first ring gear 23. Symbol P3 indicates the rotation speed (= approximately 7,000 rpm) of the first carrier 24.

[0072] In the second planetary gear 26 indicated by the solid line in FIG. 13, symbol P3 denotes the rotation speed (approximately 7000 rpm) of the second ring gear 25 that rotates integrally with the first carrier 24. Symbol P4 denotes the rotation speed (approximately 7000 rpm) of the rotatable second carrier 28. Symbol P5 denotes the rotation speed (approximately 7000 rpm) of the output shaft 29 (second sun gear 27). As can be seen, during low-speed rotation, the rotation speed (approximately 7000 rpm) of the output shaft 29 is significantly reduced from the input rotation speed (approximately 38000 rpm) and is equivalent to the rotation speed (approximately 7000 rpm) of the first carrier 24.

[0073] Next, the operation of the electric reel 1 configured as above will be described in detail with reference to the drawings.

[0074] 3, in the electric fishing reel according to this embodiment, the second planetary gear 26 supported by the second carrier 28 in the second power transmission gear mechanism 20B is a double pinion, with one first pinion 26A meshing with the second ring gear 25 and the other second pinion 26B meshing with the second sun gear 27, and further, the second carrier 28 can be switched between a rotatable state and a non-rotatable state by the speed change switching mechanism 6. As a result, when the speed change switching mechanism 6 fixes the second carrier 28 to a non-rotatable state, the rotational speed of the input shaft (motor rotating shaft 41) of the motor 4 is reduced by 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.

[0075] At this time, the rotation speed of the second planetary gear 26 increases. Since the second carrier 28 is fixed and non-rotatable, the rotation of the first pinion 26A and the second pinion 26B is not transmitted to the second planetary gear 26, which forms a double pinion. The second planetary gear 26 does not revolve, and therefore rotates at a speed faster than the rotation speed of the second ring gear 25. The rotational force of the second planetary gear 26 is transmitted to the second sun gear 27, which meshes with the second pinion 26B, at approximately the same rotational speed without being slowed down by the second carrier 28. As a result, the rotational force of the second sun gear 27 is transmitted to the output shaft 29, which is fixed to the second sun gear 27, at high speed without being slowed down.

[0076] In this way, in this embodiment, by mechanically fixing the second carrier 28 in an unrotatable state using the speed changeover mechanism 6, it is possible to increase the winding torque while maintaining the maximum speed for high-speed rotation, thereby improving fishing operability.

[0077] Furthermore, when the speed change mechanism 6 enables the second carrier 28 to rotate, the rotational speed of the input shaft (motor rotating shaft 41) of the motor 4 is reduced by 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 rotational speed of the second planetary gear 26 increases. Since the second carrier 28 is rotatable, the second planetary gear 26, which forms a double pinion, receives the rotation of the first pinion 26A and the second pinion 26B and revolves around the second ring gear 25, so that the second planetary gear 26 rotates at a speed equivalent to that of the second ring gear 25. The rotational force of the second planetary gear 26 is transmitted to the second sun gear 27, which meshes with the second pinion 26B, without being reduced in speed by the second carrier 28, at substantially the same rotational speed. 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 a low rotation speed. In this manner, in this embodiment, the second planetary gear 26 of the second power transmission gear mechanism 20B is configured as a double pinion, thereby making it possible to increase the speed difference between high speed rotation and low speed rotation.

[0078] Furthermore, in this embodiment, as shown in FIG. 8, the connecting shaft 64 that connects the switching stopper 62 of the speed change mechanism 6 and the speed change operation switch 63 for operating the switching stopper 62 also serves as a level wind shaft, thereby reducing restrictions on the arrangement and shape of the connecting shaft 64 within the electric reel 1 and improving space efficiency.

[0079] In this embodiment, the speed changeover operation switch 63 for operating the changeover stopper 62 is mounted near the lever switch 46 of the motor 4, thereby improving space efficiency.

[0080] In the electric fishing reel according to this embodiment configured as described above, the speed difference between high speed rotation and low speed rotation can be increased, and the winding torque can be increased while maintaining the maximum speed.

[0081] 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. The embodiments can be embodied in various other forms, and various omissions, substitutions, and modifications can be made without departing from the spirit of the invention. The embodiments and their modifications include, for example, those that can be easily imagined by a person skilled in the art, those that are substantially the same, and those that are equivalent.

[0082] For example, in this embodiment, a level wind shaft of a level wind mechanism is used as the connecting shaft 64 for the switching stopper 62 (switching unit) and the speed change switching operation switch (switching operation unit) for operating the switching stopper 62 to wind the fishing line evenly around the spool 3, but the present invention is not limited to using a level wind shaft.

[0083] In addition, in this embodiment, a speed change switching operation switch (switching operation unit) for operating the switching stopper 62 is provided on the lever switch 46 (speed adjustment member) of the motor 4, but the position at which the switching operation unit is provided is not limited to being a configuration shared with the speed adjustment member. [Explanation of symbols]

[0084] 1 Electric reel (electric fishing reel) 3 spools 4 motors 5 Clutch mechanism 50 Clutch operating member 41 Motor rotating shaft 46 Lever switch (speed adjustment component) 6. Speed ​​change mechanism 62 Switching stopper (switching part) 63 Speed ​​changeover operation switch (changeover 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 Career 25 Second ring gear 26 Second planetary gear 26A 1st pinion 26B 2nd pinion 27 Second Sun Gear 28 Second Career 29 Output shaft

Claims

1. An electric fishing reel having a speed change mechanism that changes the rotation speed of a motor to switch the rotation speed of a spool between high speed and low speed, The transmission 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 disposed on the motor output side, the first power transmission gear mechanism includes a first sun gear fixed non-rotatably to an input shaft, a first planetary gear meshing with the first sun gear, a first ring gear fixed to a reel body and meshing with the first planetary gear, and a first carrier supporting the first planetary gear; the second power transmission gear mechanism includes a second ring gear integrally provided with the first carrier, a second planetary gear meshing with the second ring gear, a second sun gear fixed to an output shaft and meshing with the second planetary 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, The electric fishing reel is provided with a switching unit that selectively switches the rotation of the second carrier around the motor shaft between a fixed state and a released state.

2. 2. The electric fishing reel according to claim 1, wherein the switching unit and the switching operating unit for operating the switching unit are connected using a level wind shaft of a level wind mechanism for winding the fishing line evenly around the spool.

3. 3. The electric fishing reel according to claim 1, wherein a switching operation part for operating the switching part is provided on a speed adjusting member of the drive motor.

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