Electric fishing reel

Abstract

This invention can increase the speed difference between high-speed rotation and low-speed rotation, and can increase the winding torque while maintaining the highest speed. The present invention provides an electric reel for fishing tackle with the following configuration: a first planetary gear 22 meshing with a first sun gear 21 fixed to the input shaft without rotation; a first ring gear 23 meshing with the first planetary gear 22; a first carrier 24 supporting the first planetary gear 22; a second ring gear 25 integrally disposed on the first carrier 24; a second planetary gear 26 meshing with the second ring gear 25; a second sun gear 27 fixed to the output shaft 29 and meshing with the second planetary gear 26; and a second carrier 28 supporting the second planetary gear 26; the second planetary gear 26 includes a first pinion 26A meshing with the second ring gear 25 and a second pinion 26B meshing with the second sun gear 27, and the electric reel for fishing tackle is provided with a switching unit that selectively switches the rotation of the second carrier 28 around the motor shaft to a fixed state and a deactivated state.

Description

Technical Field

[0001] This invention relates to an electric reel for fishing tackle. Prior Technology

[0002] Previously, electric reels used in fishing tackle included a speed-changing mechanism (see, for example, Patent Document 1) that transmitted the rotational speed from the motor to the reel in order to perform a winding operation corresponding to the fishing conditions. Such a speed-changing mechanism is generally known as an electrical speed-changing device that controls the amount of current supplied to the motor to adjust the motor output, thereby changing the rotational speed of the reel.

[0003] On the other hand, mechanical speed-changing devices are also well known, which use external operation to open / close (ON / OFF) a portion of the drive system, including a planetary gear reduction mechanism that reduces the rotational speed of the motor, thereby changing the gear ratio of the meshing gears and mechanically switching the rotational speed of the drum between two stages: low-speed rotation and high-speed rotation. [Prior Art Documents] [Patent Documents]

[0004] [Patent Document 1] Japanese Patent Application Publication No. 2006-174825 Summary of the Invention

[0005] [Problem to be Solved by the Invention] However, in the speed change mechanism of the prior art electric winding machine as shown in Patent Document 1 above, the gear ratio of the meshing gears is set to either a high-speed state or a low-speed state, resulting in insufficient torque at low speed rotation or reduced high-speed winding performance. That is, it is required to obtain high torque and high-speed winding performance. For example, in the case of a fixed sun gear, although the motor does not stop during switching, it is difficult to make the speed difference between high-speed rotation and low-speed rotation large, resulting in the problem that the goal of high torque and high speed as described above cannot be achieved.

[0006] This invention was made in consideration of the above-mentioned circumstances, and its object is to provide an electric reel for fishing tackle that can increase the speed difference between high-speed and low-speed rotation, thereby maintaining maximum speed while increasing the winding torque. [Technical Means for Solving the Problem]

[0007] (1) The electric reel for fishing tackle of the present invention is characterized by having a speed-changing mechanism, which changes the rotational speed of the motor and switches the rotational speed of the reel to high-speed rotation and low-speed rotation. The speed-changing mechanism includes: 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 has a first sun gear fixed non-rotatably to the input shaft, 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 support for the first planetary gear. The first carrier of the reel includes a second ring gear integrally disposed on the first carrier, a second planetary gear meshing with the second ring gear, a second sun gear fixed to the 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 meshing pinions, including a first pinion meshing with the second ring gear and a second pinion meshing with the second sun gear. The electric reel for fishing tackle is provided with a switching part that selectively switches the rotation of the second carrier around the motor shaft to a fixed state and a deactivated state.

[0008] According to the electric reel for fishing tackle of the present invention, the second power transmission gear mechanism is configured such that the second planetary gear supported on the second carrier 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. This allows the second carrier to switch between a rotatable state and a non-rotatable state via a switching mechanism. When the second carrier is fixed in a non-rotatable state by the switching mechanism, the rotational speed of the motor's input shaft is reduced by the first power transmission gear mechanism and transmitted from the second ring gear, which transmits the reduced rotational speed, to the second planetary gear. At this time, the rotational speed of the second planetary gear increases. That is, because the second carrier is fixed in a non-rotatable state and does not revolve, the second planetary gear, which forms a double pinion, rotates at a faster speed than the second ring gear. Specifically, the second planetary gear, forming a double pinion, transmits rotational force from the second ring gear to the second sun gear. The rotational speed is increased by utilizing the gear ratio resulting from the difference in the number of teeth between the second ring gear and the second sun gear. In this way, the rotational force of the second sun gear is transmitted at high speed to the output shaft fixed to it without deceleration. In this invention, by mechanically fixing the second carrier in a non-rotating state using a switching unit, a greater winding torque can be achieved while maintaining the highest rotational speed, thereby improving the operability of fishing.

[0009] Furthermore, when the second carrier is rotatable via the switching unit, the rotational speed of the motor's input shaft is reduced by the first power transmission gear mechanism and transmitted from the second ring gear, which transmits the reduced rotational speed, to the second planetary gear. At this time, the rotational speed of the second planetary gear increases. Moreover, since the second carrier is rotatable, the second planetary gear, which forms a double pinion, transmits the rotation of the first and second pinions. The second planetary gear revolves around the second ring gear and thus rotates at the same speed as the second ring gear. Furthermore, the rotational force of the second planetary gear is not reduced by the second carrier but is reduced to approximately the same rotational speed as the second sun gear meshing with the second pinion. Therefore, the rotational force of the second sun gear is transmitted at a low speed to the output shaft fixed to the second sun gear. Thus, in this invention, by making the second planetary gear of the second power transmission gear mechanism a double pinion, the speed difference between high-speed and low-speed rotation can be increased.

[0010] (2) The electric reel for fishing tackle described above may also be characterized in that the switching part and the switching operation part for operating the switching part are connected by a horizontal reel shaft of a horizontal reel mechanism for uniformly winding the fishing line in the reel.

[0011] In this case, by using the horizontal reel shaft as both the connecting shaft for the switching section and the connecting shaft for operating the switching section, the constraints of the configuration and shape of the connecting shaft in the electric reel for fishing tackle can be suppressed, thereby improving space efficiency.

[0012] (3) The above-mentioned electric reel for fishing tackle may also be characterized in that the switching operation part for operating the above-mentioned switching part is provided in the speed adjustment component of the drive motor.

[0013] In this case, since the speed adjustment component of the drive motor is equipped with a switching operation unit for operating the switching unit, commonality can be achieved, thereby improving space efficiency. [Effects of the Invention]

[0014] The electric reel for fishing tackle according to the present invention can increase the speed difference between high-speed rotation and low-speed rotation, thereby enabling a greater reeling torque while maintaining the highest speed. Simple Explanation of the Diagram

[0015] Figure 1 is a partially abbreviated perspective view showing the overall structure of the electric reel according to an embodiment of the present invention. Figure 2 is a longitudinal sectional view of the speed change mechanism including the motor. Figure 3 is an enlarged view of the main parts of the speed change mechanism shown in Figure 2. Figure 4 is a perspective view showing the structure of the stop fixing platform. Figure 5 is a perspective view of the speed change mechanism shown in Figure 2 viewed from the left oblique angle. Figure 6 is a view of the AA line arrow shown in Figure 5. Figure 7 is a sectional view of the BB line shown in Figure 5, and is a sectional perspective view of the speed change mechanism. Figure 8 is a perspective view showing the relationship between the speed change mechanism, the speed change switching mechanism, and the drum. Figure 9 is a partially broken perspective view showing the structure of the speed change switching mechanism. Figure 10 is a perspective view showing the structure of the speed change operation switch of the speed change mechanism. Figure 11 is a simplified schematic diagram showing the rotational force transmission path for high-speed and low-speed rotation. Figure 12 is a diagram showing an example of the change in the rotational speed of the first planetary gear and the second planetary gear during high-speed rotation caused by the speed change mechanism. Figure 13 is an example of the change in the rotational speed of the first planetary gear and the second planetary gear during low-speed rotation caused by the transmission mechanism. Implementation

[0016] Hereinafter, embodiments of the electric reel for fishing tackle of the present invention will be described with reference to the drawings. Furthermore, in each drawing, there are cases where the scaling ratio of each component is appropriately changed as needed to make each component a visible size.

[0017] As shown in Figures 1 and 2, the electric reel for fishing tackle in this embodiment (hereinafter referred to as electric reel 1) is driven by electricity supplied from an external power source, and has an internal power source for use as a manual reel with dual bearings.

[0018] The electric reel 1 includes: a reel body 10, which can be mounted on a fishing rod; a handle (not shown), which is rotatably mounted relative to the reel body 10 about a handle shaft 14; a spool 3, which is rotatable relative to the reel body 10 about an axis parallel to the handle shaft 14 and is used to wind fishing line (not shown); a motor 4, which is disposed on the reel body 10 and transmits rotational driving force to the spool 3; a clutch mechanism 5, which can switch between an engaged state connecting the spool 3 to the handle and an disengaged state disconnecting the spool 3 from the handle; and a speed change mechanism 20 (see Figure 2), which reduces the rotational driving force of the motor 4 before transmitting it to the spool 3. The torque of the handle is directly transmitted to the spool 3 when the clutch mechanism 5 is engaged.

[0019] In this embodiment, the handle shaft 14, the rotation axis of the drum 3, and the motor rotation axis 41 (motor shaft O, see Figure 2) of the motor 4 are respectively arranged in parallel. Their directions are defined as left-right direction X1 as needed, and the direction orthogonal to left-right direction X1 and along the direction in which the fishing line is wound out of the drum 3 is defined as front-back direction X2. Furthermore, the direction in front-back direction X2 where the fishing line is wound out of the drum 3 is defined as front, and the opposite direction is defined as rear. Left and right are defined from the viewpoint of viewing the electric reel 1 from the rear. Moreover, Figure 1 is a perspective view of the electric reel 1 viewed from an upper oblique rearward angle.

[0020] (Reel body) The reel body 10 includes: a body frame 11; a cover (not shown) that covers a portion of the body frame 11; and a depth display 17 located on the upper side of the body frame 11, which has a liquid crystal display capable of displaying the depth of a device that can be mounted on the front end of the fishing line.

[0021] The main frame 11 is a component integrally formed from, for example, synthetic resin or metal. The main 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. A right side cover is integrally formed with the right side plate 11A to cover the outer side of the right side plate 11A. A left side cover is fixed to the left side plate 11B to cover the outer side of the left side plate 11B. A space is formed between the right side plate 11A and the right side cover to accommodate the various mechanisms described below. The end of the drum rotation shaft (not shown) of the drum 3 is rotatably supported and mounted on the right side plate 11A and the left side plate 11B.

[0022] The connecting component 11C is plate-shaped and connects the lower parts of the right side plate 11A and the left side plate 11B. A rod mounting part 15 for mounting the fishing rod is installed in the approximately central portion of one of the connecting components 11C in the left-right direction X1. A plurality of connecting components 11C are plate-shaped components 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: the upper part, the lower part, and the rear part of the reel body 10. By providing such connecting components 11C, even under heavy loads on the reel body 10, deformation such as bending is less likely to occur, suppressing a decrease in reeling efficiency. A rod mounting foot is fixed to the lower connecting component 11C, and a synthetic resin handle is provided on the rear connecting component 11C to hold the reel and the fishing rod together.

[0023] Viewed from the side, the right side plate 11A and the right side cover form a roughly elliptical shape that bulges outward axially from the mounting portion of the main gear shaft (not shown). Viewed from the side, the left side plate 11B and the left side cover form a circle. The right side cover has a defined receiving space to cover the right side plate 11A, for example, by being screwed to the outer edge of the right side plate 11A. The left side cover has a defined receiving space to cover the left side plate 11B, for example, by being screwed to the outer edge of the left side plate 11B.

[0024] (Spool) The spool 3 is rotatably disposed between the right side plate 11A and the left side plate 11B via bearings (not shown). The spool 3 has a rotatable cylindrical winding body 32 and flanges 33 that expand radially outward at both ends of the winding body 32. The spool 3 is arranged with its rotation center parallel to the output shaft 29 and the motor rotation shaft 41 shown in FIG2, and is supported by the right side plate 11A and the left side plate 11B respectively via bearings, allowing it to rotatably together with the winding body 32. The output shaft 29 of the speed change mechanism 20 described below and the transmission drive gear 34 (see FIG8) are engaged with one end of the spool 3 in a non-rotatable state.

[0025] When the drive motor 4 rotates the drum 3, the rotational force of the drum 3 is transmitted from the output shaft 29 of the transmission mechanism 20 (described below) via the drum drive mechanism (drive gear 34, etc.), thereby engaging the clutch mechanism 5 driven by the clutch operating member 50. That is, the rotational force of the motor 4 is used to rotate the drum 3 by changing the speed of the transmission mechanism 20.

[0026] (Clutch Mechanism) The clutch mechanism 5, through the operation of the clutch operating component 50, can be switched between an engaged state (transmitting rotation of the handle to the drum 3) and an disengaged state (not transmitting rotation of the handle to the drum 3). In the engaged position, rotation of the pinion is transmitted to the drum 3, thus achieving the engaged state, and the pinion and drum 3 can rotate together. In the disengaged position, rotation of the pinion is not transmitted to the drum 3, thus achieving the disengaged state, and the drum 3 can rotate freely.

[0027] (Clutch Operating Component) As shown in Figure 1, the clutch operating component 50 is used to switch the clutch mechanism 5 between the engaged and disengaged states. The clutch operating component 50 is located at the rear of the reel body 10, between the right side plate 11A and the left side plate 11B, and is movable relative to the fishing rod mounting portion 15 in the direction of approaching and disengaging.

[0028] (Spool Drive Mechanism) The aforementioned spool drive mechanism drives the spool 3 in the direction of line winding, and during winding, a dragging force is generated relative to the spool 3 using a dragging part (not shown) to prevent the fishing line from cutting. The dragging part is coaxially disposed between the handle arm and the right side cover of the handle shaft 14. The spool drive mechanism includes: the aforementioned motor 4, which uses a reverse rotation prevention part in the form of a roller clutch 24A to prevent rotation in the direction of line winding; and a rotation transmission mechanism that either decelerates 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 positioned in front of the electric reel 1, closer to the drum 3 (see Figure 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 with a housing, and a motor housing 43 that houses the motor body 42. Furthermore, in Figure 2, the multilayer core (coil) of the motor 4 is omitted. The rotational force of the motor rotating shaft 41 of the motor 4 is transmitted to the output shaft 29 connected to the drum 3 via the speed change mechanism 20 described below. That is, the output shaft 29 receives rotational force from the motor 4 and is driven to rotate.

[0030] As shown in Figure 2, the motor rotating shaft 41 passes through the center of the motor body 42 in the direction of motor shaft O, and the front end 41a of one end (left side of the paper) and the base end 41b of the other end (right side of the paper) of the motor rotating shaft 41 are rotatably supported on the motor housing 43 via bearings 45. The motor housing 43 of the motor 4 is closed. Here, in the motor shaft O, the front end 41a side of the motor rotating shaft 41 will be referred to as the front end side, and the base end 41b side will be referred to as the base end side.

[0031] The first sun gear 21 is fixed to the front end 41a of the motor rotating shaft 41 in a non-rotatable, inserted state. At the front end 41a of the motor rotating shaft 41, which protrudes further than the first sun gear 21, a carrier bearing portion 245 is provided between it and the inner circumferential surface of the first carrier 24, rotatably supporting the first carrier 24. Furthermore, the front end of the motor rotating shaft 41 is connected to the output shaft 29 via a bearing. That is, the motor rotating shaft 41 and the output shaft 29 are not integral, but rotate at different speeds.

[0032] (Speed ​​Transmission Mechanism) As shown in Figure 3, the speed transmission mechanism 20 reduces the rotational driving force of the motor 4 and transmits it to the drum 3, switching the rotational speed of the drum 3 (refer to Figure 1) between high-speed rotation and low-speed rotation. The speed transmission mechanism 20 includes a first power transmission gear mechanism 20A disposed on the motor input side and a second power transmission gear mechanism 20B connected to the first power transmission gear mechanism 20A and disposed on the motor output side.

[0033] The first power transmission gear mechanism 20A includes a first sun gear 21 fixed to the motor rotating shaft 41 which serves as the input shaft, a first planet 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 planet gear 22, and a first carrier 24 supporting the first planet gear 22.

[0034] The first star gear 21 is coaxially fixed to the front end 41a of the motor rotating shaft 41. Three first planetary gears 22 mesh with the first star gear 21.

[0035] One end 221a of each planetary gear support shaft 221 of the first planetary gear 22 is supported on the first carrier 24. The first planetary gears 22 are rotatably mounted around the planetary gear support shaft 221 via bearings 223. Furthermore, the three first planetary gears 22 mesh with the inner circumferential gear 231 of the first ring gear 23.

[0036] The first ring gear 23 has an inner circumferential gear 231 that is coaxially arranged with the motor rotating shaft 41 and meshes with the three first planetary gears 22 on the inner circumferential surface of the ring. The first ring gear 23 is engaged in a non-rotating state in the motor housing 40 (see Figure 1). In this way, the first planetary gears 22 rotate on their own axis by the rotation of the first sun gear 21 and move around the inner circumferential gear 231.

[0037] The first carrier 24 supports the planetary gear support shaft 221 of the three first planetary gears 22, and moves around the meshing first ring gear 23 as the first planetary gears 22 move, while rotating around the motor rotating shaft 41 to transmit rotational driving force to the second ring gear 25. The first carrier 24 is formed into a top cylindrical shape by a support wall 241, a cylindrical portion 242, and a flange portion 243. The first carrier 24 is arranged such that the support wall 241, which forms a circular plate-shaped top wall, faces the motor 4, and the center of the support wall 241 is coaxial with the motor rotating shaft 41.

[0038] The support wall 241 has a shaft hole 241a at its center, which is rotatably supported relative to the motor rotating shaft 41 via the carrier bearing portion 245. The first carrier 24 rotates at a different number of revolutions than the first sun gear 21. The support wall 241 supports planetary gear support shafts 221 for three first planetary gears 22. The planetary gear support shafts 221 are equally spaced along the circumference of the circular support wall 241. The first planetary gears 22 supported by the planetary gear support shafts 221 are equally spaced around the first sun gear 21. The cylindrical portion 242 extends to the left from the outer periphery of the support wall 241 and fits the cylindrical body for fitting the output shaft 29. The flange portion 243 forms an annular shape when viewed axially and protrudes radially outward from the left end of the cylindrical portion 242. The outer periphery of the flange portion 243 is integrally connected to the second annular gear 25 described below. That is, the rotation of the first carrier 24 is transmitted to the second ring gear 25 at the same rotational speed.

[0039] As shown in Figures 2 and 3, the roller clutch 24A is configured to be received in a pressed-in state into the first carrier 24 and to transmit power in one direction between the first carrier 24 and the output shaft 29. That is, the roller clutch 24A is configured to transmit power in one direction between the motor rotating shaft 41 and the output shaft 29. When the output shaft 29 slows down due to a load applied by the rotation of the drum 3 in the direction of line winding, power is transmitted to the output shaft 29 and the second star gear 27 via the roller clutch 24A. Therefore, the drum 3 does not rotate in the direction of line winding. On the other hand, when the drum 3 rotates in the direction of line winding, the roller clutch 24A does not transmit power between the first carrier 24 and the output shaft 29. As a result, the drum 3 rotates in the direction of line winding.

[0040] Here, the reverse rotation prevention part of the roller clutch 24A will be explained. As shown in Figures 3 and 4, a stop fixing platform 44 is provided on the left side 23b of the first ring gear 23. The stop fixing platform 44 is formed into an annular shape with an inner diameter smaller than that of the first ring gear 23, and fits into the outer side of the cylindrical portion 242 of the first carrier 24. A rotatable stop hook 441 is provided on the left surface 44a of the stop fixing platform 44. When the stop hook 441 rotates toward the inner hollow side of the stop fixing platform 44, it engages with the outer peripheral surface of the cylindrical portion 242 of the first carrier 24, and can rotate integrally with the first carrier 24. Moreover, by providing the stop fixing platform 44, the movement of the first ring gear 23 in the left-right direction X1 is restricted. On the inner circumferential surface 44b of the stop fixing platform 44, three recesses 44c are formed along the outer diameter of the first planetary gear 22 in such a way that the tips of the three first planetary gears 22 do not interfere with each other. By setting the recesses 44c in this way, the wall thickness of the stop fixing platform 44 can be ensured, thereby allowing the stop hook 441 to be assembled onto the left surface 44a.

[0041] As shown in Figures 3 and 5-7, the second power transmission gear mechanism 20B includes a second ring gear 25 integrally mounted on the first carrier 24, a complex set (three sets in this case) of second planetary gears 26 meshing 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 supporting the second planetary gears 26. Furthermore, in Figure 7, the multilayer core (coil) of the motor 4 is omitted.

[0042] The second sun gear 27 is coaxially fixed to the middle part 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.

[0043] The second ring gear 25 has an inner circumferential gear 251 that is coaxially arranged with the output shaft 29 (the same applies to the motor rotation shaft 41) and meshes with the three sets of second planetary gears 26 on the inner circumferential surface of the ring. The front end of the second ring gear 25 is integrally fixed to the outer circumference of the flange portion 243 of the first carrier 24 in a non-rotatable state. In this way, the second planetary gears 26 rotate on their own axis while moving around the inner circumferential gear 251.

[0044] The two ends of the planetary gear support shafts 261 of the second planetary gears 26 are supported on the second carrier 28. The second planetary gears 26 are rotatably mounted around the planetary gear support shafts 261 via bearings 263. Furthermore, the three sets of second planetary gears 26 mesh with the inner circumferential gears 251 of the second ring gear 25.

[0045] The second planetary gear 26 consists of a pair of meshing pinions 26A and 26B. The pair of pinions includes 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 outer diameters of the first pinion 26A and the second pinion 26B are set to be the same (same gear ratio).

[0046] The second carrier 28 supports the planetary gear support shafts 261 of the first pinion 26A and the second pinion 26B of the three sets of second planetary gears 26, and transmits rotational driving force to the second star gear 27 as the first pinion 26A of each second planetary gear 26 moves around the meshing second ring gear 25 with the output shaft 29 as the center. The second carrier 28 rotates at a different number of revolutions than the second star gear 27.

[0047] As shown in Figure 3, the second carrier 28 has a pair of support walls 281, 282 and a cylindrical portion 283. The second carrier 28 is arranged such that the pair of circular plate-shaped support walls 281, 282 face the motor 4 side (the first power transmission gear mechanism 20A side), and the center of the pair of support walls 281, 282 is coaxial with the output shaft 29.

[0048] The first support wall 281 and the second support wall 282 are both formed in annular shape when viewed from the axial direction. The first support wall 281 is disposed 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 arranged parallel to and spaced apart from the first support wall 281. The first support wall 281 and the second support wall 282 are integrally connected by six planetary gear support shafts 261.

[0049] A second planetary gear 26 is disposed between the first support wall 281 and the second support wall 282. Two planetary gear support shafts 261 are equally spaced along the circumference of the circular first support wall 281 and the second support wall 282. The second planetary gear 26, supported by the planetary gear support shafts 261, is supported at equal intervals around the second sun gear 27. Furthermore, the second planetary gear 26 (first pinion 26A, second pinion 26B) is rotatably supported on each planetary gear support shaft 261 by bearings 263. The cylindrical portion 283 extends rearward from the inner periphery of the first support wall 281 and is rotatably disposed by bearings 291, 292 interposed between it and the output shaft 29. Here, the output shaft 29 protrudes from the annular plate 61 described below to transmit rotation to the drum 3.

[0050] (Speed ​​Switching Mechanism) As shown in Figures 3, 8, and 9, the speed switching mechanism 20 of this embodiment includes a speed switching mechanism 6 that switches the rotation of the second carrier 28 between high-speed rotation and low-speed rotation. That is, in the speed switching mechanism 20, when the second carrier 28 is fixed and in a stopped rotation state, it becomes a high-speed rotation, and when the second carrier 28 is released from its fixed position and can rotate freely, it becomes a low-speed rotation.

[0051] The speed change mechanism 6 includes: an annular plate 61, which is non-rotatably fitted into the front end of the cylindrical portion 283 of the second carrier 28 in the circumferential direction, and has cut ratchet teeth 61a on its outer circumferential surface (see Figure 8); a switching stop 62 (switching part), which can be locked by engaging with the ratchet teeth 61a; a speed change operation switch 63 (switching operation part, see Figure 8), which performs the operation of switching the switching stop 62 relative to the ratchet teeth 61a to the locked position and the unlocked position; and a connecting shaft 64, which connects the switching stop 62 and the speed change operation switch 63.

[0052] The annular plate 61 is coaxially arranged with the second carrier 28 and can rotate integrally with the second carrier 28. When the switching stop 62 is engaged with the ratchet pawl 61a, the second carrier 28 and the annular plate 61 stop rotating together. When the switching stop 62 disengages from the ratchet pawl 61a, the second carrier 28 and the annular plate 61 rotate together.

[0053] As shown in Figures 8 and 10, the speed change operation switch 63 is disposed on the outer side of the right side cover of the cable reel body 10, and is mounted in a shaft-like state that fits into the lever switch 46 (speed adjustment component) used for adjusting the speed of the motor 4. The lever switch 46 is disposed in front of the right side plate 11A on the handle side (see Figure 1), and is configured to be rotatable within a specified rotation angle range. The lever switch 46 inputs the change in the resistance value of the potentiometer caused by the rotation operation to the control unit (not shown) of the cable reel body 10. Moreover, it is configured such that the motor output of the motor 4 can be continuously increased or decreased from the motor stop state to the high output value according to the amount of operation of the lever switch 46.

[0054] The speed change operation switch 63 is rotary, capable of selectively switching between the locked and unlocked positions. A portion of the speed change operation switch 63, extending radially outward from the center of rotation, is fixed to one end 64a of the connecting shaft 64. Furthermore, the speed change operation switch 63 may also have a notch, through which the switching mode (rotation speed of the motor 4) of the speed change mechanism 20 is displayed (e.g., high-speed rotation, low-speed rotation, etc.).

[0055] A switching cam 66 protruding 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 generally the horizontal strander shaft of the horizontal strander mechanism used to evenly wind the fishing line in the spool 3. Furthermore, the connecting shaft of the speed switching mechanism 6 and the horizontal strander shaft can also be set separately.

[0056] As shown in Figures 8 and 9, the switching stop 62 is disposed outside the annular plate 61 and is rotatably supported on the fixed plate 65 about a rotation center axis (rotation axis 62a) parallel to the output shaft 29. The fixed plate 65 is a circular plate-shaped component fixed to the left side plate 11B of the reel body 10. The switching stop 62 has a ratchet pawl portion 621 that engages with the ratchet pawl teeth 61a on one side separated from the rotation axis 62a, and a pressed-in portion 622 facing the rotation direction of the switching stop 62 on the other side. The switching stop 62 is held in place on the annular plate 61 by, for example, a spring component (not shown) that applies force to the ratchet pawl portion 621 in the direction that it engages with the ratchet pawl teeth 61a. The pressed-in portion 622 is the part that is pressed in when the switching cam 66, which is provided on the connecting shaft 64, is rotated by the speed change operation switch 63.

[0057] When the shift stop 62 is in one position (high-speed mode) and the speed shifting operation switch 63 is in another position, the shifting cam 66 is disengaged from the pressed part 622, the ratchet pawl part 621 is engaged with the ratchet pawl teeth 61a, and the annular plate 61 is fixed. That is, the second carrier 28 is fixed together with the annular plate 61 (in a state where it cannot rotate), and the output shaft 29 rotates at high speed.

[0058] Furthermore, when the shift stop 62 sets the speed change operation switch 63 to the other position (low speed mode), the pressed part 622 is pressed in the rotational direction by the rotating shift cam 66, and the ratchet pawl part 621 disengages from the ratchet pawl teeth 61a, thereby allowing the annular plate 61 to rotate. That is, the second carrier 28 can rotate together with the annular plate 61, and the output shaft 29 rotates at low speed.

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

[0060] First, the high-speed rotation scenario will be explained. As shown in Figures 8 and 9, the speed change operation switch 63 is manually switched to high-speed rotation mode. At this time, the switching stop 62 is in the position where the switching cam 66 is disengaged from the pressed-in part 622, the ratchet pawl part 621 is engaged with the ratchet pawl teeth 61a, and the annular plate 61 is fixed. That is, the second carrier 28 is fixed together with the annular plate 61 (in a state where rotation is not possible).

[0061] As shown in Figures 3 and 11, under no-load conditions, when the motor 4 rotates and the motor shaft 41 rotates, the first sun gear 21, fixed to the motor shaft 41, rotates at the same speed as the motor shaft 41 in the first power transmission gear mechanism 20A. Furthermore, the rotation of the first sun gear 21 is transmitted to the three first planetary gears 22 meshing with it. While rotating, the first planetary gears 22 mesh with the internal teeth of the non-rotating first ring gear 23 and revolve around the central axis. Moreover, the first carrier 24 supporting the three first planetary gears 22 also rotates along with their revolution. That is, the rotational force of the motor shaft 41 is decelerated and transmitted to the first carrier 24 supporting the three first planetary gears 22.

[0062] Next, in the second power transmission gear mechanism 20B, the second ring gear 25, integrally disposed 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 includes three pinions, meshing with the inner circumferential gear 251 of the second ring gear 25. Specifically, in the second planetary gear 26, the first pinion 26A and the second pinion 26B, which mesh with the second ring gear 25, rotate independently. At this time, the rotational speed of the first pinion 26A and the second pinion 26B increases from that of the second ring gear 25, becoming high speed.

[0063] Here, during high-speed rotation, since the second carrier 28 is fixed and cannot rotate, the second planetary gear 26 does not revolve. That is, since the first pinion 26A and the second pinion 26B mesh with the same number of teeth, the second pinion 26B also rotates at the same speed as the first pinion 26A, and at a faster speed than the second ring gear 25. The second planetary gear 26, forming a double pinion, transmits rotational force from the second ring gear 25 to the second sun gear 27, using the gear ratio caused by the difference in the number of teeth between the second ring gear 25 and the second sun gear 27 to increase the rotational speed. In this way, the rotational force of the second sun gear 27 is transmitted to the output shaft 29 fixed to the second sun gear 27 without deceleration. Thus, the rotational force of the motor shaft 41, after being reduced in speed by the first power transmission gear mechanism 20A, is output to the output shaft 29 via high-speed rotation increased in speed by the second power transmission gear mechanism 20B. That is, in Figure 11, the transmission path of the rotational force of the first power transmission gear mechanism 20A and the second power transmission gear mechanism 20B during high-speed rotation becomes 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 idles, thus becoming the first transmission path K1.

[0064] Figure 12 illustrates an example of the variation in the rotational speeds of the first planetary gear 22 and the second planetary gear 26 during high-speed rotation caused by the transmission mechanism 20. In Figure 12, the horizontal axis represents the radial distance from the motor shaft, with the 0 side being the motor shaft, and the vertical axis represents the rotational speed (rpm). In the first planetary gear 22, indicated by the dashed line in Figure 12, symbol P1 represents the rotational speed of the input motor rotating shaft 41 (first sun gear 21) (approximately 38,000 rpm). Symbol P2 represents the rotational speed of the fixed and non-rotating first ring gear 23 (0 rpm). Symbol P3 represents the rotational speed of the first carrier 24 (approximately 7,000 rpm).

[0065] In the second planetary gear 26 shown by the solid line in Figure 12, symbol P3 represents the rotational speed (approximately 7000 rpm) of the second ring gear 25, which rotates integrally with the first carrier 24. Symbol P4 represents the rotational speed (0 rpm) of the second carrier 28, which is fixed and cannot rotate. Symbol P5 represents the rotational speed (approximately 22000 rpm) of the output shaft 29 (second sun gear 27). Thus, it can be seen that at high speed, the rotational speed of the output shaft 29 (approximately 22000 rpm) is slower than the input rotational speed (approximately 38000 rpm), but faster than the rotational speed (approximately 7000 rpm) of the first carrier 24.

[0066] Next, the low-speed rotation scenario will be explained. As shown in Figures 8 and 9, the speed change operation switch 63 is manually switched to low-speed rotation mode. At this time, in the switching stop 62, the pressed part 622 is pressed in the rotational direction by the rotating switching cam 66, and the ratchet pawl part 621 disengages from the ratchet pawl tooth 61a, thereby allowing the annular plate 61 to rotate. That is, the second carrier 28 can rotate together with the annular plate 61.

[0067] As shown in Figures 3 and 11, under no-load conditions, when the motor 4 rotates and the motor shaft 41 rotates, the first sun gear 21, fixed to the motor shaft 41, rotates at the same speed as the motor shaft 41 in the first power transmission gear mechanism 20A. Furthermore, the rotation of the first sun gear 21 is transmitted to the three first planetary gears 22 meshing with it. While rotating on their own axes, the first planetary gears 22 also revolve around the first planetary gear 23, meshing with the internal teeth of the non-rotating first ring gear 23. Moreover, the first carrier 24 supporting the three first planetary gears 22 also rotates along with their revolution. In other words, the rotational force of the motor shaft 41 is decelerated and transmitted to the first carrier 24 supporting the three first planetary gears 22.

[0068] Next, in the second power transmission gear mechanism 20B, the second ring gear 25, integrally disposed 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 includes three pinions, meshing with the inner circumferential gear 251 of the second ring gear 25. Specifically, in the second planetary gear 26, the first pinion 26A and the second pinion, which mesh with the inner teeth of the second ring gear 25, rotate independently. At this time, the rotational speed of the first pinion 26A and the second pinion 26B from the second ring gear 25 increases.

[0069] Here, during low-speed rotation without load, since the second carrier 28 is capable of rotation, the rotation of the second pinion 26B is transmitted to the second carrier 28, causing the second carrier 28 to rotate. Subsequently, the second planetary gear 26 revolves around the inner circumferential gear 251 of the second ring gear 25. That is, the rotation of the second planetary gear 26 is decelerated and transmitted to the second carrier 28. Then, the rotational force of the second planetary gear 26, which is 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 speed, and the rotational force of the motor shaft 41 is output at the speed reduced by the first power transmission gear mechanism 20A via the output shaft 29. That is, in Figure 11, the rotational force transmission paths of the first power transmission gear mechanism 20A and the second power transmission gear mechanism 20B when rotating at low speed without load become the same first transmission path K1 as when rotating at high speed. Thus, when the drum 3 rotates in the direction of winding the fishing line, the roller clutch 24A does not transmit power between the first carrier 24 and the output shaft 29, so the drum 3 rotates in the direction of winding the fishing line.

[0070] On the other hand, when rotating at low speed, the output shaft 29 slows down due to the load applied by the rotation of the drum 3 in the direction of the fishing line being wound out. Power is then transmitted to the output shaft 29 and the second stellar gear 27 via the roller clutch 24A. That is, in Figure 11, the transmission path of the rotational force of the first power transmission gear mechanism 20A and the second power transmission gear mechanism 20B under load during low-speed rotation becomes the second transmission path K2. Therefore, the drum 3 does not rotate in the direction of the fishing line being wound out. Furthermore, in this embodiment, a roller clutch 24A is provided between the first carrier 24 and the output shaft 29, but it can also be omitted. Without the roller clutch 24A, the second stellar gear 27 stops under load during low-speed rotation, and the second carrier 28 idles.

[0071] Figure 13 illustrates an example of the variation in the rotational speeds of the first planetary gear 22 and the second planetary gear 26 during low-speed rotation caused by the transmission mechanism 20. In Figure 13, the horizontal axis represents the radial distance from the motor shaft, with the 0 side being the motor shaft, and the vertical axis represents the rotational speed (rpm). In the first planetary gear 22, shown by the dashed line in Figure 13, symbol P1 represents the rotational speed of the input motor rotating shaft 41 (first sun gear 21) (approximately 38,000 rpm). Symbol P2 represents the rotational speed of the fixed and non-rotating first ring gear 23 (0 rpm). Symbol P3 represents the rotational speed of the first carrier 24 (approximately 7,000 rpm).

[0072] In the second planetary gear 26 shown by the solid line in Figure 13, symbol P3 represents the rotational speed (approximately 7000 rpm) of the second ring gear 25, which rotates integrally with the first carrier 24. Symbol P4 represents the rotational speed (approximately 7000 rpm) of the second carrier 28, which is capable of rotation. Symbol P5 represents the rotational speed (approximately 7000 rpm) of the output shaft 29 (the second sun gear 27). Thus, it can be seen that at low speeds, the rotational speed of the output shaft 29 (approximately 7000 rpm) is significantly reduced compared to the input rotational speed (approximately 38000 rpm), and becomes the same rotational speed as the first carrier 24 (approximately 7000 rpm).

[0073] Next, the function of the electric reel 1 configured as shown in the diagram will be explained in detail.

[0074] In the electric reel for fishing tackle of this embodiment, as shown in FIG3, the second power transmission gear mechanism 20B is configured such that the second planetary gear 26 supported on the second carrier 28 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. This allows the second carrier 28 to switch between a rotatable state and a non-rotatable state using the speed switching mechanism 6. When the second carrier 28 is fixed in a non-rotatable state by the speed switching mechanism 6, the rotational speed of the input shaft (motor rotation shaft 41) of the motor 4 is reduced by the first power transmission gear mechanism 20A and transmitted from the second ring gear 25, which transmits the reduced rotational speed, to the second planetary gear 26.

[0075] At this time, the rotational speed of the second planetary gear 26 increases. Furthermore, since the second carrier 28 is fixed and cannot rotate, the second planetary gear 26, forming a double pinion, does not transmit the rotation of the first pinion 26A and the second pinion 26B, and therefore does not revolve. Consequently, the second planetary gear 26 rotates at a speed faster than that of the second ring gear 25. Moreover, the rotational force of the second planetary gear 26 is not decelerated by the second carrier 28, but is transmitted at approximately the same rotational speed as the second sun gear 27 meshing with the second pinion 26B. Thus, the rotational force of the second sun gear 27 is transmitted at high speed without deceleration to the output shaft 29 fixed to the second sun gear 27.

[0076] Thus, in this embodiment, by using the speed switching mechanism 6 to mechanically fix the second carrier 28 in a non-rotating state, it is possible to maintain the highest speed of high-speed rotation while increasing the winding torque, thereby improving the operability of fishing.

[0077] Furthermore, when the second carrier 28 is rotatable via the speed change mechanism 6, the rotational speed of the input shaft (motor rotation shaft 41) of the motor 4 is reduced by the first power transmission gear mechanism 20A, and transmitted from the second ring gear 25, which transmits the reduced rotational speed, to the second planetary gear 26. At this time, the rotational speed of the second planetary gear 26 increases. Moreover, since the second carrier 28 is rotatable, the second planetary gear 26, which forms a double pinion, transmits the rotation of the first pinion 26A and the second pinion 26B. The second planetary gear 26 revolves around the second ring gear 25, and therefore rotates at the same speed as the second ring gear 25. Furthermore, the rotational force of the second planetary gear 26 is not reduced by the second carrier 28, but is reduced to a rotational speed approximately the same as that of the second sun gear 27 meshing with the second pinion 26B. In this way, the rotational force of the second star gear 27 is transmitted to the output shaft 29 fixed to the second star gear 27 at a low speed. Thus, in this embodiment, by making the second planetary gear 26 of the second power transmission gear mechanism 20B a double pinion, the speed difference between high-speed rotation and low-speed rotation can be increased.

[0078] Furthermore, in this embodiment, as shown in FIG8, by using the horizontal stranding shaft as both the connecting shaft 64 for connecting the switching stop 62 of the speed switching mechanism 6 and the speed switching operation switch 63 for operating the switching stop 62, the constraints of the configuration and shape of the connecting shaft 64 within the electric winding machine 1 can be suppressed, thereby improving space efficiency.

[0079] In this embodiment, since a speed switching operation switch 63 for operating the switching stop 62 is mounted near the lever switch 46 of the motor 4, space efficiency can be improved.

[0080] In the electric reel for fishing tackle of this embodiment constructed in the manner described above, the speed difference between high-speed rotation and low-speed rotation can be increased, thereby enabling a greater winding torque while maintaining the highest speed.

[0081] The embodiments of the electric reel for fishing tackle of the present invention have been described above. However, these embodiments are provided as examples and are not intended to limit the scope of the invention. The embodiments can be implemented in various other ways, and various omissions, substitutions, and modifications can be made without departing from the spirit of the invention. Examples of embodiments and their variations include, for instance, content that is easily conceived by the operator, substantially the same content, and content of equal scope.

[0082] For example, in this embodiment, the switching stop 62 (switching unit) and the speed switching operation switch (switching operation unit) used to operate the switching stop 62 are connected by the horizontal stranding shaft of the horizontal stranding mechanism as the connecting shaft 64 for uniformly winding the fishing line in the drum 3, but it is not limited to using the horizontal stranding shaft.

[0083] Furthermore, in this embodiment, the speed switching operation switch (switching operation unit) for operating the switching stop 62 is provided on the lever switch 46 (speed adjustment component) of the motor 4, but the position for providing the switching operation unit is not limited to a configuration shared with the speed adjustment component.

[0084] 1: Electric reel (electric reel for fishing tackle) 3: Roll 4: Motor 5: Clutch mechanism 6: Speed ​​switching mechanism 10: Cable reel body 11: Ontology Framework 11A: Right side panel 11B: Left side panel 11C: Connecting component 14: Handle shaft 15: Fishing rod mounting section 17: Depth Display Section 20: Transmission Mechanism 20A: First power transmission gear mechanism 20B: Second power transmission gear mechanism 21: The First Star Gear 22: Planetary Gear No. 1 23: First ring gear 23b: Left side 24: First Carrier 24A: Roller clutch 25: Second ring gear 26: Second Planetary Gear 26A: Pinion 1 26B: Second pinion 27: The Second Star Gear 28: Second Carrier 29: Output shaft 29b: Middle part of the shaft 32: Main body of the coil 33: Flange portion 41: Motor rotating shaft 41a: Front end of shaft 41b: Shaft base end 42: Motor body 43: Motor housing 44: Stop fixing platform 44a: Left surface 44b: Inner circumferential surface 44c: concave part 45: Bearing 46: Lever switch (speed adjustment component) 50: Clutch operating components 61: Circular plate 61a: Ratchet pawl teeth 62: Switching stop (switching unit) 62a: Rotation axis 63: Speed ​​change operation switch (switching operation unit) 64: Connecting shaft 64a: One end 64b: The other end 65: Fixing plate 66: Switching Cam 221: Planetary gear support shaft 221a: One end 223: Bearing 231: Internal circumferential gear 241: Support Wall 241a: Shaft hole 242: Cylindrical section 243: Flange portion 245: Carrier bearing section 251: Inner circumferential gear 261: Planetary gear support shaft 263: Bearing 281: Support Wall 282: Support Wall 283: Cylindrical section 291: Bearing 292: Bearing 441: Stop hook 621: Ratchet Pad 622: The part that was pressed in

Claims

1. An electric reel for fishing tackle, comprising a speed-changing mechanism that switches the rotational speed of a motor to high-speed rotation and low-speed rotation of a drum, the speed-changing 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 non-rotatably to an input shaft, 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 comprising a second ring gear integrally disposed on 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 aforementioned second planetary gear is a pair of meshing pinions. The pair of pinions includes a first pinion meshing with the aforementioned second ring gear and a second pinion meshing with the aforementioned second planetary gear. The aforementioned electric reel for fishing tackle is provided with a switching unit that selectively switches the rotation of the aforementioned second carrier around the motor shaft to a fixed state and a deactivated state.

2. The electric reel for fishing tackle as claimed in claim 1, wherein the switching unit and the switching operation unit for operating the switching unit are connected by a horizontal stranding shaft of a horizontal stranding mechanism for uniformly winding fishing line in the reel.

3. The electric reel for fishing tackle as requested in item 1 or 2, wherein the switching operation unit for operating the aforementioned switching unit is provided in the speed adjustment component of the drive motor.

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