Dual bearing spooling wheel

Abstract

The present application can miniaturize a double bearing winding reel in the axial direction. The present application provides a double bearing winding reel configured to transmit rotation of a handle to a winding drum (30) via a planetary gear (60), and provided with a clutch that switches on and off the transmission. The winding drum shaft (31) of the winding drum (30) has a clutch pin (51), the planetary gear (60) has a gear portion (65) and an engagement groove (64), the gear portion (65) has a tooth portion on the outer periphery, the engagement groove (64) engages with the clutch pin (51) in the on state of the clutch that transmits the rotation of the handle to the winding drum (30), and at least a part of the gear portion (65) and the engagement groove (64) overlap in the winding drum axial direction (X).

Description

Technical Field

[0001] This invention relates to a double-bearing winding reel. Background Technology

[0002] Conventional double-bearing reels are known to include those that transmit the rotation of a handle to a drum via a planetary gear and have a clutch that switches the transmission on and off (for example, see Patent Document 1).

[0003] Furthermore, in the aforementioned double-bearing winding reels, there are cases where a double-bearing winding reel equipped with a clutch pin is used. This clutch pin is configured to be able to be switched by clutch operation to an engaged position (rotating relative to the planetary gears) and a disengaged position (separated from the planetary gears), protruding radially outward from the drum. When a clutch pin is provided, an inclined portion is provided to guide the clutch pin towards the engaged position on the planetary gears (for example, see Patent Document 2).

[0004] Patent document 1: Japanese Patent Application Publication No. 2012-100624.

[0005] Patent Document 2: Japanese Patent Application Publication No. 2008-125467.

[0006] In such traditional double-bearing winding reels, such as Figure 7 As shown, the teeth 101 provided on the outer periphery of the planetary gear 100 and the engaging portion 102 for engaging the clutch pin are arranged separately in the axial direction 103 of the drum, which limits the miniaturization of the double-bearing winding wheel in the axial direction.

[0007] Furthermore, in order to process the inclined portion 104 guided towards the engaging portion 102 as described in Patent Document 2, machining is performed using the side of the end mill to avoid interference of the cutting tool with the tooth portion 101. Therefore, it is necessary to make the engaging portion of the clutch pin, including the inclined portion 104, protrude longer in the axial direction of the drum compared to the planetary gear, making it difficult to miniaturize the double-bearing winding reel in the axial direction, and there is room for improvement in this regard. Summary of the Invention

[0008] The present invention was made in consideration of such circumstances, and its object is to provide a dual-bearing winding wheel that enables axial miniaturization of the dual-bearing winding wheel.

[0009] (1) The double-bearing winding wheel of the present invention transmits the rotation of the handle to the drum via a planetary gear and has a clutch for switching the connection and disconnection of the transmission. The double-bearing winding wheel is characterized in that the drum shaft of the drum has an engaging portion, the planetary gear has a gear portion and an engaging portion, the gear portion has teeth on its outer periphery, and the engaging portion engages with the engaging portion when the clutch is engaged in the state where the rotation of the handle is transmitted to the drum. At least a portion of the teeth and the engaging portion overlap in the axial direction of the drum.

[0010] According to the double-bearing winding reel of the present invention, at least a portion of the engaging portion engages with the engaged portion in a state of overlapping with the planetary gear in the axial direction of the drum, so that the double-bearing winding reel can be miniaturized in the axial direction of the drum.

[0011] Furthermore, in this invention, the engaging part is disposed in the gear part of the planetary gear, so it is possible to perform machining by means of the end of the end mill rather than by means of the side of the end mill. Therefore, it is not necessary to have a long part that extends in the axial direction of the drum as in the past, and the double bearing winding wheel can be miniaturized in the axial direction of the drum.

[0012] (2) Preferably, the aforementioned engaging portion is a clutch pin that protrudes radially outward from the axial direction of the aforementioned drum.

[0013] In this case, at least a portion of the planetary gear engages with the engaged portion in an overlapping state along the drum axis, so as a double-bearing winding reel, it can be miniaturized along the drum axis.

[0014] (3) Alternatively, the aforementioned double-bearing winding wheel is characterized in that a recess is formed in the central part of the radial inner side of the aforementioned gear portion, which is recessed in the axial direction of the aforementioned drum, and the aforementioned engaged portion is provided in the aforementioned recess for engaging the aforementioned clutch pin.

[0015] In this case, the clutch pin engages with the engaging part provided in the recess of the gear section, so that the axial overlap of the gear section and the engaging part of the drum can be increased, and the miniaturization of the double bearing winding wheel can be carried out more effectively.

[0016] (4) Alternatively, the aforementioned double-bearing winding wheel is characterized in that a stepped portion is formed in the aforementioned recess along the circumferential direction surrounding the aforementioned drum shaft, and a groove-shaped engaging portion is provided at the lowest position of the aforementioned stepped portion.

[0017] In this case, a stepped portion is provided in the gear section of the planetary gear, so that the clutch pin can be guided to the engaged portion, i.e., the engaged position, by means of the stepped portion to engage.

[0018] Furthermore, in this invention, by providing a stepped portion, machining can be performed using the end portion of an end mill.

[0019] (5) Alternatively, the aforementioned double-bearing winding wheel is characterized in that the cross-section of the aforementioned clutch pin is circular, and the circumferential width dimension of the aforementioned stepped portion at the radial center end orthogonal to the aforementioned drum shaft is smaller than the radius of the cross-section of the aforementioned clutch pin.

[0020] In this case, the width of the central end of the stepped portion becomes narrower, so the clutch pin, which is temporarily moved to the stepped portion, will not remain in the stepped portion and can easily enter the engaged portion from the stepped portion. That is, in this case, the clutch pin can be reliably guided to the engaged portion.

[0021] Invention Effects The double-bearing winding wheel according to the present invention enables the double-bearing winding wheel to be miniaturized in the axial direction. Attached Figure Description

[0022] Figure 1 This is a perspective view showing the overall structure of the double-bearing winding wheel according to an embodiment of the present invention.

[0023] Figure 2 yes Figure 1 The XI-XI sectional view shown in the figure is a sectional view of a double-bearing winding wheel.

[0024] Figure 3 It is a three-dimensional diagram showing a partial fracture of the planetary gear structure.

[0025] Figure 4 It is a 3D diagram of a planetary gear.

[0026] Figure 5 This is a top view of the first end of the planetary gear as seen from the axial direction of the drum.

[0027] Figure 6 yes Figure 3 The XII-XII line direction view is shown in the figure.

[0028] Figure 7 It is a three-dimensional diagram showing the structure of a conventional planetary gear. Detailed Implementation

[0029] Hereinafter, embodiments of the double-bearing winding reel of the present invention will be described with reference to the accompanying drawings. Furthermore, in each drawing, the scale of each structural component may be appropriately altered as needed to allow for observation and confirmation of its size.

[0030] <Overall Structure> like Figure 1As shown, the dual-bearing fishing reel 1 of this embodiment includes a reel body 10, a handle 20 for rotating the spool disposed on the side of the reel body 10, and a star-shaped drag unit 3 disposed on the side of the handle 20 on the reel body 10. The spool 30, which releases and winds the fishing line by rotation, is rotatably mounted on the reel body 10. The reel body 10 is mounted to a fishing rod via a rod mounting part 18.

[0031] Here, "left and right direction" in the following description refers to the left and right direction as observed by the angler when holding the fishing rod equipped with the double-bearing reel 1. In this embodiment, the handle 20 is located on the right side of the reel body 10.

[0032] <Handle> The handle 20 has a crank arm 21 and a handle 22. The crank arm 21 is non-rotatably mounted to the end 41a of a drive gear shaft 41 (described later) protruding to the right side of the winding reel body 10. The handle 22 is rotatably mounted to one end of the crank arm 21 about an axis orthogonal to one end of the crank arm 21.

[0033] <Winding Reel Body> The winding reel body 10 has a frame 11, a right side cover 12, and a left side cover 13. The frame 11 has a right side plate 11A and a left side plate 11B arranged at predetermined intervals, and a plurality of connecting members 11C connecting the right side plate 11A and the left side plate 11B. The right side cover 12 is integrally formed with the right side plate 11A in such a way that it covers the outside of the right side plate 11A. The left side cover 13 is fixed to the left side plate 11B in such a way that it covers the outside of the left side plate 11B. A space is formed between the right side plate 11A and the right side cover 12 for accommodating various mechanisms described later.

[0034] Viewed from the side, the right side plate 11A and the right side cover 12 are roughly elliptical in shape, bulging outward axially from the assembly part of the drive gear shaft 41 (described later). The left side plate 11B and the left side cover 13 are circular when viewed from the side. The right side cover 12 is detachably connected to the right side plate 11A. The left side cover 13 is detachably connected to the left side plate 11B.

[0035] Multiple connecting parts 11C are plate-shaped components integrally formed with the right side plate 11A and the left side plate 11B, connecting the right side plate 11A and the left side plate 11B at three locations: the upper part, the lower part, and the rear part of the winding reel body 10. By providing such connecting parts 11C, even if a large load is applied to the winding reel body 10 and deformation such as deflection occurs, the decrease in winding efficiency is suppressed. The rod mounting part 18 is fixed to the lower connecting part 11C, and the rear connecting part 11C is equipped with a clutch operating part 14.

[0036] The right side plate 11A rotatably supports the base end of the drive gear shaft 41 (described later) that connects to the handle 20, and also supports the planetary gear 60 (described later, see reference). Figure 2 It can be rotated freely and moved axially to provide support.

[0037] like Figure 2 As shown, a spool 30 for winding line is rotatably arranged between the right side plate 11A and the left side plate 11B, a horizontal winding mechanism 16 for evenly winding fishing line into the spool 30, and the aforementioned clutch operating component 14 are also present.

[0038] At the center of the drum 30, the drum shaft 31 is fixed through. The drum shaft 31 is rotatably supported by the right side plate 11A and the left side plate 11B via bearings 32 and 33.

[0039] The clutch operating component 14 is configured to switch the clutch mechanism 50 to a clutch engaged state and a clutch disengaged state in order to swing around the drum shaft 31.

[0040] here, Figure 2 The reference numeral O in the attached figures indicates the centerline of the drum shaft 31. Furthermore, the axial direction of the drum is indicated by the reference numeral X.

[0041] In the space between the right side plate 11A and the right side cover 12, a rotation transmission mechanism 40 for transmitting torque from the handle 20 to the drum 30 is disposed, and a clutch mechanism 50 is disposed within the rotation transmission mechanism 40. Furthermore, in the space between the right side plate 11A and the right side cover 12, a clutch control mechanism for controlling the clutch mechanism 50 in accordance with the operation of the clutch operating member 14, a traction mechanism, and a braking mechanism (i.e., a throwing control mechanism) for adjusting the resistance during the rotation of the drum 30 are also disposed. These clutch control mechanisms, traction mechanisms, and throwing control mechanisms are known constructions, so detailed descriptions are omitted here.

[0042] Furthermore, a drum braking device is disposed between the left side plate 11B and the left side cover 13, which brakes the drum 30 by means of centrifugal force. The drum braking device is a device used to suppress recoil during throwing.

[0043] <Rolls and spools> like Figure 2 As shown, the spool 30 has a cylindrical body 301 around which fishing line is wound, a pair of flanges 302 on the left and right sides, and a shaft insertion hole 303. The flanges 302 are integrally formed at both ends of the body 301, protruding radially outward. The spool 30 is integrally rotatably connected to a spool shaft 31, which is fixedly inserted and supported in the shaft insertion hole 303.

[0044] The spool 31 extends outward from the right side plate 11A through it. One end 31a of the spool 31 is rotatably supported by a first bearing 32 housed inside the left side plate 11B. Furthermore, the other end 31b of the spool 31 is rotatably supported by a second bearing 33 provided on the right side plate 11A. The portion of the spool 31 supported by the second bearing 33 is formed to have a larger diameter than the rest of the spool 31. Thus, the spool 31 is supported by bearings at two locations on the winding reel body 10.

[0045] A clutch section 5 constituting the clutch mechanism 50 is provided in the through portion of the right side plate 11A through which the drum shaft 31 passes. Figure 3 As shown, the clutch part 5 has a clutch pin 51 (engaging part) through which the drum shaft 31 passes. The clutch pin 51 is formed with a circular cross-section, passes through the drum shaft 31 in a direction orthogonal to the drum shaft, and its two ends protrude radially from the drum shaft 31. The pin-through portion 31c of the drum shaft 31 through which the clutch pin 51 passes is formed with the same large diameter as the portion of the drum shaft 31 supported by the second bearing 33.

[0046] <Clutch Mechanism> like Figure 2 As shown, the clutch mechanism 50 includes a clutch section 5 with a clutch pin 51 and a planetary gear 60 (described later). The clutch mechanism 50 can transmit and cut off the rotation from the handle 20 transmitted to the drum 30 via a drive gear (not shown). The state in which the rotation from the handle 20 is transmitted to the drum 30 is the clutch engaged state, and the state in which the rotation from the handle 20 is cut off is the clutch disengaged state. In the clutch disengaged state, the drum 30 rotates freely, and the fishing line can be released.

[0047] <Rotary Transmission Mechanism> The rotary transmission mechanism 40 includes a function to limit the torque transmitted in the opposite direction from the drum 30 to the handle 20. Furthermore, a centrifugal braking mechanism is disposed at the center of the left side plate 11B, which is used to brake the drum 30, which rotates freely in the wire release direction.

[0048] The rotary transmission mechanism 40 has a drive gear shaft 41 with a handle 20 fixed to one end (right end), a drive gear (not shown) connected to the other end (left end) of the drive gear shaft 41, and a planetary gear 60 meshing with the drive gear. The drive gear has gears on its outer circumference and is rotatably mounted to the drive gear shaft 41. The planetary gear 60 constitutes the rotary transmission mechanism 40 and also functions as a clutch mechanism 50.

[0049] The drive gear shaft 41 is arranged parallel to the drum shaft 31, and one end is rotatably supported on the right side plate 11A. The drive gear is connected to one end of the drive gear shaft 41 in a manner that allows it to rotate integrally. In this structure, when the clutch mechanism 50 is engaged, the torque from the handle 20 is directly transmitted to the drum 30.

[0050] In the clutch mechanism 50, the planetary gear 60 slides along the drum shaft 31, causing the engagement groove 64 (described later) to engage with the clutch pin 51, thereby transmitting rotational force between the drum shaft 31 and the planetary gear 60. This state is the engaged state (clutch engaged state).

[0051] When the engagement groove 64 and the clutch pin 51 disengage, no rotational force is transmitted between the drum shaft 31 and the planetary gear 60. This state is the disengaged state (clutch disengaged state). In the clutch disengaged state, the drum 30 rotates freely.

[0052] The planetary gear 60 is subjected to force in the direction of engagement between the engagement groove 64 and the clutch pin 51, i.e., in the clutch engaged state, due to the clutch operating member 14 arranged on the outside of the right side cover 12. In this way, the clutch operating member 14 is used to perform engagement and disengagement operations on the clutch mechanism 50.

[0053] like Figure 2 As shown, the planetary gear 60 is a component made of metals such as stainless steel alloy or brass alloy. The planetary gear 60 has a stepped through-hole 60a (see reference) through which the drum shaft 31 passes through the center. Figure 4 The cylindrical component is a planetary gear 60. The planetary gear 60 is rotatably supported on the winding reel body 10 by a bearing (not shown) and is movable freely along the axial direction X of the drum. The planetary gear 60 moves axially between a clutch engaged position close to the drum 30 and a clutch disengaged position away from the drum 30, by means of the clutch control mechanism described above.

[0054] At the planetary gear 60, a connecting portion 61 and a support portion 62 are provided on the right side from the second end 60c on the side opposite to the first end 60b on the drum 30 side.

[0055] The connecting part 61 is disposed between the planetary gear 60 and the support part 62. The outer diameter of the connecting part 61 is smaller than the diameter of the planetary gear 60.

[0056] The planetary gear 60 is supported by bearings that allow it to rotate freely and move axially relative to the right side plate 11A. A support portion 62 is located on the right side of the connecting portion 61. The support portion 62 is supported by bearings that allow it to rotate freely and move axially on the right side cover 12. Thus, the planetary gear 60 is supported at both ends by the winding reel body 10, making it difficult for the planetary gear 60 to tilt and preventing it from contacting the spool shaft 31.

[0057] like Figures 3-7 As shown, the planetary gear 60 is formed as a disk shape with its center coaxial with the drum shaft 31, and has a gear portion 65 (tooth portion) on its outer periphery.

[0058] When viewed from the side in a direction orthogonal to the drum axis X, the gear portion 65 is positioned approximately in the same position as the engagement groove 64 described later, and is configured to engage with the teeth of the drive gear.

[0059] Thus, planetary gear 60, as Figure 1 As shown, a rotation transmission mechanism 40 is formed, which rotates in conjunction with the handle 20 to transmit the rotation of the handle 20 to the drum 30, and also forms a clutch mechanism 50 that reciprocates along the direction of the drum shaft 31 in response to the operation of the clutch operating component 14.

[0060] On the end face of the first end 60b on the drum 30 side of the planetary gear 60, a recess 63 is formed in the central part on the radially inward side along the drum axial direction X. In the recess 63, an engagement groove 64 (engaged part) is provided, which can engage and disengage relative to the clutch pin 51 when the rotation of the handle 20 is transmitted to the drum 30.

[0061] A generally circular protrusion 631 is formed in the center of the recess 63. The height of the protrusion 631 along the axial direction X of the drum (from the first end 60b to the upper surface 631a of the protrusion 631) is smaller than the recess size of the recess 63. In the protrusion 631, stepped portions 632 are formed at two locations along the circumferential direction surrounding the drum axis. Furthermore, the aforementioned groove-shaped engaging groove 64 is provided at the lower step portion of these stepped portions 632.

[0062] The stepped portion 632 is positioned opposite each other across the through hole 60a (drum shaft 31), and the upper stepped portion 632A and the lower stepped portion (engaging groove 64) are arranged counterclockwise in the drum axial direction X when viewed from the direction toward the first end 60b. The stepped portion 632 is configured such that the circumferential width dimension of its radially upward center end orthogonal to the drum shaft 31 is smaller than the radius of the cross-section of the clutch pin 51.

[0063] Furthermore, at least a portion of the gear portion 65 and the engagement groove 64 overlap in the axial direction X of the drum.

[0064] A pair of engagement grooves 64 are provided in a straight line along the radial direction of the spool shaft 31. The engagement grooves 64 are formed radially at the end face of the first end 60b located on the bottom surface of the recess 63. The two engagement grooves 64 each have a bottom 64a, a first wall portion 64b, and a second wall portion 64c. The bottom 64a is recessed from the first end 60b and is arranged along the rotation direction of the planetary gear 60. The first wall portion 64b is a wall portion arranged upstream of the planetary gear 60 in the winding direction of the engagement groove 64. The second wall portion 64c is a wall portion arranged facing the first wall portion 64b downstream of the planetary gear 60 in the winding direction of the engagement groove 64.

[0065] The first wall portion 64b is formed such that, when rotation from the drum 30 to the wire release direction is transmitted via the clutch pin 51, the planetary gear 60 is subjected to force in the direction away from the drum 30 (clutch disengagement direction) by means of the clutch pin 51.

[0066] Next, the function of the double-bearing winding wheel 1 with this configuration will be explained in detail based on the accompanying drawings.

[0067] In the double-bearing winding wheel 1 of this embodiment, as follows: Figures 3-5 As shown, the rotation of the handle 20 is transmitted to the drum 30 via the planetary gear 60, and a clutch is provided to switch the transmission on and off. The drum shaft 31 of the drum 30 has a clutch pin 51, and the planetary gear 60 has a gear portion 65 and an engagement groove 64. The gear portion 65 has teeth on its outer periphery, and the engagement groove 64 engages with the clutch pin 51 when the clutch that transmits the rotation of the handle 20 to the drum 30 is engaged. At least a portion of the gear portion 65 and the engagement groove 64 overlap in the drum axial direction X.

[0068] Thus, at least a portion of the clutch pin 51 engages with the engagement groove 64 relative to the planetary gear 60 in an overlapping state in the direction of the drum shaft 31, so that the double-bearing winding wheel 1 can be miniaturized in the drum axial direction X.

[0069] Furthermore, in this embodiment, the engagement groove 64 is disposed on the gear portion 65 of the planetary gear 60, so it can be machined by means of the end of the end mill rather than by means of the side of the end mill. Therefore, it is not necessary to have a long extension in the axial direction X of the drum as in the past, and the double bearing winding wheel 1 can be miniaturized in the axial direction X of the drum.

[0070] Furthermore, in this embodiment, the clutch pin 51 protrudes radially outward from the drum shaft 31 of the drum 30, and at least a portion of the planetary gear 60 engages with the engagement groove 64 in an overlapping state in the drum axial direction X, so as a double-bearing winding wheel 1, it can be miniaturized in the drum axial direction X.

[0071] Furthermore, in this embodiment, a recess 63 is formed in the central part of the radially inner side of the gear portion 65, which is recessed in the direction of the drum shaft 31, and an engagement groove 64 for engaging the clutch pin 51 is provided in the recess 63.

[0072] Therefore, the clutch pin 51 engages with the engagement groove 64 provided in the recess 63 of the gear section 65, so that the overlap of the drum axis X of the gear section 65 and the engagement groove 64 can be increased, and the miniaturization of the double bearing winding wheel 1 can be carried out more effectively.

[0073] Furthermore, in this embodiment, a stepped portion 632 is formed in the recess 63 along the circumferential direction surrounding the drum shaft, and a groove-shaped engaging groove 64 is provided at the lowest position of the stepped portion 632.

[0074] Therefore, a stepped portion 632 is provided in the gear portion 65 of the planetary gear 60, so that the clutch pin 51 can be guided to the engagement groove 64, i.e., the engagement position, by means of the stepped portion 632 to engage.

[0075] Furthermore, in this embodiment, by providing a stepped portion 632, machining can be performed using the end portion of the end mill.

[0076] Furthermore, in this embodiment, the cross-section of the clutch pin 51 is circular, and the circumferential width of the stepped portion 632 of the recess 63 at the radially central end orthogonal to the drum shaft 31 is smaller than the radius of the cross-section of the clutch pin 51.

[0077] As a result, the width of the central end of the stepped portion 632 becomes narrower, so the clutch pin 51, which is temporarily moved to the stepped portion 632, will not remain in the stepped portion 632 and will easily fall from the stepped portion 632 into the engaged portion 64. That is, in this case, the clutch pin 51 can be reliably guided into the engaged groove 64.

[0078] According to the double-bearing winding wheel 1 of this embodiment configured as described above, the double-bearing winding wheel 1 can be miniaturized in the axial direction.

[0079] The embodiments of the dual-bearing winding wheel of the present invention have been described above, but these embodiments are presented as examples and are not intended to limit the scope of the invention. Furthermore, the embodiments can be implemented in various ways, and various omissions, substitutions, and modifications can be made without departing from the spirit of the invention. Embodiments and their variations include, for example, substantially identical and equivalent solutions that are readily conceived by those skilled in the art.

[0080] For example, in this embodiment, the engaging portion is provided as a clutch pin 51 that protrudes radially outward from the drum shaft 31 of the drum 30, but is not limited to providing a clutch pin 51 in this manner.

[0081] Furthermore, in this embodiment, a recess is formed in the central part of the radially inner side of the gear portion 65, which is recessed in the axial direction X of the drum. The recess 63 has an engagement groove 64 for engaging the clutch pin 51, but it is not limited to this.

[0082] Furthermore, in this embodiment, a stepped portion 632 is formed in the recess 63 along the circumferential direction surrounding the drum shaft, and a groove-shaped engaging groove 64 is provided at the lowest position of the stepped portion 632, but it is not limited to this.

[0083] Furthermore, in this embodiment, the clutch pin 51 has a circular cross-section, and the stepped portion 632 is configured such that the circumferential width dimension of the end of the radially central side orthogonal to the drum shaft 31 is smaller than the radius of the cross-section of the clutch pin 51, but is not limited thereto.

[0084] Explanation of reference numerals in the attached figures 1 Double-bearing winding reel 10. Winding reel body 20 handles 30 rolls 31. Roller shaft 40 Rotary transmission mechanism 41 Drive gear shaft 50 Clutch Mechanism 51 Clutch pin (engaging part) 60 Planetary Gears 63 recess 64. Engaging slot (engaged part) 65 Gear section 632 Step section X represents the axial direction of the drum.

Claims

1. A double-bearing reel, wherein the double-bearing reel transmits rotation of a handle to a drum via a planetary gear, and includes a clutch for switching the transmission on and off, characterized in that... The aforementioned drum shaft has an engaging portion. The aforementioned planetary gear has a gear portion and an engaging portion. The gear portion has teeth on its outer periphery. The engaging portion engages with the engaging portion when the clutch is engaged, which transmits the rotation of the aforementioned handle to the aforementioned drum. At least a portion of the aforementioned teeth and the aforementioned engaged portion overlap in the axial direction of the drum.

2. The double-bearing winding reel as described in claim 1, characterized in that, The aforementioned engaging part is a clutch pin that protrudes radially outward from the axial direction of the aforementioned drum.

3. The double-bearing winding reel as described in claim 2, characterized in that, A recess is formed in the center of the radially inner side of the aforementioned gear portion, which is recessed on the aforementioned drum shaft. The aforementioned recess is provided with the aforementioned engaged portion for engaging the aforementioned clutch pin.

4. The double-bearing winding reel as described in claim 3, characterized in that, In the aforementioned recess, a stepped portion is formed along the circumference surrounding the aforementioned roller shaft. A groove-shaped engaging portion is provided at the lowest position of the aforementioned stepped portion.

5. The double-bearing winding reel as described in claim 4, characterized in that, The aforementioned clutch pin has a circular cross-section. The circumferential width of the aforementioned stepped portion at its radially central end, which is orthogonal to the aforementioned drum shaft, is smaller than the radius of the cross-section of the aforementioned clutch pin.

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