JP2014042471A - Double bearing type reel - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a double bearing type reel which inhibits malfunction of changeover operation of a pinion gear, which may be caused by shaving-off of a yoke.SOLUTION: A double bearing type reel includes: a drive gear which can be rotated by take-up operation of a handle; a pinion gear movably provided between a connecting position and a separating position along the axial direction of a spool shaft and engaged with the spool shaft at the connecting position to transmit the rotation of the drive gear to the spool shaft; a yoke disposed so as to be engaged with the small-diameter part of the pinion gear and including a yoke body formed of resin; an urging spring for urging the yoke in one direction to hold the pinion gear at the connecting position; and a clutch cam for holding the pinion gear at the separating position by moving the yoke in the other direction according to the movement of an operation part. The yoke includes a reinforcement member harder than the yoke body on a part of or on the whole of a contact surface contacting the small diameter part of the yoke body.

Description

  The present invention relates to a double bearing type reel.

  The dual-bearing type reel generally includes a reel body, a handle provided on the reel body, and a spool that is pivotally supported on each of the left and right side plates of the reel body. In a typical dual-bearing type reel, the rotation of the handle is transmitted to the spool via a drive gear that rotates with the handle and a pinion gear that is arranged to mesh with the drive gear. Such a double-bearing type reel is disclosed in, for example, Japanese Patent Application Laid-Open No. 2000-139298 (Patent Document 1).

  As shown in Patent Document 1, a dual-bearing type reel is generally provided with a clutch mechanism, and the pinion gear is provided so as to be movable along the axial direction of the spool shaft by the operation of the clutch mechanism. When the pinion gear is in the coupling position where it engages with the spool shaft, the rotation of the handle is transmitted to the spool shaft via the drive gear and the pinion gear, while when the pinion gear is in the separated position separated from the spool shaft, the handle is Separated from the spool shaft, the spool is in a free rotating state.

  Generally, a small-diameter portion that receives a yoke (sometimes called a clutch plate, a clutch yoke, or a pinion support plate) is formed on the outer peripheral surface of the pinion gear. The yoke is generally made of a resin such as polyoxymethylene, and is always urged in one direction along the axial direction of the spool shaft, and the pinion gear is held at the coupling position by the urging of the spring. The yoke is moved in the other direction of the spool shaft against the biasing force of the spring by a clutch cam that moves (rotates, slides, etc.) according to the operation of the clutch operating portion, and holds the pinion gear in the separation position. Can do.

JP 2000-139298 A

  In order to improve fishing results, there is a need for a double-bearing type reel that can increase the number of castings by increasing the winding speed during actual fishing, i.e., improving the rewinding. To increase the winding speed, A high gear ratio of drive gear and pinion gear is achieved. In the double-bearing type reel, in order to avoid an increase in the size of the reel, a high gear ratio is achieved by reducing the outer diameter of the pinion gear instead of increasing the outer diameter of the drive gear. Therefore, the contact area between the pinion gear and the yoke engaged with the small-diameter portion of the pinion gear is reduced, and the resin yoke is easily scraped by the metal pinion gear during the winding operation. If the yoke is shaved, the clutch yoke and the small diameter portion of the pinion gear may not be sufficiently engaged when the clutch is turned off, and the pinion gear may not be moved to the separation position by the clutch yoke. As described above, when the yoke is shaved, an operation failure is likely to occur in the switching operation of the pinion gear.

  Therefore, according to various embodiments of the present invention, in the dual-bearing type reel, a malfunction of the pinion gear switching operation that may occur when the yoke is shaved is suppressed.

  A dual-bearing reel according to an embodiment of the present invention is a dual-bearing reel that rotates a spool provided on a reel body around a spool shaft by rotating a handle. In one embodiment of the present invention, the dual-bearing reel is movable between a drive gear that can be rotated by the winding operation of the handle and a connecting position and a separating position along the axial direction of the spool shaft. A pinion gear that engages with the spool shaft at the coupling position and transmits the rotation of the drive gear to the spool shaft; and a yoke main body made of resin that is arranged to engage with a small diameter portion of the pinion gear. A yoke having a biasing spring that biases the yoke in one direction to hold the pinion gear in the coupling position, and moves the yoke in the other direction in accordance with the movement of the operation unit, thereby separating the pinion gear. A yoke operating member held in position. In one aspect, the yoke includes a reinforcing member that is harder than the resin on part or all of the contact surface that contacts the small diameter portion of the yoke body.

  According to various embodiments of the present invention, in a dual-bearing type reel, it is possible to suppress a malfunction of the pinion gear switching operation that may occur when the yoke is shaved.

The figure which shows the double bearing type reel for fishing which concerns on one embodiment of this invention. The figure which shows the structure of the clutch mechanism in the double bearing type reel for fishing which concerns on one embodiment of this invention. The fragmentary sectional view (clutch ON state) of the double bearing type reel for fishing concerning one embodiment of the present invention. The fragmentary sectional view (clutch OFF state) of the double bearing type reel for fishing concerning one embodiment of the present invention. The figure which shows the clutch yoke in the double bearing type reel for fishing which concerns on one embodiment of this invention. Sectional drawing along the AA line of FIG. The figure which shows the components of the clutch yoke in the double bearing type reel for fishing which concerns on other embodiment of this invention. The figure which shows the clutch yoke in the double bearing type reel for fishing which concerns on other embodiment of this invention. The figure which shows the clutch yoke in the double bearing type reel for fishing which concerns on other embodiment of this invention. Sectional drawing along the BB line of FIG. The figure which shows the clutch yoke in the double bearing type reel for fishing which concerns on other embodiment of this invention.

  Hereinafter, various embodiments of the present invention will be described with reference to the drawings as appropriate. In each drawing, common constituent elements are given the same reference numerals. Moreover, each drawing is not necessarily shown to an exact scale for convenience of explanation.

  As shown in FIG. 1, a reel body 1 of a dual bearing reel for fishing according to an embodiment of the present invention includes a left frame 3a, a right frame 3b, a left side plate 5a, and a right side plate 5b. . The side plates 5a and 5b are attached to the outside of the corresponding frames 3a and 3b by screws, screwing, fitting or the like. A spool shaft 8 is rotatably supported between the left and right frames 3a and 3b via left and right bearings 7a and 7b. A spool 8b around which a fishing line (not shown) is wound is fixed to the spool shaft 8.

  A handle shaft 10a is rotatably supported on the right side plate 5b via a bearing 11. A handle 10 is attached to the tip of the handle shaft 10a. The space between the right frame 3b and the right side plate 5b accommodates a drive mechanism 20 that transmits the rotation of the handle 10 to the spool shaft 8 and rotates the spool 8b. The drive mechanism 20 includes a drive gear 25 attached to the handle shaft 10 a via a drag mechanism 27, and a pinion gear 21 disposed so as to mesh with the drive gear 25.

  As most clearly shown in the enlarged views of FIGS. 3 and 4, the pinion gear 21 includes an engagement groove 21c formed at the axially inner end thereof and a cylindrical portion fitted to the pinion shaft 8a. A tooth portion 21d formed on the outer periphery of the tooth 21a, and a small diameter portion 21b formed between the tooth portion 21d and the engaging groove 21c and having a smaller diameter than the tooth portion 21d. The pinion shaft 8a is arranged coaxially with the spool shaft 8, and the pinion gear 21 is supported so as to rotate around the pinion shaft 8a. The pinion gear 21 is provided to be movable between a connection position close to the spool shaft 8 and a separation position far from the spool shaft 8 in accordance with an ON / OFF state of a clutch mechanism described later. FIG. 3 shows the pinion gear 21 in the coupling position, and FIG. 4 shows the pinion gear 21 in the separation position. As shown in FIG. 3, when the pinion gear 21 is in the coupling position, the engagement pin 8 b provided so as to protrude in the radial direction on the spool shaft 8 engages with the engagement groove 21 c of the pinion gear 21. The rotation of the pinion gear 21 is transmitted to the spool shaft 8 by the engagement pin 8b engaging with the engagement groove 21c. Thus, the state in which the rotation of the handle shaft 10a is transmitted to the spool shaft 8 via the drive gear 25 and the pinion gear 21 is referred to as a clutch ON state. On the other hand, as shown in FIG. 4, when the pinion gear 21 is in the separated position, the engagement pin 8b is disengaged from the engagement groove 21c, and the rotation of the pinion gear 21 (and hence the rotation of the handle shaft 10a) is not transmitted to the spool shaft 8. It will be in the OFF state.

  The pinion gear 21 is provided with a small-diameter portion 21b formed in a groove shape that has a smaller diameter than the tooth portion 21d and extends in the circumferential direction on the outer peripheral surface of the pinion gear 21. As shown in the figure, the clutch yoke 23 is engaged with the small diameter portion 21b. The clutch yoke 23 is constantly urged by a biasing spring 26 in one direction along the pinion shaft (a direction approaching the spool shaft 8, that is, inward in the spool shaft direction). The pinion gear 21 is held at the coupling position. Details of the clutch yoke 23 will be described later.

  The drive gear 25 is formed in a cylindrical shape having an open front surface (surface on the handle 10 side) and closed back surface, and a drag mechanism 27 is accommodated therein. The drag mechanism 27 includes, for example, a metal washer arranged to rotate integrally with the drive gear 25, a plurality of metal washers fixed to the handle shaft 10a, and a lining material arranged between the metal washers. And a desired drag force can be applied by rotating the drag operation lever 30 screwed to the handle shaft 10a and pressing the friction engagement member in the axial direction. it can.

  A gear 35 is rotatably provided on the base end side of the handle shaft 10a. The gear 35 is provided in a plurality of holes formed on the back surface (surface on the side opposite to the handle 10) of the drive gear 25 described above. A plurality of projections that can be fitted are provided. For this reason, the gear 35 always rotates integrally with the drive gear 25.

  The back surface of the gear 35 (the surface opposite to the surface on which the plurality of protrusions are provided) is formed in a flat shape and is in contact with a clutch return gear 37 that is fixed to the handle shaft 10a. Further, the base end portion of the handle shaft 10a is rotatably supported by the right frame 3b via a bearing 38.

  According to the configuration described above, the rotation of the handle shaft 10 a when the handle 10 is rotated in the clutch ON state is transmitted to the pinion gear 21 via the drive gear 25. At this time, when the spool shaft 8 engaged with the pinion gear 21 rotates in conjunction with the pinion gear 21, the spool 8b rotates in the fishing line winding direction. In this way, the fishing line can be wound up by rotating the handle 10 in the clutch ON state.

  FIG. 2 shows the configuration of the clutch mechanism viewed from the handle 10 side in a state where the handle 10 and the right side plate 5b are removed. FIG. 2 shows the clutch mechanism in the clutch-on state.

  As shown in the figure, the clutch mechanism includes a clutch lever 50 that can be manually turned off, a clutch cam 52 that rotates in conjunction with the turning-off operation of the clutch lever 50, and rotation of the clutch cam 52. A clutch yoke 23 that moves in conjunction with each other and a return operation piece 54 that engages with the clutch return gear 37 when the clutch is switched from ON to OFF. The clutch cam 52 is supported so as to be rotatable between the clutch ON position and the clutch OFF position around the pinion shaft 8a. The rotation range of the clutch cam 52 is regulated by a boss 51 protruding from the right frame 3b.

  The right frame 3b is provided with a pair of guide shafts 56a and 56b extending in parallel with the pinion shaft 8a. The clutch yoke 23 is guided in the axial direction of the pinion shaft 8a by the pair of guide shafts 56a and 56b. Has been. In addition, the clutch yoke 23 is constantly pressed in the direction of the clutch cam 52 by the biasing spring 26 while being engaged with the small diameter portion 21 b of the pinion gear 21. Since the clutch yoke 23 is engaged with the small diameter portion 21 b of the pinion gear 21, when the clutch yoke 23 is pressed and moved in the direction of the clutch cam 52, the pinion gear 21 moves to the coupling position and engages with the spool shaft 8.

  A surface cam 58 is formed on the surface of the clutch cam 52 facing the clutch yoke 23. When the clutch cam 52 is rotated by the clutch OFF operation of the clutch lever 50 (operation for rotating the clutch lever 50 downward in FIG. 2), the face cam 58 is engaged with the clutch yoke 23, and the clutch yoke 23 is energized. The spring 26 moves against the biasing force of the spring 26 in the direction away from the spool shaft 8 (outward in the spool shaft direction) along the guide shafts 56a and 56b. As a result, the clutch yoke 23 moves to the separation position in the direction away from the clutch cam 52, and the engagement state between the pinion gear 21 and the spool shaft 8 is released.

  Further, in order to hold the clutch cam 52 at the clutch ON position and the clutch OFF position, a hold spring 60 is provided in the clutch mechanism. One end of the hold spring 60 is supported by the clutch cam 52, and the other end is supported by the flange 64 of the right frame 3b. The hold spring 60 causes the spring force in the clockwise direction in FIG. 2 to act on the clutch cam 52 in the clutch ON state shown in FIG. 2, and the spring force in the counterclockwise direction in FIG. 52.

  A long hole is formed in the return working piece 54, and a guide shaft 56a is inserted into the long hole. Accordingly, the return working piece 54 is disposed so as to be swingable about the guide shaft 56a. The return operating piece 54 is provided with an engaging portion 66 that can be engaged with the clutch return gear 37.

  Further, the clutch mechanism may include an urging spring 68 having one end locked to the return operation piece 54 and the other end locked to the flange 64 of the right frame 3b. The urging spring 68 constantly urges the return operating piece 54 in the direction in which the engaging portion 66 engages with the clutch return gear 37.

  Further, the clutch mechanism of the present embodiment may include an operation restricting portion 72. The operation restricting portion 72 is formed in a cam shape that is inclined by a predetermined angle with respect to an arc-shaped locus centering on the spool shaft 8. A contact portion 74 that can contact the operation restricting portion 72 is formed on the return operation piece 54. The contact portion 74 contacts the lower end 72a of the operation restricting portion 72 by the spring force of the urging spring 68 acting on the return operation piece 54 in the clutch ON state shown in FIG. The contact portion 74 slides from the lower end 72a of the operation restricting portion 72 toward the upper end 72b when switching from the clutch ON state to the clutch OFF state, and disengages from the upper end 72b of the operation restricting portion 72 in the clutch OFF state. It is configured.

  Thus, in the clutch ON state shown in FIG. 2, the spring force in the clockwise direction in the drawing acts on the clutch cam 52 by the hold spring 60. At this time, the return operating piece 54 is maintained in a state in which the contact portion 74 is in contact with the lower end 72 a of the operation restricting portion 72 by the spring force of the biasing spring 68. In this case, the engaging portion 66 of the return working piece 54 is in a non-engaged state separated from the clutch return gear 37 by a predetermined distance. In this state, by rotating the handle 10 to rotate the handle shaft 10a, the spool 8b can be rotated in the fishing line winding direction.

  When the clutch lever 50 is depressed to switch from the clutch ON state to the clutch OFF state, the clutch cam 52 rotates in the counterclockwise direction in FIG. At this time, the surface cam 58 engages with the clutch yoke 23 to move the clutch yoke 23 outward from the spool shaft. Further, the operation restricting portion 72 maintains the state inclined by a predetermined angle with respect to the arc-shaped locus with respect to the rotation shaft (spool shaft 8) of the clutch cam 52, and with the rotation of the clutch cam 52. Move. As the operation restricting portion 72 moves in this manner, the contact portion 74 slides from the lower end 72a of the operation restricting portion 72 toward the upper end 72b.

  In the clutch OFF state, the clutch yoke 23 has moved to the disengaged position, whereby the engagement between the pinion gear 21 and the spool shaft 8 is released, and the spool shaft 8 can freely rotate. Further, the contact portion 74 of the return working piece 54 is disengaged from the upper end 72 b of the operation restricting portion 72. At this time, the return actuating piece 54 swings counterclockwise in FIG. 2 around the guide shaft 56a by the spring force of the biasing spring 68 in the contraction direction, and the engaging portion 66 is engaged with the clutch return gear. 37 is engaged. Thus, the engaging portion 66 engages with the return gear 37, whereby the clutch cam 52 is held at the clutch OFF position, and the spool shaft 8 is held in a freely rotatable state.

  In order to switch from the clutch OFF state to the clutch ON state, when the handle 10 is rotated in the winding direction as is well known, the clutch cam 52 is rotated clockwise via the clutch return gear 37 and the return operation piece 54. The hold spring 60 is urged and held in the ON state.

  Next, the clutch yoke 23 in the double bearing type reel for fishing according to an embodiment of the present invention will be described in more detail with reference to FIGS. FIG. 5 shows a clutch yoke 23 provided in a fishing double-bearing reel according to an embodiment of the present invention, and FIG. 6 is a cross-sectional view taken along line AA of FIG. FIG. 5 shows a view of the clutch yoke 23 as viewed from the outside in the axial direction of the spool shaft 8. As illustrated, the clutch yoke 23 includes a yoke main body 23a and a reinforcing member 23b attached to the yoke main body 23a. The yoke body 23a is made of a resin such as polyoxymethylene. The resin used as the material of the yoke body 23a is not limited to polyoxymethylene, and any industrial resin suitable as the material of the clutch yoke of the double-bearing type reel can be used as the material of the yoke body 23a.

  The yoke body 23a includes a substantially semicircular central portion 82 having a locking groove 81 that engages with the small diameter portion 21b of the pinion gear 21, linear arm portions 83 and 84 extending from the central portion 82 to both sides, And approximately circular end portions 85 and 86 formed at the tips of the arm portions 83 and 84, respectively. Guide grooves 87 and 88 through which the guide shafts 56a and 56b are inserted are formed in the end portions 85 and 86, respectively.

  The yoke body 23a is formed with a substantially T-shaped recess, and the reinforcing member 23b is configured to have a substantially T-shaped outer shape that substantially matches the recess. The reinforcing member 23b is attached to the yoke body 23a by welding, for example. The reinforcing member 23b is made of, for example, various alloys such as SUS and copper alloy, or various metals such as aluminum whose surface is anodized, but the material of the reinforcing member 23b is not limited to these, and the yoke body Any material harder than 23a can be used. In the present specification, “hard” means that the hardness is high. The hardness of the yoke main body 23a and the hardness of the reinforcing member 23b are compared by, for example, Vickers hardness.

  In FIG. 5, two two-dot chain circles are shown concentrically with the locking groove 81 of the central portion 82. Of these, the outer circle C indicates the outer periphery of the peak portion of the tooth portion 21 d of the pinion gear 21. Therefore, the area inside the circle C of the clutch yoke 23 comes into contact with the wall surface of the small diameter portion 21 b of the pinion gear 21. In this sense, a region on the inner side of the circle C in FIG. 5 in the surface of the clutch yoke 23 facing outward in the axial direction of the spool shaft 8 may be referred to as a “contact region” in this specification. The reinforcing member 23b is provided so as to exist in at least a part of the contact area. In the embodiment shown in FIG. 5, the contact member 23b is arranged with respect to the yoke body 23a so that the lower end of the reinforcing member 23b exists near the top of the semicircular arc-shaped contact region.

  The shape and arrangement of the reinforcing member 23b shown in FIG. 5 is merely an example, and the shape of the reinforcing member 23b and its attachment position with respect to the yoke body 23a are such that at least a part of the reinforcing member 23b exists in at least a part of the contact area. As long as it is optional. The reinforcing member 23b may exist on the entire contact area. For example, in the embodiment shown in FIG. 11 to be described later, the entire contact area is covered with a reinforcing member. Further, by forming the lower end of the reinforcing member 23b shown in FIG. 5 in an arc shape corresponding to the contact area, the entire surface of the contact area can be covered with (a part of) the reinforcing member 23b.

  In a dual bearing type reel having a low-speed gear ratio specification in which the outer diameter of the pinion gear 21 is relatively large, the clutch yoke 23 is not easily scraped by the pinion gear 21, and the reinforcing member 23b can be omitted. In the clutch yoke 23 shown in FIG. 5, since the reinforcing member 23b is provided only in a part of the contact area, the double-bearing type reel having a low gear ratio specification in which the outer diameter of the pinion gear 21 is relatively large is The clutch yoke 23 (that is, the yoke body 23a) in which the reinforcing member 23b is omitted can be installed, and the high-speed gear ratio dual-bearing type reel in which the outer diameter of the pinion gear 21 is relatively small is provided on the yoke body 23a and the reinforcing member 23b. Can be attached to form the clutch yoke 23 shown in FIG. 5, and the clutch yoke 23 can be installed on the reel. Thus, by providing the reinforcing member 23b only in a part of the contact area of the clutch yoke 23, the clutch yoke can be shared by the reel with the low speed gear ratio specification and the reel with the high speed gear ratio specification.

  Further, by providing the reinforcing member 23b only in a part of the contact area of the clutch yoke 23, the contact area of the clutch yoke 23 includes a part made of resin and a part provided with the reinforcing member 23b. Thereby, while maintaining the strength of the clutch yoke 23, it is possible to reduce noise generated by the contact between the high-strength reinforcing member 23 b and the pinion gear 21 when the pinion gear 21 rotates.

  A clutch yoke 23 ′ in a fishing double bearing reel according to another embodiment of the present invention will be further described with reference to FIGS. 7 and 8. FIG. 7 shows components of a clutch yoke in a fishing double bearing type reel according to another embodiment of the present invention, and FIG. 8 shows the clutch yoke after assembly.

  As shown in the drawing, a substantially T-shaped recess 89 is formed in the yoke body 23 a ′, and the reinforcing member 23 b ′ is formed so that its contour substantially matches the contour of the recess 89. Further, a screw hole H1 is formed in the recess 89, and a screw hole H2 is formed at a position corresponding to the screw hole H1 of the reinforcing member 23b '. As shown in FIG. 8, the reinforcing member 23 b ′ is screwed to the yoke body 23 a ′ using a screw S. Thereby, the reinforcing member 23b 'can be more reliably attached to the yoke body 23a'.

  A clutch yoke 23 "in a fishing double-bearing reel according to still another embodiment of the present invention will be further described with reference to Figs. 9 and 10. Fig. 9 shows another embodiment of the present invention. FIG. 10 shows a sectional view taken along line B-B in FIG. 9.

  As shown in the figure, in the present embodiment, a substantially rectangular concave portion 90 is formed in the central portion 82 of the clutch yoke 23 ″. Of the side walls defining the concave portion 90, the side walls connected to the right arm 84 are formed on the side walls. A convex portion P that protrudes toward the inside of the concave portion 90 is formed. The top portion of the central portion 82 of the yoke body 23a ″ is spaced from the bottom portion of the concave portion 90 and extends inside the concave portion 90. A claw T is formed.

  The reinforcing member 23b ″ is formed so that its contour substantially coincides with the contour of the concave portion 90, and an engaging concave portion that engages with the convex portion P is formed at a position corresponding to the convex portion P. In addition, a substantially semicircular through hole corresponding to the locking groove 81 is formed on the lower end side of the reinforcing member 23b ″. By inserting the reinforcing member 23b ″ thus configured into the recess 90, the clutch yoke 23 ″ shown in FIG. 9 is obtained. In the clutch yoke 23 ″, the vertical movement of the reinforcing member 23b ″ in FIG. 9 is restricted by the convex portion P, and the movement of the reinforcing member 23b ″ in the front direction of FIG. 23b ″ can be securely attached to the yoke body 23a ″.

  FIG. 11 shows a modification of the clutch yoke 23 ″ shown in FIG. 10. In the embodiment shown in FIG. 11, the claw T is removed from the yoke body 23a ″, and instead, the reinforcing member 23b ″ is screwed. S is used to screw the yoke body 23a ″. Also in the embodiment of FIG. 11, the reinforcing member 23b ″ can be securely attached to the yoke body 23a ″.

  As described above, in various embodiments of the present invention, a reinforcing member that is harder than the yoke body is provided in at least a part of the contact area that contacts the wall surface of the small-diameter portion of the pinion gear in the outer surface of the clutch yoke. The clutch yoke is less likely to be scraped when the clutch is switched than a conventional clutch yoke that does not include a reinforcing member. Conventionally, when the clutch yoke is scraped, the clutch yoke and the small diameter portion of the pinion gear are not sufficiently engaged when the clutch is turned off, and the pinion gear may not be moved to the separation position by the clutch yoke. In the embodiment of the invention, since the clutch yoke is hard to be scraped, the occurrence of such a problem can be prevented or suppressed.

  Further, since the reinforcing member is attached to the yoke body by a method such as welding, screwing, fitting, or a combination thereof, it is possible to prevent the reinforcing member from dropping from the yoke body more reliably than when an adhesive is used.

8 Spool shaft 21 Pinion gears 23, 23 ', 23 "Clutch yokes 23a, 23a', 23a" Yoke body 23b, 23b ', 23b "Reinforcing member

Claims (5)

A double-bearing type reel that rotates a spool provided on a reel body around a spool shaft by rotating a handle;
A drive gear that can be rotated by a winding operation of the handle;
A pinion gear provided so as to be movable between a connecting position and a separating position along an axial direction of the spool shaft, and engaging with the spool shaft at the connecting position to transmit rotation of the drive gear to the spool shaft; ,
A yoke that is arranged to engage with the small diameter portion of the pinion gear and includes a yoke body made of resin;
A biasing spring that biases the yoke in one direction to hold the pinion gear in the coupling position;
A yoke operating member that holds the pinion gear in the separation position by moving the yoke in the other direction in accordance with the movement of the operation unit;
With
The yoke includes a reinforcing member that is harder than the yoke body on a part or all of the contact surface that contacts the small diameter portion of the yoke body.
Double bearing type reel.   The dual bearing reel according to claim 1, wherein the reinforcing member is provided on a part of the contact surface. The reinforcing member is welded to the yoke body.
The double-bearing type reel according to claim 1 or 2. The reinforcing member is screwed to the yoke body.
The double-bearing type reel according to claim 1 or 2. The reinforcing member is fitted into the yoke body.
The double-bearing type reel according to claim 1 or 2.

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