JP2010000042A - Spinning reel - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a spinning reel which can impart a sufficient braking force to a drive gear, can stabilize braking performance, and can lighten a braking mechanism. <P>SOLUTION: This spinning reel 10 includes a braking plate 64 locked and fit to a handle shaft in a state capable of being moved in the axial direction of the handle shaft 36, and a drive gear 50 pressed through a frictional plate 62 disposed between the braking plate and the drive gear, when the braking plate is moved in the axial direction of the handle shaft. The braking plate has a base 82 which is moved toward the drive gear along the axial direction of the handle shaft, a first reinforcing portion 84 extended from the base in the radial outer direction relative to the handle shaft and disposed on the side opposite to the drive gear-arranged side, and a second reinforcing portion 86 circularly formed at the radial outer direction end relative to the base of the braking plate and extended in the direction opposite to the drive gear-arranged side. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a fishing reel, and more particularly to a fishing reel provided with a mechanism for applying a braking force to a drive gear that continuously rotates when a fishing line is fed out by operating a braking force adjusting body provided on a handle shaft. Reel related.

  In general, a fishing reel braking device (drag mechanism) applies a braking force to a spool rotatably supported between side plates of a reel body. In such a braking device, a drive gear is rotatably disposed on a handle shaft supported by one side plate, and the drive gear is frictionally coupled to the handle shaft by a brake member and is screwed onto the handle shaft. The frictional coupling force between the drive gear and the handle shaft, that is, the braking force applied to the spool can be adjusted by rotating the body and adjusting the axial pressing force of the braking member to be strong or weak.

Then, the braking force adjuster (star drag) is rotationally operated with the brake plate and the friction lining material fitted to the drive gear rotatably supported by the handle shaft so as to be movable along the axial direction of the handle shaft. A fishing reel provided with a braking device that adjusts the frictional coupling force (drag force) with respect to the handle shaft by pressing the handle shaft is known, for example, in Patent Document 1. The fishing reel disclosed in Patent Document 1 is an end portion of a seal member in which a flat brake plate fitted to a handle shaft so as to be movable in the axial direction is mounted on the outer periphery of a cylinder portion of a drive gear. Has a structure in which it is pressed inward in the axial direction by a pressing plate having an outer peripheral surface with which the abuts.
JP 2005-204616 A

  By having the structure disclosed in Patent Document 1, transmission of the pressing force by the pressing plate to the braking portion (the braking plate, the friction lining material, and the friction surface of the drive gear) is separated from the pressing plate by the braking plate. Loss due to the separation structure reduces transmission efficiency, and it is difficult to obtain sufficient braking force and stable braking performance. In addition, since the end of the seal member extends radially inward and contacts the outer periphery of the pressing plate, there is a restriction on increasing the pressing diameter of the pressing plate, and sufficient braking force In order to maintain it, it is necessary to increase the number of brake plates. For this reason, the braking mechanism becomes complicated and heavy.

  The present invention has been made based on such circumstances, and can provide a sufficient braking force to the drive gear, stabilize the braking performance, and reduce the weight of the braking mechanism. The purpose is to provide a reel.

  The fishing reel of the present invention that achieves the above object is provided with a braking plate that is fixed to the handle shaft so as to be movable in the axial direction of the handle shaft, and a control plate disposed on the handle shaft. A drive gear that is pressed through a friction plate disposed between the brake plate and the brake plate when the brake plate is moved in the axial direction of the handle shaft by an operation of a power adjustment body; A base portion that moves in the direction of the drive gear along the axial direction of the handle shaft by the operation of the braking force adjuster, and extends radially outward from the base portion with respect to the axial direction of the handle shaft. A first reinforcing portion having a reinforcing meat portion on at least a part of the side close to the base portion on the opposite side to the side where the drive gear is disposed, and the base portion of the brake plate Annularly at the radially outer end against The made are together have side where the drive gears are disposed and a second reinforcing portion shaped flange that extends in opposite directions.

The drive gear includes a flange portion in which the second reinforcing portion is disposed, and the second reinforcing portion is engaged with an inner peripheral surface of the flange portion of the drive gear. It is preferable that an engaging member is provided.
Further, it is preferable that at least one of the seal member and the sounding body is disposed on the outer periphery of the second reinforcing portion.
Further, the inner peripheral surface of the base portion of the brake plate has a circular portion that is supported by being fitted to the handle shaft along the axial direction of the handle shaft, and a non-circular shape that is non-circularly fitted to the handle shaft. It is preferable that the parts are arranged in parallel.

  According to this fishing reel, when the braking plate is moved along the axial direction of the handle shaft by operating the braking force adjusting body, the braking plate is moved by the first reinforcing portion and the second reinforcing portion of the braking plate. The first reinforcing portion and the second reinforcing portion can be pressed against the friction plate (for example, friction lining material) with a stronger force. For this reason, it is possible to efficiently transmit and act on the pressing force from the brake plate to the friction plate with as little loss as possible, and to apply the braking force to the drive gear. Further, since the brake plate has the first and second reinforcing portions, the number of friction plates can be suppressed and the weight can be reduced. Therefore, according to the fishing reel, not only the braking performance is stable, but also a sufficient braking force can be generated and the number of braking plates can be reduced to reduce the weight.

1 to 4 show a fishing reel 10 according to a first embodiment of the present invention.
As shown in FIG. 1 as a whole, the fishing reel 10 of this embodiment is formed as a double-bearing type manually wound reel. The reel body 12 of the fishing reel 10 is formed in a circular shape or a circular shape on the outside of each of the pair of left and right frames 14a and 14b integrated by a connecting member or the like by, for example, screwing, screws or fitting means. Cylindrical side plates 16a and 16b are attached to form a rigid housing as a whole, and are fixed to a fishing rod via attachment legs (not shown).

  The spool 18 around which the fishing line is wound is rotatably supported between the left and right frames 14a and 14b. The right side plate 16 b supports a fishing line winding drive mechanism 22 that rotates the spool 18 via the spool shaft 20. In the right side plate 16b, various mechanisms such as a driving force transmission system and a drag system, which will be described later, of the fishing line winding drive mechanism 22 are accommodated in a space defined by the right frame 14b.

  Between the frames 14a and 14b of the reel body 12, both ends of a spool shaft 20 which is mounted with a spool 18 and rotates together with the spool 18 are rotatably supported via ball bearings 22a and 22b as shown in the figure, for example. Has been. A pinion shaft 20a disposed coaxially with the spool shaft 20 is disposed at an end portion protruding from one end side of the spool shaft 20 through the right frame 14b. The pinion shaft 20a abuts on the right end of the spool shaft 20 in the reel body 12, and the pressing force of the adjusting screw 24 provided on the right plate 16b acts on the spool shaft 20 to prevent the spool 18 from rattling. However, it is held at a predetermined position in the axial direction. On the pinion shaft 20a, a pinion gear 28 that is rotationally driven by the operation of the handle 26 is movably supported.

  The pinion gear 28 has a cylindrical structure through which the pinion shaft 20a is inserted, and is rotatable with respect to the reel body 12 and movable in the axial direction by bearings 30a and 30b supported by the right frame 14b and the right side plate 16b. It is supported. By turning ON / OFF a clutch mechanism (not shown) via a clutch lever (not shown) disposed between the left and right frames 14a and 14b, the pinion gear 28 is fitted to the spool shaft 20 as shown in FIG. It is possible to move between an engagement position that rotates integrally with the shaft 20 and a non-engagement position (not shown) in which the engagement state with the spool shaft 20 is released.

  The movement of the pinion gear 28 can be performed by moving the yoke 32 that engages with the circumferential groove 28a formed in the pinion gear 28 along the pinion shaft 20a in conjunction with the ON / OFF operation of the clutch mechanism. When the pinion gear 28 is disposed at the engagement position shown in FIG. 1, the fishing line can be wound with the clutch ON, and at the non-engagement position (not shown), the spool is in a spool-free rotation state with the clutch OFF. The fishing reel 10 of the present embodiment has a magnetic braking device 34 that prevents backlash by preventing over-rotation of the spool 18 when the fishing line is released in a clutch OFF state in which the spool 18 can freely rotate. Is provided at the end of the spool shaft 20 on the left frame 14a side.

  Further, a handle shaft 36 having a handle 26 attached to one end is disposed in the right side plate 16b in parallel with the pinion shaft 20a, and is rotated by rotating the handle 24.

  As shown in FIGS. 1 and 2, the handle shaft 36 is rotatably supported by the right frame 14b and the right side plate 16b via bearings 38a and 38b. A bearing 38b for supporting the handle shaft 36 on the handle 24 side is provided on a projecting portion 16c projecting in a substantially cylindrical shape on the right side plate 16b, and in the projecting portion 16c, the handle shaft 36 extends in the fishing line winding direction. A one-way clutch 40 that allows rotation and prevents reverse rotation is disposed as a reverse rotation prevention mechanism. Reference numeral 17 denotes a protective cover member that covers the protruding portion 16c.

  Further, the handle shaft 36 is formed with an annular groove 36a at a portion close to the base end portion 35 supported by the right frame 14b via the bearing 38a, and the retaining member 42 fitted into the annular groove 36a is provided on the right side. It is fixed to the frame 14b and is retained from the right frame 14b. Further, the urging member 44 that engages with the end surface of the base end portion 35 urges the handle shaft 36 through the base end portion 35, and moves the free clearance of the handle shaft 36 to smoothly move the handle shaft 36. Rotation can be maintained.

  A portion close to the base end 35 is interlocked with a clutch return rotating body (ratchet gear) 46 that returns to the clutch ON state when the handle 26 is rotated with the pinion gear 28 separated from the spool shaft 20. A gear (supporting part) 48 is supported in a state in which it is fitted to the non-circular part 36 b of the cross section of the handle shaft 36. The clutch return rotating body 46 is supported by a flange portion 37 formed integrally with the handle shaft 36.

  Further, a drive gear 50 is rotatably mounted on the handle shaft 36. The drive gear 50 is supported on the right frame 14b side by the flange portion 37 together with the interlocking gear 48 and the clutch return rotating body 46 via a friction lining material (friction plate) 52 formed in a donut shape on the pressing surface 50b as a bottom surface thereof. The frictional coupling force with the handle shaft 36 is adjustable via the drag mechanism 54.

  As shown in FIG. 2, a lining material positioning washer (diameter) is provided between the interlocking gear 48 that supports the handle shaft 36 and the pressing surface (bottom surface) 50 b of the drive gear 50 and on the outer periphery of the handle shaft 36. (Direction regulating annular member) 52a is fitted. The washer 52a may be either rotatable or non-rotatable with respect to the handle shaft 36, but is preferably rotatable. The above-described friction lining material 52 is rotatably fitted to the washer 52a on the outer periphery of the washer 52a. The thickness of the friction lining material 52 is larger (thicker) than the thickness of the washer 52a. By adopting such a structure, the reference surface when the gear of the drive gear 50, the washer 52a, and the friction lining material 52 are incorporated can be the same bottom surface portion (pressing surface 50b) of the drive gear 50. it can. For this reason, rotation performance improves. At this time, since the washer 52a is disposed inside the doughnut-shaped friction lining material 52, the friction lining material 52 can be easily positioned.

  The friction lining material 52 is always disposed outside the washer 52a. For this reason, the friction lining material 52 is formed so as to contact the drive gear 50 and the interlocking gear 48 at a position where the circumference is as long as possible. Therefore, the contact area between a brake plate 64 and a friction lining material 52, which will be described later, can be made larger than the center side of the friction lining material 52. In other words, the average pressure contact diameter of the friction lining material 52 can be increased, a sufficient braking force can be obtained with a simple structure, and the friction lining material 52 can be incorporated into the handle shaft 36 sequentially. Can be attached and good workability can be maintained. Further, since the friction lining material 52 is formed in a donut shape, the friction lining material 52 can be reduced in weight as compared with the case where there is a meat portion on the outer periphery of the handle shaft 36 immediately.

  The interlocking gear 48 disposed on the spool 18 side on the handle shaft 36 meshes with a gear 58 a that drives a screw shaft (worm shaft) 58 of a level wind mechanism 56 disposed on the front side of the spool 18. The screw shaft 58 is accommodated in a cylindrical body 60 extending between the left and right frames 14a and 14b, and a traverse formed on the outer peripheral surface when the gear 58a attached to the end is rotated by the interlocking gear 48. An engagement member 60 a that engages with the groove slides left and right along the cylindrical body 60. Thus, the fishing line is evenly wound on the spool 18 through the guide hole formed in the engaging member 60a.

  The drive gear 50 forms a part of a fishing line winding drive mechanism, and is formed in a cylindrical shape (bottomed cylindrical shape) having an opening on the handle 26 side, and has a flange portion 50a extending to the handle 26 side. Then, the tooth portion formed on the outer peripheral portion of the flange portion 50 a of the drive gear 50 meshes with the pinion gear 28. The drag mechanism 54 provided between the drive gear 50 and the handle shaft 36 substantially presses the drive gear 50 via a doughnut-shaped friction lining material (friction plate) 62 accommodated in the internal space of the drive gear 50. A disc-shaped brake plate 64 is provided. The brake plate 64 functions as a support member that supports the drive gear 50 together with the interlocking gear 48.

  The inner peripheral surface of the friction lining material 62 is separated from the outer peripheral surface of the handle shaft 36 and is formed so as to contact the drive gear 50 and the brake plate 64 at a position where the circumference is as long as possible. . That is, the friction lining material 62 contacts the drive gear 50 and the brake plate 64 at a position where the contact area is larger. Further, since the friction lining material 62 is formed in a donut shape, the weight of the friction lining material 62 can be reduced as compared with the case where there is a meat portion on the outer periphery of the handle shaft 36. Since the friction lining material 62 is disposed inside the flange portion 50a of the drive gear 50 and covered with the brake plate 64 from above, the positioning is extremely easy.

  When the star drag (drag operating member) 66 (see FIG. 1) screwed to the outer end side of the handle shaft 36 is rotated, the flange portion 37 on the base end side of the non-circular section 36b of the handle shaft 36 is moved in the axial direction. The brake plate 64 is pressed in the axial direction between the disc gear 70 and the sleeve 68 disposed on the inner peripheral side of the one-way clutch 40 with the drive gear 50 whose movement is restricted. For this reason, the frictional coupling force of the drive gear 50 with respect to the handle shaft 36, that is, a desired drag force can be applied to the spool 18 that is driven and rotated.

  That is, by rotating the handle 26, the driving force is transmitted from the handle shaft 36 to the drive gear 50, the pinion gear 28, and the spool shaft 20 via the drag mechanism 54, and the spool 18 is rotated. The star drag 66 functions as a braking force adjusting body that adjusts the frictional coupling force between the drive gear 50 and the handle shaft 36.

  If the force that rotates the spool 18 in the fishing line feeding direction does not exceed the frictional coupling force of the drag mechanism 54 when the fish is caught, the fishing line releasing direction acting on the spool 18, that is, the force in the fishing line feeding direction, It is transmitted to the drive gear 50 via the shaft 20 and the pinion gear 28, and acts on the handle shaft 36 via the drag mechanism 54 from the drive gear 50 and is prevented from rotating by the one-way clutch 40.

  When the force that rotates the spool 18 in the fishing line feeding direction exceeds the frictional coupling force of the drag mechanism 54, that is, the drag force, the drive gear 50 rotates with respect to the brake plate 64 and the handle shaft 36, and the spool 18 moves in the fishing line feeding direction. Rotate. This prevents breakage of the fishing line. When the spool 18 rotates in the direction of feeding the fishing line in this way, the drive gear 50 that rotates together with the spool 18 via the pinion gear 28 notifies the sound generation mechanism 72.

  As shown in FIGS. 2 to 4, the sound generation mechanism 72 is mounted inside the brake plate 64 that functions as a support member of the drive gear 50, and the front end portion protrudes radially outward from the outer periphery of the brake plate 64. A sound emitting pin 74 urged by a spring 74a radially outward and a sounding body 78 in which an uneven portion 76 that sounds when the tip of the sound generating pin 74 is disengaged is disposed on the inner peripheral surface. With. In the present embodiment, the sounding body 78 is formed of a ring-shaped plate material and is integrally fitted to the inner peripheral portion of the drive gear 50. If necessary, they can be integrated using a fixing member (not shown) such as a screw or a pin.

  The concavo-convex portion 76 is formed by alternately arranging concave portions and convex portions extending in the axial direction along the circumferential direction. By arranging such an uneven portion 76 on the inner peripheral surface side of the drive gear 50 having a cylindrical structure that accommodates the friction lining material 62 and the brake plate 64, the friction lining materials 52 and 62 wear with the progress of use. Even when the drive gear 50 and the brake plate 64 move, the engagement / disengagement state between the sound output pin 74 urged by the spring 74a and the concavo-convex portion 76 does not change, and the same engagement / disengagement state is maintained. Can do. Further, neither the sound output pin 74 of the sound generation mechanism 72 nor the sound generator 78 interferes with other members such as the drive gear 50 or the brake plate 64. Therefore, a sufficient friction engagement surface can be maintained between the drive gear 50 and the brake plate 64, and the sound generation mechanism 72 does not impair the drag performance. Therefore, the sound generation mechanism 72 can stably maintain good click performance and drag performance over a long period of time regardless of the position of the brake plate 64 as a support member.

  In the present embodiment, the recess 65 that accommodates the sound output pin 74 and the spring 74a extends perpendicularly and radially with respect to the handle shaft 36, but is inclined with respect to the handle shaft 36 and radially. It is also possible to extend in the inclined direction, and the number is not limited to two shown in FIG. 4, but may be one or three or more at equal intervals.

  Further, by providing an O-ring (engagement member) 80 as a seal member between the outer peripheral portion of the brake plate 64 and the inner peripheral portion of the sounding body 78 disposed on the inner periphery of the flange portion 50a of the drive gear 50. In addition, it is possible to achieve waterproofing and dustproofing of the sounding part where the sounding pin 74 and the uneven part 76 are engaged. Such an O-ring 80 not only protects the sound output part when dust-proofing the inside of the recess of the drive gear 50, but also when, for example, chips are generated due to friction in the sound output part. It is possible to prevent such chips from adversely affecting the meshing portion with the drive gear 50 and the pinion gear 28.

  As shown in FIG. 4, the brake plate 64 of the drag mechanism 54 includes a base portion 82 that is fixed to the handle shaft 36 and a large-diameter reinforcing portion (first reinforcing member) that extends radially outward from the base portion 82. Part) 84, an annular wall reinforcing part (second reinforcing part) 86 formed on the radially outer side of the large-diameter reinforcing part 84 (radially outer end with respect to the base part 82), and a friction lining material pressing surface 88. I have.

  The inner peripheral surface of the base portion 82 is a non-circular portion 82a formed in a non-circular shape on the side close to the sleeve 68 described above, and a circular portion 82b formed in a circular shape on the side close to the drive gear 50. For this reason, when the base portion 82 of the brake plate 64 moves along the axial direction of the handle shaft 36, the circular portion 82b is fitted and supported by the handle shaft 36, and the non-circular portion 82a is supported by being rotated. Is done. That is, when the handle 26 is operated while the brake plate 64 is pressed and the handle shaft 36 rotates about the axis, the circular portion of the handle shaft 36 is the circular portion 82b, and the non-circular portion is non-circular. It arrange | positions at the circular part 82a. Therefore, the concentricity of the brake plate 64 with respect to the handle shaft 36 is improved, and when the brake plate 64 is pressed, a stable braking force is reliably transmitted from the handle shaft 36 to the base portion 82 of the brake plate 64 without loss. be able to. Accordingly, the braking performance can be stabilized and the rotation performance can be prevented from being lowered.

  The large-diameter reinforcing portion 84 is thicker toward the side closer to the base portion 82, and is formed to be thinner as the distance from the base portion 82 increases. Of the large-diameter reinforcing portion 84, a portion adjacent to the annular wall reinforcing portion 86 is formed to be substantially flat. That is, the large-diameter reinforcing portion 84 includes an inclined surface (reinforcing meat portion) 84 a that is close to the base portion 82 and a flat surface (reinforcing meat portion) 84 b that is close to the annular wall reinforcing portion 86. It is preferable that the boundary portion between the inclined surface 84a and the flat surface 84b is smoothly continuous without a step.

  The flat surface 84b is a portion that is formed thinner as the large-diameter reinforcing portion 84 moves away from the base portion 82. However, since the concave portion 65 in which the sound output pin 74 and the spring 74a are disposed is formed. Since the concave portion 65 is formed and the shape of the concave portion 65 needs to be maintained, the thickness is increased accordingly. For example, it is necessary to form an appropriate thickness on the outer peripheral side of the flat surface 84 b that is larger than the diameter of the sound output pin 74 and the spring 74 a and larger than the diameter of the recess 65. As shown in FIG. 4, a pair of recesses 65 are formed at opposing positions on the brake plate 64, for example, and the other part is solid, so the flat part 84 b is formed thick and high in strength. . That is, not only the inclined surface 84a but also the flat surface 84b is reinforced. Therefore, when the braking plate 64 is pressed in the axial direction via the sleeve 68 and the disc spring 70 by the rotation operation of the star drag 66, the force can be reliably transmitted from the base 82 to the large-diameter reinforcing portion 84.

  The recess 65, the sound output pin 74, and the spring 74a may be provided at one place instead of a pair.

  The annular wall reinforcing portion 86 extends from the flat portion 84 b of the large diameter reinforcing portion 84 in a flange shape in the direction opposite to the drive gear 50. For this reason, the annular wall reinforcing portion 86 is formed thicker than the flat portion 84b. Therefore, the annular wall reinforcing portion 86 is prevented from being deformed. Therefore, when the braking plate 64 is pressed in the axial direction of the handle shaft 36 through the disc spring 70 and the sleeve 68 by the rotation operation of the star drag 66, the force is reliably transmitted from the base 82 to the large diameter reinforcing portion 84. Thus, it can be transmitted to the annular wall reinforcing portion 86.

  In addition, on the outer peripheral surface of the annular wall reinforcing portion 86, a sounding pin (engaging member) 74 that engages with the sounding body 78 of the sounding mechanism 72 described above and the O ring (engaging member) 80 described above are provided. It is arranged. Therefore, the brake plate 64 is in a desired state with respect to the sounding body 78 disposed inside the flange portion 50a of the drive gear 50 by the elastic force of the spring 74a itself of the sound output pin 74 and the O-ring 80 itself. Maintain the engaged state.

  Therefore, the reinforcement of the brake plate 64 suppresses the deformation of the brake plate 64 itself, prevents the bias from being transmitted from the pressing surface 88 of the brake plate 64 to the friction lining material 62, and efficiently transmits the drive force. A braking action can be exerted on the gear 50. For this reason, by reinforcing the large-diameter reinforcing portion (first reinforcing portion) 84 and the annular wall reinforcing portion (second reinforcing portion) 86 of the brake plate 64, they are made to interact with each other, and to the drive gear 50. A desired braking action can be exerted with a simpler structure than in the prior art.

  At this time, the flange portion 37 formed integrally with the handle shaft 36 restricts the movement of the handle shaft 36 in the axial direction of the interlocking gear 48 that supports the clutch return rotating body 46 and the drive gear 50. Yes. For this reason, when the drive gear 50 moves along the axial direction of the handle shaft 36 on the side opposite to the brake plate 64 in the drive gear 50, the friction lining between the interlocking gear 48 and the pressing surface 50b of the drive gear 50 is obtained. A force acts so as to sandwich the material 52. The friction lining material 52 disposed between the interlocking gear 48 and the drive gear 50 is disposed away from the outer periphery of the handle shaft 36. Between the outer periphery of the handle shaft 36 and the inner peripheral surface of the friction lining material 52, a washer (radial direction regulating annular member) 52a having a thickness smaller than that of the friction lining material 52 is disposed. That is, the washer 52a is provided on the outer periphery of the handle shaft 36, and the friction lining material 52 is provided on the outer side thereof. Can be pressed.

  Accordingly, it is possible to increase the average diameter of the pressure contact between the friction lining material 52 and the drive gear 50 and to obtain sufficient braking performance. Further, since only the washer 52a and the friction lining material 52 provided outside the washer 52a are mounted on the handle shaft 36, the mounting to the handle shaft 36 is easy and good workability is maintained. Can do. Moreover, since the washer 52a is formed thinner than the friction lining material 52, the weight can be reduced by using a light material for the washer 52a.

  In this embodiment, the example in which the sound generation mechanism 72 and the O-ring 80 are provided on the outer periphery of the annular wall reinforcing portion 86 has been described. However, the O-ring 80 may be removed. Alternatively, as described in a third embodiment (see FIG. 6) described later, the sound generation mechanism 72 may be removed. That is, either or both of the sound generation mechanism 72 and the O-ring 80 can be appropriately provided according to the design specifications, and a wide range of correspondence is possible.

  For example, even if the sound generation mechanism 72 is not provided, the inside of the drag mechanism 54 can be waterproofed and dustproofed by the O-ring 80. Alternatively, even if the O-ring 80 is not provided, when the spool 18 rotates in the fishing line feeding direction so as to prevent the fishing line from being broken, the drive gear 50 that rotates together with the spool 18 via the pinion gear 28 causes the sounding mechanism 72 to pass through. Can be notified.

  Next, a second embodiment will be described with reference to FIG. This embodiment is a modification of the first embodiment, and the same members or members having the same functions as those described in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 5, the position where the friction lining material 62 is disposed on the side of the brake plate 64 where the friction lining material 62 is not pressed is, for example, annular or at an appropriate interval. Is formed. For this reason, the weight reduction of the brake plate 64 can be achieved. Therefore, it is possible to contribute to weight reduction of the fishing reel 10.

  At this time, since both the inclined surface 84a of the braking plate 64 and the flat surface 84b that contacts the friction lining material 62 are formed thick, the first embodiment is not affected by the thinned portion 64a. The effects described in (1) can be obtained in the same manner. In addition to this, as described above, the brake plate 64 can be reduced in weight.

  Next, a third embodiment will be described with reference to FIG. This embodiment is a modification of the first embodiment and the second embodiment, and the same members or members having the same functions as those described in the first embodiment and the second embodiment are denoted by the same reference numerals. A detailed description will be omitted.

  As shown in FIG. 6, an annular portion (reinforcing meat portion) 84 c is formed as a first reinforcing portion on the side of the braking plate 64 that is close to the base portion 82. On the handle 26 side of the brake plate 64, a step is formed between the base portion 82 and the annular portion 84c.

  In this embodiment, the sound generation mechanism 72 is removed. For this reason, the braking plate 64 does not require the thickness of the concave portion 65, that is, the flat surface portion 64b formed in a state where the thickness of the sound emitting pin 74 and the spring 74a is reduced. Is formed. And the level | step difference is formed between the cyclic | annular part 84c and the plane part 64b. For this reason, the plane part 64b is formed thinner than the annular part 84c.

  An annular wall reinforcing portion (second reinforcing portion) 86 is formed at the distal end portion of the brake plate 64 with respect to the handle shaft 36 in the same manner as in the first and second embodiments. The O-ring 80 disposed on the outer peripheral surface of the annular wall reinforcing portion 86 is in direct contact with the inner peripheral surface of the flange portion 50 a of the drive gear 50.

  Therefore, when the brake plate 64 is moved along the axial direction of the handle shaft 36, the movement is surely performed from the base portion 82 to the annular portion 84c, and is also transmitted to the flat portion 64b. And since the annular wall reinforcement part 86 integrally formed in the plane part 64b is formed thickly, similarly, since the annular part 84c integrally formed in the plane part 64b is formed thickly, The flat surface portion 64b between the annular wall reinforcing portion 86 and the annular portion 84c is prevented from being deformed as much as possible. For this reason, the friction lining material 62 can be reliably pressed by the surface on the drive gear 50 side of the flat portion 64b of the braking plate 64.

  Therefore, the pressing force applied from the disc spring 70 to the braking plate 64 via the sleeve 68 is transmitted without loss when transmitted from the base 82 of the braking plate 64 to the flat surface portion 64b via the annular portion 84c. It can also be transmitted to the annular wall reinforcing portion 86 outside the flat surface portion 64b.

  Next, a fourth embodiment will be described with reference to FIG. This embodiment is a modification of the first to third embodiments, and the same members or members having the same functions as the members described in the first to third embodiments are denoted by the same reference numerals. A detailed description will be omitted.

  As shown in FIG. 7A and FIG. 7B, the opposite side of the braking plate 64 to the side where the friction lining material 62 is disposed is inclined from the base portion 82 as a first reinforcing portion. A rib (reinforcing meat portion) 84d is formed. The rib 84d transmits the movement force when the base portion 82 is pressed to the annular wall reinforcing portion 86 via the rib 84d and the flat surface portion 64b.

  As shown in FIG. 7A, the engagement members such as the sound generation mechanism 72 and the O-ring 80 may not be provided.

  Therefore, when the brake plate 64 is moved along the axial direction of the handle shaft 36, the movement is surely performed from the base portion 82 to the rib 84d and is also transmitted to the flat portion 64b. Since the annular wall reinforcing portion 86 formed integrally with the flat portion 64b is formed thick, and similarly, the rib 84d formed integrally with the flat portion 64b is formed thick, The flat portion 64b between the wall reinforcing portion 86 and the rib 84d is prevented from being deformed as much as possible. For this reason, the friction lining material 62 can be reliably pressed by the surface on the drive gear 50 side of the flat portion 64b of the braking plate 64.

  For this reason, the pressing force applied to the brake plate 64 from the disc spring 70 via the sleeve 68 is transmitted without loss when transmitted from the base 82 of the brake plate 64 to the flat surface portion 64b via the rib 84d. It can also be transmitted to the annular wall reinforcing portion 86 outside the portion 64b.

  Next, a fifth embodiment will be described with reference to FIG. This embodiment is a modification of the first to fourth embodiments, and the same members or members having the same functions as the members described in the first to fourth embodiments are denoted by the same reference numerals. A detailed description will be omitted.

FIG. 8 shows a state in which the interlocking gear 48 shown in FIG.
For this reason, the lining material positioning washer 52a and the friction lining material 52 shown in FIG. 8 are disposed between the drive gear 50 and a clutch return rotating body (ratchet gear) 46 as a support portion of the drive gear 50. ing.

  The clutch return rotating body 46 that supports the drive gear 50 is restricted from moving in the axial direction of the handle shaft 36 by a flange portion 37 formed integrally with the handle shaft 36. For this reason, when the drive gear 50 moves along the axial direction of the handle shaft 36 on the side opposite to the brake plate 64 in the drive gear 50, the friction lining material between the clutch return rotating body 46 and the drive gear 50 is provided. A force acts so as to sandwich 52. The friction lining material 52 disposed between the clutch return rotating body 46 and the drive gear 50 is disposed away from the outer periphery of the handle shaft 36. Between the outer periphery of the handle shaft 36 and the inner peripheral surface of the friction lining material 52, a washer (radial direction regulating annular member) 52a having a thickness smaller than that of the friction lining material 52 is disposed. That is, the washer 52a is provided on the outer periphery of the handle shaft 36, and the friction lining material 52 is provided on the outer side thereof. Can be pressed.

  Accordingly, it is possible to increase the average diameter of the pressure contact between the friction lining material 52 and the pressing surface 50b of the drive gear 50, and a sufficient braking performance can be obtained. Further, since only the washer 52a and the friction lining material 52 provided outside the washer 52a are mounted on the handle shaft 36, the mounting to the handle shaft 36 is easy and good workability is maintained. Can do. Moreover, since the washer 52a is formed thinner than the friction lining material 52, the weight can be reduced by using a light material for the washer 52a.

  In the various embodiments described above, the sound output pin 74 is provided on the brake plate 64 or the interlocking gear 48 as a support member that rotates together with the handle shaft 36, and the uneven portion 76 is provided on the drive gear 50 that rotates together with the spool 18. However, when the spool 18 rotates against the drag force, it can be provided in any part as long as it can sound stably over a long period of time without impairing the click performance and the drag performance. .

  Further, the present invention is not limited to the dual-bearing type reel, and can be applied to a spinning reel as long as the drive gear is connected to the handle shaft via a drag mechanism. It is not limited, and various combinations can be changed.

Sectional drawing which shows the fishing reel by preferable embodiment of this invention. Sectional drawing which expanded a part of fishing reel which concerns on 1st Embodiment. The sound generation mechanism of the fishing reel which concerns on 1st Embodiment is expanded and shown, (A) is explanatory drawing which shows the arrangement | positioning state with respect to a drive gear, (B) is a cross section in alignment with the 3B-3B line in (A). Figure. Sectional drawing which shows the braking plate of the fishing reel which concerns on 1st Embodiment. Sectional drawing which expanded a part of fishing reel which concerns on 2nd Embodiment. Sectional drawing which expanded a part of fishing reel which concerns on 3rd Embodiment. (A) is sectional drawing which expanded a part of fishing reel which concerns on 4th Embodiment, (B) is the schematic which follows the 7B-7B line | wire in (A). Sectional drawing which expanded a part of fishing reel which concerns on 4th Embodiment.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 ... Fishing reel, 12 ... Reel main body, 22 ... Fishing-line winding drive mechanism, 36 ... Handle shaft, 50 ... Drive gear, 50a ... Flange part, 54 ... Drag mechanism, 62 ... Friction lining material (friction plate), 64 ... Brake plate, 72 ... Sound generating mechanism, 74 ... Sound output pin (engagement member), 74a ... Spring, 76 ... Uneven portion, 78 ... Sound generator, 80 ... O-ring (engagement member), 82 ... Base, 82a ... non-circular part, 82b ... circular part, 84 ... large-diameter reinforcing part (first reinforcing part), 84a ... slope part (reinforcing meat part), 84b ... flat part (reinforcing meat part), 86 ... annular wall Reinforcing part (second reinforcing part).

Claims (4)

A braking plate fitted to the handle shaft so as to be able to move along the axial direction of the handle shaft;
A drive that is pressed via a friction plate disposed between the brake plate and the brake plate when the brake plate moves in the axial direction of the handle shaft by operation of a brake force adjuster disposed on the handle shaft. With
The braking plate is
A base that moves in the direction of the drive gear along the axial direction of the handle shaft by operation of the braking force adjuster;
At least a part of the side adjacent to the base, on the opposite side to the side where the drive gear is disposed, extends radially outward from the base in the axial direction of the handle shaft. A first reinforcing part having a reinforcing meat part on
A flange-shaped second reinforcing portion formed in an annular shape at the radially outer end with respect to the base portion of the brake plate and extending in a direction opposite to the side on which the drive gear is disposed. A fishing reel characterized by that. The drive gear includes a flange portion on which the second reinforcing portion is disposed,
The fishing reel according to claim 1, wherein an engagement member that is engaged with an inner peripheral surface of the flange portion of the drive gear is disposed in the second reinforcing portion.   The fishing reel according to claim 2, wherein at least one of a seal member and a sounding body is disposed on the outer periphery of the second reinforcing portion.   An inner peripheral surface of the base portion of the brake plate has a circular portion that is supported by being fitted to the handle shaft along the axial direction of the handle shaft, and a non-circular portion that is fitted to the handle shaft to be detented. The fishing reel according to claim 1, wherein the fishing reels are arranged side by side.

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