JP2006180777A5 - - Google Patents

Description

One-way clutch of double-bearing reel

  The present invention relates to a one-way clutch, and more particularly to a one-way clutch that prohibits reverse rotation of a handle shaft that is rotatably mounted on a reel body of a dual-bearing reel and that is mounted with a main gear.

  In general, a drag device for a dual-bearing reel is equipped with a one-way clutch for prohibiting rotation of an interlocking member that can be interlocked with a spool during a drag operation. For example, in the case of a star drag type drag device provided around the handle shaft, a one-way clutch is mounted on the handle shaft. In the case of a lever drag type drag device provided around the spool shaft, a one-way clutch is provided on the spool shaft, handle shaft or drag disk.

  A claw-type one-way clutch is generally used as a one-way clutch used in a drag device for this type of lever drag reel. The claw-type one-way clutch has a ratchet wheel that is formed with a circumferentially spaced tooth on the outer peripheral portion and is non-rotatably mounted on the interlocking member, and a separation that separates from a contact posture that contacts the tooth portion of the ratchet wheel. It has a ratchet claw that is mounted on the reel body so as to be swingable between postures, and a biasing member that biases the ratchet claw toward the contact posture. The ratchet pawl has a tip disposed downstream of the swing center in the yarn winding direction.

  In the claw-type one-way clutch configured as described above, when the ratchet wheel rotates in the yarn winding direction in conjunction with the rotation of the spool in the yarn winding direction, the ratchet claw is pressed toward the separated posture by the tooth portion. However, when the tooth portion passes through the ratchet pawl, it is urged toward the contact posture by the urging member and contacts the ratchet wheel. For this reason, when the spool rotates in the yarn winding direction, the ratchet pawl vibrates and comes into contact with the ratchet wheel, and an intermittent click sound is generated. When such a click sound is generated, for example, when fishing such as jigging that frequently repeats the winding operation is performed, the noise becomes unpleasant continuously. In addition, since the ratchet pawl comes into contact with the ratchet wheel, the rotational resistance during winding increases and the winding efficiency also decreases.

Therefore, in order to eliminate the click sound at the time of winding the yarn, there is known one provided with a biasing member that biases the ratchet pawl by friction instead of biasing by a spring (see, for example, Patent Document 1). The urging member is composed of a thin plate member bent in a C shape, and is fixed to the ratchet pawl. A pair of tips of the urging members elastically contact both side surfaces of the ratchet wheel so as to sandwich the ratchet wheel. In the one-way clutch provided with such a biasing member by friction, when the ratchet wheel rotates in the yarn winding direction, the ratchet pawl is biased by the friction toward the separating posture, and when rotated in the yarn unwinding direction, the ratchet pawl moves toward the contact posture by friction. Be energized. For this reason, no click sound is generated when winding the yarn.
JP 2001-207322 A

  In the conventional one-way clutch, when the ratchet pawl is moved relative to the handle shaft in the axial direction when the one-way clutch is assembled or disassembled for maintenance or parts replacement, the ratchet wheel and the handle shaft are moved together. May attempt to move relative to the ratchet pawl. If the ratchet wheel moves relative to the ratchet pawl together with the handle shaft, the urging member holding the ratchet wheel may be deformed.

  When the urging member is deformed, a frictional force is not generated between the urging member and the ratchet wheel, and the ratchet pawl cannot be normally urged. As a result, the one-way clutch does not operate normally.

  The subject of this invention is suppressing the deformation | transformation of the urging | biasing member by the urging | biasing member moving relatively with a ratchet wheel in the one-way clutch provided with the urging | biasing member which urges | biases a ratchet nail | claw by friction with a ratchet wheel. .

  A one-way clutch of a dual-bearing reel according to a first aspect of the present invention is a one-way clutch that is rotatably mounted on a reel body and prohibits reverse rotation of a handle shaft on which a main gear is mounted, and includes a ratchet wheel, a ratchet pawl, and an urging member And a claw support portion. The ratchet wheel is a wheel in which a plurality of tooth portions are formed on the outer peripheral portion of the shaft end portion of the handle shaft so as to be interlocked with the main gear with a gap therebetween and spaced in the circumferential direction. The ratchet pawl is arranged on the outer peripheral side of the ratchet wheel and is swingable between a contact posture in which the tip contacts the tooth portion and a separation posture in which the tooth portion is separated from the tooth portion. Is prohibited. The urging member is provided on the ratchet claw, elastically sandwiches both side surfaces of the ratchet wheel, and when the ratchet wheel rotates in the yarn winding direction, the ratchet claw is urged toward the separation posture and rotated in the yarn unwinding direction. It is a member that urges to the contact posture side. The claw support portion has a fixed bracket that is detachably mounted on the reel body with the ratchet wheel interposed therebetween, and a swing support pin that is mounted on the fixed bracket and supports the ratchet claw so that it can be inserted and removed from the ratchet wheel side and swingably. is doing.

  In this one-way clutch, when assembling the ratchet pawl and the ratchet wheel, the ratchet pawl is attached to the ratchet wheel in a posture that can prevent reverse rotation of the thread unwinding direction with both side surfaces of the ratchet wheel held between biasing members. Install the wheel on the handle shaft alongside the main gear. When the ratchet wheel is attached to the handle shaft, the fixed bracket with the swing support pin attached is brought close to the ratchet wheel side and attached to the reel unit. At this time, the swing support pin can support the ratchet pawl. Since the swing support pin can be inserted and removed from the ratchet wheel side, the biasing member and the ratchet wheel do not move in the axial direction even when the fixed bracket is brought close to the reel body with the ratchet pawl attached to the ratchet wheel. For this reason, deformation of the urging member can be suppressed. Here, the swinging support pin is attached to a fixed bracket arranged with the ratchet wheel interposed therebetween and supports the ratchet claw so that it can be inserted and removed from the ratchet wheel side. Therefore, the biasing member attached to the ratchet claw at the time of assembly is Even if the swing support pin is moved in the direction approaching the ratchet wheel while the ratchet wheel is being held, and the ratchet pawl attempts to move relative to the ratchet wheel, the ratchet pawl with the urging member attached to the ratchet wheel Both are stationary. For this reason, the urging member is not deformed by the ratchet wheel, and deformation of the urging member can be suppressed.

  A one-way clutch of a dual-bearing reel according to a second aspect of the present invention is the clutch according to the first aspect, further comprising a fixing bolt that is screwed into the shaft end of the handle shaft and fixes the ratchet wheel, and the fixing bracket exposes the fixing bolt. Is formed. In this case, since the fixing bracket is formed so that the fixing bolt is exposed, the fixing bolt can be tightened after the fixing bracket is attached. Therefore, the ratchet wheel can be fixed to the handle shaft with the fixing bolt after the fixing bracket is fixed to the reel body. Therefore, movement of the ratchet wheel in the handle shaft direction together with the urging member is allowed during assembly, and deformation of the urging member can be further suppressed.

  A one-way clutch for a dual-bearing reel according to a third aspect of the present invention is the clutch according to the first or second aspect, wherein the reel body covers a reel frame having ring-shaped first and second side plates and outer sides of both side plates. 1 and a second cover member, the handle shaft is rotatably supported by the second cover member, and the fixing bracket is fixed to the inner surface of the second cover member. In this case, since the handle shaft is cantilevered by the second cover member and the fixed bracket is disposed on the unsupported shaft end side, the ratchet pawl is fixed even if the ratchet wheel is disposed on the shaft end side. Can be easily supported.

  A one-way clutch of a dual-bearing reel according to a fourth aspect of the present invention is the clutch according to any one of the first to third aspects, wherein the ratchet wheel is connected to the main gear at a plurality of locations in the circumferential direction so as not to be relatively rotatable by connecting means. In this case, since the rotation of the handle shaft can be transmitted to the main gear via the ratchet wheel, it is not necessary to connect the main gear to the handle shaft in a non-rotatable manner, and the processing of the main gear and the handle shaft is facilitated. .

  A one-way clutch of a dual-bearing reel according to a fifth aspect of the present invention is the clutch according to any one of the first to fourth aspects, wherein the one-way clutch is attached to a fixed bracket and contacts the ratchet pawl when the ratchet pawl swings away from the side. A restriction pin for restricting the nail to the position is further provided. In this case, the urging member cannot be detached from the ratchet wheel by regulating the separation position of the ratchet claw with the regulating pin.

  According to the present invention, the swing support pin is attached to the fixed bracket arranged with the ratchet wheel interposed therebetween, and supports the ratchet claw so that it can be inserted and removed from the ratchet wheel side. Even when the swing support pin is moved in the direction approaching the ratchet wheel while the biasing member is holding the ratchet wheel, the ratchet pawl with the biasing member attached is used even if the ratchet pawl attempts to move relative to the ratchet wheel. Will remain stationary with respect to the ratchet wheel. For this reason, the urging member is not deformed by the ratchet wheel, and deformation of the urging member can be suppressed.

  As shown in FIGS. 1 and 2, the dual-bearing reel according to the embodiment of the present invention is a medium lever drag type, and is disposed so as to be swingable on the reel body 1 and the side of the reel body 1. A drag operation member 2, a handle 3 rotatably supported by the reel body 1 below the drag operation member 2, and a spool 4 disposed inside the reel body 1.

<Structure of reel body>
The reel body 1 includes a frame 10 and first and second side covers 13a and 13b that cover the frame 10 on both sides. The frame 10 includes a pair of left and right first and second side plates 11a and 11b and a plurality of connecting portions 12 that connect the first and second side plates 11a and 11b. The first and second side plates 11a and 11b are members having a substantially circular shape when viewed from the side, and the diameter of the second side plate 11b is formed to be larger than the diameter of the first side plate 11a. For example, the diameter of the second side plate 11b ranges from 110% to 140% of the diameter of the first side plate 11a. In this embodiment, the diameter is 110% to 120% of the diameter of the first side plate 11a. The plurality of connecting portions 12 are integrally formed with the first and second side plates 11a and 11b, and the lower connecting portion 12 is used for mounting the reel to the fishing rod RD as shown in FIGS. Long metal heel mounting legs 7 are fixed to the front and rear.

A rod clamp 8 that sandwiches the fishing rod RD is disposed opposite to the rod mounting leg portion 7. The rod clamp 8 is made of metal having an arc portion 8a and a pair of attachment portions 8b, 8b extending from both sides of the arc portion 8a. The rod clamp 8 is fixed to the lower connecting portion 12 by the first and second fasteners 9a and 9b with the fishing rod RD interposed therebetween . The first and second fastening portions 9a and 9b are connected to the first and second fastening bolts 9c and 9e, which are attached to the mounting portions 8b and 8b, and the first and second fastening bolts 9c and 9e are screwed together. 12 and first and second fastening nuts 9d and 9f. In this embodiment, since the second side plate 11b has a larger diameter than the first side plate 11a, the connecting portion of the connecting portion 12 with the second side plate 11b is more than the connecting portion with the first side plate 11a on the fishing rod RD side. The distance from the connecting portion 12 to the mounting portion 8b of the rod clamp 9 is short on the second side plate 11b side. For this reason, the length of the second fastening portion 9b on the second side plate 11b side is shorter than that of the first fastening portion 9a on the first side plate 11a side. Specifically, the lengths of the fastening bolts 9c and 9e are the same, but the lengths of the fastening nuts 9d and 9f are shorter than the fastening nut 9d on the first side plate 11a side.

  As shown in FIGS. 1 and 2, the first side cover 13a is a substantially circular member that is attached to the side of the first side plate 11a in a side view. The second side cover 13b has a cylindrical portion 14 attached to the side of the second side plate 11b, and a bulging portion 15 protruding outward in the axial direction of the cylindrical portion 14 (right side in FIG. 2). The first side cover 13a and the cylindrical portion 14 are substantially circular members in side view having substantially the same diameter as the first and second side plates 11a and 11b, respectively. The diameter of the second side cover 13b is the diameter of the first side cover 13a. It is formed to have a larger diameter. For example, the diameter of the cylindrical portion 14 is in the range of 110% to 140% of the diameter of the first side cover 13a. In the present embodiment, the diameter is 110% to 120% of the diameter of the first side cover 13a.

  As shown in FIGS. 1 and 2, the cylindrical portion 14 is a cylindrical member that is mounted on the side of the second side plate 11 b and is substantially circular in a side view. The bulging portion 15 is integrally formed with the cylindrical portion 14 and is formed to protrude outward in the axial direction (right side in FIG. 2) so as to have a space communicating with the cylindrical portion 14 therein. The bulging portion 15 is a substantially raindrop-shaped member having a small arc portion and a large arc portion in a side view, and is formed such that the lower large arc portion projects downward from the cylindrical portion 14. A drag operation member 2 and a handle 3 are attached to the bulging portion 15 so as to be exposed to the outside.

  As shown in FIGS. 1 and 2, a protruding cylinder 16 for mounting the handle 3 is formed to protrude outwardly below the drag operation member 2 of the bulging portion 15. As shown in FIG. 2, a cylindrical handle shaft 31 is disposed inside the protruding cylinder 16 in parallel with the spool shaft 5 that is the rotation shaft of the spool 4. As shown in FIG. 2, the handle shaft 31 is cantilevered and supported by the projecting cylinder 16 by two bearings 32 and 33 disposed at both ends of the projecting cylinder 16, and one shaft end is supported by the bearing 32. It is arranged to protrude inward. A main gear 60 is rotatably mounted on the protrusion of the handle shaft 31 on the bearing 32 side. A pair of rotation transmission holes 60 a is formed in the disc portion of the main gear 60. The main gear 60 is in contact with the bearing 32 via a washer 59. The handle 3 is mounted on the other shaft end of the handle shaft 31 so as not to rotate.

  A roller-type first one-way clutch 62 is disposed between the bearings 32 and 33. The first one-way clutch 62 allows only forward rotation of the handle shaft 31 in the yarn winding direction and prohibits reverse rotation in the yarn unwinding direction. A claw-type second one-way clutch 63 according to an embodiment of the present invention is disposed at one shaft end of the handle shaft 31. The second one-way clutch 63 also prohibits reverse rotation of the handle shaft 31. These first and second one-way clutches 62 and 63 are mainly used for operating a drag mechanism 6 (described later) that brakes the rotation of the spool 4 in the yarn unwinding direction. The shaft end portion 31b on the bearing 32 side of the handle shaft 31 is formed with a rotation locking portion 31a having a non-circular cross section such as a rectangle.

<Configuration of the second one-way clutch>
As shown in FIGS. 3 to 6, the second one-way clutch 63 includes a ratchet wheel 65 and a ratchet wheel that are arranged side by side with a clearance so as to interlock with the main gear 60 on the rotation locking portion 31 a of the handle shaft 31. The ratchet pawl 66 positioned on the outer peripheral side of the motor, a biasing member 67 that biases the ratchet pawl, a pawl support 68 that swingably supports the ratchet pawl 66, and the ratchet wheel 65 are fixed to the handle shaft 31. And a fixing bolt 69.

  The ratchet wheel 65 is a member in which a plurality of serrated teeth 65a are formed on the outer peripheral portion at intervals in the circumferential direction. The ratchet wheel 65 is a substantially disk-shaped member having a smaller diameter than the main gear 60, and a rectangular mounting hole 65 b that engages with the rotation locking portion 31 a of the handle shaft 31 is formed at the center. In the disk portion, a pair of rotation transmission holes 65 c penetrating both side surfaces are formed at positions that can face the rotation transmission holes 60 a of the main gear 60. A connecting pin 70 for connecting both the rotation transmission holes 60a and 65c is disposed between the main gear 60 and the ratchet wheel 65, and is inserted into the both rotation transmission holes 60a and 65c. With such a configuration, the rotation of the ratchet wheel 65, that is, the rotation of the handle shaft 31 is transmitted to the main gear 60 via the connecting pin 70. The fixing bolt 69 is screwed into the shaft end portion 31 b of the handle shaft 31, and the ratchet wheel 65 is fixed to the handle shaft 31 by the fixing bolt 69. The fixing bolt 69 presses the main gear 60 via the ratchet wheel 65, and the main gear 60 is in contact with the inner ring of the bearing 32 via the washer 59. For this reason, the main gear 60 is also positioned and fixed by the fixing bolt 69.

As shown in FIG. 5, the ratchet claw 66 is swingably attached to the claw support portion 68 in a contact posture indicated by a solid line that contacts the tooth portion 65a and a separation posture indicated by a two-dot chain line that is separated from the tooth portion 65a. ing. When the ratchet pawl 66 is arranged in the contact posture, the handle shaft 31 is prohibited from rotating in the thread drawing direction. Therefore, when the spool 4 rotates in the yarn feeding direction, a drag mechanism 6 described later operates. The ratchet claw 66 has a support hole 66a into which a swing support pin 76 described later is fitted. The tip 66b of the ratchet pawl 66 is disposed downstream of the support hole 66a in the yarn winding direction R of the ratchet wheel 65. The ratchet claw 66 is restricted by the main gear 60 from moving and deflecting in the axial direction toward the main gear 60.

  The urging member 67 is a metal plate member having elasticity bent in a C-shape, and is fitted into an intermediate portion of the ratchet claw 66 and is fixed by a caulking pin 73, for example. As shown in FIG. 6, the pair of distal ends 67 a of the urging member 67 elastically contact with both side surfaces of the ratchet wheel 65 to sandwich the ratchet wheel 65. A regulation pin 71 is provided on the claw support portion 68 on the side away from the ratchet claw 66 so as to regulate the swing range so that the urging member 67 does not come off the ratchet wheel 65. When the ratchet wheel 65 rotates in the yarn winding direction R, the urging member 67 urges the ratchet pawl 66 toward the separation posture by friction with the ratchet wheel 65. The ratchet pawl 66 urged toward the separation posture is in contact with the regulation pin 71 and is maintained in the separation posture shown by a two-dot chain line in FIG. Thereby, the ratchet pawl 66 does not come into contact with the tooth portion 65a of the ratchet wheel 65 when winding the yarn, and noise can be suppressed. In addition, an increase in rotational resistance can be suppressed, and a decrease in winding efficiency of the spool 4 can be suppressed. On the other hand, when the ratchet wheel 65 rotates in the yarn drawing direction, the ratchet pawl 66 is urged toward the contact posture by friction with the ratchet wheel 65. Thereby, the rotation of the handle shaft 31 in the yarn feeding direction can be prohibited.

  The claw support portion 68 includes, for example, a fixing bracket 75 fixed to the inner surface of the bulging portion 15 of the second side cover 13b with a ratchet wheel 65 by a screw member 77, and a ratchet claw 66 attached to the fixing bracket 75. It has a swing support pin 76 that supports the ratchet wheel 65 so that it can be inserted and removed in a swingable manner. The fixing bracket 75 is formed in a crescent shape so that the head 69a of the fixing bolt 69 is exposed. Thus, the fixing bolt 69 can be tightened after the fixing bracket 75 is fixed to the bulging portion 15. The fixing bracket 75 is formed with a first fixing hole 75a for caulking and fixing the swing support pin 76 and a second fixing hole 75b for caulking and fixing the regulation pin 71. Further, a deflection preventing projection 75 c for preventing the ratchet claw 66 from flexing toward the fixing bracket 75 is formed to project toward the ratchet claw 66. The swinging support pin 76 is a shaft member with a hook having a large diameter at the center, and a ratchet claw 66 is swingably mounted at the tip of the swinging support pin 76 and can be inserted into and removed from the ratchet wheel 65 side.

  In the second one-way clutch 63 configured as described above, the swing support pin 76 is attached to the fixed bracket 75 arranged with the ratchet wheel 65 interposed therebetween, and supports the ratchet pawl 66 so that it can be inserted and removed from the ratchet wheel 65 side. Therefore, the swinging support pin 76 is moved in a direction approaching the ratchet wheel 65 in a state in which the biasing member 67 attached to the ratchet claw 66 holds the ratchet wheel 65 during assembly, and the ratchet claw 66 moves to the ratchet wheel 65. Even if it is going to move relative to 65, the ratchet pawl 66 to which the urging member 67 is attached is in a state where both the ratchet wheel 65 are stationary. For this reason, the urging member 67 is not deformed by the ratchet wheel 65, and the deformation of the urging member 67 can be suppressed.

  As shown in FIG. 2, the handle 3 is fixed to the other end of the handle shaft 31. The handle 3 includes a handle arm 40 fixed to the distal end of the handle shaft 31 and a handle grip 41 supported rotatably at the distal end of the handle arm 40. The handle arm 40 is fixed to the tip end of the handle shaft 31 by a screw member 42 so that the handle shaft 31 cannot rotate relative to the handle arm 40. The handle grip 41 is formed to have a substantially T-shaped rounded outer shape in order to make it easier to grip with force.

<Spool configuration>
As shown in FIG. 2, the spool 4 includes a cylindrical bobbin trunk 4a and first and second flange portions 4b and 4c formed on both sides of the bobbin trunk 4a and having a larger diameter than the bobbin trunk 4a. Have. The spool 4 is rotatably supported on the spool shaft 5 by bearings 20a and 20b. A drag mechanism 6 is provided on the handle 3 side of the spool 4 to brake the rotation of the spool 4 in the yarn unwinding direction. A centrifugal braking mechanism 18 that brakes the spool 4 is provided on the first side cover 13 a side of the spool 4. A spool sound generating mechanism 19 is provided between the spool 4 and the first side cover 13a. The spool sound generation mechanism 19 can be switched between a sound generation state and a silent state in which sound is not generated according to the rotation of the spool 4.

  As shown in FIG. 2, the second flange portion 4c is formed to have a larger diameter than the first flange portion 4b. As shown in an enlarged view in FIG. 5, the second flange portion 4 c is a cylindrical small-diameter portion 4 d formed such that the bobbin trunk portion 4 a side has a smaller diameter than a first braking member 25 described later that constitutes the drag mechanism 6. And a cylindrical large-diameter portion 4e formed so that the outermost peripheral side has a larger diameter than the first braking member 25. The small diameter portion 4d is integrally formed with the large diameter portion 4e so as to have a smaller diameter than the large diameter portion 4e, and is provided so as to generate a step between the large diameter portion 4e and the end of the bobbin trunk 4a. . Here, the fishing line is wound around the outer periphery of the bobbin trunk 4a, but the fishing line can be wound up to the outermost diameter of the small diameter part 4d by the step of the small diameter part 4d. The second side plate 11b is disposed so as to cover the space between the large diameter portion 4e and the small diameter portion 4d, and the tip end portion extends radially inward so as to be close to the small diameter portion 4d. For this reason, it is possible to prevent the fishing line from being wound around the outer periphery of the small diameter portion 4d and to restrict the fishing line from moving outward in the axial direction.

  As shown in FIG. 2, the diameter of the small diameter portion 4d is formed to be substantially the same as the diameter of the first flange portion 4b. The diameter of the large diameter portion 4e is in the range of 110% to 140% of the diameter of the small diameter portion 4d. In the present embodiment, the diameter is 120% to 130% of the diameter of the small diameter portion 4d. Moreover, the diameter of the large diameter part 4e is formed so that it may become substantially the same diameter as the diameter of the 1st side plate 11a and the 1st side cover 13a. Further, the diameter of the first braking member 25 is in the range of 90% or more of the diameter of the small diameter portion 4d, and in this embodiment, is 130% to 140% of the diameter of the small diameter portion 4d. The outer diameter of the bobbin trunk 4a is 30% to 40% of the diameter of the small diameter portion 4d.

<Configuration of drag mechanism>
As shown in FIG. 2, the drag mechanism 6 is for changing and adjusting the braking force applied to the rotation of the spool 4 mounted on the spool shaft 5 in the yarn feeding direction. As shown in FIG. 7, the drag mechanism 6 includes a drag operation member 2, a first cam member 21 provided on the inner periphery of the drag operation member 2, and a first cam member 21 disposed in contact with the first cam member 21. Two cam members 22, a drag adjusting member 27 that is attached to the second cam member 22 so as to be relatively rotatable, and pulls the spool shaft 5 outward (right side in FIG. 7), and the drag adjusting member 27 is attached to the second cam member 22. A retaining member 23 for retaining in the axial direction, a first urging member 24a (see FIG. 2) composed of, for example, four disc springs for urging the spool 4 inward in the axial direction, and a second attachment composed of a coil spring. The biasing member 24b, the third biasing member 24c formed of a coil spring that biases the drag adjusting member 27 outward in the axial direction (right side in FIG. 2), and the spool 4 is fixed outward in the axial direction (right side in FIG. 7). The first braking member 25 and the first braking member 25 are in contact with each other. And a second braking member 26 arranged capability. In FIG. 2, the upper half of the spool shaft 5 indicates the axial position when the maximum drag operation is performed, and the lower half indicates the drag force reduction position.

  As shown in FIG. 7, the drag operation member 2 has a boss portion 2a formed at the center thereof rotatably supported by the second side cover 13b, and a lever portion 2b extending radially outward therefrom from the second side cover 13b. The cover 13b is configured to be locked at a plurality of locations in the circumferential direction. Moreover, as shown in FIG. 8, the attachment member 2c for mounting | wearing with the 1st cam member 21 is being fixed to the inner peripheral part of the boss | hub part 2a so that relative rotation is impossible.

  As shown in FIG. 8, the first cam member 21 is a rod-like cam pin fixed at a plurality of locations on the attachment member 2 c of the drag operation member 2. The second cam member 22 is a cylindrical member that is disposed in contact with the first cam member 21, can move in the axial direction in accordance with the swing of the first cam member 21, and cannot rotate with respect to the spool shaft 5. . The second cam member 22 is an inclined cam having an inclined surface 22 a on which the contact surface with the first cam member 21 is inclined. The inner peripheral portion of the second cam member 22 is attached to a guide member 17 that is caulked and fixed to a portion through which the spool shaft 5 penetrates the second side cover 13b so that it cannot rotate but can move in the axial direction. As shown in FIG. 9, the guide member 17 is formed with six flat portions 17a that are, for example, regular hexagonal sides and an arc portion 17b that connects the flat portions 17a on the outer peripheral portion. As shown in FIG. 10, the second cam member 22 is formed adjacent to the hexagonal hole 22b and the hexagonal hole 22b that engages the flat portion 17a and the circular arc portion 17b of the guide member 17 on the inner peripheral portion. And a circular hole 22c that fits into a circle 17c that connects the two. Since the hexagonal hole 2c is formed by, for example, press molding, it cannot be formed with a very hot thickness (length in the axial direction) in consideration of accuracy. When the hexagonal hole 22d having such a small thickness is attached to the guide member 17 so as not to rotate and move in the axial direction, the second cam member 22 may be rattled because the axial length is short. Therefore, the circular arc portion 17b is formed in the guide member 17 and the circular hole 22c is formed adjacent to the hexagonal hole 22b. The fitting of the circular hole 22c and the circular arc portion 17b of the guide member 17 causes the second cam member 22 to be bent. It suppresses rattling.

  The second cam member 22 moves to the left in the axial direction on the upper side of FIG. 8 due to the counterclockwise swing of the drag operation member 2 in FIG. 2, and the drag force becomes weaker. Further, when the drag operation member 2 is swung clockwise in FIG. 2, the drag operation member 2 moves to the right in the axial direction on the lower side in FIG.

  The second cam member 22 is retained in the axial direction with respect to the drag adjusting member 27 by a retaining member 23. The retaining member 23 is, for example, a C-shaped retaining ring made of synthetic resin having elasticity. The retaining member 23 is disposed so as to be in contact with the outer peripheral surface of the second cam member 22 and the inner peripheral surface of the drag adjusting member 27, and the shaft of both members is caused by the force of the C-shaped retaining ring spreading outward. The movement of the direction is regulated.

  As shown in FIG. 8, the drag adjusting member 27 is a bottomed cylindrical cap member, and is an adjusting member for initially setting the drag force. The drag adjusting member 27 is attached to the second cam member 22 so as to be relatively rotatable. The end of the spool shaft 5 protruding outward from the second side cover 13b is screwed together, and the spool shaft 5 is rotated by rotation in the screwing direction. Is a member that pulls outward in the axial direction (right side in FIG. 8). A female screw portion 27 a is formed on the inner peripheral portion of the drag adjusting member 27, and a male screw portion 5 a formed at the end of the spool shaft 5 is screwed. A third urging member 24c made of a coil spring is mounted between the inner peripheral portion of the drag adjusting member 27 and the axial end surface of the inner peripheral portion of the second cam member 22, and the drag adjusting member 27 is always attached. Energizing outward. Thereby, rattling of the second cam member 22 can be prevented. On the outer peripheral portion of the tip end portion of the drag adjusting member 27, a stepped portion 27b recessed from the other portion is formed in a groove shape along the circumferential direction. When the drag adjusting member 27 is attached or detached, the step 27b is picked and pulled outward in the axial direction (right side in FIG. 8), so that the drag adjusting member 27 can be attached and detached easily.

  The drag adjusting member 27 moves slightly to the left in the axial direction on the upper side of FIG. 8 by turning counterclockwise, and the drag force is slightly weakened. Further, when the drag adjusting member 27 is rotated clockwise, the drag force is slightly increased by slightly moving to the right in the axial direction on the lower side of FIG.

  As shown in FIG. 2, the spool shaft 5 is a shaft member that is supported on the reel body 1 so as to be movable in the axial direction and not to be relatively rotatable. On the outer periphery of the spool shaft 5, bearings 20a and 20b for rotatably mounting the spool 4 and a bearing 20c for rotatably supporting a second braking member 26 described later are mounted. On the outer periphery of the spool shaft 5 between the bearings 20a and 20b, as shown in FIGS. 2 and 7, a second urging member 24b comprising a coil spring that urges the spool 4 inward in the axial direction (left side in FIG. 2). Is installed. Further, on the outer periphery of the spool shaft 5 in the axially inward direction (left side in FIG. 2) of the bearing 20a, as shown in FIG. 2, there is a second disc spring that urges the spool 4 inward in the axial direction (left side in FIG. 2). One urging member 24a is attached. The first biasing member 24a has a stronger biasing force than the second biasing member 24b. For this reason, when the spool shaft 5 moves in the axial direction, the first urging member 24a acts first, and then the second urging member 24b acts.

  A bearing 20d is mounted on the inner peripheral portion of the second side cover 13b, and supports the outer peripheral portion of the pinion gear 61 mounted on the outer periphery of the spool shaft 5. As shown in FIG. 2, the pinion gear 61 meshes with the main gear 60 fixed to the handle shaft 31. The tip of the pinion gear 61 is fixed to the inner peripheral side of the second braking member 26 described later. As a result, the rotation from the handle 3 is transmitted to the first braking member 25 via the main gear 60, the pinion gear 61, and the second braking member 26, and is transmitted from the first braking member 25 to the spool 4, and the spool 4 rotates. To do.

  As shown in FIGS. 2 and 7, the first braking member 25 is an annular member that is fixed to the outside of the spool 4 in the axial direction (right side in FIG. 2) inside the second side plate 11 b. The first braking member 25 is formed to have a larger diameter than the small-diameter portion 4d of the second flange portion 4c, which is a thread winding diameter of the spool 4. The first braking member 25 is fixed to the end surface of the spool 4 with a plurality of screw members 51. The first braking member 25 is made of a heat-resistant synthetic resin such as a fiber reinforced resin obtained by impregnating a carbon fiber woven fabric with a heat-resistant resin such as a phenol resin.

  As shown in an enlarged view in FIG. 11, the second braking member 26 includes a donut-shaped sliding disk 26 a on which the first braking member 25 is disposed so as to be in press contact with the spool shaft 5, and is not axially movable and rotatable. And a mounted main body member 26b. The sliding disk 26a is made of a heat and corrosion resistant metal such as stainless steel. The sliding disk 26 a has a slightly smaller diameter than the first braking member 25 and is fixed to the main body member 26 b by a plurality of screw members 52. The main body member 26b is a disk-shaped member having a boss portion 26c, and is rotatably supported on the spool shaft 5 by a bearing 20c. The main body member 26b meshes with the pinion gear 61 on the inner peripheral surface at the boss portion 26c. Further, the movement of the main body member 26b outward in the axial direction (right side in FIG. 2) is restricted by the reel main body 1 via the pinion gear 61 and the bearing 20d.

  The outer sides of the first and second braking members 25 and 26 are covered with a cover disk 28. The outer peripheral portion of the cover disk 28 is fixed to the tip portion on the axially outer side (right side in FIG. 2) of the large diameter portion 4e of the second flange portion 4c. The cover disk 28 is fixed to the tip end portion of the large diameter portion 4e of the second flange portion 4c by a screw member 53. Further, a seal member 29 having a lip 29a is disposed on the outer periphery of the cover disc 28 and the boss portion 26c, and the inside of the cover disc 28 is sealed. When the lip 29a is in the drag free state shown in FIG. 7, the lip 29a does not come into contact with the cover disk 28, and as shown in FIG. 11, the first braking member 25 and the second braking member 26 are moved by the operation of the drag operating member 2. When contacted, the cover disk 28 is contacted to seal the inside. Thereby, the rotation resistance of the spool 4 at the time of drag free can be reduced.

  As shown in FIG. 12, the centrifugal braking mechanism 18 is provided to prevent yarn dander on the spool 4 caused by excessive rotation of the spool 4 called so-called backlash. The centrifugal braking mechanism 18 includes a rotary frame 78 fixed to the outer surface of the flange portion 4 b of the spool 4, for example, four guide shafts 79 radiating from the rotary frame 78, and radial directions on the guide shaft 79. For example, there are four sliders 80 that are movably mounted, and a cylindrical brake liner 81 that is fixed to the inner surface of the first side cover 13a. The rotary mount 78 is arranged concentrically with the spool 4 while being centered on the outer surface of the flange portion 4 b by indicia bonding, and is fixed by a screw member 82. The rotary mount 78 includes a first cylinder part 78a disposed around the first urging member 24a, a disk part 78b integrally formed on the outer peripheral surface of the first cylinder part 78a, and an outer peripheral part of the disk part 78b. And a second cylindrical portion 78c formed integrally with the first cylindrical portion. This disc part 78 b is fixed to the outer surface of the flange part 4 b of the spool 4. A guide shaft 79 is inserted into the second cylindrical portion 78c, and four insertion holes 78d are formed.

  The guide shaft 79 is a shaft member having a large-diameter flange portion 79a at the base end, and is attached to the insertion hole 78d from the inner peripheral surface of the second cylindrical portion 78c. The guide shaft 79 is prevented from coming off by a head portion 82 a of a screw member 82 for fixing the rotary mount 78. Specifically, the head 82a of the screw member 82 is stopped so as not to come out of the insertion hole 78d by contacting the flange 79a.

The slider 80 contacts the inner peripheral surface of the annular brake liner 81 by centrifugal force when the spool 4 rotates, and brakes the spool 4.

  When the second one-way clutch 63 is assembled in the double-bearing reel configured as described above, the two connecting pins 70 are attached to the rotation transmission hole 60 a of the main gear 60 attached to the handle shaft 31. Then, the ratchet wheel 65 is attached to the rotation locking portion 31 a at the shaft end of the handle shaft 31. At this time, it attaches to the rotation latching | locking part 31a so that the connection pin 70 may be inserted in the rotation transmission hole 65c. Thereby, the ratchet wheel 65 and the main gear 60 are connected so as not to rotate. When the ratchet wheel 65 is attached, the urging member 67 fixed to the ratchet claw 66 is mounted so as to sandwich the outer peripheral surface of the ratchet wheel 65. In this state, the fixing bracket 75 to which the swing support pin 76 is fixed is fixed to the inner surface of the bulging portion 15 by the screw member 77. At this time, the swing support pin 76 is inserted into the support hole 66 a of the ratchet claw 66. The swinging support pin 76 can be attached to the ratchet wheel 66 so that the ratchet claw 66 can be inserted into and removed from the ratchet wheel. Therefore, even when the ratchet wheel 65 moves in the axial direction when the fixing bracket 75 is fixed, the ratchet wheel 76 follows the ratchet wheel. The claw 66 moves and the urging member 67 is not deformed. When the fixing bracket 75 is fixed, finally, the fixing bolt 69 is screwed into the shaft end of the handle shaft 31 to fix the ratchet wheel 65. As a result, the main gear 60 is pressed by the ratchet wheel 65 and positioned and fixed in the axial direction.

  Further, when disassembling the second one-way clutch 63, the work is performed in the reverse order of the above assembling work.

  First, with the second side cover 13b removed from the frame 10, the screw member 77 is loosened and the fixing bracket 75 is removed. At this time, even if the swing support pin 76 moves in the axial direction, the urging member 67 remains stationary with respect to the ratchet wheel 65 for the reason described above, and the urging member 67 is not deformed. When the fixing bracket 75 is removed, the swing support pin 76 is also detached from the ratchet pawl 66. Then, the fixing bolt 69 is removed to release the ratchet wheel 65 from being fixed. Next, when the ratchet pawl 66 is removed from the ratchet wheel 65 and further the ratchet wheel 65 is removed from the handle shaft 31, the disassembly of the second one-way clutch 63 is completed. During this disassembling work, an excessive force does not act on the urging member 67 and the urging member 67 is not deformed.

  In this embodiment, since the head 69a of the fixing bolt 69 is exposed with the fixing bracket 75 attached, the fixing bolt 69 can be loosened without removing the fixing bracket 75. For this reason, when the second one-way clutch 63 is disassembled, the fixing bracket 75 and the ratchet wheel 65 may not be removed separately, but the ratchet wheel 65 may be removed together with the fixing bracket 75 after the screw member 77 is removed. . In this case, since the relative movement between the swing support pin 76 and the ratchet pawl 76 does not occur, the biasing member is not further deformed.

  Here, the swinging support pin 76 is attached to the fixed bracket 75 arranged with the ratchet wheel 65 interposed therebetween, and supports the ratchet claw 66 so that it can be freely inserted and removed from the ratchet wheel 65 side. Even if the ratchet claw 66 tries to move relative to the ratchet wheel 65 by moving the swinging support pin 76 in a direction approaching the ratchet wheel 65 with the biasing member 67 sandwiching the ratchet wheel 65, The ratchet pawl 66 to which the urging member 67 is attached is in a stationary state with respect to the ratchet wheel 65. For this reason, the urging member 67 is not deformed by the ratchet wheel 65, and deformation of the urging member can be suppressed.

[Other Embodiments]
(A) In the above embodiment, the present invention is applied to a medium-sized lever drag type dual-bearing reel. However, the present invention is applied to all one-way clutches in which a ratchet wheel is attached to the shaft end of the handle shaft of the dual-bearing reel. it can. For example, the present invention can be applied to a claw-type one-way clutch employed in a star drag mechanism.

  (B) In the above embodiment, the fixing bracket 75 is formed so as to expose the head 69a of the fixing bolt 69, but the head 69a may not be exposed. However, in this case, as described above, the fixing bracket 75 and the ratchet wheel 65 cannot be assembled and disassembled simultaneously during assembly and disassembly.

  (C) In the above-described embodiment, the ratchet wheel 65 and the main gear 60 are connected by the connecting pin. However, the main gear 60 may be attached to the handle shaft so as not to rotate without being connected. Further, when connected, the ratchet wheel 65 may be rotatably mounted on the handle shaft 31 so that the rotation is transmitted from the main gear 60.

The perspective view of the double bearing reel by one Embodiment of this invention. Sectional drawing of the said double bearing reel. The expanded sectional view of the 2nd one way clutch. The disassembled perspective view of a 2nd one-way clutch. The front view of a 2nd one-way clutch. VI-VI sectional drawing of FIG. The expanded sectional view of a drag mechanism. The expanded sectional view around a drag adjustment member. The front view of a guide member. A half-sectional view of the second cam member. The expanded sectional view around the 1st braking member. The expanded sectional view which shows the structure of a centrifugal braking mechanism.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Reel body 13b 2nd side cover 15 Expansion part 31 Handle shaft 60 Main gear 63 2nd one-way clutch 65 Ratchet wheel 66 Ratchet claw 67 Energizing member 68 Claw support part 69 Fixing bolt 70 Connection pin 71 Restriction pin 75 Fixation bracket 76 Swing support pin