JP2010017100A - Drag mechanism for dual-bearing reel - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a drag mechanism capable of preventing the rotation of a friction disk even by using a holding space having an easily sealable form. <P>SOLUTION: The drag mechanism 6 includes a friction disk 21, a cover member 26, a brake disk 22, and a drag adjusting mechanism. The friction disk is placed in a holding space of a first flange 9b of a spool 4 and has an engaging recess 21a formed on an external circumferential surface. The cover member 26 has a cylindrical portion 26a fitting to the internal circumferential surface of the holding space, an engaging protrusion 26e on an end surface of the cylindrical portion to engage with the engaging recess, and a protrusion mating closely with an end face of the first flange. The cover member 26 is fixed to the first flange and covers the holding space from outside. The brake disk is arranged in the holding space facing the friction disk and constructed not to rotate in a direction to reel out the line. The cam mechanism is designed to relatively move the friction disk and the spool together along an axial direction of the spool with respect to the brake disk such that the friction disk is pressed against the brake disk. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a drag mechanism, and more particularly to a drag mechanism for a dual-bearing reel that brakes the spool by moving relative to a spool mounted on a reel body of a bearing reel in the axial direction of the spool.

  A double-bearing reel, particularly a lever-drag type double-bearing reel, is provided with a drag mechanism that moves and brakes the spool in the spool axial direction. In such a drag mechanism, the drag force is adjusted by a drag adjusting lever that swings around the spool shaft. The drag mechanism includes a friction disk that rotates integrally with the spool, a moving mechanism that moves the friction disk in the spool axial direction together with the spool in response to the swing of the drag adjustment lever, and a brake disk that can contact and separate from the friction disk. ing. In this type of drag mechanism, a friction disk and a brake disk are disposed in a storage space provided in a flange portion, and the storage space is covered with a cover member from the outside (for example, non-patent document). 1). When the friction disk and the brake disk are arranged in the storage space covered with the cover member in this way, the two disks are hardly wetted, and fluctuations in the drag force due to the wettability can be prevented.

A conventional drag mechanism includes a friction disk having four engaging projections projecting outward on an outer peripheral surface disposed in a cylindrical storage space formed in a flange portion of a spool, and a storage space fixed to the flange portion. And a moving mechanism for moving the friction disk in the spool axial direction together with the spool, and a braking disk disposed in the storage space and capable of contacting the friction disk. The cover member has a cylindrical portion having a male screw portion that is screwed into the inner peripheral surface of the storage space. On the inner peripheral surface of the storage space, there are formed a female screw portion that is screwed into the male screw portion, and four engagement concave portions that are engaged with the engagement convex portion. As a result, the friction disk is prevented from rotating with respect to the spool. Further, the friction disk is prevented from coming off at the tip of the cylindrical portion.
Issued by Shimano Co., Ltd. TLD2 Speed Parts List Issue Date April 9, 2008 (part numbers 171, 238, 246 in particular)

  In the conventional drag mechanism, an engagement recess is provided in the storage space, and an engagement protrusion is provided in the friction disk to prevent the friction disk from rotating with respect to the spool. When the engagement recess is provided in the storage space and the friction disk is prevented from rotating, the clearance between the cover member and the cover member is increased by the amount of the engagement recess. It becomes difficult to seal the space.

  SUMMARY OF THE INVENTION An object of the present invention is to enable a friction disk to be prevented from rotating in a drag mechanism of a dual-bearing reel even if the storage space is shaped to be easily sealed.

  A drag mechanism for a dual-bearing reel according to a first aspect of the present invention is a mechanism that brakes the spool by moving relative to the spool mounted on the reel body of the dual-bearing reel in the axial direction of the spool, and includes a friction disk, a cover member, A disc and a moving mechanism. The friction disk is disposed in a cylindrical storage space formed in the flange portion of the spool, and has at least one engagement recess recessed on the outer peripheral surface on the inner peripheral side. The cover member includes a cylindrical portion having an outer peripheral surface fitted to the inner peripheral surface of the storage space, at least one engagement protrusion provided on the distal end surface of the cylindrical portion and engaged with the engagement recess, and an outer peripheral surface of the cylindrical portion. A member that protrudes in a circular shape and has a protruding portion that can be brought into close contact with the end surface of the flange portion, is fixed to the flange portion, and covers the storage space from the outside in the axial direction. The brake disk is disposed in the storage space so as to face the friction disk, and cannot be rotated in the yarn feeding direction. The moving mechanism is a mechanism that moves the friction disk relative to the brake disk together with the spool in the axial direction of the spool to press the friction disk and the brake disk in pressure contact.

  When assembling the drag mechanism, for example, a brake disc and a friction disc are placed on the cover member side after the spool is mounted on the spool shaft. At this time, the engaging recess of the friction disk and the engaging protrusion of the cover member are engaged. Then, the protruding portion of the cover member is brought into close contact with the end surface of the flange portion through the spool shaft. At this time, when the projecting portion is not in close contact, the engaging projection is not accurately engaged with the engaging recess, and therefore the engaging projection and the engaging recess are engaged again. Finally, the phase of the screw hole and the screw passage hole are matched, and the cover member is fixed to the flange portion by the screw member. As a result, the friction disk is prevented from rotating with respect to the spool. If the engagement protrusion is not engaged with the engagement recess, a gap is formed between the protrusion and the end surface of the flange portion. Therefore, whether the engagement protrusion and the engagement recess are engaged or not is determined. Easy to grasp visually. Here, the friction disk is prevented from rotating by the cover member, not the storage space. For this reason, the cylindrical part of a cover member can be fitted in storage space, and the clearance gap between a cover member and storage space can be made small. In addition, the protruding portion is in close contact with the end surface of the flange portion. Therefore, the friction disk can be prevented from rotating even if the storage space has a shape that is easy to seal.

  A drag mechanism for a dual-bearing reel according to a second aspect of the present invention is the mechanism according to the first aspect, wherein the engagement protrusion is formed to protrude toward the flange portion in a circular arc shape at a distal end of the cylindrical portion with a circumferential interval. Yes. In this case, since the plurality of engaging projections are formed protruding from the tip of the cylindrical portion, the torque of the spool can be transmitted to the friction disk by the plurality of engaging projections, and the transmission torque can be dispersed.

  The dual-bearing reel drag mechanism according to a third aspect of the present invention is the mechanism according to the second aspect, wherein the cylindrical portion has a spool axial length that allows the tip to approach the side surface of the friction disk when the cover member is fixed to the flange portion. Have. In this case, even if the brake disc is separated from the friction disc, the friction disc is less likely to rattle.

  A drag mechanism for a dual-bearing reel according to a fourth aspect of the present invention is the mechanism according to the third aspect, wherein the engagement protrusion has a length in the spool axial direction such that a gap is formed between the outer surface of the flange portion. ing. In this case, even if the protrusion is brought into contact with the flange portion and the cover member is fixed to the flange portion, the engagement protrusion does not contact the outer surface of the flange portion, and the gap between the cover member and the storage space is further reduced. can do.

  According to the present invention, the friction disk is prevented from rotating by the cover member rather than the storage space. For this reason, the cylindrical part of a cover member can be fitted in storage space, and the clearance gap between a cover member and storage space can be made small. In addition, the protruding portion is in close contact with the end surface of the flange portion. Therefore, the friction disk can be prevented from rotating even if the storage space has a shape that is easy to seal.

  As shown in FIGS. 1 to 3, the dual-bearing reel according to the embodiment of the present invention is a small lever drag type capable of winding a fishing line around an axis that is different from a fishing rod. The dual-bearing reel includes a reel body 1, a drag adjustment mechanism 7 including a drag adjustment lever 2 that is rotatably disposed on the side of the reel body 1, and a reel body 1 that is rotatable below the drag adjustment lever 2. A supported handle 3 and a spool 4 disposed inside the reel body 1 are provided. The double-bearing reel includes a spool shaft 5 that rotatably supports the spool 4 and a drag mechanism 6 that brakes the rotation of the spool 4 in the yarn unwinding direction.

<Structure of reel body>
The reel body 1 is a metal member such as an aluminum alloy. The reel body 1 includes a frame 10 and first and second side plates 13 a and 13 b that cover both sides of the frame 10. In this embodiment, the second side plate 13b is formed integrally with the frame 10, but may be configured to be separately fixed to the frame. The frame 10 includes a first tube portion 11a on the handle 3 side, a second tube portion 11b having a smaller diameter than the first tube portion 11a and spaced from the first tube portion 11a in the spool axis direction, and both tube portions 11a. , 11b and a plurality of connecting portions 12a to 12c for connecting the front and rear and the lower portion. For example, the outer diameter of the first cylinder portion 11a is in the range of 110% to 140% of the outer diameter of the second cylinder portion 11b. In this embodiment, the outer diameter is 110% to 120% of the diameter of the second cylinder portion 11b. ing. The plurality of connecting portions 12a to 12c are integrally formed with the first and second cylindrical portions 11a and 11b, and the lower connecting portion 12c is mounted with a reel on the fishing rod RD as shown in FIGS. A long metal rod mounting leg portion 8a is fixed before and after the operation. A rod clamp 8b sandwiching the fishing rod RD is disposed opposite to the rod mounting leg portion 8a.

  As shown in FIGS. 1 to 3, the first side plate 13 a includes a cylindrical portion 14 attached to the side of the first cylindrical portion 11 b and a bulge protruding outward in the axial direction of the cylindrical portion 14 (right side in FIG. 2). And an exit portion 15. As shown in FIGS. 1 and 3, the second side plate 13 b is a member that is integrally formed on the side of the second cylindrical portion 11 b and has a substantially circular shape when viewed from the side. The cylindrical portion 14 and the second side plate 13b are substantially circular members in a side view substantially the same diameter as the first and second cylindrical portions 11a and 11b, respectively. The outer diameter of the first side plate 13a is the outer diameter of the second side plate 13b. It is formed to have a larger diameter. For example, the outer diameter of the cylindrical portion 14 is in the range of 110% to 140% of the outer diameter of the second side plate 13b, and is 110% to 120% of the outer diameter of the second side plate 13b in this embodiment.

  The bulging portion 15 is integrally formed with the cylindrical portion 14 and is formed so as 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 adjusting lever 2 and a handle 3 are attached to the bulging portion 15 so as to be exposed to the outside.

  As shown in FIGS. 4 and 5, a boss portion 34 for rotatably supporting the drag adjusting lever 2 and supporting the spool shaft 5 is provided on the mounting portion of the bulging portion 15 of the drag adjusting lever 2. It is formed so as to protrude outward from the portion. The boss part 34 is a part having a large-diameter projecting part 34a and a small-diameter projecting part 34b projecting from the large-diameter projecting part 34a. Inside the large-diameter projecting part 34a, a bearing 20d described later (see FIG. 5) is provided. It is stored. A guide member 17 that guides a cam member 50 described later (see FIG. 5) to be non-rotatable and axially movable is fixed to the inner peripheral side of the boss portion 34, specifically, the inner peripheral side of the small-diameter protruding portion 34b. Has been.

  The guide member 17 is fixed by caulking through the first side plate 13a on the inner peripheral side of the small-diameter protruding portion 34b through which the spool shaft 5 of the first side plate 13a passes. A guide hexagonal guide portion 17a is formed on the outer peripheral surface of the guide member 17, and a passage hole 17b through which the spool shaft 5 can pass is formed on the inner peripheral surface. A stopper 35 for restricting the maximum drag position of the drag adjusting lever 2 is fixed in front of the boss portion 34 of the bulging portion 15. The stopper 35 abuts on a later-described lever portion 47b of the drag adjusting lever 2 to restrict the clockwise rotation of the drag adjusting lever 2 in FIG.

<Configuration of rotation transmission system>
Below the drag adjustment lever 2 of the bulging portion 15, a protruding cylinder 16 for mounting the handle 3 is formed to protrude outward. As shown in FIGS. 3 and 5, 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. The handle shaft 31 is rotatably supported on the projecting cylinder 16 by two bearings 32 and 33 disposed at both ends of the projecting cylinder 16, and one (left side in FIG. 5) shaft end is axially inward of the bearing 32. It is arranged to protrude. A main gear 60 is rotatably mounted on a protruding portion of the handle shaft 31 on the bearing 32 side.

  As shown in FIGS. 1 to 3, the handle 3 is fixed to the other end (tip) 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 end of the handle shaft 31 by a screw member 42 so as to be integrally rotatable with the handle shaft 31. 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.

  As shown in FIG. 5, the main gear 60 is prevented from rotating by the rotation preventing member 63 and rotates integrally with the handle shaft 31. The anti-rotation member 63 is connected to the handle shaft 31 so as to be integrally rotatable, and is fixed to the handle shaft 31 by a fixing bolt 65 screwed into one end of the handle shaft 31. The anti-rotation member 63 is a pair of a ring portion 63a that is coupled to the handle shaft 31 so as to be integrally rotatable, and a pair of portions that are bent in an L shape from the outer peripheral portion of the ring portion 63a to both sides in the radial direction to lock the main gear 60. And a locking portion 63b. The main gear 60 is formed with a pair of locking holes 60a that are locked to the locking portions 63b. The main gear 60 meshes with the pinion gear 61.

  The pinion gear 61 is mounted on the outer peripheral side of the spool shaft 5 so as to be rotatable with respect to the spool shaft 5. The pinion gear 61 is rotatably supported on the reel body 1 by a bearing 20d mounted inside the large-diameter protruding portion 34a of the boss portion 34 of the first side plate 13a. As shown in FIG. 6, the pinion gear 61 has gear teeth 61 a that mesh with the main gear 60 and a disk support portion 61 b that is formed in a substantially rectangular shape on the outer peripheral surface. In the disk support portion 61b, a processing trace of a gear cutting tool when the gear teeth 61a are formed remains. The inner peripheral surface has a through hole 61c through which the spool shaft 5 passes. An inner peripheral portion of a brake disc 22 (described later) constituting the drag mechanism 6 is coupled to the disc support portion 61b of the pinion gear 61 so as to be integrally rotatable. As a result, the rotation from the handle 3 is transmitted to the friction disk 21 to be described later via the main gear 60, the pinion gear 61, and the brake disk 22, and is transmitted from the friction disk 21 to the spool 4, and the spool 4 rotates. A spring support plate 69 constituting a second one-way clutch 64, which will be described later, is also mounted on the disk support portion 61b so as to be integrally rotatable.

<Spool shaft and surrounding configuration>
As shown in FIG. 3, 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. The left end of the spool shaft 5 in FIG. 3 is supported by a boss portion 13c formed inwardly projecting from the center portion of the second side plate 13b so as to be axially movable and non-rotatable. On the left end side of the spool shaft 5, an anti-rotation pin 5 a for preventing the spool shaft 5 from rotating is disposed through the spool shaft 5. The detent pin 5a is engaged with a detent groove 13d formed in the boss portion 13c.

  Bearings 20a and 20b for rotatably mounting the spool 4 and a bearing 20c for rotatably supporting the brake disk 22 are mounted on the outer periphery of the spool shaft 5.

<Configuration of one-way clutch>
A roller-type first one-way clutch 62 is arranged between the bearings 32 and 33 as shown in FIG. 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 64 is arranged on the outer peripheral side of the spool shaft 5. The second one-way clutch 64 prohibits reverse rotation of the handle shaft 31 via the pinion gear 61.

  The first and second one-way clutches 62 and 64 are mainly used for operating the drag mechanism 6. As shown in FIG. 6, the second one-way clutch 64 includes a ratchet wheel 66 that is coupled to the brake disk 22 so as to be integrally rotatable, a ratchet pawl 67 that locks the ratchet wheel 66, and a spring that biases the ratchet pawl 67. A member 68 and a spring support plate 69 for mounting the spring member 68 are provided.

  The ratchet wheel 66 is a plate-like member having a substantially serrated ratchet tooth 66a meshing with the ratchet pawl 67 on the outer peripheral surface and an engagement protrusion 66b engaging with the brake disk 22 on the inner peripheral portion. The engagement protrusion 66b is coupled to an end surface of a main body member 25 (described later) of the brake disk 22 so as to be integrally rotatable.

  The ratchet claw 67 is rotatably supported by a rotation shaft 65 that is screwed into the inner side surface of the first side plate 13a. The ratchet claw 67 has a rotation support portion 67b having a support hole 67a supported by the rotation shaft 65 at the base end portion, and a claw portion 67c that bites into the ratchet teeth 66a of the ratchet wheel 66 at the distal end portion. Yes. An engagement slot 67d with which the spring member 68 is engaged is formed in the intermediate portion. The ratchet pawl 67 is brought into contact with the ratchet wheel 66 by the action of the spring member 68 and a contact position where the rotation of the ratchet wheel 66 is prohibited, and a separation position where the ratchet claw 67 is separated from the contact position. Rotate between. The separation position of the ratchet pawl 67 is restricted to a position slightly separated from the ratchet wheel 66 by a restriction portion (not shown) provided on the inner side surface of the first side plate 13a.

  The spring member 68 separates the ratchet pawl 67 from the ratchet wheel 66 when the spool 4 rotates in the yarn winding direction, thereby reducing the noise of the second one-way clutch 64, and at the time of rotating in the yarn unwinding direction. Is urged toward the ratchet wheel 66. The spring member 68 is a member made of a metal wire having a spring property, and biases the ratchet pawl 67 in different directions according to the rotation direction of the spool 4. The spring member 68 includes a C-shaped mounting portion 68a that frictionally engages with the mounting groove 69a of the spring support plate 69, an arm portion 68b that extends in a radial direction from the mounting portion 68a, and a U-shape that is bent from the arm portion 68b. And a curved portion 68c that is curved to engage with the engaging slot 67d. The spring member 68 urges the ratchet pawl 67 in a direction away from the ratchet wheel 66 when the spool 4 rotates in the yarn winding direction and the brake disk 22 rotates in the same direction. Further, when the spool 4 rotates in the yarn feeding direction and the brake disk 22 rotates in the same direction, the ratchet pawl 67 is urged in a direction approaching the ratchet wheel 66. As a result, rotation of the brake disk 22 in the yarn unwinding direction is prevented.

  The spring support plate 69 is a disk-like member, and a mounting groove 69a in which the mounting portion 68a of the spring member 68 is frictionally engaged is formed on the outer peripheral surface. A rectangular connection hole 69b is formed in the inner peripheral portion so as to be connected to the disk support portion 61b of the pinion gear 61 so as to be integrally rotatable.

<Spool configuration>
As shown in FIG. 7, the spool 4 has a spool body 9 and a fishing line locking pin 23 fixed to the spool body 9. The spool body 9 includes a cylindrical bobbin trunk 9a on which an outer circumferential surface and an inner circumferential surface of the spool shaft 5 are disposed with a gap therebetween and a fishing line can be wound around the outer circumferential surface, and a spool formed on both sides of the bobbin trunk 9a. It has the 1st flange part 9b and the 2nd flange part 9c larger diameter than the trunk | drum 9a. The spool body 9 includes a countersink portion 9f formed on the outer peripheral surface of the bobbin trunk 9a and a pin fixing portion 9h formed on the countersink portion 9f.

  The spool body 9 is rotatably supported on the spool shaft 5 by bearings 20a and 20b. A drag mechanism 6 is provided on the handle 4 side of the spool 4. Further, a spool sound generation mechanism 18 that generates sound by the rotation of the spool 4 is provided on the second side plate 13 b side of the spool 4.

  The countersink portion 9f is formed in a circularly concave shape on the outer peripheral surface of the central portion in the axial direction of the bobbin trunk portion 9a, as shown in an enlarged manner in the G portion of FIG. The bottom face 9g of the counterbore part 9f is flat, and a pin fixing part 9h having a through hole 9i is formed at the center of the bottom face 9g. The through hole 9i is formed to penetrate from the bottom surface 9g to the inner peripheral surface of the bobbin trunk 9a along the radial direction of the bobbin trunk 9a.

  The fishing line locking pin 23 is used to stop the tip of the fishing line, and is press-fitted and fixed in the through hole 9i in the central portion in the axial direction of the bobbin trunk 9a. The fishing line locking pin 23 has a first shaft part 23a fixed to the through hole 9i by press-fitting, and a second shaft that has a larger diameter than the first shaft part 23a and can be locked by, for example, tying a fishing line on the outer peripheral surface. It has the part 23b and the head 23c larger diameter than the 2nd axial part 23b.

  In this manner, the fishing line locking pin 23 is formed with the first shaft portion 23a and the second shaft portion 23b having a larger diameter than the first shaft portion 23a, and the first shaft portion 23a is press-fitted into the through hole. A flat bottom surface 9g is formed on the counterbore 9f. For this reason, when the step portion between the first shaft portion 23a and the second shaft portion 23b comes into contact with the bottom portion 9g, the press-fitting of the fishing line locking pin 23 can be finished, and the press-fitting amount of the fishing line locking pin 23 is set to a predetermined amount. Can be maintained. In addition, since the step portion contacts the flat bottom portion 9g, a gap is hardly formed between the step portion and the bottom surface 9g, and the fishing line is not easily caught between the step portion and the bottom surface 9g.

  The first flange portion 9b has a larger diameter than the second flange portion 9c, and the axial length of the outer peripheral surface 9d is longer than the axial length of the outer peripheral surface 9e of the second flange portion 9c. A storage space 36 in which the drag mechanism 6 can be stored is formed on the outer surface of the first flange portion 9b.

  The first and second flange portions 9b and 9c respectively enter the first tube portion 11a and the second tube portion 11b. The first cylinder portion 11a has a circular first opening 19a into which the first flange portion 9b can enter. Moreover, the 1st cylinder part 11a is provided in the opening end of the 1st opening 19a, and a minute clearance (for example, 0.2 mm-0.7 mm) is opposed to the outer peripheral surface of the 1st flange part 9b at an opening end. A first opposing portion 19c that is shorter than the outer peripheral surface of the first flange portion 9b and that is larger in diameter than the first opposing portion 19c on the outer side in the spool axis direction than the first opposing portion 19c. 1 relief part 19e. Furthermore, the 1st cylinder part 11a has the 1st escape part 19e formed larger diameter than the 1st opposing part 19c inside the spool axial direction of the 1st opposing part 19c. Here, the inward direction in the spool axial direction is a direction toward the axial center of the spool body 9 (specifically, the portion on which the fishing line locking pin 23 is mounted), and is in the spool axial direction. The outward direction is a direction away from the center of the spool body 9.

  The second cylinder portion 11b has a circular second opening 19b into which the small-diameter second flange portion 9c of the spool body 9 can enter. Therefore, the second opening 19b has a smaller diameter than the first opening 19a. Further, as shown in FIG. 7, the second cylinder portion 11b is provided at the opening end of the second opening 19b, and is opposed to the outer peripheral surface of the second flange portion 9c at the opening end (for example, 0. 2 mm to 0.7 mm) and shorter than the outer peripheral surface of the second flange portion 9 c, the second facing portion 19 d and the second facing portion 19 d outward from the second facing portion 19 d in the spool axial direction. And a second relief portion 19f having a large diameter. Furthermore, the second cylinder part 11b has a fourth relief part 19h formed on the inner side in the spool axis direction of the second opposing part 19d with a diameter larger than that of the second opposing part 19d.

  As described above, since the length of the facing portion between the first flange portion 9b and the first opening 19a, which is longer than the second flange portion 9c, is usually shortened, the gap remains even if liquid enters the gap. It becomes easy to flow to the wide 1st relief part 19e side. For this reason, even if the liquid enters the gap between the first opening 19a and the first flange portion 9b, the free rotation of the spool 4 is hardly hindered.

  In the portion where the lower connecting portion 12c is formed, the first and second drain holes 13e, 19f are formed in the first and second relief portions 19e, 19f forming portions of the first and second cylinder portions 11a, 11b. 13f penetrates the inner and outer peripheral surfaces and is formed along the radial direction. The first and second drain holes 13e and 13f are for discharging liquid that has entered from between the first and second flange portions 9b and 9c and the first and second openings 19a and 19b.

<Configuration of drag adjustment mechanism>
As shown in FIGS. 3 to 5, the drag adjusting mechanism 7 is for changing and adjusting the drag force applied to the rotation of the spool 4 mounted on the spool shaft 5 in the yarn unwinding direction. 6 functions as a moving mechanism for moving 6. 3 and 5, the lower side of the axis X of the spool shaft 5 indicates the axial position of the spool shaft 5 at the maximum drag, and the upper side indicates the axial position at the time of drag release.

  The drag adjustment mechanism 7 includes a cam mechanism 43 that converts the rotation of the drag adjustment lever 2 into a movement of the drag mechanism 6 in the spool axis direction, and a rotation that is provided in the cam mechanism 43 and restricts the rotation of the drag adjustment lever 2. A regulating portion 44 (see FIG. 10) and a lever sounding mechanism 45 that generates sound by the rotation of the drag adjusting lever 2 are provided.

<Configuration of drag adjustment lever>
When the drag adjusting lever 2 is rotated clockwise in FIG. 2, the drag force is increased, and when it is rotated counterclockwise, the drag force is decreased. The position rotated slightly clockwise from the position indicated by the solid line is the strike position, the position indicated by the two-dot chain line is the drag release position, and the position indicated by the broken line is the maximum drag position. Here, the strike position is a position that can be adjusted to the drag force that can firmly pierce the fish hook into the fish mouth without cutting the fishing line even when sudden pulling due to a fish hit suddenly, and generally the fishing line cutting strength The drag adjusting lever 2 having a value of about 1/3 is rotatably mounted on the outer peripheral surfaces of the large-diameter protruding portion 34a and the small-diameter protruding portion 34b of the boss portion 34 of the first side plate 13a. The drag adjusting lever 2 includes, for example, an aluminum alloy lever main body 47 and an insert member 48 made of, for example, zinc alloy press-fitted into the lever main body 47. The lever main body 47 has a cylindrical base end portion 47a disposed around the boss portion 34, and a lever portion 47b extending radially outward from the base end portion 47a. On the inner peripheral surface of the base end portion 47a, a cutout portion 47c that is cut obliquely is formed at the boundary portion with the lever portion 47b, and the lever sound generating mechanism 45 is attached thereto. An insert member 48 is fixed to the inner peripheral surface of the base end portion 47a by press-fitting.

  The insert member 48 is a stepped cylindrical member that is rotatably supported by the large-diameter protruding portion 34a and the small-diameter protruding portion 34b. The outer peripheral surface of the small-diameter-side cylindrical portion 48a has, for example, a cam mechanism 43. Two cam receiving pins 52a constituting the cam receiving portion 52 are erected along the radial direction. As shown in FIG. 4, a radial bush 46a for supporting the insert member 48 in the rotating direction is disposed between the small diameter side cylinder portion 48a of the insert member 48 and the small diameter protrusion portion 34b of the boss portion 34. A thrust ring 46b for axial support is mounted between the insert member 48 and the wall surface 34c of the boss portion 34.

<Structure of lever sounding mechanism>
The lever sound generation mechanism 45 generates a sound by rotating the drag adjustment lever 2 and positions the drag adjustment lever 2. As shown in FIGS. 4 and 5, the lever sound generating mechanism 45 includes a cylindrical sound generating member 70 mounted on the outer peripheral surface of the large-diameter protruding portion 34 a of the boss portion 34 and a striking portion that repeatedly collides with the sound generating member 70. 71.

  The sound generating member 70 is a ring-shaped member made of a synthetic resin, such as polyacetal, which is relatively hard and highly slidable. The sound generating member 70 has a cone surface 70a inclined so as to have a smaller diameter as it goes outward in the axial direction of the spool shaft 5, and an uneven portion 70b formed along the circumferential direction of the cone surface 70a. The concavo-convex portion 70b is formed to be recessed in an arc shape on the cone surface 70a. The sound generating member 70 is mounted on the large-diameter protruding portion 34a in a state in which it cannot rotate but is restricted from moving inward in the axial direction and is free to move outward in the axial direction. The sound generating member 70 is restricted from moving inward in the axial direction by the outer wall surface 15 a of the boss portion 34 forming portion of the bulging portion 15. A rotation preventing hole 15b for preventing rotation is formed on the outer wall surface 15a, and a rotation stopping projection 70c that engages with the rotation stopping hole 15b is formed on the sound generation member 70. Thereby, the movement of the sound generating member 70 in the axially inward direction is restricted, and the sound generating member 70 is prevented from rotating. However, the sound generating member 70 is not restricted from moving outward in the axial direction.

  The lever sound generation mechanism 45 further includes a mounting portion 72 having a mounting hole 72a formed in the cutout portion 47c of the drag adjusting lever 2 along an axis substantially orthogonal to the cone surface 70a. The striking part 71 is mounted in the mounting hole 72a so as to urge the sounding pin 73 toward the concavo-convex part 70b and the sounding pin 73 mounted in the mounting hole 72a so as to be able to advance and retreat toward the cone surface 70a. A spring member 74 in the form of a coil spring. The sound output pin 73 is a pin member made of, for example, a synthetic resin having a spherical tip, and has a base end smaller in diameter than the tip. A spring member 74 is disposed on the outer peripheral side of the base end portion.

  Here, a cone surface 70a inclined so as to have a smaller diameter as it goes outward in the axial direction is formed on the sound generating member 70, an uneven portion 70b is formed on the cone surface 70a, and the sound of the hitting portion 71 is formed on the uneven portion 70b. The delivery pin 73 is in elastic contact. For this reason, since the sounding member 70 can be urged inward in the axial direction by the striking portion 71, the sounding member 70 can be prevented from coming off by the striking portion 71. For this reason, the sound generation member 70 can be attached to the boss portion 34 without providing a retaining structure.

  The mounting hole 72a is formed along an axis substantially orthogonal to the cone surface 70a. For this reason, the sound generating member 73 that can be moved outward in the axial direction can be biased inward in the axial direction by the sound output pin 73 biased by the spring member 74. For this reason, since the sound generating member can be urged inward in the axial direction by the sound output pin urged by the spring member 74, the sound generating member can be prevented from coming off by the striking member. As a result, a clearer click sound can be generated and the sound producing member can be more reliably prevented by the sound output pin.

  In addition, since the mounting hole 72a is formed obliquely, the distance between the mounting hole 72a and the inner surface gradually increases even if the mounting hole 72a is formed at a position close to the inner surface of the drag adjusting lever 2. . For this reason, even if the mounting hole 72a is formed, the drag adjusting lever 2 is unlikely to have a thin portion, and a reduction in strength of the portion can be suppressed.

  Further, since the sound producing pin 73 is made of a synthetic resin which is not easily corroded, there is no possibility that the sound producing pin 73 which is difficult to take out once attached to the attaching hole 72a is fixed to the attaching hole 72a due to corrosion, and maintenance of the lever sound generating mechanism 45 is not required. become.

<Composition of cam mechanism>
The cam mechanism 43 includes a cam member 50 having a cam surface 49, a drag adjustment knob 51 for setting the adjustment range of the drag adjustment lever 2, and a drag adjustment lever 2 provided in contact with the cam surface 49 in FIG. A cam receiving portion 52 that moves the cam member 50 in the first axial direction (rightward in FIG. 5) by turning around, and a drag adjusting knob 51 that moves the cam member 50 counterclockwise in FIG. And a first urging member 53 made of a coil spring as an urging portion that moves in the second axial direction in contact with the cam receiving portion 52. Further, the drag adjusting mechanism 7 includes a second urging member 54 formed of, for example, four disc springs that urge the spool 4 in a direction away from the spool shaft 5 (rightward in FIG. 3).

<Composition of cam member>
The cam member 50 is a cylindrical member made of stainless steel, for example, and connects the outer cylinder portion 50a and the inner cylinder portion 50b, and the outer cylinder portion 50a and the inner cylinder portion 50b, as shown in FIGS. Disc part 50c. A cam surface 49 is formed at the tip of the outer cylinder portion 50a. In addition, an annular groove 50d in which the O-ring 56 is mounted is formed on the outer peripheral surface of the outer cylinder portion 50a. A hexagonal hole 50e that engages with the hexagonal guide portion 17a of the guide member 17 is formed in the inner peripheral surface of the inner cylinder portion 50b. Further, a sound producing recess 50f constituting a knob sound generating mechanism 55 described later is formed on the outer surface of the disc portion 50c.

  As shown in FIG. 8 and FIG. 10, the cam surface 49 is composed of an inclined surface whose projecting height gradually decreases in an arc shape along the end surface of the cam member 50 as a whole. Two of the same shape are formed. A rotation restricting portion 44 that restricts the rotation of the drag adjusting lever 2 is formed on both sides of the restricting position C in the middle of the cam surface 49. Here, the restriction position C is, for example, a position away from the reference position A of the cam surface 49 by about 25 degrees to 30 degrees.

  The rotation restricting portion 44 has a restricting protrusion 44a that protrudes toward the cam receiving pin 52a. The restricting protrusion 44a includes a vertex 44b located at the restricting position C, a first inclined surface 44c that extends from the vertex 44b to the first position B corresponding to the drag release position, and a first head that faces the first position B from the vertex 44b. 2 inclined surfaces 44d. The inclination angle α of the first inclined surface 44c is smaller than the inclination angle β of the second inclined surface 44d. For example, in this embodiment, the inclination angle α is 14 degrees, preferably in the range of more than 10 degrees and 18 degrees or less. The second inclined surface 44d is formed by an arc having a radius substantially the same as the radius of the cam receiving pin 52a shown by a two-dot chain line in FIG. For example, in this embodiment, the inclination angle β at the tangent line that is in contact with the vertex 44b is 20 degrees, and is preferably in the range of more than 18 degrees and not more than 25 degrees. In the restricting protrusion 44a, the first height H1 of the vertex 44b in the spool axis direction is smaller than half of the second height H2 of the second position E corresponding to the maximum drag position. For example, in this embodiment, the first height H1 of the vertex 44b is 0.6 mm to 0.8 mm, and the second height H2 of the second position E is 1.7 mm to 2.mm. mm. In this embodiment, the second position E is 150 degrees away from the reference position A.

  Here, in the first inclined surface 44c and the second inclined surface 44d sandwiching the apex 44b of the restricting protrusion 44a, the inclination angle α of the first inclined surface 44c on the drag release position side is smaller than the inclination angle β of the second inclined surface 44d. is doing. For this reason, when the drag adjusting lever 2 is rotated from the maximum drag position side to the rotation restricting portion 44, the drag force increases before the restricting projection 44a, and the turning operation to the drag releasing position is in the middle. It becomes difficult to do. Further, in the rotation operation from the drag release position toward the rotation restricting portion 44, the first inclined surface 44c is gently inclined, so that the change in the drag force is reduced and the rotation operation is facilitated.

  In the restricting protrusion 44a, the first height H1 of the apex 44b in the spool axis direction is smaller than half of the second height H2 of the second position corresponding to the maximum drag position. For this reason, since the apex 44b is located at a position where the movement amount is half or less of the maximum movement amount of the spool shaft 5, a small drag force can be applied to the spool 4 during regulation.

  The cam surface 49 is formed from the first position B to the reference position A, and is formed from the second position E to the fourth position F. The first flat surface 49a is disposed substantially orthogonal to the spool shaft. A second flat surface 49b that is arranged in parallel with the surface 49a and protrudes in the axial direction from the first flat surface 49a; and a third inclined surface 49c that connects the first flat surface 49a and the second flat surface 49b. . The restricting protrusion 44a is formed so as to protrude between the first flat surface 49a and the third inclined surface 49c.

  In this embodiment, the third inclined surface 49c is composed of a fourth inclined surface 49d and a fifth inclined surface 49e having different inclination angles at a third position D of 100 degrees from the reference position A. The inclination angle γ of the fourth inclined surface 49d exceeds 3 degrees and is 4 degrees or less, and the inclination angle δ of the fifth inclined surface 49e is smaller than the fourth inclined surface 49d and exceeds 2 degrees and is 3 degrees or less. . The third position D is formed with a recessed portion 49f that is slightly recessed (for example, in a range of 0.05 mm to 0.2 mm) in an arc shape for notifying the strike position. The recess 49f is also formed with a radius substantially the same as that of the cam receiving pin 52a. If the strike position is exceeded, the tilt angle becomes smaller, so the drag force increase rate becomes smaller when the strike position is passed.

  The angle from the reference position A to the fourth position F is, for example, 170 degrees. In the fourth position F, a regulation wall 49g parallel to the spool shaft is formed. The drag release position is regulated by the regulating wall 49g, and the drag adjusting lever 2 does not rotate any more. However, on the maximum drag position side, if there is no stopper 35 as described above, it can rotate beyond the regulating wall 49g. For this reason, the stopper 35 restricts the drag adjusting lever 2 from rotating beyond the maximum drag position. The regulating wall 49g is also formed with an arc surface having the same diameter as the cam receiving pin 52a.

<Other cam mechanism configurations>
As shown in FIGS. 4 and 5, the drag adjustment knob 51 is a member that is screwed into a male screw portion 5 c formed at the tip of the spool shaft 5. The drag adjustment knob 51 can adjust the drag force at the strike position and the adjustment range of the drag force by adjusting the screwing amount. The drag adjustment knob 51 is provided with a knob sound generation mechanism 55 that generates sound during operation. The knob sound generating mechanism 55 is attached to the sounding recess 50f formed in the cam member 50 and the storage hole 51a formed along the spool shaft 5 in the drag adjusting knob 51 so as to be able to advance and retract toward the sounding recess 50f. And a spring member 55b that urges the sound output pin 55a toward the sound output recess 50f.

  As described above, the cam receiving portion 52 has the two cam receiving pins 52 a erected on the insert member 48 of the drag adjusting lever 2. The cam receiving pin 52a is, for example, a rod-shaped member made of stainless alloy, and is fixed to the outer peripheral surface of the cylindrical portion 48a on the small diameter side of the insert member 48 by appropriate fixing means such as press fitting or adhesion. The cam receiving pin 52a contacts the cam surface 49 to move the cam member 50.

  The first biasing member 53 is disposed on the outer periphery of the spool shaft 5 between the bearing 20b and the bearing 20c. The first urging member 53 urges the spool 4 in a direction away from the drag mechanism 6 to bring the cam member 50 into contact with the cam receiving portion 52. The second urging member 54 is disposed on the outer periphery of the spool shaft 5 on the axially outer side (left side in FIG. 3) of the bearing 20a. The second biasing member 54 biases the spool 4 axially inward (right side in FIG. 3) with respect to the spool shaft 5. The second urging member 54 is disposed between the retaining ring 5b attached to the spool shaft 5 and the bearing 20a. The first urging member 53 is weaker than the second urging member 54. For this reason, when the spool shaft 5 moves to the right in the axial direction during drag adjustment, the first urging member 53 is first compressed, and then the second urging member 54 is compressed. The second urging member 54 is provided for smoothly changing the drag force.

<Configuration of drag mechanism>
The drag mechanism 6 relatively moves in the direction of the spool 4 and the spool shaft 5 and brakes the rotation of the spool 4 in the yarn unwinding direction. As shown in FIGS. 5 and 6, the drag mechanism 6 is stored in a circular storage space 36 formed on the first flange portion 9 b side of the spool 4. The drag mechanism 6 includes a friction disk 21 that can rotate integrally with the spool body 9, a braking disk 22 that is disposed to face the friction disk 21, and a cover member 26 that covers the storage space 36 from the outside in the spool axial direction. Have.

  The friction disk 21 is disposed in contact with the outer surface of the first flange portion 9 b of the spool body 9 in the storage space 36. The friction disk 21 is a disk-shaped member having at least one (for example, four) engaging recesses 21a that are recessed on the inner peripheral side on the outer peripheral surface. The friction disk 21 is connected to the spool body 9 by a cover member 26 so as to be integrally rotatable. The friction disk 21 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.

  The cover member 26 is a bottomed cylindrical metal member such as an aluminum alloy having a cylindrical portion 26a and a bottom portion 26b, and a plurality of screw members (see FIG. 5) on the end surface of the first flange portion 9b. 28 is fixed. The cover member 26 has a passage hole 26c through which the main body member 25 of the brake disk 22 can pass at the center of the bottom portion 26b. The cylindrical portion 26 a has an outer peripheral surface 26 d that fits to the inner peripheral surface of the first flange portion 9 b that is the inner peripheral surface of the storage space 36. The cylindrical portion 26 a has a length in the spool axial direction in which the tip can approach the side surface of the friction disk 21 when the cover member 26 is fixed to the first flange portion 9 b. On the outer peripheral surface 26d of the cylindrical portion 26a, a protruding portion 26f that protrudes in a circular shape from the outer peripheral surface and can be in close contact with the end surface of the first flange portion 9b is formed. The protruding portion 26f is disposed to face the end surface of the first flange portion 9b, and a plurality of screw passage holes 26g to which the screw members 28 (FIG. 7) are attached are formed at intervals in the circumferential direction. A screw hole 9j (FIG. 7) into which the screw member 28 is screwed is formed on the end face of the first flange portion 9b.

  The cover member 26 has at least one engagement protrusion 26e that is provided on the distal end surface of the cylindrical portion 26a and engages with the engagement recess 21a. A plurality of (for example, four) engagement protrusions 26e are formed in a circular arc shape at the distal end of the cylindrical portion 26a and projecting toward the outer surface of the first flange portion 9b with a gap in the circumferential direction. The engaging protrusion 26e has a protruding length in the spool axial direction so that a slight gap is formed between the tip portion and the outer surface of the first flange portion 9b.

  The brake disk 22 is connected to the second one-way clutch 64, and is prohibited from rotating in the yarn feeding direction. As shown in FIGS. 5 and 6, the braking disk 22 includes a donut-shaped sliding disk 24 on which the friction disk 21 can be pressed and a main body that is mounted on the spool shaft 5 so as not to be axially movable and rotatable. Member 25. The sliding disk 24 is made of a heat and corrosion resistant metal such as stainless steel. The sliding disk 24 has a slightly smaller diameter than the friction disk 21, and is prevented from being detached from the main body member 25 by a retaining member 27. The sliding disk 24 has a rectangular engagement hole 24a that engages with the main body member 25 so as to be integrally rotatable.

  The main body member 25 is a substantially cylindrical member made of, for example, an aluminum alloy. The main body member 25 is rotatably supported on the spool shaft 5 by the bearing 20c as described above. A rectangular engagement hole 25a (FIG. 5) is formed on the inner peripheral surface of the main body member 25 on the pinion gear 61 side so that the disk support portion 61b of the pinion gear 61 can be integrally rotated. Further, a connecting groove 25b for connecting the ratchet wheel 66 of the second one-way clutch 64 so as to be integrally rotatable is formed along the diameter direction on the shaft end surface on the pinion gear 61 side. The ratchet wheel 66 rotates integrally with the pinion gear 61 and the main body member 25 by engaging the engagement protrusion 66b of the ratchet wheel 66 with the connection groove 25b.

  On the outer peripheral surface of the main body member 25 opposite to the pinion gear 61, a rectangular detent 25c for connecting the sliding disk 24 so as to be integrally rotatable is formed. The main body member 25 and the sliding disk 24 rotate together by engaging the engaging hole 24a of the sliding disk with the rotation preventing portion 25c. In addition, an annular groove 25d for mounting the retaining member 27 is formed in the rotation preventing portion 25c. Further, an annular mounting groove 25e for mounting a seal member 29 for sealing the inside of the cover member 26 is formed on the outer peripheral surface between the rotation stopper 25c and the connecting groove 25b. Since the main body member 25 is engaged with the pinion gear 61 on the inner peripheral surface, the reel main body 1 is restricted from moving axially outward (right side in FIG. 5) via the pinion gear 61 and the bearing 20d. Yes.

  The seal member 29 has a lip 29a on the outer peripheral portion. The lip 29a does not come into contact with the cover member 26 when in the drag released state shown on the upper side of the spool shaft core X in FIG. 5, but comes into contact with the cover member 26 when in the maximum drag state shown on the lower side of the spool shaft core X. It is configured to seal the inside. Thereby, the rotational resistance of the spool 4 when freely rotating in the drag released state can be reduced.

  When assembling the drag mechanism 6 having such a configuration, for example, the brake disk 22 and the friction disk 21 are placed on the cover member 26 side after the spool 4 is mounted on the spool shaft 5. At this time, the engagement recess 21a of the friction disk 21 and the engagement protrusion 26e of the cover member 26 are engaged. Then, the protruding portion 26 f of the cover member 26 is brought into close contact with the end surface of the first flange portion 9 b through the spool shaft 5. At this time, when the protrusion 26f is not in close contact, the engagement protrusion 26e is not accurately engaged with the engagement recess 21a, so that the engagement protrusion 26e and the engagement recess 21a are engaged again. Finally, the cover member 26 is fixed to the first flange portion 9b by the screw member 28 in phase with the screw hole 9j and the screw passage hole 26g. As a result, the friction disk 26 is prevented from rotating with respect to the spool 4. As described above, if the engagement protrusion 26e is not engaged with the engagement recess 21a, a gap is formed between the protruding portion 26f and the end surface of the first flange portion 9b. Whether or not the mating recess 21a is engaged can be easily grasped visually. Here, the friction disk 21 is prevented from rotating by the cover member 26 instead of the storage space 36. For this reason, the cylindrical portion 26a of the cover member 26 can be fitted into the storage space 36, and the gap between the cover member 26 and the storage space 36 can be reduced. Moreover, the protruding portion 26f is in close contact with the end surface of the first flange portion 9b. Therefore, the friction disk 21 can be prevented from rotating even if the storage space 36 is shaped to be easily sealed.

  Further, the cylindrical portion 26a has a length in the spool axial direction in which the tip can approach the side surface of the friction disc 21 when the cover member 26 is fixed to the first flange portion 9b. Even if the friction disk 21 is separated from the friction disk 21, the friction disk 21 is less likely to rattle.

  Furthermore, the engagement protrusion 26e has a length in the spool axial direction such that a gap is formed between the engagement protrusion 26e and the outer surface of the first flange portion 9b. For this reason, even if the cover member 26 is fixed to the first flange portion 9b, the tip end portion of the engagement protrusion 26e does not come into contact with the outer surface of the first flange portion 9b, and a gap between the cover member 26 and the storage space 36 is formed. It can be further reduced.

<Configuration of spool sound generation mechanism>
8 and 11, the spool sound generation mechanism 18 includes a sound generation member 75 fixed to the outer surface of the second flange portion 9c of the spool body 9, and a sound generation position where the second side plate 13b contacts the sound generation member 75. A striking member 76 that is mounted so as to freely move to and away from the silent position; a knob member 77 that moves the striking member 76; and a biasing member 78 that biases the striking member 76 to the neutral position. .

  The sound generating member 75 is a member made of, for example, synthetic resin, and has a disk-shaped mounting portion 75a fixed to the spool body 9, and a plurality of gear tooth-shaped irregularities formed integrally with the mounting portion 75a. And an uneven portion 75b. The sound generating member 75 rotates together with the spool 4.

  The striking member 76 is a member made of, for example, a synthetic resin, and repeats a collision with a base end portion 76a that is swingably supported by the knob member 77, and a tip end formed in a taper shape extending from the base end portion. It has a striking part 76b and a constricted part 76c formed between the base end part 76a and the striking part 76b. The striking member 76 is disposed at a portion where the second relief portion 19f of the second cylindrical portion 11b is formed when the striking member 76 retreats to the silent position. Thereby, a striking member can be arrange | positioned radially outward rather than the conventional thing, and the diameter of the sounding member 75 can be enlarged. For this reason, the uneven | corrugated | grooved part 75b increases the number of unevenness | corrugations, and can generate a finer click sound.

  The knob member 77 is a member that moves the striking member 76 between the sound generation position and the silence position. The knob member 77 is a shaft member with a hook having a shaft portion 77a and a knob portion 77b formed at a proximal end portion of the shaft portion 77a and having a diameter larger than that of the shaft portion 77a. The shaft portion 77a is guided by a long hole 13g formed through the inner surface of the outer side surface of the second side plate 13b. The striking member 76 is swingably connected to the tip of the shaft portion 77a.

  The urging member 78 is a member made of, for example, a synthetic resin, and has a C-shaped cylindrical spring portion 78a having a facing portion 78c shaped such that a part of the circumference is cut out, and an intermediate portion of the spring portion 78a. And a mounting portion 78b formed in a plate shape. When the striking member 76 advances to the sound generation position, the constricted portion 76c of the striking member 76 can come into contact with the spring portion 78a between the opposing portions 78c. The attachment portion 78b has a fixing hole 78d through which the screw member 79 penetrates at the center, and has a pair of positioning projections 78e and 78f for positioning on both sides of the fixing hole 78d. The fixing hole 78d can be opposed to the screw hole 13h formed on the inner side surface of the second side plate 13b and to which the screw member 79 is screwed, and the positioning protrusions 78e and 78f are positioning holes 13i formed on both sides of the screw hole 13h. , 13j. As a result, the positioning accuracy can be improved, and the biasing member that has been conventionally fixed with two screw members can be fixed with one screw member, and the number of parts can be reduced.

<Drag force adjustment range setting operation>
In the dual-bearing reel configured as described above, the drag adjusting knob 51 is used when setting the drag force adjustment range of the drag mechanism 6. When the drag adjustment knob 51 is rotated counterclockwise, the drag adjustment knob 51 moves slightly to the left in the axial direction on the lower side of FIG. 5 and shifts in a direction in which the adjustment range of the drag force is slightly weakened. Further, when the drag adjustment knob 51 is rotated clockwise, the drag adjustment knob 51 is moved slightly to the right in the axial direction on the lower side of FIG. 5 and shifted in a direction in which the drag force adjustment range is slightly increased. Specifically, a weight of a predetermined mass is tied to the tip of the fishing line, and the drag adjustment range is adjusted so that the drag is activated when the drag adjustment lever 2 is pulled to the strike position.

  When adjusting the drag force of the drag mechanism 6, the drag adjustment lever 2 is rotated. When the drag adjusting lever 2 is arranged at the drag release position, which is the closest rotation position indicated by a two-dot chain line in FIG. 2, as shown in FIG. 10, the cam receiving pin 52a is a first flat that is the drag release position. Arranged on the surface 49a. Then, when the drag adjusting lever 2 is rotated clockwise in FIG. 2, the cam receiving pin 52a moves along the first inclined surface 44c of the restricting projection 44a of the cam surface 49 and reaches the apex 44b. At this time, the first urging member 53 having a weak urging force is compressed and the cam member 50 is gradually moved outward in the spool axial direction (right side in FIG. 3), and the spool shaft 5 and the spool 4 are gradually moved to the right side in FIG. Move.

  In the case of the normal drag adjustment range, the friction disk 21 is moved to the braking disk 22 at the position of the first inclined surface 44c lower than the lowest position of the curved second inclined surface 44d. Contact and drag force is generated. Then, the drag force gradually increases when the apex 44b of the restricting protrusion 44a is detected, and once the apex 44b is exceeded, the drag force is once weakened. However, when the lowest position of the second inclined surface 44d is exceeded, the cam receiving pin 52a comes into contact with the third inclined surface 49c, and the drag force gradually increases. When the second flat surface 49b is reached, the maximum drag force in the drag adjustment range is obtained. In the turning operation until the vertex 44b is exceeded, since the first inclined surface 44c has a smaller inclination angle than the second inclined surface 4d (angle α <angle β), the rate of increase of the drag force is reduced and the rotation operation is performed. It becomes easier to do.

  When the drag adjusting lever 2 is further operated clockwise in FIG. 2 while the brake disk 22 is in contact with the friction disk 21, the spool shaft 5 is moved and the disc spring of the second urging member 54 is gradually compressed. The drag force increases in proportion to the amount of compression. When the strike position is reached, the cam receiving pin 52a is arranged in the recess 49f, and the operator can recognize this with a slight click feeling. When the operation is performed up to the strike position, a predetermined drag force adjusted by the operation of the drag adjustment knob 51 is obtained. If the drag operation lever 2 is further rotated from the strike position, the rate of increase becomes smaller than before. When the cam receiving pin 52a reaches the second flat portion 49b, the drag force becomes the maximum adjustment range.

  On the other hand, when the drag adjusting lever 2 is turned in the reverse direction (counterclockwise in FIG. 2), the spool 4 and the second urging member 54 made of four disc springs and the first urging member 53 made of a coil spring are used. The spool shaft 5 is urged to the left in FIG. 3, and the drag force gradually decreases. When the urging force becomes weaker than the urging force by the first urging member 53 by the second urging member 54, the friction disk 21 is separated from the braking disk 22 to be in a brake release state. If the cam receiving pin 52a reaches the restricting projection 44a of the rotation restricting portion 44 during this turning operation, the drag force increases once and it becomes difficult to turn. For this reason, even if the drag adjustment lever 2 is operated to the drag release position side, it is difficult to rotate the drag adjustment lever 2 on the front side of the drag release position.

<Other embodiments>
(A) In the above-described embodiment, the four engagement recesses 21a and the engagement protrusions 26e are provided.

  (B) In the above embodiment, the present invention has been described by taking the drag mechanism disposed on the handle 3 side as an example, but the present invention can also be applied to a drag mechanism disposed on the opposite side of the handle 3.

  (C) In the above-described embodiment, the tip of the cylindrical portion 26a is brought close to the friction disk 21 and the friction disk 21 is prevented from being removed by the cover member 26, but may be retained by another member.

  (D) In the above embodiment, the cover member 26 is fixed to the first flange portion 9b by the screw member 28. However, the cover member 26 may be fixed by other fixing means such as elastic locking or screw connection. For example, in FIG. 12, a male screw portion 126h is formed on the outer peripheral surface 126d of the cylindrical portion 126a of the cover member 126, and a female screw portion 109k that is screwed to the male screw portion 126h is formed on the inner peripheral surface of the first flange portion 109b of the spool body 109. Provided. Further, the protruding portion 126f can be in close contact with the end surface of the first flange portion 109b as in the above-described embodiment. In this embodiment, the thickness of the cylindrical portion on the outer peripheral side of the first flange portion 109b can be made thinner than that in the above embodiment. For this reason, the diameter of the sliding disk 125 of the friction disk 121 and the brake disk 122 can be made larger than the said embodiment.

  (E) In the embodiment described above, a seal member such as packing is not provided between the cover member 26 and the first flange portion 9b, but a seal member may be provided. For example, in FIG. 13, an annular mounting groove 226i is formed on the outer circumferential surface 226d of the cylindrical portion 226a of the cover member 226. A sealing member 80 in the form of an O-ring, for example, is mounted in the annular mounting groove 226i, and seals the gap between the outer peripheral surface 226d of the cylindrical portion 226a and the inner peripheral surface of the first flange portion 9b. When such a seal member 80 is mounted between the cover member 226 and the first flange portion 9b, the liquid is less likely to enter the storage space 36.

  The seal member is not limited to the O-ring, and the mounting position of the seal member is not limited between the outer peripheral surface of the cylindrical portion 226a and the inner peripheral surface of the first flange portion 9b. For example, a ring-shaped sheet packing may be attached to the end surface of the first flange portion and the inner surface of the protruding portion of the cover member.

The perspective view of the double bearing reel which employ | adopted one Embodiment of this invention. The handle | side side view of the said double bearing reel. Sectional drawing of the said double bearing reel. The exploded perspective view of a drag adjustment mechanism. The expanded sectional view which shows the structure of each part by the side of a handle | steering-wheel. The disassembled perspective view which shows the structure of the rotation transmission system containing a drag mechanism. Sectional drawing partial drawing of the circumference | surroundings of a spool. The front view of a cam member. Sectional drawing of a cam member. FIG. 3 is a development view in which an arcuate cam surface is linearly developed. The exploded perspective view of a spool sound generation mechanism. The figure equivalent to FIG. 5 of other embodiment. The figure equivalent to Drawing 5 of other embodiments.

Explanation of symbols

1 Reel body 4 Spool 5 Spool shaft 6 Drag mechanism 7 Drag adjustment mechanism (an example of movement mechanism)
9a 1st flange part (an example of a flange part)
21 Friction disk 21a Engaging recess 22 Brake disk 26 Cover member 26a Cylindrical part 26d Outer peripheral surface 26e Engaging protrusion 26f Projecting part 36 Storage space

Claims (4)

A drag mechanism for a dual-bearing reel that brakes the spool by moving relative to a spool mounted in a reel body of the dual-bearing reel in the axial direction of the spool,
A friction disk disposed in a cylindrical storage space formed in the flange portion of the spool and having at least one engaging recess recessed on the outer peripheral surface on the inner peripheral side;
From the cylindrical portion having an outer peripheral surface that fits to the inner peripheral surface of the storage space, at least one engaging protrusion provided on the distal end surface of the cylindrical portion and engaging with the engaging recess, and the outer peripheral surface of the cylindrical portion A cover member that protrudes in a circular shape and is provided so as to be in close contact with the end face of the flange portion, and is fixed to the flange portion and covers the storage space from the outside in the axial direction;
A braking disk that is disposed in the storage space so as to face the friction disk, and that cannot rotate in the yarn unwinding direction;
A moving mechanism for moving the friction disk relative to the brake disk together with the spool in the spool axial direction to press-contact the friction disk and the brake disk;
The double-bearing reel drag mechanism with   2. The drag mechanism for a dual-bearing reel according to claim 1, wherein the engaging protrusion is formed to protrude toward the flange portion in a circular arc shape at a distal end of the cylindrical portion at a circumferential interval.   3. The drag mechanism of the dual-bearing reel according to claim 2, wherein the cylindrical portion has a length in the spool axial direction in which the tip can approach the side surface of the friction disk when the cover member is fixed to the flange portion. .   4. The drag mechanism for a dual-bearing reel according to claim 3, wherein the engagement protrusion has a length in the spool axial direction such that a gap is formed between the engagement protrusion and the outer surface of the flange portion.

Images