JP5536591B2 - Double bearing reel - Google Patents

Description

  The present invention relates to a dual-bearing reel, and more particularly to a dual-bearing reel having a roller-type one-way clutch between a reel body and a handle shaft.

  Generally, a roller-type one-way clutch for operating a drag mechanism is mounted on a handle shaft on a dual-bearing reel (see, for example, Patent Document 1). The conventional one-way clutch is disposed between the reel body and the handle shaft, and prohibits reverse rotation of the handle shaft. In addition to the one-way clutch on the roller side, a claw-type one-way clutch is provided to prevent reverse rotation of the handle shaft. The conventional roller type one-way clutch prevents the reverse rotation of the handle shaft until a predetermined limit torque is exceeded, and allows the reverse rotation when the predetermined limit torque is exceeded. This prevents damage to the roller type one-way clutch. The conventional roller type one-way clutch is an inner ring idle type, and the limit torque is adjusted to be smaller than the maximum drag torque when the maximum drag force is applied to the drag mechanism by the finishing accuracy of the outer peripheral surface of the inner ring. ing.

Japanese Patent No. 3325754

  In the conventional configuration, the limit torque at which the sliding starts is set by the finishing accuracy of the outer peripheral surface of the inner ring. For this reason, the limit torque may vary due to factors such as variations in the dimensions of the one-way clutch and changes in the viscosity of the grease due to temperature changes.

  In the conventional configuration, the rotation is prevented until a predetermined limit torque set smaller than the maximum drag torque is exceeded, and the rotation is allowed if the rotational force exceeds the limit torque. For this reason, the maximum rotational resistance torque of the one-way clutch is not sufficiently exhibited.

  An object of the present invention is to provide a double-bearing reel having a roller-type one-way clutch so that the limit torque at the start of sliding of the one-way clutch can be stably obtained and the maximum rotational resistance torque of the one-way clutch can be fully exhibited. There is to do.

  A dual-bearing reel according to a first aspect of the present invention includes a reel body having a handle disposed on a side, a spool, a rotation transmission mechanism, a drag mechanism, a roller-type first one-way clutch, and a press-fitting ring. . The spool is rotatable with respect to the reel body. The rotation transmission mechanism has a handle shaft, a main gear, and a pinion gear. The handle shaft has a handle attached thereto. The main gear is provided on the handle shaft. The pinion gear is mounted on the rotating shaft of the spool and meshes with the main gear. The drag mechanism is disposed around the handle shaft. The roller type first one-way clutch is disposed between the reel body and the handle shaft. The press-fitting ring has a plurality of protrusions that protrude in the radial direction and are spaced apart in the circumferential direction. In the press-fitting ring, a force with a limit torque that is greater than the maximum drag torque of the drag mechanism and less than the maximum rotation resistance torque of the first one-way clutch is applied to the handle shaft between either the reel body or the handle shaft and the first one-way clutch. The first one-way clutch is press-fitted so as to start rotating.

  In the dual-bearing reel, a press-fit ring is disposed between the reel body and the first one-way clutch or the first one-way clutch and the handle shaft. The press-fitting ring is press-fitted so that the first one-way clutch starts to slip when the torque of the limit torque acts on the outer peripheral side or the inner peripheral side of the first one-way clutch. For this reason, the first one-way clutch can be slid with high accuracy when the torque of the limit torque acts on the press-fitting ring only by keeping the accuracy of the press-fitting surface of the reel body or the handle shaft constant. As a result, the limit torque at the start of slipping of the first one-way clutch can be stably obtained. In addition, since it starts to slip at a limit torque that is larger than the maximum drag torque of the drag mechanism and less than the maximum rotation resistance torque of the first one-way clutch, the maximum rotation resistance torque of the first one-way clutch can be fully exhibited.

  A dual-bearing reel according to a second aspect of the present invention is the reel according to the first aspect, wherein the press-fitting ring is disposed between the reel body and the first one-way clutch. In this case, since the outer ring side of the first one-way clutch having a large diameter slips, in the case of the inner ring idle type, it is possible to protect the outer ring that is easily damaged due to the formation of a cam surface. Moreover, since the outer ring has a larger diameter than the inner ring, the limit torque at the start of sliding can be increased.

  The dual-bearing reel according to a third aspect is the reel according to the second aspect, wherein the first one-way clutch has an outer ring, an inner ring, and a rolling element. The outer ring is non-rotatably connected to the reel body. The inner ring is coupled to the handle shaft so as to be integrally rotatable via a drag mechanism. The rolling element is disposed between the outer ring and the inner ring. The press-fitting ring is disposed between the outer ring and the reel body.

  A dual-bearing reel according to a fourth aspect of the present invention is the reel according to any one of the first to third aspects, wherein the press-fitting ring has a slit at one place in the circumferential direction. In this case, since the slit is provided in the press-fitting ring, the allowable size of the press-fitting ring increases.

  A dual-bearing reel according to a fifth aspect of the present invention is the reel according to any one of the first to fourth aspects, wherein the press-fitting ring is a tolerance ring for absorbing a dimensional error. In this case, since the tolerance ring machined with high accuracy for absorbing the dimensional error is used as the press-fitting ring, a stable limit torque of the sliding torque can be obtained with higher accuracy.

  A dual-bearing reel according to a sixth aspect of the present invention is the reel according to any one of the first to fifth aspects, wherein at least a portion of the reel body to which the first one-way clutch is mounted is made of an aluminum alloy, and the reel body of the first one-way clutch The portion to be attached to is made of a stainless alloy. In this case, since the first one-way clutch is harder than the reel main body, the press-fitting ring is easily inserted into the reel main body, and the first one-way clutch is surely slipped with respect to the press-fitting ring.

  A dual-bearing reel according to a seventh aspect of the present invention is the reel according to any one of the first to sixth aspects, wherein the second one-way clutch of a claw type having a ratchet wheel and a ratchet pawl arranged so as to be integrally rotatable with the handle shaft is provided. It has more. The ratchet pawl is swingably supported by the reel body so as to prevent the ratchet wheel from rotating in the yarn unwinding direction. In this case, even if the first one-way clutch starts to slide in the yarn feeding direction together with the handle shaft, the rotation of the handle shaft in the yarn feeding direction can be stopped by the meshing of the teeth of the ratchet wheel and the ratchet pawl.

  According to the present invention, the press-fitting ring is press-fitted so that the one-way clutch starts to slip when the torque of the limit torque acts on the outer peripheral side or the inner peripheral side of the one-way clutch. For this reason, it can be easily slid only by maintaining the accuracy of the press-fitting surface of the reel main body or the handle shaft. As a result, the limit torque at the start of slipping of the first one-way clutch can be stably obtained. In addition, since it starts to slip at a limit torque that is larger than the maximum drag torque of the drag mechanism and less than the maximum rotation resistance torque of the first one-way clutch, the maximum rotation resistance torque of the first one-way clutch can be fully exhibited.

The side view of the double bearing reel by one Embodiment of this invention. II-II sectional view taken on the line of FIG. The cross-sectional enlarged view of the drag mechanism part of FIG. The exploded perspective view of the rotation transmission mechanism containing a drag mechanism.

  1 and 2, a double-bearing reel adopting an embodiment of the present invention is a round double-bearing reel used for bait casting, jigging and the like. The dual-bearing reel includes a reel body 1, a spool rotation handle 2 disposed on the side of the reel body 1, and a spool 12 rotatably mounted inside the reel body 1.

  In the following description, front, rear, left, and right refer to the direction in which the fishing line is fed out with both bearing reels mounted on a fishing rod, and the left and right when viewed from the rear.

  The handle 2 is of a single handle type having a plate-like arm portion 2a and a handle 2b rotatably attached to the tip of the arm portion 2a. As shown in FIG. 2, the arm portion 2 a is attached to the tip end of the handle shaft 30 so as to be integrally rotatable, and is fastened to the handle shaft 30 by a nut 28.

  As shown in FIG. 2, the reel body 1 is a metal member such as an aluminum alloy or a magnesium alloy, and includes a frame 5, a first side cover 6 and a second side cover mounted on both sides of the frame 5. 7. A spool 12 is rotatably mounted inside the reel body 1 via a spool shaft 20. The frame 5 includes a pair of left and right ring-shaped first side plates 8 and second side plates 9 arranged at a predetermined interval, and a plurality of connecting portions 10 that connect the first side plates 8 and the second side plates 9; have. The first side plate 8 has a smaller diameter than the second side plate 9.

  The plurality of connecting portions 10 are integrally formed with the first side plate 8 and the second side plate 9. As shown in FIG. 1, a connecting rod 10 formed on the lower side is riveted with a rod mounting leg portion 4 made of metal such as aluminum alloy which is long before and after the reel is mounted on a fishing rod. .

  The first side cover 6 is circular when viewed from the outside in the spool axial direction, and is integrally formed with the first side plate 8. The first side cover 6 rotatably supports a left end of a spool shaft 20 described later.

  As shown in FIG. 1, the second side cover 7 includes a circular portion 7a and a bulging portion 7b that protrudes outward and radially outward from the circular portion 7a. The bulging portion 7b is formed in a deformed oval shape when viewed from the side. A cylindrical first boss portion 7c for supporting the handle shaft 30 is formed on the bulging portion 7b.

  As shown in FIG. 2, the second side cover 7 is made of, for example, an aluminum alloy, and supports the handle shaft 30 rotatably. A clutch lever 17 is attached to the rear portion of the second side cover 7. A mechanism mounting plate 37 constituting the frame 5 is disposed between the second side cover 7 and the second side plate 9.

  As shown in FIG. 2, between the second side cover 7 and the mechanism mounting plate 37, there are a rotation transmission mechanism 19, a clutch mechanism 21, a clutch control mechanism 22, a drag mechanism 23, a casting control mechanism 24, and the like. , Is arranged. The rotation transmission mechanism 19 transmits the rotational force from the handle 2 to the spool 12. The clutch mechanism 21 connects and disconnects the handle 2 and the spool 12. When the clutch mechanism 21 is in the clutch-off state (disengaged state), the spool 12 is in a freely rotatable state. The clutch control mechanism 22 includes a clutch yoke 35 and a clutch plate (not shown), and controls the clutch mechanism 21 between a clutch-on state (connected state) and a clutch-off state according to the operation of the clutch lever 17. The drag mechanism 23 brakes the rotation of the spool 12 in the yarn feeding direction. The casting control mechanism 24 adjusts the resistance force when the spool 12 rotates. In addition, a spool lock mechanism (not shown) that can lock and unlock the rotation of the spool 12 in the yarn feeding direction is provided between the spool 12 and the first side cover 6.

  As shown in FIG. 2, the spool 12 has a pair of left and right dish-shaped flange portions 12a on both sides, and a cylindrical bobbin trunk 12b between the pair of flange portions 12a. The outer peripheral surface of the flange portion 12a on the left side of FIG. 2 is disposed with a slight gap on the inner peripheral side of the opening in order to prevent thread biting. The spool 12 is fixed to the spool shaft 20 penetrating the inner peripheral side of the bobbin trunk 12b so as not to rotate by, for example, serration coupling. This fixing method is not limited to serration coupling, and various coupling methods such as key coupling and spline coupling can be used.

  As shown in FIG. 2, the spool shaft 20 is made of metal such as SUS304, and is disposed in parallel with the handle shaft 30. The spool shaft 20 extends through the second side plate 9 to the second boss portion 7 f of the second side cover 7. The spool shaft 20 is rotatably supported on the reel body 1 by the first bearing 26 a and the second bearing 26 b on both sides of the spool 12. A large-diameter portion 20a is formed at the center of the spool shaft 20, and an engagement pin 29 constituting the clutch mechanism 21 is fixed to the large-diameter portion 20a. The engagement pin 29 penetrates the large diameter portion 20a along the diameter, and both ends thereof protrude in the radial direction.

  The clutch lever 17 is swingably attached to the rear portion of the second side cover 7. The clutch lever 17 is connected to the clutch control mechanism 22, and when the clutch lever 17 swings, the clutch mechanism 21 is turned on and off.

  As shown in FIG. 4, the rotation transmission mechanism 19 includes a handle shaft 30, a main gear 31 fixed to the handle shaft 30, and a cylindrical pinion gear 32 that meshes with the main gear 31.

  The handle shaft 30 is rotatably mounted on the mechanism mounting plate 37 and the second side cover 7 by a bearing 15 and a bearing 16 (FIG. 2). As shown in FIG. 3, the handle shaft 30 is formed with a plurality of anti-rotation portions 30a each having a notch surface parallel to the outer peripheral surface. A first male screw portion 30b for fixing the arm portion 2a of the handle 2 and a second male screw portion 30c for adjusting the drag force of the drag mechanism 23 are formed on the outer peripheral surface. As shown in FIG. 4, the handle shaft 30 is prohibited from rotating (reversely rotating) in the yarn feeding direction by the roller-type first one-way clutch 86 and the claw-type second one-way clutch 87.

  As shown in FIG. 3, the first one-way clutch 86 is mounted between the first boss portion 7 c of the second side cover 7 and the handle shaft 30. The first one-way clutch 86 includes an outer ring 86a that is non-rotatably attached to a first boss portion 7c that protrudes outward from the second side cover 7, and an inner ring 86b that is non-rotatably connected to the handle shaft 30. A rolling element 86c that can be inserted between the outer ring 86a and the inner ring 86b. The outer ring 86a is made of, for example, a stainless alloy. The inner peripheral surface of the first boss portion 7c and the outer peripheral surface of the outer ring 86a are not circular in which engaging portions for preventing rotation are arranged at intervals in the circumferential direction as in the prior art, and both are simple circular shapes. . A pair of locking projections 86d protruding in the axial direction are formed on one end surface of the inner ring 86b.

  A press-fit ring 54 is press-fitted between the outer ring 86 a of the first one-way clutch 86 and the first boss portion 7 c. As shown in FIG. 4, the press-fit ring 54 is a substantially cylindrical member, and has a slit 54 a at one place in the circumferential direction. The press-fit ring 54 has a plurality of protrusions 54b that protrude in the radial direction and are spaced apart in the circumferential direction. The protrusion 54b has an oval shape that is long in the axial direction, and protrudes outward in the radial direction. The press-fitting ring 54 uses a tolerance ring for cross absorption, and uses an elastic force to prevent the outer ring 86a from rotating. Here, the processing intersection of the outer peripheral surface of the outer ring 86a and the inner peripheral surface of the first boss portion 7c may be, for example, H9 / h9. The press-fit ring 54 is press-fitted with a predetermined force into the gap between the inner peripheral surface of the first boss portion 7c and the outer peripheral surface of the outer ring 86a. This pressure input is a force that causes the first one-way clutch 86 to start to slip when a force of a limit torque that is greater than or equal to the maximum drag torque of the drag mechanism 23 and less than the maximum rotation resistance torque of the first one-way clutch 86 acts on the handle shaft 30. Set to The pressure input is determined by the difference between the inner diameter of the first boss 7c and the outer diameter of the press-fit ring 54 in a free state.

  Originally, if the maximum drag torque is smaller than the maximum rotation resistance torque of the first one-way clutch 86, no force greater than the maximum rotation resistance torque acts on the first one-way clutch 86. For this reason, it is considered that the first one-way clutch 86 is not damaged. However, in actuality, when an impact load is applied, such as a wake (hooking), a force exceeding the maximum rotational resistance torque acts on the first one-way clutch 86 before the drag mechanism 23 operates. In such a case, in this embodiment, since the first one-way clutch 86 and the press-fit ring 54 are slipped, the first one-way clutch 86 is not easily damaged.

  As shown in FIG. 4, the second one-way clutch 87 includes a ratchet wheel 88 that is mounted on the handle shaft 30 so as to be integrally rotatable, and a ratchet pawl 89 that is swingably mounted on the mechanism mounting plate 37. ing. As shown in FIG. 3, the ratchet wheel 88 is disposed on the back side of the main gear 31 with the drag disk 65 d interposed therebetween. The ratchet wheel 88 has a plurality of ratchet teeth (not shown) arranged on the outer periphery with a sense in the circumferential direction. The ratchet pawl 89 is swingably mounted on a boss shaft (not shown) formed to protrude from the mechanism mounting plate 37. The ratchet pawl 89 swings between a reverse rotation prevention position that engages with the ratchet teeth of the ratchet wheel 88 and a reverse rotation permission position that moves away from the reverse rotation prevention position. The ratchet pawl 89 swings to a reverse rotation permission position when the handle shaft 30 rotates in the yarn winding direction by an urging member (not shown), and swings to a reverse rotation prohibition position when the handle shaft 30 rotates in the yarn unwinding direction.

  The main gear 31 is rotatably mounted on the handle shaft 30 and is frictionally coupled to the handle shaft 30 via the drag mechanism 23. On the right side surface of the main gear 31, a circular storage recess 31a for storing the drag mechanism 23 is formed. A pair of engagement recesses 31b are formed on the inner peripheral surface of the storage recess 31a so that a pair of ears 52a of a second drag washer 52, which will be described later, engage with each other so as to be integrally rotatable.

  As shown in FIG. 2, the pinion gear 32 is a cylindrical member that extends inward from the outside of the second side plate 9 and through which the spool shaft 20 penetrates, and is mounted on the spool shaft 20 so as to be movable in the axial direction. ing. Further, the left end of FIG. 2 of the pinion gear 32 is supported on the mechanism mounting plate 37 by a bearing 18a so as to be rotatable and axially movable. The right end portion of the pinion gear 32 in FIG. 2 is rotatably supported by the second boss portion 7f by a bearing 18b attached to the second boss portion 7f. An engagement groove 32 a that engages with the engagement pin 29 is formed at the left end of the pinion gear 32 in FIG. 2. The meshing groove 32a and the engaging pin 29 constitute the clutch mechanism 21. A bearing 18a is disposed on the outer peripheral surface of the meshing groove 32a. A constricted portion 32b having a small diameter is formed adjacent to the meshing groove 32a, and a gear portion 32c that meshes with the main gear 31 is formed at the intermediate portion.

  As shown in FIG. 2, the clutch control mechanism 22 has a clutch yoke 35 that engages with the constricted portion 32 b of the pinion gear 32 and moves the pinion gear 32 along the spool shaft 20 direction. By the swinging operation of the clutch lever 17 from the clutch-on position to the clutch-off position, the clutch yoke 35 is moved rightward in FIG.

  As shown in FIG. 2, the casting control mechanism 24 includes a plurality of friction plates 48 disposed so as to sandwich both ends of the spool shaft 20, and a braking cap 49 for adjusting the clamping force of the spool shaft 20 by the friction plates 48. have. The left friction plate 48 is attached to the center of the first side cover 6. The braking cap 49 is screwed to the outer peripheral surface of the second boss portion 7 f of the second side cover 7.

<Configuration of drag mechanism>
As shown in FIGS. 2, 3 and 4, the drag mechanism 23 has a drag force that changes according to the operation position of the drag adjusting star drag 3, and brakes the spool 12 so that the rotation of the spool 12 in the yarn unwinding direction can be adjusted. To do. The star drag 3 has a nut portion 3 a that is screwed into the second male screw portion 30 c of the handle shaft 30.

  The drag mechanism 23 is provided around the handle shaft 30. The drag mechanism 23 is pressed by the nut portion 3a of the star drag 3, for example, two disc springs 50 shown in FIG. 2, the first drag washer 51, the second drag washer 52 shown in FIG. 3 and FIG. A third drag washer 53. The disc spring 50 is disposed between the star drag 3 and the bearing 16, and the spring force changed by the axial movement of the star drag 3 is applied to the first drag via the bearing 16 and the inner ring 86 b of the first one-way clutch 86. This is transmitted to the washer 51.

  A non-circular detent hole 51a that engages with the detent portion 30a of the handle shaft 30 and a pair of locking projections 86d of the inner ring 86b are coupled to the inner peripheral surface of the first drag washer 51 so as to be integrally rotatable. A pair of connecting recesses 51b are formed. Thus, the first drag washer 51 is coupled to the handle shaft 30 so as to be integrally rotatable. The first drag washer 51 is coupled to the inner ring 86b so as to be integrally rotatable and in contact with the axial direction. As a result, the inner ring 86b can rotate integrally with the handle shaft 30, and the first drag washer 51 is pressed by the inner ring 86b.

  The second drag washer 52 is coupled to the main gear 31 so as to be integrally rotatable. The second drag washer 52 has a pair of locking ears 52a bent on the left side on the outer peripheral surface. The locking ear 52a engages with the engaging recess 31b of the main gear 31.

  The third drag washer 53 has a non-circular anti-rotation hole 53 a that engages with the anti-rotation portion 30 a of the handle shaft 30 on the inner peripheral surface, and can rotate integrally with the handle shaft 30. Accordingly, since the handle shaft 30 is not allowed to rotate reversely by the first one-way clutch 86 and the second one-way clutch 87 and cannot rotate, the first drag washer 51 and the third drag washer 53 are rotated by the main gear 31 rotating in the yarn feeding direction. Also does not rotate in the thread feeding direction.

  Between the first drag washer 51 and the second drag washer 52, between the second drag washer 52 and the third drag washer 53, between the third drag washer 53 and the main gear 31, and between the main gear 31 and the ratchet wheel 88. In between, for example, drag disks 65a to 65d made of carbon or felt are mounted separately.

  The ratchet wheel 88 also functions as the drag mechanism 23. The ratchet wheel 88 is disposed in contact with the flange portion 30d formed on the outer peripheral surface of the handle shaft 30 with a large diameter. The pressing force of the star drag 3 is received by the flange portion 30d.

<Reel operation during actual fishing>
When fishing, first, the clutch lever 17 is operated to the clutch-off position, and the clutch mechanism 21 is brought into the clutch-off state. Casting is performed in this state, and the fishing line is fed out from the spool 12. When the device reaches the water, the handle 2 is slightly rotated in the yarn winding direction. Then, a clutch return mechanism (not shown) operates and the clutch mechanism 21 returns to the clutch-on state.

  Wait for the fish to catch in this state. When a fish is caught on the device, the angler rotates the handle 2 in the direction of winding the yarn and takes in the caught fish. At this time, the main gear 31 rotates in the yarn winding direction (clockwise in FIG. 3).

  In this state, the drag mechanism 23 operates when the fish caught in the device pulls the fishing line with a force greater than the set drag force. That is, in the clutch-on state, the spool 12 rotates in the yarn feeding direction, and the main gear 31 reverses in the yarn feeding direction (counterclockwise in FIG. 4). However, since the handle shaft 30 is prohibited from reversing the yarn feeding direction by the first one-way clutch 86 and the second one-way clutch 87, the main gear 31 rotates in the yarn feeding direction while being braked by the set drag force. If pulling stronger than the set drag force occurs at the start of the drag operation, an excessive force may act on the inner ring 86b of the first one-way clutch 86 before the second one-way clutch 87 is prohibited from reverse rotation. In this case, since the press-fitting ring 54 press-fitted with a predetermined force is disposed between the outer ring 86a and the first boss portion 7c of the reel body 1, a slightly smaller value is obtained due to the torque of the limit torque that the first one-way clutch 86 starts to slide. It is possible to slide the outer ring 86a. The first one-way clutch 86 is stabilized together with the press-fit ring 54 by determining that the press-fit ring 54 slides between the first boss 7c and the first one-way clutch 86 at a value slightly lower than the limit torque of the first one-way clutch 86. And slide out. As a result, the reverse rotation of the handle shaft 30 is prevented by the second one-way clutch 87 without damaging the first one-way clutch 86.

<Features>
The above embodiment can be expressed as follows.

  (A) The dual-bearing reel includes the reel body 1, the spool 12, the rotation transmission mechanism 19, the drag mechanism 23, a roller-type first one-way clutch 86, and a press-fit ring 54. The spool 12 is rotatable with respect to the reel body 1. The rotation transmission mechanism 19 includes a handle shaft 30, a main gear 31, and a pinion gear 32. The handle shaft 30 has the handle 2 attached thereto. The main gear 31 is provided on the handle shaft 30. The pinion gear 32 is attached to the spool shaft 20 that is the rotation shaft of the spool 12 and meshes with the main gear 31. The drag mechanism 23 is disposed around the handle shaft 30. The roller type first one-way clutch 86 is disposed between the first boss portion 7 c of the reel body 1 and the handle shaft 30. The press-fit ring 54 has a plurality of protrusions 54b that protrude in the radial direction and are spaced apart in the circumferential direction. The press-fit ring 54 has a limit torque force between the first boss portion 7 c and the first one-way clutch 86 that is greater than the maximum drag torque of the drag mechanism 23 and less than the maximum rotation resistance torque of the first one-way clutch 86. The force is set such that the first one-way clutch 86 starts to slide when the first actuating action is applied.

  In the dual-bearing reel, a press-fit ring 54 is disposed between the reel body 1 and the first one-way clutch 86 (or between the handle shaft and the one-way clutch). In the press-fit ring 54, the force of the limit torque that is greater than the maximum drag torque of the drag mechanism and less than the maximum rotation resistance torque of the first one-way clutch acts on the handle shaft on the outer peripheral side (or inner peripheral side) of the first one-way clutch 86. Then, the first one-way clutch is press-fitted so as to start rotating. For this reason, only by maintaining the accuracy of the press-fitting surface (the inner peripheral surface of the first boss portion 7c (or the outer peripheral surface of the handle shaft)) of the reel body 1 (or handle shaft), the press-fitting ring 54 has a limit torque. When the torque acts, the first one-way clutch 86 can be slid with high accuracy. For this reason, the limit torque at the start of slipping of the first one-way clutch 86 can be stably obtained. In addition, since the slip starts with a limit torque that is larger than the maximum drag torque of the drag mechanism 23 and less than the maximum rotation resistance torque of the first one-way clutch 86, the maximum rotation resistance torque of the first one-way clutch 86 can be fully exhibited. .

  (B) In the dual-bearing reel, the press-fitting ring 54 is disposed between the reel body 1 and the first one-way clutch 86. In this case, since the first one-way clutch 86 slides on the outer ring 86a side where the diameter of the first one-way clutch 86 is large, in the case of the inner ring idle type, a cam surface is formed and the outer ring 86a that is easily damaged is protected. be able to. Moreover, since the outer ring 86a has a larger diameter than the inner ring 86b, the limit torque at the start of sliding can be increased.

  (C) In the dual-bearing reel, the first one-way clutch 86 has an outer ring 86a, an inner ring 86b, and a rolling element 86c. The outer ring 86a is connected to the reel body 1 so as not to rotate. The inner ring 86b is coupled to the handle shaft 30 via the drag mechanism 23 so as to be integrally rotatable. The rolling element 86c is disposed between the outer ring 86a and the inner ring 86b. The press-fit ring 54 is disposed between the outer ring 86 a and the second side cover 7 of the reel body 1.

  (D) In the dual-bearing reel, the press-fitting ring 54 has a slit 54a at one place in the circumferential direction. In this case, since the slits 54a are provided in the press-fit ring 54, the allowable size of the press-fit ring 54 is increased.

  (E) In the dual-bearing reel reel, the press-fit ring 54 is a tolerance ring for absorbing dimensional errors. In this case, since the tolerance ring machined with high accuracy for absorbing the dimensional error is used as the press-fitting ring, a stable limit torque of the sliding torque can be obtained with higher accuracy.

  (F) In the dual-bearing reel, the second side cover 7 to which at least the first one-way clutch of the reel body 1 is attached is made of aluminum alloy, and the outer ring to be attached to the second side cover 7 of the first one-way clutch 86. 86a is made of a stainless alloy. In this case, since the outer ring 56 a is harder than the second side cover 7, the press-fit ring 54 is easily inserted into the second side cover 7, and the first one-way clutch 86 can slide with respect to the press-fit ring 54 reliably. become.

  (G) The double-bearing reel further includes a claw-type second one-way clutch having a ratchet wheel 88 and a ratchet pawl 89 that are arranged to be rotatable integrally with the handle shaft 30. The ratchet pawl 89 is swingably supported by the mechanism mounting plate 37 of the reel body 1 so as to prevent the ratchet wheel 88 from rotating in the yarn drawing direction. In this case, even if the first one-way clutch 86 starts to slide with the handle shaft 30 in the yarn feeding direction, the rotation of the handle shaft 30 in the yarn feeding direction can be stopped by the engagement between the teeth of the ratchet wheel 88 and the ratchet pawl 89.

<Other embodiments>
As mentioned above, although one Embodiment of this invention was described, this invention is not limited to the said embodiment, A various change is possible in the range which does not deviate from the summary of invention.

  (A) In the above-described embodiment, the press-fitting ring is disposed between the outer ring of the roller-type first one-way clutch that prohibits the reverse rotation of the handle shaft 30 and the reel body, but the present invention is not limited to this. For example, the present invention is also applied to a roller type first one-way clutch provided so that the drag mechanism is activated when the hand is released without prohibiting reverse rotation of the handle shaft and the reel body, and the present invention is applied. it can.

  (B) In the above embodiment, the press-fit ring is disposed between the roller-type first one-way clutch and the reel body, but the one-way clutch and the handle shaft, specifically, the inner ring of the one-way clutch and the handle shaft are arranged. A press-fit ring may be arranged.

  (C) In the above-described embodiment, the protruding portion 54b protrudes radially outward, but the protruding portion may protrude radially inward. Moreover, in the said embodiment, although it protruded in the ellipse, the protrusion shape is not limited to an ellipse. For example, it may be corrugated irregularities, or a part of the circumferential surface may be cut and protruded radially outward or inward.

  (D) In the embodiment, the claw-type second one-way clutch 87 is provided in addition to the roller-type first one-way clutch 86, but the second one-way clutch may not be provided.

DESCRIPTION OF SYMBOLS 1 Reel body 2 Handle 7 2nd side cover 7c 1st boss | hub part 12 Spool 19 Rotation transmission mechanism 23 Drag mechanism 30 Handle shaft 31 Main gear 32 Pinion gear 54 Press-fit ring 54a Slit 54b Projection part 86 1st one-way clutch 86a Outer ring 86b Inner ring 86c Rolling element 86d Locking protrusion

Claims (7)

The reel body with the handle on the side,
A spool rotatable relative to the reel body;
A rotation transmission mechanism having a handle shaft on which the handle is mounted, a main gear provided on the handle shaft, and a pinion gear that is mounted on the rotation shaft of the spool and meshes with the main gear;
A drag mechanism disposed around the handle shaft;
A roller-type first one-way clutch disposed between the reel body and the handle shaft;
A plurality of protrusions projecting in a radial direction and spaced apart in a circumferential direction; between the reel main body and the handle shaft and the first one-way clutch; A double bearing comprising: a press-fitting ring that is press-fitted so that the entire first one-way clutch starts to rotate when a force having a limit value less than the maximum rotational resistance force of the first one-way clutch is applied to the handle shaft. reel.   2. The dual bearing reel according to claim 1, wherein the press-fitting ring is disposed between the reel body and the first one-way clutch. The first one-way clutch includes an outer ring that is non-rotatably coupled to the reel body;
An inner ring coupled to the handle shaft via a drag mechanism so as to be integrally rotatable;
A rolling element disposed between the outer ring and the inner ring,
The dual-bearing reel according to claim 2, wherein the press-fitting ring is disposed between the outer ring and the reel body.   4. The dual-bearing reel according to claim 1, wherein the press-fitting ring has a slit at one place in a circumferential direction. 5.   5. The dual-bearing reel according to claim 1, wherein the press-fitting ring is a tolerance ring for absorbing a dimensional error. 6. At least a portion of the reel body where the first one-way clutch is mounted is made of an aluminum alloy,
The dual-bearing reel according to any one of claims 1 to 5, wherein a portion of the first one-way clutch to be mounted on the reel body is made of a stainless alloy. A claw-type first having a ratchet wheel arranged to rotate integrally with the handle shaft, and a ratchet claw supported swingably on the reel body so as to prevent rotation of the ratchet wheel in a yarn pay-out direction. The double-bearing reel according to claim 1, further comprising a two-way clutch.

Images