Double bearing reel

Abstract

To provide a double-bearing reel in which the braking forces of a plurality of brakes can be easily adjusted from the outside. [Solution] The double-bearing reel (1) has a spool portion (2) for winding fishing line onto it, a housing (6, 33) that rotatably supports the spool portion (2), a first brake unit (5) and a second brake unit (4) that are provided within the housing (6, 33) and are used to control the rotation of the spool portion (2), and a first dial (7) and a second dial (34) that are provided outside the housing (6, 33) and are used to adjust the braking force of the first brake unit (5) and the second brake unit (4), the second dial (34) being cylindrical and rotatably provided on the outside of the first dial (7).

Description

[Technical Field]

[0001] This invention relates to a double-bearing fishing reel. [Background technology]

[0002] Conventionally, dual-bearing reels have been proposed that are equipped with a magnetic brake and a mechanical brake as a braking device that controls the rotation of the spool portion to prevent backlash (see, for example, Patent Document 1). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Utility Model Registration No. 3236349 Summary of the Invention [Problem to be solved by the invention]

[0004] However, with conventional dual-bearing reels such as those described above, although the braking force of the mechanical brake can be adjusted from outside the dual-bearing reel using a dial, adjusting the braking force of the magnetic brake requires disassembly of the dual-bearing reel, which is a complicated process.

[0005] The present invention was made in consideration of the above problems, and its object is to provide a dual-bearing reel in which the braking force of multiple brakes can be easily adjusted externally. [Means for solving the problem]

[0006] In order to solve the above problems, the present invention a spool portion for winding a fishing line; a housing that rotatably supports the spool portion; a first brake unit and a second brake unit provided in the housing for controlling rotation of the spool portion; a first dial and a second dial provided outside the housing for adjusting the braking forces of the first brake unit and the second brake unit, The present invention provides a double-bearing reel, wherein the second dial is cylindrical and rotatably provided on the outside of the first dial. [Effects of the Invention]

[0007] According to the present invention, it is possible to provide a dual-bearing reel in which the braking force of multiple brakes can be easily adjusted externally. [Brief explanation of the drawings]

[0008] [Figure 1] FIG. 1 is a partial cross-sectional view showing a schematic configuration of a main part of a dual-bearing reel according to an embodiment of the present invention. [Figure 2] FIG. 2(a) is a perspective view showing the configuration of a spool portion in a double-bearing reel, and FIG. 2(b) is a front view of FIG. 2(a). [Figure 3] FIG. 3 is an exploded view showing the configuration of the electromagnetic brake unit in a double-bearing reel. [Figure 4] FIG. 4 is an exploded view showing the configuration of the friction brake unit in a double-bearing reel. [Figure 5] Figure 5(a) is a diagram showing the normal state of the braking device in a double-bearing reel, Figure 5(b) is a diagram showing the state where the spool section has moved from the state in Figure 5(a) (corresponding to section A in Figure 6), Figure 5(c) is a diagram showing the state where the magnet section has moved from the state in Figure 5(b) (corresponding to the first half of section B-C in Figure 6), and Figure 5(d) is a diagram showing the state where the magnet section has returned to its original position from the state in Figure 5(c) (corresponding to the second half of section C in Figure 6). [Figure 6] FIG. 6 is a graph showing the relationship between the rotation speed of the spool and the time the lure is flying when a user casts a lure by strongly swinging a rod equipped with a double-bearing reel. [Figure 7]FIG. 7 is a graph showing the relationship between the rotation speed of the spool and the time the lure is flying when a user casts a lure by gently swinging a rod equipped with a double-bearing reel. [Figure 8] FIG. 8 is an exploded view showing the configuration of a first modified example of the shaft and friction brake unit in a dual-bearing reel. [Figure 9] Figure 9(a) is a diagram showing the front side of a side cup in a double-bearing reel (the right side of the side cup on the right side in Figure 1), Figure 9(b) is a diagram showing the back side of the side cup, and Figure 9(c) is a diagram showing the plate. [Figure 10] Figure 10(a) is a diagram showing the front side of the first dial in a double-bearing reel, Figure 10(b) is a diagram showing the back side of the first dial, Figure 10(c) is a diagram showing the front side of the second dial, Figure 10(d) is a diagram showing the back side of the second dial, Figure 10(e) is a diagram showing the back side of the inclined member, Figure 10(f) is a diagram showing the back side of the inclined member, and Figure 10(g) is a diagram showing the front side of the inclined member. [Figure 11] Figure 11 shows how the braking force of the electromagnetic brake is adjusted by rotating the second dial, where Figure 11(a) shows the state in which the push rod of the second dial abuts against a thin part of the inclined member, and Figure 11(b) shows the state in which the push rod of the second dial abuts against a thick part of the inclined member. [Figure 12] Figure 12 shows the configuration of a second variant of the double-bearing reel, where Figure 12(a) shows the state when the electromagnetic brake unit 4 is not operating, Figure 12(b) shows the state where the magnet part has moved towards the second dial side from the state in Figure 12(a), and Figure 12(c) shows the state where the magnet part has moved towards the spool part side from the state in Figure 12(b). [Figure 13] Figure 13(a) is an exploded view showing the configuration of an electromagnetic brake unit in a third variant of a double-bearing reel, Figure 13(b) is a view showing the appearance of the electromagnetic brake unit, and Figure 13(c) is a cross-sectional view of the electromagnetic brake unit. [Figure 14]Figure 14 shows the configuration of a third variant of a double-bearing reel, where Figure 14(a) shows the state when the electromagnetic brake unit is not operating, Figure 14(b) shows the state where the magnet part has moved toward the spool part from the state in Figure 14(a), and Figure 14(c) shows the state where the magnet part has moved toward the second dial from the state in Figure 14(b). DETAILED DESCRIPTION OF THE INVENTION

[0009] A dual bearing reel according to an embodiment of the present invention will be described with reference to the accompanying drawings. The dual-bearing reel 1 according to the embodiment shown in Figure 1 is a baitcasting reel suitable for lure fishing, and has a spool 2 for winding a fishing line around it, and a braking device 3 for braking the spool 2. The braking device 3 includes an electromagnetic brake unit (magnetic brake) 4 and a friction brake unit (mechanical brake) 5.

[0010] The spool portion 2 and electromagnetic brake unit 4 are housed within a metal frame 6. A cylindrical side cup 31 with a bottom is attached to one side (the left side in FIG. 1) of the frame 6, and a handle 8 is provided on the outside of the side cup 31. A disc-shaped plate 32 is attached to the other side of the frame 6, and a side cup 33 having approximately the same shape as the side cup 31 is attached to the outside of the plate 32. A first dial (cast control dial) 7 incorporating a friction brake unit 5 and a second dial 34, which will be described later, are provided on the outside of the side cup 33. The frame 6, plate 32, and side cups 31 and 33 are collectively referred to as the housing.

[0011] In the dual-bearing reel 1 according to the embodiment, the components other than the spool portion 2, braking device 3, and first and second dials 7, 34 are configured in the same way as a typical dual-bearing reel, and therefore a description thereof will be omitted.

[0012] As shown in Figures 2(a) and 2(b), the spool section 2 comprises a spool 10 and a thin, cylindrical metal shaft 11. The spool 10 comprises a small cylindrical hub (small cylindrical section) 12a fixed to the shaft 11, a large cylindrical bobbin (large cylindrical section) 12b concentric with the hub 12a for winding the fishing line, and a plurality of spokes 12c connecting the hub 12a and the bobbin 12b.

[0013] The multiple spokes 12c are made of elongated rod-like members extending radially from the outer circumferential surface of the hub 12a toward the inner circumferential surface of the bobbin 12b and are integrally formed with the hub 12a and bobbin 12b. The spokes 12c are machined to have inclined surfaces with respect to a plane perpendicular to the rotation axis of the shaft 11, allowing them to function as propeller blades. An annular plate 12d with a smaller diameter than the bobbin 12b is integrally formed on the end faces of the hub 12a and spokes 12c facing the electromagnetic brake unit. The spokes 12c, annular plate 12d, hub 12a, and bobbin 12b are made of a nonmagnetic, conductive material, such as aluminum in this embodiment. The shape of the spokes 12c is not limited to the above-described one, as long as they function as a propeller. For example, the spokes 12c may have a twist angle, or the width of the spokes 12c may vary continuously among the hub 12a-side, middle, and bobbin 12b-side portions.

[0014] The shaft 11 is supported for rotation and axial movement by two bearings 13, 13 fixed to the frame 6 and the plate 32. One end of the shaft 11 is connected to the handle 8, and a user of the dual-bearing reel 1 can rotate the spool portion 2 by rotating the handle 8.

[0015] As shown in Figure 3, the electromagnetic brake unit 4 consists of a magnet part 14, a cylindrical retaining tube 15 that holds the magnet part 14, a spring 16 that biases the magnet part 14, and a disk-shaped base 35 that supports the retaining tube 15 and the spring 16.

[0016] The magnet portion 14 is made up of a bolt portion 17 in the shape of a bolt and a nut portion 18 in the shape of a nut into which the bolt portion 17 is screwed, and has an overall cylindrical outer shape. The bolt portion 17 has a through hole 17a formed therein, into which the shaft 11 of the spool portion 2 is inserted. A plurality of permanent magnets 19 are embedded in the axially outer surface of the head of the bolt portion 17, surrounding the through hole 17a. A plurality of protrusions 18a extending radially outward are provided on the outer peripheral surface of the nut portion 18. The magnet portion 14 is rotatably fitted onto the shaft 11 of the spool portion 2. The end of the nut portion 18 on the first dial 7 side (the lower side in Figure 3) in the axial direction has a bottomed through hole (not shown) formed in the center, into which the shaft 11 is inserted.

[0017] The retaining cylinder 15 holds the magnet part 14 and serves to convert the rotational motion of the magnet part 14 into linear motion in the axial direction. The retaining cylinder 15 has multiple slits 15a that extend obliquely relative to the central axis of the retaining cylinder 15, and protrusions 18a of the nut part 18 are inserted into the slits 15a. The multiple slits 15a are designed to be inclined at the same angle, and the direction of the inclination is set in a direction that does not interfere with the rotation of the magnet part 14. The retaining cylinder 15 is fixed to the base 35.

[0018] The spring 16 is a cylindrical coil spring and is disposed inside the retaining tube 15. The spring 16 abuts against the bottom surface of the nut portion 18 and the base 35, and biases the magnet portion 14 toward the spool portion 2 in the axial direction. 3, a through hole 35a is formed in the center of the base 35, into which the shaft 11 of the spool portion 2 is inserted. The tips of three protrusions 36a of a tilting member 36 (described later) are fixed to the surface of the base 35 opposite the retaining cylinder 15 (see FIG. 11(b)), which allows the electromagnetic brake unit 4 to move integrally with the tilting member 36 in the axial direction.

[0019] As shown in Figure 4, the first dial (rotating member) 7 consists of a bottomed cylindrical member 21 made of metal with a screw groove 21a formed on its inner surface, a spring 22, and a shaft support member 23, which together form the friction brake unit 5.

[0020] 1, the side cup 33 has a through hole 6a formed in a position facing the shaft 11 of the spool portion 2, and is integrally provided with a cylindrical portion 6b that surrounds the through hole 6a and extends to the outside of the side cup 33. A screw thread 6c that screws into the screw groove 21a of the cylindrical member 21 of the first dial 7 is formed on the outer circumferential surface of the cylindrical portion 6b, allowing the first dial 7 to be detachably attached to the side cup 33.

[0021] The shaft support member 23 consists of a circular metallic dish-shaped portion 23a against which the tip of the shaft 11 of the spool portion 2 abuts, and a cylindrical shaft-shaped portion 23b that is concentric with and integral with the dish-shaped portion 23a (see Figure 4).

[0022] The spring 22 is a conical coil spring with a smaller elastic force than the spring 16 of the magnet portion 14, and its end with a larger coil diameter is fixed to the bottom surface 21b of the cylindrical member 21. The shaft-shaped portion 23b of the shaft support member 23 is fixed to the end with a smaller coil diameter of the spring 22. The spring 22 holds the shaft support member 23 movably in the axial direction and biases the shaft support member 23 in a direction pressing it against the shaft 11 of the spool portion 2. This constantly eliminates axial rattle of the spool portion 2. Note that by using a conical coil spring for the spring 22, the larger coil diameter portion of the spring 22 comes into contact with the inner circumferential surface of the cylindrical member 21, allowing the shaft support member 23 and the cylindrical member 21 to be centered, and allowing the tip of the shaft 11 to properly abut against the dish-shaped portion 23a.

[0023] The shaft 11 of the spool portion 2 is inserted into the through-hole 17a of the bolt portion 17 so that the annular plate 12d of the spool portion 2 faces the permanent magnet 19 provided on the bolt portion 17 of the magnet portion 14. The shaft 11 passes through the center of the nut portion 18, the retaining tube 15, and the spring 16, passes through the through-hole 35a of the base 35 and the through-hole 32a of the plate 32, protrudes from the through-hole 6a of the side cup 33, and enters the first dial 7 attached to the side cup 33, where it abuts against the dish-shaped portion 23a of the shaft support member 23.

[0024] In a dual-bearing reel 1 having this configuration, when the spool portion 2 rotates, the annular plate 12d of the spool portion 2, which is a conductor, rotates within the magnetic field of the permanent magnet 19 of the magnet portion 14, generating an attractive force between the spool portion 2 and the magnet portion 14. This prevents the spool portion 2 from rotating, applying a brake (electromagnetic brake), and attracting the spool portion 2 toward the magnet portion 14 (see Figure 5(b)).

[0025] By rotating the bolt portion 17 relative to the nut portion 18 of the magnet portion 14, the axial positions of the bolt portion 17 and the permanent magnet 19 can be changed to adjust the distance between the permanent magnet 19 and the annular plate 12d, thereby adjusting the braking force of the electromagnetic brake. Specifically, the braking force can be increased by reducing the distance between the permanent magnet 19 and the annular plate 12d, and decreased by increasing the distance.

[0026] Furthermore, when the spool 2 rotates, friction between the tip of the shaft 11 of the spool 2 and the dish-shaped portion 23a of the first dial 7 applies a brake (friction brake) to the rotation of the spool 2.

[0027] Furthermore, when the first dial 7 is tightened to bring the cylindrical member 21 closer to the side cup 33, a load is applied to the spring 22, causing the dish-shaped portion 23a to abut more firmly against the tip of the shaft 11, increasing friction and making it possible to increase the braking force of the friction brake. Conversely, when the first dial 7 is loosened to move the cylindrical member 21 away from the side cup 33, the braking force of the friction brake can be reduced, making it possible to adjust the braking force of the friction brake.

[0028] As shown in FIG. 1, a cylindrical metal second dial 34 for adjusting the braking force of the electromagnetic brake is rotatably fitted to the first dial 7. A plate-shaped ring portion 34a extending radially inward is integrally formed at the end of the second dial 34 on the side cup 33 side, and a single, slender, cylindrical push rod 34b extending axially outward is integrally provided with the ring portion 34a (see FIG. 10(d)). As shown in FIG. 9(a), an arc-shaped slit 33a is formed in the side cup 33, which is concentric with the cylindrical portion 6b and penetrates the side cup 33 so as to surround approximately half of the cylindrical portion 6b. The push rod 34b of the second dial 34 is inserted into the side cup 33 through the arc-shaped slit 33a of the side cup 33.

[0029] As shown in FIG. 1, a metal tilting member 36 is disposed within the side cup 33. The tilting member 36 is made of an arc-shaped plate-like member as shown in FIG. 10(e). As shown in FIG. 10(f), the thickness of the tilting member 36 decreases from one end to the other end when viewed from the side. In other words, the surface shown in FIG. 10(g) (the surface on the right side in FIG. 1) forms an inclined surface that is inclined relative to the second dial 34. The inclined surface of the tilting member 36 has an arc-shaped groove 36b that has a substantially semicircular cross section and extends along the inclined surface. The groove 36b guides the push rod 34b of the second dial 34 described above.

[0030] As shown in Fig. 10(f), three elongated cylindrical protrusions 36a extending axially outward are integrally formed on the back surface of the tilting member 36. More specifically, the three protrusions 36a are arranged at equal intervals on the back surface of the tilting member 36 so as to face the grooves 36b on the tilting surface. As shown in Fig. 9(c), a through hole 32a is formed in the plate 32 at a position facing the magnet portion 14, and a bearing 13 for supporting the shaft 11 of the spool portion 2 is disposed in the through hole 32a. Three small circular through holes 32b are formed around the through hole 32a in the plate 32, corresponding to the three protrusions 36a of the tilting member 36.

[0031] The three protrusions 36a of the tilting member 36 are inserted into springs 37, which are cylindrical coil springs, and are further inserted into through holes 32b of the plate 32 so as to be movable in the axial direction. The tilting member 36 is biased by the springs 37 together with the electromagnetic brake unit 4 toward the first dial 7 in the axial direction (to the right in FIG. 1).

[0032] 11(a), that is, when the push rod 34b of the second dial 34 is in contact with the thin portion of the tilting member 36, rotating the second dial 34 clockwise causes the push rod 34b to move within the arc-shaped slit 33a of the side cup 33. At this time, the tip of the push rod 34b slides along the groove 36b in the tilted surface of the tilting member 36, moving the tilting member 36 axially toward the spool 2 against the biasing force of the spring 37. Then, the electromagnetic brake unit 4 moves integrally with the tilting member 36 toward the spool 2 (see FIG. 11(b)), and the permanent magnet 19 of the magnet portion 14 approaches the annular plate 12d of the spool 2, thereby increasing the braking force of the electromagnetic brake.

[0033] 11(b), that is, when the push rod 34b of the second dial 34 is in contact with the thicker portion of the tilting member 36, rotating the second dial 34 counterclockwise causes the tip of the push rod 34b to slide along the groove 36b of the tilting member 36 in the direction opposite to that described above, and the biasing force of the spring 37 causes the tilting member 36 to move axially toward the first dial 7 together with the electromagnetic brake unit 4 (see FIG. 11(a)). As a result, the permanent magnet 19 of the magnet portion 14 moves away from the annular plate 12d of the spool portion 2, thereby weakening the braking force of the electromagnetic brake. As described above, by rotating the second dial 34 and abutting the tip of the push rod 34b at different positions on the inclined surface of the inclined member 36, the axial position of the electromagnetic brake unit 4 can be changed to adjust the distance between the permanent magnet 19 and the annular plate 12d of the spool portion 2, thereby adjusting the braking force of the electromagnetic brake.

[0034] The operation of the electromagnetic brake unit 4 and friction brake unit 5 during casting in dual-bearing reel 1 will be described below. Dual-bearing reel 1 is used by winding a fishing line with a lure attached to the end around spool 2 and attaching it to a baitcasting rod via a reel seat. Figure 6 is a graph showing the relationship between the rotation speed of spool 2 and the time the lure flies when the user casts the lure by strongly swinging the rod.

[0035] As shown in FIG. 6, the rotational speed of the spool 2 reaches its maximum immediately (after several rotations) after it begins to rotate during casting. At this time, the propulsive force of the spokes 12c, which function as a propeller, causes the spool 2 to move rapidly toward the magnet 14, minimizing the distance between the annular plate 12d of the spool 2 and the permanent magnet 19 of the magnet 14 (see FIG. 5(b)). This increases and maximizes the braking force of the electromagnetic brake. Furthermore, as the spool 2 moves, the shaft 11 pushes the shaft support member 23 away against the biasing force of the spring 22 of the first dial 7, pressing the shaft-shaped portion 23b of the shaft support member 23 against the bottom surface 21b of the cylindrical member 21 (see FIG. 5(b)). This causes the tip of the shaft 11 to more strongly abut the dish-shaped portion 23a of the shaft support member 23, maximizing the braking force of the friction brake.

[0036] Backlash is most likely to occur in section A shown in Figure 6, where the rotational acceleration of the spool 2 increases rapidly, and therefore it is necessary to apply maximum braking to the spool 2. In this section A, as described above, the spool 2 can be moved quickly by the propulsive force of the spokes 12c, and maximum electromagnetic braking and maximum friction braking can be applied to the spool 2, thereby effectively preventing backlash.

[0037] When the spool portion 2 moves toward the magnet portion 14, the aforementioned mutual attractive force generated between the spool portion 2 and the magnet portion 14 causes the magnet portion 14 to rotate in the same direction as the spool portion 2. As a result, the protrusions 18a of the magnet portion 14 are guided into the slits 15a of the retaining cylinder 15, and the magnet portion 14 moves axially while rotating, specifically in the direction away from the spool portion 2 (see FIG. 5(c)). This increases the distance between the permanent magnet 19 of the magnet portion 14 and the annular plate 12d of the spool portion 2, and the braking force of the electromagnetic brake decreases accordingly. At this time, the position of the spool portion 2 remains moved toward the magnet portion 14, so the braking force of the friction brake remains at its maximum.

[0038] If the maximum electromagnetic brake and maximum friction brake are continuously applied to the spool 2, the casting distance of the lure will be shortened. For this reason, it is necessary to reduce the braking force in section B in Figure 6, where the rotation speed of the spool 2 is steadily decreasing. In this section B, the dual-bearing reel 1 can reduce the braking force of the electromagnetic brake by moving the magnet section 14 as described above, thereby effectively extending the casting distance of the lure (referred to as "Brake Control A").

[0039] In particular, the timing at which the magnet portion 14 starts to move away from the spool portion 2 is delayed from the timing at which the spool portion 2 has finished moving toward the magnet portion 14 due to the static friction force acting between the magnet portion 14 and the retaining tube 15. As a result, the electromagnetic brake and friction brake are maintained at their maximum for a certain period of time, and the braking force of the electromagnetic brake can be reduced as described above once the rotational acceleration of the spool portion 2 has ceased. In other words, backlash can be sufficiently prevented when the rotational acceleration of the spool portion 2 is high, and the electromagnetic brake can be reduced thereafter.

[0040] When the rotational speed of the spool portion 2 decreases, the mutual attractive force generated between the spool portion 2 and the magnet portion 14 weakens, and the magnet portion 14 is no longer able to rotate in the same direction as the spool portion 2, so the force of the spring 16 pushes the magnet portion 14 back toward the spool portion 2. More specifically, the force of the spring 16 causes the magnet portion 14 to move toward the spool portion 2 while rotating in the opposite direction relative to the retaining cylinder 15, and returns to its original position (see FIG. 5(d)). Note that even when the magnet portion 14 returns to its original position and the distance between the permanent magnet 19 of the magnet portion 14 and the annular plate 12d of the spool portion 2 returns to its original position, the braking force of the electromagnetic brake becomes smaller because the rotational speed of the spool portion 2 has decreased.

[0041] When the rotational speed of the spool portion 2 further decreases, the force of the spring 22 of the first dial 7 pushes the spool portion 2 back in a direction away from the magnet portion 14, returning it to its original position (see FIG. 5(a)). More specifically, the shaft-shaped portion 23b of the shaft support member 23 moves away from the bottom surface 21b of the cylindrical member 21, and the dish-shaped portion 23a pushes the shaft 11 back to its original position. This minimizes the braking forces of both the friction brake and the magnetic brake.

[0042] As shown in Figure 6, in section C where the rotation speed of the spool 2 is decreasing, it is necessary to weaken the brake to increase the casting distance of the lure. In this section C, as mentioned above, with the dual-bearing reel 1, the rotation speed of the spool 2 decreases, the magnetic brake becomes weaker, and the spool 2 returns to its original position, minimizing the braking force of the friction brake and effectively increasing the casting distance of the lure.

[0043] 6 described above shows a case where the user casts a lure by strongly swinging the rod, i.e., the rotational acceleration of spool 2 is large, causing spool 2 to move toward magnet 14, and then magnet 14 to move away from spool 2. In this case, brake control A is activated, and the braking force during rotation due to inertial force after the rotational acceleration of spool 2 has ceased can be adjusted to increase the casting distance of the lure.

[0044] In contrast, when the user casts a lure with a weak swing of the rod, backlash is less likely to occur, and the brake control is similar to that of section C in Figure 6. As shown in Figure 7, the rotational acceleration of the spool 2 peaks immediately after the spool 2 begins to rotate, as in Figure 6. However, because the initial rotational speed is low, the spool 2 simply moves toward the magnet 14, and the brake control A is not activated. The rotational speed of the spool 2 is then reduced by the electromagnetic brake and friction brake, and the spool 2 is pushed back by the force of the spring 22 of the first dial 7. This reduces the braking force of the electromagnetic brake and friction brake, effectively extending the casting distance of the lure. Thus, when a lure is cast with a weak swing of the rod, the dual-bearing reel 1 can appropriately brake the spool 2 without the magnet 14 moving.

[0045] As described above, the dual-bearing reel 1 according to this embodiment can automatically and appropriately adjust the braking force of the friction brake and electromagnetic brake at optimal timing to match the rotational movement of the spool 2 during casting, whether the user swings the rod strongly or weakly. This allows the brake to be applied strongly to the spool 2 during the first half of the cast, when the rotational acceleration of the spool 2 is high, effectively preventing backlash, and then the brake is weakened during the second half of the cast, when the rotational acceleration of the spool 2 has subsided, greatly increasing the casting distance of the lure.

[0046] Note that, when the first dial 7 is tightened to move the axial position of the cylindrical member 21 closer to the side cup 33, the braking force of the friction brake can be increased as described above. At the same time, the movable range of the shaft support member 23 and the spool portion 2 is reduced, so the range of strength of the braking force of the friction brake and the electromagnetic brake (the difference between the maximum and minimum values) can be reduced. On the other hand, when the first dial 7 is loosened to move the cylindrical member 21 away from the side cup 33, the braking force of the friction brake can be reduced while the range of strength of the braking force of the friction brake and the electromagnetic brake can be increased. In particular, because the spool portion 2 is brought closer to the magnet portion 14, the braking force of the electromagnetic brake can be maximized.

[0047] Therefore, the dual-bearing reel 1 according to this embodiment can flexibly adjust the braking force of the electromagnetic brake and the friction brake by adjusting the axial position of the permanent magnet 19 by rotating the bolt portion 17 of the magnet portion 14 relative to the nut portion 18 and / or by rotating the second dial 34, as described above, and by adjusting the axial position of the cylindrical member 21 of the first dial 7 by rotating the first dial 7. Also, by preparing and appropriately replacing multiple springs with different biasing forces as the spring 22 of the first dial 7, the dual-bearing reel 1 can be used with lures of various weights.

[0048] Alternatively, a thread may be provided on the inner peripheral surface of the retaining tube 15 on the side of the first dial 7 in the axial direction, and the base 35 may be shaped like a bolt that screws into the thread of the retaining tube 15. With this configuration, by rotating the base 35 relative to the retaining tube 15, the axial position of the permanent magnet 19 can be changed to adjust the distance between the permanent magnet 19 and the annular plate 12d, just as in the case where the bolt portion 17 is rotated relative to the nut portion 18 of the magnet portion 14, and this makes it possible to adjust the braking force of the electromagnetic brake.

[0049] As described above, this embodiment realizes a dual-bearing reel and a braking device for a dual-bearing reel that has a simple configuration, provides good control of the brake size and timing, prevents backlash, and ensures lure casting distance, and is capable of adjusting the braking force while eliminating axial rattle of the spool. Note that the braking device (spool portion 2, friction brake unit 5, and electromagnetic brake unit 4) can also be applied to dual-bearing reels with a simple configuration (such as antique reels).

[0050] As described above, the spool portion 2 in this embodiment is configured to move in a direction in which the braking force of the mechanical brake and magnetic brake becomes greater due to the propulsive force of the spoke 12c. However, such a spool portion 2 is not limited to mechanical brakes and magnetic brakes, and can also be applied to centrifugal brakes to increase the braking force.

[0051] (First Modification) The shaft 11 and first dial 7 of the dual-bearing reel 1 are not limited to the above-described configuration, and may employ the configuration of a first modified example shown in FIG. 8. Specifically, the end of the shaft 11 on the first dial 7 side is provided with a cylindrical small-diameter section 11a and a step section 11b perpendicular to the axial direction, in that order from the tip, and the tip of the small-diameter section 11a is hemispherical. Furthermore, the shaft support member 23 of the first dial 7 is eliminated, and the end of the spring 22 with a small coil diameter is provided with a ring-shaped section 22a into which the small-diameter section 11a of the shaft 11 is inserted. More specifically, the tip of the spring 22 is wound two and a half times or three times to form the ring-shaped section 22a. With this configuration, when the spool section 2 rotates, friction between the step section 11b of the shaft 11 and the ring-shaped section 22a of the spring 22 applies a friction brake to the rotation of the spool section 2. When the spool portion 2 moves toward the first dial 7, the step portion 11b pushes the ring-shaped portion 22a, contracting the spring 22, and the tip of the small diameter portion 11a abuts against the bottom surface 21b of the cylindrical member 21, and the step portion 11b abuts more strongly against the ring-shaped portion 22a, maximizing the braking force of the friction brake. In other words, the modified example of the shaft 11 and the first dial 7 can achieve the same effects as the shaft 11 and the first dial 7 described above.

[0052] (Second Modification) The spool section 2 and first dial 7 in the dual-bearing reel 1 may adopt the configuration of the second modified example shown in Figure 12(a). In detail, the shaft support member 23 and spring 22 of the first dial 7 are eliminated, and the tip of the shaft 11 of the spool section 2 abuts against the bottom surface 21b of the cylindrical member 21 of the first dial 7. Furthermore, the inclined surfaces formed by cutting the spokes 12c of the spool section 2 are eliminated, and the spokes 12c do not function as propeller blades.

[0053] With this configuration, the electromagnetic brake unit 4 can perform the operations shown in Figures 12(a) to 12(c) and described below. Note that the second dial 34, inclined member 36, etc. are not shown in Figures 12(a) to 12(c) and Figures 14(a) to 14(c) described below.

[0054] As shown in Figure 12(a), when the electromagnetic brake unit 4 is not operating (normally), the magnet part 14 is located closest to the spool part 2, i.e., the distance between the permanent magnet 19 of the magnet part 14 and the annular plate 12d, which is the magnetic force acting plate of the spool part 2, is the smallest.

[0055] In Figure 12(a), when the spool portion 2 begins to rotate due to casting, the braking force of the electromagnetic brake reaches its maximum due to the magnetic interaction between the permanent magnet 19 and the annular plate 12d, and a rotational force is applied to the magnet portion 14 in the same direction as the rotation of the spool portion 2. As a result, the magnet portion 14 moves in the axial direction while rotating, more specifically, in the direction away from the spool portion 2 (see Figure 12(b)). This increases the distance between the permanent magnet 19 and the annular plate 12d, and the braking force of the electromagnetic brake decreases.

[0056] As shown in Figure 12(b), when the magnet section 14 moves away from the spool section 2, the biasing force of the spring 16 causes the magnet section 14 to rotate in the opposite direction while moving axially, specifically, toward the spool section 2 (see Figure 12(c)). This reduces the distance between the permanent magnet 19 and the annular plate 12d, and increases the braking force of the electromagnetic brake.

[0057] While the spool portion 2 is rotating at high or medium speed due to casting, the magnet portion 14 moves axially as described above, causing the electromagnetic brake unit 4 to alternate between the state shown in Figure 12(b) and the state shown in Figure 12(c), thereby automatically and appropriately adjusting the braking force of the electromagnetic brake and effectively preventing backlash.

[0058] As the rotation speed of the spool 2 slows and the rotational force weakens, the magnetic force weakens and the magnet 14 moves closer to the spool 2. This further reduces the braking force of the electromagnetic brake, effectively increasing the casting distance of the lure. When the rotation of the spool 2 stops, the electromagnetic brake unit 4 returns to the state shown in Figure 12(a).

[0059] The second modified example of the dual-bearing reel 1 described above is effective in increasing the flight distance of lures that are easy to cast, such as lures weighing 5 g or more. In the second modified example, the axial position of the spool portion 2 remains unchanged when the electromagnetic brake unit 4 is in operation. When the first dial 7 is tightened to move the cylindrical member 21 closer to the side cup 33, the tip of the shaft 11 comes into stronger contact with the bottom surface 21b of the cylindrical member 21, increasing friction and making it possible to increase the braking force of the friction brake. Conversely, when the first dial 7 is loosened to move the cylindrical member 21 away from the side cup 33, the braking force of the friction brake can be reduced, making it possible to adjust the braking force of the friction brake. This is also true for the third modified example, which will be described later.

[0060] (Third Modification) The spool portion 2, first dial 7, and electromagnetic brake unit 4 in the dual-bearing reel 1 may adopt the configuration of the third modified example shown in Figure 14(a). Specifically, the spool portion 2 and first dial 7 have the same configuration as the second modified example. As shown in Figure 13(a), the electromagnetic brake unit 4 has a plate-shaped ring portion 15b that extends radially inward and is integrally formed at the end of the retaining tube 15 on the spool portion 2 side (upper side in Figure 13(a)).

[0061] Furthermore, the bolt portion 17 and the nut portion 18 of the magnet portion 14 are slidably fitted to the ring portion 15b of the retaining tube 15, and a spring 16 is disposed between the magnet portion 14 and the retaining tube 15 in the radial direction. More specifically, as shown in FIG. 13(c), the spring 16 is disposed so as to abut against the ring portion 15b of the retaining tube 15 and the protrusion 18a of the nut portion 18, and biases the magnet portion 14 toward the first dial 7. The inclination of the slit 15a of the retaining tube 15 is opposite to the inclination of the slit 15a of the retaining tube 15 in the second modified example. With the above configuration, the electromagnetic brake unit 4 can perform the operations shown in FIGS. 14(a) to 14(c) and described below.

[0062] As shown in Figure 14(a), when the electromagnetic brake unit 4 is not operating (normally), the magnet part 14 is located at the farthest position from the spool part 2, i.e., the distance between the permanent magnet 19 of the magnet part 14 and the circular plate 12d, which is the magnetic force acting plate of the spool part 2, is the greatest.

[0063] In Figure 14(a), when the spool portion 2 begins to rotate due to casting, the magnetic force between the permanent magnet 19 and the annular plate 12d applies a rotational force to the magnet portion 14 in the same direction as the rotation of the spool portion 2. As a result, the magnet portion 14 moves in the axial direction while rotating, more specifically, in the direction approaching the spool portion 2 (see Figure 14(b)). This reduces the distance between the permanent magnet 19 and the annular plate 12d, and the braking force of the electromagnetic brake increases.

[0064] As shown in Figure 14(b), when the magnet section 14 approaches the spool section 2, the biasing force of the spring 16 causes the magnet section 14 to rotate in the opposite direction while moving axially, more specifically, away from the spool section 2 (see Figure 14(c)). This increases the distance between the permanent magnet 19 and the annular plate 12d, reducing the braking force of the electromagnetic brake.

[0065] While the spool portion 2 is rotating at high or medium speed due to casting, the magnet portion 14 moves axially as described above, and the electromagnetic brake unit 4 alternates between the state shown in Figure 14(b) and the state shown in Figure 14(c), thereby making it possible to automatically and appropriately adjust the braking force of the electromagnetic brake, as in the second modified example described above, and effectively preventing backlash.

[0066] As the rotation speed of the spool 2 slows and the rotational force weakens, the magnetic force weakens and the magnet 14 moves away from the spool 2. This further reduces the braking force of the electromagnetic brake, effectively increasing the casting distance of the lure, just as in the second modified example. When the rotation of the spool 2 stops, the electromagnetic brake unit 4 returns to the state shown in Figure 14(a). The third modified example of the dual-bearing reel 1 described above is effective in preventing backlash with a lightweight lure, such as a lure weighing less than 5 g.

[0067] According to the dual-bearing reel 1 and its first to third modifications according to the present embodiment described above, the braking force of the friction brake and the electromagnetic brake can be adjusted by rotating the first and second dials 7, 34. In other words, the user can easily adjust the braking force of the friction brake and the electromagnetic brake from the outside without disassembling the dual-bearing reel 1.

[0068] Furthermore, in this embodiment and each of the modified examples, the second dial 34 is provided so as to be rotatable fitted onto the first dial 7 provided on the axis of the shaft 11 of the spool portion 2. Therefore, even when the present invention is applied to a conventional reel with a traditional design, specifically a so-called drum-type double-bearing reel equipped with a first dial, the aesthetic appearance of the reel can be maintained.

[0069] Furthermore, this embodiment and each of the modified examples show an example in which an electromagnetic brake unit 4 and a friction brake unit 5 are provided, the braking force of the friction brake is adjusted with the first dial 7, and the braking force of the electromagnetic brake is adjusted with the second dial 34. However, the type of brake is not limited to these, and it is also possible to realize a dual-bearing reel that is provided with, for example, a centrifugal brake unit or an electronically controlled brake unit instead of the electromagnetic brake unit 4, and that adjusts the braking force of the centrifugal brake or electronically controlled brake by changing the axial position of the centrifugal brake unit or electronically controlled brake unit with the second dial 34.

[0070] As a result of the above, it is possible to provide a dual-bearing reel in which the braking force of multiple brakes can be easily adjusted externally. [Explanation of symbols]

[0071] 1 Double bearing reel 2 Spool section 3 Braking device 4 Electromagnetic brake unit 5 Friction Brake Unit 6 frames 7 First Dial 8 Handle 10 spools 11 Shaft 11a Small diameter section 11b Step 12c spokes 14 Magnet part 15 Holding tube 16 springs 17 Bolt section 18 Nut part 19 Magnet 21 Cylindrical member 22 Spring 22a Circumferential 23 Shaft support member 31 Side cup 32 plates 33 Side cup 34 Second Dial 35 base 36 Inclined member 37 Spring

Claims

1. a spool portion for winding a fishing line; a housing that rotatably supports the spool portion; a first brake unit and a second brake unit provided in the housing for controlling rotation of the spool portion; a first dial and a second dial provided outside the housing for adjusting the braking forces of the first brake unit and the second brake unit, A double-bearing reel, wherein the second dial is cylindrical and rotatably mounted on the outside of the first dial.

2. The second dial includes a push rod extending in the axial direction of the spool portion, an arc-shaped slit is formed in the housing to guide the push rod of the second dial into the housing; a tilting member having an inclined surface inclined with respect to the second dial, and a spring that biases the tilting member toward the second dial in the axial direction, provided within the housing; the inclined member is connected to the second brake unit and is movable in the axial direction integrally with the second brake unit, a tip of the push rod of the second dial abuts against the inclined surface of the inclined member, A double-bearing reel as described in claim 1, characterized in that the tilting member and the second brake unit are moved by rotating the second dial to abut the tip of the push rod at a different position on the tilted surface, thereby changing the axial position of the second brake unit.

3. 3. The dual-bearing reel according to claim 2, wherein the second brake unit is an electromagnetic brake unit and includes a magnet portion provided with a magnet facing the spool portion.

4. 3. The dual-bearing reel according to claim 2, wherein the second brake unit is an electronically controlled brake unit.

5. the first brake unit is a friction brake unit, the first dial has a cylindrical member with a bottom attached to the housing so as to be movable in the axial direction, 3. A double-bearing reel according to claim 2, wherein the tip of the shaft of the spool portion abuts against the bottom surface of the cylindrical member.

6. the first brake unit is a friction brake unit, the first dial has a cylindrical member with a bottom attached to the housing so as to be movable in the axial direction, and a spring fixed to the bottom surface of the cylindrical member so as to be expandable and contractible in the axial direction, A double-bearing reel as described in claim 2, characterized in that the shaft of the spool portion is supported in the housing so as to be rotatable and axially movable, and is urged axially in the direction opposite the second dial by the spring.

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