JP7797300B2 - Dual-bearing reel spool braking device - Google Patents

Description

The present invention relates to a spool braking device for a dual-bearing reel.

Some dual-bearing reels have a spool braking device that uses centrifugal force to brake the rotation of the spool (see Patent Document 1). In a spool braking device, a spool and a rotating member are attached to the spool shaft. A brake shoe is attached to the rotating member so that it can swing. The brake shoe slides against the brake drum via the rotating member in conjunction with the rotation of the spool.

Japanese Patent Application Laid-Open No. 2016-202123

In conventional spool braking devices, when the spool and rotating member rotate together with the spool shaft, centrifugal force proportional to the square of the rotational speed of the rotating member acts on the brake shoe, generating friction between the brake shoe and the brake drum. In other words, the higher the rotational speed of the spool and rotating member, the greater the braking force on the spool.

For this reason, if the braking force on the spool suddenly becomes too large when the rotational speed of the spool and rotating members is high, there is a risk of a decrease in casting distance. Furthermore, if the rotational speed of the spool and rotating members decreases from a high rotational speed, the above-mentioned frictional force suddenly decreases, and the braking force on the spool becomes too small. In this case, there is a risk of backlash occurring.

The object of the present invention is to provide a spool braking device for a dual-bearing reel that can optimally apply braking force to the spool.

A dual-bearing reel spool braking device according to one aspect of the present invention uses centrifugal force to brake the spool, which rotates integrally with the spool shaft rotatably supported on the reel body.

The spool braking device comprises a brake drum and a rotating structure. The brake drum is attached to the reel body. The brake drum is arranged alongside the spool in the axial direction along which the rotational axis of the spool shaft extends. The brake drum has a tapered outer surface that narrows in diameter toward the spool.

The rotating structure is positioned axially between the spool and the brake drum. The rotating structure has a support portion, a brake shoe, and a biasing member. The support portion rotates in conjunction with the spool shaft. The brake shoe is supported by the support portion so that it can swing. The center of gravity of the brake shoe is positioned radially outward from the brake drum, away from the rotation axis. The brake shoe contacts the tapered surface of the brake drum.

The biasing member biases either the support portion or the brake drum toward the other of the support portion or the brake drum. Either the support portion or the brake drum is arranged to be axially movable relative to the other of the support portion or the brake drum.

With this spool braking device, when the rotational speed of the spool and support part increases while the brake shoe is in contact with the tapered surface of the brake drum, the force with which the brake shoe presses against the tapered surface of the brake drum increases, causing the support part and the brake drum to move away from each other. This allows the brake shoe to contact the smaller diameter side of the tapered surface, thereby reducing the braking force on the spool. In other words, this spool braking device solves the problem of the prior art, where an increase in the braking force on the spool reduces the throwing distance.

In addition, with this spool braking device, when the rotational speed of the spool and support part slows from a high speed, the biasing member brings the support part and the brake drum closer together. This causes the brake shoe to come into contact with the large diameter side of the brake drum, allowing the braking force of the spool to be restored. In other words, this spool braking device solves the problem of the prior art, where a decrease in the braking force of the spool causes backlash.

In a dual-bearing reel spool braking device according to another aspect of the present invention, it is preferable that the rotation structure further includes a cam mechanism. In this case, the cam mechanism guides the support portion, which is movable axially relative to the brake drum, in the axial direction away from the brake drum. The support portion is disposed axially between the cam mechanism and the biasing member. This configuration allows either the support portion or the brake drum to be suitably moved axially relative to the other of the support portion and the brake drum.

In a dual-bearing reel spool braking device according to another aspect of the present invention, the cam mechanism preferably includes a cam portion and a cam receiver. In this case, the cam portion includes a first main body portion that rotates integrally with the spool shaft, and a protrusion that protrudes from the first main body portion toward the support portion. The cam receiver includes a second main body portion that rotates integrally with the support portion, and a recess provided on the second main body portion that engages with the protrusion. Here, the protrusion has a pair of inclined surfaces that face each other in the circumferential direction around the rotation axis. The circumferential spacing between the pair of inclined surfaces decreases in the axial direction toward the spool.

In a dual-bearing reel spool braking device according to another aspect of the present invention, the rotating structure preferably further includes a positioning member. The positioning member is for positioning the support portion at an initial position. The support portion is movable axially relative to the brake drum. The support portion is disposed axially between the positioning member and the biasing member. This configuration allows the support portion to be suitably positioned at the initial position.

In a dual-bearing reel spool braking device according to another aspect of the present invention, the cam mechanism has a cam portion and a cam receiver. The cam portion has a first main body portion that rotates integrally with the spool shaft and a protrusion that protrudes from the first main body portion toward the support portion. The cam receiver has a second main body portion that is positioned axially opposite the first main body portion and rotates integrally with the support portion, and a recess provided in the second main body portion that engages with the protrusion. This configuration allows the cam mechanism to operate optimally.

In a dual-bearing reel spool braking device according to another aspect of the present invention, the cam mechanism includes a cam portion and a cam receiver. The cam portion includes a first main body portion including a cylindrical portion that rotates integrally with the spool shaft and a flange portion extending radially outward from the cylindrical portion, and a protrusion portion that protrudes from the flange portion toward the support portion. The cam receiver includes a second main body portion that is disposed on the outer peripheral surface of the cylindrical portion between the axial direction of the flange portion and the support portion and rotates integrally with the support portion, and a recess portion provided in the second main body portion that engages with the protrusion portion.

In this configuration, the second main body portion of the cam receiver is positioned on the outer peripheral surface of the cylindrical portion, axially between the second flange portion and the support portion. In this state, the cam receiver moves toward and away from the cam portion on the outer peripheral surface of the cylindrical portion. This allows the cam receiver to move axially stably.

In a dual-bearing reel spool braking device according to another aspect of the present invention, the cam mechanism has a cam portion and a cam receiver. The cam portion has a first main body portion that rotates integrally with the spool shaft and a protrusion that protrudes from the first main body portion toward the support portion. The cam receiver has a second main body portion that rotates integrally with the support portion, a recess provided in the second main body portion that engages with the protrusion, and a boss portion that protrudes from the second main body portion. The first main body portion has a non-circular hole that engages with the outer peripheral surface of the spool shaft so as not to rotate relative to the spool shaft, and a circular hole that is provided to communicate with the non-circular hole. The boss portion is positioned radially between the spool shaft and the circular hole.

With this configuration, when the tip of the boss is positioned in the circular hole in the cam, the cam receiver moves toward and away from the cam on the spool shaft. This configuration allows the cam receiver to move axially in a stable manner.

This invention allows the spool braking device for a dual-bearing reel to optimally apply braking force to the spool.

1 is an external perspective view of a dual-bearing reel according to an embodiment of the present invention; Cross-sectional view of a dual-bearing reel. FIG. 2 is a perspective view of the frame, spool, spool shaft, and rotating structure. FIG. FIG. FIG. 10 is an enlarged cross-sectional view of the vicinity of a rotation structure in Modification 1. FIG. 11 is an enlarged cross-sectional view of the vicinity of a rotation structure in Modification 2. FIG. 13 is a perspective view of a cam mechanism according to a third modified example. FIG. 13 is a perspective view of a cam mechanism according to a fourth modified example.

As shown in Figure 1, a dual-bearing reel 1 incorporating one embodiment of the present invention comprises a reel body 3, a spool 5, and a handle 7. As shown in Figure 2, the dual-bearing reel 1 further comprises a spool shaft 11 and a spool braking device 13.

Note that the axial direction is the direction in which the rotational axis X1 of the spool shaft 11 extends. The radial direction is the direction perpendicular to and away from the rotational axis X1 of the spool shaft 11. The circumferential direction is the direction around the rotational axis X1 of the spool shaft 11.

As shown in FIG. 2, the reel body 3 has a frame 31, a first side cover 33, and a second side cover 35. The frame 31 has a first side plate 31a, a second side plate 31b, and multiple connecting portions 31c.

The first side plate 31a and the second side plate 31b are arranged at an axial distance from each other. The first side plate 31a and the second side plate 31b are connected to each other via multiple connecting portions 31c. The first side plate 31a, the second side plate 31b, and the multiple connecting portions 31c are integrally formed.

The first side cover 33 is attached to the frame 31. The first side cover 33 covers the first side plate 31a. For example, the first side cover 33 covers the first side plate 31a on the side opposite the handle 7. The first side cover 33 has a cylindrical shaft support portion 34.

The shaft support portion 34 is positioned radially outward of the spool shaft 11. The shaft support portion 34 rotatably supports the spool shaft 11 via a bearing 37. An operating member 61 (described later) is positioned between the first side cover 33 and the first side plate 31a to axially move the brake drum 51 (described later) of the spool braking device 13.

The second side cover 35 is attached to the frame 31. The second side cover 35 covers the second side plate 31b. For example, the second side cover 35 covers the second side plate 31b between the handle 7 (see Figure 1) and the second side plate 31b. A rotation transmission mechanism 10 for transmitting the rotation of the handle 7 to the spool 5 is disposed between the second side cover 35 and the second side plate 31b.

The spool 5 is rotatably supported on the reel body 3. For example, the spool 5 is rotatably supported on the reel body 3 via the spool shaft 11. The spool 5 has a bobbin trunk 5a, a boss 5b, and an annular wall 5c. Fishing line is wound around the bobbin trunk 5a. The boss 5b is attached to the spool shaft 11 so as to rotate integrally with the spool shaft 11. The annular wall 5c connects the bobbin trunk 5a and the boss 5b. For example, the annular wall 5c is formed integrally with the bobbin trunk 5a and the boss 5b.

As shown in Figure 1, the handle 7 is rotatably attached to the reel body 3. For example, the handle 7 is rotatably supported on the reel body 3 via the drive shaft 10a shown in Figure 2.

The rotation transmission mechanism 10 shown in Figure 2 is a mechanism that transmits the rotation of the handle 7 to the spool shaft 11. The rotation transmission mechanism 10 is disposed between the second side cover 35 and the second side plate 31b. The rotation transmission mechanism 10 has a drive shaft 10a that rotates integrally with the handle 7, a drive gear 10b that rotates integrally with the drive shaft 10a, and a pinion gear 10c that meshes with the drive gear 10b.

When the handle 7 rotates, the drive shaft 10a, drive gear 10b, and pinion gear 10c rotate. The spool shaft 11 is inserted into the inner periphery of the pinion gear 10c. Rotation from the pinion gear 10c to the spool shaft 11 is transmitted via a clutch mechanism (not shown).

As shown in Figure 2, the spool shaft 11 is rotatably supported on the reel body 3. For example, the spool shaft 11 is rotatably supported on the shaft support portion 34 of the first side cover 33 and the second side plate 31b via bearings 37 and 39. A spool 5 is attached to the spool shaft 11.

The spool braking device 13 uses centrifugal force to brake the spool 5, which rotates integrally with the spool shaft 11. As shown in Figure 2, the spool braking device 13 includes a brake drum 51 and a rotating structure 53.

The brake drum 51 is positioned axially alongside the spool 5. The brake drum 51 is positioned radially outward of the shaft support portion 34 of the first side cover 33. The brake drum 51 is positioned radially inward of the brake shoe 67 (described below). The brake drum 51 is provided on the reel body 3. For example, the brake drum 51 is attached to the shaft support portion 34 of the first side cover 33 via a movement mechanism 55.

As shown in Figures 3 and 4, the brake drum 51 has a drum main body 57 and a tapered surface 58. The drum main body 57 is formed in a cylindrical shape. The drum main body 57 is disposed on the outer peripheral surface of the shaft support portion 34. The tapered surface 58 is provided at one end of the drum main body 57. For example, the tapered surface 58 is provided on the outer peripheral surface of one end of the drum main body 57. The tapered surface 58 tapers in diameter toward the spool 5. In other words, the outer diameter of the tapered surface 58 becomes smaller as it approaches the spool 5.

As shown in FIG. 4, the brake drum 51 is configured to be movable in the axial direction by a movement mechanism 55. The movement mechanism 55 is attached to the first side cover 33. The movement mechanism 55 is disposed between the first side cover 33 and the first side plate 31a. The movement mechanism 55 has an operating member 61 and a drum cam 63.

The operating member 61 is operated to move the brake drum 51 in the axial direction. The operating member 61 is rotatably attached to the reel body 3, for example, to the shaft support portion 34 of the first side cover 33. The operating member 61 is formed in an annular shape. The operating member 61 is positioned radially outward from the brake drum 51. The operating member 61 is positioned axially by a cover member 62 attached to the first side cover 33. The operating member 61 engages with the brake drum 51 and drum cam 63.

For example, as shown in Figures 3 and 4, a groove 51a extending in the axial direction is formed on the outer peripheral surface of the brake drum 51. A first protrusion 61a protruding radially inward is formed on the inner peripheral surface of the operating member 61. The first protrusion 61a engages with the groove 51a of the brake drum 51. As a result, the operating member 61 and brake drum 51 rotate together, and the brake drum 51 moves axially relative to the operating member 61.

As shown in Figure 4, the drum cam 63 moves the brake drum 51 in the axial direction. The drum cam 63 is disposed on the outer peripheral surface of the shaft support portion 34. For example, the drum cam 63 is disposed radially between the shaft support portion 34 and the brake drum 51. The drum cam 63 engages with the brake drum 51 and moves the brake drum 51 in the axial direction.

For example, as shown in FIG. 3, a second protrusion 51b that protrudes radially inward is formed on the inner peripheral surface of the brake drum 51. As shown in FIG. 4, a spiral groove 63a extending circumferentially and axially is formed on the outer peripheral surface of the drum cam 63. The second protrusion 51b engages with the spiral groove 63a. In this state, when the operating member 61 and the brake drum 51 rotate integrally, the second protrusion 51b moves along the spiral groove 63a. As a result, the brake drum 51 moves axially while rotating circumferentially.

As shown in FIG. 2, the rotating structure 53 is disposed axially between the spool 5 and the brake drum 51. The rotating structure 53 rotates in conjunction with the spool shaft 11. As shown in FIG. 3, the rotating structure 53 has a shoe support portion 65, a plurality of (e.g., four) brake shoes 67, and a coil spring 69 (an example of a biasing member). The rotating structure 53 also has a retaining ring 71 (an example of a positioning member). The rotating structure 53 also has a cam mechanism 73.

The shoe support portion 65 supports the brake shoe 67 so that it can swing. The shoe support portion 65 rotates in conjunction with the spool shaft 11. For example, the shoe support portion 65 rotates with the spool shaft 11 via a cam mechanism 73. The shoe support portion 65 is formed in a disc shape. For example, the shoe support portion 65 is formed in a bowl shape.

As shown in FIG. 4, the shoe support portion 65 is disposed axially between the retaining ring 71 and the coil spring 69. For example, the shoe support portion 65 is disposed axially between the cam mechanism 73 and the coil spring 69. In more detail, the shoe support portion 65 is disposed axially between the first flange portion 77a2 (described below) of the cam receiver 77 and the coil spring 69.

The shoe support portion 65 is positioned radially outward from the spool shaft 11. The shoe support portion 65 is configured to be movable in the axial direction relative to the brake drum 51. For example, the shoe support portion 65 moves axially relative to the brake drum 51 together with the cam receiver 77. The shoe support portion 65 is attached to the first cylindrical portion 77a1 (described below) of the cam receiver 77 so as to rotate integrally with the cam receiver 77. The shoe support portion 65 and the cam receiver 77 rotate with the spool shaft 11 via the cam portion 75 (described below) of the cam mechanism 73.

As shown in FIG. 4, the multiple brake shoes 67 are configured to be able to contact the brake drum 51. The multiple brake shoes 67 are supported to be able to swing on the shoe support portion 65. For example, each brake shoe 67 is supported to be able to swing on the outer periphery of the shoe support portion 65 via a swing shaft 68. The brake shoes 67 are arranged at intervals from each other in the circumferential direction.

The center of gravity G of each brake shoe 67 is located radially outside the brake drum 51. For example, when the shoe support portion 65 rotates, centrifugal force acts on the center of gravity G of each brake shoe 67, causing each brake shoe 67 to swing around the swing axis 68. As a result, each brake shoe 67 comes into contact with the tapered surface 58 of the brake drum 51.

As shown in FIG. 4, the coil spring 69 biases the shoe support portion 65 toward the brake drum 51. The coil spring 69 is positioned in a compressed state between the spool 5 and the shoe support portion 65 in the axial direction. For example, one end of the coil spring 69 is positioned radially outside the boss portion 5b of the spool 5 and abuts against the annular wall portion 5c of the spool 5. The other end of the coil spring 69 abuts against the shoe support portion 65.

The retaining ring 71 is used to position the shoe support portion 65 in its initial position. The retaining ring 71 is C-shaped. The retaining ring 71 is attached to the spool shaft 11. For example, the retaining ring 71 is attached to the annular groove 11a of the spool shaft 11 (see Figure 3).

The cam mechanism 73 shown in Figures 3 and 4 guides the shoe support portion 65 in the axial direction away from the brake drum 51. The cam mechanism 73 has a cam portion 75 and a cam receiver 77. As shown in Figure 4, the cam portion 75 is positioned axially between the retaining ring 71 and the cam receiver 77. The cam portion 75 abuts against the retaining ring 71. The cam portion 75 engages with the cam receiver 77.

As shown in FIG. 5, the cam portion 75 has a first main body portion 75a and multiple (e.g., two) protrusions 75b. The first main body portion 75a is attached to the spool shaft 11 so as to rotate integrally with the spool shaft 11. For example, the first main body portion 75a is formed in a circular plate shape. The first main body portion 75a is attached to the outer surface of the spool shaft 11 by non-circular engagement.

This allows the first body portion 75a to rotate integrally with the spool shaft 11. The first body portion 75a is positioned between the stepped wall 11b of the spool shaft 11 (see Figure 3) and the retaining ring 71. This restricts axial movement of the first body portion 75a relative to the spool shaft 11.

The multiple protrusions 75b are formed integrally with the first main body portion 75a. The multiple protrusions 75b protrude from the first main body portion 75a toward the shoe support portion 65. The multiple protrusions 75b are arranged at intervals from one another in the circumferential direction. Each protrusion 75b has a pair of inclined surfaces 75b1 that face each other in the circumferential direction. The circumferential spacing between the pair of inclined surfaces 75b1 decreases toward the spool 5.

As shown in FIG. 5, the cam receiver 77 has a second main body portion 77a and multiple (e.g., two) recesses 77b. The second main body portion 77a is attached to the spool shaft 11 so as to rotate integrally with the shoe support portion 65. The second main body portion 77a is positioned opposite the first main body portion 75a in the axial direction.

For example, the second main body portion 77a has a first cylindrical portion 77a1 and a first flange portion 77a2. The first cylindrical portion 77a1 is disposed on the outer peripheral surface of the spool shaft 11. The first cylindrical portion 77a1 moves axially relative to the spool shaft 11. The shoe support portion 65 is fixed to the outer peripheral surface of the first cylindrical portion 77a1, and the first cylindrical portion 77a1 rotates integrally with the shoe support portion 65.

The first flange portion 77a2 extends radially outward from the first cylindrical portion 77a1 and is formed in an annular shape. As shown in FIG. 4, the first flange portion 77a2 is positioned axially between the shoe support portion 65 and the cam portion 75 (first main body portion 75a).

As shown in FIG. 5, multiple recesses 77b are provided in the second main body portion 77a. For example, multiple recesses 77b are provided in the first flange portion 77a2. The multiple recesses 77b are arranged at intervals from one another in the circumferential direction.

The multiple recesses 77b are positioned facing the multiple protrusions 75b of the cam portion 75, respectively. The multiple recesses 77b engage with the multiple protrusions 75b of the cam portion 75, respectively. The wall of each recess 77b is formed to fit along the inclined surface 75b1 of each protrusion 75b. The wall of each recess 77b is slidable along the inclined surface 75b1 of the protrusion 75b.

In the spool braking device 13 configured as described above, the spool 5 and spool shaft 11 rotate with the multiple recesses 77b of the cam receiver 77 engaged with the multiple protrusions 75b of the cam portion 75. In this state, the rotation of the spool shaft 11 is transmitted from the cam portion 75 to the cam receiver 77, and from the cam receiver 77 to the shoe support portion 65.

This causes the spool shaft 11, cam mechanism 73 (cam portion 75 and cam receiver 77), and shoe support portion 65 to rotate. In this state, the brake shoe 67 comes into contact with the tapered surface 58 of the brake drum 51, and the brake shoe 67 slides against the tapered surface 58 of the brake drum 51.

Here, if the rotational speed of the spool 5 (the rotational speed of the shoe support portion 65) increases and the force with which the brake shoe 67 presses against the tapered surface 58 of the brake drum 51 increases, the reaction force acting on the brake shoe 67 from the tapered surface 58 of the brake drum 51 causes the shoe support portion 65 to move axially away from the brake drum 51.

As a result, the brake shoe 67 comes into contact with the smaller diameter side of the tapered surface 58, reducing the braking force on the spool 5. In other words, the spool braking device 13 can optimally apply braking force to the spool 5 so as not to reduce casting distance, even if the rotational speed of the spool 5 increases.

Furthermore, when the rotational speed of the spool 5 (the rotational speed of the shoe support portion 65) decreases from a high speed, the reaction force acting on the brake shoe 67 from the tapered surface 58 of the brake drum 51 decreases, and the shoe support portion 65 is pressed by the coil spring 69 and moves closer to the brake drum 51.

As a result, the brake shoe 67 comes into contact with the large diameter side of the brake drum 51, allowing the braking force of the spool 5 to be restored. In other words, the spool braking device 13 can appropriately apply braking force to the spool 5 so as not to generate backlash, even if the rotational speed of the spool 5 slows down from a high speed.

(Modification)
The above embodiment can be modified as in the following modification example 1.

Modification 1
In the above embodiment, an example has been shown in which the shoe support portion 65 moves in the axial direction relative to the brake drum 51. Instead of this configuration, the brake drum 51 may be configured to move in the axial direction relative to the shoe support portion 65, as shown in FIG.

In this case, the shoe support portion 65 is press-fitted onto the spool shaft 11 and abuts against the annular protrusion 11c of the spool shaft 11. This prevents the shoe support portion 65 from moving axially or rotating relative to the spool shaft 11. The coil spring 169 (an example of a biasing member) is positioned axially between the brake drum 51 and the first side cover 33.

For example, a stepped portion 57a is formed on the other end of the drum body 57 of the brake drum 51. One end of the coil spring 169 is disposed on the outer peripheral surface of the stepped portion 57a. One end of the coil spring 169 abuts against the wall of the stepped portion 57a. The other end of the coil spring 169 is disposed radially outside the shaft support portion 34 of the first side cover 33, for example, outside the pressing cam 163. The other end of the coil spring 169 abuts against the pressing member 165. An O-ring 170 is disposed at the tip of the shaft support portion 34 of the first side cover 33 to prevent the brake drum 51 from slipping out of the shaft support portion 34 of the first side cover 33.

In this case, by operating the operating member 61, the pressing member 165 is moved axially by the pressing cam 163. This changes the strength of the pressing force with which the pressing member 165 presses the coil spring 169. Note that the movement of the pressing member 165 is the same as the movement of the drum cam 63 of the movement mechanism 55 in the previous embodiment.

With this configuration, when the rotational speed of the spool 5 (the rotational speed of the shoe support portion 65) increases, the brake drum 51 moves away from the shoe support portion 65, allowing the brake shoe 67 to contact the small diameter side of the tapered surface 58. This allows the braking force to be applied appropriately to the spool 5 so as not to reduce the casting distance, even if the rotational speed of the spool 5 increases.

Furthermore, when the rotational speed of the spool 5 (the rotational speed of the shoe support portion 65) decreases from a high speed, the brake drum 51 is pressed by the coil spring 169 and moves closer to the shoe support portion 65, allowing the brake shoe 67 to come into contact with the large diameter side of the brake drum 51. As a result, even if the rotational speed of the spool 5 decreases from a high speed, braking force can be applied appropriately to the spool 5 to prevent backlash from occurring.

Modification 2
The cam mechanism 73 of the above embodiment may be configured as follows. As shown in Fig. 7 , the cam mechanism 173 has a cam portion 175 and a cam receiver 177. The cam portion 175 has a cylindrical first main body portion 175a and a plurality of (e.g., two) protrusions 75b (see Fig. 5 ) provided on the outer periphery of the cylindrical first main body portion 175a. The first main body portion 175a has a second cylindrical portion 175a1 (an example of a cylindrical portion) and a second flange portion 175a2 (an example of a flange portion).

The second cylindrical portion 175a1 is formed in a cylindrical shape. The inner surface of the second cylindrical portion 175a1 engages with the outer surface of the spool shaft 11 through a non-circular engagement. This allows the second cylindrical portion 175a1 to rotate integrally with the spool shaft 11. The second cylindrical portion 175a1 is positioned between the stepped wall 111b of the spool shaft 11 and the retaining ring 71. This restricts axial movement of the second cylindrical portion 175a1 relative to the spool shaft 11.

The second flange 175a2 extends radially outward from the second cylindrical portion 175a1. The second flange 175a2 is formed integrally with the second cylindrical portion 175a1. The second flange 175a2 is formed in an annular shape. The second flange 175a2 has multiple protrusions 75b (see Figure 5). The multiple protrusions 75b protrude axially from the second flange 175a2.

The cam receiver 177 has a second main body portion 177a and multiple (e.g., two) recesses 77b (see Figure 5). The second main body portion 177a is attached to the shoe support portion 65 so as to rotate integrally with the shoe support portion 65. The second main body portion 177a may be formed integrally with the shoe support portion 65.

The second main body portion 177a is formed in a cylindrical shape. The second main body portion 177a is arranged on the outer peripheral surface of the second cylindrical portion 175a1, axially between the second flange portion 175a2 and the shoe support portion 65. The second main body portion 177a rotates relative to the second cylindrical portion 175a1. The second main body portion 177a is provided with multiple recesses 77b (see Figure 5). The multiple recesses 77b respectively engage with the multiple protrusions 75b.

In this configuration, the cam receiver 177 (second main body portion 177a) is positioned on the outer peripheral surface of the second cylindrical portion 175a1, axially between the second flange portion 175a2 of the cam portion 175 and the shoe support portion 65. In this state, the cam receiver 177 moves toward and away from the cam portion 175 on the outer peripheral surface of the second cylindrical portion 175a1. This allows the cam receiver 177 to move axially in a stable manner.

Modification 3
The cam mechanism 73 of the above embodiment may be configured as follows. As shown in Fig. 8, the cam mechanism 273 has a cam portion 275 and a cam receiver 277. The cam portion 275 has a cylindrical first main body portion 275a and a plurality of (e.g., two) protrusions 75b provided on the outer periphery of the cylindrical first main body portion 275a. The first main body portion 275a rotates integrally with the spool shaft 11, and axial movement of the first main body portion 275a relative to the spool shaft 11 is restricted.

The first main body portion 275a has a non-circular hole 275a1 and a circular hole 275a2. The non-circular hole 275a1 engages with the outer peripheral surface of the spool shaft 11 so as to be unable to rotate relative to the spool shaft 11. This allows the first main body portion 275a to rotate integrally with the spool shaft 11. In other words, the cam portion 275 rotates integrally with the spool shaft 11.

The circular hole 275a2 is provided to communicate with the non-circular hole 275a1. The boss portion 77c (described below) of the cam receiver 277 is disposed in the circular hole 275a2. The first main body portion 275a is provided with multiple protrusions 75b. The multiple protrusions 75b protrude axially from the first main body portion 275a.

The cam receiver 277 has a second main body portion 77a, multiple (e.g., two) recesses 77b, and a boss portion 77c. The configuration of the second main body portion 77a and the multiple recesses 77b is the same as that in the previous embodiment. The same configuration as that in the previous embodiment follows the explanation for the previous embodiment.

The boss portion 77c protrudes from the second main body portion 77a. For example, the boss portion 77c extends axially from the first cylindrical portion 77a1. The boss portion 77c and the first cylindrical portion 77a1 are disposed on the outer peripheral surface of the spool shaft 11. The boss portion 77c and the first cylindrical portion 77a1 rotate relative to the spool shaft 11 and move axially relative to the spool shaft 11.

The boss portion 77c is positioned in the circular hole 275a2 of the cam portion 275. For example, when the tip of the boss portion 77c is positioned in the circular hole 275a2, the tip of the boss portion 77c is positioned radially between the inner surface of the circular hole 275a2 and the outer surface of the spool shaft 11.

In this configuration, with the tip of the boss portion 77c of the cam receiver 277 positioned in the circular hole 275a2 of the cam portion 275, the cam receiver 277 moves toward and away from the cam portion 275 on the spool shaft 11. This configuration allows the cam receiver 277 to move axially in a stable manner.

Modification 4
The cam mechanism 73 of the above embodiment may be configured as follows. As shown in Fig. 9, the cam mechanism 373 has a cam portion 275 and a cam receiving portion 377. The configuration of the cam portion 275 is the same as that of Modification Example 3. The same configuration as that of Modification Example 3 follows the description of Modification Example 3.

The cam receiver 377 has a second main body portion 377a, multiple (e.g., two) recesses 77b, and a boss portion 77c. The second main body portion 377a is formed in a cylindrical shape. The second main body portion 377a is disposed on the outer peripheral surface of the spool shaft 11. The shoe support portion 65 shown in Figures 3 and 4 is attached to the outer peripheral surface of the second main body portion 377a. The shoe support portion 65 rotates integrally with the second main body portion 377a.

Multiple recesses 77b are provided on the outer periphery of the second main body portion 377a. The boss portion 77c protrudes from the second main body portion 377a. The boss portion 77c is disposed on the outer periphery of the spool shaft 11. The second main body portion 377a and the boss portion 77c rotate relative to the spool shaft 11 and move axially relative to the spool shaft 11.

In this configuration, as with Variation 3, with the tip of the boss portion 77c of the cam receiver 377 positioned in the circular hole 275a2 of the cam portion 275, the cam receiver 377 moves toward and away from the cam portion 275 on the spool shaft 11. This configuration allows the cam receiver 377 to move axially in a stable manner.

1 Dual-bearing reel 3 Reel body 5 Spool 11 Spool shaft 13 Spool braking device 51 Brake drum 53 Rotation structure 57 Drum body 58 Tapered surface 65 Shoe support portion 67 Brake shoe 69, 169 Coil spring 71 Retaining ring 73 Cam mechanism 75, 175, 275 Cam portion 75a, 175a, 275a First body portion 75b Protrusion 75b1 Inclined surface 77, 177, 277, 377 Cam receiving portion 77a, 177a, 277a, 377a Second body portion 77b Recess 77c Boss portion 79 Positioning member 79b Locking portion 175a1 Second cylindrical portion 175a2 Second flange portion 275a1 Non-circular hole 275a2 Circular hole G Center of gravity X1 of brake shoe Rotation axis

Claims (7)

A dual-bearing reel spool braking device that uses centrifugal force to brake a spool that rotates integrally with a spool shaft rotatably supported on a reel body,
a brake drum provided on the reel body, arranged alongside the spool in an axial direction along which the rotational axis of the spool shaft extends, the brake drum having a tapered surface on its outer circumferential surface that reduces in diameter toward the spool;
a rotating structure disposed between the spool and the brake drum in the axial direction;
Equipped with
the rotation structure includes a support portion that rotates in conjunction with the spool shaft, a brake shoe that is swingably supported by the support portion, that has a center of gravity disposed outside the brake drum in a radial direction away from the rotation axis center, and that contacts the tapered surface of the brake drum, and a biasing member that biases either the support portion or the brake drum toward the other of the support portion or the brake drum,
the one of the support portion and the brake drum is arranged to be movable in the axial direction relative to the other of the support portion and the brake drum.
A spool braking device for dual-bearing reels.
The rotation structure further includes a cam mechanism that guides the support portion, which is movable in the axial direction relative to the brake drum, in the axial direction away from the brake drum,
the support portion is disposed between the cam mechanism and the biasing member in the axial direction.
2. A dual-bearing reel spool braking device according to claim 1.
The cam mechanism
a cam portion having a first main body portion that rotates integrally with the spool shaft and a protrusion that protrudes from the first main body portion toward the support portion;
a cam receiving portion including a second main body portion that rotates integrally with the support portion and a recess that is provided in the second main body portion and engages with the protrusion;
and
the protrusion has a pair of inclined surfaces facing each other in a circumferential direction around the rotation axis,
a circumferential distance between the pair of inclined surfaces that decreases in the axial direction toward the spool;
3. A dual-bearing reel spool braking device according to claim 2.
The rotating structure further includes a positioning member for positioning the support portion, which is axially movable relative to the brake drum, at an initial position,
The support portion is disposed between the positioning member and the biasing member in the axial direction.
The dual-bearing reel spool braking device according to any one of claims 1 to 3.
The cam mechanism
a cam portion having a first main body portion that rotates integrally with the spool shaft and a protrusion that protrudes from the first main body portion toward the support portion;
a second body portion disposed opposite the first body portion in the axial direction and rotating integrally with the support portion; and a cam receiving portion having a recess provided on the second body portion and engaging with the protrusion,
3. A dual-bearing reel spool braking device according to claim 2.
The cam mechanism
a cam portion having a first main body portion including a cylindrical portion that rotates integrally with the spool shaft and a flange portion that extends radially outward from the cylindrical portion, and a protrusion that protrudes from the flange portion toward the support portion;
a second main body portion disposed on the outer peripheral surface of the cylindrical portion between the flange portion and the support portion in the axial direction and rotating integrally with the support portion; and a cam receiving portion having a recess provided on the second main body portion and engaging with the protrusion,
3. A dual-bearing reel spool braking device according to claim 2.
The cam mechanism
a cam portion having a first main body portion that rotates integrally with the spool shaft and a protrusion that protrudes from the first main body portion toward the support portion;
a cam receiving portion including a second main body portion that rotates integrally with the support portion, a recess that is provided on the second main body portion and engages with the protrusion, and a boss portion that protrudes from the second main body portion;
and
the first main body portion has a non-circular hole that engages with an outer circumferential surface of the spool shaft so as to be non-rotatable relative to the spool shaft, and a circular hole that is provided so as to communicate with the non-circular hole,
the boss portion is disposed between the spool shaft and the circular hole in the radial direction.
3. A dual-bearing reel spool braking device according to claim 2.