JP4324268B2 - Double-bearing reel braking device - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a braking device, and more particularly to a dual bearing that is provided in the middle of a rotation transmission mechanism that transmits rotation from a handle rotatably mounted on a reel body of a dual-bearing reel to a spool, and brakes rotation in a line-feeding direction. The present invention relates to a reel braking device.
[0002]
[Prior art]
As a kind of double-bearing reel, a big fishing reel called a trolling reel is known. The trolling reel includes a spool around which fishing line is wound around an outer periphery, a spool shaft that supports the spool, and a reel body that supports the spool shaft at the center thereof. The reel body is provided with a handle shaft that is disposed so as to protrude to the outside in parallel to the spool shaft and has a handle fixed to the tip. In addition, a rotation transmission mechanism for transmitting rotation from the handle shaft to the spool is provided between the handle shaft and the spool, and a lever drag for braking the rotation of the spool in the yarn unwinding direction is provided in the middle of the rotation transmission mechanism. A mechanism is provided.
[0003]
As a lever drag mechanism mounted on a trolling reel, a double drag type lever drag mechanism capable of obtaining a strong drag force is known. The lever drag mechanism is disposed to face one end surface of the spool opposite to the handle mounting side. The lever drag mechanism includes a brake disk member that is non-rotatably mounted on one end face of the spool, and first and second disk members that are disposed to face each other with a gap between the brake disk members, And a moving means for reciprocally moving the spool and the second disk member in the spool axial direction so that the brake disk member can be held between the first and second disk members.
[0004]
The brake disc member corresponds to a disc of a vehicle disc brake, and both disc members correspond to calipers. The brake disc member is mounted on the spool so as to be movable a predetermined distance in the spool axial direction. The first disk member is mounted on the spool shaft in a non-rotatable manner and cannot be rotated in the yarn feeding direction with respect to the reel body. Further, the first disk member is immovable in the axial direction of the spool shaft. The second disk member is mounted on the spool shaft so as not to rotate and is movable in the axial direction, and rotates in conjunction with the first disk member.
[0005]
The moving means includes a braking operation lever that is swingably mounted around the spool shaft, and a moving mechanism that converts the swinging of the braking operation lever into a reciprocating movement in the spool shaft direction. The moving mechanism includes a cam mechanism that moves the spool and the second disk member in one of the axial directions via members such as a bearing and a pinion gear arranged around the spool shaft in response to the swing of the brake operation lever. And a return spring that moves the spool pressed by the cam mechanism and the second disk member to the other side in the axial direction.
[0006]
In the double drag type drag mechanism having such a configuration, when the brake operation lever is swung in one direction, the spool and the second disk member move in one of the axial directions in accordance with the swing, and the brake disk member together with the spool. When the two disc members come into contact with the brake disc member, the spool is braked with a drag force corresponding to the pressure contact force. Further, when the brake operation lever is swung in the other direction, the spool and the second disk member are urged by the return spring according to the swing, and gradually move to the other in the axial direction. When separated, the spool can freely rotate. The drag force at this time can be adjusted by adjusting the rocking position of the brake operation lever to change the pressure contact force between both the disk members and the brake disk member.
[0007]
[Problems to be solved by the invention]
In the conventional drag mechanism, for example, when attempting to freely rotate the spool from the braking state to the braking release state in order to put in a device, the timing at which both disk members separate from the braking disk member tends to vary. This is presumably because the axial behavior of the brake disk member is not stable because the brake disk member is mounted on the spool so as to be movable in the axial direction. When the separation timing varies in this way, the state where the brake disk member remains in contact with any one of the disk members is maintained, the brake release state cannot be secured, and the spool cannot be freely rotated.
[0008]
An object of the present invention is to ensure a brake release state in a double drag type lever drag mechanism.
[0009]
[Means for Solving the Problems]
A brake device for a dual-bearing reel according to a first aspect of the present invention is provided in the middle of a rotation transmission mechanism for transmitting rotation from a handle rotatably mounted on a reel main body of the dual-bearing reel to the spool, and the rotation of the spool in the yarn unwinding direction. Is provided with a braking disk member, a first disk member, a second disk member, a first urging member, and a moving means. The brake disc member is a member that is mounted at one end of the spool so as not to rotate with a gap and to be movable a predetermined distance in the axial direction of the spool. The rotation of the first disk member is transmitted from the handle, and is disposed opposite to the surface of the brake disk member opposite to the spool, and is prohibited from rotating in the yarn unwinding direction with respect to the reel body and at least of the axial direction. It is a member that cannot move in a direction away from the brake disk member. The second disk member is disposed to face the surface of the brake disk member on the spool side, and rotates in conjunction with the first disk member and is movable in the axial direction so as to be in contact with and away from the first disk member. It is a member. The first biasing member is a member that biases the braking disk member in a direction away from the second disk member. The moving means is means for reciprocally moving the spool and the second disk member in the axial direction so that the brake disk member can be held between the first and second disk members. The first and second disk members are non-rotatably mounted on a spool shaft that passes through the center of the spool and rotatably supports the spool. The moving means presses the spool and the second disk member in accordance with the movement of the braking operation member to the maximum braking position, the braking operation member provided on the reel body so as to be movable between the braking release position and the maximum braking position. And a pressing means for moving in one axial direction approaching the first disk member, and the spool and the second disk member in response to the movement of the braking operation member to the braking release position by urging the second disk member. A second urging member for moving in the other axial direction. When the brake operation member is moved to the brake release position and the second disk member is moved to the maximum in the other axial direction, the gap between the first disk member and the brake disk member is the second disk member and the brake disk. It is larger than the gap with the member.
[0010]
In this brake device, when the spool and the second disk member are moved in the direction approaching the first disk member by the moving means, the brake disk member urged in the direction away from the second disk member by the first urging member. Moves together with the spool toward the first disk member which cannot move in the direction away from the brake disk and contacts. When the brake disk member comes into contact with the first disk member, only the spool and the second disk member move and the distance from the brake disk member becomes small. When the second disk member comes into contact with the brake disk member by further moving, the brake disk member is sandwiched between the two disk members. As a result, since the rotation of the both disk members in the thread unwinding direction is prohibited, the rotation of the brake disk member in the thread unwinding direction is braked, and the spool on which the brake disk member is mounted non-rotatably is braked. When the second disk member is further moved, the pressure contact force of the both disk members against the brake disk member is increased and the braking force (drag force) is further increased.
[0011]
When the spool and the second disk member are moved in the reverse direction by the moving means from the braking state, the pressure contact force of both the disk members gradually decreases and the drag force gradually decreases, and the second disk member separates from the braking disk member. . At this time, since the brake disk member is urged by the first urging member in a direction away from the second disk member, the brake disk member remains in contact with the first disk member until the spool moves a predetermined distance. For this reason, in this state, a slight drag force acts on the spool via the brake disk member. When the spool moves a predetermined distance, the brake disk member is separated from the second disk member to be in a brake release state, and the spool can freely rotate.
[0012]
Here, the braking disk member is urged by the first urging member in a direction away from the second disk member, and the braking disk member is mounted on the spool so as to be movable by a predetermined distance. Is stable and reliably separated from the second disk member, and the timing at which the first disk member is separated from the brake disk member to enter the brake release state is the time when the spool has moved a predetermined distance, and the timing is constant. For this reason, it can change to a braking release state from a braking state reliably, and can ensure a braking release state reliably.
[0013]
Further, since the first disk member and the second disk member are non-rotatably mounted on the spool shaft, it is possible to easily realize a configuration in which both disk members are rotated in conjunction with each other.
[0014]
Furthermore, since the pressing means only needs to press the spool and the second disk, the configuration is simplified. If a cam mechanism or the like is used, a relatively large distance can be pressed in the axial direction even if the amount of movement of the braking operation member is small.
[0015]
Furthermore, when braking is released, the distance after the braking disk member is separated from the first disk member can be increased, and the braking released state can be ensured in a wide range. During braking, the first disk member contacts the brake disk member until the second disk member contacts the brake disk member while the spool approaches the brake disk member against the biasing force of the first biasing member. This shortens the time (distance) and reduces the time during which the brake disk member is in contact with only the first disk member, thereby effectively increasing the drag force.
[0016]
In the dual- bearing reel braking device according to a second aspect of the present invention, in the device according to the first aspect , the second urging member urges both members in a direction in which the second disk member and the first disk member are separated from each other. In this case, since both the disk members are urged away from each other, the separation of both the disk members and the movement of the second disk member and the spool in the other axial direction can be realized by one urging member. .
[0017]
A braking device for a dual- bearing reel according to a third aspect of the present invention is the device according to the first or second aspect , wherein the braking operation member is mounted on the reel body so as to be swingable around the axis of the spool, and the spool is mounted on the rotating shaft of the spool. The pressing means is rotatably mounted, and the pressing means presses and moves the spool in one direction via a member disposed around the rotation shaft in response to the swing of the braking operation member, and the second disk member via the spool. Is moved in one direction. In this case, the spool is pressed through members such as bearings and gears arranged around the spool shaft, and the second disk member is pressed through the spool to move in one direction. The interval between the second disk members is always the same, and the braking start timing tends to be constant.
[0018]
A dual-bearing reel braking device according to a fourth aspect of the present invention is the device according to any one of the first to third aspects, wherein the braking disk member is mounted on the end surface of the spool opposite to the handle. In this case, since the braking device is disposed on the side opposite to the handle having a relatively large space, the double drag type braking device can be disposed without increasing the size of the reel.
[0019]
The dual-bearing reel braking device according to a fifth aspect of the present invention is the device according to any one of the first to fourth aspects, wherein the braking disk member is a non-rotating member disposed radially outward of the first and second disk members. The spool is mounted so as not to rotate. In this case, since the brake disk member is prevented from being rotated around the spool by the rotation preventing member outside the two disk members having a relatively large space, the structure of the rotation preventing member is simplified.
[0020]
A dual-bearing reel braking device according to a sixth aspect of the present invention is the device according to any one of the first to fifth aspects, wherein the braking disk member is pivoted by a limiting member disposed radially outward of the first and second disk members. The movement of the direction is limited, and it moves by a predetermined distance. In this case, since the movement of the braking disk member is restricted by the restriction member outside the two disk members having a relatively large space, the structure of the restriction member is simplified.
[0021]
The double-bearing reel braking device according to a seventh aspect is the device according to the sixth aspect , wherein the rotation preventing member is also used as the limiting member. In this case, since both members are shared, the configuration of both members is further simplified.
[0022]
DETAILED DESCRIPTION OF THE INVENTION
In FIG. 1, a trolling reel that is a dual-bearing reel according to an embodiment of the present invention includes a cylindrical reel body 1, a spool shaft 2 that is rotatably mounted at the center of the reel body 1, and a spool shaft 2. The spool 3 is supported so as to be rotatable and immovable in the axial direction, and a handle 4 disposed on the side of the reel body 1 is provided. Further, the trolling reel regulates the rotation transmission mechanism 6 that transmits the rotation of the handle 4 to the spool 3, the lever drag mechanism 7 that brakes the rotation of the spool 3 in the yarn feeding direction, and the rotation of the spool 3 in the yarn feeding direction. A reverse rotation prevention mechanism 9 is provided inside the reel body 1.
[0023]
The reel body 1 is made of metal in which a pair of left and right plate-shaped side plates 10, 11 and side plates 10, 11 are concentrically connected to both ends by a torsion connection and fixed by a plurality of fixing screws 8. And a perforated cylindrical reel body 12. The side plates 10 and 11 support both ends of the spool shaft 2 so that the side plates 10 and 11 can turn at substantially the center thereof. The side plate 11 on the handle 4 side is provided with a boss portion 11a protruding outward in the axial direction to support the spool shaft 2, and the handle shaft 5 of the handle 4 is mounted around the boss portion 11a. A thick disk-shaped bearing block 15 for this purpose is screwed.
[0024]
A harness lug 13 for mounting on a reel harness is mounted on the upper portion between the reel body 12 and the side plates 10 and 11 with a gap therebetween. At the bottom of the reel body 12, a rod attachment portion 14 for mounting the reel on a fishing rod is provided.
[0025]
The spool shaft 2 is rotatably supported on the side plates 10 and 11 of the reel body 1 by a pair of left and right bearings 31a and 31b disposed at both ends. In addition, the spool 3 is rotatably supported by two bearings 32a and 32b disposed at both ends of the spool 3 with an axial interval inside. The components of the moving mechanism (described later) of the lever drag mechanism 7 are in contact with the right side of the outer ring of the bearing 31b at the right end of the spool shaft 2. A third gear (described later) of the rotation transmission mechanism 6 is in contact with the left side of the inner ring. The reverse rotation prevention mechanism 9 is in contact with the right side of the inner ring of the bearing 31a at the left end of the spool shaft 2. The side plate 10 is in contact with the right end of the outer ring. The spool is in contact with the left side of the outer ring of the right bearing 32 b that supports the spool 3 via a heat-sensitive hydraulic drag mechanism 33. A disc spring 34 is in contact with the right side of the inner ring via a washer (not shown). The disc spring 34 is provided so that the drag force can be adjusted over a wide range without abruptly increasing the drag force with respect to the swing of a brake operation lever (described later). A second disk plate (to be described later) of the lever drag mechanism 7 is in contact with the left side of the inner ring of the left bearing 32 a that supports the spool 3. The right side of the outer ring is in contact with the spool 3.
[0026]
The spool 3 includes a bobbin trunk 3a and flanges 3b integrally formed at both ends of the bobbin trunk 3a. The end face of the right flange portion 3b is provided with a sound ring 35 having a large number of sound output holes 35a in the circumferential direction for outputting sound during drag operation. A sound output pin 36 attached to the side plate 11 faces the sound output hole 35 a of the sound output ring 35. The sound output pin 36 is biased toward the protruding side. Further, the sound output pin 36 can be moved between an advanced position and a retracted position by a lever 37 (FIG. 2), and is normally arranged at the advanced position by the lever 37 except when a device is turned on. For this reason, normally, when the spool 3 rotates, a clicking sound is generated.
[0027]
The handle 4 is fixed to a protruding end of a cylindrical handle shaft 5 disposed below the spool shaft 2 in parallel with the spool shaft 2. The handle shaft 5 is rotatably supported on the reel body 1 by two bearings 33a and 33b disposed below the boss portion 11a with an interval in the axial direction. The bearings 33a and 33b are attached to both ends of the inner peripheral surface of the cylindrical member 15a fitted into the bearing block 15 below the boss portion 11a. As shown in FIG. 3, a slit 5a penetrating in the radial direction is formed at the tip of the handle shaft 5, and a female screw 5d is formed on the inner surface of the tip.
[0028]
The rotation transmission mechanism 6 includes a speed change mechanism that can be switched between high and low speeds. As shown in FIGS. 1 and 3, the rotation transmission mechanism 6 includes a first gear 16 for high-speed winding and a second gear 17 for low-speed winding, which are rotatably supported on the handle shaft 5 of the handle 4. A third gear 18 and a fourth gear 19 that are non-rotatably mounted on the spool shaft 2 in mesh with the gears 16 and 17, respectively, one of the first and second gears 16 and 17, and the handle shaft 5. The engagement piece 20 for transmitting rotation, two compression springs 21a and 21b for positioning the engagement piece 20 on both sides of the engagement piece 20, and an operating shaft 22 for setting the position of the engagement piece 20. have.
[0029]
The engagement piece 20 is disposed in the slit 5 a of the handle shaft 5 so as not to rotate. A protrusion 20 a is provided at the center of the engagement piece 20. The protrusion 20a is disposed on the inner peripheral side of the flange-shaped spring receiver 24 that receives the compression spring 21a. The spring receiver 24 is screwed to the tip of the handle shaft 5.
[0030]
The operation shaft 22 penetrates the handle shaft 5 inside the handle shaft 5 and protrudes to the outside. The operation shaft 22 is supported so as to be movable in the axial direction by a guide portion 5 b screwed into the protruding end of the handle shaft 5 and a guide portion 5 c formed on the inner peripheral surface of the intermediate portion of the handle shaft 5. A groove 22 a is formed at the projecting end of the operation shaft 22 to the outside. The handle 4 is provided with a slide type stopper 23 that engages with the groove 22a. A spring receiving member 22b that receives the compression spring 21b is attached to the opposite end of the operation shaft 22.
[0031]
In the rotation transmission mechanism 6 having such a configuration, when the operating shaft 22 is pushed in as shown on the upper side of the operating shaft core in FIGS. 1 and 3, the engagement piece 20 is arranged on the second gear 17 and the handle 4 is rotated. The spool shaft 2 and the spool 3 rotate at a low speed by being transmitted to the fourth gear 19 via the second gear 17. On the other hand, when the slide type stopper 23 is slid and the operation shaft 22 is pulled out as shown below the operation shaft core in FIG. 3, the engagement piece 20 is disposed on the first gear 16 and the rotation of the handle 4 causes the first gear to rotate. 16 is transmitted to the third gear 18 via 16 and the spool shaft 2 and the spool 3 rotate at high speed.
[0032]
As shown in FIG. 1, the lever drag mechanism 7 includes a brake disk 25 mounted on the left end of the spool 3 in FIG. 1, a pair of friction disks 26 and 27 disposed on both sides of the brake disk 25, and a brake disk 25. Coil spring 28 (FIG. 5) as a biasing means for biasing the spool 3 and the friction disk 27 through the spool 3 in a direction away from the friction disk 27, and a moving mechanism 29 for reciprocating the spool 3 and the friction disk 27 in the spool axial direction. And have.
[0033]
As shown in FIG. 4, the brake disc 25 is a washer-like disk member made of, for example, stainless steel, and a flange portion on the left side of the spool 3 by a plurality of mounting pins 40 arranged at intervals in the circumferential direction. It is mounted on the end surface of 3b so as to be movable a predetermined distance in a direction in which it is in contact with and away from the spool 3 and not rotatable relative to the spool 3. The mounting pin 40 includes a screw portion 40a that is screwed into the end face of the flange portion 3b, a guide portion 40b that has a larger diameter than the screw portion 40a, and a head portion 40c that has a larger diameter than the guide portion 40b. The brake disc 25 is mounted on the guide portion 40b of the mounting pin 40 so as to be movable in the axial direction, and is movable for a predetermined distance obtained by subtracting its own thickness from the axial length of the guide portion 40b. The mounting pin 40 serves as both a detent member and a restricting member for the brake disk 25. The brake disc 25 is arranged at a position where it is urged by the coil spring 28 and contacts the head 40c in the brake release state. 3 and 4, the braking state is depicted above the spool shaft core and the braking release state is depicted below.
[0034]
The friction disk 26 is disposed to face the surface of the braking disk 25 opposite to the spool 3. A ring-shaped friction plate 26a made of a wear-resistant material such as carbon graphite or fiber reinforced resin is fixed to the surface of the friction disk 26 facing the braking disk 25 by appropriate fixing means such as screws. The friction disk 26 has a cylindrical boss portion 26b at the center, and a pin 2a attached to the spool shaft 2 through the boss portion 26b along the radial direction of the spool shaft 2 is locked. ing. As a result, the friction disk 26 is non-rotatably mounted on the spool shaft 2 and rotates together with the spool shaft 2. Further, the ratchet wheel 50 of the reverse rotation prevention mechanism 9 is in contact with the left end surface of the boss portion 26b of the friction disk 26 in FIG. The ratchet wheel 50 is mounted on the outer peripheral surface of the boss portion 26b in a non-rotatable manner by appropriate locking means such as serration. The ratchet wheel 50 is in contact with the inner ring of the bearing 31a. Further, the outer ring of the bearing 31a is in contact with the side plate 10 as described above. As a result, the friction disk 26 cannot move outward in the spool axial direction (left side in FIG. 4), that is, in a direction away from the brake disk 25, and the ratchet wheel 50 is prohibited from rotating in the yarn unwinding direction.
[0035]
The reverse rotation preventing mechanism 9 is a claw type having a ratchet wheel 50 having a sawtooth 50a formed on the outer peripheral surface, and a ratchet claw 51 disposed on the outer peripheral side of the ratchet wheel 50 and having a tip locking the sawtooth 50a. is there. The ratchet pawl 51 is swingably mounted on the inner surface of the side plate 10 and is biased toward the side where the saw tooth 50a is locked by a tension spring.
[0036]
The friction disk 27 is disposed so as to face the surface of the brake disk 25 on the spool 3 side, rotates in conjunction with the friction disk 26, and is freely movable in the spool axial direction so as to move toward and away from the friction disk 26. Mounted on the shaft 2. A ring-shaped friction plate 27a made of a wear-resistant material such as carbon graphite or fiber reinforced resin is screwed to the surface of the friction disk 27 facing the brake disk 25. The friction disk 27 is non-rotatably mounted on the spool shaft 2 at the center by a pin 2b that penetrates along the radial direction of the spool shaft 2 and is mounted on the spool shaft 2. Further, the inner ring of the bearing 32 a is in contact with the right end surface of the friction disk 27 through the washer 30 in FIG. 4. As a result, the friction disk 27 is pressed by the spool 3 via the bearing 32 a and also presses the spool 3.
[0037]
When the brake is released, the gap A between the friction plate 26a of the friction disk 26 and the brake disk 25 is larger than the gap B between the friction plate 27a of the friction disk 27 and the brake disk 25 as shown in FIG. large. The reason for this will be described in the braking operation described later.
[0038]
The outside of the friction disk 26 is covered with a drag cover 41. The drag cover 41 is made of, for example, an aluminum alloy considering heat dissipation performance, and includes a dish-shaped cover body 41a having a circular opening at the center, and a ring-shaped attachment portion 41b integrally formed on the outer peripheral surface of the cover body 41a. have. The cover body 41a has a space in which the friction disks 26 and 27 and the brake disk 25 can be stored. The attachment portion 41b is fixed to the end surface of the flange portion 3b of the spool 3 by appropriate fixing means such as a plurality of screws. When the plurality of screws are fixed as described above, the tightening torque can be easily managed and the assembly can be easily performed as compared with the case where the whole is fixed to the spool by screwing.
[0039]
The attachment portion 41b is provided with a cylindrical seal portion 41c protruding from the spool side end surface toward the spool 3 side. An annular groove 3c is formed on the end surface of the left flange portion 3b of the spool 3, and a seal portion 41c is fitted in the annular groove 3c. By fitting the seal portion 41c into the annular groove 3c, the spool 3 and the drag cover 41 are centered on the inner peripheral surface of the seal portion 41c. An O-ring 42 is mounted on the outer peripheral surface of the seal portion 41c to prevent liquid from entering from the outer peripheral side.
[0040]
A seal portion 41d that protrudes toward the friction disk 26 is also provided on the inner peripheral surface of the cover body 41a. A seal member 43 with a lip is attached to the seal portion 41d. The tip of the lip of the seal member 43 is in contact with the outer peripheral surface of the boss portion 26 b of the friction disk 26. This also prevents liquid from entering from the inner periphery. The drag cover 41, the spool 3, the drag cover 41, and the friction disk 26 are sealed by the O-ring 42 and the seal member 43, and the inside of the drag cover 41 in which the braking disk 25 and the friction disks 26, 27 are disposed is watertight. Sealed. Thus, by combining the O-ring 42 and the seal member 43, a highly reliable drag waterproof structure can be obtained. In order to facilitate mounting of the O-ring 42, an O-ring mounting groove may be provided in the seal portion 41c.
[0041]
As shown in FIGS. 2 to 4, the moving mechanism 29 includes a brake operation lever 45 that is swingably provided on the reel body 1, and the spool 3 and the above-mentioned in response to the clockwise swing of the brake operation member in FIG. The pressing mechanism 46 that presses the friction disk 27 and moves it to the left in FIG. 3 and the spool and the friction disk 27 in FIG. 3 according to the counterclockwise movement of the braking operation lever 45 in FIG. And a return spring 47 for moving to the right.
[0042]
The return spring 47 is mounted in a compressed state between the friction disks 26 and 27 on the outer peripheral side of the spool shaft 2 and urges the friction disks 26 and 27 in a direction away from the friction disk 26 and 27. 4 Energize to the right.
[0043]
The braking operation lever 45 is swingably mounted on the reel body 1 between a braking release position indicated by a solid line and a maximum braking position indicated by a two-dot chain line in FIG. The braking operation lever 45 includes a lever portion 45a that is swingably attached to the boss portion 11a, and a knob portion 45b that is fixed to the tip of the lever portion 45a. The base end portion of the lever portion 45 a is locked to the first cam member 60 constituting the pressing mechanism 46 so as not to rotate.
[0044]
The pressing mechanism 46 includes a first cam member 60 mounted on the inner peripheral surface of the boss portion 11 a so as to be rotatable and immovable in the axial direction, and a second cam member 61 moving in the axial direction by the rotation of the first cam member 60. And a pressing member 62 that moves in the axial direction in conjunction with the second cam member 61, and a pressing force adjusting mechanism 65 for adjusting the pressing force by the pressing member 62.
[0045]
The first cam member 60 is a large and small two-stage cylindrical member that rotates in conjunction with the swing of the braking operation lever 45. The base end of the lever portion 45a of the brake operation lever 45 is non-rotatably locked to the outer peripheral surface of the first cam member 60 on the distal end side (right side in FIG. 3) by appropriate locking means such as serration. . An inclined cam 60a is formed on the end surface of the large-diameter base end side.
[0046]
The 2nd cam member 61 is a cylindrical member, and is attached to the inner peripheral surface of the boss | hub part 11a so that it cannot rotate but can move to an axial direction. An inclined cam 61 a that engages with the inclined cam 60 a is formed on the outer peripheral end surface of the second cam member 61 that faces the first cam member 60. By the relative rotation of the two inclined cams 60a and 61a, the rotational motion of the first cam member 60 is converted into the linear motion of the second cam member 61 in the axial direction, and the second cam member 61 moves in the axial direction. The second cam member 61 is provided with two locking pins 63 protruding in the radial direction. The front end of the locking pin 63 is locked to a locking groove 11b formed in the axial direction on the inner peripheral surface of the boss portion 11a, and the second cam member 61 is locked to the boss portion 11a so as not to rotate. is doing. The inner peripheral surface of the second cam member 61 is screwed into the pressing member 62. Thereby, the relative positional relationship in the axial direction between the second cam member 61 and the pressing member 62 can be adjusted, and the drag force of the braking operation lever 45 at a predetermined position can be adjusted.
[0047]
The pressing member 62 is a cylindrical member with a flange, and the outer peripheral surface of the cylindrical portion is screwed into the second cam member 61. Further, the left end surface in FIG. 3 of the flange portion slightly protrudes, and this protruding portion is in contact with the outer ring of the bearing 32b.
[0048]
The pressing force adjustment mechanism 65 has an adjustment knob 66 at the center portion of the pressing member 62 that is locked so that the tip end portion 66a cannot rotate but can move in the axial direction. The adjustment knob 66 is mounted on the reel body 1 so as to be rotatable around the spool axis, and is configured to generate a click sound by rotation. When the adjustment knob 66 is rotated, the pressing member 62 is rotated, and the relative position in the axial direction between the pressing member 62 and the second cam member 61 screwed into the pressing member 62 changes. As a result, the drag force when the braking operation lever 45 is at the predetermined position can be adjusted. FIG. 3 shows a state where the pressing member 62 and the second cam member 61 are brought into contact with each other below the spool shaft core and the pressing force is adjusted to the minimum, and the pressing member 62 and the second cam member are arranged on the upper side. 61 shows the state in which the pressing force is adjusted to the maximum with the distance 61 being the most separated.
[0049]
Next, the braking operation of the lever drag mechanism 7 will be described.
[0050]
In the lever drag mechanism 7, when the braking operation lever 45 is swung from the braking position indicated by the two-dot chain line in FIG. 2 to the braking release position indicated by the solid line, the lever drag mechanism 7 is moved downward from the state shown above the spool shaft core in FIGS. Changes to the state shown on the side. First, the friction disk 27 is pressed by the urging force of the return spring 47 and moves to the right in FIG. When the friction disk 27 moves, the brake disk 25 is biased in a direction away from the spool 3 by the coil spring 28 (a direction away from the friction disk 27), so that the brake disk 25 is pressed against the friction disk 26. The friction disk 27 is separated from the brake disk 25, and a gap is forcibly formed between the brake disk 25 and the friction disk 27. Further, the spool 3 is pressed through the bearing 32a and moves to the right side. When the spool 3 moves by a predetermined distance, the brake disk 25 is locked to the head 40c of the mounting pin 40 and moves to the right side in FIG. As a result, the brake disk 25 is separated from the friction disk 26, and a gap is forcibly formed between the brake disk 25 and the friction disk 26. Thereby, the brake of the spool 3 is released. On the other hand, when the spool 3 moves, the second cam member 61 and the pressing member 62 are pressed through the heat-sensitive hydraulic drag mechanism 33, the bearing 32b, the disc spring 34, the third and fourth gears 18 and 19, and the bearing 31b. Retreat to the right in FIG. Then, when the brake operation lever 45 swings to the brake release position, the state becomes below the spool shaft core in FIGS. 3 and 4, and the member on the left side of the disc spring 34 including the spool 3 moves by the distance S1. The member on the right side of the disc spring 34 including the third and fourth gears 18 and 19 moves by a distance S2. Then, the friction disks 26 and 27 are completely separated from the brake disk 25. At this time, since the gap A between the friction disk 26 and the brake disk 25 is larger than the gap B between the friction disk 27 and the brake disk 25 as described above, the brake disk 25 is separated from the friction disk 26 when the brake is released. Thus, the braking release state can be secured in a wide range.
[0051]
On the other hand, when the brake operation lever 45 is swung from the brake release position shown by the solid line in FIG. 2 to the brake position shown by the two-dot chain line, the state shown from the lower side to the upper side of the spool shaft core in FIGS. To change. First, the first cam member 60 is rotated by the swing of the brake operation lever 45, and the second cam member 61 is moved to the left in the spool axial direction. In conjunction with this, the pressing member 62 presses and moves the outer ring of the bearing 31b, and the spool 3 is pressed via the third and fourth gears, the disc spring 34, the bearing 32b, and the heat-sensitive hydraulic drag mechanism 33, and the spool shaft. Move to the left of the direction (left side of FIG. 1). As a result, the braking disk 25 biased by the coil spring 28 also moves leftward in the axial direction. On the other hand, the friction disk 27 is also pressed through the spool 3 and the bearing 32a and moves to the left in the axial direction. As a result, the brake disk 25 and the friction disk 27 approach the friction disk 26. When the brake disk 25 comes into contact with the friction disk 26 that cannot move in the axial direction and cannot rotate in the yarn feeding direction, a slight drag force acts on the spool 3. When the spool 3 is further pressed, the spool 3 approaches the brake disk 25 that is in contact with the friction disk 26, and the brake disk 25 and the friction disk 27 come into contact with each other. When the braking operation lever 45 is swung to the maximum swinging position, the pressing force is maximized, and the braking disk 25 is sandwiched between the two friction disks 26 and 27 to obtain a large drag force. At this time, as described above, the gap A between the friction disk 26 and the brake disk 25 is larger than the gap B between the friction disk 27 and the brake disk 25. Therefore, when the brake disk 25 contacts the friction disk 26 during braking, The friction disk 27 contacts the brake disk 25, and the drag force can be effectively increased with high sensitivity. That is, the time (distance) from when the friction disk 26 comes into contact with the brake disk 25 until the friction disk 27 comes into contact with the brake disk 25 while approaching the spool 3 against the biasing force of the coil spring 28. Becomes shorter and the time during which the braking disk 25 is in contact with only the friction disk 26 is reduced, and the drag force can be effectively increased.
[0052]
Next, a method for operating the trolling reel will be described.
[0053]
When the high-speed winding is performed by the rotation transmission mechanism 6, the operation shaft 22 is pulled out. Thereby, the engagement piece 20 is engaged with the first gear 16 by the urging force of the compression spring 21a. As a result, the rotation of the handle 4 is transmitted to the spool 3 via the handle shaft 5, the first gear 16, the third gear 18, the spool shaft 2, and the lever drag mechanism 7, and the spool 3 rotates at high speed.
[0054]
On the other hand, the operating shaft 22 is pushed in when winding at low speed. Accordingly, the engagement piece 20 is engaged with the second gear 17 by the urging force of the compression spring 21b. As a result, the rotation of the handle 4 is transmitted to the spool 3 via the handle shaft 5, the second gear 17, the fourth gear 19, the spool shaft 2, and the lever drag mechanism 7, and the spool 3 rotates at a low speed. When the operation shaft 22 is pushed in, the operation shaft 22 is kept pushed when the stopper 23 is engaged with the groove 22a.
[0055]
Further, when adjusting the pressing force at the predetermined swing position of the braking operation lever 45 of the lever drag mechanism 7, the relative position in the axial direction between the pressing member 62 and the second cam member 61 is changed by the adjustment knob 66. For example, when the adjustment knob 66 is rotated counterclockwise in FIG. 2 to bring them close to each other, the spool 3 moves in a direction away from the friction disk 26, so that the pressing force decreases. On the other hand, when the adjustment knob 66 is rotated clockwise in FIG. 2 and separated from each other, the spool 3 moves in the direction approaching the friction disk 26, and thus the pressing force increases.
[0056]
When adjusting the drag force by the brake operation lever 45, when the brake operation lever 45 is gradually swung between the brake release position and the maximum brake position, the second cam member 61 moves to the left in FIG. Thus, the pressing force of the pressing member 62 is transmitted to members around the spool shaft 2 such as the bearing 31b, and the spool 3 and the friction disk 27 move, and the frictional force between the brake disk 25 and the two friction disks 26 and 27 gradually increases. growing. Thereby, drag force can be adjusted. Then, when the spool is reversely rotated by pulling the fish when the fish is caught and the reverse rotation is controlled by the reverse rotation prevention mechanism 9 via the lever drag mechanism 7, the drag force set by the lever drag mechanism 7 acts on the spool 3.
[0057]
[Other Embodiments]
(A) The mounting position of the lever drag mechanism 7 is not limited to the position on the side opposite to the handle of the spool 3, but may be the position on the handle side. In this case, the spool shaft may be mounted on the reel body so as not to rotate, and the rotation of the third and fourth gears of the rotation transmission mechanism may be directly transmitted to the friction disks 26 and 27 of the lever drag mechanism without passing through the spool shaft. .
[0058]
(B) The configuration of the moving mechanism 29 is not limited to a cam, and screws or other moving means may be used. Further, the braking operation member is not limited to the swinging lever, and may be a linearly moving member or a rotating member.
[0059]
【The invention's effect】
According to the dual-bearing reel braking device of the present invention, the braking disk member is urged by the first urging member in a direction away from the second disk member, and the braking disk member is mounted on the spool so as to be movable a predetermined distance. Therefore, the timing of the brake disk member in the axial direction is stable and reliably separated from the second disk member, and the timing at which the first disk member is separated from the brake disk member and enters the brake release state is when the spool moves a predetermined distance. And the timing is constant. For this reason, it can change to a braking release state from a braking state reliably, and can ensure a braking release state reliably.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a trolling reel according to an embodiment of the present invention.
FIG. 2 is a side view thereof.
FIG. 3 is an enlarged view of the right cross section.
FIG. 4 is an enlarged left cross-sectional view thereof.
FIG. 5 is a partial cross-sectional view of a lever drag mechanism.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Reel body 2 Spool shaft 3 Spool 4 Handle 6 Rotation transmission mechanism 7 Lever drag mechanism 25 Brake disk 26, 27 Friction disk 28 Coil spring 29 Movement mechanism 45 Braking operation lever 46 Pressing mechanism 47 Return spring

Claims (7)

A brake device for a dual-bearing reel provided in the middle of a rotation transmission mechanism for transmitting rotation from a handle rotatably mounted on the reel body of the dual-bearing reel to the spool, and for braking the rotation of the spool in the yarn unwinding direction. Because
A brake disk member mounted at one end of the spool so as not to be rotatable at an interval and to be movable a predetermined distance in the axial direction of the spool;
Rotation from the handle is transmitted and disposed opposite to the surface of the brake disc member opposite to the spool, and rotation in the yarn unwinding direction is prohibited with respect to the reel body, and at least the axial direction A first disk member that is immovable in a direction away from the brake disk member;
The brake disk member is disposed opposite to the spool-side surface, rotates in conjunction with the first disk member, and is movable in the axial direction so as to move toward and away from the first disk member. Two disk members;
A first urging member that urges the braking disk member in a direction away from the second disk member;
And a moving means for reciprocating the said braking disc member sandwiched capable spool and the second disk member in the first and second disc members to said axial direction
The first and second disk members are non-rotatably mounted on a spool shaft that passes through the center of the spool and rotatably supports the spool,
The moving means is
A braking operation member provided on the reel body so as to be movable between a braking release position and a maximum braking position;
A pressing unit that presses the spool and the second disk member in accordance with the movement of the braking operation member to the maximum braking position and moves the spool and the second disk member in one axial direction approaching the first disk member;
A second urging member for urging the second disk member to move the spool and the second disk member in the other axial direction in response to the movement of the braking operation member to the brake release position. And
When the braking operation member is moved to the braking release position and the second disk member is moved to the maximum in the other axial direction, the gap between the first disk member and the braking disk member is A braking mechanism for a dual-bearing reel that is larger than the gap between the second disk member and the braking disk member. 2. The double-bearing reel braking mechanism according to claim 1 , wherein the second urging member urges both the members in a direction in which the second disk member and the first disk member are separated from each other. The braking operation member is attached to the reel body so as to be swingable about the axis of the spool,
The spool is rotatably mounted on a rotation shaft of the spool,
The pressing means presses and moves the spool in the one direction via a member arranged around the rotation shaft in response to the swing of the braking operation member, and the second disk via the spool. The braking device for a dual-bearing reel according to claim 1 or 2, wherein the member is pressed and moved in the one direction. The braking device for a dual-bearing reel according to any one of claims 1 to 3 , wherein the braking disk member is mounted on an end surface of the spool opposite to the handle. The brake disc member, said first and is non-rotatably mounted to the spool by the arranged detent member radially outward of the second disc member, both as claimed in any one of claims 1 to 4 Braking device for bearing reel. The brake disc member is limited to movement of the axial movement by the predetermined distance by the first and second disk restriction member diameter disposed outwardly of the member, one of claims 1 to 5 A brake device for a double-bearing reel according to claim 1. The double-bearing reel braking device according to claim 6 , wherein the rotation preventing member is also used as the limiting member.

Images