KR102766003B1 - Dual-bearing reel for fishing - Google Patents

Abstract

[Task] To stably provide sufficient braking force to the worm shaft of the level wind mechanism.
[Solution] A gear engagement portion (111) installed at one end of a worm shaft (11), a transmission gear (13) that is engaged with the gear engagement portion (111) and transmits rotation of a spool to the worm shaft (11), a shaft-contacting member (14) that is engaged with the gear engagement portion (111) penetrating the transmission gear (13) and has a friction surface (14a) larger in area than the gear engagement portion (111) when viewed from the direction of the shaft axis (O), a friction plate (15) that is arranged opposite to the friction surface (14a) of the shaft-contacting member (14) and is installed so as to be in contact with the friction surface (14a) in the direction of the shaft axis (O), and a braking device that can press the friction plate (15) toward the shaft-contacting member (14). A dual-bearing fishing reel is provided, which comprises a knob (16), a plate spring (17) interposed between a brake knob (16) and a friction plate (15), and a pair of rigid members (18A, 18B) that hold the plate spring (17) so that it cannot rotate from both sides in the direction of a shaft axis (O).

Description

DUAL-BEARING REEL FOR FISHING

The present invention relates to a dual-bearing reel for fishing.

Conventionally, in medium-sized or larger fishing dual-bearing reels with a wide spool width, a level wind mechanism has been used that is linked to the spool without a clutch mechanism that switches the spool between a state of rotation in the fishing line winding direction and a state of allowing rotation in the fishing line release direction. In devices employing such a level wind mechanism, it is known that braking force is obtained by pressing not the end face of the spool shaft, but the end face of the worm shaft of the level wind mechanism as shown in Patent Document 1, for example, as a braking mechanism for adjusting the falling speed of the fishing tackle.

Japanese Patent Gazette Patent No. 3305926

However, in the level wind mechanism used in conventional fishing double bearing reels, a transmission gear that transmits rotation to the spool shaft is connected to the end of the worm shaft.

For this reason, for example, the worm shaft end is formed in a large, two-sided, differently sized, mating shape, and a transmission gear is fitted to the worm shaft end to prevent rotation. That is, since the cross-sectional area of the worm shaft end is small, it is difficult to obtain sufficient and stable braking force by pressing the worm shaft end, and there is room for improvement in this respect.

The present invention has been made in consideration of such circumstances, and its purpose is to provide a dual-bearing reel for fishing capable of stably applying sufficient braking force to a worm shaft of a level wind mechanism.

The dual-bearing reel for fishing related to the present invention is a dual-bearing reel for fishing having a worm shaft that rotates synchronously with the rotation of a spool, and a fishing line guide that reciprocates by the rotation of the worm shaft, and a level wind mechanism that obtains braking force by pressing a cross section of the worm shaft, and is provided with a gear engaging portion provided at one end of the worm shaft in the shaft axial direction, a transmission gear engaged with the gear engaging portion and transmitting the rotation of the spool to the worm shaft, a shaft contact member engaged with the gear engaging portion penetrating the transmission gear and having a friction surface having a larger area than the gear engaging portion when viewed from the shaft axial direction, and a friction member that is arranged opposite the friction surface of the shaft contact member and is provided so as to be in contact with the friction surface in the shaft axial direction, and the shaft contact member has the friction surface on the friction member side in the shaft axial direction. The invention is characterized in that the shaft has a disc portion and a gear engagement portion that engages the gear engagement portion on the transmission gear side, the disc portion has an axial contact surface facing the transmission gear side, and the gear engagement portion has a contact surface that is provided in the shaft axial direction to the axial contact surface.

According to the fishing dual-bearing reel related to the present invention, the area of the friction surface of the shaft-mounted member that is engaged with the gear engagement portion at the end of the worm shaft and rotates integrally is configured to be larger than the area of the gear engagement portion when viewed in the shaft axial direction. Therefore, when applying braking force by pressing the end face of the worm shaft, the friction member can be pressed against the friction surface of the shaft-mounted member over a large area, so that sufficient braking force (mechanical braking force) can be stably applied to the rotation of the spool when releasing the fishing line.

(2) It is preferable that a braking knob capable of pressing the friction member toward the axle contact member is installed, and that an elastic member is interposed between the braking knob and the friction member.

In this case, by interposing an elastic member between the friction member that generates braking force and the braking knob, stable friction force can be exerted, and high-precision axial force management is possible, so that the inclination of the brake curve, etc. can be adjusted.

(3) It is preferable that the elastic member is held in place so that it cannot rotate by rigid members from both sides in the direction of the shaft axis.

In this case, since the elastic member does not directly contact the brake knob or the friction member, when the friction member is pressed toward the axial contact member by the brake knob, the elastic member can be prevented from being stuck in the friction member.

In addition, in the present invention, since the pressure force by the braking knob is transmitted to one elastic member through the rigid member, and further transmitted to the friction member from the other elastic member, the braking force can be stably transmitted to the friction member and the shaft contact member.

According to the fishing double-bearing reel related to the present invention, sufficient braking force can be stably applied to the worm shaft of the level wind mechanism.

FIG. 1 is a perspective view from an oblique rearward direction showing the configuration of a two-axis electric reel according to an embodiment of the present invention.
Figure 2 is a perspective view of the two-axis electric reel shown in Figure 1, viewed obliquely from the front.
Figure 3 is a perspective view showing the internal structure of a two-axis electric reel, and is a drawing omitting the left side plate of the main body frame, etc.
Figure 4 is a side view showing the configuration of a level wind device and a braking force control mechanism.
Fig. 5 is an enlarged cross-sectional view showing the main parts of the level wind device and the braking force control mechanism, and is a cross-sectional view viewed from a direction perpendicular to the shaft axis.
Figure 6 is a perspective view showing a state in which a transmission gear is attached to a worm shaft.
Fig. 7 is a perspective view showing a state in which an axial contact member is engaged with the gear engagement portion shown in Fig. 6.
Figure 8 is a perspective view showing a braking force adjustment mechanism installed on a worm shaft.
Figure 9 is an exploded perspective view of the braking force control mechanism shown in Figure 8.
Figure 10 is a plan view of the friction plate and the rigid member as viewed from the shaft axis direction.

Hereinafter, embodiments of a fishing double-bearing reel according to the present invention will be described with reference to the drawings. In addition, in each drawing, the scale of each component may be changed as necessary to make each component a size that can be seen.

As shown in FIGS. 1 and 2, the fishing dual-bearing reel of the present embodiment (hereinafter referred to as a dual-axis electric reel (1)) is driven by power supplied from an external power source and has an internal power source for use as a hand-winding dual-bearing reel.

A dual-axis electric reel (1) comprises a reel body (2) mountable on a fishing rod, a handle (20) attached so as to be rotatable about a handle axis (C1) with respect to the reel body (2), a spool (3) rotatable about a spool axis (C2) parallel to the handle axis (C1) with respect to the reel body (2) and on which a fishing line (not shown) is wound, a motor (4) installed on the reel body (2) and transmitting a rotational driving force to the spool (3), a clutch mechanism (5) capable of switching a connection state connecting the spool (3) and the handle (20) and a blocking state, and a level wind device (10) that obtains braking force by pressing a cross section of a worm shaft (11) shown in FIG. 3 while being linked with the spool (3) without going through the clutch mechanism (5).

Here, in the present embodiment, as shown in Fig. 3, the handle axis (C1), the spool axis (C2), and the shaft axis (O) are each installed in parallel, and their directions are defined as left-right directions (L1) as necessary, and the direction along the direction in which the fishing line wound on the spool (3) is released is defined as the front-back direction (L2) along the direction orthogonal to the left-right direction (L1). Furthermore, in the front-back direction (L2), the direction in which the fishing line is released from the spool (3) is defined as front (前方), and the opposite direction is defined as rear (後方), and left and right are defined when the dual-axis electric reel (1) is viewed from the rear side. In addition, Fig. 1 is a perspective view of the dual-axis electric reel (1) as viewed from the rear obliquely upward, and Fig. 2 is a perspective view of the dual-axis electric reel (1) as viewed from the front obliquely downward.

(reel body)

As shown in Fig. 1, the reel body (2) is equipped with a body frame (21), a cover (22) covering a part of the body frame (21), and a depth indicator (23) located on the upper side of the body frame (21).

The main body frame (21) is an integrally formed member made of, for example, synthetic resin or metal. The main body frame (21) has a right plate (21A) that is the handle (20) side with the spool (3) interposed in the left-right direction (L1), a left plate (21B) located on the opposite side to the right plate (21A), and a plurality of connecting members (21C) (see Fig. 2) that connect the right plate (21A) and the left plate (21B).

The right side plate (21A) and the left side plate (21B) are arranged with a gap between them in the left-right direction (L1). In addition, on each side plate (21A, 21B), a support member for supporting a spool (3) or a motor (4), and a rotational driving mechanism such as a clutch mechanism (5) and a level wind device (10) are arranged.

The spool shaft (31) (see Fig. 3) of the spool (3) is mounted in a rotatably supported state on the right plate (21A) and the left plate (21B). The connecting member (21C) shown in Fig. 2 is plate-shaped and connects the lower parts of the right plate (21A) and the left plate (21B). A fishing rod mounting portion (24) for attaching to a fishing rod is mounted on one of the connecting members (21C) at approximately the center portion in the left-right direction (L1).

The cover (22) is provided with a right cover (22A), a left cover (22B), and a front cover (22C). The right cover (22A) covers the right plate (21A) by providing a predetermined receiving space, and is fastened to the outer edge of the right plate (21A) with, for example, a screw. The left cover (22B) covers the left cover (22B) by providing a predetermined receiving space, and is fastened to the outer edge of the left plate (21B) with, for example, a screw. The front cover (22C) covers the entire front of the main body frame (21).

As shown in Fig. 2, a connector (28) for connecting a power cable from outside is mounted on the front lower part of the right side panel (21A) with the connection end (28a) facing downward.

(depth indicator)

The depth display unit (23) is arranged between the right plate (21A) and the left plate (21B), as shown in Fig. 1. The depth display unit (23) has a display panel (23A) made of a liquid crystal display capable of displaying the depth of a tackle that can be mounted on the tip of a fishing line, and a reel control unit (not shown). The depth display unit (23) comprises a case portion mounted on the upper portions of the right plate (21A) and the left plate (21B), is fixed with screws to the outer surfaces of the right plate (21A) and the left plate (21B), and has a plurality of operation buttons (23B) (three in this embodiment) for performing display operations.

(handle)

As shown in FIGS. 1 and 2, the handle (20) has a handle arm (25) that is non-rotatably mounted on a tip end (20a) of the handle shaft, a handle knob (26) that is rotatably mounted on one end of the handle arm (25) about an axis parallel to the handle axis line (C1), and a drag (27) arranged on the reel body (2) side.

Torque from the handle (20) is directly transmitted to the spool (3) when the clutch mechanism (5) is in the clutch-on state.

(spool)

The spool (3) is installed so as to be rotatable between the right plate (21A) and the left plate (21B) via bearings (not shown). As shown in Fig. 3, the spool (3) is provided with a spool shaft (31), a cylindrical line winding body (32) that is arranged coaxially with the spool shaft (31) and rotatable in conjunction with it, and flange parts (33) that are expanded outward in the radial direction at both ends of the line winding body (32).

The spool (3) is rotationally driven from the motor (4) through a motor power transmission gear (a plurality of spool transmission gears (34)), and is linked to a clutch mechanism (5) driven by a clutch operating member (50) shown in Fig. 1. The spool shaft (31) is rotatably supported separately through bearings on the right cover (22A) and the left cover (22B).

(clutch mechanism)

As shown in Fig. 1, the clutch mechanism (5) can be switched between a clutch-on state in which the rotation of the handle (20) can be transmitted to the spool (3) by operating the clutch operating member (50), and a clutch-off state in which the rotation of the handle (20) cannot be transmitted to the spool (3). In the clutch-on position, the rotation of the pinion gear is transmitted to the spool shaft (31), the clutch-on state is established, and the pinion gear and the spool shaft (31) are capable of rotating as one. In addition, in the clutch-off position, since the rotation of the pinion gear is not transmitted to the spool shaft (31), the clutch-off state is established, and the spool (3) is capable of freely rotating.

(absence of clutch operation)

The clutch operating member (50) is for switching the clutch mechanism (5) between the clutch-on state and the clutch-off state, as shown in Fig. 1. The clutch operating member (50) is installed at the rear of the reel body (2) between the right plate (21A) and the left plate (21B) so as to be movable in the direction of approaching and departing from the fishing rod mounting portion (24) at the rear of the reel body (2). In the present embodiment, the clutch operating member (50) is installed so as to be oscillating around the spool axis (C2).

(Spool drive mechanism)

The above-described spool drive mechanism drives the spool (3) in the line winding direction. In addition, when winding, a drag force is generated by the drag (27) against the spool (3), thereby preventing the fishing line from being cut.

The drag (27) is installed coaxially with the handle axis (C1) between the handle arm (25) of the handle (20) and the right cover (22A). The spool drive mechanism comprises the above-described motor (4) whose rotation in the line winding direction is prevented by a reverse prevention part in the form of a roller clutch (not shown), and a rotation transmission mechanism that reduces the rotation of the motor (4) and transmits it to the spool (3) or increases the rotation of the handle (20) and transmits it to the spool (3).

(motor)

The motor (4) is installed in a position in front of the spool (3) (see Fig. 1) in the entirety of the two-axis electric reel (1) and is covered by a motor receiver (40) (see Fig. 2) having a shape divided in half. As shown in Fig. 3, the motor (4) has a motor rotation shaft, a motor body, and a case that holds the motor body. In addition, the motor (4) is accommodated in a normal motor case (41).

The motor rotation shaft penetrates the center of the motor body in the direction of the motor axis, and both ends of the motor rotation shaft are rotatably supported by the case and the motor end cap (42) described later.

(Level wind device (10))

The level wind device (10) (level wind mechanism) has, as shown in Fig. 4, a worm shaft (11) that rotates synchronously with the rotation of the spool (3), and a fishing line guide part (12) that reciprocates by the rotation of the worm shaft (11). The level wind device (10) is a mechanism in which braking force is obtained by pressing the cross section of the worm shaft (11).

As shown in Fig. 3, the worm shaft (11) is rotatably supported at both ends relative to side plates (21A, 21B) in front of the spool axis (31) of the spool (3). The worm shaft (11) is connected to a motor power transmission gear (spool transmission gear (34)) via a transmission gear (13) and a level wind power transmission gear (113), and rotates synchronously with the rotation of the spool (3). Then, the rotation of the worm shaft (11) is transmitted to the fishing line guide (12) via a driving connecting member (122), as shown in Fig. 4.

The left end (11a) of the worm shaft (11) in the direction of the shaft axis (O) is formed in a circular cross-section as shown in FIGS. 5 to 7. At the shaft tip (11b) (see FIG. 5) of the one end (11a) of the worm shaft (11), a gear engagement portion (111) of a different radial cross-section from the circular cross-section of the one end (11a) is provided, which protrudes coaxially toward the left in the direction of the shaft axis (O) and is provided. The gear engagement portion (111) has a rectangular cross-section, and both ends of the long sides thereof extend to a position where they protrude radially outward from the outer periphery of the shaft tip (11b) (see FIG. 9).

As shown in FIGS. 6 to 8, a transmission gear (13) that transmits the rotation of the spool (3) to the worm shaft (11) is non-rotatably engaged in a state in which it is inserted from the tip side in the gear engagement portion (111). The gear engagement portion (111) protrudes from the engagement transmission gear (13) toward the tip side. As shown in FIG. 5, an axial contact member (14) of a braking force adjusting mechanism (10A) described later is fixed to a protruding portion (111a) of the gear engagement portion (111). A contact surface (111b) on the left side of the gear engagement portion (111) contacts an axial contact surface (141a) of a disc portion (141) of the axial contact member (14). In addition, on the contact surface (111b) of the gear engagement portion (111), an engagement projection (111c) protruding toward the left on the shaft axis (O) is formed.

As shown in Fig. 6 and Fig. 9, the transmission gear (13) has a cross-shaped through hole (13a) formed in the center. In the through hole (13a), a gear engagement portion (111) having a rectangular cross section is capable of engagement at positions spaced at 90 degrees apart. As shown in Fig. 3, the transmission gear (13) provides rotational resistance to the spool (3) applied to the worm shaft (11) via the spool shaft (31) by a plurality of gears (level wind power transmission gears (113)).

As shown in Fig. 4, the fishing line guide (12) reciprocates on a rod (121) spanned between the side plates (21A, 21B) by the rotation of the worm shaft (11). As a result, the fishing line guide (12) reciprocates on the rod (121), and the fishing line can be evenly wound around the line winding body (32) of the spool (3).

(Brake force control mechanism (10A))

As shown in FIG. 5 and FIG. 9, a braking force adjusting mechanism (10A) for applying braking force to the spool (3) is installed at one end (11a) of the anti-handle side of the worm shaft (11). The braking force adjusting mechanism (10A) and the transmission gear (13) described above are accommodated on the inner side of a receiving convex portion (211) formed on the left side plate (21B) of the main body frame (21), excluding the handle portion (162) of the braking knob (16) described later (see FIG. 4).

Here, the left plate (21B), as shown in Fig. 5, is formed with the receiving convex portion (211) that is convex toward the left and is approximately coaxial with the shaft axis (O). The receiving convex portion (211) has a peripheral wall portion (212) that protrudes toward the left from the plate surface (21a) of the left plate (21B), and a terminal plate (213) that blocks the protruding end of the peripheral wall portion (212). A circular tip opening portion (213a) that is coaxial with the shaft axis (O) is formed in the terminal plate (213). On the inside of the tip opening portion (213a), a pressure shaft (161) of a brake knob (16) described later is arranged so as to be able to move forward and backward in the direction of the shaft axis (O).

In addition, a male screw is formed on the outer surface (211a) of the single plate (213) side of the receiving convex portion (211), and a female screw is formed on the inner surface (162a) of the barrel (described later) of the handle portion (162) of the brake knob (16) so that it can be screwed in.

The braking force control mechanism (10A), as shown in FIG. 5 and FIG. 9, is configured to include a shaft-contacting member (14) that is engaged with a gear engagement portion (111) penetrating a transmission gear (13) and has a friction surface (14a) larger in area than the gear engagement portion (111) when viewed from the direction of the shaft axis (O), a friction plate (15) (friction member) that is arranged opposite the friction surface (14a) of the shaft-contacting member (14) and is installed so as to be in contact with the friction surface (14a) in the direction of the shaft axis (O), a braking knob (16) that can press the friction plate (15) toward the shaft-contacting member (14), a disc spring (17) (elastic member) interposed between the braking knob (16) and the friction plate (15), and a disc spring (17) that is configured to be rotated non-rotatably from both sides in the direction of the shaft axis (O). It has a pair of rigid members (18) (18A, 18B) that support each other.

In the gear engagement portion (111) of the worm shaft (11), a transmission gear (13), a shaft-contacting member (14), a friction plate (15), a disc spring (17), a pair of rigid members (18A, 18B), and a brake knob (16) are arranged coaxially with the shaft axis (O), respectively. Of these, the disc portion (141) of the shaft-contacting member (14), the friction plate (15), the disc spring (17), and a pair of rigid members (18A, 18B) are arranged in a state of overlapping in the direction of the shaft axis (O).

As shown in Fig. 5, the shaft contact member (14) has a disc portion (141) and a fitting member (142) that is installed on one surface (the shaft contact surface (141a)) of the disc portion (141) on the transmission gear (13) side, and has a concave groove (143) formed to fit into a protruding portion (111a) of a gear fitting portion (111) of a worm shaft (11).

In the center of the disc portion (141), an engagement hole (141b) penetrating in the thickness direction is formed. An engagement projection (111c) of a gear engagement portion (111) that fits into a concave groove (143) is inserted into this engagement hole (141b).

The concave groove (143) has groove surfaces that are parallel and opposite to each other along the groove extension direction. The shaft contact member (14) is engaged with the gear engagement portion (111) by interlocking the groove surfaces of the concave groove (143) and is engaged with the gear engagement portion (111) in a non-rotatable manner. The contact surface (111b) of the gear engagement portion (111) engaged with the concave groove (143) is in contact with the shaft contact surface (141a) of the disc portion (141).

In addition, the friction plate (15) is configured to approach and separate from the other surface (friction surface (14a)) of the disc portion (141), and when approaching, the friction plate (15) comes into contact, thereby generating frictional force between the two.

The friction plate (15) is interposed between the disc portion (141) of the shaft-contacting member (14) and the first rigid member (18A). The friction plate (15) is formed in a disc shape having an area almost equal to the shaft-contacting surface (141a) of the disc portion (141) of the shaft-contacting member (14), and rotation stop pieces (151) protruding radially outward from both sides with the center therebetween are installed (see Fig. 10). The friction plate (15) is accommodated in a state in which rotation around the shaft axis (O) is regulated by engaging a pair of rotation stop pieces (151, 151) in engaging concave portions (212a) (see Fig. 4) formed on the inner side of the accommodation convex portion (211) of the left plate (21B).

As a member of the friction plate (15), a member equivalent to the rigid member (18) is preferable, and a member having a strength that does not deform under pressure, such as brass, stainless steel alloy, aluminum alloy, etc., can be used.

The brake knob (16) is positioned so as to protrude further outward from the left cover (22B). The brake knob (16) has a pressure shaft (161) extending along the shaft axis (O) and a handle portion (162) coaxially installed at one end of the pressure shaft (161) and positioned on the outside of the left cover (22B).

The pressurizing shaft (161) has a circular cross-section and is positioned so as to be movable in the direction of the shaft axis (O) on the inside of the tip opening (213a) of the receiving convex portion (211) of the left plate (21B). The pressurizing surface (161a) of the tip of the pressurizing shaft (161) is formed on a plane perpendicular to the shaft axis (O), and is positioned so as to approach and deviate from one of the second rigid members (18B) in the direction of the shaft axis (O), and is also installed so as to be in contact with the second rigid member (18B).

The handle portion (162) is formed as a normal shape with a top, and a female screw is formed on the inner surface (162a) of the barrel. The brake knob (16) is installed so as to be able to move forward and backward together with the pressure shaft (161) in the direction of the shaft axis (O) by engaging the inner surface (162a) of the barrel of the handle portion (162) with the male screw of the outer surface (211a) of the receiving convex portion (211).

The plate spring (17) is clamped so that it cannot rotate on both sides in the direction of the shaft axis (O) by rigid members (18A, 18B). By installing the plate spring (17), the amount of movement (operation amount) of the pressure shaft (161) by the braking knob (16) and the braking force of the worm shaft (11) can be smoothly proportional.

A pair of rigid members (18A, 18B) are interposed between a friction plate (15) and a pressing surface (161a) of a pressing shaft (161) of a brake knob (16), with a plate spring (17) sandwiched between the two sides. The rigid members (18A, 18B) are each formed in a disk shape, and rotation stop pieces (181) protruding radially outward from both sides with the center therebetween are provided (see Fig. 10). The rigid members (18A, 18B) are accommodated in a state in which rotation around the shaft axis (O) is regulated by engaging a pair of rotation stop pieces (181, 181) in an engaging concave portion (212a) formed on the inner side of a receiving convex portion (211) of the left plate (21B).

As a member of the rigid member (18A, 18B), a member having a strength that does not deform under the pressure of the pressurizing shaft (161) is preferable, and examples thereof include brass, stainless steel alloy, aluminum alloy, etc.

As an operation of the braking force control mechanism (10A) that provides friction braking force to the rotation of the spool (3) in this way, when the handle portion (162) of the braking knob (16) is turned in one direction (for example, in the direction of symbol E1 in FIGS. 4 and 5) to move the pressure shaft (161) to the right (in the direction of arrow P1) in the direction of the shaft axis (O), the second rigid member (18B) is pressed toward the right in the direction of the shaft axis (O) at the pressure surface (161a) of the pressure shaft (161), and the pressure increases. Then, the gear engagement portion (111) that is fixed to the worm shaft (11) in that order is pressed from the second rigid member (18B), the disc spring (17), the first rigid member (18A), the friction plate (15), and the shaft contact member (14). By this, the frictional force generated by the friction plate (15) coming into contact with the shaft contact surface (141a) of the shaft contact member (14) increases, and rotational resistance is applied to the worm shaft (11), thereby applying braking.

In addition, when the handle part (162) is turned in the opposite direction (the symbol E2 direction of FIGS. 4 and 5) to move the pressure shaft (161) to the left (arrow P2 direction) in the direction of the shaft axis (O), the pressure surface (161a) of the pressure shaft (161) moves to the left, and the pressure of the pressure surface (161a) against the second rigid member (18B) is relieved. Then, the pressure (braking force) that was pressurizing the plate spring (17), the first rigid member (18A), the friction plate (15), the shaft contact member (14), and the gear engagement part (111) of the worm shaft (11) in that order from the second rigid member (18B) is also released or relieved. By this, the frictional force generated between the friction plate (15) and the shaft contact surface (141a) of the shaft contact member (14) is reduced, and the rotational resistance applied to the worm shaft (11) is also reduced, thereby preventing braking.

Next, the operation of the two-axis electric reel (1) configured in this manner will be described in detail based on the drawings.

As shown in FIGS. 4 and 5, in the dual-axis electric reel (1) according to the present embodiment, the area of the friction surface of the shaft-mounted member (14) that is engaged with the gear engagement portion (111) at the end of the worm shaft (11) and rotates integrally, as viewed from the shaft axis direction, is configured to be larger than the area of the gear engagement portion (111). Therefore, when applying braking force by pressing the end face of the worm shaft (11), the friction plate (15) can be pressed against the friction surface (14a) of the shaft-mounted member (14) over a large area, so that sufficient braking force (mechanical braking force) can be stably applied to the rotation of the spool (3) when releasing the fishing line.

In addition, in this embodiment, by interposing a plate spring (17) between the friction plate (15) that generates braking force and the braking knob (16), stable friction force can be exerted, and high-precision axial force management is possible, so that the inclination of the brake curve, etc. can be adjusted.

Furthermore, in this embodiment, since the plate spring (17) is clamped by the plate spring (17) so as not to rotate from both sides in the direction of the shaft axis (O), the plate spring (17) does not directly contact the brake knob (16) or the friction plate (15), when the friction plate (15) is pressed toward the shaft contact member (14) by the brake knob (16), the plate spring (17) can be prevented from being stuck to the friction plate (15).

In addition, in this embodiment, since the pressure force by the braking knob (16) is transmitted from one second rigid member (18B) to the plate spring (17), and further transmitted from the other first rigid member (18A) to the friction plate (15), the braking force can be stably transmitted to the friction plate (15) and the shaft contact member (14).

In the dual-axis electric reel (1) according to the present embodiment configured as described above, sufficient braking force can be stably applied to the worm shaft of the level wind mechanism.

Hereinafter, the embodiments of the fishing double-bearing reel according to the present invention have been described, but these embodiments have been presented as examples and are not intended to limit the scope of the invention. The embodiments can be implemented in various other forms, and various omissions, substitutions, and changes can be made without departing from the gist of the invention. The embodiments and their modifications include, for example, those that can be easily conceived by those skilled in the art, those that are substantially the same, those that are in an equivalent range, etc.

For example, in the above embodiment, a pair of rigid members (18A, 18B) and a plate spring (17) (elastic member) are interposed between the brake knob (16) and the friction plate (15) (friction member), but it is also possible to omit these rigid members or elastic members. For example, only the elastic member may be interposed and the rigid member may be omitted, or both the elastic member and the rigid member may be omitted. Furthermore, as in the present embodiment, only the first rigid member (18A) on the friction plate (15) side of the pair of rigid members (18A, 18B) may be omitted.

In addition, although a plate spring (17) is employed as an elastic member in the above embodiment, it is not limited to a plate spring, and other elastic members such as a wave washer, a coil spring, a rubber washer, etc. may be employed. The point is that the elastic member may be a member capable of gently proportioning the amount of movement (operation amount) of the compression shaft by the braking knob and the braking force of the worm shaft.

In addition, the shape and size of the rigid member or friction member can be set arbitrarily, but in order to ensure stability of braking force, it is preferable that it be a flat plate shape as in the present embodiment.

1: Dual shaft electric reel (double bearing reel for fishing)
2: Reel body
3: Spool
4: Motor
10: Level wind device (level wind mechanism)
10A: Braking force control mechanism
11: Worm shaft
12: Fishing line guide
13: Transmission Gear
14: Absence of axle contact
14a: Friction surface
15: Friction plate (friction member)
16: Brake Knob
17: Plate spring (elastic member)
18, 18A, 18B: Rigid member
21: Body Frame
21B: Left side
31: Spool shaft
111: Gear engagement part
111b: Contact surface
141: Original plate
141a: Axial contact surface
143: Concave Home
161: Compression
211: Receiving convex part
O: Shaft axis

Claims (3)

A dual-bearing fishing reel having a worm shaft that rotates synchronously with the rotation of a spool, a fishing line guide that reciprocates by the rotation of the worm shaft, and a level wind mechanism that obtains braking force by pressing the end surface of the worm shaft,
A gear engagement portion installed at one end of the shaft axial direction of the above worm shaft,
A transmission gear that is engaged with the gear engagement portion and transmits the rotation of the spool to the worm shaft;
A shaft contact member that is engaged with the gear engagement portion penetrating the transmission gear and has a friction surface having a larger area than the gear engagement portion when viewed from the shaft axial direction,
A friction member is arranged opposite to the friction surface of the above-mentioned shaft contact member and is installed so as to be in contact with the friction surface in the shaft axial direction.
Equipped with,
The above-mentioned shaft contact member has a disc portion having the friction surface on the friction member side in the shaft axial direction, and a fitting member that fits the gear fitting portion on the transmission gear side.
The above disc portion has an axial contact surface facing the transmission gear side,
A fishing dual-bearing reel, wherein the gear engaging portion has a contact surface that contacts the shaft contact surface in the shaft axial direction. In the first paragraph,
A braking knob is installed that can pressurize the friction member toward the axle contact member side,
A dual-bearing fishing reel, wherein an elastic member is interposed between the brake knob and the friction member. In the second paragraph,
A dual-bearing reel for fishing, wherein the elastic member is held in place by rigid members on both sides of the shaft axis so that the elastic member cannot rotate.