阅读说明：本技术 钓鱼用渔线轮的驱动齿轮 (Drive gear of fishing reel for fishing ) 是由 池袋哲史 于 2021-02-26 设计创作，主要内容包括：本发明提供一种钓鱼用渔线轮的驱动齿轮。驱动齿轮(11)具有圆板部(30)和多个齿轮齿(31)。圆板部(30)具有转动轴心(X)。多个齿轮齿(31)分别从圆板部(30)上的外周侧的侧表面向转动轴心(X)延伸的方向突出。齿轮齿(31)具有主体部(32)和延伸部(33)。由穿过主体部(32)的齿顶面(31c)的圆筒面(CP1)与延伸部(33)的径向内侧表面(31d)形成的第一角度(a11、a12)比啮合压力角(b)大。据此,提供一种能提高转动感的钓鱼用渔线轮的驱动齿轮。(The invention provides a drive gear of a fishing reel for fishing. The drive gear (11) has a disk portion (30) and a plurality of gear teeth (31). The disc portion (30) has a rotation axis (X). The plurality of gear teeth (31) protrude from the outer peripheral side surface of the disk portion (30) in the direction in which the rotation axis (X) extends. The gear teeth (31) have a main body portion (32) and an extension portion (33). A first angle (a11, a12) formed by a cylindrical surface (CP1) passing through the tooth crest (31c) of the main body portion (32) and the radially inner surface (31d) of the extension portion (33) is larger than the meshing pressure angle (b). Thus, a drive gear for a fishing reel is provided which can improve the spinning feeling.)

1. A drive gear for a fishing reel, which is used for the fishing reel,

the drive gear of the fishing reel is characterized in that,

having a circular plate portion and a plurality of gear teeth, wherein,

the circular plate part is provided with a rotating shaft center;

a plurality of gear teeth projecting from a side surface on an outer peripheral side of the circular plate portion in a direction in which the rotational axis extends,

the gear teeth have a main body portion and an extended portion extending radially inward from the main body portion,

a first angle formed by a cylindrical surface around the rotational axis passing through an axially outer side surface of the main body portion and a radially inner side surface of the extension portion is larger than an engagement pressure angle.

2. A fishing reel drive gear according to claim 1,

the first angle is larger than a second angle formed by the cylindrical surface and an axially outer surface of the body portion.

3. A fishing reel drive gear according to claim 1 or 2,

a pair of tooth surfaces are formed on the main body portion and the extended portion at intervals from each other in a circumferential direction,

the tooth surface has a first end side and a second end side, wherein the first end side extends in a tooth trace direction on a base end side of the gear tooth; the second end edge extends in the tooth trace direction on the tip end side of the gear teeth,

the first end edge is longer than the second end edge.

4. A fishing reel drive gear according to claim 3,

a ratio of the first edge to the second edge is 1.28 or more.

5. A fishing reel drive gear according to claim 3 or 4, wherein the drive gear is a gear having a gear ring,

the tooth surface further having a third end edge and a fourth end edge, wherein the third end edge connects the first end edge and the second end edge radially inward of the gear teeth; the fourth end edge connects the first end edge and the second end edge radially outward of the gear teeth,

the third end is longer than the fourth end.

6. A fishing reel drive gear according to claim 5,

a ratio of the third edge to the fourth edge is 1.10 or more.

7. A fishing reel for fishing, characterized in that,

fishing reel body, handle and claimsThe drive gear of any of the above, wherein,

the handle is rotatably supported by the reel unit;

the drive gear is rotated by rotation of the handle.

Technical Field

The present invention relates to a drive gear for a fishing reel.

Background

The prior art drive gear has a plurality of gear teeth. Each gear tooth in the prior art has a pair of flanks. Each tooth face is meshed with a pinion (pinion gear). A rotational direction meshing line L1 and a plurality of simultaneous meshing contact lines L2 intersecting the rotational direction meshing line L1 are defined on each tooth face (refer to fig. 9 of the specification of the present application).

Here, the rotational direction meshing line L1 is a line formed by connecting the positions where the respective tooth flanks are highest on the plurality of simultaneous meshing contact lines L2. The plurality of simultaneous meshing contact lines L2 are each a line at which the pinion gear contacts the tooth face of the drive gear.

[ Prior art documents ]

[ patent document ]

Patent document 1: japanese patent application laid-open No. 6202796

Disclosure of Invention

[ problem to be solved by the invention ]

In the drive gear of the related art, the rotational direction meshing line L1 extends from the base end on the outer peripheral side on the gear teeth to the tooth tip on the inner peripheral side on the gear teeth.

In this state, when the pinion gear meshes with the tooth crests on the inner peripheral side of the gear teeth, that is, when the pinion gear meshes with the corner portions QR on the inner peripheral side of the tooth faces where the simultaneous meshing contact line L2 is short, stress concentration occurs at the tooth crests on the inner peripheral side of the gear teeth of the drive gear (corner portions QR in fig. 9).

In this case, a bending moment (bending moment) acting on the base end portions of the gear teeth may become large, and the gear teeth may be deformed. Accordingly, there is a fear that the drive gear cannot be smoothly rotated. Further, when the drive gear cannot smoothly rotate, there is a concern that an abnormal sound may be generated when the drive gear rotates while meshing with the pinion gear.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a drive gear for a fishing reel, which can improve a sense of rotation. Another object of the present invention is to provide a drive gear for a fishing reel that can suppress abnormal noise generated during rotation. [ solution for solving problems ]

A drive gear for a fishing reel according to an aspect of the present invention is a drive gear used for a fishing reel. The drive gear of the fishing reel has a disc portion and a plurality of gear teeth. The disc portion has a rotation axis. The plurality of gear teeth project from the outer peripheral side surface of the disk portion in a direction extending toward the rotation axis.

The gear teeth have a main body portion and an extended portion extending radially inward from the main body portion. A first angle formed by an axially outer side surface of the main body portion and a radially inner side surface of the extension portion is larger than the engagement pressure angle.

In the present drive gear, the extending portion extends radially inward from the main body portion in the gear teeth. Here, the first angle is larger than the engagement pressure angle. In this way, by providing the gear teeth with the extending portions, the first angle is made larger than the meshing pressure angle, and the stress generated at the inner peripheral side corner portions on the tooth tips of the gear teeth can be made smaller than that generated in the related art. Accordingly, the rotation feeling of the drive gear can be improved. In addition, by improving the rotation feeling of the drive gear, abnormal noise generated when the drive gear rotates can be suppressed.

In the fishing reel drive gear according to another aspect of the present invention, the first angle is larger than a second angle formed by the axially outer surface of the main body and the radially outer surface of the main body.

In this case, since the first angle is larger than the second angle, the rotation feeling of the drive gear can be appropriately improved. In addition, abnormal noise generated when the driving gear rotates can be properly restrained.

In the fishing reel drive gear according to another aspect of the present invention, the pair of tooth surfaces are formed on the main body portion and the extended portion at intervals in the circumferential direction. The tooth surface has a first end edge and a second end edge, wherein the first end edge extends in a tooth trace direction (tooth trace direction) on a base end side of the gear tooth; the second end edge extends in the tooth trace direction on the tip side of the gear teeth. The first end edge is longer than the second end edge.

In this case, since the first end side is longer than the second end side, deformation of the gear teeth can be suppressed. Accordingly, the rotation feeling of the drive gear can be appropriately improved. In addition, abnormal noise generated when the driving gear rotates can be properly restrained.

In the fishing reel drive gear according to another aspect of the present invention, the ratio of the first edge side to the second edge side is 1.28 or more. Accordingly, the rotation feeling of the drive gear can be further improved appropriately. In addition, abnormal noise generated when the driving gear rotates can be further properly restrained.

In the fishing reel drive gear according to another aspect of the present invention, the tooth surface further includes a third end edge and a fourth end edge, wherein the third end edge connects the first end edge and the second end edge on a radially inner side of the gear teeth; the fourth end edge connects the first end edge with the second end edge radially outward of the gear teeth. The third end side is longer than the fourth end side.

In this case, by making the third end longer than the fourth end, the simultaneous meshing contact line at the corner portion on the inner peripheral side on the tooth tip of the gear tooth can be made longer than in the related art. Accordingly, the rotation feeling of the drive gear can be appropriately improved. In addition, abnormal noise generated when the driving gear rotates can be properly restrained.

In the fishing reel drive gear according to another aspect of the present invention, the ratio of the third edge to the fourth edge is 1.10 or more. Accordingly, the rotation feeling of the drive gear can be further improved appropriately. In addition, abnormal noise generated when the driving gear rotates can be further properly restrained.

A fishing reel according to another aspect of the present invention includes a reel unit, a handle rotatably supported by the reel unit, and the drive gear; the drive gear is rotated by the rotation of the handle. The fishing reel can obtain the same effect as the above-mentioned driving gear.

[ Effect of the invention ]

According to the present invention, the rotation feeling of the drive gear of the fishing reel can be improved. In addition, abnormal noise generated when the driving gear of the fishing reel rotates can be restrained.

Drawings

Fig. 1 is a cross-sectional view of a spinning reel according to an embodiment of the present invention.

Fig. 2 is a sectional view of section line II of fig. 1.

Fig. 3 is an exploded perspective view of the rotor drive mechanism.

Fig. 4 is a plan view of the rotor driving mechanism.

Fig. 5 is a perspective view of the gear teeth of the drive gear.

Fig. 6A is a side view of the gear teeth of the drive gear.

Fig. 6B is a side view of the gear teeth of the drive gear.

Fig. 6C is a cross-sectional view of the section line VIC of fig. 5.

Fig. 7 is a cross-sectional view through plane C of fig. 6A through the engagement end point P.

Fig. 8A is a side view showing an area of gear teeth of the drive gear that is not used for meshing.

FIG. 8B is a side view showing a region of gear teeth of a drive gear of other embodiments that is not used for meshing.

Fig. 9 is a reference diagram for explaining the prior art.

[ description of reference numerals ]

11, driving a gear; 30: a circular plate portion; 31: gear teeth; 31 a: a first side surface; 31 b: a second side surface; 31 c: tooth crest; 31 d: a radially inner side surface; 31 e: a radially outer surface; 32: a main body portion; 33: an extension portion; b1: a first end edge; b2: a second end edge; b3: a third end edge; b4: a fourth end edge; a11, a 12: a first angle; a21, a 22: a second angle; b: the engagement pressure angle.

Detailed Description

As shown in fig. 1, a spinning reel 100 (an example of a fishing reel) according to an embodiment of the present invention includes a handle 1, a reel unit 2, a rotor 3, and a spool 4, wherein the reel unit 2 rotatably supports the handle 1. The rotor 3 is rotatably supported by the front portion of the reel unit 2.

The handle 1 has a handle shaft 1a, a handle arm 1b, and a handle grip 1 c. The drive shaft 10 is connected to the handle shaft 1a so as to be rotatable integrally with the handle shaft 1 a. The handle arm 1b is provided to the handle shaft 1 a. The handle grip 1c is provided to the handle arm 1 b. The handle 1 may be attached to either the left or right side of the reel unit 2.

A fishing line is wound around the outer peripheral surface of the spool 4. The spool 4 is disposed at the front of the rotor 3 so as to be movable in the front-rear direction. The spool 4 is mounted on the tip of the spool shaft 15. The spool shaft 15 has a spool axial center X1. The rotor 3 is connected to the pinion gear 12 so as to be rotatable integrally with the pinion gear 12. The rotor 3 is supported by the reel unit 2 so as to be rotatable with respect to the reel unit 2.

< Structure of reel unit >

As shown in fig. 1, the reel unit 2 includes a reel body 2a and a cover member 2b (fig. 2), wherein the reel body 2a has a storage space opened at a side portion therein; the cover member 2b is detachably attached to the reel body 2a, and closes the housing space of the reel body 2 a. The reel unit 2 includes a unit cover 26 that covers the rear portions of the reel body 2a and the cover member 2 b.

A fishing rod mounting leg 2c is integrally formed on the reel body 2 a. The reel body 2a is provided therein with a rotor drive mechanism 5 and a swing mechanism 6. The swing mechanism 6 is a mechanism for moving the spool shaft 15 in the front-rear direction. The spool 4 is moved in the front-rear direction by the operation of the swing mechanism 6. Since the structure of the swing mechanism 6 is substantially the same as that of the swing mechanism in the related art, the description thereof is omitted here.

< Structure of rotor drive mechanism >

The rotor driving mechanism 5 transmits the rotation of the handle 1 to the rotor 3. As shown in fig. 2 and 3, the rotor drive mechanism 5 has a drive gear 11 and a pinion gear 12. The drive gear 11 rotates integrally with the drive shaft 10. The pinion gear 12 meshes with the drive gear 11.

As shown in fig. 3, the pinion gear 12 has a cylindrical gear body 12a and a gear portion 12 b. The gear body 12a is disposed on the reel body 2a so as to intersect the handle shaft 1 a. Specifically, the gear body 12a is disposed on the reel body 2a so as to intersect with the rotation axis X of the drive gear 11.

The gear unit 12a is rotatably supported by the reel body 2 a. For example, the gear body 12a is rotatably supported by the reel body 2a via a bearing 14a and a bearing 14 b. The gear body 12a is formed with a through hole 12d through which the spool shaft 15 can be inserted.

The gear body 12a is formed with a male screw portion 12e and a rotation preventing flat surface 12 f. The male screw portion 12e and the rotation preventing flat surface 12f are engaged with the rotor 3, whereby the gear body 12a is connected to the rotor 3 so as to be rotatable integrally with the rotor 3. The gear portion 12b is formed in the gear main body 12 a.

As shown in fig. 2, the drive gear 11 is formed integrally with the drive shaft 10. The drive gear 11 may also be formed separately from the drive shaft 10. The drive shaft 10 is integrally rotated with the handle shaft 1a by screw coupling. The drive shaft 10 may be integrally rotated with the handle shaft 1a by non-circular engagement. The drive shaft 10 is rotatably attached to the reel body 2a via a bearing 27a attached to the cover member 2b and a bearing 27b attached to the reel body 2 a.

In the present embodiment, as shown in fig. 2, 3, and 4, the drive gear 11 is a face gear (face gear). The drive gear 11 has a disc portion 30 and a plurality of gear teeth 31. The disc portion 30 has a rotation axis X. The circular plate portion 30 is formed in a circular plate shape. The disc portion 30 is formed integrally with the drive shaft 10. The disc portion 30 may be formed separately from the drive shaft 10.

As shown in fig. 2 and 3, each of the plurality of gear teeth 31 protrudes from the outer peripheral side surface of the disk portion 30 in a direction extending toward the rotation axis X. For example, a plurality of gear teeth 31 are integrally formed on the outer peripheral side surface of the disk portion 30. The plurality of gear teeth 31 are formed at predetermined intervals in the circumferential direction on the outer peripheral side of one surface of the disk portion 30. The circumferential direction is a direction around the rotation axis X with the rotation axis X as a reference.

As shown in fig. 5, each gear tooth 31 has a main body portion 32 and an extended portion 33. The main body portion 32 forms a radially outer portion of the gear teeth 31. In detail, the body portion 32 forms a radially central portion and a radially outer portion. The main body portion 32 has a tooth crest 31c (an example of an axially outer surface) and a radially outer surface 31 e. The body portion 32 forms a part of the first side surface 31a and a part of the second side surface 31 b.

As shown in fig. 5, the extending portion 33 extends radially inward from the main body portion 32. The extension 33 forms a radially inner portion of the gear teeth 31. The extension 33 has a radially inner side surface 31 d. The extension 33 forms a part of the first side surface 31a and a part of the second side surface 31 b. The first side surface 31a and the second side surface 31b form a pair of side surfaces of the main body portion 32 and a pair of side surfaces of the extension portion 33.

In fig. 5, the boundary between the extension portion 33 and the main body portion 32 is indicated by a broken line. The plane indicated by the dotted line is perpendicular with respect to the circular plate portion 30. The plane passes through the tooth crest 31c and the corner portion of the radially inner side surface 31 d. In fig. 6B and 6C described later, the broken line also has the same meaning.

Each gear tooth 31 has a first side surface 31a, a second side surface 31b, a tooth top surface 31c, a radially inner side surface 31d, and a radially outer side surface 31 e. The first side surface 31a and the second side surface 31b exemplify a pair of tooth surfaces.

The first side surface 31a is a tooth surface that engages with the pinion gear 12 when the handle 1 is rotated in the wire winding direction. The second side surface 31b is a tooth surface that engages with the pinion gear 12 when the handle 1 is rotated in the wire releasing direction.

The first and second side surfaces 31a and 31b form a pair of side surfaces of the gear teeth 31. For example, the first side surface 31a and the second side surface 31b form a pair of side surfaces of the main body portion 32 and the extension portion 33. The first side surface 31a and the second side surface 31b are formed on the main body portion 32 and the extended portion 33 at intervals from each other in the circumferential direction. The first side surface 31a and the second side surface 31B each have a first end edge B1 and a second end edge B2.

The first end side B1 of the first side surface 31a extends in the tooth trace direction on the base end side of the gear tooth 31. The first end edge B1 of the first side surface 31a is formed by the corner portion of the first side surface 31a and the side surface of the circular plate portion 30.

The second end edge B2 of the first side surface 31a extends in the tooth trace direction on the tip end side of the gear teeth 31. The second end edge B2 of the first side surface 31a is formed by a corner of the first side surface 31a and the tooth top surface 31 c.

The first end side B1 of the second side surface 31B extends in the tooth trace direction on the base end side of the gear tooth 31. The first end edge B1 of the second side surface 31B is formed by the corner portion of the second side surface 31B and the side surface of the circular plate portion 30. The first end B1 of the second side surface 31B is circumferentially spaced apart from the first end B1 of the first side surface 31 a.

The second end edge B2 of the second side surface 31B extends in the tooth trace direction on the tip end side of the gear tooth 31. The second end edge B2 of the second side surface 31B is formed by the corner of the second side surface 31B and the tooth crest 31 c. The second end edge B2 of the second side surface 31B is circumferentially spaced apart from the second end edge B2 of the first side surface 31 a. It is also construed that the second end edge B2 of the first side surface 31a and the second end edge B2 of the second side surface 31B are also included in the tooth top 31 c.

The first and second side surfaces 31a and 31B also have third and fourth ends B3 and B4. The third end edge B3 of the first side surface 31a connects with the first end edge B1 of the first side surface 31a and the second end edge B2 of the first side surface 31a radially inward of the gear teeth 31. The third end edge B3 of the first side surface 31a is formed by a corner portion of the first side surface 31a and the radially inner side surface 31 d.

The fourth end edge B4 of the first side surface 31a connects with the first end edge B1 of the first side surface 31a and the second end edge B2 of the first side surface 31a radially outward of the gear teeth 31. The fourth end edge B4 of the first side surface 31a is formed by a corner portion of the first side surface 31a and the radially outer side surface 31 e.

The third end edge B3 of the second side surface 31B connects with the first end edge B1 of the second side surface 31B and the second end edge B2 of the second side surface 31B radially inward of the gear teeth 31. The third end edge B3 of the second side surface 31B is formed by a corner portion of the second side surface 31B and the radially inner side surface 31 d.

The third end B3 of the second side surface 31B is circumferentially spaced apart from the third end B3 of the first side surface 31 a. It can also be interpreted that the third end side B3 of the first side surface 31a and the third end side B3 of the second side surface 31B are also included in the radially inner side surface 31 d.

The fourth end edge B4 of the second side surface 31B connects with the first end edge B1 of the second side surface 31B and the second end edge B2 of the second side surface 31B radially outward of the gear teeth 31. The fourth end edge B4 of the second side surface 31B is formed by a corner portion of the second side surface 31B and the radially outer side surface 31 e.

The fourth end B4 of the second side surface 31B is disposed at a distance from the fourth end B4 of the first side surface 31a in the circumferential direction. It can also be interpreted that the fourth end B4 of the first side surface 31a and the fourth end B4 of the second side surface 31B are also included in the radially outer side surface 31 e.

The top land 31c forms the top end face of the gear teeth 31. For example, the tooth top surface 31c forms the tip end surface of the main body portion 32. The tooth crest 31c is connected with the radially inner side surface 31d and the radially outer side surface 31 e. The tooth top 31c is connected to the first and second side surfaces 31a and 31 b. In detail, the tooth crest 31c forms an outer surface of the gear tooth 31 (body portion 32) between the second end edge B2 of the first side surface 31a and the second end edge B2 of the second side surface 31B.

The radially inner side surface 31d forms an outer surface on the side of the gear teeth 31 close to the rotation axis X. For example, the radially inner side surface 31d forms a radially inner outer surface on the extension 33. The radially inner surface 31d is connected to the tooth crest 31c and the side surface of the circular plate portion 30. The radially inner side surface 31d is connected with the first side surface 31a and the second side surface 31 b. In detail, the radially inner side surface 31d forms an outer surface of the gear tooth 31 (the extension 33) between the third end side B3 of the first side surface 31a and the third end side B3 of the second side surface 31B.

The radially outer side surface 31e forms an outer surface on the side of the gear teeth 31 away from the rotational axis X. For example, the radially outer surface 31e forms a radially outer surface on the main body portion 32. The radially outer surface 31e is connected to the tooth crest 31c and the disk portion 30. The radially outer side surface 31e is connected with the first side surface 31a and the second side surface 31 b. In detail, the radially outer surface 31e forms an outer surface of the gear tooth 31 (body portion 32) between the fourth end B4 of the first side surface 31a and the fourth end B4 of the second side surface 31B.

The gear teeth 31 having the above-described structure are configured as follows. Fig. 6A and 6B are views of each gear tooth 31 as viewed from the outside in the circumferential direction R1 (see fig. 5).

As shown by the broken-line arrows in fig. 6A, the engagement pressure angle b gradually becomes smaller from the radially outer side to the radially inner side. For example, the engagement pressure angle B gradually decreases from the radially outer side to the radially inner side along the first end edge B1, from the first end edge B1 to the second end edge B2, and from the radially inner side along the second end edge B2.

In fig. 6A, the engagement end point is denoted by reference numeral P. Here, the intersection of the second end side B2 and the third end side B3 becomes the engagement end point P. The engagement end point P is a point at which the engagement pressure angle b becomes minimum. In FIG. 6A, a plane C is defined through the engagement end point P. The plane C passes through the engagement end point P, is perpendicular to the side surface of the circular plate portion 30, and extends in the circumferential direction R1.

Here, as shown in fig. 7, in a cross section of the gear tooth 31 cut by the plane C (see fig. 6A), the meshing pressure angle b is an angle formed by a plane P1 passing through the meshing end point P and being parallel to the circular plate portion 30 and a plane P2 (a normal line perpendicular to a line indicating the first side surface 31a in fig. 7) perpendicular to the first side surface 31a at the meshing end point P.

As shown in fig. 6B, the first angle a11 is larger than the engagement pressure angle B (refer to fig. 7). The first angle a11 is an angle formed by the cylindrical surface CP1 and the third end B3 around the rotation axis X2 when each gear tooth 31 is viewed from the outside in the circumferential direction R1 (see fig. 5). In addition, the first angle a11 is greater than the second angle a 21. The second angle a21 is an angle formed by the cylindrical surface CP2 and the fourth end B4 about the rotation axis X2. The cylindrical surfaces CP1, CP2 pass through the second end edge B2 (the tooth crest 31c of the main body portion 32).

Fig. 6C is a cross section of each gear tooth 31 taken by a surface extending in the axial direction (see a cutting line VIC in fig. 5) including the second end edge B2 on the first side surface 31a side on the tooth crest 31C. This plane (see the section line VIC in fig. 5) may be a plane perpendicular to the disk portion 30 and including the second end edge B2 of the tooth crest 31 c. When the second end edge B2 is a straight line, the plane (see the section line VIC in fig. 5) is a plane. In the case where the second end edge B2 is curved, the surface (see the section line VIC of fig. 5) is curved.

In the cross section of fig. 6C, the first angle a12 is larger than the engagement pressure angle b (see fig. 7). The first angle a12 is an angle formed by the cylindrical surface CP1 around the rotation axis center X2 and the radially inner side surface 31d of the extension 33. In addition, the first angle a12 is greater than the second angle a 22. The second angle a22 is an angle formed by the cylindrical surface CP2 around the rotation axis X2 and the radially outer surface 31e of the main body portion 32. The cylindrical surfaces CP1, CP2 pass through the tooth crest 31c (second end edge B2) of the main body portion 32.

In addition, as shown in fig. 6A and 6B, the first end edge B1 of the first side surface 31a is longer than the second end edge B2 of the first side surface 31 a. For example, the ratio of the first end edge B1 of the first side surface 31a to the second end edge B2 of the first side surface 31a is 1.28 or more. Specifically, it is preferable that the ratio of the first end edge B1 of the first side surface 31a to the second end edge B2 of the first side surface 31a is 1.28 or more and "1.50 or less".

Likewise, the first end edge B1 of the second side surface 31B is longer than the second end edge B2 of the second side surface 31B. For example, the ratio of the first end edge B1 of the second side surface 31B to the second end edge B2 of the second side surface 31B is 1.28 or more. Specifically, it is preferable that the ratio of the first end edge B1 of the second side surface 31B to the second end edge B2 of the second side surface 31B is 1.28 or more and "1.50 or less".

In addition, as shown in fig. 6A and 6B, the third end edge B3 of the first side surface 31a is longer than the fourth end edge B4 of the first side surface 31 a. For example, the ratio of the third end edge B3 of the first side surface 31a to the fourth end edge B4 of the first side surface 31a is 1.10 or more. Specifically, it is preferable that the ratio of the third end edge B3 of the first side surface 31a to the fourth end edge B4 of the first side surface 31a is 1.10 or more and "1.50 or less".

Likewise, the third end edge B3 of the second side surface 31B is longer than the fourth end edge B4 of the second side surface 31B. For example, the ratio of the third end edge B3 of the second side surface 31B to the fourth end edge B4 of the second side surface 31B is 1.10 or more. Specifically, the ratio of the third end edge B3 of the second side surface 31B to the fourth end edge B4 of the second side surface 31B is 1.10 or more and "1.50 or less".

In the drive gear 11 of the spinning reel 100, the extending portion 33 extends radially inward from the main body portion 32 in each gear tooth 31. Here, the first angles a11, a12 are greater than the engagement pressure angle b. In the prior art, the extending portion 33 is not formed on each gear tooth 31, and only the main body portion 32 is formed.

In this way, by providing the extending portion 33 in each gear tooth 31 and making the first angles a11, a12 larger than the meshing pressure angle b, the stress generated at the corner portion on the inner peripheral side on the tooth tip of each gear tooth 31, for example, the stress generated at the corner portion having the first angles a11, a12 can be made smaller than that generated in the related art.

This improves the rotation feeling of the drive gear 11. Further, by improving the rotation feeling of the drive gear 11, it is possible to suppress the generation of abnormal noise when the drive gear 11 rotates.

In addition, in the drive gear 11, the first angles a11, a12 are larger than the second angles a21, a 22. This can suitably improve the rotation feeling of the drive gear 11. In addition, abnormal noise generated when the drive gear 11 rotates can be appropriately suppressed.

In addition, in the drive gear 11, the first end side B1 is longer than the second end side B2. Specifically, in the drive gear 11, the ratio of the first end side B1 to the second end side B2 is 1.28 or more. Accordingly, deformation of each gear tooth 31 can be suppressed. This can further suitably improve the turning feeling of the drive gear 11. In addition, the generation of abnormal noise generated when the drive gear 11 rotates can be further appropriately suppressed.

Further, in the drive gear 11, the third end side B3 is longer than the fourth end side B4. Specifically, in the drive gear 11, the ratio of the third end B3 to the fourth end B4 is 1.10 or more. This can further suitably improve the turning feeling of the drive gear 11. In addition, the generation of abnormal noise generated when the drive gear 11 rotates can be further appropriately suppressed.

< other embodiment >

While one embodiment of the present invention has been described above, the present invention is not limited to the above embodiment, and various modifications can be made without departing from the scope of the invention. In particular, the plurality of embodiments and modifications described in the present specification can be combined as desired.

(a) The drive gear 11 of the above embodiment may be formed by die forming, machining, or pressing.

(b) In the above embodiment, the spinning reel 100 is described as the fishing reel, but the present invention is also applicable to other fishing reels.

(c) In the above embodiment, an example of a case where the engagement end point P is an intersection of the second end side B2 and the third end side B3 is shown. In this case, for example, as shown in fig. 8A, a region NR1 (a dotted line region) not used for engagement is formed on the first side surface 31a except for the intersection of the second end edge B2 and the third end edge B3.

In contrast, as shown in fig. 8B, a region NR2 (dashed line region) not used for engagement may be formed on the first side surface 31a including the intersection of the second end side B2 and the third end side B3. In this case, the engagement end point P is formed on the second end side B2 except for the intersection of the second end side B2 and the third end side B3.

As such, the engagement end point P is disposed on the second end side B2 at a position away from the regions NR1, NR2 (dashed line regions) not used for engagement. Even if structured as above, the gear teeth 31 are formed in the same manner as the above-described embodiment in the relationship of the first angles a11, a12, the second angles a21, a22, and the meshing pressure angle b.