JP2017018062A

JP2017018062A - Inversion prevention mechanism for fishing reel

Info

Publication number: JP2017018062A
Application number: JP2015140543A
Authority: JP
Inventors: 諒永井; Makoto Nagai
Original assignee: Globeride Inc
Current assignee: Globeride Inc
Priority date: 2015-07-14
Filing date: 2015-07-14
Publication date: 2017-01-26
Anticipated expiration: 2035-07-14
Also published as: JP6560551B2

Abstract

PROBLEM TO BE SOLVED: To provide an inversion prevention mechanism having a relatively high freedom degree of a design, capable of surely maintaining an inversion prevention performance and achieving smooth winding rotation operation property.SOLUTION: An inversion prevention mechanism for a fishing reel comprises: an inversion prevention gear 12; an inversion prevention claw 20 which is engaged to the inversion prevention gear 12; and a cam 30 for performing control so as to engage and disengage the inversion prevention claw 20 to/from the inversion prevention gear 12. The cam 30 comprises: a friction holding body 31 which holds a rotor 10, and rotates with the rotor 10 by friction force with the rotor 10; and an energization member 32 which energizes the friction holding body 31 in a direction where holding force thereof is increased. The friction holding body 31 comprises: two holding parts 33, 34 for holding the rotor 10; a connection part 35 for connecting the two holding parts 33, 34 so as to be opened and closed freely; and an engagement part 36 formed on one of the two holding parts 33, 34 and engaged to the inversion prevention claw 20.SELECTED DRAWING: Figure 6

Description

本発明は、魚釣用リールの逆転防止機構に関する。 The present invention relates to a mechanism for preventing reverse rotation of a fishing reel.

魚釣用リールには、ロータの釣糸の繰り出し方向への回転（以下、「逆転」と称する）を規制するため、ハンドル軸や駆動軸筒などの回転体の逆転を防止する逆転防止機構が設けられている。
このような逆転防止機構は、一般に、回転体と一体に回転する逆転防止歯車と、回転体の逆転時に逆転防止歯車に係合する逆転防止爪とを備えている。 The fishing reel is provided with a reverse rotation prevention mechanism for preventing the rotation of the rotating body such as the handle shaft and the drive shaft cylinder in order to restrict the rotation of the rotor in the feeding direction of the fishing line (hereinafter referred to as “reverse rotation”). It has been.
Such a reverse rotation prevention mechanism generally includes a reverse rotation prevention gear that rotates integrally with the rotating body, and a reverse rotation prevention claw that engages with the reverse rotation preventing gear when the rotating body rotates in reverse.

また、特許文献１の逆転防止機構では、上記した逆転防止歯車と逆転防止爪の他に、ロータの釣糸の巻き取り方向への回転（以下、「正転」と称する）時に逆転防止爪を起こすカムが設けられている。
このカムによれば、ハンドル操作により回転体が正転すると、逆転防止歯車の歯の軌道上から逆転防止爪が離脱した状態になり、逆転防止爪が逆転防止歯車の歯を乗り越した際に接触音が発生するという問題が回避される。 Further, in the reverse rotation prevention mechanism of Patent Document 1, in addition to the above-described reverse rotation prevention gear and the reverse rotation prevention pawl, the reverse rotation prevention pawl is raised when the rotor rotates in the winding direction of the fishing line (hereinafter referred to as “forward rotation”). A cam is provided.
According to this cam, when the rotating body is rotated forward by the handle operation, the anti-reverse pawl is detached from the tooth trajectory of the anti-reverse gear, and contact is made when the anti-reverse pawl passes over the teeth of the anti-reverse gear. The problem of generating sound is avoided.

ところで、特許文献１のカムは、回転体に挟着して回転体との摩擦力により回転体とともに回転する摩擦挟着体と、摩擦挟着体の挟着力が増す方向に付勢するコイルスプリング（弾性体）とで構成されている。また、特許文献１の摩擦挟着体は、回転体を挟む２つの挟着部と、２つの挟着部を開閉自在に連結する連結部とを備え、この連結部が径方向外側に位置して逆転防止爪と係合する突起を成している。
これによれば、弾性体によって摩擦挟着体と回転体との間に摩擦力が作用するようになる。この結果、逆転防止爪を起こす際に突起が逆転防止爪から反力を受けるものの、カムが回転体とともに正転するようになり、確実に逆転防止爪を起こすことができる。
なお、カムが逆転防止爪を起こした後は、突起が逆転防止爪に係合し続け、カムの正転が規制される。 By the way, the cam of Patent Document 1 includes a friction sandwiching body that is sandwiched between the rotating body and rotates together with the rotating body by a frictional force with the rotating body, and a coil spring that biases in a direction in which the sandwiching force of the friction sandwiching body increases. (Elastic body). Further, the friction sandwiched body of Patent Document 1 includes two sandwiched portions that sandwich the rotating body, and a coupling portion that couples the two sandwiched portions so as to be openable and closable, and this coupled portion is located on the radially outer side. And a protrusion that engages with the reverse rotation prevention claw.
According to this, a frictional force comes to act between the friction sandwiching body and the rotating body by the elastic body. As a result, when the reverse rotation preventing claw is raised, the protrusion receives a reaction force from the reverse rotation prevention claw, but the cam comes to rotate forward together with the rotating body, and the reverse rotation prevention claw can be surely raised.
In addition, after the cam raises the reverse rotation prevention claw, the projection continues to engage with the reverse rotation prevention claw, and the forward rotation of the cam is restricted.

特開２００３−２５０４０１号公報JP 2003-250401 A

しかしながら、巻取回転操作時（正転時）において、突起が逆転防止爪に係合し続けた状態で回転体に作用するカムの摩擦力は、２つの挟着部の連結部が逆転防止爪に係合する構成のため、弾性体による弾性力（２つの挟着部の挟着力）を低減させる方向に作用する力が弱い。このため、結果的には、安定した逆転防止性能は得られるものの、回転体の軽快な正転による巻き取り操作性が得られない。
更に、従来技術によれば、連結部を逆転防止爪に対する切り替え制御部として機能させているため、リール本体の大小、駆動部の位置等より切り替え制御部の位置やサイズ的な制約を受け易く、設計の自由度が限定される。 However, during the winding rotation operation (forward rotation), the frictional force of the cam that acts on the rotating body while the protrusion continues to engage with the reverse rotation prevention claw is such that the connecting portion of the two sandwiched portions is the reverse rotation prevention claw. Therefore, the force acting in the direction of reducing the elastic force by the elastic body (the clamping force of the two clamping parts) is weak. For this reason, as a result, although stable reverse rotation prevention performance can be obtained, winding operability due to light forward rotation of the rotating body cannot be obtained.
Furthermore, according to the prior art, because the connecting portion functions as a switching control unit for the reverse rotation prevention claw, the position and size of the switching control unit are easily affected by the size of the reel body, the position of the drive unit, etc. The degree of freedom of design is limited.

本発明は、このような課題を解決するために創作されたものであり、設計の自由度が比較的高い逆転防止機構であって、確実な逆転防止性能の維持を図りながら軽快な巻き取り回転操作性を実現することを目的とする。 The present invention was created in order to solve such problems, and is a reverse rotation prevention mechanism having a relatively high degree of freedom in design, and a simple winding rotation while maintaining reliable reverse rotation prevention performance. The purpose is to realize operability.

前記課題を解決するため、本発明に係る魚釣用リールの逆転防止機構は、ハンドル操作により回転する回転体に設けられた逆転防止歯車と、前記逆転防止歯車に係合する逆転防止爪と、前記回転体の回転方向に応じて前記逆転防止歯車に前記逆転防止爪を係脱制御するカムと、を備えた魚釣用リールの逆転防止機構であって、前記カムは、前記回転体に挟着し、前記回転体との摩擦力により前記回転体とともに回転する摩擦挟着体と、前記摩擦挟着体の挟着力が増す方向に付勢する付勢部材と、を備え、前記摩擦挟着体は、前記回転体を挟む２つの挟着部と、前記２つの挟着部を開閉自在に連結する連結部と、前記２つの挟着部の一方に形成されて前記逆転防止爪と係合する係合部と、を備えていることを特徴とする。 In order to solve the above-described problem, a fishing reel reverse rotation prevention mechanism according to the present invention includes a reverse rotation prevention gear provided on a rotating body that rotates by a handle operation, a reverse rotation prevention claw that engages with the rotation prevention gear, A reverse rotation prevention mechanism for a fishing reel comprising a cam for engaging and disengaging the reverse rotation prevention pawl to and from the reverse rotation prevention gear according to the rotation direction of the rotation body, wherein the cam is sandwiched between the rotation bodies. A friction clamping body that is attached and rotates together with the rotating body by a frictional force with the rotating body, and a biasing member that biases the friction clamping body in a direction in which the clamping force of the friction clamping body increases. The body is formed on one of the two sandwiching portions and is engaged with the reverse rotation preventing claw, the two sandwiching portions sandwiching the rotating body, the connecting portion coupling the two sandwiching portions so as to be freely opened and closed And an engaging portion.

前記発明によれば、ハンドル操作により回転体及びカムが回転し、カムの係合部が逆転防止爪に係合した場合にカムの回転が規制される。そして、ハンドル操作により回転体が更に回転すると、係合方向（押圧方向）と逆方向の反力が係合部に作用する。言い換えれば、係合部が設けられた一方の挟着部は、連結部を支点として開く方向又は閉じる方向への荷重を受ける。
ここで、一方の挟着部が開く方向への荷重を受ける場合、摩擦挟着体と回転体との摩擦力が低減し、巻取方向のハンドル操作を軽くすることができる。
他方、一方の挟着部が閉じる方向への荷重を受ける場合、摩擦挟着体と回転体との摩擦力が増加し、釣糸の繰出しに伴う逆転防止を確実に機能させることができる。
以上、前記発明によれば、逆転防止爪との係合の前後において摩擦挟着体と回転体との摩擦力を変化させることで、ハンドル操作性を変えることができる。
また、前記発明によれば、係合部に係合部逆転防止爪に対する切り替え制御部として機能させている。このため、連結部を設計する際の制約が低減して逆転防止機構の設計の自由度が向上する。 According to the invention, when the rotating body and the cam are rotated by the handle operation and the cam engaging portion is engaged with the reverse rotation preventing claw, the rotation of the cam is restricted. When the rotating body further rotates by the handle operation, a reaction force opposite to the engaging direction (pressing direction) acts on the engaging portion. In other words, one clamping part provided with the engaging part receives a load in the opening direction or the closing direction with the connecting part as a fulcrum.
Here, when receiving a load in the direction in which one of the sandwiching portions opens, the frictional force between the friction sandwiching body and the rotating body is reduced, and the handle operation in the winding direction can be lightened.
On the other hand, when a load is applied in the direction in which one of the sandwiched portions closes, the frictional force between the friction sandwiched body and the rotating body increases, and the reverse rotation prevention associated with the feeding of the fishing line can be reliably functioned.
As described above, according to the present invention, the handle operability can be changed by changing the frictional force between the friction clamping body and the rotating body before and after the engagement with the reverse rotation preventing claw.
Moreover, according to the said invention, the engaging part is made to function as a switching control part with respect to an engaging part reverse rotation prevention nail | claw. For this reason, the restriction | limiting at the time of designing a connection part reduces, and the freedom degree of design of a reverse rotation prevention mechanism improves.

また、前記係合部が設けられる前記一方の挟着部は、前記連結部に対して正転方向に配置されていることが好ましい。 Moreover, it is preferable that said one clamping part provided with the said engaging part is arrange | positioned in the normal rotation direction with respect to the said connection part.

前記構成によれば、ハンドル操作により回転体が正転した場合、挟着部は開く方向に移動する荷重を受け、回転体との摩擦力が低減する。よって、回転体及びロータはスムーズに回転する。
一方で、ロータが逆転しようとすると、一方の挟着部が閉じる方向への反力を受け、回転体との摩擦力が増加する。よって、逆転防止爪から反力を受けても空転することなく、確実に回転して逆転防止爪を押圧する（回動させる）ことができる。 According to the above configuration, when the rotating body is rotated forward by the handle operation, the clamping portion receives a load that moves in the opening direction, and the frictional force with the rotating body is reduced. Therefore, the rotating body and the rotor rotate smoothly.
On the other hand, when the rotor tries to reverse, the reaction force in the direction in which one clamping part closes receives a frictional force with the rotating body. Therefore, even if a reaction force is received from the reverse rotation preventing claw, the reverse rotation preventing claw can be reliably rotated and pressed (turned) without idling.

また、前記係合部は、前記一方の挟着部の径方向外側に突出した突起で形成されて、前記逆転防止爪の凹部からなる被係合部に係合することように構成してもよい。 Further, the engaging portion may be formed by a protrusion protruding outward in the radial direction of the one sandwiched portion and engaged with an engaged portion formed by a recess of the reverse rotation preventing claw. Good.

また、前記係合部は、前記一方の挟着部の先端側に位置していることが好ましい。 Moreover, it is preferable that the engaging part is located on a tip side of the one sandwiching part.

前記構成によれば、逆転防止爪から反力を受ける係合部（力点）と連結部（支点）との距離が長くなり、挟着部（作用点）に作用する荷重が大きくなる。よって、より効果的に摩擦力を変化させることができる。 According to the said structure, the distance of the engaging part (force point) which receives reaction force from a reverse rotation prevention nail | claw and a connection part (fulcrum) becomes long, and the load which acts on a clamping part (action point) becomes large. Therefore, the frictional force can be changed more effectively.

前記する発明によれば、逆転防止機構の設計の自由度が比較的高く、確実な逆転防止性能の維持を図りながら軽快な巻き取り回転操作性を実現することをできる。 According to the above-described invention, the degree of freedom in designing the reverse rotation prevention mechanism is relatively high, and light winding and rotating operability can be realized while maintaining reliable reverse rotation prevention performance.

実施形態の逆転防止機構を備えた魚釣用スピニングリールの概略図である。It is the schematic of the spinning reel for fishing provided with the reverse rotation prevention mechanism of embodiment. リール本体の前方から視た逆転防止機構の正面図である。It is a front view of the reverse rotation prevention mechanism seen from the front of the reel body. 図２のＩＩＩ−ＩＩＩ線矢視断面図である。FIG. 3 is a cross-sectional view taken along line III-III in FIG. 2. リール本体と駆動軸筒とカムとを分解した分解斜視図である。It is the disassembled perspective view which decomposed | disassembled the reel main body, the drive shaft cylinder, and the cam. カムの分解斜視図である。It is a disassembled perspective view of a cam. 図３のＶＩ−ＶＩ線矢視断面図であり、切り替えレバーが逆転許可状態に設定された場合を示す断面図である。FIG. 4 is a cross-sectional view taken along the line VI-VI in FIG. 3 and is a cross-sectional view showing a case where a switching lever is set in a reverse rotation permission state. 図６の状態から、切り替えレバーが逆転防止状態に設定された場合を示す断面図である。It is sectional drawing which shows the case where the switching lever is set to the reverse rotation prevention state from the state of FIG. 図７の状態から駆動軸筒が逆転し、逆転防止歯車と逆転防止爪が係合した状態を示す断面図である。FIG. 8 is a cross-sectional view showing a state in which the drive shaft cylinder is reversed from the state of FIG. 7 and the reverse rotation prevention gear and the reverse rotation prevention pawl are engaged. 図８の状態から駆動軸筒が正転した状態を示す断面図である。FIG. 9 is a cross-sectional view showing a state where the drive shaft cylinder is rotated forward from the state of FIG. 8. 図９の状態から駆動軸筒がさらに正転し、逆転防止歯車と逆転防止爪との係合が解除された状態を示す断面図である。FIG. 10 is a cross-sectional view illustrating a state in which the drive shaft cylinder further rotates forward from the state of FIG. 9 and the engagement between the reverse rotation prevention gear and the reverse rotation prevention pawl is released. （ａ）は係合部及び被係合部の第１変形例を示す図、（ｂ）は係合部及び被係合部の第２変形例を示す図である。(A) is a figure which shows the 1st modification of an engaging part and a to-be-engaged part, (b) is a figure which shows the 2nd modification of an engaging part and a to-be-engaged part. （ａ）は摩擦挟着体の第１変形例を示す図、（ｂ）は摩擦挟着体の第２変形例を示す図、（ｃ）は摩擦挟着体の第３変形例を示す図、（ｄ）は摩擦挟着体の第４変形例を示す図である。(A) is a figure which shows the 1st modification of a friction clamping body, (b) is a figure which shows the 2nd modification of a friction clamping body, (c) is a figure which shows the 3rd modification of a friction clamping body. (D) is a figure which shows the 4th modification of a friction clamping body. （ａ）は摩擦挟着体の第５変形例を示す図、（ｂ）は図１３（ａ）のＸＩＩＩＢ−ＸＩＩＩＢ線矢視断面図、（ｃ）は摩擦挟着体の第６変形例を示す図、（ｄ）は図１３（ｃ）のＸＩＩＩＤ−ＸＩＩＩＤ線矢視断面図である。(A) is a figure which shows the 5th modification of a friction clamping body, (b) is XIIIB-XIIIB sectional view taken on the line of FIG. 13 (a), (c) is the 6th modification of a friction clamping body. The figure to show, (d) is XIIID-XIIID arrow sectional drawing of FIG.13 (c).

本実施形態に係る逆転防止機構を備えた魚釣用スピニングリールについて、適宜図面を参照しながら説明する。なお、本発明の逆転防止機構は、魚釣用スピニングリールに限定されず、ベイトリールに適用してもよい。また、実施形態の説明において、「前後」及び「上下」を言うときは図１に示した方向を基準とし、「左右」を言うときは図２に示した方向を基準とする。 A fishing spinning reel provided with a reverse rotation prevention mechanism according to the present embodiment will be described with reference to the drawings as appropriate. The reverse rotation prevention mechanism of the present invention is not limited to a fishing spinning reel, and may be applied to a bait reel. In the description of the embodiment, when referring to “front and back” and “up and down”, the direction shown in FIG. 1 is used as a reference, and when saying “left and right”, the direction shown in FIG. 2 is used as a reference.

図１に示すように、魚釣用スピニングリール１は、前後方向に延びるスプール軸８及び駆動軸筒１０を有するリール本体２と、駆動軸筒１０の前端部に固定されたロータ３と、スプール軸８の前端部に取り付けられたスプール４とを主に備えている。
以下、スプール軸８の中心軸Ｏを単に「中心軸Ｏ」と称する。 As shown in FIG. 1, a fishing spinning reel 1 includes a reel body 2 having a spool shaft 8 and a drive shaft cylinder 10 extending in the front-rear direction, a rotor 3 fixed to the front end of the drive shaft cylinder 10, and a spool. A spool 4 attached to the front end of the shaft 8 is mainly provided.
Hereinafter, the center axis O of the spool shaft 8 is simply referred to as “center axis O”.

リール本体２は、内部空間が形成され、上部に釣竿に装着される脚部２ａが形成された部品である。
リール本体２はハンドル軸５を回転自在に支持し、リール本体２内をハンドル軸５が左右方向に延在している。
ハンドル軸５には歯車５ａとドライブギヤ６とが連結し、ハンドル軸５の回転により歯車５ａ及びドライブギヤ６が回転する。
なお、ハンドル軸５の端部は、リール本体２を貫通してリール本体２の側部に配置され、その端部にハンドル（不図示）が取り付けられている。 The reel body 2 is a component in which an internal space is formed and a leg portion 2a to be attached to a fishing rod is formed at the top.
The reel body 2 rotatably supports the handle shaft 5, and the handle shaft 5 extends in the left-right direction within the reel body 2.
A gear 5 a and a drive gear 6 are connected to the handle shaft 5, and the gear 5 a and the drive gear 6 are rotated by the rotation of the handle shaft 5.
Note that an end portion of the handle shaft 5 passes through the reel body 2 and is disposed on a side portion of the reel body 2, and a handle (not shown) is attached to the end portion.

図２〜図４に示すように、リール本体２の前部には、リール本体２の前面から前方に突出する筒部２ｂが設けられている。この筒部２ｂは、略円筒状に形成され、かつ、リール本体２と一体に形成されている。
なお、本発明の筒部２ｂは、実施形態で示すリール本体２と一体に形成されたものに限定されず、リール本体２と別体に形成されて接着、螺合又は締結具等によりリール本体２と一体になったものであってもよい。また、本発明の筒部２ｂの形状は、円筒状に限定されず、非円形であってもよく、特に限定されない。 As shown in FIGS. 2 to 4, the front portion of the reel body 2 is provided with a cylindrical portion 2 b that protrudes forward from the front surface of the reel body 2. The cylindrical portion 2 b is formed in a substantially cylindrical shape and is formed integrally with the reel body 2.
The cylindrical portion 2b of the present invention is not limited to one formed integrally with the reel body 2 shown in the embodiment, and is formed separately from the reel body 2 and bonded, screwed, or fastened by a fastener or the like. 2 may be integrated. Moreover, the shape of the cylinder part 2b of this invention is not limited to a cylindrical shape, A non-circular shape may be sufficient and it is not specifically limited.

図２に示すように、筒部２ｂには、後述するねじ４０、４１（図２において不図示。図３参照）を取り付けるために、筒部２ｂから左上方向に突出して前端面にねじ穴２ｆが形成された第１ボス部２ｃと、筒部２ｂから右下方向に突出して前端面に貫通孔２ｇが形成された第２ボス部２ｄとが形成されている。
図３に示すように、貫通孔２ｇの延長線上にねじ穴２ｉが形成され、ねじ４１は、貫通孔２ｇを貫通してねじ穴２ｉに螺合して固定されるようになっている。
そのほか、ねじ４１には、ねじ４１回りに回動自在な円筒部材４２が外嵌されている。 As shown in FIG. 2, in order to attach screws 40 and 41 (not shown in FIG. 2; see FIG. 3), which will be described later, to the cylindrical portion 2 b, it protrudes from the cylindrical portion 2 b in the upper left direction and has a screw hole 2 f on the front end surface. Are formed, and a second boss portion 2d is formed which protrudes from the cylindrical portion 2b in the lower right direction and has a through hole 2g formed in the front end surface.
As shown in FIG. 3, a screw hole 2i is formed on the extension line of the through hole 2g, and the screw 41 is fixed by being screwed into the screw hole 2i through the through hole 2g.
In addition, a cylindrical member 42 that is rotatable around the screw 41 is fitted on the screw 41.

図３に示すように、第２ボス部２ｄには、筒部２ｂの内部と外部とを連通する開口部２ｅが形成されている。そして、開口部２ｅ内には、ねじ４１と円筒部材４２とが前後方向に延在するとともに、後述する逆転防止爪２０が配置されている。 As shown in FIG. 3, the 2nd boss | hub part 2d is formed with the opening part 2e which connects the inside and the exterior of the cylinder part 2b. And in the opening part 2e, the screw 41 and the cylindrical member 42 are extended in the front-back direction, and the reverse rotation prevention nail | claw 20 mentioned later is arrange | positioned.

図２、図４に示すように、第２ボス部２ｄには、筒部２ｂ内と貫通孔２ｇ内とを連通する切り欠き溝２ｈが形成されている。切り欠き溝２ｈは、後述するカム３０を筒部２ｂ内に収容する際に、カム３０の突起３６を挿通させるためのものであり、筒部２ｂの前端面から開口部２ｅまで連続している。
次に、筒部２ｂ内に収容されるスプール軸８と駆動軸筒１０とについて説明する。 As shown in FIGS. 2 and 4, the second boss portion 2d is formed with a notch groove 2h that communicates the inside of the cylindrical portion 2b and the inside of the through hole 2g. The notch groove 2h is for inserting a protrusion 36 of the cam 30 when the cam 30 described later is accommodated in the cylinder 2b, and is continuous from the front end surface of the cylinder 2b to the opening 2e. .
Next, the spool shaft 8 and the drive shaft cylinder 10 accommodated in the cylinder portion 2b will be described.

図４に示すように、駆動軸筒１０は、略円筒状の部材であり、筒部２ｂの前方から筒部２ｂ内に収容される。
図３に示すように、駆動軸筒１０は、後端がリール本体２に形成された軸受部１０ａに支持され、前部が筒部２ｂに内嵌された軸受１０ｂに支持されている。よって、駆動軸筒１０は、筒部２ｂ内に回転自在に支持されている。
なお、ねじ４０、４１の頭部のそれぞれが軸受１０ｂに当接し、軸受１０ｂが脱落しないように保持されている。 As shown in FIG. 4, the drive shaft cylinder 10 is a substantially cylindrical member, and is accommodated in the cylinder part 2b from the front of the cylinder part 2b.
As shown in FIG. 3, the drive shaft cylinder 10 is supported by a bearing portion 10a formed on the reel body 2 at the rear end, and supported by a bearing 10b fitted inside the cylinder portion 2b. Therefore, the drive shaft cylinder 10 is rotatably supported in the cylinder portion 2b.
Each of the heads of the screws 40 and 41 is in contact with the bearing 10b and is held so that the bearing 10b does not fall off.

駆動軸筒１０の外周面には、後方から前方に向って、ピニオン１１、逆転防止歯車１２、カム収容溝１３、凸部１４、ロータ非円形嵌合面１５、ねじ部１６が形成されている。 A pinion 11, a reverse rotation preventing gear 12, a cam housing groove 13, a convex portion 14, a rotor non-circular fitting surface 15, and a screw portion 16 are formed on the outer peripheral surface of the drive shaft cylinder 10 from the rear to the front. .

ピニオン１１は、駆動軸筒１０と一体に形成された歯車であり、ドライブギヤ６と噛合している。よって、ハンドル操作によりドライブギヤ６が回転すると、ピニオン１１を介して駆動力が駆動軸筒１０に伝達し、駆動軸筒１０が回転する。
また、ロータ非円形嵌合面１５には、ロータ３の固定部３ａが回り止め外嵌され、ロータ３と駆動軸筒１０とが一体になっている。このため、駆動軸筒１０とロータ３とが同方向に回転（正転、逆転）する。
なお、ロータ３の固定部３ａは、ねじ部１６に螺合するナットＮにより締め付けられ、脱落しないように保持されている。 The pinion 11 is a gear formed integrally with the drive shaft cylinder 10 and meshes with the drive gear 6. Therefore, when the drive gear 6 is rotated by the handle operation, the driving force is transmitted to the drive shaft cylinder 10 via the pinion 11, and the drive shaft cylinder 10 is rotated.
Further, the fixed portion 3a of the rotor 3 is non-rotatably fitted to the rotor non-circular fitting surface 15, and the rotor 3 and the drive shaft cylinder 10 are integrated. For this reason, the drive shaft cylinder 10 and the rotor 3 rotate (forward rotation, reverse rotation) in the same direction.
The fixed portion 3a of the rotor 3 is tightened by a nut N that is screwed into the screw portion 16, and is held so as not to drop off.

また、本実施形態では、駆動軸筒１０及びロータ３の正転、逆転との関係については、次のようになっている。
正転とは、ハンドルの巻き取り操作が行われてロータ３が釣糸の巻き取り方向へ回転する場合であり、本実施形態では、前方から視て時計回りに駆動軸筒１０及びロータ３が回転する場合である（図２の矢印Ａ参照）。
逆転とは、前方から視て反時計回りに駆動軸筒１０及びロータ３が回転する場合である（図２の矢印Ｂ参照）。 In the present embodiment, the relationship between the forward rotation and the reverse rotation of the drive shaft cylinder 10 and the rotor 3 is as follows.
The forward rotation is a case where the handle winding operation is performed and the rotor 3 rotates in the fishing line winding direction. In this embodiment, the drive shaft cylinder 10 and the rotor 3 rotate clockwise as viewed from the front. (See arrow A in FIG. 2).
The reverse rotation is a case where the drive shaft cylinder 10 and the rotor 3 rotate counterclockwise as viewed from the front (see arrow B in FIG. 2).

カム収容溝１３は、駆動軸筒１０に挟着するカム３０を前後方向に移動しないように規制するための凹状の溝である。カム収容溝１３は、逆転防止歯車１２の前側に形成され、カム３０と逆転防止歯車１２とが前後方向に隣り合っている。
なお、カム３０と逆転防止歯車１２との詳細については後述する。 The cam housing groove 13 is a concave groove for regulating the cam 30 sandwiched between the drive shaft cylinders 10 so as not to move in the front-rear direction. The cam accommodation groove 13 is formed on the front side of the reverse rotation prevention gear 12, and the cam 30 and the reverse rotation prevention gear 12 are adjacent to each other in the front-rear direction.
Details of the cam 30 and the reverse rotation prevention gear 12 will be described later.

図１に示すように、スプール軸８の前端部には、スプール４が装着されている。一方で、スプール軸８の後端部には、スプール軸８を前後動させるためのスプール往復動装置と連結している。 As shown in FIG. 1, a spool 4 is attached to the front end portion of the spool shaft 8. On the other hand, the rear end portion of the spool shaft 8 is connected to a spool reciprocating device for moving the spool shaft 8 back and forth.

スプール往復動装置は、歯車５ａに噛合する連動歯車５ｂと、連動歯車５ｂに設けられた偏芯突部５ｃと、スプール軸８の後端部に取り付けられるとともに偏芯突部５ｃと係合する案内溝９ａが形成された摺動子９とを備えている。
上記構成によれば、ハンドルの巻き取り操作が行われると、ハンドル操作の駆動力がスプール往復動装置に伝達されてスプール４が前後動し、図示しない釣糸がスプール４に平行かつ均等に巻回される。 The spool reciprocating device is attached to the interlocking gear 5b meshing with the gear 5a, the eccentric protrusion 5c provided on the interlocking gear 5b, and the rear end portion of the spool shaft 8, and engages with the eccentric protrusion 5c. And a slider 9 in which a guide groove 9a is formed.
According to the above configuration, when the winding operation of the handle is performed, the driving force of the steering operation is transmitted to the spool reciprocating device, the spool 4 moves back and forth, and the fishing line (not shown) is wound on the spool 4 in a parallel and even manner. Is done.

つぎに、本実施形態の逆転防止機構（逆転防止歯車１２と逆転防止爪２０とカム３０）について説明する。 Next, the reverse rotation prevention mechanism (the reverse rotation prevention gear 12, the reverse rotation prevention claw 20, and the cam 30) of this embodiment will be described.

図６に示すように、逆転防止歯車１２は、駆動軸筒１０と一体に形成されたのこぎり歯（ラチェット）の歯車である。
逆転防止歯車１２の歯形は、正転方向（矢印Ａ参照）の歯面が斜面１２ａを構成し、逆転方向（矢印Ｂ参照）の歯面が駆動軸筒１０の径方向に延びる縦壁面１２ｂを構成している。 As shown in FIG. 6, the reverse rotation prevention gear 12 is a sawtooth gear formed integrally with the drive shaft cylinder 10.
As for the tooth profile of the reverse rotation preventing gear 12, the tooth surface in the forward rotation direction (see arrow A) constitutes the inclined surface 12a, and the tooth surface in the reverse rotation direction (see arrow B) has the vertical wall surface 12b extending in the radial direction of the drive shaft cylinder 10. It is composed.

逆転防止爪２０は、筒部２ｂの開口部２ｅ内に配置されて、筒部２ｂ内の逆転防止歯車１２とカム３０とに対向する部品である。逆転防止爪２０は、円筒部材４２に装着され、ねじ４１回りに回動自在に抜け止めした状態で設けられている。 The reverse rotation preventing claw 20 is a component that is disposed in the opening 2e of the cylindrical portion 2b and faces the reverse rotation preventing gear 12 and the cam 30 in the cylindrical portion 2b. The reverse rotation preventing claw 20 is attached to the cylindrical member 42 and is provided in a state in which the reverse rotation preventing claw 20 is rotatably prevented around the screw 41.

逆転防止爪２０は、前方から視て略Ｌ字状に形成され、円筒部材４２に外嵌された爪本体部２１と、爪本体部２１から正転方向（矢印Ａ参照）へ延びる爪部２２と、爪本体部２１から逆転方向（矢印Ｂ参照）へ延びる被作動部２３と、を備えている。
尚、逆転防止爪２０を時計回りに回動させて逆転防止歯車１２に当接するように常時付勢する図示しない付勢部材をさらに設けてもよい。 The reverse rotation prevention claw 20 is formed in a substantially L shape when viewed from the front, and has a claw body portion 21 fitted on the cylindrical member 42 and a claw portion 22 extending from the claw body portion 21 in the forward rotation direction (see arrow A). And an actuated portion 23 extending in the reverse direction (see arrow B) from the claw body portion 21.
An urging member (not shown) that constantly urges the anti-reverse rotation claw 20 so as to contact the reverse rotation prevention gear 12 by rotating clockwise may be further provided.

爪本体部２１の外周面においてカム３０と対向する部位に、カム３０の突起（係合部）３６と係合する被係合部２６が形成されている。
本実施形態の被係合部２６は、爪本体部２１の一部を切り欠いてなる凹部で構成され、逆転防止爪２０の時計回り方向を向く第１面２６ａと、反時計回り方向を向く第２面２６ｂとを備えている。
なお、実施形態の被係合部２６は、凹部により構成されているが、これに限定されない。たとえば、凹部の代わりに、爪本体部２１の外周面に外側に突出する２つの凸部を形成し、この２つの凸部で突起３６を挟むようにしてもよい。 An engaged portion 26 that engages with a projection (engaging portion) 36 of the cam 30 is formed at a portion facing the cam 30 on the outer peripheral surface of the claw body portion 21.
The engaged portion 26 of the present embodiment is constituted by a recess formed by cutting out a part of the claw main body portion 21, and faces the first surface 26a facing the clockwise direction of the reverse rotation preventing claw 20 and the counterclockwise direction. And a second surface 26b.
In addition, although the to-be-engaged part 26 of embodiment is comprised by the recessed part, it is not limited to this. For example, instead of the concave portion, two convex portions that protrude outward may be formed on the outer peripheral surface of the claw body portion 21, and the projection 36 may be sandwiched between the two convex portions.

爪部２２の先端側には、筒部２ｂ内に向って突出して逆転防止歯車１２の縦壁面１２ｂに係合可能な先端部２２ａが形成されている。
先端部２２ａの軸方向（前後方向）の厚みは、筒部２ｂの中心側に向うにつれて薄くなるように形成されている。これにより、先端部２２ａは、逆転防止歯車１２の前側に配置されたカム３０に接触することなく、逆転防止歯車１２の歯の軌道内に侵入するようになっている（図８参照）。 A tip end portion 22 a that protrudes into the cylindrical portion 2 b and engages with the vertical wall surface 12 b of the reverse rotation prevention gear 12 is formed on the tip end side of the claw portion 22.
The tip portion 22a is formed such that the thickness in the axial direction (front-rear direction) becomes thinner toward the center side of the cylindrical portion 2b. Thereby, the front-end | tip part 22a penetrate | invades in the track | orbit of the tooth | gear of the reverse rotation prevention gear 12, without contacting the cam 30 arrange | positioned at the front side of the reverse rotation prevention gear 12 (refer FIG. 8).

図６に示すように、被作動部２３は、筒部２ｂの外側に配置されて作動片５０が接触するようになっている。作動片５０は、ロータ３の回転の切り替えレバー（不図示）の操作により、軸５１を中心に回動する部材である（図６の矢印Ｄ１と図７の矢印Ｄ２参照）。
なお、切り替えレバー（不図示）がロータ３の逆転許可状態に設定された場合、作動片５０は、時計回りに回動する（図６の矢印Ｄ１を参照）。
一方で、切り替えレバー（不図示）がロータ３の逆転停止状態に設定された場合、作動片５０は、反時計回りに回動する（図７の矢印Ｄ２を参照）。 As shown in FIG. 6, the actuated part 23 is arranged outside the cylinder part 2b so that the actuating piece 50 comes into contact therewith. The operating piece 50 is a member that rotates around the shaft 51 by operating a rotation switching lever (not shown) of the rotor 3 (see arrow D1 in FIG. 6 and arrow D2 in FIG. 7).
In addition, when the switching lever (not shown) is set to the reverse rotation permission state of the rotor 3, the operating piece 50 rotates clockwise (see arrow D1 in FIG. 6).
On the other hand, when the switching lever (not shown) is set to the reverse rotation stop state of the rotor 3, the operating piece 50 rotates counterclockwise (see arrow D2 in FIG. 7).

そのほか、逆転防止爪２０における爪本体部２１と爪部２２とは、開口部２ｅ内に配置されて開口部２ｅ内の大部分を占有している。このため、開口部２ｅを介して水、異物等が筒部２ｂ内に進入し難い。 In addition, the nail body portion 21 and the claw portion 22 in the reverse rotation preventing claw 20 are disposed in the opening 2e and occupy most of the opening 2e. For this reason, it is difficult for water, foreign matter, etc. to enter the cylindrical portion 2b through the opening 2e.

カム３０は、駆動軸筒１０の正転時に逆転防止爪２０を回動制御する役割（逆転防止爪２０を起こす役割）を果たす部品である。
図５に示すように、カム３０は、駆動軸筒（回転体）１０に挟着し、駆動軸筒１０との摩擦力により駆動軸筒１０とともに回転する摩擦挟着体３１と、摩擦挟着体３１の挟着力が増す方向に付勢するトーションバネ（付勢部材）３２と、を備えている。 The cam 30 is a component that plays a role of controlling the rotation of the reverse rotation prevention pawl 20 during the normal rotation of the drive shaft cylinder 10 (the role of raising the reverse rotation prevention pawl 20).
As shown in FIG. 5, the cam 30 is sandwiched between the drive shaft cylinder (rotating body) 10, and a friction sandwich body 31 that rotates together with the drive shaft cylinder 10 by frictional force with the drive shaft cylinder 10, and friction sandwiching. A torsion spring (biasing member) 32 that urges the body 31 in the direction in which the clamping force increases.

摩擦挟着体３１は、駆動軸筒１０を挟む２つの挟着部３３，３４と、２つの挟着部３３，３４を開閉自在に連結する連結部３５と、２つの挟着部３３，３４のうち一方から径方向外側に突出し、逆転防止爪２０と係合するための突起（係合部）３６と、を備えている。また、本実施形態の摩擦挟着体３１は、各構成（２つの挟着部３３，３４と連結部３５と突起３６）が樹脂成形により一体に形成されてなる単位部品であり、各構成が分離不可能に形成されている。 The friction sandwiching body 31 includes two sandwiching portions 33 and 34 sandwiching the drive shaft cylinder 10, a connecting portion 35 that couples the two sandwiching portions 33 and 34 so as to be freely opened and closed, and two sandwiching portions 33 and 34. And a protrusion (engagement portion) 36 for engaging with the reverse rotation prevention claw 20. Further, the friction sandwiching body 31 of the present embodiment is a unit part in which each configuration (two sandwiching portions 33, 34, a connecting portion 35, and a projection 36) is integrally formed by resin molding. It is formed inseparable.

２つの挟着部３３，３４のそれぞれは、前方から視て略Ｃ字状に形成され、内周面（接触部３７）が駆動軸筒１０の外周面に当接している（図６参照）。
なお、２つの挟着部３３，３４において、連結部３５よりも正転方向に配置されている方を第１挟着部３３と称し、連結部３５よりも逆転方向に配置されている方を第２挟着部３４と称する。 Each of the two sandwiching portions 33 and 34 is formed in a substantially C shape when viewed from the front, and the inner peripheral surface (contact portion 37) is in contact with the outer peripheral surface of the drive shaft cylinder 10 (see FIG. 6). .
Note that, in the two sandwiching portions 33 and 34, the one disposed in the forward rotation direction from the connecting portion 35 is referred to as the first sandwiching portion 33, and the one disposed in the reverse rotation direction from the connecting portion 35. This is referred to as a second sandwiching portion 34.

第１挟着部３３と第２挟着部３４との基部には、トーションバネ３２の各端３２ａ，３２ｂを収容するための係止溝３３ａ，３４ａが形成されている。
なお、トーションバネ３２は、無負荷状態から両端が広がった状態で係止溝３３ａ，３４ａに収容されている。
これにより、第１挟着部３３と第２挟着部３４とは、閉じる方向に常時付勢されて駆動軸筒１０に対して摩擦力が作用するようになっている。 Locking grooves 33 a and 34 a for accommodating the ends 32 a and 32 b of the torsion spring 32 are formed at the base of the first sandwiching portion 33 and the second sandwiching portion 34.
The torsion spring 32 is accommodated in the locking grooves 33a and 34a in a state where both ends are expanded from the no-load state.
Thereby, the first clamping part 33 and the second clamping part 34 are constantly urged in the closing direction so that a frictional force acts on the drive shaft cylinder 10.

第１挟着部３３と第２挟着部３４には、内周面から径方向内側に突出して駆動軸筒１０接触する３つの接触部３７（第１接触部３７ａ〜第３接触部３７ｃ）が形成されている。
この接触部３７によれば、駆動軸筒１０に対する第１挟着部３３と第２挟着部３４との接触面積が減少し、第１挟着部３３と第２挟着部３４とによる挟着力が接触部３７（第１接触部３７ａ〜第３接触部３７ｃ）に集中する。つまり、カム３０自体を大型化することなく挟着力を向上させることができ、カム３０を小型化することができる。 Three contact portions 37 (first contact portion 37 a to third contact portion 37 c) projecting radially inward from the inner peripheral surface and contacting the drive shaft cylinder 10 are formed on the first sandwiching portion 33 and the second sandwiching portion 34. Is formed.
According to the contact portion 37, the contact area between the first sandwiching portion 33 and the second sandwiching portion 34 with respect to the drive shaft cylinder 10 is reduced, and the sandwiching between the first sandwiching portion 33 and the second sandwiching portion 34 is performed. The applied force concentrates on the contact portion 37 (the first contact portion 37a to the third contact portion 37c). That is, the clamping force can be improved without increasing the size of the cam 30 itself, and the cam 30 can be reduced in size.

なお、３つ接触部３７の配置位置に関し、図６に示すように、第１接触部３７ａは、第１挟着部３３の先端部側に位置している。第２接触部３７ｂは、第１挟着部３３の基端部側に位置している。第３接触部３７ｃは、第２挟着部３４の略中央部に位置している。
つまり、第１接触部３７ａ〜第３接触部３７ｃが周方向に略等間隔で配置され、接触部３７の増加を抑えつつ、摩擦挟着体３１が駆動軸筒１０に安定して挟着するように構成されている。 Regarding the arrangement position of the three contact portions 37, the first contact portion 37 a is located on the tip end side of the first sandwiching portion 33 as shown in FIG. 6. The second contact portion 37 b is located on the proximal end side of the first sandwiching portion 33. The third contact part 37 c is located at a substantially central part of the second sandwiching part 34.
That is, the first contact portion 37 a to the third contact portion 37 c are arranged at substantially equal intervals in the circumferential direction, and the frictional sandwiching body 31 is stably sandwiched by the drive shaft cylinder 10 while suppressing an increase in the contact portion 37. It is configured as follows.

連結部３５は、第１挟着部３３の基端部と第２挟着部３４の基端部との間で周方向に延び、可撓性を有するように薄肉に形成された帯状部分である。
なお、連結部３５と第１挟着部３３と第２挟着部３４からなる連続する外周面は、円弧状を成し、筒部２ｂの内周面に引っ掛かり難くなっている。 The connecting portion 35 is a strip-shaped portion that extends in the circumferential direction between the proximal end portion of the first sandwiching portion 33 and the proximal end portion of the second sandwiching portion 34 and is formed thin so as to have flexibility. is there.
In addition, the continuous outer peripheral surface which consists of the connection part 35, the 1st clamping part 33, and the 2nd clamping part 34 comprises circular arc shape, and is hard to be hooked on the internal peripheral surface of the cylinder part 2b.

突起３６は、逆転防止爪２０の被係合部２６に係合し、カム３０の回転運動を逆転防止爪２０に伝達するためのものである。
本実施形態の突起３６は、第１挟着部３３の外周面の先端側に設けられている。
また、突起３６は、開口部２ｅ内に位置（突出）し、逆転防止爪２０の被係合部２６に係合するように配置されている。
なお、カム３０を筒部２ｂ内に収容する際、突起３６を筒部２ｂの切り欠き溝２ｈ（図２参照）に合わせ、切り欠き溝２ｈに沿って突起３６を通過させることで、カム３０を筒部２ｂ内に収容しつつ突起３６を開口部２ｅ内に配置することができる。 The protrusion 36 is engaged with the engaged portion 26 of the reverse rotation preventing claw 20 to transmit the rotational motion of the cam 30 to the reverse rotation preventing claw 20.
The protrusion 36 of the present embodiment is provided on the distal end side of the outer peripheral surface of the first sandwiching portion 33.
Further, the protrusion 36 is positioned (projected) in the opening 2 e and is disposed so as to engage with the engaged portion 26 of the reverse rotation preventing claw 20.
When the cam 30 is accommodated in the cylindrical portion 2b, the protrusion 36 is aligned with the notch groove 2h (see FIG. 2) of the cylindrical portion 2b, and the protrusion 36 is allowed to pass along the notch groove 2h. The projection 36 can be disposed in the opening 2e while being accommodated in the cylindrical portion 2b.

そのほか、カム３０（突起３６を除く）は、図２に示すように、筒部２ｂに装着される軸受１０ｂの外径よりも小径に形成され、カム３０を筒部２ｂに収容可能になっている。このため、駆動軸筒１０及びカム３０を筒部２ｂ内に収容した後に、軸受１０ｂを外側から筒部２ｂに嵌め込むことができる。従って、カム３０及び軸受１０ｂの組み込み作業性がよい。
また、図６に示すように、摩擦挟着体３１は、筒部２ｂの内周面との間で隙間Ｓが生じるように形成されている。このため、駆動軸筒１０に挟着する第１挟着部３３と第２挟着部３４は、筒部２ｂ内で開くことができるようになっている。 In addition, as shown in FIG. 2, the cam 30 (excluding the protrusion 36) is formed to have a smaller diameter than the outer diameter of the bearing 10b attached to the cylindrical portion 2b, so that the cam 30 can be accommodated in the cylindrical portion 2b. Yes. For this reason, after accommodating the drive shaft cylinder 10 and the cam 30 in the cylinder part 2b, the bearing 10b can be fitted into the cylinder part 2b from the outside. Therefore, the workability of assembling the cam 30 and the bearing 10b is good.
Moreover, as shown in FIG. 6, the friction clamping body 31 is formed so that the clearance gap S may arise between the internal peripheral surfaces of the cylinder part 2b. For this reason, the 1st clamping part 33 and the 2nd clamping part 34 which are clamped to the drive shaft cylinder 10 can be opened in the cylinder part 2b.

次に、逆転防止機構の作動例について説明する。 Next, an operation example of the reverse rotation prevention mechanism will be described.

〈逆転許可状態〉
図６に示すように、切り替えレバー（不図示）がロータ３の逆転許可状態に設定された場合、作動片５０は、時計回りに回動し（図６の矢印Ｄ１参照）、被作動部２３を押圧する。これにより、逆転防止爪２０が反時計回りに回動し、逆転防止歯車１２の歯の軌道上から爪部２２が離脱する。
また、被作動部２３が筒部２ｂと作動片５０とに挟み込まれて逆転防止歯車１２の回転が規制される。よって、逆転防止歯車１２の歯の軌道上から爪部２２が離脱した状態が保持される。 <Reverse rotation permission state>
As shown in FIG. 6, when the switching lever (not shown) is set in the reverse rotation permission state of the rotor 3, the operating piece 50 rotates clockwise (see the arrow D <b> 1 in FIG. 6), and the operated part 23. Press. As a result, the reverse rotation preventing claw 20 rotates counterclockwise, and the claw portion 22 is detached from the tooth trajectory of the reverse rotation preventing gear 12.
Further, the operated portion 23 is sandwiched between the cylinder portion 2b and the operating piece 50, and the rotation of the reverse rotation preventing gear 12 is restricted. Therefore, the state where the claw portion 22 is detached from the tooth trajectory of the reverse rotation preventing gear 12 is maintained.

〈逆転防止状態〉
図７に示すように、切り替えレバー（不図示）がロータ３の逆転防止状態に設定された場合、作動片５０は、反時計回りに回動する（図７の矢印Ｄ２参照）。これにより、被作動部２３が作動片５０に係合しなくなり、逆転防止爪２０が回動可能となる。 <Reverse rotation prevention state>
As shown in FIG. 7, when the switching lever (not shown) is set to prevent the rotor 3 from rotating in the reverse direction, the operating piece 50 rotates counterclockwise (see arrow D <b> 2 in FIG. 7). As a result, the actuated portion 23 is not engaged with the operating piece 50, and the reverse rotation preventing claw 20 can be rotated.

〈逆転防止状態―逆転〉
そして、釣糸が送り出される方向の力を受けてロータ３が逆転した場合、駆動軸筒１０及びカム３０も逆転し（矢印Ｂ参照）、カム３０の突起３６が被係合部２６の第２面２６ｂを押圧する（図７の矢印Ｅ１参照）。 <Reverse rotation prevention state-Reverse rotation>
When the rotor 3 rotates in reverse due to the force in the direction in which the fishing line is sent out, the drive shaft cylinder 10 and the cam 30 also reverse (see arrow B), and the projection 36 of the cam 30 is the second surface of the engaged portion 26. 26b is pressed (see arrow E1 in FIG. 7).

ここで、突起３６は、第２面２６ｂから係合方向（押圧方向）とは逆方向の反力（図７の矢印Ｆ１参照）を受ける。このため、突起３６（力点）が設けられた第１挟着部３３（作用点）には、連結部３５を支点として閉じる方向への荷重（図７の矢印Ｆ２参照）が作用し、駆動軸筒１０と第１挟着部３３との摩擦力が増加する。よって、カム３０は、逆転防止爪２０から反力を受けるものの、空転することなく確実に駆動軸筒１０と共回りする。 Here, the protrusion 36 receives a reaction force (see arrow F1 in FIG. 7) in the direction opposite to the engaging direction (pressing direction) from the second surface 26b. For this reason, a load (see arrow F2 in FIG. 7) in the direction of closing the connecting portion 35 as a fulcrum acts on the first clamping portion 33 (action point) provided with the protrusion 36 (power point), and the drive shaft The frictional force between the cylinder 10 and the first clamping part 33 increases. Therefore, although the cam 30 receives the reaction force from the reverse rotation preventing claw 20, it rotates reliably with the drive shaft cylinder 10 without idling.

そして、カム３０に押圧された逆転防止爪２０は時計方向回りに回動し、逆転防止爪２０の先端部２２ａが逆転防止歯車１２の歯の軌道内に侵入する（図７の矢印Ｅ２参照）。
この結果、ロータ３がさらに逆転しようとしても、図８に示すように、逆転防止爪２０の先端部２２ａが逆転防止歯車１２の縦壁面１２ｂに係合し、駆動軸筒１０及びロータ３の逆転が規制される。 Then, the reverse rotation preventing claw 20 pressed by the cam 30 rotates clockwise, and the tip 22a of the reverse rotation preventing claw 20 enters the tooth trajectory of the reverse rotation preventing gear 12 (see arrow E2 in FIG. 7). .
As a result, even if the rotor 3 tries to further reverse, as shown in FIG. 8, the tip 22 a of the anti-reverse pawl 20 engages with the vertical wall surface 12 b of the anti-reverse gear 12, and the reverse of the drive shaft cylinder 10 and the rotor 3. Is regulated.

〈逆転防止状態―正転〉
一方で、ハンドルの巻き取り操作により駆動軸筒１０が正転した場合（矢印Ａ参照）、逆転防止爪２０の先端部２２ａは、逆転防止歯車１２の斜面１２ａに乗り上げて歯を乗り越す。よって、駆動軸筒１０の回転が規制されず、ロータ３の正転が許容される。 <Reverse rotation prevention state-forward rotation>
On the other hand, when the drive shaft cylinder 10 is rotated forward by the winding operation of the handle (see arrow A), the tip portion 22a of the reverse rotation preventing claw 20 rides on the inclined surface 12a of the reverse rotation preventing gear 12 and gets over the teeth. Therefore, the rotation of the drive shaft cylinder 10 is not restricted, and the forward rotation of the rotor 3 is allowed.

また、図９に示すように、駆動軸筒１０の正転に伴ってカム３０が正転した場合（矢印Ａ参照）、カム３０の突起３６が逆転防止爪２０の第１面２６ａを押圧し（図９の矢印Ｅ３参照）、逆転防止爪２０が反時計回りに回動する（図９の矢印Ｅ４参照）
この結果、図１０に示すように、先端部２２ａが逆転防止歯車１２の歯の軌道上から離脱し、逆転防止爪２０が逆転防止歯車１２の歯を乗り越した際に接触音が発生する、ということが回避されるようになる。
また、先端部２２ａが逆転防止歯車１２の歯の軌道上から離脱した場合、被作動部２３が筒部２ｂの外周面に当接し、逆転防止爪２０による反時計回り方向への回動が規制される。 Further, as shown in FIG. 9, when the cam 30 rotates forward with the forward rotation of the drive shaft cylinder 10 (see arrow A), the projection 36 of the cam 30 presses the first surface 26 a of the reverse rotation preventing claw 20. (Refer to arrow E3 in FIG. 9), the reverse rotation prevention pawl 20 rotates counterclockwise (see arrow E4 in FIG. 9).
As a result, as shown in FIG. 10, when the tip 22 a is separated from the tooth trajectory of the anti-reverse gear 12, a contact sound is generated when the anti-reverse pawl 20 passes over the teeth of the anti-reverse gear 12. It will be avoided.
Further, when the tip 22a is separated from the tooth orbit of the reverse rotation preventing gear 12, the actuated portion 23 comes into contact with the outer peripheral surface of the cylindrical portion 2b, and the counterclockwise rotation by the reverse rotation preventing claw 20 is restricted. Is done.

そして、このような状態でカム３０がさらに正転すると、突起３６は、第１面２６ａから係合方向（押圧方向）とは逆方向の反力（図１０の矢印Ｆ３参照）を受ける。このため、突起３６（力点）が設けられた第１挟着部３３（作用点）には、連結部３５を支点として開く方向への荷重（図１０の矢印Ｆ４参照）が作用する。
この結果、第１挟着部３３と駆動軸筒１０との摩擦力が低減し、駆動軸筒１０の正転がスムーズとなる。
なお、第１挟着部３３に作用する荷重がトーションバネ３２の付勢力よりも大きい場合には、特に図示しないが、トーションバネ３２の付勢力に逆らって第１挟着部３３が開く方向に移動し、第１接触部３７ａ及び第２接触部３７ｂが駆動軸筒１０と接触しないようになる。 When the cam 30 further rotates forward in such a state, the protrusion 36 receives a reaction force (see arrow F3 in FIG. 10) in the direction opposite to the engaging direction (pressing direction) from the first surface 26a. For this reason, a load (see an arrow F4 in FIG. 10) is applied to the first sandwiching portion 33 (operation point) provided with the protrusion 36 (power point) in a direction in which the connection portion 35 is opened as a fulcrum.
As a result, the frictional force between the first clamping part 33 and the drive shaft cylinder 10 is reduced, and the normal rotation of the drive shaft cylinder 10 becomes smooth.
When the load acting on the first clamping part 33 is larger than the urging force of the torsion spring 32, although not particularly shown, the first clamping part 33 opens in a direction against the urging force of the torsion spring 32. The first contact portion 37a and the second contact portion 37b do not come into contact with the drive shaft cylinder 10 by moving.

以上、逆転防止状態におけるロータ３の正転時と逆転時とについて説明したが、つぎに、逆転許可状態のロータ３の正転時と逆転時とについて説明する。 The forward rotation and the reverse rotation of the rotor 3 in the reverse rotation prevention state have been described above. Next, the forward rotation and the reverse rotation of the rotor 3 in the reverse rotation permission state will be described.

〈逆転許可状態―正転時〉
図６に示すように、逆転許可状態は、前記したように逆転防止歯車１２の歯の軌道上から爪部２２が離脱した状態が保持されている。よって、ハンドル操作により駆動軸筒１０及びカム３０が正転すると（矢印Ａ参照）、突起３６が被係合部２６の第１面２６ａから係合方向（押圧方向）とは逆方向の反力を受け、第１挟着部３３（作用点）に、連結部３５を支点として開く方向への荷重が作用する。この結果、駆動軸筒１０と第１挟着部３３との摩擦力が低減し、駆動軸筒１０がスムーズに回転する。 <Reverse rotation permission state-Forward rotation>
As shown in FIG. 6, in the reverse rotation permission state, as described above, the state in which the claw portion 22 is detached from the tooth trajectory of the reverse rotation prevention gear 12 is maintained. Therefore, when the drive shaft cylinder 10 and the cam 30 are rotated forward by the handle operation (see arrow A), the protrusion 36 reacts from the first surface 26a of the engaged portion 26 in the direction opposite to the engaging direction (pressing direction). In response, a load is applied to the first sandwiching portion 33 (operation point) in a direction to open the connection portion 35 as a fulcrum. As a result, the frictional force between the drive shaft cylinder 10 and the first clamping portion 33 is reduced, and the drive shaft cylinder 10 rotates smoothly.

〈逆転許可状態―逆転時〉
一方で、ロータ３の逆転により、駆動軸筒１０及びカム３０が逆転すると（矢印Ｂ参照）、突起３６が被係合部２６の第２面２６ｂから係合方向（押圧方向）とは逆方向の反力を受け、第１挟着部３３に閉じる方向への荷重が作用する。この結果、カム３０の駆動軸筒１０に対する摩擦力が増加し、ブレーキがかかった状態で駆動軸筒１０が逆転する。
よって、ロータ３の逆転による釣糸繰出し操作時や仕掛け準備作業中のロータ３の逆転時等に適度なブレーキが作用して不用意なロータ３の過回転によるトラブルが防止できる。 <Reverse rotation permission state-During reverse rotation>
On the other hand, when the drive shaft cylinder 10 and the cam 30 are reversed due to the reverse rotation of the rotor 3 (see arrow B), the protrusion 36 is opposite to the engagement direction (pressing direction) from the second surface 26b of the engaged portion 26. In response to this reaction force, a load in the closing direction acts on the first sandwiching portion 33. As a result, the frictional force of the cam 30 on the drive shaft cylinder 10 increases, and the drive shaft cylinder 10 rotates in the reverse direction in a braked state.
Accordingly, an appropriate brake is applied during fishing line feeding operation due to the reverse rotation of the rotor 3 or during the reverse rotation of the rotor 3 during the preparation preparation work, thereby preventing troubles due to unintentional excessive rotation of the rotor 3.

次に、突起３６と被係合部２６との係合により作用する第１挟着部３３への荷重の詳細について説明する。 Next, the details of the load applied to the first clamping part 33 that acts by the engagement between the protrusion 36 and the engaged part 26 will be described.

図６に示すように、突起３６が第１挟着部３３の先端部側に位置していることから、突起３６を第１挟着部３３の基端側に形成した場合よりも、反力を受ける突起３６（力点）と連結部３５（支点）との距離が長く、第１挟着部３３（作用点）に作用する荷重がより大きくなるように構成されている。つまり、より効果的に第１挟着部３３と駆動軸筒１０との摩擦力が大きく変化するようになっている。 As shown in FIG. 6, since the protrusion 36 is located on the distal end side of the first sandwiching portion 33, the reaction force is greater than when the protrusion 36 is formed on the proximal end side of the first sandwiching portion 33. The distance between the projection 36 (power point) receiving the connection portion 35 (fulcrum) is long, and the load acting on the first sandwiching portion 33 (operation point) is further increased. That is, the frictional force between the first clamping part 33 and the drive shaft cylinder 10 is greatly changed more effectively.

また、第１挟着部３３は、連結部３５を支点として開閉（傾倒）するように構成されていることから、第１挟着部３３に作用する荷重は、第１挟着部３３全体において、支点（連結部）から最も遠い先端部に大きく作用する。
よって、本実施形態では、第１挟着部３３の先端部に第１接触部３７ａを配置することで、より効果的に摩擦力が変化するようになっている。 Moreover, since the 1st clamping part 33 is comprised so that it may open and close (tilt) with the connection part 35 as a fulcrum, the load which acts on the 1st clamping part 33 in the 1st clamping part 33 whole. , It acts on the tip farthest from the fulcrum (connecting portion).
Therefore, in this embodiment, the frictional force is changed more effectively by disposing the first contact portion 37 a at the tip of the first sandwiching portion 33.

また、本実施形態では、被係合部２６との係合により開く方向又は閉じる方向への荷重が作用する第１挟着部３３の方に多くの接触部３７が設けられている。
このため、荷重を受けた場合に増減する摩擦力が大きくなり、より効果的に第１挟着部３３と駆動軸筒１０との摩擦力が大きく変化するようになっている。
なお、接触部３７は、２つの挟着部３３，３４の内周面に周方向に等間隔で３つ形成して駆動軸筒（回転体）１０の外周面を圧接する構成としているため、安定した接触状態の維持の面から好ましい。 Further, in the present embodiment, a large number of contact portions 37 are provided on the first sandwiching portion 33 to which a load in the opening direction or the closing direction is applied by the engagement with the engaged portion 26.
For this reason, the frictional force which increases / decreases when receiving a load is increased, and the frictional force between the first clamping part 33 and the drive shaft cylinder 10 is greatly changed more effectively.
In addition, since the contact part 37 is formed on the inner peripheral surface of the two sandwiching parts 33 and 34 at three circumferential intervals at equal intervals, the outer peripheral surface of the drive shaft cylinder (rotating body) 10 is configured to be pressed. This is preferable from the viewpoint of maintaining a stable contact state.

以上、本実施形態によれば、突起３６と逆転防止爪２０（被係合部２６）との係合により、カム３０（摩擦挟着体３１）と駆動軸筒１０（回転体）との摩擦力を効果的に変化させることができ、駆動軸筒１０の逆転時に確実な逆転防止性能の維持を図れる。
特に、ハンドルの釣糸巻き取り操作により駆動軸筒１０が正転した場合、カム３０（摩擦挟着体３１）と駆動軸筒１０の摩擦力が大きく低減し、ハンドル操作性が軽い魚釣用リールを提供することができる。また、カム３０（摩擦挟着体３１）の摩耗が大幅に抑制されて部品交換の回数が減り、メンテナンス性の向上も図れる。 As described above, according to the present embodiment, the friction between the cam 30 (friction sandwiching body 31) and the drive shaft cylinder 10 (rotating body) due to the engagement between the protrusion 36 and the reverse rotation preventing claw 20 (the engaged portion 26). The force can be changed effectively, and reliable reversal prevention performance can be maintained when the drive shaft cylinder 10 is reversed.
In particular, when the drive shaft cylinder 10 is rotated forward by the fishing line winding operation of the handle, the frictional force between the cam 30 (friction pinching body 31) and the drive shaft cylinder 10 is greatly reduced, and the fishing reel has a light handle operability. Can be provided. In addition, the wear of the cam 30 (friction sandwiching body 31) is greatly suppressed, the number of parts replacement is reduced, and maintenance can be improved.

また、本実施形態によれば、第１挟持部３３に突起（係合部）３６を逆転防止爪２０に対する切り替え制御部として機能させている。このため、従来技術のように連結部が切り替え制御部として機能する場合よりも、連結部の設計上の制約が低減し、逆転防止機構の設計の自由度が向上する。 Further, according to the present embodiment, the projection (engagement portion) 36 is caused to function as a switching control portion for the reverse rotation preventing claw 20 in the first clamping portion 33. For this reason, compared with the case where a connection part functions as a switching control part like the prior art, the restrictions on the design of a connection part reduce and the freedom degree of design of a reverse rotation prevention mechanism improves.

また、本実施形態の配置構造によれば、逆転防止歯車１２とカム３０とは、筒部２ｂ内に収容され、衝撃、水、及び異物から保護されるので安定した逆転防止機能が得られる。
また、逆転防止爪２０における係合箇所（逆転防止歯車１２と係合する先端部２２ａと、カム３０と係合する被係合部２６）は、筒部２ｂ内を向き、筒部２ｂの外側に露出しないため、衝撃、水及び異物から保護される。
さらに、筒部２ｂ内に逆転防止歯車１２とカム３０とのみを収容しているので、逆転防止機構全てを収容する場合よりも、筒部２ｂを比較的小さく設計できる。
また、筒部２ｂの一部である開口部２ｅに逆転防止爪２０が配置されているため、筒部２ｂと逆転防止爪２０とが占有する空間が狭小となる。
以上から、逆転防止機構の保護と魚釣用スピニングリール１の小型化の両立を図ることができる。 Further, according to the arrangement structure of the present embodiment, the reverse rotation preventing gear 12 and the cam 30 are accommodated in the cylindrical portion 2b and protected from impact, water, and foreign matter, so that a stable reverse rotation preventing function is obtained.
Further, the engagement portion (the tip end portion 22a that engages with the anti-reverse rotation gear 12 and the engaged portion 26 that engages with the cam 30) in the anti-reverse rotation pawl 20 faces the inside of the cylindrical portion 2b and the outside of the cylindrical portion 2b. Protected against impact, water and foreign objects.
Furthermore, since only the reverse rotation preventing gear 12 and the cam 30 are accommodated in the cylindrical portion 2b, the cylindrical portion 2b can be designed to be relatively smaller than the case where all the reverse rotation preventing mechanisms are accommodated.
Moreover, since the reverse rotation prevention nail | claw 20 is arrange | positioned in the opening part 2e which is a part of the cylinder part 2b, the space which the cylinder part 2b and the reverse rotation prevention claw 20 occupy becomes narrow.
From the above, it is possible to achieve both protection of the reverse rotation prevention mechanism and downsizing of the fishing spinning reel 1.

また、本実施形態によれば、摩擦挟着体３１の各構成が一体になっていることから、カム３０を駆動軸筒１０に挟着させる場合に２つの挟着部３３，３４が分離するおそれがない。このため、駆動軸筒１０への組み付け性が向上するとともに、第１挟着部３３と第２挟着部３４と連結部３５とを別体で形成した場合よりも部品点数を低減でき、製造工数の低減及び組み付け労力の低減を図ることができる。この結果、逆転防止機構が安価となる。 Further, according to the present embodiment, since the respective components of the friction clamping body 31 are integrated, the two clamping portions 33 and 34 are separated when the cam 30 is clamped to the drive shaft cylinder 10. There is no fear. For this reason, the assembly to the drive shaft cylinder 10 is improved, and the number of parts can be reduced as compared with the case where the first sandwiching portion 33, the second sandwiching portion 34, and the connecting portion 35 are formed separately. It is possible to reduce man-hours and assembly labor. As a result, the reverse rotation prevention mechanism becomes inexpensive.

以上、実施形態の逆転防止機構について説明したが、本発明は実施形態で説明した例に限定されない。 Although the reverse rotation prevention mechanism of the embodiment has been described above, the present invention is not limited to the example described in the embodiment.

本実施形態では、逆転防止歯車１２と駆動軸筒１０とが一体に形成されたものを使用しているが、別体で形成された逆転防止歯車１２と駆動軸筒１０とを一体化したものを使用してもよい。 In this embodiment, the reverse rotation preventing gear 12 and the drive shaft cylinder 10 are integrally formed, but the reverse rotation preventing gear 12 and the drive shaft cylinder 10 formed separately are integrated. May be used.

本実施形態では、逆転防止機構（逆転防止歯車１２と逆転防止爪２０とカム３０）が駆動軸筒１０の回転を規制することでロータ３の逆転を防止するように構成されているが、逆転防止機構がハンドル軸５の回転を規制することでロータ３の逆転を防止するように構成してもよい。
つまり、逆転防止機構により回転が規制される回転体は、ロータ３と連動して回転する回転体であれば特に限定されない。 In this embodiment, the reverse rotation prevention mechanism (the reverse rotation prevention gear 12, the reverse rotation prevention claw 20, and the cam 30) is configured to prevent the rotation of the rotor 3 by restricting the rotation of the drive shaft cylinder 10. The prevention mechanism may be configured to prevent reverse rotation of the rotor 3 by restricting rotation of the handle shaft 5.
That is, the rotating body whose rotation is restricted by the reverse rotation prevention mechanism is not particularly limited as long as the rotating body rotates in conjunction with the rotor 3.

本実施形態では、逆転許可機構（切り替えレバーや作動片５０）を備えているが、逆転許可機構（切り替えレバーや作動片５０）を備えていなくてもよい。 In the present embodiment, the reverse rotation permission mechanism (switching lever and operating piece 50) is provided, but the reverse rotation permission mechanism (switching lever and operating piece 50) may not be provided.

本実施形態では、カム３０が逆転防止爪２０に係合するための構成として、径方向外側に突出する突起３６を備えているが、本発明はこれに限定されない。つまり、逆転防止爪２０の被係合部２６との係合作用により、逆転防止爪２０の逆転防止状態と逆転許可状態とを切り替え制御できれば特に限定されない。
たとえば、図１１（ａ）に示すように、カム３０の第１挟着部３３側に凹部（係合部）３６を形成し、この凹部（係合部）３６に係合する凸部（被係合部）２６を逆転防止爪２０に形成してもよい。
または、図１１（ｂ）に示すように、前方に突出する突起（係合部）３６を第１挟着部３３の前端面に設け、この突起（係合部）３６に係合する凹部（被係合部）２６を逆転防止爪に形成してもよい。 In this embodiment, the cam 30 is provided with the protrusion 36 protruding radially outward as a configuration for engaging the reverse rotation preventing claw 20, but the present invention is not limited to this. That is, there is no particular limitation as long as the reverse rotation preventing state and the reverse rotation permission state of the reverse rotation preventing claw 20 can be switched by the engaging action of the reverse rotation preventing claw 20 with the engaged portion 26.
For example, as shown in FIG. 11A, a concave portion (engagement portion) 36 is formed on the first sandwiching portion 33 side of the cam 30, and a convex portion (covered portion) engaged with the concave portion (engagement portion) 36 is formed. (Engagement portion) 26 may be formed on the reverse rotation preventing claw 20.
Alternatively, as shown in FIG. 11B, a protrusion (engaging portion) 36 that protrudes forward is provided on the front end surface of the first sandwiching portion 33, and a recess (engagement with the protrusion (engaging portion) 36 ( The engaged portion 26 may be formed on a reverse rotation preventing claw.

本実施形態では、突起（係合部）３６が第１挟着部３３に設けられているが、突起３６が第２挟着部３４に設けられてもよい（図１２（ｄ）参照）。
このような変形例によれば、逆転防止機構により回転が規制される回転体がハンドル軸仕様である場合、駆動軸筒１０の矢印Ｂ方向（反時計回り方向）回転が巻き取り操作における正転時となり、仕様変更に伴う摩擦力の設定が効果的に行える。 In the present embodiment, the projection (engagement portion) 36 is provided on the first clamping portion 33, but the projection 36 may be provided on the second clamping portion 34 (see FIG. 12D).
According to such a modification, when the rotating body whose rotation is restricted by the reverse rotation prevention mechanism is a handle shaft specification, the rotation of the drive shaft cylinder 10 in the arrow B direction (counterclockwise direction) is the forward rotation in the winding operation. At times, it is possible to effectively set the frictional force associated with the specification change.

本実施形態では、突起（係合部）３６が第１挟着部３３の先端側に設けられているが、突起３６を基端側（図１２（ｃ）参照）や略中央部（図１２（ａ），（ｂ）参照）に設けられてもよい。同様に、突起３６を第２挟着部３４に設ける場合においても先端側に限定されない。 In the present embodiment, the protrusion (engaging portion) 36 is provided on the distal end side of the first sandwiching portion 33, but the protrusion 36 is located on the proximal end side (see FIG. 12C) or the substantially central portion (FIG. 12). (See (a) and (b)). Similarly, when the protrusion 36 is provided on the second sandwiching portion 34, it is not limited to the tip side.

本実施形態では、第１挟着部３３と第２挟着部３４とに対し、接触部３７（第１接触部３７ａ〜第３接触部３７ｃ）を形成しているが、特に接触部３７を形成しなくてもよい。
また、接触部３７を形成しない場合において、第１挟着部３３と第２挟着部３４との長さを調節することで所望の摩擦力を得るようにしてもよい。 In the present embodiment, the contact portion 37 (first contact portion 37a to third contact portion 37c) is formed with respect to the first sandwiching portion 33 and the second sandwiching portion 34. It does not have to be formed.
Further, when the contact portion 37 is not formed, a desired frictional force may be obtained by adjusting the lengths of the first sandwiching portion 33 and the second sandwiching portion 34.

本実施形態では、接触部３７を３つ形成しているが、これに限定されない。
本発明の接触部３７は、第１挟着部３３と第２挟着部３４とのそれぞれに少なくても１つ以上形成すればよい。よって、図１２（ａ）、（ｂ）に示すように、第１挟着部３３と第２挟着部３４に形成される接触部３７の合計数が２つや４つ以上であってもよい。 In the present embodiment, three contact portions 37 are formed, but the present invention is not limited to this.
At least one or more contact portions 37 of the present invention may be formed in each of the first sandwiching portion 33 and the second sandwiching portion 34. Therefore, as shown in FIGS. 12A and 12B, the total number of contact portions 37 formed on the first sandwiching portion 33 and the second sandwiching portion 34 may be two or four or more. .

本実施形態では、３つの接触部３７が周方向に等間隔で配置されているが、カム３０の挟着が安定できれば、特に限定されない。 In the present embodiment, the three contact portions 37 are arranged at equal intervals in the circumferential direction, but are not particularly limited as long as the cam 30 can be stably clamped.

本実施形態では、連結部３５が周方向に延びる薄肉の帯状としているが、可撓性を有していればよく、これに限定されない。例えば、図１２に示すように、連結部３５は、径方向外側に突出する略Ｕ字のもの（図１２（ａ），（ｂ）参照）、蛇腹状のもの（図１２（ｃ）参照）のものであってもよい。
また、連結部３５は、第１挟着部３３と第２挟着部３４との内周面に沿って延びるもの（図１２（ｄ）参照）であってもよい。 In this embodiment, although the connection part 35 is made into the thin strip | belt shape extended in the circumferential direction, it should just have flexibility and is not limited to this. For example, as shown in FIG. 12, the connecting portion 35 has a substantially U-shape projecting radially outward (see FIGS. 12A and 12B) and a bellows shape (see FIG. 12C). It may be.
Moreover, the connection part 35 may extend along the inner peripheral surface of the 1st clamping part 33 and the 2nd clamping part 34 (refer FIG.12 (d)).

本実施形態では、第１挟着部３３と第２挟着部３４と連結部３５との各構成が一体に形成されて分離不可能な摩擦挟着体３１を利用しているが、これに限定されない。
たとえば、図１３（ａ）、（ｂ）に示すように、先端に抜け止め部３９が形成された軸部３８（連結部）により、別体の第１挟着部３３と第２挟着部３４とを分離不可能にした摩擦挟着体３１を利用してもよい。
このような構成であれば、２つの挟着部３３，３４が互いに異なる素材により形成することができる。よって、摩耗し易い方の挟着部を金属材料で形成することが可能となる。 In the present embodiment, the first sandwiching portion 33, the second sandwiching portion 34, and the connecting portion 35 are integrally formed, and the friction sandwiching body 31 that cannot be separated is used. It is not limited.
For example, as shown in FIGS. 13A and 13B, separate first and second sandwiching portions 33 and 2 are provided by a shaft portion 38 (connecting portion) having a retaining portion 39 formed at the tip. Alternatively, the friction sandwiching body 31 that cannot be separated from the belt 34 may be used.
If it is such a structure, the two clamping parts 33 and 34 can be formed with a mutually different raw material. Accordingly, it is possible to form the sandwiched portion that is more likely to be worn with a metal material.

なお、本発明は、図１３（ｃ）、（ｄ）で示すように、軸部３８（連結部）のみが形成され、別体の第１挟着部３３と第２挟着部３４と分離可能な摩擦挟着体３１を利用してもよい。 In the present invention, as shown in FIGS. 13C and 13D, only the shaft portion 38 (connecting portion) is formed, and the first and second sandwiching portions 33 and 34 are separated from each other. A possible frictional sandwich 31 may be used.

本実施形態では、第１挟着部３３と第２挟着部３４との摩擦力を高めるための付勢部材としてトーションバネ３２を利用しているが、これに限定されない。たとえば、コイルスプリング（図１２（ｂ）〜（ｄ）参照）や永久磁石の磁力を用いてもよい。
なお、永久磁石の磁力を用いる方法として、第１挟着部３３の先端部と、第１挟着部３３の先端部に対向する第２挟着部３４の先端部とに、互いに引かれ合うように永久磁石を配置する方法が挙げられる。これによれば、第１挟着部３３の先端部と第２挟着部３４の先端部とが閉じる方向に付勢され、駆動軸筒１０に挟着可能となる。
また、付勢部材を配置する箇所に関し、第１挟着部３３と第２挟着部３４との基端部側でなく、先端側に配置してもよい（図１２（ｂ）〜（ｄ）、図１３参照）。 In the present embodiment, the torsion spring 32 is used as a biasing member for increasing the frictional force between the first sandwiching portion 33 and the second sandwiching portion 34, but is not limited to this. For example, a coil spring (see FIGS. 12B to 12D) or the magnetic force of a permanent magnet may be used.
As a method of using the magnetic force of the permanent magnet, the tip of the first sandwiching portion 33 and the tip of the second sandwiching portion 34 facing the tip of the first sandwiching portion 33 are attracted to each other. A method of arranging permanent magnets is mentioned. According to this, the distal end portion of the first sandwiching portion 33 and the distal end portion of the second sandwiching portion 34 are biased in the closing direction, and the drive shaft cylinder 10 can be sandwiched.
Further, regarding the place where the urging member is disposed, it may be disposed not on the proximal end side of the first sandwiching portion 33 and the second sandwiching portion 34 but on the distal end side (FIGS. 12B to 12D). ), See FIG.

１魚釣用スピニングリール
２リール本体
２ｂ筒部
２ｅ開口部
３ロータ
４スプール
８スプール軸
１０駆動軸筒（回転体）
１２逆転防止歯車
２０逆転防止爪
２６被係合部
３０カム
３１摩擦挟着体
３２トーションばね（付勢部材）
３３第１挟着部（挟着部）
３４第２挟着部（挟着部）
３５連結部
３６突起（係合部）
３７（３７ａ〜３７ｃ）接触部（第１接触部〜第３接触部）
５０作動片 DESCRIPTION OF SYMBOLS 1 Spinning reel for fishing 2 Reel main body 2b Tube part 2e Opening part 3 Rotor 4 Spool 8 Spool shaft 10 Drive shaft cylinder (rotating body)
DESCRIPTION OF SYMBOLS 12 Reverse rotation prevention gear 20 Reverse rotation prevention claw 26 Engagement part 30 Cam 31 Friction pinching body 32 Torsion spring (biasing member)
33 1st clamping part (clamping part)
34 2nd clamping part (clamping part)
35 Connecting part 36 Protrusion (engaging part)
37 (37a to 37c) contact portion (first contact portion to third contact portion)
50 working pieces

Claims

An anti-reverse gear provided on a rotating body that rotates by a handle operation;
An anti-reverse claw engaged with the anti-reverse gear;
A reverse rotation prevention mechanism for a fishing reel comprising: a cam for engaging and disengaging the reverse rotation prevention pawl to and from the reverse rotation prevention gear according to the rotation direction of the rotating body;
The cam
A friction sandwiching body sandwiched between the rotating body and rotating together with the rotating body by a frictional force with the rotating body;
An urging member for urging in a direction in which the clamping force of the friction clamping body increases,
The friction sandwich body is
Two sandwiching parts sandwiching the rotating body;
A connecting part for connecting the two sandwiching parts so as to be freely opened and closed;
An engaging portion that is formed on one of the two clamping portions and engages with the anti-reverse claw;
A mechanism for preventing reversal of a fishing reel.

2. The fishing reel reverse rotation prevention mechanism according to claim 1, wherein the one sandwiching portion provided with the engagement portion is disposed in a normal rotation direction with respect to the coupling portion.

The engagement portion is formed by a protrusion protruding outward in the radial direction of the one sandwiching portion, and engages with an engaged portion formed of a recess of the reverse rotation prevention claw. The mechanism for preventing reverse rotation of the fishing reel according to claim 2.

4. The fishing reel reverse rotation prevention mechanism according to claim 1, wherein the engaging portion is located on a distal end side of the one sandwiching portion. 5.