JP6764266B2 - Ratchet mechanism - Google Patents

Ratchet mechanism Download PDF

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JP6764266B2
JP6764266B2 JP2016124860A JP2016124860A JP6764266B2 JP 6764266 B2 JP6764266 B2 JP 6764266B2 JP 2016124860 A JP2016124860 A JP 2016124860A JP 2016124860 A JP2016124860 A JP 2016124860A JP 6764266 B2 JP6764266 B2 JP 6764266B2
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engaging
rotating member
ratchet
ratchet mechanism
engaging claw
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JP2017227291A (en
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遼平 小室
遼平 小室
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Nidec Sankyo Corp
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Description

本発明は、ワンウエイクラッチとして利用されるラチェット機構、およびラチェット機構を備えた排水弁駆動装置に関するものである。 The present invention relates to a ratchet mechanism used as a one-way clutch and a drain valve drive device including the ratchet mechanism.

洗濯機等の排水弁駆動装置では、モータ部の駆動力を歯車等の第１回転部材、歯車等の第２回転部材、クランク部材等を経由させて排水弁を開方向に駆動し、モータ部の駆動を停止した際、排水弁は付勢部材の付勢力によって閉方向に移動する。このため、第１回転部材と第２回転部材等との間にワンウエイクラッチとしてのラチェット機構を設け、排水弁が付勢部材の付勢力によって閉方向に移動する際、ラチェット機構を空周りさせる技術が提案されている（特許文献１参照）。ラチェット機構では、例えば、図７に示すように、第１回転部材６ｘにラチェット部材８ｘを囲む周壁６６ｘを設ける一方、周壁６６ｘの内周面に複数の係合歯６３ｘを設ける。また、ラチェット部材８ｘには、第２回転部材７ｘと結合された円形の本体部８１ｘから反時計周りＣＣＷの方向に向けて３つの係合爪８０ｘを延在させて係合爪８０ｘの先端部を係合歯６３ｘに係合させる。従って、第１回転部材６ｘが軸線Ｌ周りに時計周りＣＷに回転すると、かかる回転は、ラチェット部材８ｘを介して第２回転部材７ｘに伝達される。これに対して、第２回転部材７ｘが軸線Ｌ周りに時計周りＣＷに回転した際、ラチェット部材８ｘでは、係合歯６３ｘを乗り越える度に係合爪８０ｘが径方向内側に撓むだけで、第２回転部材７ｘから第１回転部材６ｘには回転が伝達されない。 In a drain valve driving device such as a washing machine, the driving force of the motor unit is driven in the opening direction via a first rotating member such as a gear, a second rotating member such as a gear, a crank member, etc., and the motor unit is driven. When the drive of the drain valve is stopped, the drain valve moves in the closing direction by the urging force of the urging member. Therefore, a technique of providing a ratchet mechanism as a one-way clutch between the first rotating member and the second rotating member, etc., and causing the ratchet mechanism to idle when the drain valve moves in the closing direction by the urging force of the urging member. Has been proposed (see Patent Document 1). In the ratchet mechanism, for example, as shown in FIG. 7, the first rotating member 6x is provided with a peripheral wall 66x surrounding the ratchet member 8x, while a plurality of engaging teeth 63x are provided on the inner peripheral surface of the peripheral wall 66x. Further, on the ratchet member 8x, three engaging claws 80x extend from the circular main body 81x coupled to the second rotating member 7x in the counterclockwise direction of CCW, and the tip portion of the engaging claw 80x. Is engaged with the engaging tooth 63x. Therefore, when the first rotating member 6x rotates clockwise CW about the axis L, such rotation is transmitted to the second rotating member 7x via the ratchet member 8x. On the other hand, when the second rotating member 7x rotates clockwise CW around the axis L, the ratchet member 8x only bends the engaging claw 80x radially inward each time it gets over the engaging tooth 63x. No rotation is transmitted from the second rotating member 7x to the first rotating member 6x.

特開２０１１−１９８０号公報Japanese Unexamined Patent Publication No. 2011-1980

図７に示すラチェット機構４ｘにおいて、付勢部材の付勢力によって排水弁を閉方向に移動させるときに排水弁が損傷しないように、係合爪８０ｘが係合歯６３ｘに乗り上げた際の摩擦力によって、出力軸にブレーキ力を加えることが好ましい。しかしながら、図７に示すラチェット機構４ｘでは、係合爪８０ｘが係合歯６３ｘを乗り越える際の摩擦力が小さい。かといって、１つの係合爪８０ｘ当たりの摩擦力を高めた構造を採用すると、係合爪８０ｘに大きな応力が加わるため、係合爪８０ｘに摩耗や破損が発生しやすい。 In the ratchet mechanism 4x shown in FIG. 7, the frictional force when the engaging claw 80x rides on the engaging tooth 63x so that the drain valve is not damaged when the drain valve is moved in the closing direction by the urging force of the urging member. Therefore, it is preferable to apply a braking force to the output shaft. However, in the ratchet mechanism 4x shown in FIG. 7, the frictional force when the engaging claw 80x gets over the engaging tooth 63x is small. On the other hand, if a structure in which the frictional force per engaging claw 80x is increased is adopted, a large stress is applied to the engaging claw 80x, so that the engaging claw 80x is likely to be worn or damaged.

以上の問題点に鑑みて、本発明の課題は、係合爪の摩擦力を利用したブレーキ力を増大させても、係合爪に過大な応力が加わることを抑制することのできるラチェット機構および排水弁駆動装置を提供することにある。 In view of the above problems, the subject of the present invention is a ratchet mechanism capable of suppressing excessive stress applied to the engaging claws even if the braking force utilizing the frictional force of the engaging claws is increased. The purpose is to provide a drain valve drive device.

上記課題を解決するため、本発明に係るラチェット機構は、回転中心軸線を囲む周壁の内周面に複数の係合歯が設けられた第１回転部材と、前記第１回転部材と同軸状に配置されたラチェット部材と、を有し、前記ラチェット部材は、前記周壁の内側に、本体部と、前記本体部に繋がる根元部分から前記回転中心軸線周りの一方側に延在して先端部が前記係合歯に当接する複数の係合爪と、を備え、前記複数の係合爪は各々、前記回転中心軸線周りの一方側で隣り合う前記係合爪の前記根元部分に隙間を介して径方向外側で重なる重なり部分を有し、前記係合爪は、前記回転中心軸線から離間した位置を中心とする円弧状に延在していることを特徴とする。
In order to solve the above problems, the ratchet mechanism according to the present invention has a first rotating member provided with a plurality of engaging teeth on the inner peripheral surface of the peripheral wall surrounding the rotation center axis, and a first rotating member coaxial with the first rotating member. The ratchet member has an arranged ratchet member, and the ratchet member extends from the main body portion and the root portion connected to the main body portion to one side around the rotation center axis, and has a tip portion inside the peripheral wall. A plurality of engaging claws abutting on the engaging teeth are provided, and each of the plurality of engaging claws is provided with a gap at the root portion of the engaging claws adjacent to each other on one side around the rotation center axis. It has overlapping portions that overlap on the outer side in the radial direction, and the engaging claws extend in an arc shape centered on a position separated from the rotation center axis .

本発明では、第１回転部材が回転中心軸線周りの他方側に回転した際、第１回転部材の係合歯にラチェット部材の係合爪の先端側が当接しているため、第１回転部材の回転がラチェット部材に伝達され、ラチェット部材が回転する。これに対して、ラチェット部材が回転中心軸線周りに他方側に回転した際、ラチェット部材では、係合爪を乗り越える度に係合爪が内側に撓むだけで、ラチェット部材から第１回転部材には回転が伝達されない。その際、ラチェット機構がワンウエイクラッチと機能するとともに、係合爪が係合歯に乗り上げた際の摩擦力によって、ラチェット部材に負荷が印加されるので、ラチェット部材の回転速度が低下する。ここで、複数の係合爪は各々、回転中心軸線周りの一方側で隣り合う係合爪の根元部分に隙間を介して径方向外側で重なる重なり部分を有するまで、係合爪同士の間隔が狭く設定されているので、係合爪の数を増やすことができる。従って、１つの係合爪に加わる応力を低減することができるので、係合爪に摩耗や破損が発生しにくい。それ故、ラチェット機構の耐久性を向上することができる。なお、上記の作用効果は、ラチェット機構を、ラチェット部材の回転を第１回転部材に伝達するようなワンウエイクラッチとして用いた場合でも同様である。また、かかる態様によれば、係合爪が撓んだ際、係合爪は、回転中心軸線周りの一方側に位置する係合爪の根元部分と接触しにくい。
In the present invention, when the first rotating member rotates to the other side around the rotation center axis, the tip side of the engaging claw of the ratchet member is in contact with the engaging teeth of the first rotating member, so that the first rotating member The rotation is transmitted to the ratchet member, and the ratchet member rotates. On the other hand, when the ratchet member rotates to the other side around the rotation center axis, the ratchet member changes from the ratchet member to the first rotating member by simply bending the engaging claw inward each time the ratchet member gets over the engaging claw. The rotation is not transmitted. At that time, the ratchet mechanism functions as a one-way clutch, and a load is applied to the ratchet member by the frictional force when the engaging claw rides on the engaging tooth, so that the rotation speed of the ratchet member decreases. Here, the distance between the engaging claws is such that each of the plurality of engaging claws has an overlapping portion that overlaps radially outward through a gap at the root portion of the engaging claws adjacent to each other on one side around the center axis of rotation. Since it is set narrow, the number of engaging claws can be increased. Therefore, since the stress applied to one engaging claw can be reduced, the engaging claw is less likely to be worn or damaged. Therefore, the durability of the ratchet mechanism can be improved. The above-mentioned action and effect are the same even when the ratchet mechanism is used as a one-way clutch that transmits the rotation of the ratchet member to the first rotating member. Further, according to this aspect, when the engaging claw is bent, the engaging claw is unlikely to come into contact with the root portion of the engaging claw located on one side around the rotation center axis.

本発明において、前記第１回転部材と同軸状に配置された第２回転部材を有し、前記ラチェット部材は、前記本体部に前記第２回転部材との結合部を有している態様を採用することができる。 In the present invention, an embodiment is adopted in which the ratchet member has a second rotating member coaxially arranged with the first rotating member, and the ratchet member has a connecting portion with the second rotating member in the main body portion. can do.

本発明において、前記係合爪は、前記根元部分から前記回転中心軸線周りの一方側に延在している態様を採用することができる。かかる態様によれば、ラチェット部材の外径を拡大しなくても、複数の係合爪が各々、回転中心軸線周りの一方側で隣り合う係合爪の根元部分に隙間を介して径方向外側で重なる重なり部分を有するまで、係合爪同士の間隔を狭くすることができる。従って、係合爪の数を増やすのに適している。
In the present invention, the engagement claw can adopt a manner extending from the root portion to one side around the rotation center axis. According to such an embodiment, without expanding the outer diameter of the ratchet member, each of the plurality of engaging claws is radially outward through a gap at the root portion of the engaging claws adjacent to each other on one side around the rotation center axis. The distance between the engaging claws can be narrowed until the overlapping portion is provided. Therefore, it is suitable for increasing the number of engaging claws.

本発明において、前記係合爪は、４つ、５つあるいは６つ設けられている態様を採用することができる。 In the present invention, it is possible to adopt an embodiment in which four, five or six engaging claws are provided.

本発明において、前記根元部分の周方向の寸法が、前記係合爪の前記根元部分より先端側に位置する部分の径方向の寸法より大である態様を採用することができる。かかる態様によれば、係合爪の根元部分の強度を大とすることができるとともに、係合爪を撓みやすくすることができる。 In the present invention, it is possible to adopt an embodiment in which the circumferential dimension of the root portion is larger than the radial dimension of the portion of the engaging claw located on the tip side of the root portion. According to this aspect, the strength of the base portion of the engaging claw can be increased, and the engaging claw can be easily bent.

本発明では、第１回転部材が回転中心軸線周りの他方側に回転した際、第１回転部材の係合歯にラチェット部材の係合爪の先端側が当接しているため、第１回転部材の回転がラチェット部材に伝達され、ラチェット部材が回転する。これに対して、ラチェット部材が回転中心軸線周りに他方側に回転した際、ラチェット部材では、係合爪を乗り越える度に
係合爪が内側に撓むだけで、ラチェット部材から第１回転部材には回転が伝達されない。その際、ラチェット機構がワンウエイクラッチと機能するとともに、係合爪が係合歯に乗り上げた際の摩擦力によって、ラチェット部材に負荷が印加されるので、ラチェット部材の回転速度が低下する。ここで、複数の係合爪は各々、回転中心軸線周りの一方側で隣り合う係合爪の根元部分に隙間を介して径方向外側で重なる重なり部分を有するまで、係合爪同士の間隔が狭く設定されているので、係合爪の数を増やすことができる。従って、１つの係合爪に加わる応力を低減することができるので、係合爪に摩耗や破損が発生しにくい。それ故、ラチェット機構の耐久性を向上することができる。 In the present invention, when the first rotating member rotates to the other side around the rotation center axis, the tip side of the engaging claw of the ratchet member is in contact with the engaging teeth of the first rotating member, so that the first rotating member The rotation is transmitted to the ratchet member, and the ratchet member rotates. On the other hand, when the ratchet member rotates to the other side around the rotation center axis, the ratchet member changes from the ratchet member to the first rotating member by simply bending the engaging claw inward each time the ratchet member gets over the engaging claw. The rotation is not transmitted. At that time, the ratchet mechanism functions as a one-way clutch, and a load is applied to the ratchet member by the frictional force when the engaging claw rides on the engaging tooth, so that the rotation speed of the ratchet member decreases. Here, the distance between the engaging claws is such that each of the plurality of engaging claws has an overlapping portion that overlaps radially outward through a gap at the root portion of the engaging claws adjacent to each other on one side around the center axis of rotation. Since it is set narrow, the number of engaging claws can be increased. Therefore, since the stress applied to one engaging claw can be reduced, the engaging claw is less likely to be worn or damaged. Therefore, the durability of the ratchet mechanism can be improved.

本発明を適用した排水弁駆動装置の外観を示す斜視図である。It is a perspective view which shows the appearance of the drain valve drive device to which this invention is applied. 本発明を適用した排水弁駆動装置の分解斜視図である。It is an exploded perspective view of the drain valve drive device to which this invention is applied. 本発明を適用したラチェット機構を軸線方向の一方側からみた斜視図である。It is a perspective view which saw the ratchet mechanism to which this invention was applied from one side in the axial direction. 本発明を適用したラチェット機構の全体を示す説明図である。It is explanatory drawing which shows the whole of the ratchet mechanism to which this invention is applied. 本発明を適用したラチェット機構のラチェット部材の説明図である。It is explanatory drawing of the ratchet member of the ratchet mechanism to which this invention is applied. 本発明を適用したラチェット機構の耐久性試験結果を示すグラフである。It is a graph which shows the durability test result of the ratchet mechanism to which this invention was applied. 本発明の参考例に係るラチェット機構の説明図である。It is explanatory drawing of the ratchet mechanism which concerns on the reference example of this invention.

図面を参照して、本発明を適用したラチェット機構を備えた駆動装置を説明する。以下の説明では、駆動装置を、被駆動部材としての排水弁を開方向および閉方向に駆動する排水弁駆動装置として構成した例を中心に説明する。なお、以下の説明において、本発明の回転中心軸線周りの一方側は、軸線Ｌ周りの反時計周りＣＣＷに相当し、回転中心軸線周りの他方側は、軸線Ｌ周りの時計周りＣＷに相当する。 A drive device provided with a ratchet mechanism to which the present invention is applied will be described with reference to the drawings. In the following description, an example in which the drive device is configured as a drain valve drive device for driving the drain valve as a driven member in the open direction and the closed direction will be mainly described. In the following description, one side around the rotation center axis of the present invention corresponds to a counterclockwise CCW around the axis L, and the other side around the rotation center axis corresponds to a clockwise CW around the axis L. ..

（全体構成）
図１は、本発明を適用した排水弁駆動装置１００の外観を示す斜視図である。図２は、本発明を適用した排水弁駆動装置１００の分解斜視図である。 (overall structure)
FIG. 1 is a perspective view showing the appearance of the drain valve drive device 100 to which the present invention is applied. FIG. 2 is an exploded perspective view of the drain valve drive device 100 to which the present invention is applied.

図１および図２において、本発明を適用した排水弁駆動装置１００は、下ケース３１および上ケース３２からなるケース体３０を備え、上ケース３２に形成された開口部３２０からクランク部材１０が突出している。下ケース３１と上ケース３２との間には支持板３３が配置されている。下ケース３１には、駆動源としてのモータ部１ａが配置され、かかるモータ部１ａの回転力は、輪列２を介してクランク部材１０に伝達される。輪列２は、モータ部１ａの回転軸１ｂに取り付けられたピニオン（図示せず）から第１歯車２１、第２歯車２２、第３歯車２３、第４歯車２４および第５歯車２５をこの順に備えており、第５歯車２５は、ネジ２９によってクランク部材１０と連結されている。 In FIGS. 1 and 2, the drain valve drive device 100 to which the present invention is applied includes a case body 30 including a lower case 31 and an upper case 32, and a crank member 10 projects from an opening 320 formed in the upper case 32. ing. A support plate 33 is arranged between the lower case 31 and the upper case 32. A motor unit 1a as a drive source is arranged in the lower case 31, and the rotational force of the motor unit 1a is transmitted to the crank member 10 via the train wheel 2. In the train wheel 2, the first gear 21, the second gear 22, the third gear 23, the fourth gear 24, and the fifth gear 25 are arranged in this order from a pinion (not shown) attached to the rotating shaft 1b of the motor unit 1a. The fifth gear 25 is connected to the crank member 10 by a screw 29.

クランク部材１０は、円筒状胴部１７と、その上端側に設けられた円盤部１８と、円盤部１８の外周から上方に突出したロッド係合歯１９とを備えている。ロッド係合歯１９は、クランク部材１０の回転中心軸線からずれた位置にあり、図１に一点鎖線で示すように、ロッド２０が係合している。円筒状胴部１７は、下端側の外周面にカム部１６を備えている。カム部１６は、図２に示すスイッチ５の可動接片５１が接触した状態となっており、クランク部材１０が回転することにより、スイッチ５をオンまたはオフさせる。かかるスイッチ５は、クランク部材１０の回転位置の検出に用いられる。 The crank member 10 includes a cylindrical body portion 17, a disk portion 18 provided on the upper end side thereof, and a rod engaging tooth 19 protruding upward from the outer circumference of the disk portion 18. The rod engaging tooth 19 is located at a position deviated from the rotation center axis of the crank member 10, and the rod 20 is engaged as shown by the alternate long and short dash line in FIG. The cylindrical body portion 17 is provided with a cam portion 16 on the outer peripheral surface on the lower end side. The cam portion 16 is in a state where the movable contact piece 51 of the switch 5 shown in FIG. 2 is in contact with the cam portion 16, and the switch 5 is turned on or off by rotating the crank member 10. Such a switch 5 is used to detect the rotational position of the crank member 10.

排水弁駆動装置１００では、クランク部材１０が第５歯車２５の回転を受けて軸線Ｌ１０周りに回転することにより、ロッド係合歯１９に係合しているロッド２０に直線的な往復運動を行わせる。ロッド２０の他端側には弁機構（図示せず）が存在し、ロッド２０の直線的な往復運動により、排水弁１１０に開閉動作を行なわせる。 In the drain valve drive device 100, the crank member 10 receives the rotation of the fifth gear 25 and rotates around the axis L10 to linearly reciprocate the rod 20 engaged with the rod engaging teeth 19. Let me. A valve mechanism (not shown) exists on the other end side of the rod 20, and the drain valve 110 is opened and closed by the linear reciprocating motion of the rod 20.

排水弁１１０には、付勢部材（図示せず）によって、全閉状態に復帰しようとする付勢力（図１に矢印Ｆで示す）が常時加わっている。この排水弁１１０を開動作させる際は、その全閉状態に復帰しようとする力に抗してロッド２０が排水弁１１０を引っ張るようにして、図１の矢印Ｘ１方向に動作する。逆に、全開状態にある排水弁１１０を全閉状態とする際は、ロッド２０は全閉状態に復帰しようとする付勢力を受けて図１の矢印Ｘ２方向に動作する。 The drain valve 110 is constantly subjected to an urging force (indicated by an arrow F in FIG. 1) for returning to the fully closed state by an urging member (not shown). When the drain valve 110 is opened, the rod 20 pulls the drain valve 110 against the force of returning to the fully closed state, and the drain valve 110 operates in the direction of arrow X1 in FIG. On the contrary, when the drain valve 110 in the fully open state is brought into the fully closed state, the rod 20 operates in the direction of arrow X2 in FIG. 1 by receiving an urging force for returning to the fully closed state.

このように構成した排水弁駆動装置１００において、図２に示す第２歯車２２には、図３、図４および図５を参照して後述するラチェット機構４が構成されている。 In the drain valve drive device 100 configured in this way, the second gear 22 shown in FIG. 2 is configured with a ratchet mechanism 4 described later with reference to FIGS. 3, 4 and 5.

（ラチェット機構の構成）
図３は、本発明を適用したラチェット機構４を軸線Ｌ方向の一方側からみた斜視図であり、図３（ａ）、（ｂ）は、ラチェット機構４全体の斜視図、およびラチェット機構４の分解斜視図である。図４は、本発明を適用したラチェット機構４の全体を示す説明図であり、図４（ａ）、（ｂ）は、ラチェット機構４の平面図、および側面図である。図５は、本発明を適用したラチェット機構４のラチェット部材８の説明図であり、図５（ａ）、（ｂ）は、ラチェット部材８の平面図、および一部を切り欠いて示す部分断面図である。 (Structure of ratchet mechanism)
FIG. 3 is a perspective view of the ratchet mechanism 4 to which the present invention is applied as viewed from one side in the L direction of the axis, and FIGS. 3 (a) and 3 (b) are a perspective view of the entire ratchet mechanism 4 and the ratchet mechanism 4. It is an exploded perspective view. FIG. 4 is an explanatory view showing the whole of the ratchet mechanism 4 to which the present invention is applied, and FIGS. 4A and 4B are a plan view and a side view of the ratchet mechanism 4. 5A and 5B are explanatory views of the ratchet member 8 of the ratchet mechanism 4 to which the present invention is applied, and FIGS. 5A and 5B are a plan view of the ratchet member 8 and a partial cross section shown by cutting out a part thereof. It is a figure.

図３、図４および図５に示すように、ラチェット機構４は、支軸４１の軸線Ｌ（回転中心軸線）周りに回転可能な第１回転部材６と、第１回転部材６と同軸状に設けられたラチェット部材８とを有している。また、ラチェット機構４は、第１回転部材６およびラチェット部材８と同軸状に配置された第２回転部材７を有しており、ラチェット部材８と第２回転部材７とは一体に回転する。 As shown in FIGS. 3, 4 and 5, the ratchet mechanism 4 has a first rotating member 6 that can rotate around the axis L (rotation center axis) of the support shaft 41 and a first rotating member 6 coaxially with the first rotating member 6. It has a ratchet member 8 provided. Further, the ratchet mechanism 4 has a first rotating member 6 and a second rotating member 7 arranged coaxially with the ratchet member 8, and the ratchet member 8 and the second rotating member 7 rotate integrally.

第１回転部材６は、外周部に歯車６１が形成された円板部６５と、円板部６５から軸線Ｌ方向の一方側Ｌ１に突出した円筒状の周壁６６と、円板部６５から軸線Ｌ方向の他方側Ｌ２に突出した円筒部６７とを備えている。円板部６５、周壁６６および円筒部６７は同軸状であり、円筒部６７は、円板部６５の中央で円形の穴６９として開口している。 The first rotating member 6 includes a disk portion 65 having a gear 61 formed on the outer peripheral portion, a cylindrical peripheral wall 66 protruding from the disk portion 65 on one side L1 in the axis L direction, and an axis line from the disk portion 65. It is provided with a cylindrical portion 67 projecting to L2 on the other side in the L direction. The disc portion 65, the peripheral wall 66, and the cylindrical portion 67 are coaxial, and the cylindrical portion 67 is opened as a circular hole 69 at the center of the disc portion 65.

周壁６６の内周面には、周方向に三角歯状の複数の係合歯６３が等角度間隔に複数形成されている。複数の係合歯６３は各々、頂部６３０から時計周りＣＷの側に設けられた第１斜面６３１と、頂部６３０から反時計周りＣＣＷの側に設けられた第２斜面６３２とを有している。第２斜面６３２の傾きは、第１斜面６３１の傾きより緩やかであり、第１斜面６３１は、急峻である。 On the inner peripheral surface of the peripheral wall 66, a plurality of engaging teeth 63 having a triangular tooth shape in the circumferential direction are formed at equal angular intervals. Each of the plurality of engaging teeth 63 has a first slope 631 provided on the side of the clockwise CW from the top 630 and a second slope 632 provided on the side of the counterclockwise CCW from the top 630. .. The inclination of the second slope 632 is gentler than the inclination of the first slope 631, and the inclination of the first slope 631 is steep.

第２回転部材７は、外周部に歯車７１が形成された胴部７５と、胴部７５の中心から軸線Ｌ方向の一方側Ｌ１に突出した第１軸部７６と、胴部７５から軸線Ｌ方向の他方側Ｌ２に突出した第２軸部７７とを備えており、胴部７５、第１軸部７６および第２軸部７７は同軸状である。第２回転部材７は、第１軸部７６、胴部７５および第２軸部７７を軸線Ｌ方向に貫通する軸穴７２が形成されており、軸穴７２には支軸４１が嵌っている。従って、第２回転部材７は支軸４１によって軸線Ｌ周りに回転可能に支持されている。 The second rotating member 7 includes a body portion 75 having a gear 71 formed on the outer peripheral portion, a first shaft portion 76 projecting from the center of the body portion 75 to one side L1 in the axis L direction, and an axis line L from the body portion 75. A second shaft portion 77 projecting to the other side L2 in the direction is provided, and the body portion 75, the first shaft portion 76, and the second shaft portion 77 are coaxial. The second rotating member 7 is formed with a shaft hole 72 that penetrates the first shaft portion 76, the body portion 75, and the second shaft portion 77 in the axis L direction, and a support shaft 41 is fitted in the shaft hole 72. .. Therefore, the second rotating member 7 is rotatably supported around the axis L by the support shaft 41.

また、第１回転部材６は、円筒部６７が第１回転部材７に第１軸部７６に嵌ることによって、第１軸部７６によって軸線Ｌ周りに回転可能に支持されている。この状態で、第１軸部７６は、第２回転部材６の円板部６５から軸線Ｌ方向の一方側Ｌ１に突出している。 Further, the first rotating member 6 is rotatably supported around the axis L by the first shaft portion 76 by fitting the cylindrical portion 67 into the first rotating member 7 with the first shaft portion 76. In this state, the first shaft portion 76 projects from the disc portion 65 of the second rotating member 6 to one side L1 in the axis L direction.

（ラチェット部材８の構成）
第１回転部材６に対して第２回転部材７とは反対側には、第１回転部材６の周壁６６の内側にラチェット部材８が設けられている。ラチェット部材８は樹脂製である。ラチェッ
ト部材８は、第２回転部材７と結合する円盤状の本体部８１と、本体部８１に繋がる根元部分８０１から反時計周りＣＣＷの方向に延在する複数の係合爪８０を有しており、複数の係合爪８０の先端部８０２は各々、係合歯６３に時計周りＣＷの側から当接している。本体部８１では、軸線Ｌ方向の一方側Ｌ１の端面８１０に、環状のリブ８１１が形成されている。本形態において、係合爪８０は、軸線Ｌを中心に等角度間隔に形成されている。本形態において、係合爪８０は、軸線Ｌを中心に９０°の等角度間隔に４つ形成されている。 (Structure of ratchet member 8)
A ratchet member 8 is provided inside the peripheral wall 66 of the first rotating member 6 on the side opposite to the second rotating member 7 with respect to the first rotating member 6. The ratchet member 8 is made of resin. The ratchet member 8 has a disk-shaped main body 81 that is connected to the second rotating member 7, and a plurality of engaging claws 80 that extend counterclockwise in the CCW direction from the root portion 801 connected to the main body 81. The tip portions 802 of the plurality of engaging claws 80 are in contact with the engaging teeth 63 from the clockwise CW side. In the main body 81, an annular rib 811 is formed on the end surface 810 of one side L1 in the axis L direction. In the present embodiment, the engaging claws 80 are formed at equal angular intervals about the axis L. In this embodiment, four engaging claws 80 are formed at equal intervals of 90 ° about the axis L.

第２回転部材７とラチェット部材８の本体部８１とは、第１回転部材６の円筒部６７を貫通する第２回転部材７の第１軸部７６を介して結合されている。より具体的には、ラチェット部材８において、本体部８１の中央には、第２回転部材７との結合部としての長穴８１８が形成されている一方、第２回転部材７の第１軸部７６の軸線Ｌ方向の一方側Ｌ１の端部７６０は、長穴８１８に嵌る断面長円形状になっている。 The second rotating member 7 and the main body 81 of the ratchet member 8 are connected via the first shaft portion 76 of the second rotating member 7 that penetrates the cylindrical portion 67 of the first rotating member 6. More specifically, in the ratchet member 8, an elongated hole 818 as a connecting portion with the second rotating member 7 is formed in the center of the main body portion 81, while the first shaft portion of the second rotating member 7 is formed. The end portion 760 of one side L1 in the axis L direction of 76 has an oval cross section that fits into the slotted hole 818.

図５（ａ）に示すように、ラチェット部材８において、複数の係合爪８０は各々、反時計周りＣＣＷの側で隣り合う係合爪８０の根元部分８０１に隙間Ｇを介して径方向外側で重なる重なり部分８０３を有している。より具体的には、軸線Ｌと根元部分８０１の周方向の端部とを結ぶ仮想の直線Ｌａ、Ｌｂを描いたとき、係合爪８０のうち、直線Ｌａ、Ｌｂの間に位置する部分が、根元部分８０１に隙間Ｇを介して径方向外側で重なる重なり部分８０３である。 As shown in FIG. 5A, in the ratchet member 8, each of the plurality of engaging claws 80 is radially outside through a gap G at the root portion 801 of the engaging claws 80 adjacent to each other on the counterclockwise CCW side. It has an overlapping portion 803 that overlaps with. More specifically, when a virtual straight line La or Lb connecting the axis L and the end portion in the circumferential direction of the root portion 801 is drawn, the portion of the engaging claw 80 located between the straight lines La and Lb is located. , The overlapping portion 803 that overlaps the root portion 801 on the outer side in the radial direction via the gap G.

ここで、係合爪８０は、根元部分８０１から軸線Ｌ周りの反時計周りＣＣＷの側に延在している。
Here, the engaging claw 80 extends from root portion 801 to the side of the counter-clockwise CCW about the axis L.

また、係合爪８０は、軸線Ｌから離間した位置を中心Ｏとする円弧状に延在しており、係合爪８０の曲率は、係合爪８０の延在方向で一定である。また、係合爪８０において、根元部分８０１から先端部８０２付近までの径方向の寸法Ｗｂは一定である、このため、係合爪８０の内周端面８０６は、軸線Ｌから離間した位置を中心Ｏに一定の曲率半径を有する円弧状に延在し、内周端面８０６の曲率は、内周端面８０６の延在方向で一定である。また、係合爪８０の外周端面８０７も、軸線Ｌから離間した位置を中心Ｏに一定の曲率半径を有する円弧状に延在し、外周端面８０７の曲率は、外周端面８０７の延在方向で一定である。また、係合爪８０は、根元部分８０１の周方向の寸法Ｗａが、係合爪８０の根元部分８０１より先端側に位置する部分の径方向の寸法Ｗｂより大である。
Further, the engaging claw 80 extends in an arc shape centered on a position separated from the axis L, and the curvature of the engaging claw 80 is constant in the extending direction of the engaging claw 80. Further, in the engaging claw 80, the radial dimension Wb from the root portion 801 to the vicinity of the tip portion 802 is constant. Therefore, the inner peripheral end surface 806 of the engaging claw 80 is centered on a position separated from the axis L. It extends in an arc shape having a constant radius of curvature in O, and the curvature of the inner peripheral end surface 806 is constant in the extending direction of the inner peripheral end surface 806. Further, the outer peripheral end surface 807 of the engaging claw 80 also extends in an arc shape having a constant radius of curvature around the center O at a position separated from the axis L, and the curvature of the outer peripheral end surface 807 is in the extending direction of the outer peripheral end surface 807. It is constant. Further, in the engaging claw 80, the circumferential dimension Wa of the root portion 801 is larger than the radial dimension Wb of the portion located on the tip side of the root portion 801 of the engaging claw 80.

（動作）
このように構成した排水弁駆動装置１００において、ラチェット機構４では、モータ部１ａから伝達された回転駆動力によって、第１回転部材６が時計周りＣＷに回転すると、第１回転部材６の係合歯６３とラチェット部材８の係合爪８０とが係合するため、第１回転部材６の時計周りＣＷの回転がラチェット部材８を介して第２回転部材７に伝達される。かかる回転は、第３歯車２３から第４歯車２４および第５歯車２５を介して、図１に示すクランク部材１０に伝達され、クランク部材１０が軸線Ｌ１０周りの一方側Ｒ１０に回転すると、ロッド２０を介して排水弁１１０が開方向に駆動される。 (motion)
In the drain valve drive device 100 configured as described above, in the ratchet mechanism 4, when the first rotating member 6 rotates clockwise CW by the rotational driving force transmitted from the motor unit 1a, the first rotating member 6 is engaged. Since the teeth 63 and the engaging claw 80 of the ratchet member 8 engage with each other, the rotation of the clockwise CW of the first rotating member 6 is transmitted to the second rotating member 7 via the ratchet member 8. Such rotation is transmitted from the third gear 23 to the crank member 10 shown in FIG. 1 via the fourth gear 24 and the fifth gear 25, and when the crank member 10 rotates to one side R10 around the axis L10, the rod 20 The drain valve 110 is driven in the opening direction via.

これに対して、モータ部１ａの回転が停止すると、排水弁１１０に印加された閉方向の付勢力によって、クランク部材１０が軸線Ｌ１０周りの一方側Ｒ１０に回転し、かかる回転が第５歯車２５、第４歯車２４および第３歯車２３を介して第２回転部材７に伝達される。但し、その際の第２回転部材７の回転方向は、時計周りＣＷ（他方側）であり、第１
回転部材６の係合歯６３とラチェット部材８の係合爪８０との係合が解除される方向である。従って、ラチェット部材８と第２回転部材７とが時計周りＣＷ（他方側）に回転するが、係合爪８０は、係合歯６３を乗り越えるように撓むため、第１回転部材６は回転しない。それ故、排水弁の閉方向の移動が妨げられない。 On the other hand, when the rotation of the motor portion 1a is stopped, the crank member 10 is rotated to one side R10 around the axis L10 by the urging force in the closing direction applied to the drain valve 110, and the rotation is the fifth gear 25. , Is transmitted to the second rotating member 7 via the fourth gear 24 and the third gear 23. However, the rotation direction of the second rotating member 7 at that time is clockwise CW (the other side), and the first
This is the direction in which the engaging teeth 63 of the rotating member 6 and the engaging claws 80 of the ratchet member 8 are disengaged. Therefore, the ratchet member 8 and the second rotating member 7 rotate clockwise CW (the other side), but the engaging claw 80 bends so as to get over the engaging tooth 63, so that the first rotating member 6 rotates. do not do. Therefore, the movement of the drain valve in the closing direction is not hindered.

また、ラチェット機構４において、係合爪８０が係合歯６３に乗り上げた際の摩擦力によって、第２回転部材７にはブレーキ力が加わるので、排水弁１１０にブレーキ力が加わる。従って、排水弁１１０に損傷が発生しにくい。 Further, in the ratchet mechanism 4, the braking force is applied to the second rotating member 7 by the frictional force when the engaging claw 80 rides on the engaging tooth 63, so that the braking force is applied to the drain valve 110. Therefore, the drain valve 110 is less likely to be damaged.

（本形態の主な効果）
以上説明したように、本形態のラチェット機構４では、ワンウエイクラッチとして機能するとともに、係合爪８０が係合歯６３に乗り上げた際の摩擦力によって、ブレーキ力を発生させる。ここで、複数の係合爪８０は各々、軸線Ｌ周りの反時計周りＣＣＷ（一方側）で隣り合う係合爪８０の根元部分８０１に隙間Ｇを介して径方向外側で重なる重なり部分８０３を有するまで、係合爪８０同士の間隔を狭くしてある。従って、図７に示す構成に比して、係合爪８０の数を増やすことができる。例えば、図７に示す構成では、係合爪８０の数が３つであったが、本形態では、係合爪８０の数が４つである。それ故、第２回転部材７に大きな負荷が印加することができるので、第２回転部材７の回転速度をより低下させることができる。この場合でも、係合爪８０の数を増やしたため、１つの係合爪８０に加わる応力を低減することができる。従って、係合爪８０に摩耗や破損が発生しにくいので、ラチェット機構４の耐久性を向上することができる。 (Main effect of this form)
As described above, the ratchet mechanism 4 of the present embodiment functions as a one-way clutch and generates a braking force by the frictional force when the engaging claw 80 rides on the engaging tooth 63. Here, each of the plurality of engaging claws 80 has an overlapping portion 803 that overlaps the root portion 801 of the adjacent engaging claws 80 in the counterclockwise CCW (one side) around the axis L via the gap G on the outer side in the radial direction. The distance between the engaging claws 80 is narrowed until they are held. Therefore, the number of engaging claws 80 can be increased as compared with the configuration shown in FIG. For example, in the configuration shown in FIG. 7, the number of engaging claws 80 was three, but in this embodiment, the number of engaging claws 80 is four. Therefore, since a large load can be applied to the second rotating member 7, the rotational speed of the second rotating member 7 can be further reduced. Even in this case, since the number of engaging claws 80 is increased, the stress applied to one engaging claw 80 can be reduced. Therefore, since the engaging claw 80 is less likely to be worn or damaged, the durability of the ratchet mechanism 4 can be improved.

例えば、排水弁１１０が付勢部材の付勢力によって開状態から閉状態に戻るまでの時間についての耐久性試験を行ったところ、図６に示す結果が得られた。図６は、本発明を適用したラチェット機構４の耐久性試験結果を示すグラフである。なお、図６には、本発明を適用したラチェット機構４の耐久性試験結果を実線Ａで示し、図７を参照して説明した参考例に係るラチェット機構４ｘの耐久性試験結果を実線Ｂで示してある。 For example, when a durability test was conducted on the time required for the drain valve 110 to return from the open state to the closed state by the urging force of the urging member, the results shown in FIG. 6 were obtained. FIG. 6 is a graph showing the durability test results of the ratchet mechanism 4 to which the present invention is applied. In FIG. 6, the durability test result of the ratchet mechanism 4 to which the present invention is applied is shown by the solid line A, and the durability test result of the ratchet mechanism 4x according to the reference example described with reference to FIG. 7 is shown by the solid line B. It is shown.

図７からわかるように、本発明を適用したラチェット機構４は、参考例に係るラチェット機構４ｘに比較して、初期段階および耐久試験中のいずれにおいても、排水弁１１０が開状態から閉状態に戻るまでの時間が長く、大きなブレーキ力が得られる。また、本発明を適用したラチェット機構４は、参考例に係るラチェット機構４ｘに比較して、耐久試験中で摩擦力の変化（排水弁１１０が開状態から閉状態に戻るまでの時間Ｍの変化）が小さいことが確認できた。 As can be seen from FIG. 7, in the ratchet mechanism 4 to which the present invention is applied, the drain valve 110 is changed from the open state to the closed state in both the initial stage and the durability test as compared with the ratchet mechanism 4x according to the reference example. It takes a long time to return, and a large braking force can be obtained. Further, the ratchet mechanism 4 to which the present invention is applied has a change in frictional force (change in time M until the drain valve 110 returns from the open state to the closed state) during the durability test as compared with the ratchet mechanism 4x according to the reference example. ) Was small.

また、本形態では、図７に示す構成と違って、係合爪８０は、根元部分８０１から、軸線Ｌ周りの反時計周りＣＣＷ（一方側）に延在している。このため、ラチェット部材８の外径を拡大しなくても、複数の係合爪８０が各々、軸線Ｌ周りの反時計周りＣＣＷ（一方側）で隣り合う係合爪８０の根元部分８０１に隙間Ｇを介して径方向外側で重なる重なり部分８０３を有するまで、係合爪８０同士の間隔を狭くすることができる。それ故、係合爪８０の数を増やすことができる。
Further, in the present embodiment, unlike the configuration shown in FIG. 7, the engaging claw 80 extends from the root portion 801 to the counterclockwise CCW (one side) around the axis L. Therefore, even if the outer diameter of the ratchet member 8 is not expanded, each of the plurality of engaging claws 80 has a gap in the root portion 801 of the engaging claws 80 adjacent to each other in the counterclockwise CCW (one side) around the axis L. The distance between the engaging claws 80 can be narrowed until the overlapping portion 803 is provided on the outer side in the radial direction via G. Therefore, the number of engaging claws 80 can be increased.

また、係合爪８０の根元部分８０１の周方向の寸法Ｗａが、係合爪８０の根元部分８０１より先端側に位置する部分の径方向の寸法Ｗｂより大である。このため、係合爪８０の根元部分８０１の強度を大とすることができるとともに、係合爪８０を撓みやすくすることができる。 Further, the circumferential dimension Wa of the root portion 801 of the engaging claw 80 is larger than the radial dimension Wb of the portion located on the tip side of the root portion 801 of the engaging claw 80. Therefore, the strength of the root portion 801 of the engaging claw 80 can be increased, and the engaging claw 80 can be easily bent.

また、係合爪８０は、軸線Ｌから離間した位置を中心Ｏとする円弧状に延在しており、係合爪８０の曲率は、係合爪８０の延在方向で一定である。このため、係合爪８０の周方向の強度を大とすることができるとともに、係合爪８０を径方向に撓みやすくすることが
できる。 Further, the engaging claw 80 extends in an arc shape centered on a position separated from the axis L, and the curvature of the engaging claw 80 is constant in the extending direction of the engaging claw 80. Therefore, the strength of the engaging claw 80 in the circumferential direction can be increased, and the engaging claw 80 can be easily bent in the radial direction.

また、係合爪８０は、軸線Ｌから離間した位置を中心Ｏとする円弧状に延在しているため、係合爪８０が撓んだ際、係合爪８０は、反時計周りＣＣＷの側に位置する係合爪８０の根元部分８０１と接触しにくい。 Further, since the engaging claw 80 extends in an arc shape centered on a position separated from the axis L , when the engaging claw 80 bends, the engaging claw 80 becomes a counterclockwise CCW. It is difficult to come into contact with the root portion 801 of the engaging claw 80 located on the side.

また、本形態では、本体部８１に環状のリブ８１１が設けられている。このため、ラチェット部材８に軸線Ｌ方向の一方側Ｌ１から支持板３３が接する場合でも、本体部８１と支持板３３との間に余計な摩擦が発生しにくい。また、本体部８１と周壁６６との間に係合爪８０を配置するのに十分なスペースを確保することを目的に、本体部８１の外径を、図７に示す本体部８１ｘより小さくした場合でも、本体部８１の強度を高めることができる。 Further, in the present embodiment, the main body 81 is provided with an annular rib 811. Therefore, even when the support plate 33 comes into contact with the ratchet member 8 from one side L1 in the axis L direction, extra friction is unlikely to occur between the main body portion 81 and the support plate 33. Further, the outer diameter of the main body 81 is made smaller than that of the main body 81x shown in FIG. 7 for the purpose of securing a sufficient space for arranging the engaging claw 80 between the main body 81 and the peripheral wall 66. Even in this case, the strength of the main body 81 can be increased.

（別の実施の形態）
上記実施の形態では、係合爪８０が周方向で等角度間隔に形成されていたが、係合爪８０が周方向で不等角度間隔に形成されていてもよい。例えば、４つの係合爪８０の根元部分８０１の角度間隔が７５°、８５°、９５°、１０５°になっている態様を採用してもよい。この場合でも、係合爪８０の長さを異ならせれば、複数の係合爪８０が各々、軸線Ｌ周りの反時計周りＣＣＷ（一方側）で隣り合う係合爪８０の根元部分８０１に隙間Ｇを介して径方向外側で重なる重なり部分８０３を有するまで、係合爪８０同士の間隔を狭くすることができる。従って、係合爪８０の数を増やすことができる。また、複数の係合爪８０が衝突音を発生するタイミングがずれるので、係合爪８０を増やしても、衝突音の大きさを低減することができる。 (Another embodiment)
In the above embodiment, the engaging claws 80 are formed at equal intervals in the circumferential direction, but the engaging claws 80 may be formed at unequal angles in the circumferential direction. For example, an embodiment in which the angular intervals of the root portions 801 of the four engaging claws 80 are 75 °, 85 °, 95 °, and 105 ° may be adopted. Even in this case, if the lengths of the engaging claws 80 are different, each of the plurality of engaging claws 80 has a gap in the root portion 801 of the adjacent engaging claws 80 in the counterclockwise CCW (one side) around the axis L. The distance between the engaging claws 80 can be narrowed until the overlapping portion 803 is provided on the outer side in the radial direction via G. Therefore, the number of engaging claws 80 can be increased. Further, since the timing at which the plurality of engaging claws 80 generate the collision sound is shifted, the loudness of the collision sound can be reduced even if the number of engaging claws 80 is increased.

（他の実施の形態）
上記実施形態では、排水弁駆動装置１００および排水弁駆動装置１００のラチェット機構４に本発明を適用したが、一方側に付勢された被モータ部材を駆動する駆動装置であれば、排水弁駆動装置以外の駆動装置本発明を適用してもよい。 (Other embodiments)
In the above embodiment, the present invention is applied to the drain valve drive device 100 and the ratchet mechanism 4 of the drain valve drive device 100, but if it is a drive device that drives a motorized member urged on one side, the drain valve drive Drive devices other than devices The present invention may be applied.

上記実施形態では、モータ部１ａからの回転が第２回転部材７から第１回転部材６に伝達される構成になっていたが、モータ部１ａからの回転が第１回転部材６から第２回転部材７に伝達される構成としてもよい。 In the above embodiment, the rotation from the motor unit 1a is transmitted from the second rotating member 7 to the first rotating member 6, but the rotation from the motor unit 1a is transmitted from the first rotating member 6 to the second rotating member 6. It may be configured to be transmitted to the member 7.

上記実施形態では、第２回転部材７とは別体のラチェット部材８に係合爪８０が構成されていたが、第２回転部材７とラチェット部材８とが一体のラチェット部材として構成されていてもよい。 In the above embodiment, the engaging claw 80 is configured on the ratchet member 8 that is separate from the second rotating member 7, but the second rotating member 7 and the ratchet member 8 are configured as an integral ratchet member. May be good.

上記実施形態では、係合爪８０が４つの例を示したが、係合爪８０の数は４つ以外であってもよい。例えば、係合爪８０の数は３つ、５つあるいは６つであってもよい。 In the above embodiment, the number of engaging claws 80 is four, but the number of engaging claws 80 may be other than four. For example, the number of engaging claws 80 may be 3, 5, or 6.

１ａ…モータ部、１ｂ…回転軸、２…輪列、４…ラチェット機構，６…第１回転部材、７…第２回転部材、８…ラチェット部材、１０…クランク部材、２２…第２歯車、３０…ケース体、４１…支軸、６３…係合歯、６６…周壁、８０…係合爪、８１…本体部、１００…排水弁駆動装置、１１０…排水弁、８０１…根元部分、８０２…先端部、８０３…重なり部分、８０６…内周端面、８０７…外周端面、８１１…リブ、８１８…長穴（結合部）、Ｌ…軸線（回転中心軸線）、Ｏ…中心 1a ... motor unit, 1b ... rotating shaft, 2 ... wheel train, 4 ... ratchet mechanism, 6 ... first rotating member, 7 ... second rotating member, 8 ... ratchet member, 10 ... crank member, 22 ... second gear, 30 ... case body, 41 ... support shaft, 63 ... engaging teeth, 66 ... peripheral wall, 80 ... engaging claws, 81 ... main body, 100 ... drain valve drive device, 110 ... drain valve, 801 ... root part, 802 ... Tip part, 803 ... Overlapping part, 806 ... Inner peripheral end face, 807 ... Outer peripheral end face, 811 ... Rib, 818 ... Long hole (joint part), L ... Axis line (rotation center axis), O ... Center

Claims (5)

回転中心軸線を囲む周壁の内周面に複数の係合歯が設けられた第１回転部材と、
前記第１回転部材と同軸状に配置されたラチェット部材と、
を有し、
前記ラチェット部材は、前記周壁の内側に、本体部と、前記本体部に繋がる根元部分から前記回転中心軸線周りの一方側に延在して先端部が前記係合歯に当接する複数の係合爪と、を備え、
前記複数の係合爪は各々、前記回転中心軸線周りの一方側で隣り合う前記係合爪の前記根元部分に隙間を介して径方向外側で重なる重なり部分を有し、
前記係合爪は、前記回転中心軸線から離間した位置を中心とする円弧状に延在していることを特徴とするラチェット機構。 A first rotating member provided with a plurality of engaging teeth on the inner peripheral surface of the peripheral wall surrounding the central axis of rotation, and
A ratchet member arranged coaxially with the first rotating member,
Have,
The ratchet member has a plurality of engagements that extend inside the peripheral wall from the main body portion and the root portion connected to the main body portion to one side around the rotation center axis, and the tip portion abuts on the engaging teeth. With claws,
Each of the plurality of engaging claws has an overlapping portion that overlaps radially outwardly with respect to the root portion of the engaging claws adjacent to each other on one side around the rotation center axis .
The ratchet mechanism is characterized in that the engaging claws extend in an arc shape centered on a position separated from the rotation center axis . 前記第１回転部材と同軸状に配置された第２回転部材を有し、
前記ラチェット部材は、前記本体部に前記第２回転部材との結合部を有していることを特徴とする請求項１に記載のラチェット機構。 It has a second rotating member coaxially arranged with the first rotating member.
The ratchet mechanism according to claim 1, wherein the ratchet member has a joint portion with the second rotating member in the main body portion. 前記係合爪は、前記根元部分から前記回転中心軸線周りの一方側に延在していることを特徴とする請求項１または２に記載のラチェット機構。 The engaging claw is a ratchet mechanism according to claim 1 or 2, characterized in that it extends to one side around the rotation center axis from said root portion. 前記係合爪は、４つ、５つあるいは６つ設けられていることを特徴とする請求項１から３までの何れか一項に記載のラチェット機構。 The ratchet mechanism according to any one of claims 1 to 3 , wherein the engaging claws are provided with four, five or six. 前記根元部分の周方向の寸法が、前記係合爪の前記根元部分より先端側に位置する部分の径方向の寸法より大であることを特徴とする請求項１から４までの何れか一項に記載のラチェット機構。
Any one of claims 1 to 4 , wherein the circumferential dimension of the root portion is larger than the radial dimension of the portion of the engaging claw located on the tip side of the root portion. The ratchet mechanism described in.
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