JP5446497B2

JP5446497B2 - One-way clutch

Info

Publication number: JP5446497B2
Application number: JP2009145243A
Authority: JP
Inventors: 毅伊藤; 泰明阿部; 徹也児玉; 一登小林; 隆藤岡
Original assignee: NSK Ltd
Current assignee: NSK Ltd
Priority date: 2009-06-18
Filing date: 2009-06-18
Publication date: 2014-03-19
Anticipated expiration: 2029-06-18
Also published as: JP2011002019A

Description

本発明は、自動二輪車等のスタータモータ式始動装置や、各種機械の動力伝達装置に組み込まれる一方向クラッチに関する。 The present invention relates to a starter motor type starter such as a motorcycle and a one-way clutch incorporated in a power transmission device of various machines.

自動二輪車等のスタータモータ式始動装置等に一方向クラッチを組み込むことが、従来から行われている（例えば、特許文献１〜３参照）。これらのうち、特許文献１には、図１３に示すような、自動二輪車のエンジンと始動装置との間の動力伝達構造が記載されている。セルモータ１の回転軸２の回転は、歯車伝達機構３及び一方向クラッチ４を介してクランクシャフト５に伝達される。そして、このクランクシャフト５の回転によりエンジンのピストン６が駆動され、エンジンが始動する。一方向クラッチ４は、セルモータ１の始動により、歯車機構３を構成する大歯車７に固定した出力軸８が回転した場合に、この出力軸８の回転をクランクシャフト５に伝達する。一方、エンジン始動後は、これら出力軸８とクランクシャフト５との間で動力の伝達を行わない。 Conventionally, a one-way clutch has been incorporated into a starter motor type starter or the like such as a motorcycle (see, for example, Patent Documents 1 to 3). Among these, Patent Document 1 describes a power transmission structure between an engine and a starter of a motorcycle as shown in FIG. The rotation of the rotating shaft 2 of the cell motor 1 is transmitted to the crankshaft 5 through the gear transmission mechanism 3 and the one-way clutch 4. The piston 6 of the engine is driven by the rotation of the crankshaft 5 and the engine is started. The one-way clutch 4 transmits the rotation of the output shaft 8 to the crankshaft 5 when the output shaft 8 fixed to the large gear 7 constituting the gear mechanism 3 is rotated by the start of the cell motor 1. On the other hand, no power is transmitted between the output shaft 8 and the crankshaft 5 after the engine is started.

特許文献１は、「圧縮コイルバネを収容するためのバネ孔を設けるために凹所とは異なる方向からの加工を要し、加工に手間がかかり製造コストを下げることができなかった」といった、ローラ及びバネの収納部を形成する上での問題点を提示しており（段落〔０００５〕参照）、このような問題点を改善するための手段（形状）を提案している。
図１４及び図１５は、上記各特許文献のうちの特許文献２に記載された一方向クラッチの構造を示す図である。特許文献２に記載された一方向クラッチは、特許文献１と同様の形状を打ち抜き加工する方法を提案するものである。図１４及び図１５に示すように、特許文献２に記載された一方向クラッチ１０４は、外輪１０９と、内輪１１０と、複数のローラ１１１、１１１と、これら各ローラ１１１、１１１と同数のばね１１２、１１２と、カバー１１３とから構成される。このうちの外輪１０９は、例えば、上述のクランクシャフト１０５に接続されるもので、内周面の円周方向複数個所に、それぞれが径方向外方に凹んだ凹入部１１４、１１４を形成している。 Patent Document 1 discloses a roller that “a spring hole for accommodating a compression coil spring is required to be processed from a direction different from the recess, which takes time and is difficult to reduce the manufacturing cost”. And problems in forming the spring housing (see paragraph [0005]), and a means (shape) for improving such problems is proposed.
14 and 15 are views showing the structure of the one-way clutch described in Patent Document 2 among the above-mentioned Patent Documents. The one-way clutch described in Patent Document 2 proposes a method of punching the same shape as Patent Document 1. As shown in FIGS. 14 and 15, the one-way clutch 104 described in Patent Document 2 includes an outer ring 109, an inner ring 110, a plurality of rollers 111 and 111, and the same number of springs 112 as the rollers 111 and 111. , 112 and a cover 113. Of these, the outer ring 109 is connected to, for example, the above-described crankshaft 105, and is formed with recessed portions 114, 114 that are recessed radially outward at a plurality of circumferential positions on the inner peripheral surface. Yes.

また、内輪１１０は、例えば、上述の出力軸１０８に接続されるもので、外輪１０９の内径側に配置される。また、各ローラ１１１、１１１及びばね１１２、１１２は、各凹入部１１４、１１４内にそれぞれ配置される。
また、カバー１１３は、各ローラ１１１、１１１及びばね１１２、１１２が、各凹入部１１４、１１４から脱落しないように、これら各凹入部１１４、１１４を覆うものである。 The inner ring 110 is connected to, for example, the output shaft 108 described above, and is disposed on the inner diameter side of the outer ring 109. The rollers 111 and 111 and the springs 112 and 112 are disposed in the recessed portions 114 and 114, respectively.
The cover 113 covers the recesses 114 and 114 so that the rollers 111 and 111 and the springs 112 and 112 do not fall out of the recesses 114 and 114.

また、各凹入部１１４、１１４の奥面を、それぞれカム面１１５、１１５としている。そして、これら各カム面１１５、１１５と内輪１１０の外周面との間隔を、円周方向一方（図１４及び図１５の反時計まわり）に向かう程小さくしている。各ばね１１２、１１２は、各凹入部１１４、１１４の、上記間隔が大きくなる側の円周方向片側面に一端を当接させた状態で、各ローラ１１１、１１１を上記間隔が小さくなる方向に押圧している。即ち、各凹入部１１４、１１４の円周方向片側面を、それぞれ、各ばね１１２、１１２の弾性力を支承可能な受部としている。 The back surfaces of the recessed portions 114 and 114 are cam surfaces 115 and 115, respectively. The distance between each of the cam surfaces 115 and 115 and the outer peripheral surface of the inner ring 110 is made smaller toward the one side in the circumferential direction (counterclockwise in FIGS. 14 and 15). Each of the springs 112 and 112 is configured so that each of the rollers 111 and 111 decreases in the direction in which the interval decreases, with one end abutting against one side surface in the circumferential direction of the recessed portion 114 and 114 on the side where the interval increases. Pressing. In other words, one side surface in the circumferential direction of each recessed portion 114, 114 is a receiving portion capable of supporting the elastic force of each spring 112, 112, respectively.

上述のように構成される一方向クラッチ４は、次のように作動する。即ち、内輪１１０が外輪１０９に対し、図１４及び図１５の反時計まわりに相対回転する傾向となった場合、各ローラ１１１、１１１が、内輪１１０の外周面と各カム面１１５、１１５との間の間隔が小さい部分に食い込む。この結果、内輪１１０と外輪１０９とがロック状態となり、これら内輪１１０と外輪１０９との間で動力が伝達される。これに対して、この内輪１１０が外輪１０９に対し、図１４及び図１５の時計まわりに相対回転する傾向となった場合、各ローラ１１１、１１１が、上記間隔が大きい部分に向けて変位する傾向となる。この結果、内輪１１０と外輪１０９とがオーバーラン状態となり、これら内輪１１０と外輪１０９との間で動力の伝達が行われなくなる。 The one-way clutch 4 configured as described above operates as follows. That is, when the inner ring 110 tends to rotate counterclockwise in FIG. 14 and FIG. 15 with respect to the outer ring 109, the rollers 111, 111 move between the outer peripheral surface of the inner ring 110 and the cam surfaces 115, 115. I bite into the part where the space between is small. As a result, the inner ring 110 and the outer ring 109 are locked, and power is transmitted between the inner ring 110 and the outer ring 109. On the other hand, when the inner ring 110 tends to rotate relative to the outer ring 109 in the clockwise direction in FIGS. 14 and 15, the rollers 111 and 111 tend to be displaced toward the portion where the interval is large. It becomes. As a result, the inner ring 110 and the outer ring 109 are overrun, and no power is transmitted between the inner ring 110 and the outer ring 109.

一方、図１６は、特許文献３に記載された一方向クラッチの構造を示す図である。図１６に示すように、特許文献３に記載された一方向クラッチは、外輪２０９を板金製としている。即ち、この外輪２０９を構成する、図示しない円輪部の外周緑の円周方向複数個所を折り曲げて部分円筒部２３６、２３６とし、これら各部分円筒部２３６、２３６の中間部をそれぞれ径方向内方に屈曲させることにより、カム面２１５、２１５を形成している。また、各ローラ２１１、２１１及びばね２１２ａ、２１２ａを保持するための保持器２１６を、外輪２０９の内径側に配置している。また、この保持器２１６の円周方向複数個所に、各ローラ２１１、２１１を配置するための収納部２１７、２１７を形成している。また、これら各収納部２１７、２１７にそれぞれ円周方向に亙って形成した有底溝２１８、２１８内の奥部に、各ばね２１２、２１２をそれぞれ配置している。そして、これら各ばね２１２、２１２により、各有底溝２１８、２１８の開口寄り部分に挿通した押圧棒２１９、２１９を介して、各ローラ２１１、２１１に弾性力を付与している。このような図１６に示した構造の一方向クラッチでは、各ばね２１２、２１２の弾性力を支承する受部は、各有底溝２１８、２１８の底面である。 On the other hand, FIG. 16 is a diagram showing the structure of the one-way clutch described in Patent Document 3. As shown in FIG. 16, in the one-way clutch described in Patent Document 3, the outer ring 209 is made of sheet metal. That is, a plurality of circumferential green portions of the outer ring 209 constituting the outer ring 209 are bent to form partial cylindrical portions 236 and 236, and intermediate portions of these partial cylindrical portions 236 and 236 are respectively radially inward. The cam surfaces 215 and 215 are formed by bending in the direction. A cage 216 for holding the rollers 211 and 211 and the springs 212a and 212a is disposed on the inner diameter side of the outer ring 209. In addition, storage portions 217 and 217 for arranging the rollers 211 and 211 are formed at a plurality of locations in the circumferential direction of the cage 216. In addition, the springs 212 and 212 are arranged in the inner portions of the bottomed grooves 218 and 218 formed in the respective storage portions 217 and 217 in the circumferential direction. The springs 212 and 212 apply elastic force to the rollers 211 and 211 through the pressing rods 219 and 219 inserted through the portions near the openings of the bottomed grooves 218 and 218, respectively. In the one-way clutch having the structure shown in FIG. 16, the receiving portions that support the elastic forces of the springs 212 and 212 are the bottom surfaces of the bottomed grooves 218 and 218.

また、外輪２０９と保持器２１６とは、ねじ２２０、２２０により結合している。即ち、この外輪２０９を構成する上記円輪部と、保持器２１６の各収納部２１７、２１７から外れた部分とをねじ２２０、２２０により結合している。上述のような一方向クラッチ４は、次のように作動する。即ち、保持器２１６の内径側に配置される内輪２１０が、外輪２０９に対し、図１６の時計まわりに相対回転する傾向となった場合に、内輪２１０と外輪２０９との間で動力が伝達される。これに対して、この内輪２１０が、外輪２０９に対し、図１６の反時計まわりに相対回転する傾向となった場合に、内輪２１０と外輪２０９との間で動力の伝達が行われなくなる。 Further, the outer ring 209 and the cage 216 are coupled by screws 220 and 220. That is, the above-described circular ring part constituting the outer ring 209 and the part of the retainer 216 that is detached from the storage parts 217 and 217 are coupled by the screws 220 and 220. The one-way clutch 4 as described above operates as follows. That is, when the inner ring 210 disposed on the inner diameter side of the cage 216 tends to rotate relative to the outer ring 209 in the clockwise direction in FIG. 16, power is transmitted between the inner ring 210 and the outer ring 209. The On the other hand, when the inner ring 210 tends to rotate relative to the outer ring 209 in the counterclockwise direction of FIG. 16, power is not transmitted between the inner ring 210 and the outer ring 209.

特開２００４−３４６９５１号公報JP 2004-346951 A 特開２００３−１７２３７７号公報JP 2003-172377 A 特許第２６５６３１３号公報Japanese Patent No. 2656313

しかしながら、上述の特許文献１及び特許文献２に記載された一方向クラッチにおいては、次のような問題があった。
特許文献１及び特許文献２で提案されている一方向クラッチの形状は、外周へ深くなる異形の凹形状である。この形状をリング状の部材から打ち抜き加工で形成しようとすると、カム面が破断面となってしまい、精度が悪くなる。 However, the one-way clutch described in Patent Document 1 and Patent Document 2 described above has the following problems.
The shape of the one-way clutch proposed in Patent Document 1 and Patent Document 2 is a deformed concave shape that deepens to the outer periphery. If this shape is formed from a ring-shaped member by punching, the cam surface becomes a broken surface, and the accuracy deteriorates.

精度を上げようとするならば、別途仕上げ加工が必要となる等のコストＵＰ要素を盛り込まなくてはならない。さらに、ローラとバネの軸方向（外輪の軸方向のこと）の脱落防止が必要な場合は、別途部品を追加する必要がある。総削りにより外輪内周形状を形成することは、コスト高であると考えられる。また、この形状を鍛造で製作しようとするならば、凹凸が大きいため成形応力が大きくなり、カム面の精度が悪くなる。カム面はトルク伝達面であるため、高い形状精度及び面精度が要求される。 In order to increase the accuracy, it is necessary to incorporate cost-up elements such as a need for a separate finishing process. Furthermore, when it is necessary to prevent the rollers and springs from coming off in the axial direction (the axial direction of the outer ring), it is necessary to add additional components. Forming the inner peripheral shape of the outer ring by total cutting is considered to be costly. Further, if this shape is to be manufactured by forging, since the unevenness is large, the molding stress increases, and the accuracy of the cam surface deteriorates. Since the cam surface is a torque transmission surface, high shape accuracy and surface accuracy are required.

また、特許文献２及び特許文献３に記載された一方向クラッチにおいては、次のような理由により、一方向クラッチの製造コストが嵩むという問題があった。特に、特許文献２に記載された一方向クラッチにおいては、図１４及び図１５に示すように、金属製の円筒部材に打ち抜き加工を施して、外輪１０９に凹入部１１４、１１４を形成している。また、凹入部１１４、１１４にローラ１１１、１１１及びばね１１２、１１２を配置するため、これら各凹入部１１４、１１４の深さが大きい。このため、１回の工程でこれら各凹入部１１４、１１４を打ち抜き加工により形成する場合、成形時の応力が大きくなり、これら各凹入部１１４、１１４を精度よく形成することが難しい。また、これら各凹入部１１４、１１４を打ち抜きにより形成しているため、これら各凹入部１１４、１１４の奥面に設けるカム面１１５、１１５に破断面が生じる。このため、これら各カム面１１５、１１５の加工精度を確保しにくい。 Moreover, in the one-way clutch described in Patent Document 2 and Patent Document 3, there is a problem that the manufacturing cost of the one-way clutch increases due to the following reasons. In particular, in the one-way clutch described in Patent Document 2, as shown in FIGS. 14 and 15, a metal cylindrical member is punched to form recessed portions 114 and 114 in the outer ring 109. . Further, since the rollers 111 and 111 and the springs 112 and 112 are disposed in the recessed portions 114 and 114, the depths of the recessed portions 114 and 114 are large. For this reason, when these recessed portions 114 and 114 are formed by punching in a single process, the stress during molding increases, and it is difficult to accurately form the recessed portions 114 and 114. In addition, since each of the recessed portions 114 and 114 is formed by punching, a fracture surface is generated in the cam surfaces 115 and 115 provided on the inner surface of the recessed portions 114 and 114. For this reason, it is difficult to ensure the machining accuracy of these cam surfaces 115 and 115.

これに対して、各凹入部１１４、１１４及び各カム面１１５、１１５を精度よく形成するためには、これら各凹入部１１４、１１４の打ち抜きの工程を複数回に分けて行ったり、打ち抜き後のカム面１１５、１１５の仕上げ加工を十分に行う必要がある等、製造コストが嵩む。
一方、特許文献３に記載された一方向クラッチにおいても、図１６に示すように、保持器２１６に、収納部２１７、２１７、及び有底溝２１８、２１８を別個に形成する必要があり、やはり、製造コストが嵩む。 On the other hand, in order to form each recessed part 114,114 and each cam surface 115,115 with high precision, the process of punching each of these recessed parts 114,114 is performed in multiple times, or after punching. The manufacturing cost increases because it is necessary to sufficiently finish the cam surfaces 115 and 115.
On the other hand, in the one-way clutch described in Patent Document 3, as shown in FIG. 16, it is necessary to separately form the storage portions 217 and 217 and the bottomed grooves 218 and 218 in the cage 216. , Manufacturing costs increase.

また、特許文献３に記載された一方向クラッチにおいては、外輪２０９を構成する円輪部の外周縁複数個所を折り曲げた各部分円筒部２３６、２３６の中間部を屈曲させることにより、カム面２１５を形成するため、このカム面２１５を形成した部分の強度及び剛性は低い。このため、各ローラ２１１、２１１からこのカム面２１５に大きな力が作用した場合に、このカム面２１５を形成した部分が径方向外方に変形して、内輪２１０から外輪２０９に対して動力の伝達が十分に行われない可能性がある。即ち、一方向クラッチ２０４による動力伝達を行う場合（即ち、ロック状態の場合）、各ローラ２１１、２１１が、カム面２１５と内輪２１０の外周面との間の間隔が狭い部分に向けて変位する傾向となる。この場合、各ローラ２１１、２１１からカム面２１５と内輪２１０の外周面とに対し、互いに離れる方向の力が作用する。従って、カム面２１５を形成した部分の強度及び剛性が低い場合、各ローラ２１１、２１１から作用する力により、このカム面２１５を形成した部分が径方向外方に変形し易い。そして、変形した場合には、内輪２１０の回転が、各ローラ２１１、２１１を介して外輪２０９に伝達されにくくなる（即ち、動力の伝達が行われにくくなる）。 Further, in the one-way clutch described in Patent Document 3, the cam surface 215 is bent by bending an intermediate part of each of the partial cylindrical parts 236 and 236 obtained by bending a plurality of outer peripheral edges of the annular part constituting the outer ring 209. Therefore, the strength and rigidity of the portion where the cam surface 215 is formed are low. For this reason, when a large force is applied to the cam surface 215 from each of the rollers 211 and 211, a portion where the cam surface 215 is formed is deformed radially outward, and power is transmitted from the inner ring 210 to the outer ring 209. Communication may not be sufficient. That is, when power is transmitted by the one-way clutch 204 (that is, in the locked state), the rollers 211 and 211 are displaced toward a portion where the distance between the cam surface 215 and the outer peripheral surface of the inner ring 210 is narrow. It becomes a trend. In this case, forces in a direction away from each other act on the cam surface 215 and the outer peripheral surface of the inner ring 210 from the rollers 211 and 211. Accordingly, when the strength and rigidity of the portion where the cam surface 215 is formed are low, the portion where the cam surface 215 is formed is easily deformed radially outward by the force acting from the rollers 211 and 211. And when it deform | transforms, it becomes difficult to transmit rotation of the inner ring | wheel 210 to the outer ring | wheel 209 via each roller 211, 211 (namely, it becomes difficult to transmit power).

そこで、本発明は上記の問題点に着目してなされたものであり、その目的は、外輪のカム面を形成した部分の強度を十分に確保すると共に、この外輪の製造を容易且つ精度よく行え、更には、各種装置に組み付ける作業を容易に行え、製造コストを低くできる一方向クラッチを提供することにある。 Therefore, the present invention has been made paying attention to the above-mentioned problems, and its purpose is to ensure sufficient strength of the portion of the outer ring where the cam surface is formed and to manufacture the outer ring easily and accurately. Furthermore, another object of the present invention is to provide a one-way clutch that can be easily assembled to various devices and can reduce the manufacturing cost.

本発明の請求項１に係る一方向クラッチは、円周方向に沿って凹凸形状をなすカム面を内周面に形成した外輪と、
該外輪の内側に配置される内輪の外周面と前記カム面との間に円周方向に沿って配置された複数のローラと、
前記内輪の外周面と前記カム面との間隔が狭くなる方向に前記複数のローラをそれぞれ押圧する複数の弾性部材と、
前記外輪と前記内輪との間に配置され、円環状の平板部と、前記複数の弾性部材のそれぞれの弾性力を支承可能な複数の受部と、各受部同士の間部分を、前記各ローラ及び前記各弾性部材を収納する収納部とを有する保持器と、を備えた一方向クラッチであって、
板金よりなる前記平板部の外周縁部及び内周縁部に突出して一体に設けられた複数の突片を前記平板部に対してそれぞれ折り曲げることにより前記複数の受部及び前記収納部が形成され、
前記カム面は、金属よりなる外輪の内周面を塑性変形させてなり、
前記保持器が、前記外輪の内周の直線部に対して位相決めされ、前記外輪の内周面に対して係合する爪部が形成された係合面を有し、
前記爪部の一端が前記保持器を前記外輪の内周面に挿入する方向と反対方向を向くように前記保持器の外周縁部から突出し、
弾性体つぶれ防止部が、前記収納部と一体に形成されたことを特徴としている。 The one-way clutch according to claim 1 of the present invention includes an outer ring in which a cam surface having an uneven shape along the circumferential direction is formed on the inner circumferential surface;
A plurality of rollers disposed along a circumferential direction between an outer peripheral surface of an inner ring disposed inside the outer ring and the cam surface;
A plurality of elastic members that respectively press the plurality of rollers in a direction in which the interval between the outer peripheral surface of the inner ring and the cam surface is narrowed;
An annular flat plate portion, a plurality of receiving portions capable of supporting the elastic force of each of the plurality of elastic members, and a portion between each receiving portion are disposed between the outer ring and the inner ring. A one-way clutch comprising a roller and a retainer that houses the elastic members.
The plurality of receiving portions and the storage portion are formed by bending a plurality of projecting pieces integrally provided so as to protrude from the outer peripheral edge portion and the inner peripheral edge portion of the flat plate portion made of sheet metal, respectively ,
The cam surface is formed by plastically deforming the inner peripheral surface of an outer ring made of metal,
The retainer has an engaging surface formed with a claw portion that is phased with respect to the linear portion of the inner periphery of the outer ring and engages with the inner peripheral surface of the outer ring;
One end of the claw portion protrudes from the outer peripheral edge of the retainer so as to face the direction opposite to the direction in which the retainer is inserted into the inner peripheral surface of the outer ring,
The elastic body collapse prevention part is formed integrally with the storage part .

また、本発明の請求項２に係る一方向クラッチは、請求項１に記載の一方向クラッチにおいて、前記弾性部材によって付勢された前記ローラを介して該ローラに２カ所以上の接触点を有するローラ脱落防止部が設けられたことを特徴としている。
また、本発明の請求項３に係る一方向クラッチは、請求項２に記載の一方向クラッチにおいて、前記ローラ脱落防止部は、前記平板部の外周縁部から外方にＬ字状に突出した第１の突片と、前記平板部の外周縁部から外方に突出した第２の突片とを、折り曲げることによって形成されることを特徴としている。 A one-way clutch according to a second aspect of the present invention is the one-way clutch according to the first aspect , wherein the roller has two or more contact points via the roller biased by the elastic member. A roller drop-off prevention unit is provided.
The one-way clutch according to a third aspect of the present invention is the one-way clutch according to the second aspect , wherein the roller drop-off preventing portion protrudes outwardly from an outer peripheral edge portion of the flat plate portion in an L shape. It is characterized by being formed by bending the first projecting piece and the second projecting piece projecting outward from the outer peripheral edge of the flat plate part.

また、本発明の請求項４に係る一方向クラッチは、請求項２に記載の一方向クラッチにおいて、前記ローラ脱落防止部は、前記平板部の外周縁部から外方にＬ字状に突出した第１の突片の先端部を２回折り曲げてなることを特徴としている。 The one-way clutch according to a fourth aspect of the present invention is the one-way clutch according to the second aspect , wherein the roller drop-off preventing portion protrudes outward from an outer peripheral edge portion of the flat plate portion in an L shape. It is characterized in that the tip of the first projecting piece is bent twice .

また、本発明の請求項５に係る一方向クラッチは、請求項１に記載の一方向クラッチにおいて、前記弾性体つぶれ防止部に、折り曲げられた第１の突片に荷重がかけられた際の変形抵抗となる補強部が設けられたことを特徴としている。
また、本発明の請求項６に係る一方向クラッチは、請求項５に記載の一方向クラッチにおいて、前記補強部がリブ構造をなすことを特徴としている。 A one-way clutch according to a fifth aspect of the present invention is the one-way clutch according to the first aspect , wherein a load is applied to the bent first protrusion on the elastic body collapsing prevention portion. It is characterized by the provision of a reinforcing portion that provides deformation resistance.
A one-way clutch according to a sixth aspect of the present invention is the one-way clutch according to the fifth aspect , wherein the reinforcing portion has a rib structure.

また、本発明の請求項７に係る一方向クラッチは、請求項１に記載の一方向クラッチにおいて、前記平板部の周縁部に形成される複数の突片のうち、前記収納部を形成する第１の突片と、前記弾性体を保持する保持部を形成する第３の突片と、該第３の突片と共に前記保持部を形成し、かつ前記受部を形成する第４の突片とが接触していることを特徴としている。 A one-way clutch according to a seventh aspect of the present invention is the one-way clutch according to the first aspect , wherein a plurality of projecting pieces formed on a peripheral edge portion of the flat plate portion forms the storage portion. 1 projecting piece, a third projecting piece that forms a retaining part that retains the elastic body, and a fourth projecting piece that forms the retaining part together with the third projecting piece and forms the receiving part And is in contact with each other.

本発明に係る一方向クラッチによれば、１枚の板金を折り曲げることによって保持器を形成しているため、容易に保持器を作製でき、製造コストを低くすることができる。また、各突部の円周方向片側面を、それぞれ、各弾性部材の弾性力を支承可能な受部としており、弾性部材を配置するための有底溝を設けていないため、保持器の製造コストを低くできる。 According to the one-way clutch according to the present invention, since the cage is formed by bending one sheet metal, the cage can be easily manufactured and the manufacturing cost can be reduced. In addition, since one side surface in the circumferential direction of each protrusion is a receiving portion that can support the elastic force of each elastic member, and no bottomed groove is provided for disposing the elastic member, manufacture of the cage Cost can be lowered.

また、本発明に係る一方向クラッチによれば、外輪のカム面を形成した部分の強度を十分に確保すると共に、この外輪の製造を容易且つ精度よく行え、一方向クラッチの製造コストを低くできる。
即ち、本発明によれば、金属製の円筒部材の内周面を塑性変形させることによりカム面を形成した外輪を用いているため、このカム面を形成した部分の強度を十分に確保できる。この結果、例えば、このカム面に各ローラから力が作用しても、このカム面を形成した部分が変形することを防止して、動力の伝達を十分に行える。 In addition, according to the one-way clutch according to the present invention, the strength of the portion where the cam surface of the outer ring is formed is sufficiently secured, and the outer ring can be manufactured easily and accurately, and the manufacturing cost of the one-way clutch can be reduced. .
That is, according to the present invention, since the outer ring formed with the cam surface is formed by plastically deforming the inner peripheral surface of the metal cylindrical member, the strength of the portion where the cam surface is formed can be sufficiently ensured. As a result, for example, even if a force is applied to the cam surface from each roller, the portion where the cam surface is formed is prevented from being deformed, and the power can be transmitted sufficiently.

また、本発明によれば、保持器に各ローラ及び各弾性部材を配置する収納部を形成しているため、前記外輪に収納部を設ける必要がない。
従って、この外輪の内周面の凹凸（径方向外方への凹入量）を小さくできる。このため、この外輪の素材である円筒（円環）部材の内周面を塑性変形させる加工を容易に行える。また、このように、円筒部材の内周面を塑性変形させることによりカム面を形成しているため、打ち抜きで形成した場合のような破断面が生じることがない。このため、このカム面の仕上げ加工が必要ないか、仕上げ加工を行うにしても僅かで済む。この結果、上記外輪の製造を容易且つ精度よく行える。 In addition, according to the present invention, since the storage portion in which the rollers and the elastic members are arranged is formed in the cage, it is not necessary to provide the storage portion in the outer ring.
Accordingly, it is possible to reduce the unevenness (indentation amount radially outward) on the inner peripheral surface of the outer ring. For this reason, the process which carries out plastic deformation of the internal peripheral surface of the cylindrical (annular) member which is the raw material of this outer ring | wheel can be performed easily. Further, since the cam surface is formed by plastically deforming the inner peripheral surface of the cylindrical member in this way, a fracture surface as in the case of forming by punching does not occur. For this reason, it is not necessary to finish the cam surface, or only a small amount of finishing is required. As a result, the outer ring can be manufactured easily and accurately.

本発明に係る一方向クラッチの第１の実施形態における構成を示す部分断面図である。It is a fragmentary sectional view showing composition in a 1st embodiment of a one way clutch concerning the present invention. 図１（ａ）におけるＡ−Ａ線に沿う断面図である。It is sectional drawing which follows the AA line in Fig.1 (a). 外輪のみを取り出して、（ａ）は保持器側から見た図、（ｂ）は斜視図、（ｃ）は（ｂ）と反対側から見た斜視図である。Only the outer ring is taken out, (a) is a view seen from the cage side, (b) is a perspective view, and (c) is a perspective view seen from the opposite side to (b). 素内向鍔部の内径寄り部分を除去する前の状態を、保持器側から見た図である。It is the figure which looked at the state before removing the part near an inner diameter of a raw inward saddle part from the cage | basket side. 本実施形態における保持器の構成を示す図である。It is a figure which shows the structure of the holder | retainer in this embodiment. 保持器の構成を示す図である。It is a figure which shows the structure of a holder | retainer. 保持器の構成を示す図である。It is a figure which shows the structure of a holder | retainer. （ａ）は円筒部材の正面図、（ｂ）は（ａ）のＢ−Ｂ線に沿う断面図である。(A) is a front view of a cylindrical member, (b) is sectional drawing which follows the BB line of (a). 外輪の加工工程を示す断面図である。It is sectional drawing which shows the manufacturing process of an outer ring | wheel. 本発明に係る一方向クラッチの第２の実施形態における保持器の構成を示す図である。It is a figure which shows the structure of the holder | retainer in 2nd Embodiment of the one-way clutch which concerns on this invention. 本発明に係る一方向クラッチの第３の実施形態における保持器の構成を示す図である。It is a figure which shows the structure of the holder | retainer in 3rd Embodiment of the one-way clutch which concerns on this invention. 本発明に係る一方向クラッチの第４の実施形態における保持器の構成を示す図である。It is a figure which shows the structure of the holder | retainer in 4th Embodiment of the one-way clutch which concerns on this invention. 本発明の対象となる一方向クラッチを組み込む、スタータモータ式始動装置の一例を示す模式図である。It is a mimetic diagram showing an example of a starter motor type starting device incorporating a one-way clutch used as the object of the present invention. 一方向クラッチの従来の構造を示す断面図である。It is sectional drawing which shows the conventional structure of a one-way clutch. 図１４のＣ部拡大図である。It is the C section enlarged view of FIG. 一方向クラッチの従来の構造を示す断面図である。It is sectional drawing which shows the conventional structure of a one-way clutch.

以下、本発明に係る一方向クラッチの実施形態について図面を参照して説明する。
（第１の実施形態）
図１〜図９は、本発明に係る一方向クラッチの第１の実施形態の構成を示す図である。また、図２は、図１（ａ）のＡ−Ａ線に沿う断面図である。なお、図２では、内輪、各ローラ、及び各ばねを省略している。図１〜図９に示すように、本実施形態の一方向クラッチ４は、外輪９と、円柱形をなす複数のローラ１１、１１と、弾性部材である複数のばね１２、１２と、保持器１６とを備える。外輪９は、図２に示すように、円周方向に亙って凹凸形状をなすカム面１５を内周面に有する円筒部２１と、この円筒部２１の軸方向一端部（図２における円筒部２１の右端部）から径方向内方に突出した内向鍔部２２とからなる。尚、円筒部２１と内向鍔部２２とは、一体に形成されている。また、図３では、円筒部２１の全周に亙って内向鍔部２２が形成されるように示しているが、例えば、各ローラ１１、１１及び各ばね１２、１２を配置している個所に対応した部分に、内向鍔部２２を間欠的に形成してもよい。 Embodiments of a one-way clutch according to the present invention will be described below with reference to the drawings.
(First embodiment)
FIGS. 1-9 is a figure which shows the structure of 1st Embodiment of the one-way clutch which concerns on this invention. Moreover, FIG. 2 is sectional drawing which follows the AA line of Fig.1 (a). In FIG. 2, the inner ring, each roller, and each spring are omitted. As shown in FIGS. 1 to 9, the one-way clutch 4 of the present embodiment includes an outer ring 9, a plurality of cylindrical rollers 11 and 11, a plurality of springs 12 and 12 that are elastic members, and a cage. 16. As shown in FIG. 2, the outer ring 9 includes a cylindrical portion 21 having a cam surface 15 having an uneven shape in the circumferential direction on the inner peripheral surface, and one axial end portion of this cylindrical portion 21 (the cylinder in FIG. 2). A right end portion of the portion 21) and an inward flange portion 22 protruding radially inward. The cylindrical portion 21 and the inward flange portion 22 are integrally formed. In FIG. 3, the inward flange portion 22 is formed over the entire circumference of the cylindrical portion 21. For example, the portions where the rollers 11, 11 and the springs 12, 12 are disposed. The inward eaves part 22 may be intermittently formed in the part corresponding to.

図３及び図４に示すように、外輪９を構成する円筒部２１の内周面（カム面１５）の形状は、軸方向から見た場合に略六角形としている。また、円筒部２１の内周面の円周方向に沿って複数個所（例えば、６個所）には、径方向外方に凹んだ凹部２５、２５が形成されている。これら各凹部２５、２５は、それぞれの深さ（径方向外方への凹入量）を、一方の円周方向（図１の反時計まわり）に向かう程深くしている。また、この深くなる程度は、各頂点よりも一方の円周方向（図３（ａ）、４の時計まわり）で緩やかに、各頂点よりも他方の円周方向（図３（ａ）、４の反時計まわり）で急としている。また、円周方向に隣り合う、円周方向に関し深くなる程度が異なる部分同士を、互いに滑らかに連続させている。そして、円周方向に関し深くなる程度が緩やかな部分に、保持器１６の収納部１７、１７を配置し、深くなる程度が急な部分に、同じく各突部２４、２４を配置している。従って、外輪９の内径側に内輪１０を配置した状態で、カム面１５とこの内輪１０の外周面との間隔が、円周方向一方に向かう程大きくなる。このようなカム面１５は、後述する、軸受鋼等の金属製の円筒部材（円環部材）３１（図９、１０（ａ））の内周面に、塑性加工を施すことにより形成している。 As shown in FIGS. 3 and 4, the shape of the inner peripheral surface (cam surface 15) of the cylindrical portion 21 constituting the outer ring 9 is substantially hexagonal when viewed from the axial direction. In addition, recessed portions 25 and 25 that are recessed radially outward are formed at a plurality of locations (for example, 6 locations) along the circumferential direction of the inner peripheral surface of the cylindrical portion 21. Each of these recesses 25, 25 has a depth (amount of recesses radially outward) deeper toward one circumferential direction (counterclockwise in FIG. 1). Further, the degree of the deepening is gentler in one circumferential direction (clockwise in FIG. 3 (a), 4) than each vertex, and in the other circumferential direction (FIG. 3 (a), 4) from each vertex. Counterclockwise) Further, the portions adjacent to each other in the circumferential direction and having different depths in the circumferential direction are smoothly connected to each other. And the accommodating parts 17 and 17 of the holder | retainer 16 are arrange | positioned in the part where the grade which becomes deep with respect to the circumferential direction is loose | gentle, and each protrusion 24 and 24 is similarly arrange | positioned in the part where the degree which becomes deep is steep. Therefore, in a state where the inner ring 10 is disposed on the inner diameter side of the outer ring 9, the distance between the cam surface 15 and the outer peripheral surface of the inner ring 10 increases as it goes in one circumferential direction. Such a cam surface 15 is formed by performing plastic working on the inner peripheral surface of a metal cylindrical member (annular member) 31 (FIGS. 9 and 10A), which will be described later, such as bearing steel. Yes.

また、円筒部２１には、一方向クラッチ４を自動車等の車両に取り付けるためのねじ孔５０が円周方向に複数（例えば、６個所）設けられる（図１，図３，図４，図１１（ａ），図１１（ｂ）参照）。
また、各ローラ１１、１１は、カム面１５と、外輪９の内側に配置される内輪１０の外周面との間の、円周方向複数個所（例えば、６個所）に配置される。また、各ばね１２、１２は、各ローラ１１、１１と同数配置され、これら各ローラ１１、１１を、カム面１５と内輪１０の外周面との間隔が狭くなる方向に、それぞれ押圧するように設置される。 The cylindrical portion 21 is provided with a plurality of screw holes 50 (for example, six locations) in the circumferential direction for attaching the one-way clutch 4 to a vehicle such as an automobile (FIGS. 1, 3, 4, and 11). (See (a) and FIG. 11 (b)).
Each of the rollers 11 and 11 is disposed at a plurality of locations (for example, six locations) in the circumferential direction between the cam surface 15 and the outer peripheral surface of the inner ring 10 disposed inside the outer ring 9. The springs 12 and 12 are arranged in the same number as the rollers 11 and 11 so as to press the rollers 11 and 11 in the direction in which the interval between the cam surface 15 and the outer peripheral surface of the inner ring 10 is reduced. Installed.

外輪９と内輪１０との間に配置される保持器１６は、図５に示すように、平板部２３と、この平板部２３の片側面（図２の右側面）に、円周方向に沿って複数設けられた突部２４及び収納部１７とからなる。なお、収納部１７は、各突部２４、２４同士の間部分を、各ローラ１１、１１及び各ばね１２、１２を収納する領域であり、ローラ１１を保持するローラ脱落防止部４０を含む。また、各突部２４、２４の円周方向片側面（図１の時計まわり側の側面）に、各ばね１２、１２の基端部を保持するための保持部２６、２６を形成している。そして、これら各保持部２６、２６の円周方向側面のうちの内径寄り部分を除く部分を、それぞれ、各ばね１２、１２の弾性力を支承可能な受部２７、２７としている。 As shown in FIG. 5, the retainer 16 disposed between the outer ring 9 and the inner ring 10 extends along the circumferential direction on the flat plate portion 23 and one side surface (right side surface in FIG. 2) of the flat plate portion 23. A plurality of protrusions 24 and storage portions 17 are provided. The storage portion 17 is a region for storing the rollers 11, 11 and the springs 12, 12 between the protrusions 24, 24, and includes a roller drop prevention portion 40 that holds the roller 11. Further, holding portions 26 and 26 for holding the base end portions of the springs 12 and 12 are formed on one side surface in the circumferential direction of each protrusion 24 and 24 (the side surface on the clockwise side in FIG. 1). . And the part except the inner diameter side part among the circumferential direction side surfaces of these holding parts 26 and 26 is set as the receiving parts 27 and 27 which can support the elastic force of each spring 12 and 12, respectively.

ここで、保持器１６は、一枚の板金を折り曲げて作製される。具体的には、図６（ａ）に示すように、円環状をなす平板部２３には、その外周縁部２３ａ及び内周縁部２３ｂに突出して一体に設けられた複数の突片２４ａ〜２４ｄが設けられている。複数の突片２４ａ〜２４ｄは、平板部２３に対してそれぞれ折り曲げられることによって複数の突部２４、及び複数の収納部１７を形成する。平板部２３の外周縁部２３ａには、Ｌ字形状をなす第１の突片２４ａと、矩形状をなす第２の突片２４ｂ、及び第３の突片２４ｃとが設けられている。第１の突片２４ａは、該第１の突片２４ａの側面が、第２の突片２４ｂの連続する二側面に対向するようにＬ字状をなしている。平板部２３の外周縁部２３ａには、時計回りに第２の突片２４ｂ、第１の突片２４ａ、第３の突片２４ｃの順で複数組設置されている。一方、平板部２３の外周縁部２３ａには、第３の突片２４ｃに対応する位置に矩形状をなす第４の突片２４ｄが設けられている。 Here, the cage 16 is produced by bending a single sheet metal. Specifically, as shown in FIG. 6A, a plurality of projecting pieces 24 a to 24 d that are integrally provided to project from the outer peripheral edge portion 23 a and the inner peripheral edge portion 23 b of the annular flat plate portion 23. Is provided. The plurality of protruding pieces 24 a to 24 d are bent with respect to the flat plate portion 23 to form the plurality of protruding portions 24 and the plurality of storage portions 17. The outer peripheral edge portion 23a of the flat plate portion 23 is provided with an L-shaped first projecting piece 24a, a rectangular second projecting piece 24b, and a third projecting piece 24c. The first projecting piece 24a has an L shape so that the side surface of the first projecting piece 24a faces two continuous side surfaces of the second projecting piece 24b. A plurality of sets of the second projecting piece 24b, the first projecting piece 24a, and the third projecting piece 24c are arranged in the clockwise direction on the outer peripheral edge portion 23a of the flat plate portion 23. On the other hand, the outer peripheral edge portion 23a of the flat plate portion 23 is provided with a fourth protruding piece 24d having a rectangular shape at a position corresponding to the third protruding piece 24c.

このように設けられた複数の突片２４ａ〜２４ｄは、図６（ｂ）に示すように、第１の突片２４ａ及び第２の突片２４ｂを平板部２３に対して直立するように折り曲げ、更に、Ｌ字形状をなす第１の突片２４ａの先端部を平板部２３の内方へ折り曲げることによってローラ脱落防止部４０が形成される。すなわち、第１の突片２４ａの先端部、及び第２の突片２４ｂは、ローラ脱落防止部４０としてローラ１１に２カ所以上の接触点を有するようにそれぞれ折り曲げられる。また、第１の突片２４ａの基端部から先端部が折り曲げられた部分までの領域は外輪の内周面に係合する係合面として機能する。一方、平板部２３の外周縁部２３ａに設けられた第３の突片２４ｃと平板部２３の内周縁部２３ｂに設けられた第４の突片２４ｄとが対向するように平板部２３に対してそれぞれ折り曲げ、第４の突片２４ｄの先端部を第３の突片２４ｃに接するように折り曲げることによって収納部１７が形成される。なお、第４の突片２４ｄを折り曲げた先端部は受部２７を形成する。また、第３の突片２４ｃと、第４の突片２４ｄの先端部以外の部分とが保持部２６として機能する。 The plurality of projecting pieces 24 a to 24 d thus provided are bent so that the first projecting piece 24 a and the second projecting piece 24 b stand upright with respect to the flat plate portion 23, as shown in FIG. Furthermore, the roller drop-off prevention portion 40 is formed by bending the tip portion of the L-shaped first protrusion 24 a inward of the flat plate portion 23. That is, the tip end portion of the first projecting piece 24 a and the second projecting piece 24 b are each bent so as to have two or more contact points on the roller 11 as the roller drop-off preventing portion 40. Moreover, the area | region from the base end part of the 1st protrusion 24a to the part by which the front-end | tip part was bent functions as an engagement surface engaged with the internal peripheral surface of an outer ring | wheel. On the other hand, the third protruding piece 24c provided on the outer peripheral edge portion 23a of the flat plate portion 23 and the fourth protruding piece 24d provided on the inner peripheral edge portion 23b of the flat plate portion 23 are opposed to the flat plate portion 23. Then, the storage portion 17 is formed by bending each of the four protruding pieces 24d so as to be in contact with the third protruding piece 24c. Note that the distal end portion of the fourth projecting piece 24d that is bent forms a receiving portion 27. Further, the third projecting piece 24c and a portion other than the tip of the fourth projecting piece 24d function as the holding unit 26.

このように構成された保持器１６の各収納部１７、１７内に各ばね１２、１２を配置する場合には、図６（ｃ）に示すように、これら各ばね１２、１２の基端部を各受部２７、２７に当接させる。そして、各収納部１７、１７内に各ローラ１１、１１及び各ばね１２、１２を配置した状態で、これら各ばね１２、１２によりこれら各ローラ１１、１１を、各突部２４、２４の円周方向他側面（図１の反時計まわり側の側面）に向けて押圧する。 When the springs 12 and 12 are arranged in the storage portions 17 and 17 of the cage 16 configured in this way, as shown in FIG. 6C, the base end portions of the springs 12 and 12 are arranged. Are brought into contact with the receiving portions 27, 27. And in the state which has arrange | positioned each roller 11 and 11 and each spring 12 and 12 in each accommodating part 17 and 17, these each roller 11 and 11 is made into the circle | round | yen of each protrusion 24 and 24 by these each spring 12 and 12. Press toward the other side surface in the circumferential direction (the side surface on the counterclockwise side in FIG. 1).

また、本実施形態の保持器１６には、図７（ａ）に示すように、外輪９の内周面に係合する爪部２８が突片２４ａ（係合面）に形成されている。爪部２８は、突片２４ａから切り欠かれて形成される。爪部２８は、その一端が保持器１６を外輪９の内周面に挿入する方向と反対方向を向くように保持器１６の外周縁部から突出している。
外輪９と保持器１６とを結合する場合には、まず、保持器１６の収納部１７、１７内に、各ローラ１１、１１及び各ばね１２、１２を配置しつつ、外輪９と保持器１６とを重ね合わせる。次に、外輪９の内周面の直線部と突片２４ａとを位相決めし、図７（ｂ）に示すように、保持器１６を挿入して爪部２８を外輪９と係合させる。この結果、外輪９と保持器１６とが、内部に各ローラ１１、１１及び各ばね１２、１２を配置した状態で結合される。 Further, as shown in FIG. 7A, the retainer 16 of the present embodiment is formed with a claw portion 28 that engages with the inner peripheral surface of the outer ring 9 on the projecting piece 24a (engagement surface). The claw portion 28 is formed by notching from the projecting piece 24a. The claw portion 28 protrudes from the outer peripheral edge portion of the retainer 16 so that one end thereof faces in a direction opposite to the direction in which the retainer 16 is inserted into the inner peripheral surface of the outer ring 9.
When the outer ring 9 and the cage 16 are combined, first, the rollers 11 and 11 and the springs 12 and 12 are disposed in the storage portions 17 and 17 of the cage 16, while the outer ring 9 and the cage 16 are arranged. And overlay. Next, the linear portion of the inner peripheral surface of the outer ring 9 and the projecting piece 24 a are phased, and the retainer 16 is inserted to engage the claw portion 28 with the outer ring 9 as shown in FIG. As a result, the outer ring 9 and the cage 16 are coupled together with the rollers 11 and 11 and the springs 12 and 12 disposed therein.

また、本実施形態では、外輪９と保持器１６ａとを結合した状態で、各ローラ１１、１１及び各ばね１２、１２が、外輪９の内向鍔部２２と保持器１６の平板部２３との間に配置される。すなわち、各ローラ１１、１１及び各ばね１２、１２を配置する、各収納部１７、１７の軸方向（図２の左右方向）両側を、内向鍔部２２と平板部２３とにより覆っている。 In the present embodiment, the rollers 11, 11 and the springs 12, 12 are connected between the inward flange portion 22 of the outer ring 9 and the flat plate portion 23 of the cage 16 in a state where the outer ring 9 and the cage 16 a are coupled. Arranged between. That is, both sides of the storage portions 17 and 17 in the axial direction (left and right direction in FIG. 2) where the rollers 11 and 11 and the springs 12 and 12 are arranged are covered with the inward flange portion 22 and the flat plate portion 23.

上述のように構成される本実施形態の一方向クラッチ４の場合、図１４〜図１６に記載した従来の一方向クラッチと同様に、内輪１０が外輪９に対し、図１の時計まわりに相対回転する傾向となった場合、各ローラ１１、１１が、内輪１０の外周面とカム面１５との間隔が小さい部分に食い込む。この結果、内輪１０と外輪９とがロック状態となり、これら内輪１０と外輪９ｂとの間で動力が伝達される。これに対して、この内輪１０が外輪９に対し、図１の反時計まわりに相対回転する傾向となった場合には、各ローラ１１、１１が、上記間隔が大きい部分に向けて変位する傾向となる。この結果、内輪１０と外輪９とがオーバーラン状態となり、これら内輪１０と外輪９との間で動力の伝達が行われなくなる。 In the case of the one-way clutch 4 of the present embodiment configured as described above, the inner ring 10 is relative to the outer ring 9 in the clockwise direction of FIG. 1 as in the conventional one-way clutch described in FIGS. When it becomes the tendency to rotate, each roller 11 and 11 bites into the part where the space | interval of the outer peripheral surface of the inner ring | wheel 10 and the cam surface 15 is small. As a result, the inner ring 10 and the outer ring 9 are locked, and power is transmitted between the inner ring 10 and the outer ring 9b. On the other hand, when the inner ring 10 tends to rotate relative to the outer ring 9 in the counterclockwise direction of FIG. 1, the rollers 11 and 11 tend to be displaced toward the portion where the interval is large. It becomes. As a result, the inner ring 10 and the outer ring 9 are overrun, and no power is transmitted between the inner ring 10 and the outer ring 9.

上述のように構成され作用する本実施形態の一方向クラッチ４の製造方法について、図８及び図９により説明する。
まず、図８に示すような、内径が外輪９のカム面１５の内接円の直径よりも小さい金属製の円筒部材３１を、図９（ａ）に示すように、台座３２上に載置した状態で、外周面をダイ３３により拘束する。この状態で、図９（ｂ）に示すように、円筒部材３１の内径寄り部分にパンチ３４を、軸方向に押し込む。このパンチ３４の外周面は、外輪９の円筒部２１の内周面に見合った（断面の輪郭が同じで凹凸が逆となった）形状を有する。このため、パンチ３４の押し込みにより、円筒部材３１の内周面に、外輪９のカム面１５が形成される。また、本実施形態では、このようなパンチ３４の押し込みにより生じた円筒部材３１の内径寄りの余肉部分を、円筒部材３１の一端側（図９の下端側）に移動させる。 A method for manufacturing the one-way clutch 4 configured and operated as described above will be described with reference to FIGS.
First, as shown in FIG. 8, a metal cylindrical member 31 whose inner diameter is smaller than the diameter of the inscribed circle of the cam surface 15 of the outer ring 9 is placed on the pedestal 32 as shown in FIG. In this state, the outer peripheral surface is restrained by the die 33. In this state, as shown in FIG. 9B, the punch 34 is pushed into the portion near the inner diameter of the cylindrical member 31 in the axial direction. The outer peripheral surface of the punch 34 has a shape commensurate with the inner peripheral surface of the cylindrical portion 21 of the outer ring 9 (the contour of the cross section is the same and the unevenness is reversed). For this reason, the cam surface 15 of the outer ring 9 is formed on the inner peripheral surface of the cylindrical member 31 by pushing the punch 34. Further, in the present embodiment, the surplus portion near the inner diameter of the cylindrical member 31 generated by the pressing of the punch 34 is moved to one end side (lower end side in FIG. 9) of the cylindrical member 31.

上述のような余肉部分を円筒部材３１の一端部に移動させることにより、この円筒部材３１の一端部が、カム面１５よりも径方向内方に突出し、この円筒部材３１の一端部に素内向鍔部３５が形成される。即ち、円筒部材３１の外周面は、ダイ３３により拘束されているため、パンチ３４の押し込みにより、円筒部材３１の内径寄りの余肉が、この円筒部材３１の一端部（梨子地部分）に流れる。この結果、この円筒部材３１の一端部が径方向内方に突出し、素内向鍔部３５が形成される。尚、本実施形態では、円筒部材３１の他端面（図９の上端面）を、抑え部材（図示せず）により抑え付ける等して、パンチ３４の押し込みにより円筒部材３１の軸方向（図９の上下方向）の厚さが変化しないようにしている。このため、この円筒部材３１の厚さは、加工後の外輪９の厚さと同じとしている。 By moving the surplus portion as described above to one end portion of the cylindrical member 31, one end portion of the cylindrical member 31 protrudes inward in the radial direction from the cam surface 15. An inward flange 35 is formed. That is, since the outer peripheral surface of the cylindrical member 31 is constrained by the die 33, when the punch 34 is pushed in, surplus material near the inner diameter of the cylindrical member 31 flows to one end portion (pear paste portion) of the cylindrical member 31. . As a result, one end portion of the cylindrical member 31 protrudes inward in the radial direction, and the inwardly facing flange portion 35 is formed. In the present embodiment, the other end surface (upper end surface in FIG. 9) of the cylindrical member 31 is pressed by a pressing member (not shown), and the axial direction of the cylindrical member 31 (FIG. 9) is pushed. The thickness in the vertical direction) is not changed. For this reason, the thickness of the cylindrical member 31 is the same as the thickness of the outer ring 9 after processing.

上述のようなパンチ３４による加工の後、図９（ｃ）に示すように、素内向鍔部３５の内径寄り部分を、別のパンチ３４ａにより打ち抜いて除去する。このパンチ３４ａの外径は、外輪９の内向鍔部２２の内径と同じとしている。このため、素内向鍔部３５をパンチ３４ａにより打ち抜くことにより、所定の内径を有する内向鍔部２２が形成される。このように得られた外輪９を、各ローラ１１、１１及び各ばね１２、１２を内部に配置した状態で、保持器１６と結合し、一方向クラッチ４とする。 After the processing by the punch 34 as described above, as shown in FIG. 9C, the portion closer to the inner diameter of the inner inwardly facing flange portion 35 is punched and removed by another punch 34a. The outer diameter of the punch 34 a is the same as the inner diameter of the inward flange portion 22 of the outer ring 9. For this reason, the inward flange portion 22 having a predetermined inner diameter is formed by punching the raw inward flange portion 35 with the punch 34a. The outer ring 9 obtained in this way is combined with the cage 16 with the rollers 11 and 11 and the springs 12 and 12 disposed therein to form a one-way clutch 4.

本実施形態の一方向クラッチ４によれば、外輪９のカム面１５を形成した部分の強度を十分に確保すると共に、この外輪９の製造を容易且つ精度よく行え、一方向クラッチ４の製造コストを低くできる。
即ち、本実施形態では、金属製の円筒部材３１の内周面を塑性変形させることによりカム面１５を形成し、外輪９としている。このため、特許文献３に記載された一方向クラッチ（図１６参照）のような、部分円筒部２３６、２３６の中間部を屈曲させてカム面２１５を形成した構造と比べて、カム面１５を形成した部分の強度及び剛性を十分に確保できる。また、本実施形態では、内向鍔部２２を、カム面１５を有する円筒部２１と一体に形成しているため、外輪９の強度及び剛性が向上し、このカム面１５を形成した部分を、より変形しにくくできる。この結果、内輪１０から外輪９に動力が伝達される際に、各ローラ１１、１１からカム面１５に力が作用しても、このカム面１５を形成した部分が径方向外方に変形することを防止して、一方向クラッチ４による動力の伝達を十分に行える。 According to the one-way clutch 4 of the present embodiment, the strength of the portion where the cam surface 15 of the outer ring 9 is formed is sufficiently secured, and the outer ring 9 can be manufactured easily and accurately. Can be lowered.
That is, in this embodiment, the cam surface 15 is formed by plastically deforming the inner peripheral surface of the metal cylindrical member 31, and the outer ring 9 is formed. For this reason, the cam surface 15 is compared with the one-way clutch described in Patent Document 3 (see FIG. 16) in comparison with the structure in which the cam surface 215 is formed by bending the intermediate portions of the partial cylindrical portions 236 and 236. The strength and rigidity of the formed part can be sufficiently secured. In this embodiment, since the inward flange 22 is formed integrally with the cylindrical portion 21 having the cam surface 15, the strength and rigidity of the outer ring 9 are improved, and the portion where the cam surface 15 is formed is More difficult to deform. As a result, when power is transmitted from the inner ring 10 to the outer ring 9, even if force is applied to the cam surface 15 from each of the rollers 11, 11, the portion where the cam surface 15 is formed is deformed radially outward. This prevents the power from being transmitted by the one-way clutch 4 sufficiently.

また、本実施形態では、保持器１６に各ローラ１１、１１及び各ばね１２、１２を配置する収納部１７、１７を形成しているため、外輪９のような収納部を設ける必要がない。従って、この外輪９の円筒部２１の内周面にはカム面１５を形成するだけでよく、この円筒部２１の内周面の凹凸を小さくできる。即ち、この円筒部２１の内周面に形成するのは、各収納部１７、１７と比べて凹凸の大きさが小さい（円周方向に関して内径の変化量が少ない）凹部２５、２５から構成されるカム面１５のみである。従って、外輪９の成形時の応力を小さくでき、１回のパンチの押し込みにより、カム面１５を、容易且つ精度よく形成できる。 Moreover, in this embodiment, since the accommodating parts 17 and 17 which arrange | position each roller 11 and 11 and each spring 12 and 12 are formed in the holder | retainer 16, it is not necessary to provide an accommodating part like the outer ring | wheel 9. FIG. Therefore, it is only necessary to form the cam surface 15 on the inner peripheral surface of the cylindrical portion 21 of the outer ring 9, and the unevenness of the inner peripheral surface of the cylindrical portion 21 can be reduced. That is, what is formed on the inner peripheral surface of the cylindrical portion 21 is constituted by the concave portions 25 and 25 that have a small unevenness (the amount of change in the inner diameter in the circumferential direction is small) compared to the storage portions 17 and 17. Only the cam surface 15 is provided. Therefore, the stress during molding of the outer ring 9 can be reduced, and the cam surface 15 can be easily and accurately formed by pressing the punch once.

また、本実施形態では、円筒部材３１の内周面を塑性変形させることによりカム面１５を形成しているため、カム面を打ち抜きで形成した、図１４及び図１５に示した一方向クラッチの従来構造のような破断面が生じることがない。このため、カム面１５の仕上げ加工が必要ないか、仕上げ加工を行うにしても僅かで済む。また、本実施形態では、カム面１５の形成と同時に素内向鍔部３５も形成でき、その後、この素内向鍔部３５の内径寄り部分を除去するだけで内向鍔部２２を得られる。従って、本実施形態では、外輪９を形成するための加工工数を少なくできる。この結果、外輪９の製造を、低コストで、容易且つ精度よく行える。 In the present embodiment, since the cam surface 15 is formed by plastically deforming the inner peripheral surface of the cylindrical member 31, the cam surface is formed by punching, and the one-way clutch shown in FIGS. The fracture surface as in the conventional structure does not occur. For this reason, the finishing of the cam surface 15 is not necessary, or even if the finishing is performed, only a small amount is required. In the present embodiment, the inner inwardly facing flange portion 35 can be formed simultaneously with the formation of the cam surface 15, and then the inwardly facing flange portion 22 can be obtained simply by removing the portion closer to the inner diameter of the inner inwardly facing flange portion 35. Therefore, in the present embodiment, the number of processing steps for forming the outer ring 9 can be reduced. As a result, the outer ring 9 can be manufactured easily and accurately at low cost.

また、本実施形態における保持器１６は、１枚の板金を折り曲げることによって保持器を形成しているため、容易に保持器を作製でき、製造コストを低くすることができる。尚、本実施形態では、各突部２４、２４の円周方向片側面を、それぞれ、各ばね１２、１２の弾性力を支承可能な受部２７、２７としている。即ち、特許文献３に記載された一方向クラッチ（図１６参照）のように、ばね２１２、２１２を配置するための有底溝２１８、２１８を設けていない。このため、保持器１６の製造コストを低くできる。 Moreover, since the holder | retainer 16 in this embodiment forms the holder | retainer by bending one sheet metal, a holder | retainer can be produced easily and manufacturing cost can be reduced. In this embodiment, one side surface in the circumferential direction of each protrusion 24, 24 is a receiving portion 27, 27 capable of supporting the elastic force of each spring 12, 12. That is, unlike the one-way clutch described in Patent Document 3 (see FIG. 16), the bottomed grooves 218 and 218 for disposing the springs 212 and 212 are not provided. For this reason, the manufacturing cost of the retainer 16 can be reduced.

本実施形態では、上述のように外輪９を、このように保持器１６を、それぞれ容易に得られるため、一方向クラッチ４の製造コストを低く抑えられる。
また、本実施形態では、外輪９に内向鍔部２２を一体に形成し、各ローラ１１、１１及び各ばね１２、１２を、この内向鍔部２２と保持器１６の平板部２３との間に配置している。このため、前述の一方向クラッチの従来の構造（図１４及び１５参照）のように、別途、カバー等を設けることなく、各ローラ１１、１１及び各ばね１２、１２が、保持器１６の各収納部１７、１７から脱落することを防止できる。 In this embodiment, since the outer ring 9 and the cage 16 can be easily obtained as described above, the manufacturing cost of the one-way clutch 4 can be kept low.
In the present embodiment, the inward flange portion 22 is formed integrally with the outer ring 9, and the rollers 11, 11 and the springs 12, 12 are disposed between the inward flange portion 22 and the flat plate portion 23 of the cage 16. It is arranged. For this reason, as in the conventional structure of the one-way clutch described above (see FIGS. 14 and 15), the rollers 11 and 11 and the springs 12 and 12 are connected to the cage 16 without providing a cover or the like. It is possible to prevent the storage parts 17 and 17 from falling off.

（第２の実施形態）
図１０は、本発明に係る一方向クラッチの第２の実施形態の構成を示す図である。本実施形態は、保持器１６の構成が上述の第１の実施形態と異なるのみであるので、他の構成についての説明は省略する。 (Second Embodiment)
FIG. 10 is a diagram showing a configuration of a second embodiment of the one-way clutch according to the present invention. In the present embodiment, only the configuration of the cage 16 is different from that of the first embodiment described above, and thus description of other configurations is omitted.

本実施形態においても、保持器１６は、一枚の板金を折り曲げて作製される。具体的には、図１０（ａ）に示すように、円環状をなす平板部２３には、その外周縁部２３ａ及び内周縁部２３ｂに突出して一体に設けられた複数の突片２４ａ，２４ｃ，２４ｄが設けられている。複数の突片２４ａ，２４ｃ，２４ｄは、平板部２３に対してそれぞれ折り曲げられることによって複数の突部２４、及び複数の収納部１７を形成する。平板部２３の外周縁部２３ａには、Ｌ字形状をなす第１の突片２４ａと、第３の突片２４ｃとが設けられている。第１の突片２４ａは、第１の実施形態よりも大判のＬ字状をなしている。平板部２３の外周縁部２３ａには、時計回りに第１の突片２４ａ、第３の突片２４ｃの順で複数組設置されている。一方、平板部２３の外周縁部２３ａには、第３の突片２４ｃに対応する位置に矩形状をなす第４の突片２４ｄが設けられている。 Also in this embodiment, the cage 16 is produced by bending a single sheet metal. Specifically, as shown in FIG. 10 (a), a plurality of projecting pieces 24a and 24c provided integrally on the outer peripheral edge portion 23a and the inner peripheral edge portion 23b of the flat plate portion 23 forming an annular shape. , 24d are provided. The plurality of protrusions 24 a, 24 c, and 24 d are bent with respect to the flat plate portion 23 to form a plurality of protrusions 24 and a plurality of storage portions 17. The outer peripheral edge portion 23a of the flat plate portion 23 is provided with an L-shaped first projecting piece 24a and a third projecting piece 24c. The first protruding piece 24a has a larger L-shape than the first embodiment. A plurality of sets are installed on the outer peripheral edge portion 23a of the flat plate portion 23 in the order of the first projecting piece 24a and the third projecting piece 24c in the clockwise direction. On the other hand, the outer peripheral edge portion 23a of the flat plate portion 23 is provided with a fourth protruding piece 24d having a rectangular shape at a position corresponding to the third protruding piece 24c.

このように設けられた複数の突片２４ａ，２４ｃ，２４ｄは、図１０（ｂ）に示すように、第１の突片２４ａを平板部２３に対して直立するように折り曲げ、更に、Ｌ字形状をなす第１の突片２４ａの先端部を平板部２３の内方へ２回折り曲げることによってローラ脱落防止部４０が形成される。すなわち、第１の突片２４ａの先端部は、ローラ脱落防止部４０としてローラ１１に２カ所以上の接触点を有するように２回折り曲げられる。一方、平板部２３の外周縁部２３ａに設けられた第３の突片２４ｃと平板部２３の内周縁部２３ｂに設けられた第４の突片２４ｄとが対向するように平板部２３に対してそれぞれ折り曲げ、第４の突片２４ｄの先端部を第３の突片２４ｃに接するように折り曲げることによって収納部１７が形成される。なお、第４の突片２４ｄを折り曲げた先端部は受部２７を形成する。また、第３の突片２４ｃと、第４の突片２４ｄの先端部以外の部分とが保持部２６として機能する。 The plurality of projecting pieces 24a, 24c, and 24d provided in this manner are bent so that the first projecting piece 24a stands upright with respect to the flat plate portion 23 as shown in FIG. The roller drop-off prevention part 40 is formed by bending the tip part of the first projecting piece 24 a having a shape inwardly into the flat plate part 23 twice. That is, the tip of the first projecting piece 24 a is bent twice so that the roller 11 has two or more contact points as the roller drop-off prevention unit 40. On the other hand, the third protruding piece 24c provided on the outer peripheral edge portion 23a of the flat plate portion 23 and the fourth protruding piece 24d provided on the inner peripheral edge portion 23b of the flat plate portion 23 are opposed to the flat plate portion 23. Then, the storage portion 17 is formed by bending each of the four protruding pieces 24d so as to be in contact with the third protruding piece 24c. Note that the distal end portion of the fourth projecting piece 24d that is bent forms a receiving portion 27. Further, the third projecting piece 24c and a portion other than the tip of the fourth projecting piece 24d function as the holding unit 26.

図１１（ａ）〜（ｃ）は、本発明に係る一方向クラッチの第３の実施形態の構成を示す図である。本実施形態は、保持器１６の構成が上述の第２の実施形態と異なるのみであるので、他の構成についての説明は省略する。図１１（ａ）に示すように、一方向クラッチ４のリリース時に、ばね１２にかかるローラ１１の付勢力を制限する弾性体つぶれ防止部４１として、第３の突片２４ｃ及び第４の突片２４ｄのローラ１１側の端部を折り曲げてもよい。尚、第４の突片２４ｄによって形成される受部２７から折り曲げ部分までの距離は、ばね１２の最大収縮寸法よりも長く設定される。 FIGS. 11A to 11C are views showing the configuration of the third embodiment of the one-way clutch according to the present invention. In the present embodiment, only the configuration of the cage 16 is different from that of the above-described second embodiment, and thus description of other configurations is omitted. As shown in FIG. 11 (a), the third protrusion 24c and the fourth protrusion are used as an elastic body collapsing prevention part 41 that restricts the urging force of the roller 11 applied to the spring 12 when the one-way clutch 4 is released. You may bend | fold the edge part by the side of the roller 11 of 24d. The distance from the receiving portion 27 formed by the fourth projecting piece 24d to the bent portion is set longer than the maximum contraction dimension of the spring 12.

また、図１１（ｂ）に示すように、第４の突片２４ｄと、第１の突片２４ａ及び第３の突片２４ｃとを接触させてもよい。このような構成とすることにより、一方向クラッチ４のリリース時に、弾性体つぶれ防止部４１に作用する荷重を第１の突片２４ａ、第３の突片２４ｃ、及び第４の突片２４ｄで同時に受けることができる。
また、図１１（ｃ）に示すように、弾性体つぶれ防止部４１には、ローラ１１の付勢力に対向するための補強材として、リブ４２が設けられてもよい。 Further, as shown in FIG. 11B, the fourth projecting piece 24d may be brought into contact with the first projecting piece 24a and the third projecting piece 24c. With such a configuration, when the one-way clutch 4 is released, the load acting on the elastic body collapsing prevention portion 41 is applied to the first projecting piece 24a, the third projecting piece 24c, and the fourth projecting piece 24d. You can receive it at the same time.
Moreover, as shown in FIG.11 (c), the elastic body crush prevention part 41 may be provided with the rib 42 as a reinforcing material for opposing the urging | biasing force of the roller 11. As shown in FIG.

図１２は、本発明に係る一方向クラッチの第４の実施形態の構成を示す図であり、（ａ）は保持器１６の全体構成を示す斜視図、（ｂ）は保持器１６の突片２４ａ（係合面）部分を示す斜視図、（ｃ）は保持器１６の突片２４ａ（係合面）の断面図である。本実施形態は、保持器１６の構成が上述の第２の実施形態と異なるのみであるので、他の構成についての説明は省略する。図１２（ａ）〜（ｃ）に示すように、保持器１６の突片２４ａ（係合面）には、前述した爪部２８の代わりに、外輪９の内周面に係合する突起部４３が形成されてもよい。突起部４３は、突片２４ａから突出して形成される。突起部４３も、爪部２８と同様に、外輪９と保持器１６とを結合する場合には、外輪９の内周面の直線部と位置決めされた突片２４ａ（係合面）とが位相決めされるので、保持器１６を挿入したときに外輪９と係合される。 12A and 12B are diagrams showing the configuration of the fourth embodiment of the one-way clutch according to the present invention, wherein FIG. 12A is a perspective view showing the overall configuration of the cage 16, and FIG. 12B is a protruding piece of the cage 16. FIG. 24C is a perspective view showing a portion 24a (engagement surface), and FIG. 8C is a cross-sectional view of the protruding piece 24a (engagement surface) of the cage 16. In the present embodiment, only the configuration of the cage 16 is different from that of the above-described second embodiment, and thus description of other configurations is omitted. As shown in FIGS. 12A to 12C, the protrusion 24 a (engagement surface) of the retainer 16 has a protrusion that engages with the inner peripheral surface of the outer ring 9 instead of the claw portion 28 described above. 43 may be formed. The protruding portion 43 is formed to protrude from the protruding piece 24a. Similarly to the claw portion 28, when the outer ring 9 and the retainer 16 are coupled to the protrusion 43, the linear portion of the inner peripheral surface of the outer ring 9 and the positioned protruding piece 24 a (engagement surface) are in phase. Therefore, when the retainer 16 is inserted, it is engaged with the outer ring 9.

以上、本発明の実施の形態について説明してきたが、本発明はこれに限定されずに、種々の変更、改良を行うことができる。例えば、上述の各実施形態では、それぞれローラ１１、１１が６個の構造について説明したが、各ローラ１１、１１の数はこれらに限定されることなく、目的に応じて適宜設定される。 As mentioned above, although embodiment of this invention has been described, this invention is not limited to this, A various change and improvement can be performed. For example, in each of the above-described embodiments, the structure of the six rollers 11 and 11 has been described. However, the number of the rollers 11 and 11 is not limited thereto, and is appropriately set according to the purpose.

１セルモータ
２回転軸
３歯車伝達機構
４一方向クラッチ
５クランクシャフト
６ピストン
７大歯車
８出力軸
９外輪
１０内輪
１１ローラ
１２ばね（弾性体）
１４凹入部
１５カム面
１６保持器
１７収納部
２１円筒部
２２内向鍔部
２３平板部
２４突部
２４ａ第１の突片
２４ｂ第２の突片
２４ｃ第３の突片
２４ｄ第４の突片
２５凹部
２６保持部
２７受部
２８爪部
３１円筒部材
３２台座
３３ダイ
３４パンチ
３５素内向鍔部
４０ローラ脱落防止部
４１弾性体つぶれ防止部
４２リブ
４３突起部 DESCRIPTION OF SYMBOLS 1 Cell motor 2 Rotating shaft 3 Gear transmission mechanism 4 One-way clutch 5 Crankshaft 6 Piston 7 Large gear 8 Output shaft 9 Outer ring 10 Inner ring 11 Roller 12 Spring (elastic body)
14 recessed portion 15 cam surface 16 cage 17 storage portion 21 cylindrical portion 22 inward flange portion 23 flat plate portion 24 projection portion 24a first projection piece 24b second projection piece 24c third projection piece 24d fourth projection piece 25 Concave part 26 Holding part 27 Receiving part 28 Claw part 31 Cylindrical member 32 Base 33 Die 34 Punch 35 Element inwardly facing part 40 Roller fall prevention part 41 Elastic body crush prevention part 42 Rib 43 Protrusion part

Claims

An outer ring formed on the inner peripheral surface with a cam surface having an irregular shape along the circumferential direction;
A plurality of rollers disposed along a circumferential direction between an outer peripheral surface of an inner ring disposed inside the outer ring and the cam surface;
A plurality of elastic members that respectively press the plurality of rollers in a direction in which the interval between the outer peripheral surface of the inner ring and the cam surface is narrowed;
An annular flat plate portion, a plurality of receiving portions capable of supporting the elastic force of each of the plurality of elastic members, and a portion between each receiving portion are disposed between the outer ring and the inner ring. A one-way clutch comprising a roller and a retainer that houses the elastic members.
The plurality of receiving portions and the storage portion are formed by bending a plurality of projecting pieces integrally provided so as to protrude from the outer peripheral edge portion and the inner peripheral edge portion of the flat plate portion made of sheet metal, respectively ,
The cam surface is formed by plastically deforming the inner peripheral surface of an outer ring made of metal,
The retainer has an engaging surface formed with a claw portion that is phased with respect to the linear portion of the inner periphery of the outer ring and engages with the inner peripheral surface of the outer ring;
One end of the claw portion protrudes from the outer peripheral edge of the retainer so as to face the direction opposite to the direction in which the retainer is inserted into the inner peripheral surface of the outer ring,
A one-way clutch characterized in that an elastic collapsing prevention part is formed integrally with the storage part .

2. The one-way clutch according to claim 1, wherein a roller drop prevention portion having two or more contact points is provided on the roller via the roller biased by the elastic member .

The roller drop-off preventing portion includes a first protrusion piece that protrudes outward in an L shape from the outer peripheral edge portion of the flat plate portion, and a second protrusion piece that protrudes outward from the outer peripheral edge portion of the flat plate portion. The one-way clutch according to claim 2 , wherein the one-way clutch is formed by bending .

The roller disengagement prevention part is one according to claim 2, characterized in that formed by bending twice the leading end of the first projecting piece projecting in an L-shape outward from the outer peripheral edge of said plate Direction clutch.

2. The one-way clutch according to claim 1 , wherein the elastic body collapsing prevention portion is provided with a reinforcing portion that becomes a deformation resistance when a load is applied to the bent first protruding piece .

The one-way clutch according to claim 5 , wherein the reinforcing portion has a rib structure .

Of the plurality of projecting pieces formed on the peripheral edge of the flat plate portion, a first projecting piece that forms the storage portion, a third projecting piece that forms a holding portion that holds the elastic body, The one-way clutch according to claim 1 , wherein the holding portion is formed together with the three projecting pieces and the fourth projecting piece forming the receiving portion is in contact with the one-way clutch.