JP5353869B2 - Pulley device with built-in one-way clutch for automotive auxiliary equipment - Google Patents

Pulley device with built-in one-way clutch for automotive auxiliary equipment Download PDF

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JP5353869B2
JP5353869B2 JP2010276022A JP2010276022A JP5353869B2 JP 5353869 B2 JP5353869 B2 JP 5353869B2 JP 2010276022 A JP2010276022 A JP 2010276022A JP 2010276022 A JP2010276022 A JP 2010276022A JP 5353869 B2 JP5353869 B2 JP 5353869B2
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spring
pulley
way clutch
sleeve
pair
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JP2011080603A (en
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治 篠田
康子 鈴木
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NSK Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a pulley device with a built-in one-way clutch obtaining further satisfactory clutch performance by reducing friction between a spring and a retainer. <P>SOLUTION: In the pulley device, a column part 21 of the retainer 18a includes an escape part 21a cut out near a contact part 103 of the spring 100' with a roller 17, and the escape part 21a is formed being cut out to avoid a movable region of the contact part 103 of the spring 100'. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

本発明は、一方向クラッチ内蔵型プーリ装置に関し、より詳細には、エンジンのクランク軸の動力によって駆動されるオルタネータ等の補機類の入力軸に固定して用いられる自動車の補機用一方向クラッチ内蔵型プーリ装置に関する。 The present invention relates to a pulley device with a built-in one-way clutch, and more particularly, to a one-way vehicle accessory used by being fixed to an input shaft of an auxiliary device such as an alternator driven by the power of an engine crankshaft. The present invention relates to a pulley device with a built-in clutch.

従来、自動車の駆動用エンジンを駆動源として種々の補機が駆動されており、例えば自動車に必要な発電を行なうオルタネータを駆動する際には、一方向クラッチが組み込まれたクラッチ内蔵型プーリ装置を使用することが知られている(例えば、特許文献1参照。)。   2. Description of the Related Art Conventionally, various auxiliary machines are driven using a drive engine of an automobile as a drive source. For example, when driving an alternator that generates electric power necessary for an automobile, a clutch built-in type pulley apparatus incorporating a one-way clutch is used. It is known to use (see, for example, Patent Document 1).

一方向クラッチは、内輪と外輪との間に楔空間を構成するように、内輪或いは外輪にカム面を有し、楔空間に配置されたローラの係脱によって、ロック状態とオーバーラン状態とを繰り返す。楔空間に配置される各ローラは、保持器に形成された複数のポケット内に収容されており、保持器に係止されたばねによって、楔作用を発揮する方向、即ちロック方向に弾性的に押圧される。   The one-way clutch has a cam surface on the inner ring or the outer ring so as to form a wedge space between the inner ring and the outer ring, and the locked state and the overrun state are achieved by engaging and disengaging the rollers disposed in the wedge space. repeat. Each roller arranged in the wedge space is accommodated in a plurality of pockets formed in the cage, and is elastically pressed in the direction of exerting the wedge action, that is, the lock direction, by a spring locked to the cage. Is done.

図17(a)に示すばね100は、基部101と、基部101の両側で基部101に対して折れ曲がった一対の押圧部102と、を有し、押圧部102の先端部でローラと当接する。また、図17(b)に示すばね100´は、基部101と、一対の押圧部102と、押圧部102の先端部で押圧部102に対して折れ曲がってローラと当接する一対の当接部103とを有する。   A spring 100 shown in FIG. 17A has a base 101 and a pair of pressing portions 102 bent with respect to the base 101 on both sides of the base 101, and comes into contact with a roller at the tip of the pressing portion 102. 17B includes a base portion 101, a pair of pressing portions 102, and a pair of contact portions 103 that are bent with respect to the pressing portion 102 at the distal end portion of the pressing portion 102 and contact the roller. And have.

例えば、ばね100´は、図18に示すように、保持器110の柱部111から径方向外方に延びる中央側ばね保持部112と一対の端部側ばね保持部113とで係止されて、一対の円環部114(図では、一方の円環部のみを示す。)間に配置される。   For example, as shown in FIG. 18, the spring 100 ′ is locked by a center-side spring holding portion 112 and a pair of end-side spring holding portions 113 that extend radially outward from the column portion 111 of the cage 110. , Between a pair of annular portions 114 (only one annular portion is shown in the figure).

特開平8−61433号公報JP-A-8-61433

ところで、図18に示すように、一方向クラッチのオーバーラン状態においては、ばね100´はローラ120によって押圧されて屈曲するが、その際、屈曲するばね100´の押圧部102や当接部103が保持器110の柱部111と干渉する可能性がある。このため、ばね100´の保持器110との干渉を抑制し、ばね100´と保持器110間の摩擦を低減してより良好なクラッチ性能を得ることが求められている。   By the way, as shown in FIG. 18, in the overrun state of the one-way clutch, the spring 100 ′ is bent by being pressed by the roller 120. At this time, the pressing portion 102 and the contact portion 103 of the spring 100 ′ that bends are bent. May interfere with the column part 111 of the cage 110. For this reason, it is required to suppress the interference of the spring 100 ′ with the cage 110 and reduce the friction between the spring 100 ′ and the cage 110 to obtain better clutch performance.

本発明は、前述した事情に鑑みてなされたものであり、その目的は、ばねと保持器間の摩擦を低減してより良好なクラッチ性能を得ることができる自動車の補機用一方向クラッチ内蔵型プーリ装置を提供することにある。 The present invention has been made in view of the above-described circumstances, and an object of the present invention is to incorporate a one-way clutch for an auxiliary machine of an automobile that can reduce friction between a spring and a cage to obtain better clutch performance. It is in providing a type | mold pulley apparatus.

本発明の上記目的は、下記の構成により達成される。
(1) 回転軸が内嵌されるスリーブと、スリーブの径方向外側にスリーブと同心に配置されたプーリと、スリーブの外周面とプーリの内周面との間に設けられ、プーリとスリーブの一方が他方に対して所定の方向に相対回転する傾向となる場合のみ、プーリとスリーブとの間で回転力を伝達する一方向クラッチと、スリーブの外周面とプーリの内周面との間で一方向クラッチに対して軸方向に離間した位置に設けられ、プーリに加わるラジアル荷重を支承しつつプーリとスリーブとの相対回転を可能とするサポート軸受と、を備え、
一方向クラッチは、スリーブとプーリのうちの一方の部材と共に回転する保持器と、保持器に保持された複数の係合子と、複数の係合子を係合する方向に押圧するばねと、を備え、
保持器は、一対の円環部と、一対の円環部を連結する複数の柱部と、該保持器とは別体の前記ばねを挟持する、一対の円環部の内側面で各柱部と整合する部分に設けられた一対の端部側ばね保持部と各柱部の軸方向中央部に設けられた中央側ばね保持部とを備え、
ばねは、一対の端部側ばね保持部と中央側ばね保持部に挟持される基部と、基部の両側を屈曲部として基部に対して鋭角に折れ曲がった一対の押圧部を備える板ばねである自動車の補機用一方向クラッチ内蔵型プーリ装置であって、
保持器の柱部には、ばねの接触部の可動領域を避けるように径方向に貫通した切欠きが設けられていることを特徴とする自動車の補機用一方向クラッチ内蔵型プーリ装置。
The above object of the present invention can be achieved by the following constitution.
(1) A sleeve in which the rotation shaft is fitted, a pulley disposed concentrically with the sleeve on the radially outer side of the sleeve, and provided between the outer peripheral surface of the sleeve and the inner peripheral surface of the pulley. Only when one side tends to rotate relative to the other in a predetermined direction, between the one-way clutch that transmits the rotational force between the pulley and the sleeve, and the outer peripheral surface of the sleeve and the inner peripheral surface of the pulley. A support bearing provided at a position spaced axially with respect to the one-way clutch, and supporting a radial load applied to the pulley and enabling relative rotation between the pulley and the sleeve;
The one-way clutch includes a cage that rotates together with one member of a sleeve and a pulley, a plurality of engagement elements held by the retainer, and a spring that presses the plurality of engagement elements in a direction of engagement. ,
The cage includes a pair of annular portions, a plurality of column portions that connect the pair of annular portions, and an inner surface of the pair of annular portions that sandwich the spring separately from the cage. A pair of end-side spring holding portions provided in a portion aligned with the portion and a central-side spring holding portion provided in an axial center portion of each column portion,
The spring is a leaf spring having a base that is held between the center-side spring holding portion a pair of end-side spring holding portion, a pair of pressing portions which is bent at an acute angle relative to the base on either side of the base as a bent portion automobiles A pulley device with a built-in one-way clutch for an auxiliary machine ,
A pulley apparatus with a built-in one-way clutch for an auxiliary machine of an automobile, wherein a notch penetrating in a radial direction is provided in a pillar portion of the cage so as to avoid a movable region of a contact portion of a spring.

本発明の一方向クラッチ内蔵型プーリ装置によれば、ばねが板ばねによって形成され、保持器の柱部には、ばねの接触部の可動領域を避けるように切欠きが設けられているので、ばねが屈曲した際に、ばねの接触部が保持器と干渉するのを抑制し、ばねと保持器間の摩擦を低減してより良好なクラッチ性能を得ることができる。   According to the one-way clutch built-in pulley apparatus of the present invention, the spring is formed by a leaf spring, and the pillar portion of the cage is provided with a notch so as to avoid the movable region of the contact portion of the spring. When the spring is bent, the contact portion of the spring is prevented from interfering with the cage, and the friction between the spring and the cage can be reduced to obtain better clutch performance.

本発明の第1実施形態であるクラッチ内蔵型プーリ装置の縦断面図である。It is a longitudinal cross-sectional view of the pulley apparatus with a built-in clutch which is 1st Embodiment of this invention. 外輪を取り外した状態で、図1の一方向クラッチの保持器とばねを円周方向において部分的に示す上面図である。FIG. 2 is a top view partially showing a cage and a spring of the one-way clutch in FIG. 1 in a circumferential direction with an outer ring removed. 図1の一方向クラッチのばねを示し、(a)はその側面図で、(b)はその展開図である。The spring of the one way clutch of FIG. 1 is shown, (a) is the side view, (b) is the expanded view. 第1実施形態の一方向クラッチの変形例に係るばねの先端部を示す図である。It is a figure which shows the front-end | tip part of the spring which concerns on the modification of the one-way clutch of 1st Embodiment. 第1実施形態の一方向クラッチの他の変形例に係るばねの先端部を示す図である。It is a figure which shows the front-end | tip part of the spring which concerns on the other modification of the one-way clutch of 1st Embodiment. 外輪を取り外した状態で、第2実施形態の一方向クラッチの保持器とばねを円周方向において部分的に示す上面図である。FIG. 10 is a top view partially showing a cage and a spring of a one-way clutch according to a second embodiment in a circumferential direction with an outer ring removed. 図6の一方向クラッチのばねを示し、(a)はその側面図で、(b)はその展開図である。6 shows a spring of the one-way clutch in FIG. 6, (a) is a side view thereof, and (b) is a developed view thereof. 第2実施形態の一方向クラッチの変形例に係るばねの先端部を示す図である。It is a figure which shows the front-end | tip part of the spring which concerns on the modification of the one-way clutch of 2nd Embodiment. 第2実施形態の一方向クラッチの他の変形例に係るばねの先端部を示す図である。It is a figure which shows the front-end | tip part of the spring which concerns on the other modification of the one way clutch of 2nd Embodiment. 第3実施形態の一方向クラッチのばねを示し、(a)はその斜視図で、(b)はその側面図である。The spring of the one-way clutch of 3rd Embodiment is shown, (a) is the perspective view, (b) is the side view. 第3実施形態の一方向クラッチの保持器を示し、(a)はその通常時の断面図で、(b)は、その最大変形時の断面図である。The retainer of the one-way clutch of the third embodiment is shown, in which (a) is a cross-sectional view at the normal time, and (b) is a cross-sectional view at the time of maximum deformation. 第3実施形態の一方向クラッチの保持器最大変形時のばね及び保持器を示し、(a)はその断面図で、(b)は、(a)のXII部分拡大図である。The spring and cage | basket at the time of the largest deformation | transformation of the cage | basket of the one-way clutch of 3rd Embodiment are shown, (a) is the sectional drawing, (b) is the XII partial enlarged view of (a). 本発明の第4実施形態の一方向クラッチの保持器とばねを円周方向において部分的に示す斜視図である。It is a perspective view which shows partially the holder | retainer and spring of the one-way clutch of 4th Embodiment of this invention in the circumferential direction. 図13の保持器を円周方向において部分的に示す斜視図である。FIG. 14 is a perspective view partially showing the cage of FIG. 13 in the circumferential direction. 第4実施形態の一方向クラッチの変形例に係る保持器とばねを円周方向において部分的に示す斜視図である。It is a perspective view which shows partially the holder and spring which concern on the modification of the one way clutch of 4th Embodiment in the circumferential direction. 本発明の第5実施形態の一方向クラッチの保持器とばねを円周方向において部分的に示す斜視図である。It is a perspective view which shows partially the holder | retainer and spring of the one-way clutch of 5th Embodiment of this invention in the circumferential direction. 従来の一方向クラッチのばねを示す斜視図である。It is a perspective view which shows the spring of the conventional one-way clutch. 従来の一方向クラッチの保持器とばねを示す斜視図である。It is a perspective view which shows the holder | retainer and spring of the conventional one-way clutch.

以下、本発明の各実施形態に係る一方向クラッチ内蔵型プーリ装置について図面を参照して詳細に説明する。   Hereinafter, a pulley device with a built-in one-way clutch according to each embodiment of the present invention will be described in detail with reference to the drawings.

(第1実施形態)
まず、図1〜3を参照して、本発明の第1実施形態について詳細に説明する。
図1に示すように、クラッチ内蔵型プーリ装置10は、オルタネータ等の補機の回転軸(図示せず)が螺合して内嵌されるスリーブ11と、スリーブ11の径方向外側にスリーブ11と同心に配設され、外周面にベルト溝12aが形成されたプーリ12とを備えている。ベルト溝12aには、エンジンのクランク軸に固定された駆動プーリ(図示せず)に懸架された駆動ベルト(図示せず)が掛け渡されている。
(First embodiment)
First, with reference to FIGS. 1-3, 1st Embodiment of this invention is described in detail.
As shown in FIG. 1, the pulley apparatus 10 with a built-in clutch includes a sleeve 11 into which a rotating shaft (not shown) of an auxiliary machine such as an alternator is screwed, and a sleeve 11 radially outside the sleeve 11. And a pulley 12 having a belt groove 12a formed on the outer peripheral surface thereof. A drive belt (not shown) suspended from a drive pulley (not shown) fixed to the crankshaft of the engine is stretched over the belt groove 12a.

また、スリーブ11の軸方向中間部における外周面とプーリ12の軸方向中間部における内周面との間には、一方向クラッチ13が配置されており、一方向クラッチ13に対して軸方向に離間した位置となる、スリーブ11の軸方向両端部における外周面とプーリ12の軸方向両端部における内周面との間には、一対の転がり軸受14が配置されている。一方向クラッチ13は、プーリ12がスリーブ11に対して所定方向に相対回転する傾向となる場合のみ、プーリ12とスリーブ11との間で回転力を伝達する。転がり軸受14は、深溝玉軸受等が使用されており、プーリ12に加わるラジアル荷重を支承しつつ、スリーブ11とプーリ12とを相対回転を可能とする。   In addition, a one-way clutch 13 is disposed between the outer peripheral surface of the sleeve 11 in the axial intermediate portion and the inner peripheral surface of the pulley 12 in the axial intermediate portion. A pair of rolling bearings 14 is disposed between the outer peripheral surface at both axial ends of the sleeve 11 and the inner peripheral surface at both axial ends of the pulley 12, which are spaced apart. The one-way clutch 13 transmits a rotational force between the pulley 12 and the sleeve 11 only when the pulley 12 tends to rotate relative to the sleeve 11 in a predetermined direction. As the rolling bearing 14, a deep groove ball bearing or the like is used, and the sleeve 11 and the pulley 12 can be relatively rotated while supporting a radial load applied to the pulley 12.

一方向クラッチ13は、スリーブ11の外周面に圧入固定される内輪15と、プーリ12の内周面に圧入固定される外輪16と、内輪15の外周面と外輪16の内周面との間に配置される係合子である複数のローラ17とを備える。内輪15の外周面は、複数のランプ部15aが円周方向に所定の間隔で形成されたカム面をなしており、ローラ17は外輪16の円筒面16aと各ランプ部15aとから形成される楔空間に回動自在に保持されている。   The one-way clutch 13 includes an inner ring 15 that is press-fitted and fixed to the outer peripheral surface of the sleeve 11, an outer ring 16 that is press-fitted and fixed to the inner peripheral surface of the pulley 12, and between the outer peripheral surface of the inner ring 15 and the inner peripheral surface of the outer ring 16. And a plurality of rollers 17 which are engaging elements disposed in the. The outer peripheral surface of the inner ring 15 forms a cam surface in which a plurality of ramp portions 15a are formed at predetermined intervals in the circumferential direction, and the roller 17 is formed from the cylindrical surface 16a of the outer ring 16 and each ramp portion 15a. It is rotatably held in the wedge space.

また、一方向クラッチ13は、各ローラ17を個別に収容する複数のポケットを有する保持器18と、各ローラ17を楔空間の係合する方向に弾性的に押圧するばね19とを有している。   The one-way clutch 13 includes a cage 18 having a plurality of pockets for individually accommodating the rollers 17 and a spring 19 that elastically presses the rollers 17 in a direction in which the wedge space is engaged. Yes.

図2に示すように、保持器18は、一対の円環部20と、一対の円環部20を連結する複数の柱部21とを備えている。   As shown in FIG. 2, the retainer 18 includes a pair of annular portions 20 and a plurality of column portions 21 that connect the pair of annular portions 20.

一対の円環部20の内周面には、ランプ部15aの軸方向両端部と係合する図示しない凸部が形成されており、保持器18は内輪15及びスリーブ11と共に一体に回転する。また、一対の円環部20の内側面で円周方向において各柱部21と整合する部分には、一対の端部側ばね保持部22が各柱部21の外周面側から径方向外方に突出する状態で形成されている。これに対して、各柱部21の軸方向中央部には、中央側ばね保持部23が各柱部21の外周面側から径方向外方に突出する状態で形成されている。ばね19は端部側ばね保持部22の円周方向一側面と、中央側ばね保持部23の円周方向他側面との間に挟持される。   Protrusions (not shown) that engage with both axial ends of the lamp portion 15 a are formed on the inner peripheral surfaces of the pair of annular portions 20, and the cage 18 rotates together with the inner ring 15 and the sleeve 11. In addition, a pair of end-side spring holding portions 22 are radially outward from the outer peripheral surface side of each column portion 21 at a portion that is aligned with each column portion 21 in the circumferential direction on the inner side surface of the pair of annular portions 20. It is formed in a state of projecting. On the other hand, the center side spring holding part 23 is formed in the axial direction center part of each pillar part 21 in the state which protrudes radially outward from the outer peripheral surface side of each pillar part 21. As shown in FIG. The spring 19 is sandwiched between one circumferential side surface of the end side spring holding portion 22 and the other circumferential side surface of the center side spring holding portion 23.

図2及び図3に示すように、ばね19は、板ばねからなり、長手方向中間部である基部25の両側を、折曲部(最大応力が発生する部位)26として所定の位置で折り曲げることによって押圧部27を構成しており、押圧部27の先端部をローラ17が接触する接触部28としている。これによりばね19は、接触部28で各ローラ17と接触して、各ローラ17をロック方向、即ち、ランプ部15aの溝の浅い側に向けて押圧している。   As shown in FIGS. 2 and 3, the spring 19 is a leaf spring, and bends both sides of the base portion 25, which is an intermediate portion in the longitudinal direction, at predetermined positions as bent portions (portions where maximum stress is generated) 26. The press part 27 is comprised by this, and the front-end | tip part of the press part 27 is used as the contact part 28 with which the roller 17 contacts. As a result, the spring 19 comes into contact with each roller 17 at the contact portion 28 and presses each roller 17 toward the locking direction, that is, toward the shallow side of the groove of the ramp portion 15a.

また、ばね19の接触部28は、押圧部27にかけて保持器側が矩形状に切り欠かれて、その径方向幅W1が折曲部26の径方向幅W2に比べて小さくなるように形成されている。これにより、ばね19が保持器18に配置された状態において、ばね19が屈曲した場合でも接触部28は柱部21の表面から離れて位置する。   The contact portion 28 of the spring 19 is formed so that the cage side is cut out in a rectangular shape over the pressing portion 27 and the radial width W1 thereof is smaller than the radial width W2 of the bent portion 26. Yes. Thereby, in the state where the spring 19 is disposed in the cage 18, the contact portion 28 is positioned away from the surface of the column portion 21 even when the spring 19 is bent.

このように構成された一方向クラッチ内蔵型プーリ装置10は、プーリ12の回転角速度が回転軸の回転角速度より速い場合、即ち、外輪16が内輪15に対して所定の方向に相対回転する傾向となる場合には、ローラ17が楔作用によって外輪16の円筒面と内輪15のランプ部15aとの間の楔空間に噛み込まれて、外輪16と内輪15との間で各ローラ17を介して回転力が伝達自在となる。これにより、プーリ12とスリーブ11とが相対回転不能(ロック状態)となり、エンジンの回転力が回転軸に伝達される。一方、プーリ12の回転角速度が回転軸の回転角速度より遅い場合には、ローラ17の噛み込みが解除されて、プーリ12とスリーブ11との相対回転が自在(オーバーラン状態)となる。   The pulley apparatus 10 with a built-in one-way clutch configured in this way has a tendency that the outer ring 16 rotates relative to the inner ring 15 in a predetermined direction when the rotational angular speed of the pulley 12 is faster than the rotational angular speed of the rotating shaft. In this case, the roller 17 is engaged with the wedge space between the cylindrical surface of the outer ring 16 and the ramp portion 15a of the inner ring 15 by the wedge action, and the rollers 17 are interposed between the outer ring 16 and the inner ring 15 via the respective rollers 17. Rotational force can be transmitted freely. As a result, the pulley 12 and the sleeve 11 cannot be rotated relative to each other (in a locked state), and the rotational force of the engine is transmitted to the rotating shaft. On the other hand, when the rotational angular velocity of the pulley 12 is slower than the rotational angular velocity of the rotating shaft, the engagement of the roller 17 is released, and the pulley 12 and the sleeve 11 can be freely rotated (overrun state).

ここで、オーバーラン状態等、ローラ17が内輪15のランプ部15aの溝の深い側に位置する場合には、ばね19はローラ17によって押圧されて屈曲しているが、ばね19のローラ17との接触部28は、押圧部27にかけて保持器側が矩形状に切り欠かれているので、保持器18の柱部21の表面と干渉することがなく、ばね19と保持器18間の摩擦を低減することができる。また、ばね19が屈曲した状態において、折曲部26は最大応力が発生する最大応力部位となるが、この折曲部26の径方向幅を大きく保っているので、ばね19の強度を維持することができる。   Here, when the roller 17 is positioned on the deep side of the groove of the ramp portion 15a of the inner ring 15 such as in an overrun state, the spring 19 is pressed and bent by the roller 17, but the roller 17 of the spring 19 Since the contact portion 28 is notched in a rectangular shape on the side of the pressing portion 27, the contact portion 28 does not interfere with the surface of the column portion 21 of the retainer 18, and reduces the friction between the spring 19 and the retainer 18. can do. Further, in the state where the spring 19 is bent, the bent portion 26 becomes a maximum stress portion where the maximum stress is generated. However, since the radial width of the bent portion 26 is kept large, the strength of the spring 19 is maintained. be able to.

さらに、遠心力によって保持器18が外輪側に撓んだ場合にも、保持器18がばね19の接触部28と干渉することが防止されるので、高速回転による運転環境においてもクラッチ性能が損なわれることがない。   Furthermore, even when the cage 18 bends to the outer ring side due to centrifugal force, the cage 18 is prevented from interfering with the contact portion 28 of the spring 19, so that the clutch performance is impaired even in an operating environment due to high-speed rotation. It will not be.

従って、本実施形態の一方向クラッチ内蔵型プーリ装置10によれば、ばね19が板ばねによって形成され、ばね19は、ローラ17との接触部近傍において切り欠いて、ローラ17との接触部28の径方向幅W1が折曲部26の径方向幅W2より小さくなるように形成されるので、ばね19が屈曲した際や保持器18が外輪側に撓んだ際にも、ばね19の接触部28と保持器18とが干渉するのが抑制され、ばね19と保持器18間の摩擦を低減してより良好なクラッチ性能を得ることができる。   Therefore, according to the pulley device 10 with a built-in one-way clutch of the present embodiment, the spring 19 is formed by a leaf spring, and the spring 19 is notched in the vicinity of the contact portion with the roller 17, and the contact portion 28 with the roller 17. Since the radial width W1 is smaller than the radial width W2 of the bent portion 26, the contact of the spring 19 also occurs when the spring 19 is bent or when the cage 18 is bent toward the outer ring. Interference between the portion 28 and the cage 18 is suppressed, and friction between the spring 19 and the cage 18 can be reduced to obtain better clutch performance.

なお、ばね19の押圧部27及び接触部28の形状は、本実施形態のものに限定されるものでなく、図4(a)〜(f)及び図5(a)〜(g)に示すように、接触部28の径方向幅W1が折曲部26の径方向幅W2に比べて小さくなるようなものであればいずれの形状であってもよい。   In addition, the shape of the press part 27 of the spring 19 and the contact part 28 is not limited to the thing of this embodiment, It shows to Fig.4 (a)-(f) and Fig.5 (a)-(g). As described above, any shape may be employed as long as the radial width W1 of the contact portion 28 is smaller than the radial width W2 of the bent portion 26.

具体的に、ばね19の押圧部27及び接触部28は、図4(a)に示すように保持器側の切りかかれた隅部30を湾曲した形状としてもよく、図4(b)〜(d)に示すように、保持器側径方向端面から軸方向端面に向けて直線状、或いは凸又は凹で曲線状に切り欠いて、軸方向端面に向かって径方向幅を徐々に小さくするようにしてもよい。また、押圧部27及び接触部28は、図4(e)及び(f)のように、保持器側を多段で切り欠いて、折曲部26側から軸方向端面に向かって径方向幅を徐々に小さくするようにしてもよい。さらに、図5(a)〜(g)に示すように、ばね19の押圧部27及び接触部28は、保持器側を上述した図3及び図4(a)〜(f)の特徴を持って形成すると共に外輪側も同様に形成し、即ち、外輪側と保持器側とを径方向において対称形状としてもよい。これにより、ばね19の径方向において方向性がなくなり、組み付け性を向上することができる。   Specifically, the pressing portion 27 and the contact portion 28 of the spring 19 may have a shape in which a corner portion 30 cut on the cage side is curved as shown in FIG. As shown in d), the radial width is gradually reduced toward the axial end surface by cutting out linearly from the cage side radial end surface toward the axial end surface, or by curving in a convex or concave shape. It may be. Further, as shown in FIGS. 4E and 4F, the pressing portion 27 and the contact portion 28 are notched in multiple stages on the cage side, and have a radial width from the bent portion 26 side toward the axial end surface. You may make it reduce gradually. Further, as shown in FIGS. 5 (a) to 5 (g), the pressing portion 27 and the contact portion 28 of the spring 19 have the features of FIGS. 3 and 4 (a) to (f) described above on the cage side. The outer ring side may be formed in the same manner, that is, the outer ring side and the cage side may be symmetrical in the radial direction. Thereby, the directionality in the radial direction of the spring 19 is lost, and the assembling property can be improved.

(第2実施形態)
次に、図6及び図7を参照して、本発明の第2実施形態について詳細に説明する。なお、本実施形態は、一方向クラッチのばねの形状が第1実施形態と異なるのみであり、その他の部分については第1実施形態のものと同等であり、説明を省略或いは簡略化する。
(Second Embodiment)
Next, a second embodiment of the present invention will be described in detail with reference to FIGS. The present embodiment is different from the first embodiment only in the shape of the spring of the one-way clutch, and other parts are the same as those in the first embodiment, and the description is omitted or simplified.

図6及び図7に示されるように、本実施形態のばね40は、長手方向中間部である基部41の両側を、折曲部42として所定の位置で折り曲げることによって押圧部43を構成すると共に、押圧部43の先端部を他の折曲部44として所定の位置で更に折り曲げて接触部45を構成している。   As shown in FIGS. 6 and 7, the spring 40 of the present embodiment constitutes a pressing portion 43 by bending both sides of a base portion 41 that is a middle portion in the longitudinal direction at a predetermined position as bending portions 42. The contact portion 45 is configured by further bending the distal end portion of the pressing portion 43 as another bent portion 44 at a predetermined position.

また、図7に示すように、ばね40の接触部45と接触部側の押圧部43は、保持器側において切り欠かれており、接触部45の径方向幅W1は、折曲部42の径方向幅W2に比べて小さくなるように形成されている。即ち、接触部45の径方向幅W1は、押圧部43の径方向最大幅W2より小さく設定されている。これにより、第1実施形態と同様、ばね40が保持器18に配置された状態において、ばね40が屈曲した場合でも接触部45は柱部21の表面から離れて位置する。
その他の構成及び作用については、第1実施形態のものと同様である。
Further, as shown in FIG. 7, the contact portion 45 of the spring 40 and the pressing portion 43 on the contact portion side are notched on the cage side, and the radial width W1 of the contact portion 45 is equal to that of the bent portion 42. It is formed so as to be smaller than the radial width W2. That is, the radial width W1 of the contact portion 45 is set to be smaller than the maximum radial width W2 of the pressing portion 43. Thus, as in the first embodiment, in the state where the spring 40 is disposed in the cage 18, the contact portion 45 is located away from the surface of the column portion 21 even when the spring 40 is bent.
Other configurations and operations are the same as those in the first embodiment.

なお、本実施形態においても、ばね40の接触部45と接触部側の押圧部43の形状は、本実施形態のものに限定されるものでなく、図8(a)〜(g)及び図9(a)〜(h)に示すように、接触部45の径方向幅W1が折曲部42の径方向幅W2に比べて小さくなるようなものであればいずれの形状であってもよい。   Also in the present embodiment, the shapes of the contact portion 45 of the spring 40 and the pressing portion 43 on the contact portion side are not limited to those of the present embodiment, and FIGS. 8A to 8G and FIGS. 9 (a) to 9 (h), any shape may be used as long as the radial width W1 of the contact portion 45 is smaller than the radial width W2 of the bent portion 42. .

即ち、ばね40の接触部45及び押圧部43は、図8(a)〜(c)に示すように、保持器側径方向端面から軸方向端面に向けて直線状、或いは凸又は凹で曲線状に連続に切り欠いて、軸方向端面に向かって径方向幅を徐々に小さくするようにしてもよい。或いは、図8(d)〜(f)に示すように、押圧部43の他の折曲部44まで径方向幅を徐々に小さくするように形成し、接触部45を折曲部42の径方向幅W2より小さい一様幅としてもよい。或いは、図8(g)に示すように、ばね40の接触部45及び押圧部43は、保持器側を多段で切り欠いて、折曲部26側から軸方向端面に向かって径方向幅を徐々に小さくするようにしてもよい。さらに、図9(a)〜(h)に示すように、ばね40の接触部45及び押圧部43は、外輪側と保持器側とを径方向において対称形状としてもよい。   That is, as shown in FIGS. 8A to 8C, the contact portion 45 and the pressing portion 43 of the spring 40 are linear, convex, or concave and curved from the cage side radial end surface to the axial end surface. The radial width may be gradually reduced toward the axial end face. Alternatively, as shown in FIGS. 8D to 8F, the radial width is gradually reduced to the other bent portion 44 of the pressing portion 43, and the contact portion 45 has a diameter of the bent portion 42. It may be a uniform width smaller than the direction width W2. Alternatively, as shown in FIG. 8 (g), the contact portion 45 and the pressing portion 43 of the spring 40 are notched in multiple stages on the cage side, and have a radial width from the bent portion 26 side toward the axial end surface. You may make it reduce gradually. Furthermore, as shown to Fig.9 (a)-(h), the contact part 45 and the press part 43 of the spring 40 are good also considering the outer ring | wheel side and the cage | basket side as a symmetrical shape in radial direction.

(第3実施形態)
次に、図10〜図12を参照して、本発明の第3実施形態について詳細に説明する。なお、本実施形態は、第2実施形態の図9(b)に示されたばねの寸法形状を特徴とするものであり、同一部分については同一符号を付して、説明を省略或は簡略化する。
(Third embodiment)
Next, a third embodiment of the present invention will be described in detail with reference to FIGS. In addition, this embodiment is characterized by the size and shape of the spring shown in FIG. 9B of the second embodiment. The same parts are denoted by the same reference numerals, and the description thereof is omitted or simplified. To do.

即ち、図10に示すように、本実施形態のばね40は、その接触部45及び押圧部43は、保持器側径方向端面から軸方向端面に向けて、即ち、テーパ開始点46からテーパ終点47まで直線状に切り欠いて、軸方向端面に向かって径方向幅を徐々に小さくしたテーパ形状に形成され、且つ、外輪側と保持器側とを径方向において対称形状としている。ここで、図10(b)中、βはテーパ角度、B´はテーパ終点47におけるテーパ幅、Cはテーパ長さを表す。   That is, as shown in FIG. 10, in the spring 40 of this embodiment, the contact portion 45 and the pressing portion 43 are arranged from the radial end surface of the cage side toward the axial end surface, that is, from the taper start point 46 to the taper end point. It is formed in a taper shape that is linearly cut up to 47, gradually reducing the radial width toward the axial end face, and the outer ring side and the cage side are symmetrical in the radial direction. Here, in FIG. 10B, β represents the taper angle, B ′ represents the taper width at the taper end point 47, and C represents the taper length.

一方、保持器18の柱部21は、高速回転による遠心力が作用すると、一対の円環部20に連結された軸方向両端部から軸方向中央部に亘って、図11(b)に示すように略直線的に変形する。なお、中央側ばね保持部23が形成される領域は、肉厚により実質的に変形しない。ここで、図11(a)中、Lは、柱部長さを表し、Aは、中央側ばね保持部23の軸方向寸法を表す。また、図11(b)は、保持器18が最も変形した状態を示しており、図中Bは、保持器の最大変形量を表し、αは、その時点の変形角度を表している。   On the other hand, the column portion 21 of the cage 18 is shown in FIG. 11B from the axial end portions connected to the pair of annular portions 20 to the axial center portion when centrifugal force due to high-speed rotation acts. Is deformed substantially linearly. In addition, the area | region in which the center side spring holding | maintenance part 23 is formed does not deform | transform substantially by thickness. Here, in FIG. 11A, L represents the length of the column part, and A represents the axial dimension of the center side spring holding part 23. FIG. 11B shows a state in which the cage 18 is most deformed. In FIG. 11B, B represents the maximum deformation amount of the cage, and α represents the deformation angle at that time.

図12は、保持器最大変形時のばね及び保持器を示している。ここで、ばね40のテーパ終点47におけるテーパ幅B´は、保持器18の最大変形量Bを考慮して決定されるが、ばね40のテーパ角度βが保持器18の変形角度αより大きい場合、保持器18が徐々に変形していくと、ばね40のテーパ終点47と接触する前に、ばね40のテーパ開始点46の位置で干渉してしまう。このため、ばね40のテーパ形状を最大に活用することができない。   FIG. 12 shows the spring and the cage at the time of maximum deformation of the cage. Here, the taper width B ′ at the taper end point 47 of the spring 40 is determined in consideration of the maximum deformation amount B of the cage 18, but when the taper angle β of the spring 40 is larger than the deformation angle α of the cage 18. When the cage 18 is gradually deformed, it interferes at the position of the taper start point 46 of the spring 40 before contacting the taper end point 47 of the spring 40. For this reason, the taper shape of the spring 40 cannot be utilized to the maximum.

このため、本実施形態では、保持器18が最大変形量まで変形した場合に、ばね40と保持器40との干渉を防止するように、ばね40のテーパ形状のテーパ角度βを保持器18の変形角度αより小さく設定している。即ち、
α>β ・・・(1)
For this reason, in this embodiment, when the retainer 18 is deformed to the maximum deformation amount, the taper-shaped taper angle β of the spring 40 is set so as to prevent the interference between the spring 40 and the retainer 40. It is set smaller than the deformation angle α. That is,
α> β (1)

また、変形角度αと、テーパ角度βは、それぞれ以下のように与えられる。
α=tan−1(B/((L−A)/2)) ・・・(2)
β=tan−1(B´/C) ・・・(3)
Further, the deformation angle α and the taper angle β are given as follows.
α = tan-1 (B / ((LA) / 2)) (2)
β = tan−1 (B ′ / C) (3)

従って、式(1)〜(3)、及び、最大変形量Bを考慮して決定されるテーパ幅B´から、テーパ長さCが決定され、ばね40のテーパ形状を設定することができる。また、便宜上、テーパ幅B´を最大変形量Bとした場合には、式(1)〜(3)により、
tan−1(B/((L−A)/2)) > tan−1(B/C) ・・・(4)
となり、2C>L−Aに設定される。なお、ばね40を端部側ばね保持部22のみで支持する場合には、A=0に設定される。
Therefore, the taper length C is determined from the formulas (1) to (3) and the taper width B ′ determined in consideration of the maximum deformation amount B, and the taper shape of the spring 40 can be set. For convenience, when the taper width B ′ is the maximum deformation amount B,
tan-1 (B / ((LA) / 2))> tan-1 (B / C) (4)
And 2C> LA is set. When the spring 40 is supported only by the end side spring holding part 22, A = 0 is set.

このようにばね40のテーパ寸法を設定することで、保持器18の変形によるばね40と保持器18の干渉が防止され、クラッチ機能の低下を防止することができる。また、本実施形態のばね40は、径方向に対称形状としているので、ばね40の径方向において方向性がなくなり、組付け性を向上することができる。   By setting the taper dimension of the spring 40 in this way, interference between the spring 40 and the cage 18 due to the deformation of the cage 18 can be prevented, and a reduction in the clutch function can be prevented. Moreover, since the spring 40 of this embodiment is made into a symmetrical shape in the radial direction, there is no directivity in the radial direction of the spring 40, and assemblability can be improved.

なお、本実施形態のばね40のテーパ寸法の設定は、図8(a)に示すばね40にも適用可能であり、第1実施形態の図4(b)や図5(c)に示す折曲部を有しない構成にも適用可能である。   The setting of the taper dimension of the spring 40 of this embodiment is also applicable to the spring 40 shown in FIG. 8A, and the folding shown in FIG. 4B and FIG. 5C of the first embodiment. It is applicable also to the structure which does not have a curved part.

また、本実施形態では、便宜上、ばね40の軸方向端面と保持器18の中央側ばね保持部23の軸方向端面の位置を一致させて計算しているが、これらの位置が一致しない場合にも適用可能であり、ばね40の軸方向端面の位置における保持器18の変形量を基に計算すればよい。   Further, in the present embodiment, for convenience, the calculation is performed by matching the positions of the axial end face of the spring 40 and the axial end face of the center side spring holding portion 23 of the cage 18, but when these positions do not match. Is applicable, and may be calculated based on the deformation amount of the cage 18 at the position of the axial end face of the spring 40.

(第4実施形態)
次に、図13及び図14を参照して、本発明の第4実施形態について詳細に説明する。
なお、本実施形態は、一方向クラッチの保持器の形状を特徴とするものであり、ばねは、図17(b)に示した従来のものが適用されている。その他の部分については第1実施形態のものと同等であり、説明を省略或いは簡略化する。
(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described in detail with reference to FIGS.
In addition, this embodiment is characterized by the shape of the cage of the one-way clutch, and the conventional spring shown in FIG. 17B is applied. Other parts are the same as those of the first embodiment, and the description thereof is omitted or simplified.

図13及び図14に示されるように、本実施形態の保持器18aは、第1実施形態と同様、一対の円環部20と、複数の柱部21とを備え、一対の円環部20の内周面には凸部31が形成され、各柱部21の軸方向端部と軸方向中央部には、一対の端部側ばね保持部22と中央側ばね保持部23がそれぞれ形成されている。   As shown in FIGS. 13 and 14, the retainer 18 a of this embodiment includes a pair of annular portions 20 and a plurality of column portions 21, as in the first embodiment, and a pair of annular portions 20. Convex portions 31 are formed on the inner peripheral surface of each of the two, and a pair of end-side spring holding portions 22 and a center-side spring holding portion 23 are respectively formed on the axial end portions and the axial center portion of each column portion 21. ing.

保持器18aの柱部21は、ばね100´のローラ17との接触部103近傍において切り欠かれた逃げ部21aを有している。逃げ部21aは、ばね100´の接触部103の可動領域を避けるように切り欠いて形成されており、本実施形態では、中央側ばね保持部23の円周方向一側面の位置まで円周方向に切り欠かれている。なお、柱部21は、ばね100´のローラ17との接触部103近傍において、ばね100´の接触部103と干渉しないように柱部21の外面側を部分的に切り欠いてもよく、逃げ部21aのように全体的に切り欠いてもよい。   The column portion 21 of the cage 18a has a relief portion 21a cut out in the vicinity of the contact portion 103 with the roller 17 of the spring 100 ′. The escape portion 21a is formed by cutting out so as to avoid the movable region of the contact portion 103 of the spring 100 '. In this embodiment, the escape portion 21a is circumferentially extended to the position of one side surface in the circumferential direction of the central spring holding portion 23. Notched into. The column portion 21 may be partially cut off on the outer surface side of the column portion 21 so as not to interfere with the contact portion 103 of the spring 100 ′ in the vicinity of the contact portion 103 of the spring 100 ′ with the roller 17. You may cut out entirely like the part 21a.

このように保持器18aが構成される本実施形態においても、オーバーラン状態等、ローラ17が内輪15のランプ部15aの溝の深い側に位置する場合には、ばね100´はローラ17によって押圧されて屈曲しているが、保持器18aの柱部21は逃げ部21aを有しているので、ばね100´の接触部103と保持器18aの柱部21とが干渉することがなく、ばね19と保持器18間の摩擦を低減することができる。また、遠心力によって保持器18aが外輪側に撓んだ場合にも、保持器18aがばね100´の接触部103と干渉することが防止されるので、高速回転による運転環境においてもクラッチ性能が損なわれることがない。   Even in this embodiment in which the cage 18a is configured in this way, the spring 100 'is pressed by the roller 17 when the roller 17 is positioned on the deep side of the groove of the ramp portion 15a of the inner ring 15 in an overrun state or the like. However, since the column portion 21 of the cage 18a has the relief portion 21a, the contact portion 103 of the spring 100 'and the column portion 21 of the cage 18a do not interfere with each other, and the spring The friction between 19 and the cage 18 can be reduced. Further, even when the cage 18a is bent to the outer ring side due to the centrifugal force, the cage 18a is prevented from interfering with the contact portion 103 of the spring 100 ', so that the clutch performance can be achieved even in an operating environment due to high-speed rotation. It will not be damaged.

従って、本実施形態の一方向クラッチ内蔵型プーリ装置10によれば、保持器18aの柱部21は、ばね100´のローラ17との接触部103近傍において切り欠かれた逃げ部21aを有しているので、ばね100´が屈曲した際や保持器18aが外輪側に撓んだ際にも、ばね100´の接触部103と保持器18aとが干渉するのが抑制され、ばね100´と保持器18a間の摩擦を低減してより良好なクラッチ性能を得ることができる。   Therefore, according to the pulley device 10 with a built-in one-way clutch of the present embodiment, the column portion 21 of the retainer 18a has the relief portion 21a cut out in the vicinity of the contact portion 103 with the roller 17 of the spring 100 ′. Therefore, even when the spring 100 ′ is bent or when the cage 18 a is bent toward the outer ring, the contact portion 103 of the spring 100 ′ and the cage 18 a are prevented from interfering with each other. The friction between the cages 18a can be reduced to obtain better clutch performance.

ここで、本実施形態の保持器18aは、第1〜第3実施形態のばねと組み合わせて使用してもよく、例えば、図15の変形例に示されるように、第2実施形態のばね40とともに使用されてもよい。   Here, the cage 18a of the present embodiment may be used in combination with the springs of the first to third embodiments. For example, as shown in the modification of FIG. 15, the spring 40 of the second embodiment. May be used together.

(第5実施形態)
次に、図16を参照して、本発明の第5実施形態について詳細に説明する。なお、本実施形態も、一方向クラッチの保持器の形状を特徴とするものであり、ばねは、図17(b)に示した従来のものが適用されている。その他の部分については第1実施形態のものと同等であり、説明を省略或いは簡略化する。
(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described in detail with reference to FIG. This embodiment is also characterized by the shape of a one-way clutch cage, and the conventional spring shown in FIG. 17B is applied. Other parts are the same as those of the first embodiment, and the description thereof is omitted or simplified.

図16に示されるように、本実施形態の保持器18bも、第1実施形態と同様、一対の円環部20と、複数の柱部21とを備え、一対の円環部20の内周面には図示しない凸部が形成され、各柱部21の軸方向両端部と軸方向中央部には、一対の端部側ばね保持部22´と中央側ばね保持部23がそれぞれ形成されている。   As shown in FIG. 16, the retainer 18b of the present embodiment also includes a pair of annular portions 20 and a plurality of column portions 21 as in the first embodiment, and the inner circumference of the pair of annular portions 20. A convex portion (not shown) is formed on the surface, and a pair of end-side spring holding portions 22 ′ and a center-side spring holding portion 23 are respectively formed at both axial end portions and the axial center portion of each column portion 21. Yes.

また、本実施形態の保持器18bは、一対の円環部20の内側面で円周方向において各柱部21と整合する部分に、柱部21と略等しい円周方向幅で円環部20の外周面と略等しい高さを有する一対の剛性増加部50を有している。このため、一対の端部側ばね保持部22´は、中央側ばね保持部23との間にばね100´を保持するようにして、剛性増加部50の軸方向内側に連続して形成されている。これにより、ローラ17の軸方向長さL1は、ばね100´の軸方向長さL2、即ち、保持器18bの保持部軸方向長さより長く設定される。   In addition, the cage 18b of the present embodiment has an annular portion 20 with a circumferential width substantially equal to the pillar portion 21 at a portion that is aligned with each pillar portion 21 in the circumferential direction on the inner surface of the pair of annular portions 20. It has a pair of rigidity increase parts 50 which have the height substantially equal to the outer peripheral surface. For this reason, the pair of end portion side spring holding portions 22 ′ are continuously formed on the inner side in the axial direction of the rigidity increasing portion 50 so as to hold the spring 100 ′ with the center side spring holding portion 23. Yes. As a result, the axial length L1 of the roller 17 is set longer than the axial length L2 of the spring 100 ', that is, the axial length of the holder 18b.

これら一対の剛性増加部50により、各柱部21の根元部分での剛性を向上させることができるので、遠心力によって保持器18bの各柱部21が撓むことが抑制され、保持器18bとばね100´との干渉が防止されるので、クラッチ性能が損なわれることがなく、特に、高速回転による運転環境においても有効である。   Since the rigidity at the base portion of each column portion 21 can be improved by the pair of rigidity increasing portions 50, bending of each column portion 21 of the retainer 18b due to centrifugal force is suppressed, and the retainer 18b and Since interference with the spring 100 'is prevented, the clutch performance is not impaired, and this is particularly effective in an operating environment with high-speed rotation.

また、本実施形態の剛性増加部50を有する保持器18bは、第4実施形態の逃げ部21aを有してもよく、また、第1〜第3実施形態のばね19,40が適用されてもよい。   Further, the cage 18b having the rigidity increasing portion 50 of the present embodiment may have the escape portion 21a of the fourth embodiment, and the springs 19 and 40 of the first to third embodiments are applied. Also good.

尚、本発明は、前述した実施形態に限定されるものではなく、適宜、変形、改良、等が可能である。   In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.

本実施形態では、外輪の内周面を円筒面、内輪の外周面をカム面としたが、外輪の内周面をカム面、内輪の外周面を円筒面とする構成であっても良い。
本実施形態では、一方向クラッチの内輪をスリーブ、一方向クラッチの外輪をプーリに圧入しているが、内輪をスリーブと、或いは外輪をプーリと一体に形成しても良い。
本実施形態では、クラッチ内蔵型プーリ装置はオルタネータの回転軸と従動プーリ間に装着されたが、スタータのプーリと回転軸間に装着されてもよく、この場合には、スリーブがプーリに対して所定方向に相対回転する傾向となる場合にのみ、スリーブとプーリとの間で回転力の伝達が自在となる。
In the present embodiment, the inner peripheral surface of the outer ring is a cylindrical surface and the outer peripheral surface of the inner ring is a cam surface, but the inner peripheral surface of the outer ring may be a cam surface and the outer peripheral surface of the inner ring may be a cylindrical surface.
In this embodiment, the inner ring of the one-way clutch is press-fitted into the sleeve and the outer ring of the one-way clutch is press-fitted into the pulley. However, the inner ring may be formed integrally with the sleeve, or the outer ring may be formed integrally with the pulley.
In this embodiment, the pulley device with a built-in clutch is mounted between the rotating shaft of the alternator and the driven pulley. However, it may be mounted between the pulley of the starter and the rotating shaft. Only when there is a tendency to relatively rotate in a predetermined direction, the transmission of the rotational force between the sleeve and the pulley becomes free.

また、本発明の保持器によるばねの保持方法は、本実施形態のように柱部の端部側ばね保持部と中央側ばね保持部によって保持されてもよいし、一対の円環部に設けられたばね保持部によって保持されてもよい。   Further, the spring holding method by the cage of the present invention may be held by the end side spring holding part and the center side spring holding part of the column part as in this embodiment, or provided in a pair of ring parts. It may be held by a spring holding portion.

10 クラッチ内蔵型プーリ装置
11 スリーブ
12 プーリ
13 一方向クラッチ
14 サポート軸受
15 内輪
15a ランプ部
16 外輪
17 ローラ
18 保持器
19,40 ばね
21 柱部
21a 逃げ部
26,42 折曲部(最大応力が発生する部位)
27,43 押圧部
28,45 接触部
DESCRIPTION OF SYMBOLS 10 Pulley apparatus with a built-in clutch 11 Sleeve 12 Pulley 13 One-way clutch 14 Support bearing 15 Inner ring 15a Lamp part 16 Outer ring 17 Roller 18 Cage 19,40 Spring 21 Column part 21a Escape part 26, 42 Bending part (maximum stress is generated) Part to do)
27, 43 Pressing part 28, 45 Contact part

Claims (1)

回転軸が内嵌されるスリーブと、前記スリーブの径方向外側に該スリーブと同心に配置されたプーリと、前記スリーブの外周面と前記プーリの内周面との間に設けられ、前記プーリと前記スリーブの一方が他方に対して所定の方向に相対回転する傾向となる場合のみ、前記プーリと前記スリーブとの間で回転力を伝達する一方向クラッチと、前記スリーブの外周面と前記プーリの内周面との間で前記一方向クラッチに対して軸方向に離間した位置に設けられ、前記プーリに加わるラジアル荷重を支承しつつ前記プーリと前記スリーブとの相対回転を可能とするサポート軸受と、を備え、
前記一方向クラッチは、前記スリーブと前記プーリのうちの一方の部材と共に回転する保持器と、前記保持器に保持された複数の係合子と、前記複数の係合子を係合する方向に押圧するばねと、を備え、
前記保持器は、一対の円環部と、該一対の円環部を連結する複数の柱部と、該保持器とは別体の前記ばねを挟持する、該一対の円環部の内側面で各柱部と整合する部分に設けられた一対の端部側ばね保持部と各柱部の軸方向中央部に設けられた中央側ばね保持部とを備え、
前記ばねは、前記一対の端部側ばね保持部と前記中央側ばね保持部に挟持される基部と、該基部の両側を屈曲部として該基部に対して鋭角に折れ曲がった一対の押圧部を備える板ばねである自動車の補機用一方向クラッチ内蔵型プーリ装置であって、
前記保持器の柱部には、前記ばねの接触部の可動領域を避けるように径方向に貫通した切欠きが設けられていることを特徴とする自動車の補機用一方向クラッチ内蔵型プーリ装置。
A sleeve in which a rotation shaft is fitted; a pulley disposed concentrically with the sleeve on a radially outer side of the sleeve; and provided between an outer peripheral surface of the sleeve and an inner peripheral surface of the pulley; Only when one of the sleeves tends to rotate relative to the other in a predetermined direction, a one-way clutch that transmits rotational force between the pulley and the sleeve, an outer peripheral surface of the sleeve, and the pulley A support bearing provided in a position axially separated from the inner circumferential surface with respect to the one-way clutch, and capable of rotating the pulley and the sleeve while supporting a radial load applied to the pulley; With
The one-way clutch presses a retainer that rotates together with one member of the sleeve and the pulley, a plurality of engagement elements held by the retainer, and a direction in which the engagement elements are engaged. A spring, and
The retainer includes a pair of annular portions, a plurality of column portions connecting the pair of annular portions, and an inner surface of the pair of annular portions that sandwich the spring separately from the retainer. A pair of end-side spring holding portions provided in a portion aligned with each column portion and a central-side spring holding portion provided in the axial center portion of each column portion,
The spring includes a pair of end-side spring holding portions and a base portion sandwiched between the center-side spring holding portions, and a pair of pressing portions bent at an acute angle with respect to the base portion with both sides of the base portion being bent portions. It is a pulley device with a built-in one-way clutch for automotive auxiliary equipment that is a leaf spring,
A pulley apparatus with a built-in one-way clutch for automobile auxiliary equipment , wherein a notch penetrating in a radial direction is provided in a pillar portion of the retainer so as to avoid a movable region of a contact portion of the spring. .
JP2010276022A 2005-12-14 2010-12-10 Pulley device with built-in one-way clutch for automotive auxiliary equipment Expired - Fee Related JP5353869B2 (en)

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