JP2005195116A - Pulley device - Google Patents

Pulley device Download PDF

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JP2005195116A
JP2005195116A JP2004003100A JP2004003100A JP2005195116A JP 2005195116 A JP2005195116 A JP 2005195116A JP 2004003100 A JP2004003100 A JP 2004003100A JP 2004003100 A JP2004003100 A JP 2004003100A JP 2005195116 A JP2005195116 A JP 2005195116A
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outer ring
pulley
peripheral surface
groove
parallel
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JP4345486B2 (en
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Koji Takahashi
孝治 高橋
Hiroshi Ishiguro
博 石黒
Hiroyuki Yamada
裕普 山田
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NSK Ltd
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NSK Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To realize a structure capable of preventing generation of a moment load with respect to an outer ring 7c and a pulley made of synthetic resin and arranged around the outer ring 7c and of sufficiently preventing creep generated between the outer ring 7c and the pulley. <P>SOLUTION: A spiral inclination groove 14b inclined to the circumferential direction and parallel grooves 15a, 15a parallel with the circumferential direction are formed on the outer peripheral face of the outer ring 7c. The number of turns of the inclination groove 14b is set to be an integer number. Both end parts of the inclination groove 14b and intermediate parts of each of the parallel grooves 15a, 15a are continuously connected. Due to this structure, the above problem can be solved. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

この発明に係るプーリ装置は、例えば、無端ベルトにより、自動車用のエアコンディショナに使用するコンプレッサ等の補機を駆動する機構や、タイミングベルトにより、クランクシャフトの端部に固定したクランクプーリとカムシャフトの端部に固定したカムプーリとの間で回転力を伝達する機構等のベルト伝動機構に組み込んで使用される、ガイドプーリやテンションプーリとして使用する。   The pulley device according to the present invention includes, for example, a mechanism for driving an auxiliary machine such as a compressor used in an air conditioner for an automobile by an endless belt, or a crank pulley and a cam fixed to an end of a crankshaft by a timing belt. It is used as a guide pulley or tension pulley that is used by being incorporated in a belt transmission mechanism such as a mechanism for transmitting rotational force to and from a cam pulley fixed to the end of the shaft.

ベルト伝動機構に組み込まれて使用されるガイドプーリやテンションプーリ等のプーリ装置として、重量軽減及びコスト低減を図る為に、転がり軸受の外輪に合成樹脂製のプーリを固設したプーリ装置が従来から使用されている。図６は、例えば特許文献１に記載されて従来から知られた、合成樹脂製のプーリを組み込んだプーリ装置１を示している。このプーリ装置１は、外周面にベルトを掛け渡す為の合成樹脂製のプーリ２と、このプーリ２を支持軸等に回転自在に支持する為の、単列深溝型のラジアル玉軸受である転がり軸受３とから構成される。このうちの転がり軸受３は、外周面に単列の内輪軌道４を有する内輪５と、内周面に単列の外輪軌道６を有する外輪７と、これら内輪軌道４と外輪軌道６との間に転動自在に設けられた複数個の転動体（玉）８とを備える。又、上記内輪５の両端部外周面と、上記外輪７の両端部内周面との間に密封板９、９を設け、上記各転動体８を設置した空間に充填したグリースが外部に漏れるのを防止すると共に、外部の塵芥等がこの空間内に入り込む事を防止している。そして、この様に構成される上記転がり軸受３の外輪７の外周面に、上記プーリ２を固設している。   As a pulley device such as a guide pulley or a tension pulley that is incorporated in a belt transmission mechanism, a pulley device in which a synthetic resin pulley is fixed to an outer ring of a rolling bearing has been conventionally used in order to reduce weight and cost. in use. FIG. 6 shows a pulley apparatus 1 incorporating a synthetic resin pulley described in, for example, Patent Document 1 and conventionally known. This pulley apparatus 1 is a rolling roller which is a single-row deep groove type radial ball bearing for rotatably supporting a pulley on a support shaft or the like, and a synthetic resin pulley 2 for belting the outer peripheral surface. And a bearing 3. Among these, the rolling bearing 3 includes an inner ring 5 having a single-row inner ring raceway 4 on an outer peripheral surface, an outer ring 7 having a single-row outer ring raceway 6 on an inner peripheral surface, and between the inner ring raceway 4 and the outer ring raceway 6. And a plurality of rolling elements (balls) 8 provided so as to be freely rollable. Further, sealing plates 9 and 9 are provided between the outer peripheral surfaces of both ends of the inner ring 5 and the inner peripheral surfaces of both ends of the outer ring 7, and grease filled in the space where the rolling elements 8 are installed leaks to the outside. In addition to preventing external dust and the like from entering this space. And the said pulley 2 is fixedly provided in the outer peripheral surface of the outer ring | wheel 7 of the said rolling bearing 3 comprised in this way.

上記プーリ２は、互いに同心に設けられた内径側円筒部１０及び外径側円筒部１１を有する。この内径側円筒部１０の中間部外周面と外径側円筒部１１の中間部内周面とは、円輪状の連結部１２により連結しており、この連結部１２の両側面にそれぞれ複数本ずつの補強リブ１３、１３を、それぞれ放射状に設けている。この様なプーリ２は、上記内径側円筒部１０を上記転がり軸受３を構成する外輪７の周囲に、射出成形により固設している。即ち、この外輪７の外周寄り部分をその内周側にモールドした状態で、金型内に設けた上記プーリ２の外形に対応した内形を有するキャビティ内に、溶融した熱可塑性樹脂を注入する。そして、この熱可塑性樹脂が冷却・固化した後に上記金型を開いて、上記プーリ２を上記転がり軸受３と共に、上記キャビティ内から取り出す。   The pulley 2 has an inner diameter side cylindrical portion 10 and an outer diameter side cylindrical portion 11 provided concentrically with each other. The outer peripheral surface of the intermediate portion of the inner diameter side cylindrical portion 10 and the inner peripheral surface of the intermediate portion of the outer diameter side cylindrical portion 11 are connected by a ring-shaped connecting portion 12, and a plurality of both are provided on both side surfaces of the connecting portion 12. The reinforcing ribs 13 and 13 are provided radially. In such a pulley 2, the inner diameter side cylindrical portion 10 is fixed around the outer ring 7 constituting the rolling bearing 3 by injection molding. That is, in a state where the outer ring 7 is molded on the inner peripheral side, the molten thermoplastic resin is injected into a cavity having an inner shape corresponding to the outer shape of the pulley 2 provided in the mold. . After the thermoplastic resin has cooled and solidified, the mold is opened, and the pulley 2 is taken out of the cavity together with the rolling bearing 3 from the cavity.

上述の様に構成されるプーリ装置１は、例えば、自動車の補機等を駆動するベルト伝動機構に組み込まれる、ガイドプーリやテンションプーリとして使用される。即ち、エンジンのシリンダブロック等の固定の部分に固設した支持軸に、上記転がり軸受３を構成する内輪５を外嵌固定する。そして、上記プーリ２の外周面に無端ベルトを掛け渡す。この状態で上記プーリ装置１は、この無端ベルトの走行に伴い上記プーリ２が回転し、この無端ベルトの巻き付け角度を確保したり、或はこの無端ベルトの張力を確保する。   The pulley apparatus 1 configured as described above is used as, for example, a guide pulley or a tension pulley incorporated in a belt transmission mechanism that drives an auxiliary machine of an automobile. That is, the inner ring 5 constituting the rolling bearing 3 is externally fitted and fixed to a support shaft fixed to a fixed part such as a cylinder block of the engine. Then, an endless belt is stretched around the outer peripheral surface of the pulley 2. In this state, the pulley device 1 rotates the pulley 2 as the endless belt travels, and ensures the winding angle of the endless belt or the tension of the endless belt.

上述の様に、外輪７の外周面に合成樹脂製のプーリ２を固設するプーリ装置１の場合、この外輪７が軸受鋼等の金属材料製である為、この外輪７と上記プーリ２との線膨張係数が異なる。従って、使用時の温度上昇により、これら外輪７とプーリ２との密着性が低下し、これら外輪７とプーリ２との間で相対的な滑り（クリープ）が発生する場合がある。この様なクリープを防止する為の技術として、例えば特許文献２〜３等に記載されている様に、外輪の外周面に凹溝を形成する構造が従来から知られている。   As described above, in the case of the pulley device 1 in which the synthetic resin pulley 2 is fixed to the outer peripheral surface of the outer ring 7, since the outer ring 7 is made of a metal material such as bearing steel, the outer ring 7 and the pulley 2 Have different linear expansion coefficients. Therefore, due to a temperature rise during use, the adhesion between the outer ring 7 and the pulley 2 may be reduced, and a relative slip (creep) may occur between the outer ring 7 and the pulley 2. As a technique for preventing such creep, a structure in which a concave groove is formed on the outer peripheral surface of an outer ring has been conventionally known as described in, for example, Patent Documents 2 to 3.

図７は、このうちの特許文献２に記載されている、クリープを防止する為の従来構造の第１例を示している。この構造では、外輪７ａの外周面に、円周方向に対し傾斜した傾斜凹溝１４を螺旋状に形成すると共に、円周方向に対し平行な平行凹溝１５を形成している。そして、上記外輪７ａの周囲に配置したプーリ２ａを構成する合成樹脂の一部を上記傾斜凹溝１４及び平行凹溝１５内に進入・固化させる事で、このプーリ２ａの内周面に突条１６、１６ａを形成し、この突条１６、１６ａと上記傾斜凹溝１４及び平行凹溝１５とを係合させている。このうちの傾斜凹溝１４は、円周方向に対し傾斜している為、この傾斜凹溝１４の側面と上記突条１６との噛み合いにより、上記外輪７ａとプーリ２ａとの間でクリープが発生する事を防止できる。   FIG. 7 shows a first example of a conventional structure described in Patent Document 2 for preventing creep. In this structure, the inclined groove 14 inclined with respect to the circumferential direction is formed in a spiral shape on the outer peripheral surface of the outer ring 7a, and the parallel groove 15 parallel to the circumferential direction is formed. Then, a part of the synthetic resin constituting the pulley 2a disposed around the outer ring 7a is caused to enter and solidify into the inclined concave groove 14 and the parallel concave groove 15, so that a ridge is formed on the inner peripheral surface of the pulley 2a. 16 and 16a are formed, and the protrusions 16 and 16a are engaged with the inclined grooves 14 and the parallel grooves 15. Of these, the inclined groove 14 is inclined with respect to the circumferential direction, so that creep occurs between the outer ring 7a and the pulley 2a due to the engagement between the side surface of the inclined groove 14 and the protrusion 16. Can be prevented.

又、図８は、特許文献３に記載されている、クリープを防止する為の従来構造の第２例を示している。この構造では、外輪７ｂの外周面に無端の傾斜凹溝１４ａを、円周方向に対し傾斜した状態で形成している。この構造の場合も、射出成形時にプーリの内周面に形成される突条と上記傾斜凹溝１４ａとを係合させる。この傾斜凹溝１４ａは、円周方向に対し傾斜すると共に、深さ及び幅が円周方向に漸次変化している。この為、この傾斜凹溝１４ａの側面及び底面と、上記プーリの内周面に形成された突条の側面及び先端面との噛み合いにより、上記外輪７ｂとプーリとの間でクリープが発生する事を防止できる。   FIG. 8 shows a second example of a conventional structure described in Patent Document 3 for preventing creep. In this structure, an endless inclined groove 14a is formed on the outer peripheral surface of the outer ring 7b in a state inclined with respect to the circumferential direction. Also in this structure, the protrusion formed on the inner peripheral surface of the pulley at the time of injection molding is engaged with the inclined groove 14a. The inclined concave groove 14a is inclined with respect to the circumferential direction, and the depth and width gradually change in the circumferential direction. For this reason, creep occurs between the outer ring 7b and the pulley due to the meshing of the side surface and bottom surface of the inclined groove 14a with the side surface and tip surface of the ridge formed on the inner peripheral surface of the pulley. Can be prevented.

上述の図７、８に示した構造では、傾斜凹溝１４、１４ａと突条との係合によりクリープを防止する為、プーリ２ａが外輪７ａ、７ｂに対し回転する傾向になると、上記傾斜凹溝１４、１４ａの内側面と突条の側面との押し付け合いに基づいて、上記外輪７ａ、７ｂに軸方向の分力が作用する。そして、この分力に基づいて、この外輪７ａ、７ｂにモーメント荷重が作用する場合がある。即ち、図７に示した構造の場合、この外輪７ａの円周方向に関して、上記傾斜凹溝１４の始点と終点とを完全に一致させない限り、この傾斜凹溝１４のうちで上記外輪７ａの軸方向に関して重畳した部分の数が、円周方向に関して互いに異なってしまう。上記傾斜凹溝１４の単位長さ当り、軸方向に作用する力の大きさはそれぞれ同じであると考えられる為、軸方向に重畳した数により、上記外輪７ａの軸方向に作用する分力が異なる。従って、上記傾斜凹溝１４の始点と終点とが円周方向に関して完全に一致しない限り、上記外輪７ａに対し軸方向に作用する分力が、円周方向に関して互いに異なり、この分力の差に応じたモーメント荷重が作用する。   In the structure shown in FIGS. 7 and 8 described above, when the pulley 2a tends to rotate with respect to the outer rings 7a and 7b in order to prevent creep by engagement between the inclined grooves 14 and 14a and the protrusions, the inclined grooves A component force in the axial direction acts on the outer rings 7a and 7b based on the pressing of the inner side surfaces of the grooves 14 and 14a and the side surfaces of the protrusions. A moment load may act on the outer rings 7a and 7b based on this component force. That is, in the case of the structure shown in FIG. 7, the axis of the outer ring 7a in the inclined groove 14 is not set unless the start point and the end point of the inclined groove 14 are completely coincided with each other in the circumferential direction of the outer ring 7a. The number of overlapping portions with respect to the direction is different from each other with respect to the circumferential direction. Since the magnitude of the force acting in the axial direction per unit length of the inclined concave groove 14 is considered to be the same, the component force acting in the axial direction of the outer ring 7a depends on the number superimposed in the axial direction. Different. Therefore, unless the starting point and the end point of the inclined groove 14 are completely coincident with each other in the circumferential direction, the component forces acting in the axial direction on the outer ring 7a are different from each other in the circumferential direction, and the difference between the component forces is different. The corresponding moment load is applied.

前記特許文献２に記載された構造では、外輪７ａの外周面に、傾斜凹溝１４に加え、この外輪７ａの円周方向に対し平行な平行凹溝１５を形成して、この外輪７ａに加わる軸方向の力を支承している。但し、モーメント荷重を発生する事自体を防止しない限り、上記平行凹溝１５の内側面と合成樹脂製のプーリ２ａの内周面に形成された突条１６、１６ａの側面との当接部に繰り返し押し付け力が加わる。この結果、長期間に亙る使用に伴って、上記プーリ２ａの内周面に形成された突条１６、１６ａと、上記外輪７ａの外周面に形成された傾斜凹溝１４及び平行凹溝１５との係合部に隙間が生じ、この外輪７ａに対して上記プーリ２ａががたつく可能性がある。一方、前記特許文献３に記載された構造では、無端状の傾斜凹溝１４ａとプーリの内周面に形成された突条との係合に基づいて外輪７ｂに加わるモーメント荷重を支承する為の平行凹溝を形成していない為、上述した様な問題はより顕著になる。   In the structure described in Patent Document 2, in addition to the inclined concave groove 14, a parallel concave groove 15 parallel to the circumferential direction of the outer ring 7a is formed on the outer peripheral surface of the outer ring 7a, and is added to the outer ring 7a. Axial force is supported. However, as long as the moment load itself is not prevented, the contact portion between the inner side surface of the parallel groove 15 and the side surface of the ridges 16 and 16a formed on the inner peripheral surface of the pulley 2a made of synthetic resin is used. Repeated pressing force is applied. As a result, with use over a long period of time, the ridges 16, 16a formed on the inner peripheral surface of the pulley 2a, the inclined concave grooves 14 and the parallel concave grooves 15 formed on the outer peripheral surface of the outer ring 7a, There is a possibility that a gap is formed in the engaging portion of the inner wheel, and the pulley 2a rattles against the outer ring 7a. On the other hand, in the structure described in Patent Document 3, the moment load applied to the outer ring 7b is supported based on the engagement between the endless inclined concave groove 14a and the protrusion formed on the inner peripheral surface of the pulley. Since the parallel concave grooves are not formed, the problem as described above becomes more remarkable.

特開平１０−１２２３３９号公報JP-A-10-122339 実開昭５８−３５０１３号公報Japanese Utility Model Publication No. 58-35013 特開２００３−６５４２４号公報JP 2003-65424 A

本発明は、上述の様な事情に鑑みて、外輪及びプーリにモーメント荷重が発生する事を防止すると共に、これら外輪とプーリとの間で発生するクリープを十分に防止できる構造を実現すべく発明したものである。   In view of the circumstances as described above, the present invention is designed to prevent a moment load from being generated on the outer ring and the pulley, and to realize a structure capable of sufficiently preventing creep generated between the outer ring and the pulley. It is a thing.

本発明のプーリ装置は、前述した各従来構造と同様に、内輪と、外輪と、複数個の転動体と、合成樹脂製のプーリとを備える。
このうちの内輪は、外周面に内輪軌道を有する。
又、上記外輪は、内周面に外輪軌道を有する。
又、上記各転動体は、これら内輪軌道と外輪軌道との間に、転動自在に設けられている。
更に、上記プーリは、上記外輪の外周面に固設している。
そして、この外輪の外周面に円周方向に関し傾斜した状態で形成された傾斜凹溝内に上記プーリを構成する合成樹脂の一部を進入させる事で、このプーリと上記外輪との相対回転を阻止している。
特に、本発明のプーリ装置に於いては、上記傾斜凹溝は、螺旋状に形成され、巻数が整数であり、この傾斜凹溝の一部と、上記外輪の外周面の円周方向に対し平行に形成された平行凹溝とが連続している。 The pulley apparatus of the present invention includes an inner ring, an outer ring, a plurality of rolling elements, and a synthetic resin pulley, as in the conventional structures described above.
Of these, the inner ring has an inner ring raceway on the outer peripheral surface.
The outer ring has an outer ring raceway on the inner peripheral surface.
Each of the rolling elements is provided between the inner ring raceway and the outer ring raceway so as to be freely rollable.
Further, the pulley is fixed to the outer peripheral surface of the outer ring.
Then, by causing a part of the synthetic resin constituting the pulley to enter the inclined groove formed in the outer circumferential surface of the outer ring in a state inclined with respect to the circumferential direction, relative rotation between the pulley and the outer ring is caused. Blocking.
In particular, in the pulley device of the present invention, the inclined groove is formed in a spiral shape and the number of turns is an integer. A part of the inclined groove and the circumferential direction of the outer peripheral surface of the outer ring are The parallel grooves formed in parallel are continuous.

上述の様に構成される本発明のプーリ装置の場合、外輪及びプーリにモーメント荷重が発生する事を防止すると共に、これら外輪とプーリとの間で発生するクリープを十分に防止できる。
即ち、上記外輪の外周面に螺旋状の傾斜凹溝を形成している為、全周に亙ってクリープ防止機能を発揮できる。この結果、クリープの発生を十分に防止できる。又、この傾斜凹溝の巻数（外輪外周面の周回数）が整数である為、この傾斜凹溝のうちで軸方向に関して重畳する溝の数が、全周に亙って同じとなる。従って、この傾斜凹溝とプーリの内周面に形成された突条との係合に基づいて軸方向に加わる分力の大きさが、全周に亙って同じとなる。この為、外輪とプーリとが相対回転する傾向になっても、これら外輪及びプーリにモーメント荷重が加わる事はない。 In the case of the pulley device of the present invention configured as described above, moment load is prevented from being generated in the outer ring and the pulley, and creep generated between the outer ring and the pulley can be sufficiently prevented.
That is, since the spiral inclined groove is formed on the outer peripheral surface of the outer ring, the creep preventing function can be exhibited over the entire periphery. As a result, the occurrence of creep can be sufficiently prevented. Since the number of turns of the inclined groove (the number of turns of the outer peripheral surface of the outer ring) is an integer, the number of grooves that overlap in the axial direction among the inclined grooves is the same over the entire circumference. Accordingly, the magnitude of the component force applied in the axial direction based on the engagement between the inclined concave groove and the protrusion formed on the inner peripheral surface of the pulley is the same over the entire circumference. For this reason, even if the outer ring and the pulley tend to rotate relative to each other, a moment load is not applied to the outer ring and the pulley.

又、本発明の場合、上記外輪の外周面に平行凹溝を形成している為、例えば上記傾斜凹溝と各突条との係合部の摩擦係数の相違等により、仮にモーメント荷重や軸方向荷重を相殺し切れない場合でも、これら各荷重を効果的に支承して、外輪とプーリとの結合部の強度並びに剛性をより高くできる。又、上記平行凹溝により、このプーリに対するこの外輪の軸方向の位置決め精度が向上する。更に、本発明の場合、上記傾斜凹溝の一部と上記平行凹溝とを連続させている為、これら各凹溝を形成する際に、途中で工具の位置を設定し直す事なく、１回の工程で加工を行なえる。この為、加工コストを低く抑えられる。   In the present invention, parallel grooves are formed on the outer peripheral surface of the outer ring. For example, the moment load and the shaft are temporarily changed due to the difference in the friction coefficient of the engaging portion between the inclined groove and each protrusion. Even when the directional load cannot be completely cancelled, each of these loads can be effectively supported, and the strength and rigidity of the joint between the outer ring and the pulley can be further increased. The parallel concave grooves improve the axial positioning accuracy of the outer ring with respect to the pulley. Furthermore, in the case of the present invention, since a part of the inclined grooves and the parallel grooves are made continuous, when forming these grooves, it is possible to set Processing can be performed in a single process. For this reason, the processing cost can be kept low.

本発明を実施する為に好ましくは、傾斜凹溝の巻数を３回以上とする。
この様に構成すれば、傾斜凹溝とプーリの内周面に形成される突条との係合部分が増加して、クリープ防止機能をより向上させる事ができる。 In order to carry out the present invention, the number of turns of the inclined groove is preferably 3 or more.
If comprised in this way, the engagement part of a sloping groove and the protrusion formed in the internal peripheral surface of a pulley will increase, and a creep prevention function can be improved more.

図１〜２は、本発明の実施例を示している。本実施例に組み込む外輪７ｃは、その外周面に、傾斜凹溝１４ｂと平行凹溝１５ａ、１５ａとを形成している。このうちの傾斜凹溝１４ｂは、螺旋状に形成されており、巻数（傾斜凹溝１４ｂが外輪７ｃの外周面を周回する回数）を、整数である３回としている。この為、この外輪７ｃの外周面の円周方向に関して、上記傾斜凹溝１４ｂの始点Ｐ1 と終点Ｐ2 とは、互いに同じ位置に存在する。又、本実施例の場合、上記外輪７ｃの外周面の軸方向両端寄りに、円周方向に対し平行な、上記両平行凹溝１５ａ、１５ａを形成している。そして、これら両平行凹溝１５ａ、１５ａの中間部に、上記傾斜凹溝１４ｂの両端部を、それぞれ連続させている。従って、これら各平行凹溝１５ａ、１５ａは、上記外輪７ｃの軸方向に関して、上記始点Ｐ1 と終点Ｐ2 とに整合する位置に形成されている。 1 and 2 show an embodiment of the present invention. The outer ring 7c incorporated in the present embodiment is formed with inclined concave grooves 14b and parallel concave grooves 15a and 15a on the outer peripheral surface thereof. Of these, the inclined groove 14b is formed in a spiral shape, and the number of turns (the number of times the inclined groove 14b circulates around the outer peripheral surface of the outer ring 7c) is an integer of three. For this reason, the start point P 1 and the end point P 2 of the inclined groove 14b exist at the same position with respect to the circumferential direction of the outer peripheral surface of the outer ring 7c. In the case of the present embodiment, the parallel concave grooves 15a, 15a parallel to the circumferential direction are formed near both axial ends of the outer peripheral surface of the outer ring 7c. And the both ends of the said inclined ditch | groove 14b are made to continue to the intermediate part of both these parallel ditch | grooves 15a and 15a, respectively. Accordingly, each of these parallel concave grooves 15a, 15a is formed at a position aligned with the start point P 1 and the end point P 2 in the axial direction of the outer ring 7c.

尚、上記傾斜凹溝１４ｂ及び上記各平行凹溝１５ａ、１５ａの母線形状は、それぞれ円弧状とする事が好ましい。これにより、この傾斜凹溝１４ｂとこれら各平行凹溝１５ａ、１５ａとが連続する部分の近傍で、これら各凹溝１４ｂ、１５ａ同士の間に存在する部分が破損しにくくなり、上記外輪７ｃの歩留を向上させる事ができる。又、上記各平行凹溝１５ａ、１５ａの幅寸法は、上記傾斜凹溝１４ｂよりも大きくする事が好ましい。更に、図３に示す様に、上記傾斜凹溝１４ｂの深さをｈ、溝底の直径をａ、上記外輪７ｃの外径をＤ、外輪軌道６の溝底の直径をｂ、各転動体８の直径をｄとした場合に、ｈ／Ｄ≧０．００７２、且つ、（ａ−ｂ）／ｄ≧０．３４３を満たす様に、上記傾斜凹溝１４ｂの深さｈを規制する事が好ましい。   In addition, it is preferable that the bus | bath shape of the said inclination ditch | groove 14b and each said parallel ditch | groove 15a, 15a shall be circular arc shape, respectively. Thereby, in the vicinity of the portion where the inclined groove 14b and the parallel grooves 15a and 15a are continuous, the portion existing between the grooves 14b and 15a is less likely to be damaged. Yield can be improved. Moreover, it is preferable that the width dimension of each said parallel ditch | groove 15a, 15a is made larger than the said inclined ditch | groove 14b. Further, as shown in FIG. 3, the depth of the inclined concave groove 14b is h, the diameter of the groove bottom is a, the outer diameter of the outer ring 7c is D, the diameter of the groove bottom of the outer ring raceway 6 is b, each rolling element. When the diameter of 8 is d, the depth h of the inclined groove 14b may be regulated so that h / D ≧ 0.0072 and (ab) /d≧0.343. preferable.

上述の様に、外周面に上記傾斜凹溝１４ｂ及び平行凹溝１５ａ、１５ａを形成した外輪７ｃの周囲には、前述した従来構造の場合と同様に、合成樹脂製のプーリ２ａ（図７参照）を射出成形する。即ち、上記外輪７ｃを、その外周面をキャビティの内周面部分に露出させた状態で、合成樹脂の射出成形用の金型にセットし、このキャビティ内に合成樹脂を送り込む。この結果、このキャビティ内に送り込まれた合成樹脂の一部が上記傾斜凹溝１４ｂ及び平行凹溝１５ａ、１５ａ内に入り込み、これら各凹溝１４ｂ、１５ａ内で冷却されて固化し、突条となる。この様に、外径側に合成樹脂製のプーリ２ａを固着した上記外輪７ｃは、複数の転動体８、８及び内輪５（図７参照）と組み合わせて、プーリ装置とする。   As described above, the pulley 2a made of synthetic resin (see FIG. 7) is formed around the outer ring 7c having the inclined grooves 14b and the parallel grooves 15a and 15a formed on the outer peripheral surface, as in the case of the conventional structure described above. ) Is injection molded. That is, the outer ring 7c is set in a mold for injection molding of synthetic resin with the outer peripheral surface exposed to the inner peripheral surface portion of the cavity, and the synthetic resin is fed into the cavity. As a result, a part of the synthetic resin fed into the cavity enters the inclined grooves 14b and the parallel grooves 15a and 15a, and is cooled and solidified in the grooves 14b and 15a. Become. In this way, the outer ring 7c having the pulley 2a made of synthetic resin fixed to the outer diameter side is combined with the plurality of rolling elements 8, 8 and the inner ring 5 (see FIG. 7) to form a pulley device.

尚、上記プーリ２ａを構成する合成樹脂として、ポリアミド６、ポリアミド６６、ポリアミド４６、ポリアミド６１２等のポリアミド樹脂、ポリフェニレンサルファイド、フェノール樹脂等が使用可能である。又、この様な合成樹脂に混合する補強繊維として、ガラス繊維やカーボン繊維等を使用する。この補強繊維を混合する割合は、１０〜６０質量％、好ましくは２０〜５０質量％として、この補強繊維を混合した合成樹脂の線膨張係数を５×１０-5以下、曲げ弾性係数を５GPa 以上とする事が好ましい。尚、上記補強繊維を混合する割合を１０質量％未満とした場合、合成樹脂の線膨張係数が大きくなり過ぎると共に剛性が低下する。この結果、クリープが発生し易くなる為、好ましくない。又、上記補強繊維を混合する割合を６０質量％よりも多くした場合、射出成形時の流動性が悪くなってしまい、成形不具合が発生し易くなる為、好ましくない。 As the synthetic resin constituting the pulley 2a, polyamide resins such as polyamide 6, polyamide 66, polyamide 46, and polyamide 612, polyphenylene sulfide, phenol resin, and the like can be used. Moreover, glass fiber, carbon fiber, or the like is used as a reinforcing fiber mixed with such a synthetic resin. The ratio of mixing the reinforcing fibers is 10 to 60% by mass, preferably 20 to 50% by mass. The linear expansion coefficient of the synthetic resin mixed with the reinforcing fibers is 5 × 10 −5 or less, and the flexural modulus is 5 GPa or more. Is preferable. In addition, when the ratio which mixes the said reinforcement fiber shall be less than 10 mass%, rigidity will fall while the linear expansion coefficient of a synthetic resin becomes large too much. As a result, creep tends to occur, which is not preferable. Further, when the proportion of the reinforcing fibers mixed is more than 60% by mass, the fluidity at the time of injection molding is deteriorated and molding defects are likely to occur, which is not preferable.

上述の様に構成する本実施例の場合、上記外輪７ｃにモーメント荷重が発生する事を防止すると共に、この外輪７ｃと上記プーリ２ａとの間で発生するクリープを十分に防止できる。即ち、上記外輪７ｃの外周面に螺旋状の傾斜凹溝１４ｂを形成している為、全周に亙ってクリープ防止機能を発揮できる。この結果、クリープの発生を十分に防止できる。又、上記傾斜凹溝１４ｂの巻数が整数である為、この傾斜凹溝１４ｂのうちで軸方向に関して重畳する溝の数が、全周に亙って同じとなる。言い換えれば、上記傾斜凹溝１４ｂの巻数が整数でなければ、軸方向に関して重畳する溝の数が全周に亙って同じとならない。例えば、図４〜５に示す様に、傾斜凹溝１４ｃを２．５周（２周半）させた場合、始点Ｐ1 ′と終点Ｐ2 ′とが、外輪７ｃの円周方向に関して半周ずれた位置にそれぞれ存在する事となる。そして、この場合、図４〜５からも明らかな様に、外輪７ｃの外周面に形成される傾斜凹溝１４ｃのうち、軸方向に関して重畳する溝の数がこの外輪７ｃの円周方向に関して異なる。具体的には、軸方向に重畳する溝の数が、図４〜５の上半部では３本、下半部では２本となる。 In the present embodiment configured as described above, moment load is prevented from being generated in the outer ring 7c, and creep generated between the outer ring 7c and the pulley 2a can be sufficiently prevented. That is, since the spiral inclined groove 14b is formed on the outer peripheral surface of the outer ring 7c, the creep preventing function can be exhibited over the entire periphery. As a result, the occurrence of creep can be sufficiently prevented. Further, since the number of turns of the inclined groove 14b is an integer, the number of grooves that overlap in the axial direction among the inclined grooves 14b is the same over the entire circumference. In other words, unless the number of turns of the inclined groove 14b is an integer, the number of grooves overlapping in the axial direction is not the same over the entire circumference. For example, as shown in FIGS. 4 to 5, when the inclined groove 14 c is rotated 2.5 times (2 and a half), the start point P 1 ′ and the end point P 2 ′ are shifted from each other by a half in the circumferential direction of the outer ring 7 c. It will exist at each position. In this case, as is apparent from FIGS. 4 to 5, the number of grooves overlapping in the axial direction among the inclined concave grooves 14 c formed on the outer peripheral surface of the outer ring 7 c is different in the circumferential direction of the outer ring 7 c. . Specifically, the number of grooves overlapping in the axial direction is three in the upper half of FIGS. 4 to 5 and two in the lower half.

上述の様に、軸方向に関して重畳する溝の数が円周方向に関して異なれば、上記傾斜凹溝１４ｃとプーリ２ａの内周面に形成された突条との係合に基づいて軸方向に加わる分力の大きさが、円周方向に関して異なる。図示の例では、上記外輪７ｃの上半部の方が軸方向に重畳する溝の数が多い為、下半部に比べて上半部に加わる分力の方が大きくなる。そして、この分力の差により、上記外輪７ｃ及びプーリ２ａにモーメント荷重が発生する。これに対して、本実施例の様に、上記傾斜凹溝１４ｂの巻数を整数とした場合、この傾斜凹溝１４ｂと上記プーリ２ａの内周面に形成された突条との係合に基づいて軸方向に加わる分力の大きさが、全周に亙って同じとなる為、上記外輪７ｃとプーリ２ａとが相対回転する傾向になっても、これら外輪７ｃ及びプーリ２ａにモーメント荷重が加わる事はない。尚、上記傾斜凹溝１４ｂの巻数は、整数であれば良いが、クリープ防止機能をより向上させる為には、３回以上とする事が好ましい。又、上記傾斜凹溝１４ｂの深さｈを前述の様に規制すれば、クリープ防止機能をより向上させる事ができると共に、上記外輪７ｃの強度を十分に確保できる。   As described above, if the number of grooves overlapping in the axial direction is different in the circumferential direction, it is applied in the axial direction based on the engagement between the inclined concave groove 14c and the protrusion formed on the inner peripheral surface of the pulley 2a. The magnitude of the component force differs in the circumferential direction. In the illustrated example, the upper half of the outer ring 7c has a larger number of grooves overlapping in the axial direction, so that the component force applied to the upper half is greater than that of the lower half. A moment load is generated in the outer ring 7c and the pulley 2a due to the difference in component force. On the other hand, as in this embodiment, when the number of turns of the inclined groove 14b is an integer, this is based on the engagement between the inclined groove 14b and the protrusion formed on the inner peripheral surface of the pulley 2a. Therefore, even if the outer ring 7c and the pulley 2a tend to rotate relative to each other, a moment load is applied to the outer ring 7c and the pulley 2a. There will be no participation. The number of turns of the inclined concave groove 14b may be an integer, but it is preferably 3 times or more in order to further improve the creep prevention function. Further, if the depth h of the inclined concave groove 14b is restricted as described above, the creep prevention function can be further improved and the strength of the outer ring 7c can be sufficiently secured.

又、本実施例の場合、上記外輪７ｃの外周面に平行凹溝１５ａ、１５ａを形成している為、例えば上記傾斜凹溝１４ｂと各突条との係合部の摩擦係数の相違等により、仮にモーメント荷重や軸方向荷重を相殺し切れない場合でも、これら各荷重を効果的に支承して、上記外輪７ｃとプーリ２ａとの結合部の強度並びに剛性をより高くできる。又、上記平行凹溝１５ａ、１５ａにより、このプーリ２ａに対するこの外輪７ｃの軸方向の位置決め精度が向上する。又、上記平行凹溝１５ａ、１５ａの幅寸法を、上記傾斜凹溝１４ｂの幅寸法よりも大きくすれば、上記結合部の強度並びに剛性を高くする効果が顕著になる。   In the case of the present embodiment, since the parallel concave grooves 15a and 15a are formed on the outer peripheral surface of the outer ring 7c, for example, due to the difference in the friction coefficient of the engaging portion between the inclined concave groove 14b and each protrusion. Even if the moment load and the axial load cannot be completely canceled, these loads can be effectively supported to increase the strength and rigidity of the joint between the outer ring 7c and the pulley 2a. The parallel concave grooves 15a and 15a improve the axial positioning accuracy of the outer ring 7c with respect to the pulley 2a. Further, if the width dimension of the parallel grooves 15a, 15a is made larger than the width dimension of the inclined grooves 14b, the effect of increasing the strength and rigidity of the coupling portion becomes remarkable.

更に、本実施例の場合、上記傾斜凹溝１４ｂの両端部と上記平行凹溝１５ａ、１５ａとを連続させている為、これら各凹溝１４ｂ、１５ａを形成する際に、途中で工具の位置を設定し直す事なく、１回の工程で加工を行なえる。この為、加工コストを低く抑えられる。即ち、上記外輪７ｃの一端部側に、先ず、円周方向に対し平行な平行凹溝１５ａを形成する。次に、この平行凹溝１５ａの円周方向の一部から分岐する様に、工具の進む方向を円周方向に対し傾斜させる事により上記傾斜凹溝１４ｂの加工を行なう。そして、この傾斜凹溝１４ｂの終点となる端部から、今度は、工具の進む方向を円周方向に対し平行とする事により、上記外輪７ｃの他端部側の平行凹溝１５ａを形成する。この様に、本実施例の場合、上記外輪７ｃの外周面に上記傾斜凹溝１４ｂ及び平行凹溝１５ａ、１５ａの加工を、工具の位置を設定し直す事なく連続して行なえる為、加工コストを低く抑えられる。   Furthermore, in the case of the present embodiment, since both end portions of the inclined groove 14b and the parallel grooves 15a, 15a are made continuous, the position of the tool is halfway when forming these grooves 14b, 15a. Processing can be performed in a single process without re-setting. For this reason, the processing cost can be kept low. That is, first, a parallel groove 15a parallel to the circumferential direction is formed on one end of the outer ring 7c. Next, the inclined groove 14b is processed by inclining the direction in which the tool advances with respect to the circumferential direction so as to branch from a part of the circumferential direction of the parallel groove 15a. Then, the parallel concave groove 15a on the other end side of the outer ring 7c is formed by making the direction in which the tool advances parallel to the circumferential direction from the end that is the end point of the inclined concave groove 14b. . Thus, in the case of the present embodiment, the inclined groove 14b and the parallel grooves 15a, 15a can be continuously processed on the outer peripheral surface of the outer ring 7c without resetting the position of the tool. Cost can be kept low.

本発明の実施例１を、外輪のみを取り出して示す斜視図。1 is a perspective view showing Example 1 of the present invention with only an outer ring taken out. FIG. 図１の外径側から見た図。The figure seen from the outer diameter side of FIG. 外周面に傾斜凹溝を形成した外輪の一部断面図を、外輪軌道に転動体を設置した状態で示す図。The figure which shows the partial cross section figure of the outer ring which formed the inclined ditch | groove in the outer peripheral surface in the state which installed the rolling element in the outer ring track. 好ましくない例を、外輪のみを取り出して示す斜視図。The perspective view which takes out only an outer ring | wheel and shows an example which is not preferable. 図４の外径側から見た図。The figure seen from the outer diameter side of FIG. 従来構造のプーリ装置の部分切断斜視図。The partial cutaway perspective view of the pulley apparatus of conventional structure. クリープを防止する為の従来構造の第１例を示す部分断面図。The fragmentary sectional view which shows the 1st example of the conventional structure for preventing creep. 同第２例を示す、外輪を外径側から見た図。The figure which looked at the outer ring | wheel from the outer-diameter side which shows the 2nd example.

符号の説明Explanation of symbols

１ プーリ装置
２、２ａ プーリ
３ 転がり軸受
４ 内輪軌道
５ 内輪
６ 外輪軌道
７、７ａ、７ｂ、７ｃ 外輪
８ 転動体
９ 密封板
１０ 内径側円筒部
１１ 外径側円筒部
１２ 連結部
１３ 補強リブ
１４、１４ａ、１４ｂ、１４ｃ 傾斜凹溝
１５、１５ａ 平行凹溝
１６、１６ａ 突条 DESCRIPTION OF SYMBOLS 1 Pulley apparatus 2, 2a Pulley 3 Rolling bearing 4 Inner ring track 5 Inner ring 6 Outer ring track 7, 7a, 7b, 7c Outer ring 8 Rolling element 9 Sealing plate 10 Inner diameter side cylindrical part 11 Outer diameter side cylindrical part 12 Connection part 13 Reinforcement rib 14 , 14a, 14b, 14c Inclined groove 15, 15a Parallel groove 16, 16a

Claims (2)

外周面に内輪軌道を有する内輪と、内周面に外輪軌道を有する外輪と、これら内輪軌道と外輪軌道との間に転動自在に設けられた複数個の転動体と、この外輪の外周面に固設した合成樹脂製のプーリとを備え、この外輪の外周面に円周方向に関し傾斜した状態で形成された傾斜凹溝内にこのプーリを構成する合成樹脂の一部を進入させる事でこのプーリと上記外輪との相対回転を阻止したプーリ装置に於いて、上記傾斜凹溝は、螺旋状に形成され、巻数が整数であり、この傾斜凹溝の一部と、上記外輪の外周面の円周方向に対し平行に形成された平行凹溝とが連続している事を特徴とするプーリ装置。   An inner ring having an inner ring raceway on the outer peripheral surface, an outer ring having an outer ring raceway on the inner peripheral surface, a plurality of rolling elements provided so as to roll between the inner ring raceway and the outer ring raceway, and an outer peripheral surface of the outer ring And a synthetic resin pulley fixed to the outer ring, and a part of the synthetic resin constituting the pulley is inserted into an inclined groove formed on the outer peripheral surface of the outer ring in a state inclined with respect to the circumferential direction. In the pulley device that prevents relative rotation between the pulley and the outer ring, the inclined groove is formed in a spiral shape, and the number of turns is an integer. A part of the inclined groove, and the outer peripheral surface of the outer ring A pulley apparatus characterized in that a parallel groove formed in parallel to the circumferential direction of the groove is continuous. 傾斜凹溝の巻数が３回以上である、請求項１に記載したプーリ装置。   The pulley apparatus according to claim 1, wherein the number of turns of the inclined concave groove is three or more.
JP2004003100A 2004-01-08 2004-01-08 Pulley device Expired - Fee Related JP4345486B2 (en)

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Cited By (1)

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JP2007032280A (en) * 2005-07-22 2007-02-08 Nsk Ltd Water pump

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CN1972858B (en) 2004-06-21 2011-07-06 奥蒂斯电梯公司 Elevator system including multiple cars in a hoistway and controlling mehtod thereof
KR100966534B1 (en) 2004-12-16 2010-06-29 오티스 엘리베이터 컴파니 Elevator system with multiple cars in a hoistway
JP4833225B2 (en) 2004-12-29 2011-12-07 オーチス エレベータ カンパニー Compensation in elevator systems with multiple cars in one hoistway
EP1851155B1 (en) 2005-02-04 2013-12-25 Otis Elevator Company Calls assigned to one of two cars in a hoistway to minimze delay imposed on either car
CN101119916B (en) 2005-02-17 2010-09-29 奥蒂斯电梯公司 Collision prevention in hoistway with two elevator cars
CN100554120C (en) 2005-02-17 2009-10-28 奥蒂斯电梯公司 The method of elevator passenger is informed in the operation that car is gone to pit or top
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007032280A (en) * 2005-07-22 2007-02-08 Nsk Ltd Water pump

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