JP3195867B2 - Auto tensioner - Google Patents

Auto tensioner

Info

Publication number
JP3195867B2
JP3195867B2 JP24897893A JP24897893A JP3195867B2 JP 3195867 B2 JP3195867 B2 JP 3195867B2 JP 24897893 A JP24897893 A JP 24897893A JP 24897893 A JP24897893 A JP 24897893A JP 3195867 B2 JP3195867 B2 JP 3195867B2
Authority
JP
Japan
Prior art keywords
thick
thick portion
boss
insert bearing
rotation
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP24897893A
Other languages
Japanese (ja)
Other versions
JPH07103297A (en
Inventor
公計 木村
英樹 松本
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bando Chemical Industries Ltd
Original Assignee
Bando Chemical Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bando Chemical Industries Ltd filed Critical Bando Chemical Industries Ltd
Priority to JP24897893A priority Critical patent/JP3195867B2/en
Publication of JPH07103297A publication Critical patent/JPH07103297A/en
Application granted granted Critical
Publication of JP3195867B2 publication Critical patent/JP3195867B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/081—Torsion springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/0829—Means for varying tension of belts, ropes, or chains with vibration damping means
    • F16H2007/084—Means for varying tension of belts, ropes, or chains with vibration damping means having vibration damping characteristics dependent on the moving direction of the tensioner
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/0829—Means for varying tension of belts, ropes, or chains with vibration damping means

Landscapes

  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【産業上の利用分野】この発明は、例えば自動車エンジ
ンによる補機類駆動のためのＶベルト等に所定の張力を
付与しかつ該張力の変動に応じてダンピング力を自動的
に変化させるようにしたオートテンショナに関し、特に
そのダンピング力を高める対策に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method of applying a predetermined tension to a V-belt or the like for driving accessories by an automobile engine and automatically changing a damping force in accordance with the fluctuation of the tension. In particular, the present invention relates to measures for increasing the damping force of the auto tensioner.

【０００２】[0002]

【従来の技術】この種のオートテンショナとしては、例
えば米国特許第４４７３３６２号で示されるものが一般
に知られており、駆動プーリと複数の従動プーリとの間
に巻き掛けられたベルトのプーリ間スパンを押圧して、
駆動プーリの回転力を全ての従動プーリに伝達させるた
めに用いられる。2. Description of the Related Art An automatic tensioner of this type is generally known, for example, as shown in U.S. Pat. No. 4,473,362, and a span between pulleys of a belt wound between a driving pulley and a plurality of driven pulleys. Press
It is used to transmit the rotational force of the driving pulley to all the driven pulleys.

【０００３】具体的には、図６に例示するように、軸部
ａを有して例えば自動車エンジン等の固定体に固定され
る金属製の固定部材ｂと、該固定部材ｂの軸部ａに回動
可能に外嵌合されたボス部ｃを有するとともに、先端に
ボス部ｃの軸心と平行な軸心でプーリｄを回転自在に支
持するアーム部ｅが突設され、上記ボス部ｃにおいて固
定部材ｂに回動可能に支持された金属製の回動部材ｆ
と、上記両部材ｂ，ｆ間に縮装されて該回動部材ｆを固
定部材ｂに対し所定方向に回動付勢する捩りコイルばね
ｇとを備えている。そして、上記固定部材ｂの軸部ａと
回動部材ｆのボス部ｃとの間には略筒形状のインサート
ベアリングｈが、また上記回動部材ｆのボス部ｃ外周側
には略筒形状のスプリングサポートｉが、各々、ダンピ
ング部材として配設されている。More specifically, as shown in FIG. 6, a metal fixing member b having a shaft portion a and fixed to a fixed body such as an automobile engine, for example, and a shaft portion a of the fixing member b A boss portion c rotatably fitted to the boss portion and an arm portion e rotatably supporting a pulley d at an end thereof at an axis parallel to the axis of the boss portion c. c, a metal turning member f rotatably supported by the fixed member b.
And a torsion coil spring g compressed between the two members b and f to bias the rotating member f to rotate in a predetermined direction with respect to the fixed member b. A substantially cylindrical insert bearing h is provided between the shaft portion a of the fixed member b and the boss c of the rotating member f, and a substantially cylindrical insert bearing h is provided on the outer peripheral side of the boss c of the rotating member f. Are each provided as a damping member.

【０００４】上記オートテンショナでは、上記回動部材
ｆの回動付勢力によりプーリｄに図外のベルトを押圧さ
せて所定の張力を付与するのみならず、該張力の変動に
応じてダンピング力を変化させるようになされており、
付加価値の高いテンショナとなっている。つまり、上記
プーリｄにベルトが巻き掛けられた状態では、上記イン
サートベアリングｈ及びスプリングサポートｉと回動部
材ｆのボス部ｃとの各間にはベルト力（ベルトからプー
リｄにかかる反力）と捩りコイルばねｇの付勢力とが合
わさって摩擦によるダンピング力が発生する。そして、
この状態で、上記ベルトの張力が減少方向に変動する
と、ベルト力の減少に応じてダンピング力が小さくな
り、このことで、プーリｄのベルトへの追随性が高くな
ってベルトの張力低下が防止される。一方、ベルトの張
りに対してはベルト力の増大によりダンピング力も大き
くなり、このことで、プーリｄに大きい抵抗力が付与さ
れてベルトのばたつきが防止される。In the above-mentioned auto tensioner, not only a pulley d is pressed against a belt (not shown) by a turning urging force of the turning member f to apply a predetermined tension, but also a damping force is changed in accordance with a change in the tension. It is made to change,
It is a high value-added tensioner. That is, when the belt is wound around the pulley d, a belt force (a reaction force applied to the pulley d from the belt) is applied between the insert bearing h and the spring support i and the boss c of the rotating member f. And the urging force of the torsion coil spring g combine to generate a damping force due to friction. And
In this state, if the tension of the belt fluctuates in the decreasing direction, the damping force decreases in accordance with the decrease of the belt force, and the followability of the pulley d to the belt increases, thereby preventing the belt tension from decreasing. Is done. On the other hand, with respect to the tension of the belt, the damping force also increases due to the increase in the belt force, whereby a large resistance force is applied to the pulley d to prevent the belt from fluttering.

【０００５】[0005]

【発明が解決しようとする課題】ところで、小排気量の
自動車エンジンでは、気筒数が少ないために回転変動の
増加に伴ってベルト張力の変動が増加することから、よ
り大きいダンピング力を発生させる必要がある。By the way, in an automobile engine with a small displacement, since the number of cylinders is small, the fluctuation of the belt tension increases with the increase of the rotation fluctuation, so that it is necessary to generate a larger damping force. There is.

【０００６】その場合、インサートベアリングには、そ
の周方向１８０°未満の所定領域にインサートベアリン
グの周方向１８０°以上の残る領域の径方向への肉厚に
比して径方向外方へ厚肉な厚肉部が設けられ、捩りコイ
ルばねによる回動部材の所定方向への回動付勢時に、固
定部材の軸部と回動部材のボス部との間において固定部
材の軸部の中心に対して回動部材のボス部の回動軸心を
厚肉部側に偏心させて、回動部材の所定方向への回動が
スムーズに行えるようにし、アーム部のロックを確実に
回避するようにしている。そのため、大きいダンピング
力を発生させる必要があるオートテンショナにおいて
は、回動部材の偏心により、回動部材の反所定方向への
回動により縮径する捩りコイルばねによる，ボス部とイ
ンサートベアリングの厚肉部との間の摩擦力が小さなも
のとなり、大きいダンピング力を得る上で、オートテン
ショナに改良を加える必要があった。In this case, the insert bearing has a radially outwardly thicker portion in a predetermined region of less than 180 ° in the circumferential direction than the radial thickness of the remaining region of 180 ° or more in the circumferential direction of the insert bearing. When the torsion coil spring urges the turning member to turn in a predetermined direction, a thick portion is provided between the shaft of the fixing member and the boss of the turning member. On the other hand, the rotation axis of the boss portion of the rotation member is decentered toward the thick portion so that the rotation member can be smoothly rotated in a predetermined direction, and the locking of the arm portion is reliably avoided. I have to. Therefore, in an auto-tensioner that needs to generate a large damping force, the thickness of the boss and the insert bearing is reduced by a torsion coil spring whose diameter is reduced by the rotation of the rotation member in the opposite direction due to the eccentricity of the rotation member. The frictional force between the flesh and the meat became small, and it was necessary to improve the auto tensioner in order to obtain a large damping force.

【０００７】本発明はかかる点に鑑みてなされたもの
で、その目的とするところは、アーム部のロックを回避
しつつ、大きいダンピング力を発生し得るオートテンシ
ョナを提供することにある。SUMMARY OF THE INVENTION The present invention has been made in view of the foregoing, and an object of the present invention is to provide an auto tensioner capable of generating a large damping force while avoiding locking of an arm.

【０００８】[0008]

【課題を解決するための手段】上記目的を達成するた
め、請求項１記載の発明が講じた解決手段は、軸部を有
し、固定体に固定可能な固定部材と、上記固定部材の軸
部にボス部が回動可能に外嵌合され、該回動軸心と平行
な軸心周りに回転可能なプーリを有する回動部材と、上
記固定部材及び回動部材の間に縮装されて該回動部材を
固定部材に対し所定方向に回動付勢する捩りコイルばね
と、上記固定部材及び回動部材の間に介装されて該回動
部材の回動をダンピングするためのダンピング部材とを
備え、上記回動部材の回動付勢力により上記プーリにベ
ルトを押圧させて所定の張力を付与し、かつ上記張力の
変動に応じてダンピング力を変化させるようにしたオー
トテンショナを前提とし、上記ダンピング部材を、上記
固定部材の軸部と、上記回動部材のボス部との間に介装
されて該回動部材の回動時に該ボス部の内周面との間で
ベルト張力の変動に応じた摩擦力を発生する略筒形状の
インサートベアリングにより構成する。そして、上記イ
ンサートベアリングの周方向１８０°未満の所定領域
に、インサートベアリングの周方向１８０°以上の残る
領域の径方向への肉厚に比して径方向外方へ厚肉な第１
厚肉部を設けるとともに、上記所定領域の第１厚肉部に
対して不連続に対向するインサートベアリングの周方向
１８０°未満の残る領域に、インサートベアリングの径
方向外方へ膨出する厚肉な第２厚肉部を設ける構成とし
たものである。Means for Solving the Problems To achieve the above object, a solution taken by the invention according to claim 1 is a fixing member having a shaft portion, which can be fixed to a fixed body, and a shaft of the fixing member. A boss is rotatably fitted to the outer portion of the boss, and a rotator having a pulley rotatable about an axis parallel to the rotator, and a compression member between the fixed member and the rotator. A torsion coil spring for urging the rotating member to rotate in a predetermined direction with respect to the fixed member, and a damping member interposed between the fixed member and the rotating member for damping the rotation of the rotating member. And an auto-tensioner that includes a member, and applies a predetermined tension by pressing a belt against the pulley by a rotation urging force of the rotation member, and changes a damping force according to a change in the tension. And, the damping member, the shaft portion of the fixed member, A substantially cylindrical shape that is interposed between the rotating member and the boss and generates a frictional force between the rotating member and the inner peripheral surface of the rotating member in accordance with a change in belt tension. It is composed of insert bearings. A first region radially outwardly thicker than a radially thicker region of the insert bearing in a predetermined region less than 180 ° in the circumferential direction is formed in a predetermined region less than 180 ° in the circumferential direction of the insert bearing.
A thick portion bulging radially outward of the insert bearing is provided in a remaining region of less than 180 ° in the circumferential direction of the insert bearing which is discontinuously opposed to the first thick portion in the predetermined region while providing the thick portion. And a second thick portion.

【０００９】また、請求項２記載の発明が講じた解決手
段は、上記請求項１記載の発明の第２厚肉部を特定し、
インサートベアリングの軸心方向略半分位置よりも軸部
基端側に位置する残る領域一側に段差状に設ける構成と
したものである。Further, the solution taken by the invention of claim 2 is to specify the second thick portion of the invention of claim 1,
In this configuration, the insert bearing is provided in a step shape on one side of the remaining region located closer to the shaft base end than substantially half the axial direction of the insert bearing.

【００１０】また、請求項３記載の発明が講じた解決手
段は、上記請求項２記載の発明の第１厚肉部を特定し、
インサートベアリングの軸心方向略半分位置よりも軸部
先端側に位置する所定領域他側に段差状に設ける構成と
したものである。[0010] Further, a solution taken by the invention of claim 3 is to specify the first thick portion of the invention of claim 2 described above,
The insert bearing is provided in a stepped shape on the other side of a predetermined region located on the distal end side of the shaft portion with respect to a substantially half position in the axial center direction of the insert bearing.

【００１１】さらに、請求項４記載の発明が講じた解決
手段は、上記請求項１、請求項２または請求項３記載の
発明の第１厚肉部の径方向への肉厚および第２厚肉部の
径方向への肉厚を特定し、互いに略一致せしめる構成と
したものである。[0011] Further, a solution taken by the invention according to claim 4 is that the first thick portion of the invention according to claim 1, 2, or 3 has a radial thickness and a second thickness. The thickness of the wall portion in the radial direction is specified so as to substantially match each other.

【００１２】[0012]

【作用】上記の構成により、請求項１記載の発明では、
インサートベアリングの周方向１８０°未満の所定領域
の第１厚肉部に対して不連続に対向するインサートベア
リングの周方向１８０°未満の残る領域に、インサート
ベアリングの径方向外方へ膨出する厚肉な第２厚肉部が
設けられているので、捩りコイルばねを縮径させる回動
部材の反所定方向への回動時、固定部材の軸部と回動部
材のボス部との間において、回動部材のボス部の回動軸
心が固定部材の軸部の中心に対して第１厚肉部側に偏心
することが防止され、互いに対向する第１および第２厚
肉部によって回動部材のボス部に対する摺接面積が増大
し、回動部材のボス部に対する摩擦力が大きなものとな
る。According to the above-mentioned structure, according to the first aspect of the present invention,
A thickness bulging radially outward of the insert bearing in a remaining area of less than 180 ° in the circumferential direction of the insert bearing that discontinuously opposes the first thick portion in a predetermined area of less than 180 ° in the circumferential direction of the insert bearing. Since the thick second thick portion is provided, when the rotating member for reducing the diameter of the torsion coil spring is rotated in the opposite direction to the predetermined direction, between the shaft portion of the fixed member and the boss portion of the rotating member. The rotation axis of the boss portion of the rotation member is prevented from being eccentric to the first thick portion side with respect to the center of the shaft portion of the fixed member, and the rotation is performed by the first and second thick portions facing each other. The sliding area of the moving member with respect to the boss increases, and the frictional force of the rotating member with respect to the boss increases.

【００１３】しかも、各厚肉部が互いに不連続でかつイ
ンサートベアリングの周方向１８０°未満の領域に設け
られているので、捩りコイルばねによる回動部材の所定
方向への回動付勢時、ボス部の回動軸心は、互いの厚肉
部間に設けられた隙間方向に偏心可能となり、回動部材
の回動がスムーズに行われて、アーム部のロックが回避
される。In addition, since the thick portions are provided discontinuously and in a region of less than 180 ° in the circumferential direction of the insert bearing, when the rotating member is biased by the torsion coil spring to rotate in the predetermined direction, The rotation axis of the boss can be eccentric in the direction of the gap provided between the thick portions, so that the rotation of the rotation member is performed smoothly and the lock of the arm is avoided.

【００１４】また、請求項２記載の発明では、第２厚肉
部は、インサートベアリングの軸心方向略半分位置より
も軸部基端側の残る領域一側に段差状に設けられている
ので、回動部材の反所定方向への回動時、固定部材の軸
部と回動部材のボス部との間において、回動部材の回動
時における軸部基端側でのボス部の回動軸心の第１厚肉
部側への偏心が防止され、軸部基端側において互いに対
向する第１および第２厚肉部によって回動部材のボス部
に対する摺接面積が増大し、回動部材のボス部に対する
摩擦力が同様に大きなものとなる。According to the second aspect of the present invention, the second thick portion is provided in a step shape on one side of the remaining region on the base end side of the shaft from a position substantially halfway in the axial direction of the insert bearing. When the rotating member is turned in the opposite direction, the boss is turned between the shaft of the fixed member and the boss of the rotating member on the base end side of the shaft when the rotating member is turned. The eccentricity of the dynamic axis toward the first thick portion is prevented, and the first and second thick portions facing each other on the base end side of the shaft increase the sliding contact area of the rotating member with the boss portion, and The frictional force on the boss of the moving member is likewise large.

【００１５】しかも、各厚肉部が軸部基端側においての
み互いに不連続なインサートベアリングの周方向１８０
°未満の残る領域一側に設けられていることにより、回
動部材の所定方向への回動時、ボス部の回動軸心は、互
いの厚肉部間に設けられた隙間方向および軸部先端側に
おける第１厚肉部側に対して偏心可能となり、回動部材
の回動がよりスムーズに行われて、アーム部のロックが
確実に回避される。In addition, each of the thick portions is discontinuous only at the base end side of the shaft portion in the circumferential direction 180 of the insert bearing.
When the rotating member is rotated in a predetermined direction, the rotation axis of the boss portion is aligned with the gap direction and the shaft provided between the thick portions. The eccentricity with respect to the first thick portion on the part distal end side can be made eccentric, so that the rotation of the rotating member is performed more smoothly, and the locking of the arm portion is reliably avoided.

【００１６】また、請求項３記載の発明では、第１厚肉
部は、インサートベアリングの軸心方向略半分位置より
も軸部先端側の所定領域他側に段差状に設けられている
ので、軸部基端側の残る領域一側に設けた，軸部に対す
る対角線位置の第２厚肉部と相俟って、回動部材の反所
定方向への回動時におけるボス部の回動軸心の第１厚肉
部側への偏心が第２厚肉部により防止される一方、ボス
部の回動軸心の第２厚肉部側への偏心が第１厚肉部によ
り防止され、軸部に対して対角線位置にて互いに対向す
る第１および第２厚肉部によって回動部材のボス部に対
する摺接面積が効果的に増大し、回動部材のボス部に対
する摩擦力が同様に大きなものとなる。According to the third aspect of the present invention, the first thick portion is provided in a stepped shape on the other side of the predetermined region on the distal end side of the shaft portion with respect to a substantially half position in the axial center direction of the insert bearing. The rotation axis of the boss portion when the rotation member rotates in the opposite direction to the predetermined direction, in combination with the second thick portion provided diagonally to the shaft portion and provided on one side of the remaining area on the base end side of the shaft portion. While the eccentricity of the center toward the first thick portion is prevented by the second thick portion, the eccentricity of the rotation axis of the boss toward the second thick portion is prevented by the first thick portion, The first and second thick portions opposed to each other at the diagonal position with respect to the shaft portion effectively increase the sliding contact area of the rotating member with the boss portion, and similarly increase the frictional force of the rotating member with the boss portion. It will be big.

【００１７】しかも、各厚肉部が軸部に対する対角線位
置にて互いに対向することにより、回動部材の所定方向
への回動時におけるボス部の回動軸心は、互いの厚肉部
間に設けられた隙間方向、軸部先端側における第１厚肉
部側および軸部基端側における第２厚肉部側に対して偏
心可能となり、回動部材の回動がさらにスムーズに行わ
れて、アーム部のロックが確実に回避される。Further, since the thick portions oppose each other at diagonal positions with respect to the shaft portion, the pivot axis of the boss portion when the pivot member rotates in the predetermined direction is between the thick portions. Eccentricity with respect to the gap direction provided on the shaft portion, the first thick portion side on the shaft tip side and the second thick portion side on the shaft base end side, and the rotation of the rotating member is performed more smoothly. Thus, the locking of the arm portion is reliably avoided.

【００１８】さらに、請求項４記載の発明では、第１厚
肉部の径方向への肉厚および第２厚肉部の径方向への肉
厚が互いに略一致せしめられているので、第１および第
２厚肉部の回動部材のボス部に対する摩擦力が均一なも
のとなる。Further, in the invention according to claim 4, the radial thickness of the first thick portion and the radial thickness of the second thick portion substantially match each other. In addition, the frictional force of the rotating member of the second thick portion against the boss becomes uniform.

【００１９】[0019]

【実施例】以下、この発明の実施例を図面に基づいて説
明する。図１及び図２はこの実施例に係るオートテンシ
ョナを示し、該オートテンショナは、例えば自動車エン
ジン等の固定体に固定可能なアルミ合金等の金属からな
る固定部材１と、該固定部材１に組み付けられて回動可
能に支持された金属製の回動部材２と、上記固定部材１
と回動部材２との間に縮装され、該回動部材２を固定部
材１に対し所定方向に回動付勢する捩りコイルばね３と
を備えている。Embodiments of the present invention will be described below with reference to the drawings. FIGS. 1 and 2 show an auto-tensioner according to this embodiment. The auto-tensioner is, for example, a fixing member 1 made of a metal such as an aluminum alloy that can be fixed to a fixed body such as an automobile engine, and assembled to the fixing member 1. A metal turning member 2 rotatably supported and fixed,
And a torsion coil spring 3 which is contracted between the rotating member 2 and the rotating member 2 and biases the rotating member 2 to rotate in a predetermined direction with respect to the fixed member 1.

【００２０】上記固定部材１は、フロント側（図１の上
側）が開口された有底円筒状のリヤカップ部１ａと、該
リヤカップ部１ａの底部中央から軸心ｍ方向に延びる軸
部４とを有し、図外の取付部において固定体に固定する
ようになされている。また、上記リヤカップ部１ａの周
壁部には、該周壁部を半径方向に貫通する基端側係止孔
５が形成されている。The fixing member 1 has a bottomed cylindrical rear cup portion 1a having an open front side (upper side in FIG. 1), and a shaft portion 4 extending in the direction of the axis m from the center of the bottom of the rear cup portion 1a. And is fixed to a fixed body at a mounting portion (not shown). In the peripheral wall of the rear cup portion 1a, a proximal locking hole 5 penetrating the peripheral wall in the radial direction is formed.

【００２１】上記回動部材２は、開口部が上記リヤカッ
プ部１ａの開口部と対向するフロントカップ部２ａと、
該フロントカップ部２ａの底部中央から軸心ｍ方向に延
び、かつ固定部材１の軸部４にその先端側から円筒状の
ダンピング部材であるインサートベアリング６を介して
外嵌合されるボス部７と、上記フロントカップ部２ａの
外周に半径方向外方に向けて突設され、先端にボス部７
の軸心ｍと平行な軸心ｎでプーリ８が回転自在に支持さ
れたアーム部９とを有する。該回動部材２はボス部７に
おいて固定部材１に回動可能に支持され、かつ固定部材
１の軸部４先端において合成樹脂製のスラストワッシャ
１０及び金属製のフロントプレート１１を介して図示し
ない抜止め手段により抜止めがなされている。そして、
上記プーリ８には、例えば、自動車エンジンにおける補
機類駆動用のＶベルト等のような所定の張力を付与すべ
きベルトｔが図２に仮想線で示すように巻き掛けられ
る。また、上記フロントカップ部２ａの周壁部には、該
周壁部を半径方向に貫通する先端側係止孔１２が形成さ
れている。The rotating member 2 has a front cup 2a having an opening facing the opening of the rear cup 1a,
A boss portion 7 extending in the direction of the axis m from the center of the bottom of the front cup portion 2a and externally fitted to the shaft portion 4 of the fixing member 1 from the tip side via an insert bearing 6 which is a cylindrical damping member. And a boss 7 projecting radially outward from the outer periphery of the front cup 2a.
And an arm 9 on which a pulley 8 is rotatably supported with an axis n parallel to the axis m of the pulley 8. The rotating member 2 is rotatably supported by the fixed member 1 at the boss portion 7, and is not shown via a synthetic resin thrust washer 10 and a metal front plate 11 at the tip of the shaft portion 4 of the fixed member 1. The retaining is performed by retaining means. And
A belt t to be given a predetermined tension, such as a V-belt for driving accessories in an automobile engine, is wound around the pulley 8 as shown by a virtual line in FIG. Further, a front end side locking hole 12 penetrating in a radial direction through the peripheral wall portion is formed in the peripheral wall portion of the front cup portion 2a.

【００２２】上記捩りコイルばね３は、本体が左巻き
で、基端側及び先端側の各端部３ａ，３ｂが何れも本体
から半径方向外方に向けて突出する形状とされている。
上記基端側端部３ａは固定部材１のリヤカップ部１ａ周
壁部における基端側係止孔５に、また先端側端部３ｂは
回動部材２のフロントカップ部２ａ周壁部における先端
側係止孔１２にそれぞれ半径方向に貫通して係止されて
おり、このことで、各端部３ａ，３ｂは周方向の移動が
規制されている。そして、該両端部３ａ，３ｂが係止さ
れた状態で本体が拡径する方向に動作することにより、
回動部材２を図２の反時計回り方向に回動付勢するよう
になされている。The main body of the torsion coil spring 3 is left-handed, and both the end portions 3a and 3b on the base end side and the front end side protrude radially outward from the main body.
The base end 3a is fixed to the base locking hole 5 in the peripheral wall of the rear cup 1a of the fixing member 1, and the distal end 3b is fixed to the front cup 2a of the rotating member 2 in the peripheral wall. Each of the ends 3a and 3b is restricted from moving in the circumferential direction by being respectively penetrated and locked in the holes 12 in the radial direction. By operating in the direction in which the main body expands in a state where the both ends 3a and 3b are locked,
The rotating member 2 is biased to rotate in the counterclockwise direction in FIG.

【００２３】上記インサートベアリング６の内外周面は
共に先端側が僅かながら小径となる断面テーパ状に形成
されており、これに応じて、軸部４の外周面及びボス部
７の内周面も共に同様の断面テーパ状をなしている。ま
た、インサートベアリング６は図外の回り止め手段によ
り固定部材１の軸部４側に回り止めされている。Each of the inner and outer peripheral surfaces of the insert bearing 6 is formed in a tapered cross-section having a small diameter at the tip end, and accordingly, the outer peripheral surface of the shaft portion 4 and the inner peripheral surface of the boss portion 7 are also formed. It has a similar tapered cross section. The insert bearing 6 is prevented from rotating toward the shaft portion 4 of the fixing member 1 by a rotation preventing means (not shown).

【００２４】さらに、上記捩りコイルばね３の基端側と
ボス部７との間には、ダンピング部材である円筒状のス
プリングサポート１３が介装されている。このスプリン
グサポート１３の内周面はボス部７の外周面に摺接可能
とされている。さらに、スプリングサポート１３の基端
側開口縁には、リヤカップ部１ａの底部表面に接する外
向きフランジ１３ａが形成されている。そして、外向き
フランジ１３ａが捩りコイルばね３の軸心方向の押圧力
でリヤカップ部１ａの底部表面に押し付けられることに
より、スプリングサポート１３は固定部材１側に固定さ
れている。また、この固定状態においてフロントカップ
部２ａが図２の時計回り方向に回動したとき、捩りコイ
ルばね３の本体が縮径することで、スプリングサポート
１３は締め付けられてその内周面がボス部７の外周面に
圧接するようになり、このことで、回動部材２の回動に
対するダンピング力が発生するようになされている。Further, a cylindrical spring support 13 as a damping member is interposed between the base end of the torsion coil spring 3 and the boss 7. The inner peripheral surface of the spring support 13 can slide on the outer peripheral surface of the boss 7. Further, an outward flange 13a that is in contact with the bottom surface of the rear cup portion 1a is formed at the base opening edge of the spring support 13. The outward flange 13a is pressed against the bottom surface of the rear cup portion 1a by the axial pressing force of the torsion coil spring 3, so that the spring support 13 is fixed to the fixing member 1 side. When the front cup portion 2a rotates clockwise in FIG. 2 in this fixed state, the body of the torsion coil spring 3 is reduced in diameter, so that the spring support 13 is tightened and the inner peripheral surface thereof becomes a boss portion. 7 comes into pressure contact with the outer peripheral surface of the rotary member 7, thereby generating a damping force with respect to the rotation of the rotation member 2.

【００２５】ここで、オートテンショナの作用について
説明するが、プーリ８にベルトｔが巻き掛けられた状態
でのオートテンショナの作動について説明するが、オー
トテンショナにおけるインサートベアリング６と回動部
材２のボス部７内周面及びスプリングサポート１３内周
面とボス部７外周面との各間では、それぞれベルト力と
捩りコイルばね３の付勢力とが合わさってダンピング力
が生じるようになり、この状態で上記ベルトｔの張力が
減少すると、ベルト力の減少によりダンピング力が小さ
くなる。すると、回動部材２が回動し易くなってプーリ
８のベルトｔに対する追随性が高くなり、このことで、
ベルトｔの張力低下が速やかに防止されることになる。Here, the operation of the auto tensioner will be described. The operation of the auto tensioner with the belt t wound around the pulley 8 will be described. The insert bearing 6 and the boss of the rotating member 2 in the auto tensioner will be described. Between the inner peripheral surface of the portion 7 and the inner peripheral surface of the spring support 13 and the outer peripheral surface of the boss portion 7, the belt force and the urging force of the torsion coil spring 3 are combined to generate a damping force. When the tension of the belt t decreases, the damping force decreases due to the decrease in the belt force. Then, the rotating member 2 is easily rotated, and the followability of the pulley 8 with respect to the belt t is increased.
The decrease in the tension of the belt t is quickly prevented.

【００２６】一方、ベルトｔの張りに対してはベルト力
の増大により上記ダンピング力も大きくなり、このこと
で、プーリ８に大きい抵抗力を付与してベルトｔのばた
つきが防止されることになる。On the other hand, with respect to the tension of the belt t, the above-mentioned damping force also increases due to the increase of the belt force, and this gives a large resistance to the pulley 8 to prevent the belt t from fluttering.

【００２７】そして、本発明の特徴部分として、図３お
よび図４にも示すように、上記インサートベアリング６
の周方向１８０°未満の所定領域Ａ（例えば１５０°程
度）には、インサートベアリング６の周方向１８０°以
上の残る領域Ｂ（例えば２４０°程度）の径方向への肉
厚に比して径方向外方へ略２倍程度厚肉な第１厚肉部３
１が設けられている。該第１厚肉部３１は、インサート
ベアリング６の軸心ｍ方向全長に亘って設けられてい
る。また、上記インサートベアリング６の軸心ｍ方向略
半分位置よりも軸部４基端側（図では下側）に位置する
残る領域Ｂの大径側（他側）には、インサートベアリン
グ６の径方向外方へ段差状に膨出する厚肉な第２厚肉部
３２が設けられている。該第２厚肉部３２は、上記所定
領域Ａの第１厚肉部３１に対して不連続に対向するイン
サートベアリング６の周方向１８０°未満の残る領域Ｂ
に設けられていて、上記第１厚肉部３１と略一致する肉
厚に形成されている。そして、第２厚肉部３２は、残る
領域Ｂの中央位置において第１厚肉部３１に対してボス
部７の軸心ｍを挾んで対向するよう，周方向両側部に例
えば３０°程度の隙間３３，３３を存して略１５０°の
範囲で膨出形成されてなる。この場合、第１厚肉部３１
および第２厚肉部３２のインサートベアリング６の周方
向１８０°未満の領域の設定は、ベルトｔ側から捩りコ
イルばね３に作用する捩りコイルばね３の捩じりトルク
と、捩りコイルばね３の縮径方向への変形によりインサ
ートベアリング６とボス部７との間で生じる摩擦力とに
基づいて適宜変更されるようにしている。As a characteristic part of the present invention, as shown in FIG. 3 and FIG.
In a predetermined area A (for example, about 150 °) of less than 180 ° in the circumferential direction, the diameter of the insert bearing 6 is larger than a radial thickness of a remaining area B (for example, about 240 °) of 180 ° or more in the circumferential direction. First thick portion 3 that is approximately twice as thick outward in the direction
1 is provided. The first thick portion 31 is provided over the entire length of the insert bearing 6 in the axial center m direction. In addition, the diameter of the insert bearing 6 is located on the large-diameter side (other side) of the remaining region B located on the base end side (lower side in the figure) of the shaft portion 4 than the substantially half position in the axial center m direction of the insert bearing 6. A thick second thick portion 32 bulging outward in the direction of a step is provided. The second thick portion 32 has a remaining region B of less than 180 ° in the circumferential direction of the insert bearing 6 discontinuously opposed to the first thick portion 31 in the predetermined region A.
And is formed to have a thickness substantially matching the first thick portion 31. The second thick portion 32 is, for example, about 30 ° on both sides in the circumferential direction so that the second thick portion 32 is opposed to the first thick portion 31 with the axis m of the boss portion 7 interposed therebetween at the center position of the remaining region B. The bulge is formed in a range of about 150 ° with the gaps 33 and 33 therebetween. In this case, the first thick portion 31
The setting of the region of the second thick portion 32 of less than 180 ° in the circumferential direction of the insert bearing 6 is performed by setting the torsional torque of the torsion coil spring 3 acting on the torsion coil spring 3 from the belt t side and the torsion coil spring 3 It is appropriately changed based on the frictional force generated between the insert bearing 6 and the boss portion 7 due to the deformation in the diameter reducing direction.

【００２８】したがって、上記実施例では、インサート
ベアリング６の周方向１８０°未満の所定領域Ａの第１
厚肉部３１に対して隙間３３，３３を存して不連続に対
向する，インサートベアリング６の軸心方向略半分位置
よりも軸部４基端側の残る領域Ｂの大径側に径方向外方
へ段差状に膨出する厚肉な第２厚肉部３２が設けられて
いるので、固定部材１の軸部４と回動部材２のボス部７
との間において、捩りコイルばね３の本体を縮径させる
回動部材の時計方向回りへの回動時、回動部材２の回動
時における軸部４基端側でのボス部７の回動軸心ｍの第
１厚肉部３１側への偏心が防止され、軸部４基端側にお
いて互いに対向する第１および第２厚肉部３１，３２に
よって回動部材２のボス部７に対する摺接面積が増大し
て回動部材２のボス部７に対する摩擦力が大きなものと
なり、大きなダンピング力を得ることができる。Therefore, in the above embodiment, the first region A of the predetermined region A of less than 180 ° in the circumferential direction of the insert bearing 6 is formed.
Radially in the large-diameter side of the remaining region B on the base end side of the shaft portion 4 from a position approximately halfway in the axial center direction of the insert bearing 6, which discontinuously opposes the thick portion 31 with the gaps 33, 33 therebetween. Since the thick second thick portion 32 bulging outward in a stepped manner is provided, the shaft portion 4 of the fixed member 1 and the boss portion 7 of the rotating member 2 are provided.
Between the clockwise rotation of the rotating member for reducing the diameter of the body of the torsion coil spring 3 and the rotation of the boss 7 on the base end side of the shaft portion 4 during the rotation of the rotating member 2. The eccentricity of the dynamic axis m toward the first thick portion 31 is prevented, and the first and second thick portions 31 and 32 opposed to each other on the base end side of the shaft portion 4 allow the rotating member 2 to move relative to the boss portion 7. As the sliding contact area increases, the frictional force of the rotating member 2 against the boss 7 increases, and a large damping force can be obtained.

【００２９】しかも、各厚肉部３１，３２が軸部４基端
側においてのみ隙間３３，３３により互いに不連続なイ
ンサートベアリング６の周方向１８０°未満の残る領域
Ｂの大径側に設けられていることにより、捩りコイルば
ね３の本体を拡径させる回動部材の反時計方向回りへの
回動時におけるボス部７の回動軸心ｍは、互いの厚肉部
３１，３２間に設けられた隙間３３，３３方向および軸
部４先端側における第１厚肉部３１側に対して偏心可能
となり、回動部材２の回動がスムーズに行われて、アー
ム部９のロックを確実に回避することができる。Moreover, the thick portions 31, 32 are provided only on the base end side of the shaft portion 4 by the gaps 33, 33 on the large diameter side of the region B remaining less than 180 ° in the circumferential direction of the insert bearing 6, which is discontinuous with each other. As a result, the rotation axis m of the boss portion 7 when the rotation member for expanding the diameter of the body of the torsion coil spring 3 rotates counterclockwise is located between the thick portions 31 and 32 of each other. The eccentricity can be provided with respect to the gaps 33 provided in the direction of the first thick portion 31 in the direction of the gap 33 and the tip end side of the shaft portion 4. Can be avoided.

【００３０】また、第１厚肉部３１の径方向への肉厚お
よび第２厚肉部３２の径方向への肉厚が互いに略一致せ
しめられているとともに、インサートベアリング６の周
方向における互いの厚肉部３１，３２の領域が略一致し
ているので、第１および第２厚肉部３１，３２の回動部
材２のボス部７に対する摩擦力を均一にして、各厚肉部
３１，３２の耐摩耗性の向上を図ることもできる。The radial thickness of the first thick portion 31 and the radial thickness of the second thick portion 32 are substantially equal to each other, and the thickness of the insert bearing 6 in the circumferential direction is substantially the same. Since the regions of the thick portions 31 and 32 substantially coincide with each other, the frictional force of the first and second thick portions 31 and 32 with respect to the boss 7 of the rotating member 2 is made uniform, and each thick portion 31 , 32 can be improved.

【００３１】尚、本発明は上記実施例に限定されるもの
ではなく、その他種々の変形例を包含するものである。
例えば、上記実施例では、第１厚肉部３１をインサート
ベアリング６の軸心ｍ方向全長に亘って設けたが、図５
に示すように、第１厚肉部４１が、インサートベアリン
グ６の軸心方向略半分位置よりも軸部先端側（図では上
側）に位置する所定領域Ａの小径側に段差状に設けられ
るようにしても良い。この場合には、インサートベアリ
ングの軸心方向略半分位置よりも軸部先端側に設けた所
定領域他側の第１厚肉部４１と、軸部基端側の残る領域
一側に設けた，軸部に対する対角線位置の第２厚肉部３
２とによって、回動部材の時計方向回りの回動時におけ
るボス部の回動軸心の第１厚肉部４１側への偏心が第２
厚肉部３２により防止される一方、ボス部の回動軸心の
第２厚肉部３２側への偏心が第１厚肉部４１により防止
され、軸部に対して対角線位置にて互いに対向する第１
および第２厚肉部４１，３２によって回動部材のボス部
に対する摺接面積が効果的に増大し、回動部材のボス部
に対する摩擦力が同様に大きなものとなる。しかも、各
厚肉部４１，３２が軸部に対する対角線位置にて互いに
対向することにより、回動部材の反時計方向回りの回動
時におけるボス部７の回動軸心は、互いの厚肉部４１，
３２間に設けられた隙間３３，３３方向、軸部先端側に
おける第１厚肉部４１側および軸部基端側における第２
厚肉部３２側に対して偏心可能となり、回動部材の回動
がさらにスムーズに行われてアーム部９のロックが確実
に回避されることになる。It should be noted that the present invention is not limited to the above-described embodiment, but includes various other modifications.
For example, in the above embodiment, the first thick portion 31 is provided over the entire length of the insert bearing 6 in the axial center m direction.
As shown in FIG. 5, the first thick portion 41 is provided in a stepped manner on the small diameter side of the predetermined area A located on the distal end side (upper side in the figure) of the shaft portion with respect to the substantially half position in the axial center direction of the insert bearing 6. You may do it. In this case, the first thick portion 41 on the other side of the predetermined region provided on the distal end side of the shaft portion with respect to the substantially half position in the axial direction of the insert bearing, and the remaining region on one side of the base end side of the shaft portion are provided. 2nd thick part 3 of a diagonal position to a shaft part
2, the eccentricity of the rotation axis of the boss toward the first thick portion 41 when the rotation member rotates clockwise is set to the second position.
While being prevented by the thick portion 32, the eccentricity of the rotation axis of the boss portion toward the second thick portion 32 is prevented by the first thick portion 41, and is opposed to the shaft portion at a diagonal position. First
The second thick portions 41 and 32 effectively increase the sliding contact area of the rotating member with respect to the boss portion, and similarly increase the frictional force of the rotating member with respect to the boss portion. In addition, since the thick portions 41 and 32 face each other at a diagonal position with respect to the shaft portion, the rotation axis of the boss 7 when the rotation member rotates counterclockwise becomes thicker. Part 41,
32, the first thick portion 41 on the distal end side of the shaft portion and the second on the proximal end side of the shaft portion.
The eccentricity can be achieved with respect to the thick portion 32 side, and the rotation of the rotation member is performed more smoothly, so that the lock of the arm portion 9 is reliably avoided.

【００３２】また、上記実施例では、第２厚肉部３２を
軸部基端側の残る領域Ｂの大径側に設けたが、第１厚肉
部がインサートベアリングの軸心方向全長に亘って設け
られるようにしても良く、この場合には、回動部材の時
計方向回りの回動時にボス部の回動軸心が固定部材の軸
部の中心に対して第１厚肉部側に偏心することが防止さ
れ、互いに対向する第１および第２厚肉部によって回動
部材のボス部に対する摺接面積が増大し、回動部材のボ
ス部に対する摩擦力が大きなものとなる。一方、回動部
材の反時計方向回りの回動時にボス部の回動軸心が互い
の厚肉部間の隙間に対して偏心可能となり、回動部材の
回動がスムーズに行われてアーム部のロックが確実に回
避されることになる。In the above embodiment, the second thick portion 32 is provided on the large diameter side of the remaining area B on the base end side of the shaft portion. However, the first thick portion extends over the entire length of the insert bearing in the axial center direction. In this case, when the rotating member rotates clockwise, the rotation axis of the boss portion is positioned on the first thick portion side with respect to the center of the shaft portion of the fixed member. The eccentricity is prevented, and the first and second thick portions opposing each other increase the sliding contact area of the rotating member with the boss portion, thereby increasing the frictional force of the rotating member with respect to the boss portion. On the other hand, when the rotation member rotates counterclockwise, the rotation axis of the boss portion can be decentered with respect to the gap between the thick portions, and the rotation of the rotation member is performed smoothly. Locking of the part is reliably avoided.

【００３３】[0033]

【発明の効果】以上の如く、請求項１記載の発明におけ
るオートテンショナによれば、インサートベアリングの
所定領域の第１厚肉部に対して不連続に対向する厚肉な
第２厚肉部を残る領域に設けたので、回動部材の所定方
向回りの回動時にボス部の回動軸心を隙間に対してのみ
偏心可能にしてアーム部のロックを回避しつつ、回動部
材の反所定方向回りの回動時のボス部に対する摺接面積
の増大により摩擦力を大きくして大きなダンピング力を
得ることができる。As described above, according to the auto-tensioner according to the first aspect of the present invention, the thick second thick portion that discontinuously opposes the first thick portion in the predetermined region of the insert bearing is formed. Since it is provided in the remaining area, the rotation axis of the boss can be decentered only with respect to the gap when the rotation member rotates around the predetermined direction, thereby avoiding locking of the arm portion and preventing the rotation member from rotating. The frictional force is increased by increasing the area of sliding contact with the boss during rotation around the direction, so that a large damping force can be obtained.

【００３４】また、請求項２記載の発明におけるオート
テンショナによれば、インサートベアリングの軸部基端
側の残る領域一側に第２厚肉部を段差状に設けたので、
回動部材の所定方向回りの回動時にボス部の回動軸心を
隙間方向および軸部先端側の第１厚肉部側に偏心させて
アーム部のロックをより確実に回避しつつ、回動部材の
反所定方向回りの回動時のボス部に対する大きな摩擦力
によって大きなダンピング力を得ることができる。According to the auto tensioner of the second aspect of the present invention, the second thick portion is provided in a step shape on one side of the remaining region on the base end side of the shaft portion of the insert bearing.
When the rotation member rotates around a predetermined direction, the rotation axis of the boss portion is eccentric to the gap direction and the first thick portion side on the tip end side of the shaft portion to more reliably avoid locking of the arm portion, and A large damping force can be obtained by a large frictional force with respect to the boss when the moving member rotates around the predetermined direction.

【００３５】また、請求項３記載の発明におけるオート
テンショナによれば、インサートベアリングの軸部先端
側の所定領域他側に第１厚肉部を段差状に設けたので、
回動部材の所定方向回りの回動時にボス部の回動軸心を
隙間、軸部先端側の第１厚肉部側および軸部基端側の第
２厚肉部側に偏心させてアーム部のロックをさらに確実
に回避しつつ、軸部に対する対角線位置の第２厚肉部と
相俟って回動部材の反所定方向回りの回動時のボス部に
対する摺接面積を効果的に増大させて大きなダンピング
力を得ることができる。According to the third aspect of the present invention, since the first thick portion is provided stepwise on the other side of the predetermined region on the distal end side of the shaft portion of the insert bearing,
When the rotation member rotates about a predetermined direction, the rotation axis of the boss portion is eccentric to the gap, the first thick portion side on the distal end side of the shaft portion, and the second thick portion side on the base end side of the shaft portion. In addition to avoiding the locking of the part more reliably, the sliding contact area with the boss part at the time of rotation of the rotating member about the opposite predetermined direction can be effectively achieved in combination with the second thick part at the diagonal position with respect to the shaft part. Increased damping force can be obtained.

【００３６】さらに、請求項４記載の発明におけるオー
トテンショナによれば、第１および第２厚肉部の径方向
への肉厚を互いに略一致させたので、第１および第２厚
肉部のボス部に対する摩擦力を均一にして、各厚肉部の
耐摩耗性の向上を図ることができる。Further, according to the auto-tensioner according to the fourth aspect of the present invention, since the thicknesses of the first and second thick portions in the radial direction are substantially equal to each other, the first and second thick portions have the same thickness. By making the frictional force to the boss portion uniform, the wear resistance of each thick portion can be improved.

【図面の簡単な説明】[Brief description of the drawings]

【図１】図２のＩ−Ｉ線における縦断側面図である。FIG. 1 is a vertical sectional side view taken along line II of FIG. 2;

【図２】実施例に係るオートテンショナの平面図であ
る。FIG. 2 is a plan view of the auto tensioner according to the embodiment.

【図３】実施例に係るインサートベアリングの斜視図で
ある。FIG. 3 is a perspective view of the insert bearing according to the embodiment.

【図４】実施例に係るインサートベアリングの平面図で
ある。FIG. 4 is a plan view of the insert bearing according to the embodiment.

【図５】変形例に係る図３相当図である。FIG. 5 is a diagram corresponding to FIG. 3 according to a modification.

【図６】従来例に係る図１相当図である。FIG. 6 is a diagram corresponding to FIG. 1 according to a conventional example.

【符号の説明】 １ 固定部材 ２ 回動部材 ３ 捩りコイルばね ４ 軸部 ６ インサートベアリング（ダンピング部材） ７ ボス部 ８ プーリ ３１，４１ 第１厚肉部 ３２ 第２厚肉部 Ａ 所定領域 Ｂ 残る領域 ｍ ボス部の軸心 ｎ プーリの軸心 ｔ ベルト[Description of Signs] 1 Fixed member 2 Rotating member 3 Torsional coil spring 4 Shaft 6 Insert bearing (damping member) 7 Boss 8 Pulley 31, 41 First thick portion 32 Second thick portion A Predetermined area B Remains Area m Shaft center of boss n Shaft center of pulley t Belt

───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F16H 7/00 - 7/24 ──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. 7 , DB name) F16H 7/ 00-7/24

Claims (4)

(57)【特許請求の範囲】(57) [Claims] 【請求項１】 軸部を有し、固定体に固定可能な固定部
材と、 上記固定部材の軸部にボス部が回動可能に外嵌合され、
該回動軸心と平行な軸心周りに回転可能なプーリを有す
る回動部材と、 上記固定部材及び回動部材の間に縮装されて該回動部材
を固定部材に対し所定方向に回動付勢する捩りコイルば
ねと、 上記固定部材及び回動部材の間に介装されて該回動部材
の回動をダンピングするためのダンピング部材とを備
え、 上記回動部材の回動付勢力により上記プーリにベルトを
押圧させて所定の張力を付与し、かつ上記張力の変動に
応じてダンピング力を変化させるようにしたオートテン
ショナであって、 上記ダンピング部材は、上記固定部材の軸部と、上記回
動部材のボス部との間に介装されて該回動部材の回動時
に該ボス部の内周面との間でベルト張力の変動に応じた
摩擦力を発生する略筒形状のインサートベアリングより
なり、 上記インサートベアリングの周方向１８０°未満の所定
領域には、インサートベアリングの周方向１８０°以上
の残る領域の径方向への肉厚に比して径方向外方へ厚肉
な第１厚肉部が設けられているとともに、 上記所定領域の第１厚肉部に対して不連続に対向するイ
ンサートベアリングの周方向１８０°未満の残る領域に
は、インサートベアリングの径方向外方へ膨出する厚肉
な第２厚肉部が設けられていることを特徴とするオート
テンショナ。A fixing member having a shaft portion, the boss portion being rotatably externally fitted to the shaft portion of the fixing member;
A rotation member having a pulley rotatable about an axis parallel to the rotation axis; and a rotation member which is contracted between the fixed member and the rotation member to rotate the rotation member in a predetermined direction with respect to the fixed member. A torsion coil spring that is urged to move, and a damping member interposed between the fixed member and the rotating member for damping the rotation of the rotating member. An auto-tensioner configured to apply a predetermined tension by pressing a belt to the pulley, and to change a damping force in accordance with a change in the tension, wherein the damping member includes a shaft portion of the fixing member and A substantially cylindrical shape interposed between the boss portion of the rotating member and a frictional force generated between the boss portion and the inner peripheral surface of the boss portion according to a change in belt tension when the rotating member rotates. Of the above insert bearing A first thick portion that is thicker radially outward than a radially thicker portion of the remaining region of the insert bearing that is more than 180 ° in the circumferential direction is provided in a predetermined region less than 180 ° in the circumferential direction of the bearing. In the remaining region of the insert bearing that is less than 180 ° in the circumferential direction and discontinuously opposes the first thick portion in the predetermined region, a thick wall swelling radially outward of the insert bearing is provided. An auto-tensioner comprising a second thick portion. 【請求項２】 第２厚肉部は、インサートベアリングの
軸心方向略半分位置よりも軸部基端側に位置する残る領
域他側に段差状に設けられていることを特徴とする請求
項１記載のオートテンショナ。2. The method according to claim 1, wherein the second thick portion is provided in a stepped shape on the other side of the remaining region located on the base end side of the shaft portion with respect to the substantially half position in the axial center direction of the insert bearing. Auto tensioner according to 1. 【請求項３】 第１厚肉部は、インサートベアリングの
軸心方向略半分位置よりも軸部先端側に位置する所定領
域他側に段差状に設けられていることを特徴とする請求
項２記載のオートテンショナ。3. The first thick portion is provided in a stepped shape on the other side of a predetermined region located on the distal end side of the shaft portion with respect to a substantially half position in the axial center direction of the insert bearing. Auto tensioner as described. 【請求項４】 第１厚肉部の径方向への肉厚および第２
厚肉部の径方向への肉厚は、互いに略一致していること
を特徴とする請求項１、請求項２または請求項３記載の
オートテンショナ。4. A radial thickness of the first thick portion and a second thick portion.
4. The auto-tensioner according to claim 1, wherein the thickness of the thick portion in the radial direction is substantially equal to each other.
JP24897893A 1993-10-05 1993-10-05 Auto tensioner Expired - Fee Related JP3195867B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP24897893A JP3195867B2 (en) 1993-10-05 1993-10-05 Auto tensioner

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP24897893A JP3195867B2 (en) 1993-10-05 1993-10-05 Auto tensioner

Publications (2)

Publication Number Publication Date
JPH07103297A JPH07103297A (en) 1995-04-18
JP3195867B2 true JP3195867B2 (en) 2001-08-06

Family

ID=17186217

Family Applications (1)

Application Number Title Priority Date Filing Date
JP24897893A Expired - Fee Related JP3195867B2 (en) 1993-10-05 1993-10-05 Auto tensioner

Country Status (1)

Country Link
JP (1) JP3195867B2 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITTO20131032A1 (en) * 2013-12-17 2015-06-18 Dayco Europe Srl TENSIONER FOR A BELT DRIVE

Also Published As

Publication number Publication date
JPH07103297A (en) 1995-04-18

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