JPH10252857A - Power transmitting device - Google Patents
Power transmitting deviceInfo
- Publication number
- JPH10252857A JPH10252857A JP9060947A JP6094797A JPH10252857A JP H10252857 A JPH10252857 A JP H10252857A JP 9060947 A JP9060947 A JP 9060947A JP 6094797 A JP6094797 A JP 6094797A JP H10252857 A JPH10252857 A JP H10252857A
- Authority
- JP
- Japan
- Prior art keywords
- driven
- rotating member
- tooth profile
- side rotating
- power transmission
- 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.)
- Pending
Links
Landscapes
- Transmission Devices (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は過負荷時のトルクリ
ミッターとしての機能を備えた動力伝達装置に関するも
ので、自動車用空調装置の冷凍サイクルの圧縮機駆動用
動力伝達装置として好適なものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device having a function as a torque limiter at the time of overload, and is suitable as a power transmission device for driving a compressor of a refrigeration cycle of an automotive air conditioner. .
【０００２】[0002]
【従来の技術】従来、自動車用空調装置における圧縮機
として、０容量付近まで容量を変化させることができる
可変容量圧縮機を用いる場合には、冷凍サイクルの能力
制御のために、圧縮機を断続作動させる必要がなくな
る。従って、このような可変容量圧縮機を用いるもので
は、エンジンから圧縮機への動力伝達を断続するための
クラッチ機構が不要となる。2. Description of the Related Art Conventionally, when a variable displacement compressor capable of changing its capacity to near zero capacity is used as a compressor in an automotive air conditioner, the compressor is intermittently controlled for controlling the capacity of a refrigeration cycle. There is no need to operate. Therefore, in the case of using such a variable displacement compressor, a clutch mechanism for interrupting the transmission of power from the engine to the compressor becomes unnecessary.
【０００３】一方、圧縮機の焼きつき故障等による圧縮
機ロック等の異常が発生した時には、圧縮機駆動機構の
ベルトに過大なトルクが加わり、ベルトが切損する事態
が起こる。特に、自動車の圧縮機駆動機構では、圧縮機
以外の種々な補機（バッテリ充電発電機、エンジン冷却
水用ウォータポンプ、パワーステアリング用油圧ポンプ
等）と共通のベルトにて、エンジンからの動力が伝達さ
れるようになっているので、駆動ベルトが一旦切損する
と、自動車の走行不能という重大な故障を引き起こすこ
とになる。On the other hand, when an abnormality such as compressor lock occurs due to a seizure failure of the compressor or the like, an excessive torque is applied to the belt of the compressor drive mechanism, and the belt may break. In particular, in a compressor drive mechanism of an automobile, power from the engine is transmitted through a belt common to various auxiliary devices other than the compressor (a battery charging generator, a water pump for engine cooling water, a hydraulic pump for power steering, etc.). As a result, once the drive belt is cut off, it will cause a serious failure that the vehicle cannot run.
【０００４】そこで、圧縮機ロック等の過負荷時に伝達
トルクが設定値以上に上昇すると、この伝達トルクの上
昇に対応して、圧縮機への動力伝達経路を遮断するトル
クリミッター機能を付加したものが特開平８−１５９０
２８号公報、特開平８−２１０２５０号公報にて提案さ
れている。これらの公報記載の従来技術は、ベルトが係
合され、エンジンの駆動力により回転するプーリに連結
された連結基板と、圧縮機回転軸に連結された駆動力受
承体とを所定間隔をおいて対向配置するとともに、プー
リ側の連結基板と、圧縮機側の駆動力受承体にそれぞれ
凹部を形成し、この連結基板の凹部と駆動力受承体の凹
部との間に転動ボールを配置するとともに、この連結基
板の凹部と駆動力受承体との間に、両者の間隔が狭くな
る方向に弾性手段のバネ力を作用させるようにしてい
る。Therefore, when the transmission torque rises above a set value during overload such as a compressor lock or the like, a torque limiter function for cutting off a power transmission path to the compressor is added in response to the increase in the transmission torque. Is disclosed in JP-A-8-1590
No. 28, and Japanese Patent Application Laid-Open No. 8-210250. In the prior art described in these publications, a belt is engaged and a connecting board connected to a pulley that is rotated by the driving force of an engine is connected to a driving force receiving body connected to a compressor rotating shaft at a predetermined interval. And a concave portion is formed in each of the connecting substrate on the pulley side and the driving force receiving member on the compressor side, and a rolling ball is provided between the concave portion of the connecting substrate and the concave portion of the driving force receiving member. In addition to the arrangement, the spring force of the elastic means is applied between the concave portion of the connection board and the driving force receiving body in a direction in which the distance between the two is reduced.
【０００５】そして、通常運転時は、両凹部の間に転動
ボールを収容した状態を保持することにより、この転動
ボールを介して、プーリ側の連結基板から圧縮機側の駆
動力受承体に動力が伝達されて圧縮機が作動する。一
方、圧縮機ロック等の過負荷時に伝達トルクが設定値以
上に上昇すると、上記弾性手段のバネ力に抗して、転動
ボールが上記両凹部のうち、いずれか一方の凹部から離
脱する。例えば、プーリ側の連結基板の凹部から転動ボ
ールが離脱する。すると、この転動ボールとプーリ側の
連結基板との係合状態が解除され、転動ボールに対して
プーリ側の連結基板が空回りするようになり、この結
果、圧縮機への動力伝達が遮断される。During normal operation, the state in which the rolling balls are accommodated between the two concave portions is maintained, so that the driving force on the compressor side is received from the connecting board on the pulley side via the rolling balls. Power is transmitted to the body and the compressor operates. On the other hand, if the transmission torque rises above the set value during overload of the compressor lock or the like, the rolling ball separates from one of the two recesses against the spring force of the elastic means. For example, the rolling ball separates from the concave portion of the connecting board on the pulley side. Then, the engagement state between the rolling ball and the connecting board on the pulley side is released, and the connecting board on the pulley side idles with respect to the rolling ball, and as a result, power transmission to the compressor is interrupted. Is done.
【０００６】[0006]
【発明が解決しようとする課題】ところで、上記従来技
術では、転動ボールの凹部内への収容保持状態と、転動
ボールの凹部内からの離脱状態とを切り替えることによ
り動力伝達の断続を行う構成であって、転動ボールが必
要不可欠な要素となっているが、この転動ボールは転動
自在な小体格の球形であるから、組付工程上、取扱いの
面倒なものである。そのため、圧縮機の動力伝達装置部
の組付工数の増加は不可避であり、製造コストが高くな
る。In the above-mentioned prior art, the power transmission is intermittently performed by switching between a state in which the rolling balls are accommodated and held in the recesses and a state in which the rolling balls are detached from the recesses. Although the rolling ball is an indispensable element in the configuration, the rolling ball is a small-sized sphere that can be rolled freely, so that it is troublesome to handle in the assembling process. Therefore, an increase in the number of steps for assembling the power transmission device of the compressor is inevitable, and the manufacturing cost is increased.
【０００７】また、動力伝達が転動ボールの線接触面を
介して行われ、動力伝達のための接触面積が小さいの
で、通常運転時における動力伝達の信頼性に欠ける。本
発明は上記点に鑑みてなされたもので、転動ボールを使
用しない組付性のよい構成で、通常運転時における動力
伝達の信頼性が高いとともに、過負荷時のトルクリミッ
ター機能を確実に発揮できる動力伝達装置を提供するこ
とを目的とする。Further, since power transmission is performed through the line contact surface of the rolling ball and the contact area for power transmission is small, the reliability of power transmission during normal operation is lacking. The present invention has been made in view of the above points, and has a structure with good assemblability that does not use rolling balls, has high reliability of power transmission during normal operation, and ensures a torque limiter function during overload. It is an object of the present invention to provide a power transmission device that can be used.
【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記載の発明では、駆動側回転部材（１、１
３、１４）に第１歯形部（１ｄ、１３ｂ）を設け、従動
側機器（３）の回転軸（５）に対して回転方向には回り
止めして、軸方向には移動可能に従動側回転部材（６）
を連結し、この従動側回転部材（６）に、第１歯形部
（１ｄ、１３ｂ）に噛み合うことができる第２歯形部
（６ｃ）を設け、従動側回転部材（６）にばね力を作用
させて第２歯形部（６ｃ）を第１歯形部（１ｄ、１３
ｂ）に押し付ける弾性手段（９）を備え、従動側機器
（３）の通常運転時には、弾性手段（９）のばね力によ
り第２歯形部（６ｃ）と第１歯形部（１ｄ、１３ｂ）と
の噛み合い状態を維持して、駆動側回転部材（１、１
３、１４）から従動側回転部材（６）に動力を伝達し、
一方、従動側機器（３）の過負荷時には、駆動側回転部
材（１、１３、１４）から従動側回転部材（６）を経て
弾性手段（９）に加わる軸方向荷重が所定値に到達する
と、弾性手段（９）の凹凸形状が反転して、第２歯形部
（６ｃ）が第１歯形部（１ｄ、１３ｂ）から離脱し、駆
動側回転部材（１、１３、１４）から従動側回転部材
（６）への動力伝達を遮断するようにしたことを特徴と
している。To achieve the above object, according to the first aspect of the present invention, a driving-side rotating member (1, 1) is provided.
3 and 14) are provided with first toothed portions (1d and 13b) to prevent rotation in the rotation direction with respect to the rotation axis (5) of the driven device (3) and to be movable in the axial direction on the driven side. Rotating member (6)
The driven side rotating member (6) is provided with a second toothed portion (6c) that can mesh with the first toothed portion (1d, 13b), and a spring force acts on the driven side rotating member (6). Then, the second tooth profile (6c) is moved to the first tooth profile (1d, 13).
b), the second gear part (6c) and the first gear part (1d, 13b) are formed by the spring force of the elastic means (9) during normal operation of the driven device (3). While maintaining the meshing state of the drive side rotating members (1, 1).
3, 14) to the driven side rotating member (6),
On the other hand, when the driven device (3) is overloaded, when the axial load applied to the elastic means (9) from the driving side rotating member (1, 13, 14) via the driven side rotating member (6) reaches a predetermined value. The uneven shape of the elastic means (9) is reversed, the second tooth part (6c) is separated from the first tooth part (1d, 13b), and the driven-side rotating member (1, 13, 14) rotates from the driven-side rotating member (1, 13, 14). Power transmission to the member (6) is shut off.
【０００９】これによると、従動側機器（３）の過負荷
時に弾性手段（９）の凹凸形状の反転により両歯形部の
噛み合い状態を解放して、トルクリミッター機能を発揮
しているから、予め設定した所定値において凹凸形状の
反転動作を行ってトルクリミッター機能を確実に発揮で
きる。しかも、従来技術のような転動ボールを使用しな
いため、動力伝達装置の組付け工数を減少でき、組付け
コストを低減できるとともに、通常運転時における動力
伝達を両歯形部における面接触部を通して確実に行うこ
とができ、転動ボールによる線接触の場合に比して、動
力伝達の信頼性を向上できる。According to this, when the driven device (3) is overloaded, the meshing state of the two tooth portions is released by reversing the uneven shape of the elastic means (9), and the torque limiter function is exhibited. The torque limiter function can be reliably performed by performing the inversion operation of the uneven shape at the set predetermined value. In addition, since rolling balls are not used as in the prior art, the man-hour for assembling the power transmission device can be reduced, the assembly cost can be reduced, and power transmission during normal operation can be reliably performed through the surface contact portions of the both tooth portions. The reliability of power transmission can be improved as compared with the case of line contact by rolling balls.
【００１０】特に、請求項２記載の発明では、駆動側回
転部材に、回転駆動源からの回転力がベルトを介して伝
達され回転するプーリ（１）と、このプーリ（１）の内
周側に間隔をおいて配置された円筒状のロータ（１３）
と、このプーリ（１）とロータ（１３）との間を一体に
連結する弾性変形可能なゴム部材（１４）とを備え、ロ
ータ（１３）に、その半径方向の内方に伸びる側壁部
（１３ａ）を形成し、この側壁部（１３ａ）に第１歯形
部（１３ｂ）を形成したことを特徴としている。In particular, according to the second aspect of the present invention, the pulley (1), which is rotated by transmitting the rotational force from the rotational drive source to the driving-side rotating member via the belt, and the inner peripheral side of the pulley (1). Cylindrical rotors (13) spaced apart from each other
And an elastically deformable rubber member (14) integrally connecting the pulley (1) and the rotor (13). The rotor (13) has a radially inwardly extending side wall ( 13a) and a first tooth profile (13b) formed on the side wall (13a).
【００１１】これによると、ゴム部材（１４）の弾性変
形により圧縮機等の従動側機器（３）のトルク変動を吸
収できる。従って、トルクリミッター機能とトルク変動
吸収機能とを両立させることができる。請求項４記載の
発明では、皿ばね（９）の内周部を保持する保持部材
（１０）を有し、この保持部材（１０）を回転軸（５）
にボルト（１１）によりねじ止め固定することを特徴と
している。According to this, it is possible to absorb the torque fluctuation of the driven device (3) such as a compressor by the elastic deformation of the rubber member (14). Therefore, it is possible to achieve both the torque limiter function and the torque fluctuation absorbing function. According to the fourth aspect of the present invention, there is provided a holding member (10) for holding the inner peripheral portion of the disc spring (9), and the holding member (10) is connected to the rotating shaft (5).
It is characterized in that it is screwed and fixed with bolts (11).
【００１２】これによると、保持部材（１０）のねじ止
め位置をボルト（１１）により調整することにより、皿
ばね（９）のばね力を容易に調整できる。請求項５記載
の発明では、回転駆動源からの回転力を受けて回転する
駆動側回転部材（１）に、第１歯形部（１ｄ）を設け、
従動側機器（３）の回転軸（５）に対して従動側回転部
材（６）を回り止めして連結し、第１歯形部（１ｄ）に
噛み合うことができる第２歯形部（１８ｂ）と、従動側
回転部材（６）との間を連結する弾性手段（１５、１
６）を備え、この弾性手段（１５、１６）により第２歯
形部（１８ｂ）にばね力を作用させることにより、第２
歯形部（１８ｂ）が第１歯形部（１ｄ）に押し付けられ
て第２歯形部（１８ｂ）と第１歯形部（１ｄ）とが噛み
合うようにし、従動側機器（３）の通常運転時には、弾
性手段（１５、１６）のばね力により第２歯形部（１８
ｂ）と第１歯形部（１ｄ）との噛み合い状態を維持し
て、駆動側回転部材（１）から弾性手段（１５、１６）
を介して従動側回転部材（６）に動力を伝達し、一方、
従動側機器（３）の過負荷時には、駆動側回転部材
（１）から両歯形部（１ｄ、１８ｂ）の噛み合い部を経
て弾性手段（１５、１６）に加わる軸方向荷重が所定値
に到達すると、弾性手段（１５、１６）の凹凸形状が反
転して、第２歯形部（１８ｂ）と第１歯形部（１ｄ）と
の噛み合い状態が解放され、駆動側回転部材（１）から
従動側回転部材（６）への動力伝達が遮断されるように
したことを特徴としている。According to this, the spring force of the disc spring (9) can be easily adjusted by adjusting the screwing position of the holding member (10) with the bolt (11). According to the fifth aspect of the present invention, the driving-side rotating member (1) that rotates by receiving the rotational force from the rotational driving source is provided with the first tooth profile (1d),
A second toothed portion (18b) which can be connected to the rotation shaft (5) of the driven side device (3) by preventing the driven side rotating member (6) from rotating and engaging with the first toothed portion (1d); , The elastic means (15, 1
6), and by applying a spring force to the second tooth profile (18b) by the elastic means (15, 16),
The tooth profile (18b) is pressed against the first tooth profile (1d) so that the second tooth profile (18b) and the first tooth profile (1d) mesh with each other. By means of the spring force of the means (15, 16), the second tooth profile (18)
b) while maintaining the meshing state between the first tooth profile (1d) and the driving-side rotating member (1), the elastic means (15, 16).
Power is transmitted to the driven-side rotating member (6) through
When the driven side device (3) is overloaded, when the axial load applied to the elastic means (15, 16) from the driving side rotating member (1) through the meshing portion of the two tooth portions (1d, 18b) reaches a predetermined value. The concave and convex shapes of the elastic means (15, 16) are reversed, the meshing state between the second tooth portion (18b) and the first tooth portion (1d) is released, and the driven side rotating member (1) rotates from the driven side rotating member (1). The power transmission to the member (6) is shut off.
【００１３】これによると、請求項１の発明と同様に、
従動側機器（３）の過負荷時に予め設定した所定値にお
いて弾性手段（１５、１６）の凹凸形状を反転させてト
ルクリミッター機能を確実に発揮できる。しかも、従来
技術のような転動ボールを使用しないため、組付けコス
トを低減できるとともに、通常運転時における動力伝達
を両歯形部における面接触部を通して確実に行うことが
でき、動力伝達の信頼性を向上できる。According to this, like the invention of claim 1,
When the driven apparatus (3) is overloaded, the unevenness of the elastic means (15, 16) is inverted at a predetermined value set in advance, so that the torque limiter function can be reliably exhibited. In addition, since rolling balls are not used as in the prior art, the assembly cost can be reduced, and power transmission during normal operation can be reliably performed through the surface contact portions of the both tooth portions, and the reliability of power transmission is improved. Can be improved.
【００１４】さらに、弾性手段（１５、１６）が第２歯
形部（１８ｂ）を第１歯形部（１ｄ）に押し付けるばね
力を発生する役割を果たすと同時にトルク伝達手段とし
ての役割も兼ねており、しかも、従動側回転部材（６）
を軸方向に移動可能とする必要がないので、従動側回転
部材（６）の形状を簡略化できるとともに、従動側回転
部材（６）の組付構造も著しく簡略化できる。Further, the elastic means (15, 16) have a function of generating a spring force for pressing the second tooth part (18b) against the first tooth part (1d) and also have a function of a torque transmitting means. And the driven side rotating member (6)
Since it is not necessary to be able to move in the axial direction, the shape of the driven-side rotating member (6) can be simplified, and the assembly structure of the driven-side rotating member (6) can be significantly simplified.
【００１５】なお、上記各手段の括弧内の符号は、後述
する実施形態記載の具体的手段との対応関係を示すもの
である。The reference numerals in parentheses of the above means indicate the correspondence with the specific means described in the embodiment described later.
【００１６】[0016]
【発明の実施の形態】以下、本発明の実施の形態を図に
基づいて説明する。 （第１実施形態）図１〜図５は本発明を自動車空調用圧
縮機の動力伝達装置に適用した第１実施形態を示すもの
であり、図１は通常の動力伝達状態を示し、図２は過負
荷時の動力伝達の遮断状態を示している。１は駆動側プ
ーリで、図示しないベルトを介して自動車エンジン（回
転駆動源）から回転力を受けて回転するものである。こ
のプーリ１には多重Ｖベルトが係合される多重Ｖ溝を持
ったプーリ部１ａが一体形成されており、鉄系金属で製
作されている。DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings. (First Embodiment) FIGS. 1 to 5 show a first embodiment in which the present invention is applied to a power transmission device of a compressor for an automobile air conditioner. FIG. 1 shows a normal power transmission state. Indicates a cut-off state of power transmission during overload. Reference numeral 1 denotes a drive-side pulley which rotates by receiving a rotational force from an automobile engine (rotary drive source) via a belt (not shown). The pulley 1 is integrally formed with a pulley portion 1a having a multi-V groove in which a multi-V belt is engaged, and is made of an iron-based metal.
【００１７】また、プーリ１の内周円筒部１ｂには、ベ
アリング２が配置され、このベアリング２によりプーリ
１は圧縮機（従動側機器）３のフロントハウジング４の
円筒突出部４ａ上に回転自在に支持されている。５は圧
縮機３の回転軸、６は従動側回転部材をなすハブで、鉄
系金属にて内周円筒部６ａと、この内周円筒部６ａの一
端部（反圧縮機側の端部）から半径方向外側へ延びるフ
ランジ部６ｂとを有する形状に形成されている。このハ
ブ６は回転軸５に対してインボリュートスプライン結合
等により軸方向には移動可能であり、かつ回転方向には
回り止めして結合されている。A bearing 2 is disposed on the inner peripheral cylindrical portion 1b of the pulley 1. The pulley 1 is rotatable on the cylindrical projecting portion 4a of the front housing 4 of the compressor (driven device) 3 by the bearing 2. It is supported by. Reference numeral 5 denotes a rotating shaft of the compressor 3, and reference numeral 6 denotes a hub serving as a driven-side rotating member. And a flange portion 6b extending radially outward from the front end. The hub 6 is axially movable with respect to the rotating shaft 5 by an involute spline connection or the like, and is connected to the rotating shaft 5 so as not to rotate in the rotating direction.
【００１８】そして、ハブ６の内周円筒部６ａの他端部
（圧縮機側の端部）と、回転軸５の段部５ａとの間には
リング状のストッパー７が挟み込み固定され、このスト
ッパー７とハブ６のフランジ部６ｂの内側面との間にコ
イルスプリング（弾性手段）８が配置されている。この
コイルスプリング８のばね力によりハブ６が反圧縮機側
（図１、２の左方向）への押圧力を受ける。換言する
と、ハブ６はコイルスプリング８のばね力によりプーリ
１から離れる方向の押圧力を受けるようになっている。A ring-shaped stopper 7 is sandwiched and fixed between the other end (the end on the compressor side) of the inner peripheral cylindrical portion 6a of the hub 6 and the step 5a of the rotating shaft 5. A coil spring (elastic means) 8 is arranged between the stopper 7 and the inner surface of the flange 6b of the hub 6. Due to the spring force of the coil spring 8, the hub 6 receives a pressing force on the side opposite to the compressor (leftward in FIGS. 1 and 2). In other words, the hub 6 receives a pressing force in a direction away from the pulley 1 by the spring force of the coil spring 8.
【００１９】一方、プーリ１のプーリ部１ａと内周円筒
部１ｂとを一体に連結しているリング状の側壁部１ｃの
半径方向中間部位には、その円周方向の全周にわたって
多数の第１歯形部１ｄがハブ６のフランジ部６ｂ側へ突
出するように形成されている。そして、ハブ６のフラン
ジ部６ｂの外周端部には、その円周方向の全周にわたっ
て多数の第２歯形部６ｃがプーリ１の側壁部１ｃ側へ突
出するように形成されている。この第１歯形部１ｄおよ
び第２歯形部６ｃは図３に示すように互いに略三角状に
突出して噛み合うようになっている。On the other hand, at the radially intermediate portion of the ring-shaped side wall portion 1c which integrally connects the pulley portion 1a of the pulley 1 and the inner peripheral cylindrical portion 1b, a large number of first and second circumferential portions are provided along the entire circumference. One tooth 1d is formed so as to protrude toward the flange 6b side of the hub 6. A large number of second tooth-shaped portions 6c are formed on the outer peripheral end of the flange portion 6b of the hub 6 over the entire circumference in the circumferential direction so as to project toward the side wall portion 1c of the pulley 1. As shown in FIG. 3, the first tooth portion 1d and the second tooth portion 6c project substantially in a triangular shape and mesh with each other.
【００２０】９は弾性手段をなす皿ばねで、中央に円形
穴を有する皿形状であり、炭素工具鋼、ばね鋼等の弾性
金属材料から形成されている。１０は皿ばね９の保持部
材であり、その外周円筒部１０ａに皿ばね９の中央の円
形穴を嵌合させて皿ばね９を保持する。また、保持部材
１０の内周円筒部１０ｂはボルト１１によって回転軸５
の端面に締めつけ固定される。Reference numeral 9 denotes a disc spring serving as an elastic means, which has a disc shape having a circular hole in the center and is made of an elastic metal material such as carbon tool steel and spring steel. Reference numeral 10 denotes a holding member for the disc spring 9, and the disc spring 9 is held by fitting a circular hole at the center of the disc spring 9 into the outer peripheral cylindrical portion 10a. The inner peripheral cylindrical portion 10 b of the holding member 10 is rotated by the bolt 11 with the rotating shaft 5.
To the end face of
【００２１】皿ばね９の外周縁部はハブ６のフランジ部
６ｂのリング状突起６ｄに接触するように配置されてい
るので、保持部材１０を締めつけ固定すると、皿ばね９
の中心部が軸方向に圧縮され、皿ばね９の弾性反発によ
る所定のばね力がハブ６のフランジ部６ｂに作用する。
この皿ばね９のばね力はハブ６のフランジ部６ｂの第２
歯形部６ｃをプーリ１の第１歯形部１ｄに対して押し付
けるように働くので、この両歯形部１ｄ、６ｃの噛み合
い状態が保持される。Since the outer peripheral edge of the disc spring 9 is arranged so as to contact the ring-shaped projection 6d of the flange 6b of the hub 6, when the holding member 10 is tightened and fixed, the disc spring 9
Is compressed in the axial direction, and a predetermined spring force due to the elastic repulsion of the disc spring 9 acts on the flange 6 b of the hub 6.
The spring force of this disc spring 9 is the second force of the flange 6b of the hub 6.
Since the tooth profile 6c acts to press the first tooth profile 1d of the pulley 1, the meshing state of the two tooth profiles 1d and 6c is maintained.
【００２２】なお、１２は軸シール装置で、圧縮機３の
フロントハウジング４の円筒突出部４ａの内周側と回転
軸５との間に配置され、圧縮機３の内部から外部へ冷媒
が漏れるのを防止するためのものである。次に、上記構
成において第１実施形態の作動を説明する。車両エンジ
ンのクランクプーリからの駆動力は図示しないベルトを
介してプーリ１に伝達され、プーリ１がベアリング２上
で回転する。このプーリ１の回転は、第１歯形部１ｄと
第２歯形部６ｃの噛み合い部を経てハブ６に伝達され、
さらにハブ６から回転軸５に伝達され、回転軸５が回転
するので、圧縮機３が作動する。Reference numeral 12 denotes a shaft sealing device, which is arranged between the inner peripheral side of the cylindrical projection 4a of the front housing 4 of the compressor 3 and the rotating shaft 5, and the refrigerant leaks from inside the compressor 3 to the outside. This is to prevent Next, the operation of the first embodiment in the above configuration will be described. The driving force from the crank pulley of the vehicle engine is transmitted to the pulley 1 via a belt (not shown), and the pulley 1 rotates on the bearing 2. The rotation of the pulley 1 is transmitted to the hub 6 via the meshing portion of the first tooth profile 1d and the second tooth profile 6c,
Further, the power is transmitted from the hub 6 to the rotating shaft 5, and the rotating shaft 5 rotates, so that the compressor 3 operates.
【００２３】ここで、ハブ６にはプーリ１からの駆動ト
ルクに応じて両歯形部１ｄ、６ｃによって発生する軸方
向の荷重Ｆｈと皿ばね９による軸方向の荷重Ｆｓが作用
しており、圧縮機３の通常運転時には皿ばね９による荷
重Ｆｓが駆動トルクによる荷重Ｆｈより大きくなるよう
に設定されているため、第１歯形部１ｄと第２歯形部６
ｃの噛み合い部は互いに離脱することなく噛み合い状態
を保持するので、プーリ１から圧縮機３への動力伝達が
行われる。Here, an axial load Fh generated by the tooth portions 1d and 6c in response to the driving torque from the pulley 1 and an axial load Fs generated by the disc spring 9 act on the hub 6, and the hub 6 is compressed. During normal operation of the machine 3, the load Fs by the disc spring 9 is set to be larger than the load Fh by the driving torque, so that the first tooth profile 1 d and the second tooth profile 6 are set.
Since the meshing portions c maintain the meshing state without being separated from each other, power is transmitted from the pulley 1 to the compressor 3.
【００２４】ところで、図３において、両歯形部１ｄ、
６ｃの１個あたりの軸方向の荷重Ｆｈ０は、円周方向の
荷重をＦｔ0 、駆動トルクをＴ、両歯形部１ｄ、６ｃの
数をＮ、両歯形部１ｄ、６ｃのピッチ半径をｒ（図１参
照）とすると、次の数式１、２により表すことができ
る。By the way, in FIG. 3, both tooth profile parts 1d,
The axial load Fh0 per piece of 6c is Ft0 in the circumferential direction, T is the driving torque, N is the number of both teeth 1d and 6c, and r is the pitch radius of both teeth 1d and 6c (FIG. 1), it can be represented by the following equations (1) and (2).
【００２５】[0025]
【数１】Ｆｈ0 ＝Ｆｔ0 ・ｔａｎθ## EQU1 ## Fh0 = Ft0.tan .theta.
【００２６】[0026]
【数２】Ｆｔ0 ＝Ｔ／（ｒ・Ｎ） そして、ハブ６に作用する駆動トルクによる軸方向の荷
重Ｆｈは次の数式３により表すことができる。Ft0 = T / (rN) The axial load Fh due to the driving torque acting on the hub 6 can be expressed by the following equation (3).
【００２７】[0027]
【数３】Ｆｈ＝Ｎ・Ｆｈ0 自動車用空調装置の場合、通常の運転状態での駆動トル
クの最大値はおおよそ２ｋｇｆ・ｍで、その時のＦｈは
本実施例では約４０ｋｇｆとなるように各諸元が決定さ
れており、圧縮機３のロック時にプーリ１に係合してい
るベルトがスリップし始める駆動トルクはおおよそ５ｋ
ｇｆ・ｍであると言われている。従って、ベルトがスリ
ップしないためには、駆動トルクは５ｋｇｆ・ｍ以下、
すなわちＦｈは約１００ｋｇｆ以下となる。Fh = N · Fh0 In the case of an air conditioner for a vehicle, the maximum value of the driving torque in a normal driving state is approximately 2 kgf · m, and the Fh at that time is about 40 kgf in this embodiment. The driving torque is about 5 k, when the compressor is locked, the belt engaged with the pulley 1 starts to slip when the compressor 3 is locked.
gf · m. Therefore, in order to prevent the belt from slipping, the driving torque should be 5 kgf · m or less,
That is, Fh is about 100 kgf or less.
【００２８】一方、皿ばね９は一般的に知られているよ
うに所定の荷重Ｆｍを越えた荷重が作用すると凹凸形状
が反転する特性が得られる。本実施形態の皿ばね９は図
４に示すように約６０ｋｇｆ以上の荷重Ｆｍが作用する
と、皿ばね９の凹凸形状が反転して大きく変形するよう
に設定されている。図４において、横軸の変形量は皿ば
ね９の状態Ａ（皿ばね９に荷重が付加されていない自由
状態）における皿ばね外周縁部の位置を基準位置Ｘと
し、この基準位置Ｘに対する皿ばね外周縁部の変形量を
表している。そして、図４のグラフ中のＡ、Ｂ、Ｃ、Ｄ
と、図４上部の４つの皿ばねＡ、Ｂ、Ｃ、Ｄとは対応し
ている。On the other hand, as is generally known, when a load exceeding a predetermined load Fm is applied, the disc spring 9 has such a characteristic that the uneven shape is inverted. As shown in FIG. 4, the disc spring 9 of the present embodiment is set so that when a load Fm of about 60 kgf or more acts thereon, the concavo-convex shape of the disc spring 9 is reversed and greatly deformed. In FIG. 4, the amount of deformation on the horizontal axis is defined as a reference position X, which is the position of the outer peripheral edge of the disk spring 9 in the state A of the disk spring 9 (free state in which no load is applied to the disk spring 9). It shows the amount of deformation of the outer peripheral edge of the spring. And, A, B, C, D in the graph of FIG.
4 correspond to the four disc springs A, B, C, and D in the upper part of FIG.
【００２９】そして、両歯形部１ｄ、６ｃの高さδは、
皿ばね９への荷重特性が負になる領域、具体的一例とし
ては皿ばね９の変形量が図４の６ｍｍを越えると、両歯
形部１ｄ、６ｃの噛み合い状態が外れるように設定され
ている。従って、組み付け時に保持部材８の締めつけ固
定位置により皿ばね９の変形量を約１ｍｍとして、図４
のＢ状態とし、５０ｋｇｆの荷重Ｆｓを皿ばね９に与え
ておけば、通常の運転状態では、駆動トルクの最大値
（おおよそ２ｋｇｆ・ｍ）における軸方向荷重Ｆｈは約
４０ｋｇｆとなり、荷重Ｆｓ＞荷重Ｆｈの関係になって
いる。従って、ハブ６の第２歯形部６ｃがプーリ１の第
１歯形部１ｄに押し付けられ、図１、３に示す噛み合い
状態を確実に保持する。そのため、プーリ１からハブ６
への動力伝達を確実に行うことができる。Then, the height δ of both tooth-shaped portions 1d and 6c is
When the load characteristic of the disc spring 9 becomes negative, as a specific example, when the deformation of the disc spring 9 exceeds 6 mm in FIG. 4, the meshing state of the two tooth-shaped portions 1d and 6c is set to be disengaged. . Therefore, the amount of deformation of the disc spring 9 is set to about 1 mm depending on the fastening position of the holding member 8 at the time of assembly, and FIG.
If the load Fs of 50 kgf is applied to the disc spring 9 in the B state, the axial load Fh at the maximum value of the drive torque (about 2 kgf · m) is about 40 kgf in a normal operation state, and the load Fs> load Fh. Accordingly, the second tooth profile 6c of the hub 6 is pressed against the first tooth profile 1d of the pulley 1, and the meshing state shown in FIGS. Therefore, pulley 1 to hub 6
Power transmission to the vehicle.
【００３０】これに対し、圧縮機３がロックした場合に
は、駆動トルクによる荷重Ｆｈは予め設定した所定値Ｆ
ｍ（約６０ｋｇｆ）を越えるため、皿ばね９の凹凸形状
が反転し、皿ばね９は図４のＤの状態に至る。この結
果、皿ばね９の変形量が図４のＬ＝８ｍｍに達するの
で、皿ばね９によるハブ６への軸方向荷重がなくなり、
両歯形部１ｄ、６ｃの噛み合い状態が解除され、両歯形
部１ｄ、６ｃは図２、５に示す離脱状態となる。プーリ
１からハブ６への動力伝達が遮断され、ベルトのスリッ
プによる破断を未然に防止できる。On the other hand, when the compressor 3 is locked, the load Fh due to the driving torque becomes a predetermined value F
m (about 60 kgf), the concavo-convex shape of the disc spring 9 is inverted, and the disc spring 9 reaches the state of D in FIG. As a result, since the amount of deformation of the disc spring 9 reaches L = 8 mm in FIG. 4, the axial load on the hub 6 by the disc spring 9 is eliminated,
The meshing state of the two tooth sections 1d and 6c is released, and the two tooth sections 1d and 6c are in the detached state shown in FIGS. Power transmission from the pulley 1 to the hub 6 is cut off, and breakage due to slippage of the belt can be prevented.
【００３１】また、両歯形部１ｄ、６ｃ、ハブ６、皿ば
ね９などには、摩擦の低減や、さび付き、腐食等の防止
のために、フッ素樹脂コーティング等の表面処理を必要
に応じて施すことが好ましい。 （第２実施形態）図６は第２実施形態を示すもので、第
２実施形態では、第１実施形態のプーリ１を、プーリ１
と円筒形状のロータ１３に分割し、プーリ１のプーリ部
１ａの内周側に所定間隔を開けてロータ１３を同心状に
配置するとともに、このプーリ１のプーリ部１ａの内周
側とロータ１３の外周側との間を、弾性変形可能なゴム
部材１４により一体に連結している。The toothed portions 1d, 6c, the hub 6, the disc spring 9 and the like are optionally subjected to a surface treatment such as a fluororesin coating to reduce friction, prevent rust, corrosion and the like. It is preferable to apply. (Second Embodiment) FIG. 6 shows a second embodiment. In the second embodiment, the pulley 1 of the first embodiment is
The rotor 13 is divided into a cylindrical rotor 13 and the rotor 13 is concentrically arranged at a predetermined interval on the inner peripheral side of the pulley portion 1a of the pulley 1, and the inner peripheral side of the pulley portion 1a of the pulley 1 is Are integrally connected to each other by an elastically deformable rubber member 14.
【００３２】ここで、ゴム部材１４はプーリ部１ａの内
周側とロータ１３の外周側に焼き付き接着等の方法で固
着されている。このゴム部材１４の弾性変形により圧縮
機３のトルク変動を減衰させ、騒音を低減する。そし
て、第２実施形態では、ロータ１３の半径方向内側に延
びる側壁部１３ａに、第１実施形態の第１歯形部１ｄに
相当する歯形部１３ｂが形成されており、この歯形部１
３ｂがハブ６の第２歯形部６ｃに噛み合うようになって
おり、第１実施形態と同じ機構にて過負荷時のトルクリ
ミッター機能を果たすことができる。The rubber member 14 is fixed to the inner peripheral side of the pulley portion 1a and the outer peripheral side of the rotor 13 by a method such as seizure bonding. The elastic deformation of the rubber member 14 attenuates the torque fluctuation of the compressor 3 and reduces noise. In the second embodiment, a tooth portion 13b corresponding to the first tooth portion 1d of the first embodiment is formed on a side wall portion 13a extending inward in the radial direction of the rotor 13.
3b is meshed with the second tooth profile 6c of the hub 6, so that the same mechanism as in the first embodiment can fulfill the torque limiter function at the time of overload.
【００３３】すなわち、第２実施形態によると、圧縮機
ロックのような過負荷時のトルクリミッター機能と、通
常運転時におけるトルク変動低減機能とを両立すること
ができる。 （第３実施形態）図７〜図１１は第３実施形態を示すも
ので、図７、８は通常の動力伝達状態を示し、図９は過
負荷時の動力伝達の遮断状態を示している。第１実施形
態では、プーリ１からハブ６を介して回転軸５に駆動ト
ルクを伝達しており、皿ばね９は動力伝達に関与してい
ないが、第３実施形態では、この皿ばね９に相当する弾
性手段に動力伝達の役割を兼務させるようにしたもので
ある。That is, according to the second embodiment, it is possible to achieve both a torque limiter function at the time of overload such as a compressor lock and a torque fluctuation reducing function at the time of normal operation. (Third Embodiment) FIGS. 7 to 11 show a third embodiment. FIGS. 7 and 8 show a normal power transmission state, and FIG. 9 shows a power transmission cutoff state during overload. . In the first embodiment, the driving torque is transmitted from the pulley 1 to the rotary shaft 5 via the hub 6, and the disc spring 9 is not involved in power transmission. The corresponding elastic means also serves the role of power transmission.
【００３４】すなわち、第３実施形態では、この皿ばね
９に相当する弾性手段として、図１０に示すような２枚
の円形板ばね１５、１６を用いている。この２枚の円形
板ばね１５、１６は放射状に配置した複数本（図示の例
では８本）の梁部１５ａ、１６ａと、この梁部１５ａ、
１６ａの外周側を一体に連結する円環状部１５ｂ、１６
ｂとからなり、各梁部１５ａ、１６ａの内周側先端部に
はそれぞれリベット挿通用の円形穴１５ｃ、１６ｃが設
けられている。That is, in the third embodiment, two circular leaf springs 15 and 16 as shown in FIG. 10 are used as elastic means corresponding to the disc spring 9. The two circular leaf springs 15 and 16 include a plurality of (eight in the illustrated example) beam portions 15a and 16a radially arranged, and the beam portions 15a and 16a.
Annular portions 15b, 16 for integrally connecting the outer peripheral side of 16a
b, circular holes 15c and 16c for rivet insertion are provided at the inner peripheral end portions of the beam portions 15a and 16a, respectively.
【００３５】また、円環状部１５ｂ、１６ｂにも複数
（図示の例では４個）のリベット挿通用の円形穴１５
ｄ、１６ｄが設けられている。そして、２枚の円形板ば
ね１５、１６は基本的には同一寸法の同一形状である
が、一方の円形板ばね１５において円環状部１５ｂに設
ける円形穴１５ｄの、梁部１５ａに対する円周方向の開
口位置と、他方の円形板ばね１６において円環状部１６
ｂに設ける円形穴１６ｄの、梁部１６ａに対する円周方
向の開口位置は、図８（ａ）、（ｂ）の比較から理解さ
れるように、円周方向において互いにずれた位置となっ
ている。Also, a plurality of (four in the illustrated example) rivet insertion circular holes 15 are provided in the annular portions 15b and 16b.
d and 16d are provided. The two circular leaf springs 15 and 16 have basically the same shape and the same dimensions, but the circular hole 15d provided in the annular portion 15b in one circular leaf spring 15 has a circumferential direction with respect to the beam portion 15a. And the annular portion 16 of the other circular leaf spring 16
As can be understood from the comparison between FIGS. 8A and 8B, the positions of the circular holes 16d provided in b in the circumferential direction with respect to the beam portions 16a are shifted from each other in the circumferential direction. .
【００３６】２枚の円形板ばね１５、１６はその円環状
部１５ｂ、１６ｂの円形穴１５ｄ、１６ｄが合致するよ
うにして重ね合わせ、この円形穴１５ｄ、１６ｄにリベ
ット１７を挿通するとともに、このリベット１７をリン
グ状の連結板１８の円形穴１８ａ（図８参照）に挿通し
て、このリベット１７により２枚の円形板ばね１５、１
６の円環状部１５ｂ、１６ｂを連結板１８にかしめ固定
する。The two circular leaf springs 15 and 16 are overlapped with each other so that the circular holes 15d and 16d of the annular portions 15b and 16b coincide with each other, and a rivet 17 is inserted through the circular holes 15d and 16d. The rivet 17 is inserted into the circular hole 18a (see FIG. 8) of the ring-shaped connecting plate 18, and the two circular leaf springs 15, 1
The six annular portions 15b and 16b are caulked and fixed to the connecting plate 18.
【００３７】この連結板１８には、第１実施形態のハブ
６の第２歯形部６ｃに相当する第２歯形部１８ｂが円周
方向に形成されており、プーリ１の第１歯形部１ｄに噛
み合うようになっている。ここで、連結板１８のうち、
円形穴１８ａの形成部位は歯形部１８ｂを形成していな
い。一方、２枚の円形板ばね１５、１６の円環状部１５
ｂ、１６ｂに設けた円形穴１５ｄ、１６ｄの円周方向の
開口位置がずれているため、上記のリベット１７により
２枚の円形板ばね１５、１６を連結板１８にかしめ固定
した組付状態では、各梁部１５ａ、１６ａの内周側先端
部の円形穴１５ｃ、１６ｃが図１１（ａ）に示すように
円周方向においてずれている。A second tooth profile 18b corresponding to the second tooth profile 6c of the hub 6 of the first embodiment is formed in the connecting plate 18 in the circumferential direction, and is formed on the first tooth profile 1d of the pulley 1. It is designed to engage. Here, of the connecting plates 18,
The portion where the circular hole 18a is formed does not form the tooth profile 18b. On the other hand, the annular portion 15 of the two circular leaf springs 15 and 16
Since the positions of the circular holes 15d and 16d provided in the b and 16b are shifted from each other in the circumferential direction, in the assembled state where the two circular leaf springs 15 and 16 are caulked and fixed to the connecting plate 18 by the rivets 17 described above. The circular holes 15c, 16c at the inner peripheral end portions of the beam portions 15a, 16a are shifted in the circumferential direction as shown in FIG.
【００３８】そこで、各梁部１５ａ、１６ａを円周方向
に弾性変形させて、図１１（ｂ）に示すように円形穴１
５ｃ、１６ｃを強制的に重合させ、この円形穴１５ｃ、
１６ｃにリベット１９を挿通するとともに、このリベッ
ト１９をハブ６のフランジ部６ｂの円形穴６ｅに挿通し
て、このリベット１９により各梁部１５ａ、１６ａの内
周側先端部をハブ６のフランジ部６ｂにかしめ固定す
る。これにより、連結板１８が２枚の円形板ばね１５、
１６を介してハブ６のフランジ部６ｂに一体に連結され
る。Therefore, each of the beam portions 15a and 16a is elastically deformed in the circumferential direction, and as shown in FIG.
5c, 16c are forcibly polymerized, and this circular hole 15c,
The rivet 19 is inserted through the circular hole 6e of the flange 6b of the hub 6 while the rivet 19 is inserted through the hub 6 and the inner peripheral end of each of the beams 15a and 16a is connected to the flange 6 of the hub 6 by the rivet 19. 6b. As a result, the connecting plate 18 has two circular leaf springs 15,
16 and is integrally connected to the flange portion 6 b of the hub 6.
【００３９】また、上記組付過程において、各梁部１５
ａ、１６ａを図１１（ａ）の状態から円周方向に弾性変
形させて、図１１（ｂ）に示すように両円形穴１５ｃ、
１６ｃが重合する状態に変形させることにより、この変
形に伴って各梁部１５ａ、１６ａの内周先端側の円形穴
１５ｃ、１６ｃ部に対して、各梁部１５ａ、１６ａの外
周側（円環状部１５ｂ、１６ｂ側）が軸方向（図８の右
側方向）に変形する。この軸方向変形により、２枚の円
形板ばね１５、１６は連結板１８の第２歯形部１８ｂを
プーリ１の第１歯形部１ｄに押しつけるばね力を発生し
て、第２歯形部１８ｂと第１歯形部１ｄとの噛み合い状
態を保持する。In the above assembling process, each beam 15
a and 16a are elastically deformed in the circumferential direction from the state of FIG. 11 (a), and as shown in FIG.
By deforming to a state where 16c is superimposed, the circular holes 15c and 16c on the inner peripheral tip side of each beam portion 15a and 16a due to this deformation and the outer peripheral side (annular shape) of each beam portion 15a and 16a The portions 15b and 16b) are deformed in the axial direction (the right direction in FIG. 8). Due to this axial deformation, the two circular leaf springs 15 and 16 generate a spring force that presses the second toothed portion 18b of the connecting plate 18 against the first toothed portion 1d of the pulley 1, and the second toothed portion 18b and the second toothed portion The meshing state with the one tooth portion 1d is maintained.
【００４０】また、各梁部１５ａ、１６ａが軸方向に変
形することにより、２枚の円形板ばね１５、１６は皿ば
ね９と同様に、所定の荷重が付加されると凹凸形状が軸
方向で反転する特性を得ることができる。第３実施形態
によると、圧縮機３の通常運転時には図８に示すよう
に、２枚の円形板ばね１５、１６のばね力によってプー
リ１の第１歯形部１ｄと連結板１８の第２歯形部１８ｂ
との噛み合い状態が保持されるので、プーリ１の回転が
連結板１８、２枚の円形板ばね１５、１６、ハブ６を経
て回転軸５に伝達され、圧縮機３が作動する。Further, as the beam portions 15a and 16a are deformed in the axial direction, the two circular leaf springs 15 and 16 have the uneven shape in the axial direction when a predetermined load is applied, similarly to the disc spring 9. , It is possible to obtain a reversal characteristic. According to the third embodiment, during normal operation of the compressor 3, as shown in FIG. 8, the first tooth profile 1 d of the pulley 1 and the second tooth profile of the connecting plate 18 are generated by the spring force of the two circular leaf springs 15 and 16. Part 18b
The rotation of the pulley 1 is transmitted to the rotating shaft 5 via the connecting plate 18, the two circular leaf springs 15, 16 and the hub 6, and the compressor 3 operates.
【００４１】一方、圧縮機３の過負荷時にはプーリ１の
第１歯形部１ｄと連結板１８の第２歯形部１８ｂとの噛
み合い部および連結板１８を通して２枚の円形板ばね１
５、１６の円環状部１５ｂ、１６ｂに加わる軸方向荷重
が所定値に到達すると、２枚の円形板ばね１５、１６の
凹凸形状が軸方向で反転し、図９に示すように、円環状
部１５ｂ、１６ｂがプーリ１から離れる方向に変位す
る。On the other hand, when the compressor 3 is overloaded, the two circular leaf springs 1 pass through the engaging portion between the first tooth portion 1d of the pulley 1 and the second tooth portion 18b of the connecting plate 18 and the connecting plate 18.
When the axial load applied to the annular portions 15b, 16b reaches a predetermined value, the concave and convex shapes of the two circular leaf springs 15, 16 are reversed in the axial direction, and as shown in FIG. The portions 15b and 16b are displaced away from the pulley 1.
【００４２】この結果、連結板１８の第２歯形部１８ｂ
がプーリ１の第１歯形部１ｄから離脱して、両歯形部１
ｄ、１８ｂの噛み合い状態が解放されるので、プーリ１
から回転軸５への回転伝達が遮断される。第３実施形態
では２枚の円形板ばね１５、１６が弾性手段としての役
割を果たすと同時にトルク伝達手段としての役割も兼ね
ているとともに、ハブ６を軸方向に移動可能とする必要
がないので、第１、第２実施形態に比してハブ６の形状
を簡略化でき、また、ハブ６の組付構造も著しく簡略化
できる。As a result, the second tooth profile 18b of the connecting plate 18
Is disengaged from the first tooth profile 1d of the pulley 1 and the two tooth profiles 1
Since the meshing state of d and 18b is released, the pulley 1
The rotation transmission from the shaft to the rotating shaft 5 is interrupted. In the third embodiment, the two circular leaf springs 15 and 16 serve not only as elastic means but also as torque transmitting means, and there is no need to make the hub 6 movable in the axial direction. The shape of the hub 6 can be simplified as compared with the first and second embodiments, and the assembly structure of the hub 6 can be significantly simplified.
【００４３】（他の実施形態）なお、第３実施形態では
２枚の円形板ばね１５、１６を組み合わせる構成としし
ているが、駆動トルクが小さく円形板ばねの強度に余裕
がある場合には、円形板ばねとして１枚のみ用い、この
１枚の円形板ばねにおける隣合う梁部を撓ませて、その
隣合う梁部の内周側先端の円形穴を強制的に重合させる
ように組み付けて、１枚の円形板ばねにて皿ばね特性を
得るようにしてもよい。(Other Embodiments) In the third embodiment, the two circular leaf springs 15 and 16 are combined. However, when the driving torque is small and the strength of the circular leaf springs has a margin, Only one circular leaf spring is used, and an adjacent beam portion of this one circular leaf spring is bent so that the circular hole at the inner peripheral end of the adjacent beam portion is forcibly overlapped. Alternatively, the disc spring characteristics may be obtained with a single circular leaf spring.
【００４４】また、第３実施形態において、第２実施形
態のロータ１３とゴム部材１４とを用いたトルク変動低
減機構を採用できることはもちろんである。また、本発
明は自動車用空調装置の圧縮機への動力伝達装置に限ら
ず、種々な用途のものに広く適用可能である。Further, in the third embodiment, it goes without saying that the torque fluctuation reducing mechanism using the rotor 13 and the rubber member 14 of the second embodiment can be adopted. Further, the present invention is not limited to a power transmission device to a compressor of an air conditioner for a vehicle, but can be widely applied to various applications.
【図１】本発明の第１実施形態を示す縦断面図で、通常
運転時の状態を示す。FIG. 1 is a longitudinal sectional view showing a first embodiment of the present invention, showing a state during normal operation.
【図２】第１実施形態における過負荷運転時の状態を示
す縦断面図である。FIG. 2 is a longitudinal sectional view showing a state at the time of overload operation in the first embodiment.
【図３】図１のＢ矢視による歯形部の上面図である。FIG. 3 is a top view of the tooth profile as viewed in the direction of arrow B in FIG. 1;
【図４】第１実施形態の皿ばねの作動特性の説明図であ
る。FIG. 4 is an explanatory diagram of operation characteristics of the disc spring according to the first embodiment.
【図５】第１実施形態における歯形部の離脱状態を示す
説明図である。FIG. 5 is an explanatory diagram showing a detached state of the tooth profile in the first embodiment.
【図６】本発明の第２実施形態を示す縦断面図で、通常
運転時の状態を示す。FIG. 6 is a longitudinal sectional view showing a second embodiment of the present invention, showing a state during normal operation.
【図７】本発明の第３実施形態を示す正面図である。FIG. 7 is a front view showing a third embodiment of the present invention.
【図８】図７のＥ−Ｅ矢視線に沿う断面図である。FIG. 8 is a sectional view taken along the line EE of FIG. 7;
【図９】第３実施形態における過負荷運転時の状態を示
す縦断面図である。FIG. 9 is a longitudinal sectional view showing a state at the time of overload operation in a third embodiment.
【図１０】第３実施形態で用いる２枚の円形板ばねの正
面図である。FIG. 10 is a front view of two circular leaf springs used in the third embodiment.
【図１１】第３実施形態で用いる２枚の円形板ばねの組
付説明図である。FIG. 11 is an explanatory view for assembling two circular leaf springs used in the third embodiment.
１…プーリ（駆動側回転部材）、１ｄ、１３ａ…第１歯
形部、３…圧縮機、５…回転軸、６…ハブ（従動側回転
部材）、６ｃ、１８ｂ…第２歯形部、９…皿バネ（弾性
手段）、１０…保持部材、１１…ボルト、１３…ロー
タ、１４…ゴム部材、１５、１６…円形板ばね（弾性手
段）、１５ａ、１６ａ…梁部、１５ｂ、１６ｂ…円環状
部、１８…連結板。DESCRIPTION OF SYMBOLS 1 ... Pulley (driving side rotating member), 1d, 13a ... 1st tooth profile part, 3 ... Compressor, 5 ... Rotating shaft, 6 ... Hub (driven side rotating member), 6c, 18b ... 2nd tooth profile part, 9 ... Disc spring (elastic means), 10 holding member, 11 bolt, 13 rotor, 14 rubber member, 15, 16 circular plate spring (elastic means), 15a, 16a beam, 15b, 16b annular Part, 18 ... connecting plate.
フロントページの続き (72)発明者 稲垣 光夫 愛知県西尾市下羽角町岩谷14番地 株式会 社日本自動車部品総合研究所内 (72)発明者 佐伯 学 愛知県刈谷市昭和町１丁目１番地 株式会 社デンソー内 (72)発明者 坂本 博康 愛知県刈谷市昭和町１丁目１番地 株式会 社デンソー内Continued on the front page (72) Inventor Mitsuo Inagaki 14 Iwatani, Shimowasukamachi, Nishio City, Aichi Prefecture Inside the Japan Auto Parts Research Institute (72) Inventor Manabu Saeki 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Denso Corporation (72) Inventor Hiroyasu Sakamoto 1-1-1, Showa-cho, Kariya-shi, Aichi Pref. DENSO Corporation
Claims (8)
る駆動側回転部材（１、１３、１４）と、 従動側機器（３）の回転軸（５）に対して回転方向には
回り止めして連結され、軸方向には移動可能に連結され
た従動側回転部材（６）と、 前記駆動側回転部材（１、１３、１４）に設けられた第
１歯形部（１ｄ、１３ｂ）と、 前記従動側回転部材（６）に設けられ、前記第１歯形部
（１ｄ、１３ｂ）に噛み合うことができる第２歯形部
（６ｃ）と、 前記第２歯形部（６ｃ）が前記第１歯形部（１ｄ、１３
ｂ）に押し付けられ、前記第２歯形部（６ｃ）と前記第
１歯形部（１ｄ、１３ｂ）とが噛み合うように前記従動
側回転部材（６）にばね力を作用させる弾性手段（９）
とを備え、 前記従動側機器（３）の通常運転時には、前記弾性手段
（９）のばね力により前記第２歯形部（６ｃ）と前記第
１歯形部（１ｄ、１３ｂ）との噛み合い状態が維持され
て、前記駆動側回転部材（１、１３、１４）から前記従
動側回転部材（６）に動力が伝達され、 一方、前記従動側機器（３）の過負荷時には、前記駆動
側回転部材（１、１３、１４）から前記従動側回転部材
（６）を経て前記弾性手段（９）に加わる軸方向荷重が
所定値に到達すると、前記弾性手段（９）の凹凸形状が
反転して、前記第２歯形部（６ｃ）が前記第１歯形部
（１ｄ、１３ｂ）から離脱し、前記駆動側回転部材
（１、１３、１４）から前記従動側回転部材（６）への
動力伝達が遮断されるようにしたことを特徴とする動力
伝達装置。1. A driving-side rotating member (1, 13, 14) that rotates by receiving a rotational force from a rotary driving source, and rotates in a rotational direction with respect to a rotation axis (5) of a driven-side device (3). A driven-side rotating member (6) connected and stopped so as to be movable in the axial direction; and a first tooth profile (1d, 13b) provided on the driving-side rotating member (1, 13, 14). A second tooth profile (6c) provided on the driven-side rotating member (6) and capable of meshing with the first tooth profile (1d, 13b); and the second tooth profile (6c) includes the first tooth profile (6c). Tooth profile (1d, 13
b) and elastic means (9) for applying a spring force to the driven-side rotating member (6) so that the second tooth profile (6c) and the first tooth profile (1d, 13b) mesh with each other.
During the normal operation of the driven device (3), the meshing state between the second tooth profile (6c) and the first tooth profile (1d, 13b) is established by the spring force of the elastic means (9). Power is transmitted from the driving-side rotating members (1, 13, 14) to the driven-side rotating member (6) while the driven-side device (3) is overloaded when the driven-side device (3) is overloaded. When the axial load applied to the elastic means (9) from (1, 13, 14) via the driven side rotating member (6) reaches a predetermined value, the uneven shape of the elastic means (9) is reversed, The second tooth profile (6c) is disengaged from the first tooth profile (1d, 13b), and power transmission from the driving-side rotating member (1, 13, 14) to the driven-side rotating member (6) is cut off. A power transmission device characterized in that:
らの回転力がベルトを介して伝達され回転するプーリ
（１）と、このプーリ（１）の内周側に間隔をおいて配
置された円筒状のロータ（１３）と、このプーリ（１）
とロータ（１３）との間を一体に連結する弾性変形可能
なゴム部材（１４）とを備え、 前記ロータ（１３）に、その半径方向の内方に伸びる側
壁部（１３ａ）を形成し、この側壁部（１３ａ）に前記
第１歯形部（１３ｂ）を形成したことを特徴とする請求
項１に記載の動力伝達装置。2. A pulley (1), which is rotated by transmitting a rotational force from a rotary drive source via a belt, to the driving-side rotating member, and is disposed at an inner circumferential side of the pulley (1) with a space therebetween. Cylindrical rotor (13) and this pulley (1)
An elastically deformable rubber member (14) for integrally connecting the rotor and the rotor (13); and forming a radially inwardly extending side wall (13a) on the rotor (13); The power transmission device according to claim 1, wherein the first tooth portion (13b) is formed on the side wall portion (13a).
の皿ばね（９）の外周縁部が前記従動側回転部材（６）
に圧接することを特徴とする請求項１または２に記載の
動力伝達装置。3. The elastic means is a disc spring (9), and the outer peripheral edge of the disc spring (9) is the driven side rotating member (6).
The power transmission device according to claim 1, wherein the power transmission device is pressed against the power transmission device.
持部材（１０）を有し、 この保持部材（１０）は前記回転軸（５）にボルト（１
１）によりねじ止め固定されていることを特徴とする請
求項３に記載の動力伝達装置。4. A holding member (10) for holding an inner peripheral portion of the disc spring (9), the holding member (10) being attached to the rotating shaft (5) by a bolt (1).
The power transmission device according to claim 3, wherein the power transmission device is fixed by screwing according to (1).
る駆動側回転部材（１）と、 従動側機器（３）の回転軸（５）に対して回り止めして
連結された従動側回転部材（６）と、 前記駆動側回転部材（１）に設けられた第１歯形部（１
ｄ）と、 この第１歯形部（１ｄ）に噛み合うことができる第２歯
形部（１８ｂ）と、 この第２歯形部（１８ｂ）と前記従動側回転部材（６）
との間を連結するよう配置された弾性手段（１５、１
６）とを備え、 この弾性手段（１５、１６）により前記第２歯形部（１
８ｂ）にばね力を作用させることにより、前記第２歯形
部（１８ｂ）が前記第１歯形部（１ｄ）に押し付けられ
て前記第２歯形部（６ｃ）と前記第１歯形部（１ｄ）と
が噛み合うようにし、 前記従動側機器（３）の通常運転時には、前記弾性手段
（１５、１６）のばね力により前記第２歯形部（１８
ｂ）と前記第１歯形部（１ｄ）との噛み合い状態が維持
されて、前記駆動側回転部材（１）から前記弾性手段
（１５、１６）を介して前記従動側回転部材（６）に動
力が伝達され、 一方、前記従動側機器（３）の過負荷時には、前記駆動
側回転部材（１）から前記両歯形部（１ｄ、１８ｂ）の
噛み合い部を経て前記弾性手段（１５、１６）に加わる
軸方向荷重が所定値に到達すると、前記弾性手段（１
５、１６）の凹凸形状が反転して、前記第２歯形部（１
８ｂ）が前記第１歯形部（１ｄ）から離脱し、前記駆動
側回転部材（１）から前記従動側回転部材（６）への動
力伝達が遮断されるようにしたことを特徴とする動力伝
達装置。5. A driven side rotating member (1) that rotates by receiving a rotational force from a rotary drive source, and a driven side that is connected to a rotation shaft (5) of a driven side device (3) by preventing rotation. A rotating member (6); a first tooth profile (1) provided on the driving-side rotating member (1).
d), a second tooth profile (18b) capable of meshing with the first tooth profile (1d), the second tooth profile (18b) and the driven side rotating member (6).
And elastic means (15, 1
6), and the second tooth profile (1) is provided by the elastic means (15, 16).
By applying a spring force to 8b), the second tooth part (18b) is pressed against the first tooth part (1d), and the second tooth part (6c) and the first tooth part (1d) are pressed. When the driven device (3) is in normal operation, the second tooth profile (18) is actuated by the spring force of the elastic means (15, 16).
b) and the meshing state of the first tooth portion (1d) is maintained, and power is transmitted from the driving-side rotating member (1) to the driven-side rotating member (6) via the elastic means (15, 16). On the other hand, when the driven-side device (3) is overloaded, the driven-side rotating member (1) is transmitted to the elastic means (15, 16) via the meshing portions of the two tooth portions (1d, 18b). When the applied axial load reaches a predetermined value, the elastic means (1)
The concavo-convex shape of (5, 16) is inverted, and the second tooth profile (1) is inverted.
8b) is disengaged from the first tooth portion (1d), and power transmission from the driving side rotating member (1) to the driven side rotating member (6) is cut off. apparatus.
結板（１８）を連結するとともに、この連結板（１８）
に前記第２歯形部（１８ｂ）を形成したことを特徴とす
る請求項５に記載の動力伝達装置。6. A separate connecting plate (18) is connected to said elastic means (15, 16), and said connecting plate (18) is connected.
The power transmission device according to claim 5, wherein the second tooth portion (18b) is formed on the power transmission device.
本の梁部（１５ａ、１６ａ）と、この梁部（１５ａ、１
６ａ）の外周側を一体に連結する円環状部（１５ｂ、１
６ｂ）とを有する円形板ばね（１５、１６）からなり、 前記円環状部（１５ｂ、１６ｂ）が前記連結部材（１
８）に連結され、前記複数本の梁部（１５ａ、１６ａ）
の内周側先端部が前記従動側回転部材（６）に連結さ
れ、 前記複数本の梁部（１５ａ、１６ａ）が軸方向に変形す
ることにより前記円環状部（１５ｂ、１６ｂ）から前記
連結部材（１８）に対してばね力を作用させることによ
り、前記第２歯形部（１８ｂ）を前記第１歯形部（１
ｄ）に押し付けることを特徴とする請求項５または６に
記載の動力伝達装置。7. The elastic means comprises a plurality of beams (15a, 16a) radially arranged, and the beams (15a, 16a).
6a), an annular portion (15b, 1
6b), and the annular portions (15b, 16b) are connected to the connecting member (1).
8) and connected to the plurality of beams (15a, 16a).
Is connected to the driven-side rotating member (6), and the plurality of beams (15a, 16a) are deformed in the axial direction so that the connection from the annular portions (15b, 16b) is made. By applying a spring force to the member (18), the second tooth part (18b) is connected to the first tooth part (1).
The power transmission device according to claim 5, wherein the power transmission device is pressed against d).
凍サイクルの圧縮機（３）であることを特徴とする請求
項１ないし７のいずれか１つに記載の動力伝達装置。8. The power transmission device according to claim 1, wherein the driven device is a compressor (3) of a refrigeration cycle of an air conditioner for a vehicle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9060947A JPH10252857A (en) | 1997-03-14 | 1997-03-14 | Power transmitting device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9060947A JPH10252857A (en) | 1997-03-14 | 1997-03-14 | Power transmitting device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH10252857A true JPH10252857A (en) | 1998-09-22 |
Family
ID=13157104
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9060947A Pending JPH10252857A (en) | 1997-03-14 | 1997-03-14 | Power transmitting device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH10252857A (en) |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000356258A (en) * | 1999-06-14 | 2000-12-26 | Denso Corp | Power transmission |
| US6200221B1 (en) * | 1998-12-11 | 2001-03-13 | Ogura Clutch Co., Ltd. | Power transmission apparatus |
| JP2001200906A (en) * | 2000-01-20 | 2001-07-27 | Kubota Corp | Torque transmitting device |
| JP2003074586A (en) * | 2001-08-30 | 2003-03-12 | Nok Corp | Power transmission device |
| US6913538B2 (en) | 2001-05-22 | 2005-07-05 | Denso Corporation | Torque transmission system |
| JP2007078128A (en) * | 2005-09-15 | 2007-03-29 | Toyota Motor Corp | Transmission torque limiter for vehicle |
| WO2011127898A1 (en) * | 2010-04-14 | 2011-10-20 | Schaeffler Technologies Gmbh & Co. Kg | Pulley damper |
| KR20120070634A (en) * | 2010-12-22 | 2012-07-02 | 한라공조주식회사 | Power transmission apparatus of a compressor |
| WO2014094760A1 (en) * | 2012-12-19 | 2014-06-26 | Schaeffler Technologies AG & Co. KG | Decoupler for damping a torque transmission between a drive shaft of a motor vehicle and a belt pulley |
| JP2015172348A (en) * | 2014-03-12 | 2015-10-01 | 三菱電機株式会社 | Engine starter |
| JP2016108975A (en) * | 2014-12-03 | 2016-06-20 | 三菱電機株式会社 | Engine starter |
| JP6021991B1 (en) * | 2015-04-23 | 2016-11-09 | 三菱電機株式会社 | Engine starter |
| CN111120597A (en) * | 2019-12-12 | 2020-05-08 | 安徽四创电子股份有限公司 | Belt transmission device with double overload protection |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5824537U (en) * | 1981-08-12 | 1983-02-16 | 三菱農機株式会社 | transmission drive wheel |
| JPH0564554U (en) * | 1992-02-07 | 1993-08-27 | エヌ・オー・ケー・メグラスティック株式会社 | Rotation fluctuation absorbing pulley |
-
1997
- 1997-03-14 JP JP9060947A patent/JPH10252857A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5824537U (en) * | 1981-08-12 | 1983-02-16 | 三菱農機株式会社 | transmission drive wheel |
| JPH0564554U (en) * | 1992-02-07 | 1993-08-27 | エヌ・オー・ケー・メグラスティック株式会社 | Rotation fluctuation absorbing pulley |
Cited By (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6200221B1 (en) * | 1998-12-11 | 2001-03-13 | Ogura Clutch Co., Ltd. | Power transmission apparatus |
| JP2000356258A (en) * | 1999-06-14 | 2000-12-26 | Denso Corp | Power transmission |
| JP2001200906A (en) * | 2000-01-20 | 2001-07-27 | Kubota Corp | Torque transmitting device |
| US6913538B2 (en) | 2001-05-22 | 2005-07-05 | Denso Corporation | Torque transmission system |
| JP2003074586A (en) * | 2001-08-30 | 2003-03-12 | Nok Corp | Power transmission device |
| JP2007078128A (en) * | 2005-09-15 | 2007-03-29 | Toyota Motor Corp | Transmission torque limiter for vehicle |
| US8021260B2 (en) | 2005-09-15 | 2011-09-20 | Toyota Jidosha Kabushiki Kaisha | Transmitting torque limiting apparatus for vehicle |
| CN102971551A (en) * | 2010-04-14 | 2013-03-13 | 舍弗勒技术股份两合公司 | Belt pulley damper |
| US20110263365A1 (en) * | 2010-04-14 | 2011-10-27 | Schaeffler Technologies Gmbh & Co. Kg | Belt pulley damper |
| WO2011127898A1 (en) * | 2010-04-14 | 2011-10-20 | Schaeffler Technologies Gmbh & Co. Kg | Pulley damper |
| JP2013524129A (en) * | 2010-04-14 | 2013-06-17 | シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト | Pulley damper |
| US8641563B2 (en) * | 2010-04-14 | 2014-02-04 | Schaeffler Technologies Gmbh & Co. Kg | Belt pulley damper |
| KR20120070634A (en) * | 2010-12-22 | 2012-07-02 | 한라공조주식회사 | Power transmission apparatus of a compressor |
| WO2014094760A1 (en) * | 2012-12-19 | 2014-06-26 | Schaeffler Technologies AG & Co. KG | Decoupler for damping a torque transmission between a drive shaft of a motor vehicle and a belt pulley |
| US9528590B2 (en) | 2012-12-19 | 2016-12-27 | Schaeffler Technologies AG & Co. KG | Decoupler for damping a torque transmission between a drive shaft of a motor vehicle and a belt pulley |
| JP2015172348A (en) * | 2014-03-12 | 2015-10-01 | 三菱電機株式会社 | Engine starter |
| US9726138B2 (en) | 2014-03-12 | 2017-08-08 | Mitsubishi Electric Corporation | Engine starter |
| JP2016108975A (en) * | 2014-12-03 | 2016-06-20 | 三菱電機株式会社 | Engine starter |
| JP6021991B1 (en) * | 2015-04-23 | 2016-11-09 | 三菱電機株式会社 | Engine starter |
| CN111120597A (en) * | 2019-12-12 | 2020-05-08 | 安徽四创电子股份有限公司 | Belt transmission device with double overload protection |
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