JP2008232329A - Pulley unit - Google Patents

Pulley unit Download PDF

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JP2008232329A
JP2008232329A JP2007074276A JP2007074276A JP2008232329A JP 2008232329 A JP2008232329 A JP 2008232329A JP 2007074276 A JP2007074276 A JP 2007074276A JP 2007074276 A JP2007074276 A JP 2007074276A JP 2008232329 A JP2008232329 A JP 2008232329A
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coil spring
torsion coil
peripheral surface
pulley
shaft body
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Hajime Watanabe
肇 渡邉
Hideki Fujiwara
英樹 藤原
Tomoya Yamatani
知也 山谷
Masaki Maeda
雅貴 前田
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JTEKT Corp
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JTEKT Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a pulley unit having spring characteristic of a torsion coil spring excellent in absorption of rotational fluctuation in low torque area, and capable of sufficiently maintaining its strength in a high torque area wherein torque reaches a predetermined value or more. <P>SOLUTION: The pulley unit has a shaft body 30, a pulley side outer ring body 20, and a torsion coil spring 50. In the torsion coil spring 50, and the outer ring body 20 is connected with the shaft body 30 to be capable of transmitting torque with one end surface 52 of both end surfaces 52, 54 abutted with an engagement surface 26 of the outer ring body 20, and with the other end surface 54 abutted with an engagement surface 36 of the shaft body 30. An inner circumferential surface of the torsion coil spring 50 is abutted with an outer circumferential surface of the shaft body 30 at the beginning of a torque load, and a predetermined clearance is set between the outer circumferential surface of the torsion coil spring 50 and the inner circumferential surface of the outer ring body 20. An inner diameter of the outer ring body 20 is set so that the outer circumferential surface of the torsion coil spring 50 is abutted with the inner circumferential surface of the outer ring body 20 when the torque reaches the predetermined value or more and the torsion coil spring 50 is elastically expanded by a predetermined amount. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

この発明は、軸体と、この軸体の外周に同心状に配設されるプーリ側外輪体との間に回転変動を吸収する捩りコイルバネが介在されたプーリユニットに関する。   The present invention relates to a pulley unit in which a torsion coil spring that absorbs rotational fluctuation is interposed between a shaft body and a pulley-side outer ring body that is concentrically disposed on the outer periphery of the shaft body.

この種のプーリユニットにおいては、主としてエンジンの補機類（オルタネータ、エアコンディショナ用コンプレッサ、ウオーターポンプ、冷却ファン等）に用いられる。
従来、例えば、エンジンの補機類の一つであるオルタネータに採用されるプーリユニットは、エンジンのクランクシャフトのトルクが伝達される伝動ベルトが掛け渡されるプーリと、補機類としてのオルタネータのロータ（ロータ軸）に一体回転可能に連結される内軸体とを備える。
また、この種のプーリユニットにおいて、図８に示すように、プーリ１２０と内軸体１１０との間に、プーリ１２０から内軸体１１０へトルクを伝達させたり遮断させる一方向クラッチとしてのバネクラッチ１４０と、回転変動を吸収する捩りコイルバネ１５０とが介在された構造のものが知られている（特許文献１参照）。
すなわち、図８に示すプーリユニットにおいては、摩擦力によってトルク伝達する摩擦層を外周面に有するバネクラッチ１４０がプーリ１２０の内周面に沿って配置され、このバネクラッチ１４０の一方の端末部が、内軸体１１０の外周面とプーリ１２０の内周面との間に回転可能に配置された環状連結体１３０の外周面に連結され、他方の端末部が自由端をなっている。
また、捩りコイルバネ１５０は、その両端末部の端面のうち、一方の端末部の端面が環状連結体１３０に形成されたバネ座の係合面に当接し、他方の端末部の内周面が内軸体１１０の外周面に拘束された状態で、その端末部の端面が内軸体１１０の端板部に形成されたバネ座の係合面に当接した状態で、プーリ１２０と内軸体１１０とをトルク伝達可能に接続している。
そして、プーリ１２０側からのトルクが、バネクラッチ１４０、環状連結体１３０、捩りコイルバネ１５０の順を経て内軸体１１０に伝達されるようになっている。
特表２００１−５２３３２５号公報 This type of pulley unit is mainly used for engine accessories (alternator, compressor for air conditioner, water pump, cooling fan, etc.).
2. Description of the Related Art Conventionally, for example, a pulley unit employed in an alternator, which is one of engine accessories, includes a pulley around which a transmission belt to which the torque of the engine crankshaft is transmitted, and a rotor of an alternator as an accessory. An inner shaft coupled to the (rotor shaft) so as to be integrally rotatable.
In this type of pulley unit, as shown in FIG. 8, a spring clutch as a one-way clutch that transmits or blocks torque from the pulley 120 to the inner shaft body 110 between the pulley 120 and the inner shaft body 110. A structure having a structure 140 and a torsion coil spring 150 that absorbs rotational fluctuation is known (see Patent Document 1).
That is, in the pulley unit shown in FIG. 8, a spring clutch 140 having a friction layer on the outer peripheral surface for transmitting torque by friction force is disposed along the inner peripheral surface of the pulley 120, and one end portion of the spring clutch 140 is The outer end surface of the inner shaft body 110 and the inner peripheral surface of the pulley 120 are connected to the outer peripheral surface of the annular coupling body 130 rotatably arranged, and the other end portion has a free end.
In addition, the torsion coil spring 150 has an end surface of one end portion of the end surfaces of both end portions abutting against an engagement surface of a spring seat formed on the annular coupling body 130 and an inner peripheral surface of the other end portion. The pulley 120 and the inner shaft in a state in which the end surface of the end portion is in contact with the engagement surface of the spring seat formed on the end plate portion of the inner shaft body 110 while being constrained by the outer peripheral surface of the inner shaft body 110. The body 110 is connected to be able to transmit torque.
The torque from the pulley 120 side is transmitted to the inner shaft body 110 through the spring clutch 140, the annular coupling body 130, and the torsion coil spring 150 in this order.
JP-T-2001-523325

ところで、図８に示すプーリユニットにおいては、捩りコイルバネ１５０の内周面を内軸体１１０の外周面で拘束し、捩りコイルバネ１５０の外周面の殆どが拘束されることがない。このため、捩りコイルバネ１５０のバネ定数を小さくすることができ、回転変動の吸収性に優れる。この反面、捩りコイルバネ１５０の強度が不足する傾向にある。
そこで、捩りコイルバネ１５０の外周面側を拘束することが考えられるが、捩りコイルバネ１５０の外周面側を拘束すると、内周面側を拘束した場合と比べ、強度が約２倍程度となるが、バネ定数が１．５倍程度大きくなり、回転変動の吸収性が悪くなる。 By the way, in the pulley unit shown in FIG. 8, the inner peripheral surface of the torsion coil spring 150 is restrained by the outer peripheral surface of the inner shaft body 110, and most of the outer peripheral surface of the torsion coil spring 150 is not restrained. For this reason, the spring constant of the torsion coil spring 150 can be reduced, and the rotational fluctuation absorbability is excellent. On the other hand, the strength of the torsion coil spring 150 tends to be insufficient.
Therefore, it is conceivable to restrain the outer peripheral surface side of the torsion coil spring 150. However, when the outer peripheral surface side of the torsion coil spring 150 is constrained, the strength is about twice that of the case where the inner peripheral surface side is constrained. The spring constant becomes about 1.5 times larger, and the absorbability of rotational fluctuation is worsened.

この発明の目的は、前記問題点に鑑み、トルク負荷初期の低トルク域では回転変動の吸収性に優れ、トルクが所定値以上に達した高トルク域では強度を充分に保持することができる捩りコイルバネのバネ特性が得られるプーリユニットを提供することである。   In view of the above problems, an object of the present invention is torsion that is excellent in absorbability of rotational fluctuations in a low torque region at the initial stage of torque load, and can sufficiently maintain strength in a high torque region where the torque reaches a predetermined value or more. It is to provide a pulley unit that can obtain the spring characteristics of a coil spring.

前記目的を達成するために、この発明の請求項１に係るプーリユニットは、軸体と、この軸体の外周に同心状に配設されるプーリ側外輪体との間に回転変動を吸収する捩りコイルバネが介在されたプーリユニットであって、
前記捩りコイルバネは、その両端面のうち、一方の端面が前記外輪体に形成された係合面に当接し、他方の端面が前記軸体に形成された係合面に当接した状態で前記外輪体と前記軸体とをトルク伝達可能に接続し、
トルク負荷初期には前記捩りコイルバネの内周面が前記軸体の外周面に当接すると共に、前記捩りコイルバネの外周面と前記外輪体の内周面との間に所定の隙間が設定され、
トルクが所定値以上に達して前記捩りコイルバネが所定量だけ弾性的に膨張されたときには、前記捩りコイルバネの外周面が前記外輪体の内周面に当接するように前記外輪体の内径寸法が設定されていることを特徴とする。 In order to achieve the above object, a pulley unit according to claim 1 of the present invention absorbs rotational fluctuations between a shaft body and a pulley-side outer ring body disposed concentrically on the outer periphery of the shaft body. A pulley unit in which a torsion coil spring is interposed,
The torsion coil spring has one end surface abutting on an engagement surface formed on the outer ring body and the other end surface abutting on an engagement surface formed on the shaft body. Connecting the outer ring body and the shaft body so that torque can be transmitted,
At the initial stage of torque load, the inner peripheral surface of the torsion coil spring comes into contact with the outer peripheral surface of the shaft body, and a predetermined gap is set between the outer peripheral surface of the torsion coil spring and the inner peripheral surface of the outer ring body,
When the torque reaches a predetermined value or more and the torsion coil spring is elastically expanded by a predetermined amount, the inner diameter dimension of the outer ring body is set so that the outer peripheral surface of the torsion coil spring contacts the inner peripheral surface of the outer ring body It is characterized by being.

前記構成によると、プーリ側外輪体からのトルクが、捩りコイルバネを経て軸体に伝達される。そして、トルク伝達時の回動変動が捩りコイルバネの弾性変形によって吸収されるため、プーリに掛け渡されるベルトの滑り、バタツキ、異音等の発生が抑制される。
トルク負荷初期において、捩りコイルバネの内周面の一部が外輪体の内周面に当接した状態で弾性的に膨張（拡径）する。捩りコイルバネの弾性的な膨張開始からその外周面の一部が外輪体の内周面に当接する間においては、捩りコイルバネのバネ定数が小さいため、捩りコイルバネによって回転変動を良好に吸収することができる。
トルクが所定値以上に達し、捩りコイルバネの外周面の一部が外輪体の内周面に当接すると、その後の捩りコイルバネのバネ定数は、前記したトルク負荷初期の捩りコイルバネのバネ定数に比べ、１．５倍程度大きくなり、強度が約２倍程度大きくなる。このため、トルクが所定値以上に達した高トルク域では強度を充分に保持することができる。
さらに、捩りコイルバネに過大なトルクが作用したときには、外輪体の内周面によって、捩りコイルバネの外周面が拘束される。これによって、捩りコイルバネの膨張を抑制することができ捩りコイルバネの破損を防止できる。 According to the said structure, the torque from a pulley side outer ring body is transmitted to a shaft body via a torsion coil spring. And since the rotation fluctuation at the time of torque transmission is absorbed by the elastic deformation of the torsion coil spring, the occurrence of slipping, flapping, abnormal noise, etc. of the belt stretched around the pulley is suppressed.
In the initial stage of the torque load, the torsion coil spring is elastically expanded (expanded diameter) in a state where a part of the inner peripheral surface of the torsion coil spring is in contact with the inner peripheral surface of the outer ring body. Since the spring constant of the torsion coil spring is small during a period when a part of the outer peripheral surface comes into contact with the inner peripheral surface of the outer ring body from the start of elastic expansion of the torsion coil spring, the torsion coil spring can absorb rotation fluctuations well. it can.
When the torque reaches a predetermined value or more and a part of the outer peripheral surface of the torsion coil spring comes into contact with the inner peripheral surface of the outer ring body, the spring constant of the torsion coil spring thereafter is compared with the spring constant of the torsion coil spring at the initial stage of the torque load. About 1.5 times larger and the strength about twice as large. For this reason, the strength can be sufficiently maintained in a high torque region where the torque reaches a predetermined value or more.
Furthermore, when an excessive torque is applied to the torsion coil spring, the outer peripheral surface of the torsion coil spring is restrained by the inner peripheral surface of the outer ring body. Thereby, the expansion of the torsion coil spring can be suppressed, and the torsion coil spring can be prevented from being damaged.

また、この発明の請求項２に係るプーリユニットは、内軸体と、この内軸体の外周に同心状に配設されるプーリとの間に、一方向クラッチと、回転変動を吸収する捩りコイルバネとが介在されたプーリユニットであって、
前記内軸体と、前記プーリとの間には、中間筒軸体が同心状に配置され、前記内軸体の外周面と前記中間筒軸体の内周面との間に、前記一方向クラッチが配置され、前記中間筒軸体の外周面と前記プーリの内周面との間に捩りコイルバネが配置され、
前記捩りコイルバネは、その両端面のうち、一方の端面が前記プーリ側に形成された係合面に当接し、他方の端面が前記中間筒軸体側に形成された係合面に当接した状態で前記プーリと前記中間筒軸体とをトルク伝達可能に接続し、
トルク負荷初期には前記捩りコイルバネの内周面が前記中間筒軸体の外周面に当接すると共に、前記捩りコイルバネの外周面と前記プーリの内周面との間に所定の隙間が設定され、
トルクが所定値以上に達して前記捩りコイルバネが所定量だけ弾性的に膨張されたときには、前記捩りコイルバネの外周面が前記プーリの内周面に当接するように前記プーリの内径寸法が設定されていることを特徴とする。 According to a second aspect of the present invention, there is provided a pulley unit comprising: a one-way clutch between a inner shaft body and a pulley arranged concentrically on the outer periphery of the inner shaft body; A pulley unit intervening with a coil spring,
An intermediate cylindrical shaft body is concentrically disposed between the inner shaft body and the pulley, and the one-way direction is provided between an outer peripheral surface of the inner shaft body and an inner peripheral surface of the intermediate cylindrical shaft body. A clutch is disposed, a torsion coil spring is disposed between an outer peripheral surface of the intermediate cylindrical shaft body and an inner peripheral surface of the pulley;
The torsion coil spring is in a state in which one end face of the both end faces comes into contact with an engagement face formed on the pulley side, and the other end face comes into contact with an engagement face formed on the intermediate cylinder shaft side. The pulley and the intermediate cylinder shaft body are connected so as to be able to transmit torque,
At the initial stage of torque load, the inner peripheral surface of the torsion coil spring contacts the outer peripheral surface of the intermediate cylindrical shaft body, and a predetermined gap is set between the outer peripheral surface of the torsion coil spring and the inner peripheral surface of the pulley.
When the torque reaches a predetermined value or more and the torsion coil spring is elastically expanded by a predetermined amount, the inner diameter of the pulley is set so that the outer peripheral surface of the torsion coil spring contacts the inner peripheral surface of the pulley. It is characterized by being.

前記構成によると、プーリ側からのトルクが、捩りコイルバネ、中間筒軸体、一方向クラッチの順を経て内軸体に伝達される。そして、トルク伝達時の回動変動が捩りコイルバネの弾性変形によって吸収されるため、ベルトの滑り、バタツキ、異音等の発生が抑制される。
トルク負荷初期において、捩りコイルバネの内周面の一部が中間筒軸体の外周面に当接した状態で弾性的に膨張（拡径）する。捩りコイルバネの弾性的な膨張開始からその外周面の一部がプーリの内周面に当接する間においては、捩りコイルバネのバネ定数が小さいため、捩りコイルバネによって回転変動を良好に吸収することができる。
トルクが所定値以上に達し、捩りコイルバネの外周面の一部がプーリの内周面に当接すると、その後の捩りコイルバネのバネ定数は、前記したトルク負荷初期の捩りコイルバネのバネ定数に比べ、１．５倍程度大きくなり、強度が約２倍程度大きくなる。このため、トルクが所定値以上に達した高トルク域では強度を充分に保持することができる。
さらに、捩りコイルバネに過大なトルクが作用したときには、プーリの内周面によって、捩りコイルバネの外周面が拘束される。これによって、捩りコイルバネの膨張を抑制することができ、捩りコイルバネの破損を防止できる。
また、プーリ側からのトルクが、捩りコイルバネ、中間筒軸体、一方向クラッチの順を経て内軸体に伝達されるため、プーリ側から急激なトルクによる衝撃を捩りコイルバネによって良好に吸収することができ、一方向クラッチを前記衝撃から保護することができる。これによって、一方向クラッチの耐久性の向上を図ることができる。 According to the said structure, the torque from the pulley side is transmitted to an inner shaft body through the order of a torsion coil spring, an intermediate cylinder shaft body, and a one-way clutch. And since the rotation fluctuation | variation at the time of torque transmission is absorbed by the elastic deformation of a torsion coil spring, generation | occurrence | production of the slip of a belt, flutter, abnormal noise, etc. is suppressed.
In the initial stage of the torque load, the torsion coil spring is elastically expanded (expanded diameter) in a state where a part of the inner peripheral surface of the torsion coil spring is in contact with the outer peripheral surface of the intermediate cylindrical shaft body. Since the spring constant of the torsion coil spring is small while a part of the outer peripheral surface comes into contact with the inner peripheral surface of the pulley from the start of elastic expansion of the torsion coil spring, the torsion coil spring can absorb rotation fluctuations well. .
When the torque reaches a predetermined value or more and a part of the outer peripheral surface of the torsion coil spring comes into contact with the inner peripheral surface of the pulley, the spring constant of the torsion coil spring thereafter is compared with the spring constant of the torsion coil spring at the initial stage of torque load. It becomes about 1.5 times larger and the strength becomes about twice as large. For this reason, the strength can be sufficiently maintained in a high torque region where the torque reaches a predetermined value or more.
Further, when an excessive torque is applied to the torsion coil spring, the outer peripheral surface of the torsion coil spring is restrained by the inner peripheral surface of the pulley. Thereby, the expansion of the torsion coil spring can be suppressed, and the torsion coil spring can be prevented from being damaged.
In addition, the torque from the pulley side is transmitted to the inner shaft through the torsion coil spring, the intermediate cylinder shaft, and the one-way clutch in order, so that the shock due to sudden torque from the pulley side can be absorbed well by the torsion coil spring. And the one-way clutch can be protected from the impact. Thereby, the durability of the one-way clutch can be improved.

次に、この発明を実施するための最良の形態を実施例にしたがって説明する。   Next, the best mode for carrying out the present invention will be described with reference to examples.

（実施例１）
この発明の実施例１を図１〜図７にしたがって説明する。
図１はこの発明の実施例１に係るプーリユニットを示す側断面図である。図２は図１のＩＩ−ＩＩ線に基づく横断面図である。図３は図１のＩＩＩ−ＩＩＩ線に基づく横断面図である。図４は捩りコイルバネと中間筒軸体のバネ座との関係を分離して示す斜視図である。図５はトルク負荷初期の捩りコイルバネの内周面が内軸体の外周面に当接した状態をを示す説明図である。図６はトルクが所定値以上に達して捩りコイルバネの外周面がプーリの内周面に当接した状態をを示す説明図である。図７は捩りコイルバネのねじれ角を横軸で表し負荷トルクを縦軸で表したバネ特性を示す説明図である。 Example 1
A first embodiment of the present invention will be described with reference to FIGS.
1 is a side sectional view showing a pulley unit according to Embodiment 1 of the present invention. 2 is a cross-sectional view based on the line II-II in FIG. 3 is a cross-sectional view based on the line III-III in FIG. FIG. 4 is a perspective view showing the relationship between the torsion coil spring and the spring seat of the intermediate cylinder shaft separately. FIG. 5 is an explanatory view showing a state in which the inner peripheral surface of the torsion coil spring in the initial stage of torque load is in contact with the outer peripheral surface of the inner shaft body. FIG. 6 is an explanatory view showing a state where the torque reaches a predetermined value or more and the outer peripheral surface of the torsion coil spring is in contact with the inner peripheral surface of the pulley. FIG. 7 is an explanatory diagram showing spring characteristics in which the torsion angle of the torsion coil spring is represented on the horizontal axis and the load torque is represented on the vertical axis.

図１に示すように、この実施例１に係るプーリユニットは、車載用エンジンの補機類の一つであるオルタネータに使用される場合を例示するものであり、内軸体１０、プーリ（この発明の請求項１のプーリ側外輪体に相当する）２０、中間筒軸体（この発明の請求項１の軸体に相当する）３０、一方向クラッチ４０、捩りコイルバネ５０、転がり軸受７０、７５及びすべり軸受８０を備える。   As shown in FIG. 1, the pulley unit according to the first embodiment exemplifies a case where the pulley unit is used in an alternator that is one of auxiliary components of an in-vehicle engine. (Corresponding to the pulley-side outer ring body of claim 1 of the present invention) 20, intermediate cylinder shaft body (corresponding to the shaft body of claim 1 of the present invention) 30, one-way clutch 40, torsion coil spring 50, rolling bearings 70, 75 And a plain bearing 80.

図１に示すように、内軸体１０は、オルタネータのロータのロータ軸（図示しない）の先端部軸回りに取り付けられる筒軸状に形成されている。そして、内軸体１０の内孔の軸方向略中央部には、ロータ軸の先端側に形成された雄ねじ部に締め付けられる雌ねじ１２が形成され、内軸体１０の内孔の一端側開口部には、締付工具が嵌合可能な締付部１３が形成されている。
また、この実施例１において、内軸体１０は、一方向クラッチ４０と転がり軸受７５のそれぞれの内輪体を構成している。 As shown in FIG. 1, the inner shaft body 10 is formed in a cylindrical shaft shape that is attached around a tip end shaft of a rotor shaft (not shown) of a rotor of an alternator. A female screw 12 fastened to a male screw portion formed on the tip end side of the rotor shaft is formed at a substantially central portion in the axial direction of the inner hole of the inner shaft body 10, and an opening on one end side of the inner hole of the inner shaft body 10 is formed. A tightening portion 13 into which a tightening tool can be fitted is formed.
Further, in the first embodiment, the inner shaft body 10 constitutes the inner ring bodies of the one-way clutch 40 and the rolling bearing 75.

図１に示すように、外輪体としてのプーリ２０は、内軸体１０の外周に同心に配置され、その一端側内周面が転がり軸受７０によって内軸体１０の外周に回転可能に支持され、他端側内周面がすべり軸受（ブッシュ）８０によって、次に詳述する中間筒軸体３０の外筒部３３外周に回転可能に支持される。なお、転がり軸受７０として深溝玉軸受が用いられ、その外輪７１がプーリ２０の一端側内周面に圧入固定され、内輪７２が内軸体１０の外周面に圧入固定されている。そして、外輪７１と内輪７２の両軌道面の間に複数個の玉７３が保持器によって保持された状態で転動可能に配設されている。   As shown in FIG. 1, the pulley 20 as an outer ring body is concentrically disposed on the outer periphery of the inner shaft body 10, and one end side inner peripheral surface thereof is rotatably supported on the outer periphery of the inner shaft body 10 by a rolling bearing 70. The other end side inner peripheral surface is rotatably supported by a slide bearing (bush) 80 on the outer cylindrical portion 33 outer periphery of the intermediate cylindrical shaft body 30 described in detail below. A deep groove ball bearing is used as the rolling bearing 70, the outer ring 71 is press-fitted and fixed to the inner peripheral surface of one end of the pulley 20, and the inner ring 72 is press-fitted and fixed to the outer peripheral surface of the inner shaft body 10. A plurality of balls 73 are arranged between the raceways of the outer ring 71 and the inner ring 72 so as to be able to roll while being held by a cage.

プーリ２０の外周面には伝動ベルト８が掛け渡される断面波形状のベルト溝２１が形成されている。なお、伝動ベルト８は、エンジンのクランクシャフトのプーリに掛け渡され、クランクシャフトのトルクをプーリ２０に伝達するようになっている。
また、転がり軸受７０の外輪７１に隣接するプーリ２０の内周面の部分には、後に詳述する捩りコイルバネ５０の一方の端末巻回部５１を支承する螺旋形状の支承面を有する環状のバネ座２５が突設され、このバネ座２５の端部には、一方の端末巻回部５１の端面５２に当接する係合面２６が形成されている（図２参照）。なお、バネ座２５の支承面と反対側の面は、転がり軸受７０の外輪７１の奥側端面に接するストッパとして機能している。 A belt groove 21 having a corrugated cross section is formed on the outer peripheral surface of the pulley 20 so as to span the transmission belt 8. The transmission belt 8 is stretched around a pulley of the crankshaft of the engine, and transmits the torque of the crankshaft to the pulley 20.
An annular spring having a spiral bearing surface that supports one end winding portion 51 of a torsion coil spring 50 described in detail later is provided on the inner circumferential surface of the pulley 20 adjacent to the outer ring 71 of the rolling bearing 70. A seat 25 is protruded, and an engagement surface 26 that abuts against the end surface 52 of one terminal winding portion 51 is formed at the end of the spring seat 25 (see FIG. 2). Note that the surface of the spring seat 25 opposite to the bearing surface functions as a stopper that contacts the back end surface of the outer ring 71 of the rolling bearing 70.

図１と図４に示すように、軸体としての中間筒軸体３０は、筒軸部３１と、この筒軸部３１の一端部外周面の半径方向に突出された端板部３２と、この端板部３２の外周縁から筒軸部３１に平行して折り返し状に形成された外筒部３３とを一体に備えている。
そして、中間筒軸体３０は、その筒軸部３１において、内軸体１０と、プーリ２０との間に同心状に配置されている。
また、中間筒軸体３０の端板部３２の内側面には、捩りコイルバネ５０の他方の端末巻回部５３を支承する螺旋形状の支承面を有するバネ座３５、このバネ座３５の端部には、他方の端末巻回部５３の端面５４に当接する係合面３６が形成されている。
また、中間筒軸体３０の外筒部３３の内径寸法は、プーリ２０の内径寸法Ｄｏと略同じ大きさに設定されている。 As shown in FIGS. 1 and 4, the intermediate cylindrical shaft body 30 as a shaft body includes a cylindrical shaft portion 31, an end plate portion 32 protruding in the radial direction of the outer peripheral surface of one end portion of the cylindrical shaft portion 31, and The end plate portion 32 is integrally provided with an outer tube portion 33 formed in a folded shape in parallel with the tube shaft portion 31 from the outer peripheral edge.
The intermediate cylindrical shaft body 30 is disposed concentrically between the inner shaft body 10 and the pulley 20 in the cylindrical shaft portion 31.
Further, on the inner surface of the end plate portion 32 of the intermediate cylindrical shaft body 30, a spring seat 35 having a spiral support surface for supporting the other end winding portion 53 of the torsion coil spring 50, an end portion of the spring seat 35 is provided. Is formed with an engagement surface 36 that contacts the end surface 54 of the other terminal winding portion 53.
Further, the inner diameter of the outer tube portion 33 of the intermediate cylinder shaft 30 is set to substantially the same size as the inner diameter D o of the pulley 20.

図１と図２に示すように、中間筒軸体３０の筒軸部３１は、一方向クラッチ４０と転がり軸受７５のそれぞれの外輪体を構成している。そして、内軸体１０の外周面と中間筒軸体３０の筒軸部３１の内周面との間の環状空間に一方向クラッチ４０と、転がり軸受７５の複数個の玉７６とがそれぞれ配設されている。   As shown in FIGS. 1 and 2, the cylindrical shaft portion 31 of the intermediate cylindrical shaft body 30 constitutes the outer ring bodies of the one-way clutch 40 and the rolling bearing 75. The one-way clutch 40 and the plurality of balls 76 of the rolling bearing 75 are respectively arranged in the annular space between the outer peripheral surface of the inner shaft body 10 and the inner peripheral surface of the cylindrical shaft portion 31 of the intermediate cylindrical shaft body 30. It is installed.

図１と図２に示すように、一方向クラッチ４０は、内軸体１０とプーリ２０との間の環状空間の軸方向中央領域において、円周方向に所定間隔を隔てて配設された複数のローラ４８と、これらローラ４８をロック方向に個別に付勢するコイルバネ４９と、複数のローラ４８及びコイルバネ４９を保持する保持器４１とを備えている。
すなわち、内軸体１０とプーリ２０との対向周面の間には複数（図２では８個）のくさび状空間が周方向に所定間隔を隔てて形成され、これら複数のくさび空間には、これと同数のローラ４８と、これら各ローラ４８をロック方向（くさび空間の狭い側）に個別に付勢するコイルバネ４９とが保持器４１の各ポケットに収納された状態でそれぞれ配設されている。 As shown in FIGS. 1 and 2, the one-way clutch 40 includes a plurality of one-way clutches 40 arranged at predetermined intervals in the circumferential direction in the axial central region of the annular space between the inner shaft body 10 and the pulley 20. , A coil spring 49 for individually urging the rollers 48 in the locking direction, and a holder 41 for holding the plurality of rollers 48 and the coil springs 49.
That is, a plurality (eight in FIG. 2) of wedge-shaped spaces are formed at predetermined intervals in the circumferential direction between the opposed peripheral surfaces of the inner shaft body 10 and the pulley 20, and in the plurality of wedge spaces, The same number of rollers 48 and coil springs 49 for individually urging each of the rollers 48 in the locking direction (the narrow side of the wedge space) are disposed in respective pockets of the cage 41. .

この実施例１において、内軸体１０の外周面には、複数のくさび空間を形成するために、複数のくさび空間と同数の平坦面（又は曲面）のカム面１５が周方向に形成され、これによって内軸体１０の外周面があたかも正多角形（図２では正８角形）をなす一方、プーリ２０の内周面は円形をなしている。
また、保持器４１の各柱部４５の一側面（くさび空間の狭い側に対向する面）に突設された突起４６には、コイルバネ４９の基端巻回部が嵌挿され、コイルバネ４９の先端巻回部がローラ４８の外周面に当接して、ローラ４８を内軸体１０のカム面１５とプーリ２０の内周面とで形成されるくさび状空間の狭い側（ロック状態となる側）に弾発付勢している。なお、コイルバネ４９はバネ線材が楕円形状、矩形形状等に巻回されて形成されている。 In Example 1, in order to form a plurality of wedge spaces on the outer peripheral surface of the inner shaft body 10, the same number of flat surfaces (or curved surfaces) as the plurality of wedge spaces are formed in the circumferential direction. As a result, the outer peripheral surface of the inner shaft 10 forms a regular polygon (a regular octagon in FIG. 2), while the inner peripheral surface of the pulley 20 is circular.
Further, a proximal end winding portion of the coil spring 49 is fitted and inserted into a protrusion 46 provided on one side surface (a surface facing the narrow side of the wedge space) of each column portion 45 of the cage 41. The winding end of the tip abuts on the outer peripheral surface of the roller 48, and the roller 48 is narrow on the narrow side of the wedge-shaped space formed by the cam surface 15 of the inner shaft body 10 and the inner peripheral surface of the pulley 20 (the side in the locked state). ). The coil spring 49 is formed by winding a spring wire into an elliptical shape, a rectangular shape, or the like.

図３と図４に示すように、捩りコイルバネ５０は、平板のバネ線材が螺旋状に巻回されて形成され、中間筒軸体３０の外周面とプーリ２０の内周面との間の環状空間に配置されている。そして、捩りコイルバネ５０の一方の端末巻回部５１がプーリ２０のバネ座２５に支承された状態で、一方の端末巻回部５１の端面５２がプーリ２０のバネ座２５の係合面２６に当接して係合している。
また、捩りコイルバネ５０の他方の端末巻回部５３が中間筒軸体３０の端板部３２のバネ座３５に支承された状態で、他方の端末巻回部５３の端面５４が端板部３２のバネ座３５の係合面３６に当接して係合している。
そして、捩りコイルバネ５０によって、プーリ２０と中間筒軸体３０とがトルク伝達可能に接続され、一方向クラッチ４０によって中間筒軸体３０と内筒体１０とがトルク伝達可能に接続される。つまりプーリ２０側からのトルクが捩りコイルバネ５０、中間筒軸体３０、一方向クラッチ４０の順を経て内筒体１０に伝達される。 As shown in FIGS. 3 and 4, the torsion coil spring 50 is formed by spirally winding a flat spring wire, and has an annular shape between the outer peripheral surface of the intermediate cylindrical shaft body 30 and the inner peripheral surface of the pulley 20. Arranged in space. Then, in a state where one terminal winding portion 51 of the torsion coil spring 50 is supported by the spring seat 25 of the pulley 20, the end surface 52 of one terminal winding portion 51 is on the engagement surface 26 of the spring seat 25 of the pulley 20. Abut and engage.
In addition, in a state where the other terminal winding portion 53 of the torsion coil spring 50 is supported by the spring seat 35 of the end plate portion 32 of the intermediate cylindrical shaft body 30, the end surface 54 of the other terminal winding portion 53 is the end plate portion 32. The abutment surface 36 of the spring seat 35 is in contact with and engaged.
Then, the torsion coil spring 50 connects the pulley 20 and the intermediate cylindrical shaft body 30 so as to transmit torque, and the one-way clutch 40 connects the intermediate cylindrical shaft body 30 and the inner cylindrical body 10 so as to transmit torque. That is, the torque from the pulley 20 side is transmitted to the inner cylindrical body 10 through the torsion coil spring 50, the intermediate cylindrical shaft body 30, and the one-way clutch 40.

この実施例１において、中間筒軸体３０の筒軸部３１の外径寸法Ｄｉ、プーリ２０の内径寸法（及び中間筒軸体３０の外筒部３３の内径寸法）Ｄ０、捩りコイルバネ５０のコイル平均径寸法Ｄｍは、次の式（１）〜（１６）に基づいて設定されている。
ここで、捩りコイルバネ５０のねじれ角をφ、巻き数をｎ、バネ定数をＫ、トルクをＴとした場合、次の式（１）〜式（９）によって、捩りコイルバネ５０のコイル平均膨張量（限界膨張量）ΔＤｍが計算される。 In the first embodiment, the outer diameter dimension D i of the cylinder shaft portion 31 of the intermediate cylinder shaft body 30, the inner diameter dimension of the pulley 20 (and the inner diameter dimension of the outer cylinder portion 33 of the intermediate cylinder shaft body 30) D 0 , and the torsion coil spring 50 The coil average diameter dimension Dm is set based on the following formulas (1) to (16).
Here, when the twist angle of the torsion coil spring 50 is φ, the number of turns is n, the spring constant is K, and the torque is T, the average coil expansion amount of the torsion coil spring 50 is expressed by the following equations (1) to (9). (Limit expansion amount) ΔD m is calculated.

Figure 2008232329

Figure 2008232329
 式（２）から次の式（３）が成り立つ。
Figure 2008232329
Figure 2008232329
Figure 2008232329
 From the expression (2), the following expression (3) is established.
Figure 2008232329

また、図５に示すように、捩りコイルバネ５０の内周面の一部５０ａが中間筒軸体３０の筒軸部３１の外周面に当接する捩りコイルバネ５０の弾性的な膨張開始から、図６に示すように、捩りコイルバネ５０の外周面の一部５０ｂがプーリ２０の内周面に当接する間の捩りコイルバネ５０のバネ定数Ｋは、次の式（４）によって得られる。

Figure 2008232329
式（３）及び式（４）によって、次の式（５）が成り立つ。
Figure 2008232329
 Further, as shown in FIG. 5, from the start of elastic expansion of the torsion coil spring 50 in which a part 50 a of the inner peripheral surface of the torsion coil spring 50 abuts on the outer peripheral surface of the cylindrical shaft portion 31 of the intermediate cylindrical shaft body 30. As shown, the spring constant K of the torsion coil spring 50 while the part 50b of the outer peripheral surface of the torsion coil spring 50 abuts against the inner peripheral surface of the pulley 20 is obtained by the following equation (4).
Figure 2008232329
 The following equation (5) is established by the equations (3) and (4).
Figure 2008232329

捩りコイルバネ５０の断面係数をｚ、バネ線厚寸法をｈ、バネ線幅寸法をｂとしたときの膨張時の応力σは、次の式（６）よって得られる。

Figure 2008232329
さらに、二次モーメントＩは次の式（７）によって得られる。
Figure 2008232329
 式（５）（６）及び（７）によって次の式（８）が成り立つ。
Figure 2008232329
 The stress σ during expansion when the section modulus of the torsion coil spring 50 is z, the spring wire thickness dimension is h, and the spring line width dimension is b is obtained by the following equation (6).
Figure 2008232329
 Further, the second moment I is obtained by the following equation (7).
Figure 2008232329
 The following equation (8) is established by equations (5), (6), and (7).
Figure 2008232329

そして、許容応力（バネ線材引張強度）を０．４８σＢとしたときに、次の式（９）が成り立ち、コイル平均膨張量（限界膨張量）がΔＤｍが計算される。

Figure 2008232329
When the allowable stress (spring wire tensile strength) is 0.48σ B , the following equation (9) is established, and ΔD m is calculated as the coil average expansion amount (limit expansion amount).
Figure 2008232329

次に、図６に示すように、捩りコイルバネ５０の外周面の一部５０ｂがプーリ２０の内周面に当接した後の捩りコイルバネ５０のコイル平均膨張量（限界膨張量）ΔＤｍが前記した式（３）及び次の式（１０）〜（１３）によって計算される。
先ず、捩りコイルバネ５０の外周面の一部５０ｂがプーリ２０の内周面に当接した後の捩りコイルバネ５０のバネ定数ＫＫは、次の式（１０）によって得られる。

Figure 2008232329
Next, as shown in FIG. 6, the coil average expansion amount (limit expansion amount) ΔD m of the torsion coil spring 50 after the part 50 b of the outer peripheral surface of the torsion coil spring 50 contacts the inner peripheral surface of the pulley 20 is It is calculated by the following equation (3) and the following equations (10) to (13).
First, the spring constant K K of the torsion coil spring 50 after the portion 50b of the outer peripheral surface of the torsion coil spring 50 is in contact with the inner peripheral surface of the pulley 20 is obtained by the following equation (10).
Figure 2008232329

また、膨張時の応力σＫは、次の式（１１）よって得られる。

Figure 2008232329
Further, the stress σ K at the time of expansion is obtained by the following equation (11).
Figure 2008232329

式（３）（７）（１０）及び（１１）から次の式（１２）が成り立つ。

Figure 2008232329
From the equations (3), (7), (10) and (11), the following equation (12) is established.
Figure 2008232329

そして、許容応力（バネ線材引張強度）をσＢとしたときに、次の式（１３）が成り立ち、コイル平均膨張量（限界膨張量）がΔＤｍが計算される。

Figure 2008232329
Then, when the allowable stress (spring wire tensile strength) is σ B , the following equation (13) is established, and ΔD m is calculated as the coil average expansion amount (limit expansion amount).
Figure 2008232329

そして、この実施例１においては、前記した式（１）〜（１３）に基づき、中間筒軸体３０の筒軸部３１の外径寸法Ｄｉ、プーリ２０の内径寸法Ｄ０、捩りコイルバネ５０のコイル平均径寸法Ｄｍが、次の式（１４）〜（１６）を成立する範囲内で設定されている。

Figure 2008232329

Figure 2008232329
Figure 2008232329
 In the first embodiment, the outer diameter dimension D i of the cylindrical shaft portion 31 of the intermediate cylindrical shaft body 30, the inner diameter dimension D 0 of the pulley 20, and the torsion coil spring 50 are based on the above formulas (1) to (13). Coil average diameter dimension Dm is set within a range in which the following equations (14) to (16) are satisfied.
Figure 2008232329
Figure 2008232329
Figure 2008232329

すなわち、この実施例１において、図５に示すように、トルク負荷初期には捩りコイルバネ５０の内周面の一部（端面５２から略２７０度変位した部分）５０ａが中間筒軸体３０の筒軸部３１外周面に当接すると共に、捩りコイルバネ５０の外周面とプーリ２０の内周面との間に所定の隙間が設定されている。
そして、捩りコイルバネ５０の弾性的な膨張開始から、図６に示すように、捩りコイルバネ５０の外周面の一部（端面５２から略９０度変位した部分）５０ｂがプーリ２０の内周面に当接する間においては、捩りコイルバネ５０は、破損されることなく、かつ式（４）に示す小さいバネ定数において、許容される弾性変形の範囲内で膨張し得るように設定されている。 That is, in the first embodiment, as shown in FIG. 5, at the initial stage of torque load, a part of the inner peripheral surface of the torsion coil spring 50 (part displaced by approximately 270 degrees from the end surface 52) 50 a is the cylinder of the intermediate cylindrical shaft body 30. While contacting the outer peripheral surface of the shaft portion 31, a predetermined gap is set between the outer peripheral surface of the torsion coil spring 50 and the inner peripheral surface of the pulley 20.
Then, from the start of elastic expansion of the torsion coil spring 50, as shown in FIG. 6, a part of the outer peripheral surface of the torsion coil spring 50 (a portion displaced by approximately 90 degrees from the end surface 52) 50b contacts the inner peripheral surface of the pulley 20. During the contact, the torsion coil spring 50 is set so as not to be damaged and to expand within an allowable elastic deformation range with a small spring constant shown in the equation (4).

また、トルクが所定値以上に達して捩りコイルバネ５０が所定量だけ弾性的に膨張されたときには、図６に示すように、捩りコイルバネ５０の外周面の一部５０ｂがプーリ２０の内周面に当接するように設定されている。
そして、図６に示すように、捩りコイルバネ５０は、その外周面の一部５０ｂがプーリ２０の内周面に当接した後、引き続いて、捩りコイルバネ５０は、その外周面の略全域がプーリ２０の内周面に接触するまでの間において、式（１０）に示す大きいバネ定数（トルク負荷初期の捩りコイルバネ５０のバネ定数に比べ、１．５倍程度大きいバネ定数）において、許容される弾性変形の範囲内で膨張し得るように設定されている（図７参照）。 When the torque reaches a predetermined value or more and the torsion coil spring 50 is elastically expanded by a predetermined amount, a part 50b of the outer peripheral surface of the torsion coil spring 50 is formed on the inner peripheral surface of the pulley 20, as shown in FIG. It is set to abut.
Then, as shown in FIG. 6, after the part 50b of the outer peripheral surface of the torsion coil spring 50 comes into contact with the inner peripheral surface of the pulley 20, the torsion coil spring 50 continues to have a substantially entire area of the outer peripheral surface of the pulley. 20 until the contact with the inner peripheral surface of 20 is allowed in the large spring constant shown in Formula (10) (a spring constant about 1.5 times larger than the spring constant of the torsion coil spring 50 in the initial stage of torque load). It is set so that it can expand within the range of elastic deformation (see FIG. 7).

上述したように構成されるこの実施例１に係るプーリユニットにおいて、プーリ２０側からのトルクが、捩りコイルバネ５０、中間筒軸体３０、一方向クラッチ４０の順を経て内軸体１０に伝達される。そして、トルク伝達時の回動変動が捩りコイルバネ５０の弾性変形によって吸収されるため、ベルトの滑り、バタツキ、異音等の発生が抑制される。   In the pulley unit according to the first embodiment configured as described above, torque from the pulley 20 side is transmitted to the inner shaft body 10 through the torsion coil spring 50, the intermediate cylindrical shaft body 30, and the one-way clutch 40 in this order. The And since the rotation fluctuation | variation at the time of torque transmission is absorbed by the elastic deformation of the torsion coil spring 50, generation | occurrence | production of a belt slip, flapping, abnormal noise, etc. is suppressed.

トルク負荷初期において、図５に示すように、捩りコイルバネ５０の内周面の一部５０ａが中間筒軸体３０の筒軸部３１外周面に当接した状態で弾性的に膨張（拡径）する。捩りコイルバネ５０の弾性的な膨張開始からその外周面の一部５０ｂがプーリ２０の内周面に当接する間においては、捩りコイルバネ５０のバネ定数が小さい。このため、小さいバネ定数の捩りコイルバネ５０によって回転変動を良好に吸収することができる。
トルクが所定値以上に達し、図６に示すように、捩りコイルバネ５０の外周面の一部５０ｂがプーリ２０の内周面に当接すると、その後の捩りコイルバネ５０のバネ定数は、前記したトルク負荷初期の捩りコイルバネ５０のバネ定数に比べ、１．５倍程度大きくなり、強度が約２倍程度大きくなる。このため、トルクが所定値以上に達した高トルク域では強度を充分に保持することができる。
さらに、捩りコイルバネ５０に過大なトルクが作用したときには、プーリ２０の内周面によって、捩りコイルバネ５０の外周面が拘束される。これによって、捩りコイルバネ５０の膨張を抑制することができ破損を防止できる。 In the initial stage of torque load, as shown in FIG. 5, the inner circumferential surface portion 50 a of the torsion coil spring 50 is elastically expanded (expanded diameter) in a state of being in contact with the outer circumferential surface of the cylindrical shaft portion 31 of the intermediate cylindrical shaft body 30. To do. The spring constant of the torsion coil spring 50 is small during the period from the start of elastic expansion of the torsion coil spring 50 until a part 50b of the outer peripheral surface contacts the inner peripheral surface of the pulley 20. For this reason, the rotational fluctuation can be favorably absorbed by the torsion coil spring 50 having a small spring constant.
When the torque reaches a predetermined value or more and a part 50b of the outer peripheral surface of the torsion coil spring 50 comes into contact with the inner peripheral surface of the pulley 20 as shown in FIG. 6, the spring constant of the torsion coil spring 50 thereafter is the torque described above. Compared with the spring constant of the torsion coil spring 50 at the initial stage of loading, the spring constant is about 1.5 times larger and the strength is about twice as large. For this reason, the strength can be sufficiently maintained in a high torque region where the torque reaches a predetermined value or more.
Furthermore, when an excessive torque is applied to the torsion coil spring 50, the outer peripheral surface of the torsion coil spring 50 is restrained by the inner peripheral surface of the pulley 20. Thereby, the expansion of the torsion coil spring 50 can be suppressed, and damage can be prevented.

また、プーリ２０の回転速度が内軸体１０の回転速度よりも遅くなると、一方向クラッチ４０のローラ４８がロック位置から外れてくさび状空間の広い側へ移動してフリー状態に切替わる。これにより、プーリ２０からのトルクの伝達が遮断されるが、オルタネータのロータに対応する内軸体１０はオルタネータのロータが大きな回転慣性を有するため、遮断以降も回転を継続する。
例えば、エンジンを停止したときには、この停止にともなってプーリ（外輪体）の回転が停止し、内軸体１０はオルタネータのロータの回転慣性力が消失するまで回転を継続する。 Further, when the rotation speed of the pulley 20 becomes slower than the rotation speed of the inner shaft body 10, the roller 48 of the one-way clutch 40 moves out of the lock position and moves to the wider side of the wedge-shaped space and switches to the free state. Thereby, transmission of torque from the pulley 20 is interrupted, but the inner shaft body 10 corresponding to the rotor of the alternator continues to rotate after the interruption because the rotor of the alternator has a large rotational inertia.
For example, when the engine is stopped, the pulley (outer ring body) stops rotating along with the stop, and the inner shaft body 10 continues rotating until the rotational inertia force of the rotor of the alternator disappears.

また、この実施例１において、プーリ２０側からのトルクが、捩りコイルバネ５０、中間筒軸体３０、一方向クラッチ４０の順を経て内軸体１０に伝達される。このため、プーリ２０側から急激なトルクが作用したときでも、その衝撃を捩りコイルバネ５０によって吸収することができる。このため、一方向クラッチ４０のローラ４８やくさび空間の内壁面（カム面１５及び中間筒軸体３０の筒軸部３１内周面）を前記衝撃から保護することができる。これによって、一方向クラッチ４０の耐久性の向上を図ることができる。   In the first embodiment, the torque from the pulley 20 side is transmitted to the inner shaft body 10 through the torsion coil spring 50, the intermediate cylindrical shaft body 30, and the one-way clutch 40 in this order. For this reason, even when a sudden torque is applied from the pulley 20 side, the impact can be absorbed by the torsion coil spring 50. For this reason, the roller 48 of the one-way clutch 40 and the inner wall surface of the wedge space (the cam surface 15 and the inner peripheral surface of the cylindrical shaft portion 31 of the intermediate cylindrical shaft body 30) can be protected from the impact. Thereby, the durability of the one-way clutch 40 can be improved.

なお、この発明は前記実施例１に限定するものではない。
例えば、前記実施例１においては、内軸体１０の外周面にカム面１５を形成して中間筒軸体３０の筒軸部３１内周面とカム面１５によってくさび状空間を形成したが、中間筒軸体３０の筒軸部３１内周面にカム面を形成し、内軸体１０の外周面とカム面によってくさび状空間を形成してもよい。
但し、この場合には、一方向クラッチ４０の保持器４１は、中間筒軸体３０の筒軸部３１内周面に固定（例えば圧入固定）される。
また、前記実施例１においては、複数のくさび状空間とローラ４８とを備えた一方向クラッチ４０である場合を例示したが、バネクラッチによって一方向クラッチが構成される場合においても実施可能である。
さらに、一方向クラッチが配設されないプーリユニットであっても、実施可能である。
また、この発明においては、エンジンの補機類の一つであるオルタネータに対応するプーリユニット以外のプーリユニット、例えば、エアコンディショナ用コンプレッサ、ウオーターポンプ、冷却ファン等のエンジンの補機類に対応するプーリユニットとして使用可能である。 The present invention is not limited to the first embodiment.
For example, in the first embodiment, the cam surface 15 is formed on the outer peripheral surface of the inner shaft body 10, and the wedge-shaped space is formed by the inner peripheral surface of the cylindrical shaft portion 31 of the intermediate cylindrical shaft body 30 and the cam surface 15. A cam surface may be formed on the inner peripheral surface of the cylindrical shaft portion 31 of the intermediate cylindrical shaft body 30, and a wedge-shaped space may be formed by the outer peripheral surface of the inner shaft body 10 and the cam surface.
However, in this case, the retainer 41 of the one-way clutch 40 is fixed (for example, press-fitted and fixed) to the inner peripheral surface of the cylindrical shaft portion 31 of the intermediate cylindrical shaft body 30.
In the first embodiment, the case of the one-way clutch 40 having a plurality of wedge-shaped spaces and the rollers 48 is illustrated. However, the present invention can also be implemented when the one-way clutch is configured by a spring clutch. .
Furthermore, even a pulley unit in which a one-way clutch is not provided can be implemented.
Also, in the present invention, it corresponds to a pulley unit other than a pulley unit corresponding to an alternator which is one of engine auxiliary machines, for example, an engine auxiliary machine such as an air conditioner compressor, a water pump and a cooling fan. It can be used as a pulley unit.

この発明の実施例１に係るプーリユニットを示す側断面図である。It is a sectional side view which shows the pulley unit which concerns on Example 1 of this invention. 同じく図１のＩＩ−ＩＩ線に基づく横断面図である。It is a transverse cross section similarly based on the II-II line of FIG. 同じく図１のＩＩＩ−ＩＩＩ線に基づく横断面図である。It is a transverse cross section similarly based on the III-III line of FIG. 同じく捩りコイルバネと中間筒軸体のバネ座との関係を分離して示す斜視図である。It is a perspective view which isolate | separates and similarly shows the relationship between a torsion coil spring and the spring seat of an intermediate cylinder shaft. 同じくトルク負荷初期の捩りコイルバネの内周面が内軸体の外周面に当接した状態をを示す説明図である。Similarly, it is explanatory drawing which shows the state which the inner peripheral surface of the torsion coil spring of the torque load initial stage contact | abutted to the outer peripheral surface of the inner shaft body. 同じくトルクが所定値以上に達して捩りコイルバネの外周面がプーリの内周面に当接した状態をを示す説明図である。Similarly, when the torque reaches a predetermined value or more, the outer peripheral surface of the torsion coil spring is in contact with the inner peripheral surface of the pulley. 同じく捩りコイルバネのねじれ角（弾性膨張量）を横軸で表し負荷トルクを縦軸で表したバネ特性を示す説明図である。It is explanatory drawing which shows the spring characteristic which similarly represented the torsion angle (elastic expansion amount) of the torsion coil spring on the horizontal axis, and represented the load torque on the vertical axis. 従来のプーリユニットを示す側断面図である。It is side sectional drawing which shows the conventional pulley unit.

符号の説明Explanation of symbols

１０ 内軸体
２０ プーリ（外輪体）
２５ バネ座
２６ 係合面
３０ 中間筒軸体（軸体）
３５ バネ座
３６ 係合面
４０ 一方向クラッチ
４８ ローラ
５０ 捩りコイルバネ
５２、５４ 端面 10 Inner shaft body 20 Pulley (outer ring body)
25 Spring seat 26 Engagement surface 30 Intermediate cylinder shaft (shaft)
35 Spring seat 36 Engagement surface 40 One-way clutch 48 Roller 50 Torsion coil spring 52, 54 End surface

Claims (2)

軸体と、この軸体の外周に同心状に配設されるプーリ側外輪体との間に回転変動を吸収する捩りコイルバネが介在されたプーリユニットであって、
前記捩りコイルバネは、その両端面のうち、一方の端面が前記外輪体に形成された係合面に当接し、他方の端面が前記軸体に形成された係合面に当接した状態で前記外輪体と前記軸体とをトルク伝達可能に接続し、
トルク負荷初期には前記捩りコイルバネの内周面が前記軸体の外周面に当接すると共に、前記捩りコイルバネの外周面と前記外輪体の内周面との間に所定の隙間が設定され、
トルクが所定値以上に達して前記捩りコイルバネが所定量だけ弾性的に膨張されたときには、前記捩りコイルバネの外周面が前記外輪体の内周面に当接するように前記外輪体の内径寸法が設定されていることを特徴とするプーリユニット。 A pulley unit in which a torsion coil spring that absorbs rotational fluctuation is interposed between a shaft body and a pulley-side outer ring body that is concentrically disposed on the outer periphery of the shaft body,
The torsion coil spring has one end surface abutting on an engagement surface formed on the outer ring body and the other end surface abutting on an engagement surface formed on the shaft body. Connecting the outer ring body and the shaft body so that torque can be transmitted,
At the initial stage of torque load, the inner peripheral surface of the torsion coil spring comes into contact with the outer peripheral surface of the shaft body, and a predetermined gap is set between the outer peripheral surface of the torsion coil spring and the inner peripheral surface of the outer ring body,
When the torque reaches a predetermined value or more and the torsion coil spring is elastically expanded by a predetermined amount, the inner diameter dimension of the outer ring body is set so that the outer peripheral surface of the torsion coil spring contacts the inner peripheral surface of the outer ring body Pulley unit characterized by being made. 内軸体と、この内軸体の外周に同心状に配設されるプーリとの間に、一方向クラッチと、回転変動を吸収する捩りコイルバネとが介在されたプーリユニットであって、
前記内軸体と、前記プーリとの間には、中間筒軸体が同心状に配置され、前記内軸体の外周面と前記中間筒軸体の内周面との間に、前記一方向クラッチが配置され、前記中間筒軸体の外周面と前記プーリの内周面との間に捩りコイルバネが配置され、
前記捩りコイルバネは、その両端面のうち、一方の端面が前記プーリ側に形成された係合面に当接し、他方の端面が前記中間筒軸体側に形成された係合面に当接した状態で前記プーリと前記中間筒軸体とをトルク伝達可能に接続し、
トルク負荷初期には前記捩りコイルバネの内周面が前記中間筒軸体の外周面に当接すると共に、前記捩りコイルバネの外周面と前記プーリの内周面との間に所定の隙間が設定され、
トルクが所定値以上に達して前記捩りコイルバネが所定量だけ弾性的に膨張されたときには、前記捩りコイルバネの外周面が前記プーリの内周面に当接するように前記プーリの内径寸法が設定されていることを特徴とするプーリユニット。 A pulley unit in which a one-way clutch and a torsion coil spring that absorbs rotational fluctuations are interposed between an inner shaft body and a pulley disposed concentrically on the outer periphery of the inner shaft body,
An intermediate cylindrical shaft body is concentrically disposed between the inner shaft body and the pulley, and the one-way direction is provided between an outer peripheral surface of the inner shaft body and an inner peripheral surface of the intermediate cylindrical shaft body. A clutch is disposed, a torsion coil spring is disposed between an outer peripheral surface of the intermediate cylindrical shaft body and an inner peripheral surface of the pulley;
The torsion coil spring is in a state in which one end face of the both end faces comes into contact with an engagement face formed on the pulley side, and the other end face comes into contact with an engagement face formed on the intermediate cylinder shaft side. The pulley and the intermediate cylinder shaft body are connected so as to be able to transmit torque,
At the initial stage of torque load, the inner peripheral surface of the torsion coil spring contacts the outer peripheral surface of the intermediate cylindrical shaft body, and a predetermined gap is set between the outer peripheral surface of the torsion coil spring and the inner peripheral surface of the pulley.
When the torque reaches a predetermined value or more and the torsion coil spring is elastically expanded by a predetermined amount, the inner diameter of the pulley is set so that the outer peripheral surface of the torsion coil spring contacts the inner peripheral surface of the pulley. Pulley unit characterized by that.
JP2007074276A 2007-03-22 2007-03-22 Pulley unit Pending JP2008232329A (en)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101936378A (en) * 2010-09-07 2011-01-05 江苏南方轴承股份有限公司 Unidirectional pulley for AC generator
CN102943862A (en) * 2012-11-08 2013-02-27 中联重科股份有限公司 Transmission wheel, matching wheel, secondary wheel, automatic regulating type friction wheel and rolling tube equipment
CN103352973A (en) * 2013-06-13 2013-10-16 李志敏 Unidirectional belt pulley subjected to friction clutch by spring
CN103363064A (en) * 2013-07-15 2013-10-23 李志敏 Spring friction brake one-way coupling damping belt wheel
WO2014198086A1 (en) * 2013-06-13 2014-12-18 Li Zhimin Unidirectionally coupled damping pulley
CN115143182A (en) * 2021-03-30 2022-10-04 广州汽车集团股份有限公司 Crankshaft structure and engine using same

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001523325A (en) * 1997-05-07 2001-11-20 ライテンズ オートモーティブ パートナーシップ Serpentine belt drive system with improved overrun alternator decoupler
JP2004360494A (en) * 2003-06-02 2004-12-24 Starting Ind Co Ltd Recoil starter
WO2006001337A1 (en) * 2004-06-24 2006-01-05 Nsk Ltd. Pulley device with built-in one-way clutch
JP2006070931A (en) * 2004-08-31 2006-03-16 Jtekt Corp Power transmission device
JP2006077939A (en) * 2004-09-13 2006-03-23 Jtekt Corp Power transmission device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001523325A (en) * 1997-05-07 2001-11-20 ライテンズ オートモーティブ パートナーシップ Serpentine belt drive system with improved overrun alternator decoupler
JP2004360494A (en) * 2003-06-02 2004-12-24 Starting Ind Co Ltd Recoil starter
WO2006001337A1 (en) * 2004-06-24 2006-01-05 Nsk Ltd. Pulley device with built-in one-way clutch
JP2006070931A (en) * 2004-08-31 2006-03-16 Jtekt Corp Power transmission device
JP2006077939A (en) * 2004-09-13 2006-03-23 Jtekt Corp Power transmission device

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101936378A (en) * 2010-09-07 2011-01-05 江苏南方轴承股份有限公司 Unidirectional pulley for AC generator
CN102943862A (en) * 2012-11-08 2013-02-27 中联重科股份有限公司 Transmission wheel, matching wheel, secondary wheel, automatic regulating type friction wheel and rolling tube equipment
WO2014071667A1 (en) * 2012-11-08 2014-05-15 中联重科股份有限公司 Drive wheel, match wheel, secondary wheel, self-adjustment friction wheel and roller device
CN103352973A (en) * 2013-06-13 2013-10-16 李志敏 Unidirectional belt pulley subjected to friction clutch by spring
WO2014198086A1 (en) * 2013-06-13 2014-12-18 Li Zhimin Unidirectionally coupled damping pulley
US9611928B2 (en) 2013-06-13 2017-04-04 Zhimin Li Unidirectional coupling damping pulley
CN103363064A (en) * 2013-07-15 2013-10-23 李志敏 Spring friction brake one-way coupling damping belt wheel
CN115143182A (en) * 2021-03-30 2022-10-04 广州汽车集团股份有限公司 Crankshaft structure and engine using same
CN115143182B (en) * 2021-03-30 2023-09-01 广州汽车集团股份有限公司 Crankshaft structure and engine using same

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