JP2007100830A

JP2007100830A - Power transmitting apparatus

Info

Publication number: JP2007100830A
Application number: JP2005291324A
Authority: JP
Inventors: Michiyasu Nosaka; 倫保野坂; Yasuo Tabuchi; 泰生田渕; Yoshiki Tada; 世史紀多田; Takayuki Suzuki; 孝行鈴木; Motohiko Ueda; 元彦上田
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2005-10-04
Filing date: 2005-10-04
Publication date: 2007-04-19
Anticipated expiration: 2025-10-04
Also published as: JP4285465B2

Abstract

<P>PROBLEM TO BE SOLVED: To avoid the following trouble: a power transmitting apparatus utilizing screw fastening cannot intercept the power even when a torque limiter operates. <P>SOLUTION: The power transmitting apparatus (10) comprises: rotary portions (1, 2) which rotate by receiving the rotational driving power from a driving source; and a power intercepting member (3) for intercepting the transmission of an excessive torque from the rotary portions to the rotary shaft (4) of a device to be driven by moving toward the device to be driven. The power intercepting member has a screw portion (303), and integrally rotates together with the rotary shaft by being connected by means of a screw. The rotary portions are provided so as to be arranged between the power intercepting member and the rotary shaft. Because the power intercepting member has a straight portion (403), the straight portion prevents the rotary portion from being caught in the portion between the end face (305a) of the power intercepting member on the side of the device to be driven and the rotary shaft, even when the end face has moved. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、動力伝達装置に係り、より特別には、エンジン等の外部動力源から、ベルト等を介して運転される車両カーエアコン用圧縮機に組み込まれて使用されるのに好適である。 The present invention relates to a power transmission device, and more particularly, is suitably used by being incorporated into a compressor for a vehicle car air conditioner that is operated from an external power source such as an engine via a belt or the like.

車両用カーエアコンの冷媒圧縮機は、エンジン等の外部動力源から、ベルト、プーリ等を介して駆動されるが、エンジンと圧縮機の接続を切り離すために、電磁クラッチがそれらの間に挿入されても良い。しかし、電磁クラッチを挿入しなければ、コストダウンになるため電磁クラッチが省略されることも少なくない。この場合、エンジン等の外部動力源から、ベルト等を介して運転されるカーエアコン用の圧縮機の動力伝達装置において、圧縮機が焼き付いた際にベルト切れ等の不具合を回避するためのトルクリミッタが設置される。 A refrigerant compressor of a car air conditioner for a vehicle is driven from an external power source such as an engine via a belt, a pulley, etc., but an electromagnetic clutch is inserted between them to disconnect the engine and the compressor. May be. However, if the electromagnetic clutch is not inserted, the cost is reduced and the electromagnetic clutch is often omitted. In this case, in a power transmission device for a compressor for a car air conditioner that is operated from an external power source such as an engine via a belt or the like, a torque limiter for avoiding problems such as belt breakage when the compressor is burned. Is installed.

トルクリミッタには、動力伝達経路の一部を螺子接合とし、圧縮機が焼き付いた際の過大なトルクにより、前記螺子接合部に発生する過大な軸力を利用するものがある（例えば、特許文献１参照）。このように、圧縮機に動力を伝達する従来の動力伝達装置で、圧縮機が焼き付きを起こした際に動力伝達のためのベルト切れ等の不具合を回避するために動力遮断装置（トルクリミッタ）が設置されている。動力伝達部位の一部分を螺子嵌合させた構造の動力遮断装置（トルクリミッタ）が従来提案されており、この螺子嵌合を利用したトルクリミッタ方式は、圧縮機が焼き付いた際に発生する過大なトルクにより、螺子嵌合部分に発生する過大な軸力を利用して、動力伝達経路の一部を破断することで、動力伝達経路を断つ方式である。つまり、このトルクリミッタ方式は圧縮機の焼き付き現象で発生する過大なトルクを利用し、螺子締結により発生する過大な軸力によって動力遮断部材を引っ張り力により分断する構造である。しかし、動力遮断部材が破断した際に、破断部の形状によっては、動力遮断部材の螺子部分が再締め付けされる場合が発生する可能性がある。この場合、動力遮断部材と、動力遮断部材を収納しているインナーハブの座面とで形成されたギャップ空間が無くなり、前記インナーハブの座面が前記動力遮断部材の螺子部分と圧縮機の軸端面との間で挟みこまれてしまい、動力が遮断できないという不具合があった。 Some torque limiters use screw joints as part of the power transmission path, and use excessive axial force generated in the screw joints due to excessive torque when the compressor is burned (for example, Patent Documents). 1). As described above, in the conventional power transmission device that transmits power to the compressor, a power shut-off device (torque limiter) is used to avoid problems such as belt breakage for power transmission when the compressor seizes. is set up. A power shut-off device (torque limiter) having a structure in which a part of the power transmission part is screw-fitted has been proposed in the past, and the torque limiter method using this screw-fitting is an excessively large amount generated when the compressor is burned. This is a method of breaking the power transmission path by breaking a part of the power transmission path by using an excessive axial force generated in the screw fitting portion by torque. That is, this torque limiter system uses an excessive torque generated by the seizure phenomenon of the compressor and has a structure in which the power shut-off member is divided by a pulling force by an excessive axial force generated by screw fastening. However, when the power cut-off member is broken, depending on the shape of the broken portion, the screw portion of the power cut-off member may be retightened. In this case, there is no gap space formed between the power shut-off member and the seat surface of the inner hub that houses the power shut-off member, and the seat surface of the inner hub serves as the screw portion of the power shut-off member and the shaft of the compressor. There was a problem that the power could not be cut off because it was sandwiched between the end faces.

上記の問題を有する従来の動力伝達装置５０について、図１２から１４を参照して説明する。図１２は、螺子締結を利用した動力伝達装置の従来の実施例の部分側断面図を示し、図１３及び１４は、図１２の動力伝達装置５０のトルクリミッタ（動力遮断部材）が作動して破断した後の２つの状態を示す部分側断面図である。図１２に示す動力伝達装置５０の構成は、エンジン等の動力源の回転が、ベルト等によりプーリに伝達され、更にプーリの組みつけられた動力伝達装置５０に伝達されるものである。この動力伝達装置５０の構成は、基本的には図１等に示す本発明の動力伝達装置と同様であり後述するので、ここでは詳しく説明しない。動力伝達装置５０においては、動力は先ず、ハブに伝達され、その後動力遮断部材、動力遮断部材と螺子締結される圧縮機等の回転軸の順で伝達される。 A conventional power transmission device 50 having the above problem will be described with reference to FIGS. FIG. 12 is a partial sectional side view of a conventional embodiment of a power transmission device using screw fastening, and FIGS. 13 and 14 show the operation of a torque limiter (power cutoff member) of the power transmission device 50 of FIG. It is a fragmentary sectional side view which shows two states after fracture | rupture. The configuration of the power transmission device 50 shown in FIG. 12 is such that the rotation of a power source such as an engine is transmitted to a pulley by a belt or the like, and further transmitted to the power transmission device 50 in which the pulley is assembled. The configuration of the power transmission device 50 is basically the same as that of the power transmission device of the present invention shown in FIG. 1 and the like and will be described later, and will not be described in detail here. In the power transmission device 50, the power is first transmitted to the hub, and then transmitted in the order of the power shut-off member and the rotation shaft of a compressor or the like screwed to the power shut-off member.

図１２の従来例の動力伝達装置５０において、動力遮断部材３の螺子部３０３を回転軸４の螺子部４０２に螺子結合させ、被駆動装置又は回転軸の方向（図１２において右方向）に移動させて組み立てる。これにより、ハブ２のインナーハブ２０４は、動力遮断部材３と回転軸４の間に挟まれて圧縮される。この様に、動力遮断部材３と回転軸４との螺子結合による軸圧縮力により、動力遮断部材３とインナーハブ２０４との当接面、及びインナーハブ２０４と回転軸４との当接面において摩擦力が形成される。この摩擦力により、動力遮断部材３とハブ２は回転軸４と共に一体で回転する。 In the conventional power transmission device 50 of FIG. 12, the screw portion 303 of the power shut-off member 3 is screwed to the screw portion 402 of the rotating shaft 4 and moved in the direction of the driven device or the rotating shaft (rightward in FIG. 12). Let them assemble. Thereby, the inner hub 204 of the hub 2 is sandwiched between the power cutoff member 3 and the rotating shaft 4 and compressed. In this way, due to the axial compression force generated by the screw coupling between the power cut-off member 3 and the rotary shaft 4, the contact surface between the power cut-off member 3 and the inner hub 204 and the contact surface between the inner hub 204 and the rotary shaft 4 are used. A frictional force is formed. Due to this frictional force, the power shut-off member 3 and the hub 2 rotate together with the rotating shaft 4.

図１３、図１４は、従来の実施例で動力遮断部材５０が作動し、動力遮断部材３が破断した後の構成を説明する図である。図１３において、動力遮断部材３が破断部３０１において破断すると、破断面３０６，３０７が形成され、動力遮断部材は、フランジ部３０２と螺子部材３０５に分割される。前記破断面３０６，３０７は平らな面形状とは限らない。従って、図１３において、フランジ側破断面３０６が螺子部材側の破断面３０７を回すことで、前記動力遮断部材の螺子部材３０５は、圧縮機（被駆動装置）側に進んでしまう。この現象により、図１２、１３では形成されていたギャップ９が無くなり、動力遮断部材の螺子部材３０５の端面３０５ａがハブの反当接面２０４ｄに干渉し、更に軸力によってハブ座２０４ｂを、螺子部材３０５の端面３０５ａと回転軸側の軸当接面４０４との間で挟み込み、動力が伝達されてしまう。つまり、動力遮断部材３が作動して破断しても、動力が遮断出来ずに、動力が回転軸４更には圧縮機等、被駆動装置に再伝達されてしまうという問題があった。 FIGS. 13 and 14 are diagrams for explaining the configuration after the power cut-off member 50 is operated and the power cut-off member 3 is broken in the conventional embodiment. In FIG. 13, when the power cut-off member 3 breaks at the breakage portion 301, fracture surfaces 306 and 307 are formed, and the power cut-off member is divided into a flange portion 302 and a screw member 305. The fracture surfaces 306 and 307 are not necessarily flat. Accordingly, in FIG. 13, when the flange-side fracture surface 306 rotates the screw member-side fracture surface 307, the screw member 305 of the power cut-off member advances to the compressor (driven device) side. Due to this phenomenon, the gap 9 formed in FIGS. 12 and 13 disappears, the end surface 305a of the screw member 305 of the power cut-off member interferes with the anti-contact surface 204d of the hub, and the hub seat 204b is further screwed by the axial force. The member 305 is sandwiched between the end surface 305a of the member 305 and the shaft contact surface 404 on the rotating shaft side, and power is transmitted. That is, even if the power cut-off member 3 is operated and broken, there is a problem that the power cannot be cut off and the power is retransmitted to the driven device such as the rotary shaft 4 and the compressor.

特開２００３−２０６９５０号公報JP 2003-206950 A

本発明は、上述した事情に鑑みなされたもので、この螺子締結を利用したトルクリミッタ方式において、トルクリミッタが作動しても動力が遮断出来ないという不具合を回避できる動力伝達装置を提供することを目的とする。 The present invention has been made in view of the above-described circumstances, and provides a power transmission device capable of avoiding a problem that power cannot be shut off even when the torque limiter is operated in the torque limiter system using the screw fastening. Objective.

本発明の請求項１に記載の形態では、動力伝達装置（１０）は、上述した目的を達成するために、駆動源からの回転駆動力が伝達される回転可能な回転部（１，２）と、前記回転部と被駆動装置の回転軸（４）との間の過大トルクの伝達を、前記被駆動装置の方向へ移動することにより遮断する、動力遮断部材（３）とを具備しており、動力遮断部材は前記回転軸に螺子結合して一体に回転可能である。前記回転軸には、前記回転部が直接的または間接的に当接する軸当接面（４０４）が設けられている。前記動力遮断部材の前記被駆動装置側の端面（３０５ａ）が前記被駆動装置の方向へ移動した場合においても、前記動力遮断部材の前記端面（３０５ａ）と前記軸当接面との間に前記回転部が挟まれることを阻止する挟み込み防止手段を備える。 According to the first aspect of the present invention, the power transmission device (10) includes a rotatable rotating portion (1, 2) to which a rotational driving force from a driving source is transmitted in order to achieve the above-described object. And a power shut-off member (3) that shuts off transmission of excessive torque between the rotating portion and the rotating shaft (4) of the driven device by moving in the direction of the driven device. The power cut-off member is screwed to the rotating shaft and can rotate integrally. The rotating shaft is provided with a shaft abutting surface (404) with which the rotating portion abuts directly or indirectly. Even when the driven device side end surface (305a) of the power cut-off member moves in the direction of the driven device, the end face (305a) of the power cut-off member and the shaft contact surface A pinching prevention means for preventing the rotating part from being pinched is provided.

この様に構成することにより、この螺子締結を利用したトルクリミッタ方式において、動力遮断部材の端面と回転軸との間に回転部が挟まれることを阻止する構成が具備されるため、動力遮断を円滑に行い、動力遮断部材が破断しても動力が遮断出来ないという不具合を回避できる。 By configuring in this way, in the torque limiter method using the screw fastening, a configuration for preventing the rotating part from being sandwiched between the end face of the power shut-off member and the rotating shaft is provided. Smoothly, it is possible to avoid the problem that the power cannot be cut off even if the power cut-off member is broken.

本発明の請求項２に記載の形態では、上記請求項１に記載の形態において、前記挟み込み手段は、回転軸に設けられており、前記動力遮断部材に螺子締結するための螺子部（４０２）と、前記螺子部と前記軸当接面（４０４）の間に設けられていて且つねじ切られていないか又は前記螺子部の螺子とは異なる仕様でねじ切られる、ストレート部（４０３）とを具備する。
本形態によれば、前記動力遮断部材の被駆動装置側の端面（３０５ａ）が移動した場合においても、ストレート部は動力遮断部材の端面と前記回転軸との間に前記回転部が挟まれることを阻止するので、動力伝達の遮断が確実に実施される。 According to a second aspect of the present invention, in the form according to the first aspect, the sandwiching means is provided on a rotating shaft, and is a screw portion (402) for screwing the power shut-off member. And a straight portion (403) that is provided between the screw portion and the shaft contact surface (404) and is not threaded or is threaded with a specification different from that of the screw of the screw portion. .
According to this embodiment, even when the end face (305a) on the driven device side of the power shut-off member moves, the straight part is sandwiched between the end face of the power shut-off member and the rotating shaft. Therefore, the power transmission is surely cut off.

本発明の請求項３に記載の形態では、上記請求項２に記載の形態において、前記ストレート部（４０３）の軸方向の幅（Ｂ）は、前記回転部が前記軸当接面に直接的又は間接的に当接する部分（２０４ｂ）の軸方向の厚み（Ａ）よりも広いことを特徴とする。
本形態によれば、動力遮断部材の被駆動装置側の端面が移動した場合においても、前記端面と回転軸との間に前記回転部が挟まれることを阻止するための、ストレート部の条件を明示する。 According to a third aspect of the present invention, in the form according to the second aspect, the axial width (B) of the straight portion (403) is such that the rotating portion is directly on the shaft contact surface. Or it is characterized by being wider than the thickness (A) in the axial direction of the part (204b) that abuts indirectly.
According to this embodiment, even when the end face of the power cutoff member on the driven device side moves, the straight part condition for preventing the rotating part from being sandwiched between the end face and the rotating shaft is set. Make it explicit.

本発明の請求項４に記載の形態では、上記請求項３に記載の形態において、前記ストレート部（４０３）の軸方向の幅（Ｂ）は、前記回転部の前記軸当接面に当接する部分（２０４ｂ）の軸方向の厚み（Ａ）から前記螺子部の１ピッチを減じた値と比べて、等しいか又はより大きいことを特徴とする。
本形態によれば、動力遮断部材の被駆動装置側の端面（３０５ａ）が移動した場合においても、前記端面（３０５ａ）と回転軸との間に前記回転部が挟まれることを阻止するための、ストレート部の条件をより明確にする。 According to a fourth aspect of the present invention, in the form according to the third aspect, the axial width (B) of the straight portion (403) abuts on the shaft abutting surface of the rotating portion. It is equal to or larger than a value obtained by subtracting one pitch of the screw portion from the axial thickness (A) of the portion (204b).
According to this embodiment, even when the end face (305a) on the driven device side of the power cut-off member moves, the rotating portion is prevented from being sandwiched between the end face (305a) and the rotating shaft. Make the conditions of the straight part clearer.

本発明の請求項５から８に記載の形態では、挟み込み防止手段として、前記軸当接面（４０４）と前記動力遮断部材の前記端面（３０５ａ）との間に挟み込み防止部材（８）を設置する構成か又は、前記動力遮断部材の前記端面（３０５ａ）に突起（３０５ｂ）を設ける構成とすることにより、前記端面（３０５ａ）が移動した場合においても、前記端面と前記回転軸との間に前記回転部が挟まれることを阻止する。この場合、挟み込み防止部材（８）又は突起（３０５ｂ）の軸方向の幅（Ｂ）は、回転部の軸当接面（４０４）から、回転部の反当接面（２０４ｄ）までの距離（Ａ）より大きい。
これらの形態によれば、動力遮断部材の被駆動装置側の端面（３０５ａ）が移動した場合においても、前記端面（３０５ａ）と回転軸との間に前記回転部が挟まれることを阻止する別の構成を開示し、更にその場合の阻止部材の寸法条件を明確にする。 According to the fifth to eighth aspects of the present invention, the pinching prevention member (8) is installed between the shaft contact surface (404) and the end surface (305a) of the power cut-off member as the pinching prevention means. Or by providing a projection (305b) on the end face (305a) of the power cut-off member, even when the end face (305a) is moved, the end face (305a) is moved between the end face and the rotating shaft. It prevents that the said rotation part is pinched. In this case, the axial width (B) of the pinching prevention member (8) or the protrusion (305b) is the distance (from the shaft contact surface (404) of the rotating portion to the anti-contact surface (204d) of the rotating portion ( A) Greater than.
According to these embodiments, even when the end face (305a) on the driven device side of the power shut-off member moves, the rotating portion is prevented from being sandwiched between the end face (305a) and the rotating shaft. Further, the dimensional condition of the blocking member in that case is clarified.

本発明の請求項９に記載の形態では、上記請求項８に記載の形態において、前記突起は、前記回転部が前記軸当接面に直接的または間接的に当接する部分の径方向内側に延出し、前記軸当接面に当接可能に形成されることを特徴とする。
本形態によれば、突起は、回転部の径方向内側に延出して、動力遮断部材の被駆動装置側の端面が移動した場合に、軸当接面に当接するので、端面と回転軸との間に前記回転部が挟まれることは阻止される。 According to a ninth aspect of the present invention, in the form according to the eighth aspect, the protrusion is located on a radially inner side of a portion where the rotating portion directly or indirectly contacts the shaft contact surface. It is formed so as to be able to extend and come into contact with the shaft contact surface.
According to this embodiment, the protrusion extends radially inward of the rotating part, and contacts the shaft contact surface when the driven device side end surface of the power cut-off member moves, so the end surface and the rotation shaft The rotating part is prevented from being sandwiched between the two.

本発明の請求項１０に記載の形態では、上記請求項１から９のいずれか一項に記載の形態において、前記回転部は、プーリ（１）とハブ（２）を具備する。プーリは被駆動装置のハウジングに回転可能に支持される。ハブは、前記動力遮断部材を介して回転軸に接続することを特徴とする。
本形態によれば、回転部がプーリとハブを具備する構成により、本発明はより具体化される。 According to a tenth aspect of the present invention, in the form according to any one of the first to ninth aspects, the rotating portion includes a pulley (1) and a hub (2). The pulley is rotatably supported by the housing of the driven device. The hub is connected to the rotating shaft through the power cutoff member.
According to the present embodiment, the present invention is further embodied by the configuration in which the rotating portion includes the pulley and the hub.

本発明の請求項１１に記載の形態では、上記請求項１から１０に記載の形態のいずれか一項において、被駆動装置としての車両用カーエアコンの圧縮機に連結されることを特徴とする。
本形態によれば、本発明の用途をより具体化する形態を開示する。
上記の本発明の説明において、カッコ（）内の記号又は数字は、以下に示す実施の形態との対応を示すために添付される。 In the form of Claim 11 of this invention, it is connected with the compressor of the car air conditioner for vehicles as a driven device in any one of the forms of the said Claims 1 to 10 characterized by the above-mentioned. .
According to this form, the form which actualizes the use of this invention more is disclosed.
In the above description of the present invention, symbols or numbers in parentheses () are attached to show correspondence with the embodiments described below.

以下、図面に基づいて本発明に係わる動力伝達装置の実施の形態を詳細に説明する。図１は、本発明に係る動力伝達装置の第１の実施の形態の図解的側断面図を示しており、図２は図１の動力遮断部材周辺の部分拡大側断面図である。図３及び４は第１の実施の形態において、動力遮断部材が作動して破断した２つの状態の部分拡大側断面図である。図５は第１の実施の形態において、本発明が必要とする条件の説明図である。図１から５の要素部分の符号は、図１２から１６の従来例の同様な要素部分の符号に対応している。 Embodiments of a power transmission device according to the present invention will be described below in detail with reference to the drawings. FIG. 1 shows a schematic side sectional view of a first embodiment of a power transmission device according to the present invention, and FIG. 2 is a partially enlarged side sectional view around a power cutoff member of FIG. 3 and 4 are partially enlarged side sectional views of two states in which the power cut-off member is broken by operating in the first embodiment. FIG. 5 is an explanatory diagram of conditions required by the present invention in the first embodiment. The reference numerals of the element parts in FIGS. 1 to 5 correspond to the reference numerals of the same element parts in the conventional examples of FIGS.

図１に示す本発明の第１の実施の形態の動力伝達装置１０は、車両用カーエアコンに使用されており、エンジン等の外部駆動源の回転力をカーエアコンの圧縮機に伝達するための装置であり、動力遮断部材（トルクリミッタ）３を具備する。動力伝達装置１０において、外部からの回転動力が図示されていないベルト等を介してプーリ１に伝達され、プーリの凹凸部１０１に、ハブ２の外周に設置された弾性部材からなる、凹凸部２０１が嵌合することによりハブ２のインナーハブ２０４に動力伝達される。プーリ側凹凸部１０１とハブ側凹凸部２０１は例えば、お互いに対応する複数の凹凸により嵌合する構成であって良い。動力は更にハブ２から動力遮断部材３に伝達されるが、本実施の形態においては、インナーハブ２０４と動力遮断部材３とは、インナーハブの嵌合部と動力遮断部材の嵌合部とにおいてインロー嵌合している。ここでプーリ１とハブ２は請求項における回転部に相当する。 A power transmission device 10 according to the first embodiment of the present invention shown in FIG. 1 is used in a car air conditioner for a vehicle, and transmits the rotational force of an external drive source such as an engine to a compressor of the car air conditioner. It is a device and comprises a power cut-off member (torque limiter) 3. In the power transmission device 10, rotational power from the outside is transmitted to the pulley 1 via a belt (not shown) or the like, and the uneven portion 201 made of an elastic member installed on the outer periphery of the hub 2 is provided on the uneven portion 101 of the pulley. Is transmitted to the inner hub 204 of the hub 2. For example, the pulley-side uneven portion 101 and the hub-side uneven portion 201 may be configured to be fitted by a plurality of uneven portions corresponding to each other. The power is further transmitted from the hub 2 to the power shut-off member 3, but in the present embodiment, the inner hub 204 and the power shut-off member 3 are in the fitting portion of the inner hub and the fitting portion of the power shut-off member. Inlay mating. Here, the pulley 1 and the hub 2 correspond to a rotating portion in claims.

インナーハブ２０４と動力遮断部材３とのトルク伝達は、図示されていないが例えば、動力遮断部材３のフランジ部３０２の外周である六角形状の嵌合部とハブ２の六角形状の嵌合部とのインロー嵌合又は回り止めのカシメ構造で動力伝達したり、本実施の形態には示されていないが、四角、二面幅、八角、十角、十二角等の円ではない形状で締結されたり、あるいは双方に設置された螺子で締結されてトルクを伝達しても良い。ハブ２から動力遮断部材３に伝達された動力は、動力遮断部材３から、動力遮断部材３に螺子結合する圧縮機（図示されない）の回転軸４に伝達されて圧縮機を回転駆動する。 Torque transmission between the inner hub 204 and the power cut-off member 3 is not shown, but for example, a hexagonal fitting portion that is the outer periphery of the flange portion 302 of the power cut-off member 3 and a hexagonal fitting portion of the hub 2 It is not shown in this embodiment, but it is fastened with a non-circular shape such as a square, two-sided width, octagon, decagon, twelve, etc. Or may be fastened with screws installed on both sides to transmit torque. The power transmitted from the hub 2 to the power cut-off member 3 is transmitted from the power cut-off member 3 to a rotary shaft 4 of a compressor (not shown) that is screwed to the power cut-off member 3 to rotate the compressor.

図２において、インナーハブ２０４と動力遮断部材３とは、動力遮断部材の螺子部３０３と圧縮機の回転軸４の螺子部４０２で螺子結合されることで発生する軸力で締結されている。この締結の軸方向の荷重は、インナーハブ２０４のハブ座２０４ｂで支えられており、ハブ２のハブ当接面２０４ｃと回転軸４の軸当接面４０４が接している。動力遮断部材３の圧縮機（又は回転軸）側の端面３０５ａとインナーハブ２０４のハブ座２０４ｂのハブ反当接面２０４ｄとは、その間にギャップ９が設定されて、ギャップ９を介して対面している。圧縮機の回転軸４には、螺子加工がされていない、または不完全螺子部を含むストレート部４０３（請求項における挟み込み防止手段に相当する）が設置されている。端面３０５ａとハブ反当接面２０４ｄの間に、回転軸４の螺子部４０２とストレート部４０３の境界が存在する。即ち、ストレート部４０３は、ハブ座２０４ｂのハブ反当接面２０４ｄを越えて、動力遮断部材３側に伸張する。 In FIG. 2, the inner hub 204 and the power shut-off member 3 are fastened by an axial force generated by being screwed by a screw portion 303 of the power shut-off member and a screw portion 402 of the rotary shaft 4 of the compressor. The fastening axial load is supported by the hub seat 204b of the inner hub 204, and the hub contact surface 204c of the hub 2 and the shaft contact surface 404 of the rotary shaft 4 are in contact with each other. A gap 9 is set between the end surface 305 a on the compressor (or rotating shaft) side of the power cut-off member 3 and the hub non-contact surface 204 d of the hub seat 204 b of the inner hub 204, and face each other through the gap 9. ing. The rotating shaft 4 of the compressor is provided with a straight portion 403 (corresponding to the pinching prevention means in the claims) that is not threaded or includes an incomplete screw portion. A boundary between the screw portion 402 and the straight portion 403 of the rotating shaft 4 exists between the end surface 305a and the hub non-contact surface 204d. That is, the straight portion 403 extends to the power shut-off member 3 side beyond the hub anti-contact surface 204d of the hub seat 204b.

図３及び４は、第１の実施の形態である図２の、動力遮断部材（トルクリミッタ）３が作動した後の状態を説明する図である。図２において、動力遮断部材３が作動して破断すると、動力遮断部材３は、フランジ部３０２と螺子部材３０５は分離する。従来の実施例のごとく破断部３０１の面は平らな面形状とは限らないので、フランジ側破断面３０６が、螺子部材側の破断面３０７に接触して回してしまう場合がある。分割された螺子部材３０５は、回されると軸方向（圧縮機側）に進んでしまい、ハブ座２０４ｂを挟みこもうとする。しかし、回転軸４には、ストレート部４０３が設置されているため、図４において、螺子部材３０５は、圧縮機方向に進んでも、ストレ−ト部４０３に達すると、それ以上圧縮機方向に進むことがストレート部４０３により阻止される。ハブ２を挟み込む前に動きが規制され、ハブ座２０４ｂを挟み込まずにギャップ９が確保され、ハブ座２０４ｂは、回転が拘束されることなく空転が可能となる。このように図４に示すように、ストレート部４０３が設けられていることにより、インナーハブ２０４のハブ座２０４ｂが、動力遮断部材３の螺子部材３０５と回転軸４の段差状の軸当接面４０４とに挟まれることがないので、動力遮断部材３と回転軸４の螺子結合による軸力が、インナーハブ２０４に作用することはなく、従って動力は完全に遮断される。 3 and 4 are views for explaining a state after the power cut-off member (torque limiter) 3 of FIG. 2 according to the first embodiment is operated. In FIG. 2, when the power cut-off member 3 is activated and broken, the power cut-off member 3 is separated from the flange portion 302 and the screw member 305. Since the surface of the fractured portion 301 is not necessarily flat as in the conventional example, the flange-side fracture surface 306 may rotate in contact with the fracture surface 307 on the screw member side. When the divided screw member 305 is rotated, the screw member 305 advances in the axial direction (compressor side) and tries to sandwich the hub seat 204b. However, since the straight portion 403 is installed on the rotary shaft 4, in FIG. 4, the screw member 305 advances in the compressor direction, but when it reaches the straight portion 403, it further advances in the compressor direction. Is prevented by the straight portion 403. The movement is restricted before the hub 2 is sandwiched, the gap 9 is secured without sandwiching the hub seat 204b, and the hub seat 204b can be idled without being constrained to rotate. As shown in FIG. 4, by providing the straight portion 403, the hub seat 204 b of the inner hub 204 can be connected to the stepped shaft contact surface between the screw member 305 of the power cut-off member 3 and the rotary shaft 4. Therefore, the axial force generated by the screw connection between the power cut-off member 3 and the rotary shaft 4 does not act on the inner hub 204, so that the power is completely cut off.

図５は、本実施の形態が成り立つための条件を説明する図であり、ストレート部４０３の寸法を示す。ストレート部４０３の幅Ｂは、ハブ座２０４ｂの厚みＡに対して、Ｂ≧Ａ−螺子ピッチ一回転分という関係（例えば、螺子ピッチが１．２５であれば、Ｂ≧Ａ−１．２５という関係）を有する。ストレート部４０３の径は、前記回転軸の螺子部４０２の谷径よりも大きい径を有する。また、ストレート部４０３は、動力遮断部材３の螺子形状とは異なる形状又は仕様（ピッチの違う螺子、体格の違う螺子；例えば、螺子部がＭ１０で１．２５のピッチの場合、ストレート部にＭ１０，１．０ピッチの螺子やＭ１２，１．２５ピッチの螺子でも良い）を有する。 FIG. 5 is a diagram for explaining the conditions for the present embodiment to be established, and shows the dimensions of the straight portion 403. The width B of the straight portion 403 is related to the thickness A of the hub seat 204b by B ≧ A−one screw pitch (for example, if the screw pitch is 1.25, B ≧ A−1.25. Relationship). The straight portion 403 has a diameter larger than the root diameter of the screw portion 402 of the rotating shaft. Further, the straight portion 403 has a shape or specification different from the screw shape of the power cut-off member 3 (screws having different pitches, screws having different physiques; for example, when the screw portions are M10 and 1.25 pitches, the straight portion has M10. , 1.0 pitch screw or M12, 1.25 pitch screw).

図６は、本発明の第２の実施の形態の動力伝達装置の図２に対応する部分拡大側断面図である。上記第１の実施の形態のストレート部を不完全螺子部４０５とした実施例であり、この実施の形態でも同様の効果が得られる。不完全螺子部４０５の幅Ｂは、ハブ座２０４ｂの厚みＡに対して、Ｂ≧Ａ−螺子ピッチ一回転分という関係を有する。
本第２の実施の形態の上記以外の構成は基本的に、第１の実施の形態と同様であるのでその説明は省略する。 FIG. 6 is a partially enlarged side sectional view corresponding to FIG. 2 of the power transmission device according to the second embodiment of the present invention. This is an example in which the straight portion of the first embodiment is an incomplete screw portion 405, and the same effect can be obtained in this embodiment. The width B of the incomplete screw portion 405 is related to the thickness A of the hub seat 204b by B ≧ A−one screw pitch rotation.
Since the configuration of the second embodiment other than the above is basically the same as that of the first embodiment, the description thereof is omitted.

図７及び８はそれぞれ、本発明の第３の実施の形態及びその変形形態の動力伝達装置の図２に対応する部分拡大側断面図である。図７は、ハブ２とは別部品であるリング形状の挟み込み防止部材（リング）８を設置した例である。リング８は、回転軸４と別体の環状の部材でも良く、外周には螺子を設置した構造でも良い。また図８に示すごとく、環ではなく、少なくとも１つ以上の棒状部材８でも良い。つまりはハブ座２０４ｂが回転軸の軸当接面４０４と動力遮断部材３の螺子部材３０５で挟み込まれないような状態を図８のごとく形成する、別部材（棒状部材）８でも同様の効果が得られる。ここで、リング（又は棒状部材）８の幅Ｂは、ハブ座２０４ｂの厚みＡに対して、Ｂ＞Ａという関係を有する。
本第３の実施の形態及びその変形形態の上記以外の構成は基本的に、第１の実施の形態と同様であるのでその説明は省略する。 FIGS. 7 and 8 are partially enlarged side sectional views corresponding to FIG. 2 of the power transmission device according to the third embodiment of the present invention and its modifications, respectively. FIG. 7 shows an example in which a ring-shaped pinching prevention member (ring) 8, which is a separate component from the hub 2, is installed. The ring 8 may be an annular member that is separate from the rotating shaft 4 and may have a structure in which a screw is provided on the outer periphery. Further, as shown in FIG. 8, at least one rod-shaped member 8 may be used instead of the ring. In other words, the same effect can be obtained with another member (bar-shaped member) 8 that forms a state in which the hub seat 204b is not sandwiched between the shaft contact surface 404 of the rotating shaft and the screw member 305 of the power cut-off member 3 as shown in FIG. can get. Here, the width B of the ring (or rod-shaped member) 8 has a relationship of B> A with respect to the thickness A of the hub seat 204b.
Since the third embodiment and its modifications other than those described above are basically the same as those of the first embodiment, description thereof will be omitted.

図９は、本発明の第４の実施の形態の動力伝達装置の図２に対応する部分拡大側断面図である。図９では、上記第３の実施の形態のリングに対応する、ハブ２とは別部材のワッシャリング８（請求項における挟み込み防止部材に相当する）が具備される。ワッシャリング８は、図９に示すごとく、その断面がＬ字形状であり、インナーハブ２０４のハブ座２０４ｂと回転軸４の軸当接面４０４に挟まれて、ワッシャの機能も果たしている。この場合も同様の効果が得られる。ここで図９に示すように、ワッシャリング８のリング部分８０２の幅Ｂは、ハブ座２０４ｂの厚みとワッシャリング８の平板状のワッシャ部分８０１の厚みの合計値Ａに対して、Ｂ＞Ａという関係を有する。
本第４の実施の形態の上記以外の構成は基本的に、第１の実施の形態と同様であるのでその説明は省略する。 FIG. 9 is a partially enlarged side sectional view corresponding to FIG. 2 of the power transmission device according to the fourth embodiment of the present invention. In FIG. 9, a washer ring 8 (corresponding to the pinching prevention member in the claims) corresponding to the ring of the third embodiment is provided. As shown in FIG. 9, the washer ring 8 has an L-shaped cross section and is sandwiched between the hub seat 204 b of the inner hub 204 and the shaft abutting surface 404 of the rotary shaft 4, and also functions as a washer. In this case, the same effect can be obtained. Here, as shown in FIG. 9, the width B of the ring portion 802 of the washer ring 8 is such that B> A with respect to the total value A of the thickness of the hub seat 204b and the thickness of the flat washer portion 801 of the washer ring 8. Have the relationship.
Since the configuration of the fourth embodiment other than the above is basically the same as that of the first embodiment, the description thereof is omitted.

図１０は、本発明の第５の実施の形態の動力伝達装置の図２に対応する部分拡大側断面図である。図１０は、ハブ２とは別部品であるリング状のフランジ部材８（請求項における挟み込み防止部材に相当する）を、回転軸４の軸方向における回転軸４の軸当接面４０４とインナーハブ２０４のハブ座２０４ｂとの間に設置した例である。フランジ部材８は、少なくとも１つ以上の突起８０２を具備する。この突起８０２がハブ座２０４ｂのハブ反当接面２０４ｄを越えて動力遮断部材側に突き出ることにより、上記第３の実施の形態のリングと同様な働きを有し、同様の効果が得られる。ここで図１０に示すごとく、フランジ部材８の突起８０２の幅Ｂは、ハブ座２０４ｂの厚みとフランジ部材８の平板部分８０１の厚みの合計値Ａに対して、Ｂ＞Ａという関係を有する。
本第５の実施の形態の上記以外の構成は基本的に、第１の実施の形態と同様であるのでその説明は省略する。 FIG. 10 is a partially enlarged side sectional view corresponding to FIG. 2 of the power transmission apparatus according to the fifth embodiment of the present invention. FIG. 10 shows a ring-shaped flange member 8 (corresponding to a pinching prevention member in claims), which is a separate component from the hub 2, and the shaft contact surface 404 of the rotating shaft 4 in the axial direction of the rotating shaft 4 and the inner hub. It is the example installed between 204 hub seats 204b. The flange member 8 includes at least one protrusion 802. The protrusion 802 protrudes toward the power cut-off member side beyond the hub anti-contact surface 204d of the hub seat 204b, so that it has the same function as the ring of the third embodiment and the same effect can be obtained. Here, as shown in FIG. 10, the width B of the protrusion 802 of the flange member 8 has a relationship of B> A with respect to the total value A of the thickness of the hub seat 204 b and the thickness of the flat plate portion 801 of the flange member 8.
Since the configuration of the fifth embodiment other than the above is basically the same as that of the first embodiment, the description thereof is omitted.

図１１は、本発明の第６の実施の形態の動力伝達装置の図２に対応する部分拡大側断面図である。図１１のように、ハブ座２０４ｂの半径方向の内側に入り込む形状で、動力遮断部材の螺子部材３０５の底面３０５ａから突出した形状の少なくとも１つ以上の突起３０５ｂを設置しても、動力遮断部材が破断した際に、螺子部材３０５が圧縮機側に進むことを規制する構造とできる。ハブ座２０４ｂの厚さＡと、前記突起３０５ｂの高さ（又は幅）Ｂとの関係は、Ｂ＞Ａの関係にある。
本第６の実施の形態の上記以外の構成は基本的に、第１の実施の形態と同様であるのでその説明は省略する。 FIG. 11 is a partially enlarged side sectional view corresponding to FIG. 2 of the power transmission apparatus according to the sixth embodiment of the present invention. As shown in FIG. 11, even if at least one protrusion 305b having a shape entering the inside of the hub seat 204b in the radial direction and protruding from the bottom surface 305a of the screw member 305 of the power cutoff member is installed, the power cutoff member When the screw breaks, the screw member 305 can be prevented from moving toward the compressor. The relationship between the thickness A of the hub seat 204b and the height (or width) B of the protrusion 305b is such that B> A.
Since the configuration of the sixth embodiment other than the above is basically the same as that of the first embodiment, description thereof will be omitted.

上記の第２から第６の実施の形態の図面に関して、即ち図６から１１を参照すると、図１から５に開示される第１の実施の形態の要素部分と同じ又は同様である図６から１１の要素部分は、同じ参照符号により指定されている。 With reference to the drawings of the second to sixth embodiments described above, ie with reference to FIGS. 6 to 11, from FIG. 6 which is the same as or similar to the element parts of the first embodiment disclosed in FIGS. Eleven element parts are designated by the same reference numerals.

次に上記実施の形態の効果及び作用について説明する。
本発明の第１の実施の形態の動力伝達装置により以下の効果が期待できる。
・螺子締結を利用したトルクリミッタ方式において、回転軸にストレート部を設けて、破断した場合に、動力遮断部材の螺子部がインナーハブのハブ座に当接することを阻止することにより、動力遮断を円滑に行い、動力遮断部材が破断しても動力が遮断出来ないという不具合を回避できる。 Next, effects and operations of the above embodiment will be described.
The following effects can be expected from the power transmission device according to the first embodiment of the present invention.
-In the torque limiter method using screw fastening, when the straight part is provided on the rotating shaft and it breaks, the screw part of the power shut-off member is prevented from coming into contact with the hub seat of the inner hub, thereby cutting off the power. Smoothly, it is possible to avoid the problem that the power cannot be cut off even if the power cut-off member is broken.

本発明の第２から第６の実施の形態の動力伝達装置により上記第１の実施の形態の効果と同様の効果が期待できる。 Effects similar to those of the first embodiment can be expected from the power transmission devices of the second to sixth embodiments of the present invention.

上記の実施例では本発明が車両用カーエアコンの圧縮機のための動力伝達装置として使用された例を示したが、本発明はこれ以外の用途に適用されても良く、本発明の適用をカーエアコン用に限定するものではない。
上記において記載した、あるいは添付図面に示した実施の形態において、駆動源の動力は、ベルト及びプーリを介して伝達される構成で説明されたが、本発明はこれに限定されるものではなく、例えば、歯車等の別の機構を介して動力が伝達されても良い。 In the above embodiment, the example in which the present invention is used as a power transmission device for a compressor of a car air conditioner for a vehicle is shown. However, the present invention may be applied to other uses. It is not limited to car air conditioners.
In the embodiment described above or shown in the accompanying drawings, the power of the drive source has been described as being transmitted via a belt and a pulley, but the present invention is not limited to this, For example, power may be transmitted via another mechanism such as a gear.

上記の実施の形態は本発明の例であり、本発明は、該実施の形態により制限されるものではなく、請求項に記載される事項によってのみ規定されており、上記以外の実施の形態も実施可能である。 The above-described embodiment is an example of the present invention, and the present invention is not limited by the embodiment, but is defined only by matters described in the claims, and other embodiments than the above are also possible. It can be implemented.

図１は、本発明に係る動力伝達装置の第１の実施の形態の図解的側断面図である。FIG. 1 is a schematic side sectional view of a first embodiment of a power transmission device according to the present invention. 図２は図１の動力遮断部材周辺の部分拡大側断面図である。FIG. 2 is a partially enlarged side sectional view of the periphery of the power shut-off member of FIG. 図３は、第１の実施の形態において、動力遮断部材が作動して破断した状態の部分拡大側断面図であり、破断直後の状態を示す。FIG. 3 is a partially enlarged side sectional view showing a state in which the power cut-off member is broken by operating in the first embodiment, and shows a state immediately after the break. 図４は、第１の実施の形態において、動力遮断部材が作動して破断した状態の部分拡大側断面図であり、螺子部材（３０５）がハブ座（２０４ｂ）まで進んだ状態を示す。FIG. 4 is a partially enlarged side cross-sectional view of the first embodiment in a state where the power cut-off member is activated and broken, and shows a state where the screw member (305) has advanced to the hub seat (204b). 図５は、前記第１の実施の形態が成り立つための条件の説明図である。FIG. 5 is an explanatory diagram of conditions for satisfying the first embodiment. 図６は、本発明に係る動力伝達装置の第２の実施の形態のハブ座周辺の部分拡大側断面図である。FIG. 6 is a partially enlarged side sectional view around the hub seat of the second embodiment of the power transmission device according to the present invention. 図７は、本発明に係る動力伝達装置の第３の実施の形態のハブ座周辺の部分拡大側断面図である。FIG. 7 is a partially enlarged side cross-sectional view of the periphery of the hub seat of the third embodiment of the power transmission device according to the present invention. 図８は、本発明に係る動力伝達装置の第３の実施の形態の変形形態のハブ座周辺の部分拡大側断面図である。FIG. 8 is a partially enlarged side sectional view of the periphery of the hub seat in a modified form of the third embodiment of the power transmission device according to the present invention. 図９は、本発明に係る動力伝達装置の第４の実施の形態のハブ座周辺の部分拡大側断面図である。FIG. 9 is a partially enlarged side sectional view of the periphery of the hub seat of the fourth embodiment of the power transmission device according to the present invention. 図１０は、本発明に係る動力伝達装置の第５の実施の形態のハブ座周辺の部分拡大側断面図である。FIG. 10 is a partially enlarged side sectional view of the periphery of the hub seat of the fifth embodiment of the power transmission device according to the present invention. 図１１は、本発明に係る動力伝達装置の第６の実施の形態のハブ座周辺の部分拡大側断面図である。FIG. 11 is a partially enlarged side sectional view of the periphery of the hub seat of the sixth embodiment of the power transmission device according to the present invention. 図１２は、従来例の動力伝達装置の動力遮断部材周辺の部分拡大側断面図である。FIG. 12 is a partially enlarged side cross-sectional view of the periphery of a power cutoff member of a conventional power transmission device. 図１３は、図１２の従来例において、動力遮断部材が作動して破断した状態の部分拡大側断面図であり、破断直後の状態を示す。FIG. 13 is a partially enlarged side cross-sectional view of the conventional example of FIG. 12 in a state where the power cut-off member is activated and broken, and shows a state immediately after the break. 図１４は、図１２の従来例において、動力遮断部材が作動して破断した状態の部分拡大側断面図であり、螺子部材（３０５）がハブ座まで進んだ状態を示す。FIG. 14 is a partially enlarged side cross-sectional view of the conventional example of FIG. 12 in a state where the power shut-off member is activated and broken, and shows a state where the screw member (305) has advanced to the hub seat.

符号の説明Explanation of symbols

１プーリ
１０１（プーリ側）凹凸部
２ハブ
２０１（ハブ側）凹凸部
２０４インナーハブ
２０４ｂハブ座
３動力遮断部材
３０２フランジ部
３０３螺子部
３０５螺子部材
３０５ａ端面
４回転軸
４０２螺子部
４０３ストレート部
４０４軸当接面
９ギャップ
１０動力伝達装置 DESCRIPTION OF SYMBOLS 1 Pulley 101 (Pulley side) uneven part 2 Hub 201 (Hub side) Uneven part 204 Inner hub 204b Hub seat 3 Power interruption member 302 Flange part 303 Screw part 305 Screw member 305a End surface 4 Rotating shaft 402 Screw part 403 Straight part 404 Axis Contact surface 9 Gap 10 Power transmission device

Claims

駆動源からの回転駆動力が伝達される回転可能な回転部（１，２）と、
前記回転部と被駆動装置の回転軸（４）との間の過大トルクの伝達を、前記被駆動装置の方向へ移動することにより遮断する、動力遮断部材（３）であって、前記回転軸に螺子結合して一体に回転可能な動力遮断部材と、
を具備する動力伝達装置（１０）において、
前記回転軸には、前記回転部が直接的または間接的に接触する軸当接面（４０４）が設けられており、更に
前記動力遮断部材の前記被駆動装置側の端面（３０５ａ）が前記被駆動装置の方向へ移動した場合においても、前記動力遮断部材の前記端面（３０５ａ）と前記軸当接面との間に前記回転部が挟まれることを阻止する、挟み込み防止手段を備えることを特徴とする動力伝達装置。 A rotatable rotating part (1, 2) to which a rotational driving force from a driving source is transmitted;
A power shut-off member (3) for shutting off transmission of excessive torque between the rotating portion and the rotating shaft (4) of the driven device by moving in the direction of the driven device, wherein the rotating shaft A power shut-off member that can be screwed together and rotated together,
In the power transmission device (10) comprising:
The rotating shaft is provided with a shaft abutting surface (404) with which the rotating portion comes into direct or indirect contact, and an end surface (305a) on the driven device side of the power shut-off member is further covered with the covered shaft. In the case of moving in the direction of the driving device, it is provided with a pinching prevention means for preventing the rotating part from being pinched between the end face (305a) of the power cut-off member and the shaft contact surface. Power transmission device.

前記挟み込み防止手段は、前記回転軸に設けられており、更に前記動力遮断部材に螺子締結するための螺子部（４０２）と、前記螺子部と前記軸当接面（４０４）の間に設けられていて且つねじ切られていないか又は前記螺子部の螺子とは異なる仕様でねじ切られる、ストレート部（４０３）と、を具備する、
ことを特徴とする請求項１に記載の動力伝達装置。 The pinching prevention means is provided on the rotating shaft, and is further provided between a screw portion (402) for screwing the power shut-off member and a screw portion and the shaft contact surface (404). A straight portion (403) that is unthreaded or threaded with a specification that is different from a screw of the screw portion,
The power transmission device according to claim 1.

前記ストレート部（４０３）の軸方向の幅（Ｂ）は、前記回転部が前記軸当接面に直接的または間接的に当接する部分（２０４ｂ）の軸方向の厚み（Ａ）よりも広いことを特徴とする請求項２に記載の動力伝達装置。 The axial width (B) of the straight portion (403) is wider than the axial thickness (A) of the portion (204b) where the rotating portion abuts directly or indirectly on the shaft abutting surface. The power transmission device according to claim 2.

前記ストレート部（４０３）の軸方向の幅（Ｂ）は、前記回転部が前記軸当接面に直接的または間接的に当接する部分（２０４ｂ）の軸方向の厚み（Ａ）から前記螺子部の１ピッチを減じた値と比べて、等しいか又はより大きいことを特徴とする請求項２に記載の動力伝達装置。 The axial width (B) of the straight portion (403) is determined from the axial thickness (A) of the portion (204b) where the rotating portion abuts directly or indirectly on the shaft abutting surface. The power transmission device according to claim 2, wherein the power transmission device is equal to or larger than a value obtained by subtracting one pitch.

前記挟み込み防止手段は、前記軸当接面（４０４）と前記動力遮断部材の前記端面（３０５ａ）との間に配置された挟み込み防止部材（８）であることを特徴とする請求項１に記載の動力伝達装置。 The said pinching prevention means is a pinching prevention member (8) arrange | positioned between the said shaft contact surface (404) and the said end surface (305a) of the said power interruption member. Power transmission device.

前記挟み込み防止部材（８）の軸方向の幅（Ｂ）は、前記回転部の前記軸当接面（４０４）から前記回転部の前記端面（３０５ａ）に対面する反当接面（２０４ｄ）までの距離（Ａ）より大きいことを特徴とする請求項５に記載の動力伝達装置。 The axial width (B) of the pinching prevention member (8) is from the shaft contact surface (404) of the rotating portion to the anti-contact surface (204d) facing the end surface (305a) of the rotating portion. The power transmission device according to claim 5, wherein the power transmission device is larger than the distance (A).

前記挟み込み防止手段は、前記動力遮断部材の前記端面（３０５ａ）において、前記被駆動装置側に伸張するように設けられた突起（３０５ｂ）であることを特徴とする請求項１に記載の動力伝達装置。 2. The power transmission according to claim 1, wherein the pinching prevention means is a protrusion (305 b) provided to extend toward the driven device on the end surface (305 a) of the power shut-off member. apparatus.

前記突起（３０５ｂ）の軸方向の幅（Ｂ）は、前記回転部が前記軸当接面に直接的または間接的に当接する部分（２０４ｂ）の軸方向の厚み（Ａ）より大きいことを特徴とする請求項７に記載の動力伝達装置。 The axial width (B) of the protrusion (305b) is larger than the axial thickness (A) of the portion (204b) where the rotating portion directly or indirectly contacts the shaft contact surface. The power transmission device according to claim 7.

前記突起は、前記回転部が前記軸当接面に直接的または間接的に当接する部分の径方向内側に延出し、前記軸当接面に当接可能に形成されることを特徴とする請求項８に記載の動力伝達装置。 The protrusion is formed to extend inward in a radial direction of a portion where the rotating portion directly or indirectly abuts on the shaft abutting surface, and is formed to be able to abut on the shaft abutting surface. Item 9. The power transmission device according to Item 8.

前記回転部は、前記被駆動装置のハウジングに回転可能に支持されたプーリ（１）と、前記軸当接面に直接的または間接的に接触するハブ（２）とを具備しており、
前記ハブは前記動力遮断部材を介して前記回転軸に接続していることを特徴とする請求項１から９のいずれか一項に記載の動力伝達装置。 The rotating part includes a pulley (1) rotatably supported by a housing of the driven device, and a hub (2) that directly or indirectly contacts the shaft contact surface,
The power transmission device according to any one of claims 1 to 9, wherein the hub is connected to the rotating shaft via the power cutoff member.

被駆動装置としての車両用カーエアコンの圧縮機に連結されることを特徴とする請求項１から１０のいずれか一項に記載の動力伝達装置。 The power transmission device according to any one of claims 1 to 10, wherein the power transmission device is connected to a compressor of a car air conditioner for a vehicle as a driven device.