WO2014112413A1

WO2014112413A1 - Wobble plate type variable displacement compressor

Info

Publication number: WO2014112413A1
Application number: PCT/JP2014/050125
Authority: WO
Inventors: 健二杉野; 榎本　安里; 仁簗瀬; 裕昭井古田
Original assignee: サンデン株式会社
Priority date: 2013-01-15
Filing date: 2014-01-08
Publication date: 2014-07-24
Also published as: DE112014000436B4; JP6125237B2; DE112014000436T5; JP2014136969A

Abstract

[Problem] To improve the wear resistance of an inner race rotation-preventing mechanism of a wobble plate type variable displacement compressor by minimizing wear of a housing peripheral surface. [Solution] When the inner peripheral surface of a housing (2) and the outer peripheral surface of an inner race (27) are formed in triangular shapes that correspond to each other, and the peripheral surface on the housing (2) side and the peripheral surface on the inner race (27) directly face each other, an inclined surface (27b) is formed on the peripheral surface on the inner race (27) side in such a manner that a gap between the surfaces increases toward an edge section (27c) in the peripheral direction of the inner race (27), and when the inner race (27) rotates, the peripheral surface on the housing (2) side and the peripheral surface on the inner race (27) side are brought into contact with each other in a state in which the surfaces are substantially in contact, thereby minimizing wear of the housing (2) peripheral surface.

Description

揺動板式可変容量圧縮機Swing plate type variable capacity compressor

　本発明は、駆動軸の回転に伴って揺動する揺動板によりピストンを往復動させる揺動板式可変容量圧縮機に関し、特に、車両エアコンシステム等の冷媒循環装置に使用される揺動板式可変容量圧縮機に関する。 The present invention relates to an oscillating plate type variable displacement compressor in which a piston is reciprocated by an oscillating plate that oscillates with rotation of a drive shaft, and more particularly to an oscillating plate type variable compressor used in a refrigerant circulation device such as a vehicle air conditioner system. It relates to a capacity compressor.

　この種の揺動板式可変容量圧縮機として、特許文献１に記載されたものが提案されている。特許文献１に記載された揺動板式可変容量圧縮機は、内輪回転阻止機構によって回転主軸回りの回転が阻止される内輪と、斜板に取付けられ斜板の回転により揺動板を揺動させる外輪と、内輪の回転阻止力を外輪に伝達するように内輪と外輪とを連結する連結機構と、を備え、内輪の回転阻止力が連結機構を介して外輪に伝達して揺動板の回転を阻止する構成である。そして、内輪を回転阻止する前記内輪回転阻止機構として、内輪の外周に周方向に複数の軸方向に延びる平面部を形成し、ハウジングの内周に内輪側の各平面部に対応させて軸方向に延びる平面部を形成し、回転主軸の回転時に内輪側の平面部とハウジング側の平面部を互いに当接させる当接構造により、内輪を回転阻止する構成が開示されている（特許文献１の図１１参照）。 As this type of oscillating plate variable displacement compressor, the one described in Patent Document 1 has been proposed. The oscillating plate type variable displacement compressor described in Patent Document 1 has an inner ring that is prevented from rotating around the rotation main shaft by an inner ring rotation preventing mechanism, and is attached to the swash plate and oscillates the oscillating plate by rotation of the swash plate. An outer ring, and a coupling mechanism that connects the inner ring and the outer ring so as to transmit the rotation prevention force of the inner ring to the outer ring, and the rotation prevention force of the inner ring is transmitted to the outer ring via the coupling mechanism to rotate the swing plate. It is the structure which prevents. Then, as the inner ring rotation blocking mechanism for blocking the rotation of the inner ring, a plurality of axially extending plane portions are formed on the outer periphery of the inner ring, and the axial direction corresponding to each plane portion on the inner ring side on the inner periphery of the housing A configuration is disclosed in which the inner ring is prevented from rotating by an abutment structure in which a flat part extending to the inner side is formed and the inner ring side flat part and the housing side flat part are brought into contact with each other when the rotation main shaft rotates. FIG. 11).

特開２００９－２８１３１０号公報JP 2009-281310 A

　しかしながら、特許文献１に開示された前記内輪回転阻止機構では、互いに対面する内輪側平面部とハウジング側平面部が単純な平面形状であるため、圧縮機の運転状態において内輪が回転主軸の回転による荷重を受けるときに、内輪側平面部の端縁（エッジ）がハウジングの平面部と接触するため、面接触ではなく線接触の状態となり、接触面積を大きく確保できず、過剰面圧に起因して鉄系素材からなる内輪より軟らかいアルミ系素材のハウジング内周面の摩耗が発生する虞れがある。また、ハウジング内における内輪の軸方向位置は斜板の傾斜角に応じてハウジング内の可動範囲内で軸方向に可動するため、その際にハウジング内周面に摩耗が発生する虞れがある。 However, in the inner ring rotation prevention mechanism disclosed in Patent Document 1, since the inner ring side plane portion and the housing side plane portion facing each other have a simple planar shape, the inner ring is caused by the rotation of the rotation main shaft in the operating state of the compressor. When the load is received, the edge of the inner ring side plane part comes into contact with the flat part of the housing, resulting in a line contact state, not a surface contact, and a large contact area cannot be secured, resulting in excessive surface pressure. There is a risk of wear on the inner peripheral surface of the housing made of an aluminum material that is softer than the inner ring made of an iron material. Further, since the axial position of the inner ring in the housing moves in the axial direction within the movable range in the housing in accordance with the inclination angle of the swash plate, there is a possibility that the inner peripheral surface of the housing may be worn.

　本発明は上記問題点に着目してなされたもので、ハウジング内周面の摩耗を抑制することにより、内輪回転阻止機構の耐摩耗性向上を図った揺動板式可変容量圧縮機を提供することを目的とする。 The present invention has been made paying attention to the above-mentioned problems, and provides a swing plate type variable displacement compressor that improves wear resistance of an inner ring rotation prevention mechanism by suppressing wear on the inner peripheral surface of a housing. With the goal.

　このため、本発明の揺動板式可変容量圧縮機は、回転主軸と共に回転する斜板と、シリンダボア内のピストンに連結され前記斜板の回転に伴って前記回転主軸に対して揺動してピストンを往復動させる揺動板と、前記回転主軸の回転時に前記揺動板の回転を阻止する揺動板回転阻止機構とを備え、前記回転主軸に対する斜板の傾斜角を可変して前記揺動板の揺動幅を変更し前記シリンダボアからの冷媒吐出容量を可変する揺動板式可変容量圧縮機であって、前記揺動板回転阻止機構を、前記回転主軸の軸方向に移動可能で内輪回転阻止機構によって前記回転主軸回りの回転が阻止される内輪と、前記斜板の回転により前記揺動板を揺動させる外輪と、前記内輪に対して前記外輪が揺動可能に且つ内輪の回転阻止力を外輪に伝達するように前記内輪と前記外輪とを連結する連結機構と、を備えて構成し、前記内輪回転阻止機構を、前記回転主軸の回転時に、ハウジングの内周面と当該内周面に対面させた前記内輪の外周面とを当接させる当接構造によるものにおいて、前記ハウジングの内周面と前記内輪の外周面とを互いに対応する多角形状に形成し、ハウジング側の各周面と内輪側の各周面とを、互いに正対したときに互いの面間の隙間が周方向の端縁部に向かうにつれて増大するよう形成したことを特徴とする。 For this reason, the oscillating plate type variable displacement compressor of the present invention is connected to the swash plate rotating with the rotating main shaft and the piston in the cylinder bore, and swings with respect to the rotating main shaft as the swash plate rotates. And a rocking plate rotation blocking mechanism for blocking rotation of the rocking plate when the rotating main shaft rotates, and the rocking plate can be swung by varying an inclination angle of the swash plate with respect to the rotating main shaft. An oscillating plate type variable displacement compressor that changes the oscillating width of the plate and varies the refrigerant discharge capacity from the cylinder bore, wherein the oscillating plate rotation preventing mechanism is movable in the axial direction of the rotating main shaft and rotates the inner ring. An inner ring whose rotation around the rotation main shaft is blocked by a blocking mechanism, an outer ring which rocks the rocking plate by the rotation of the swash plate, the outer ring which can rock with respect to the inner ring and the rotation prevention of the inner ring Front to transmit force to the outer ring A coupling mechanism that couples the inner ring and the outer ring, and an outer periphery of the inner ring in which the inner ring rotation prevention mechanism faces the inner circumferential surface of the housing and the inner circumferential surface when the rotation main shaft rotates. In the contact structure for contacting the surface, the inner peripheral surface of the housing and the outer peripheral surface of the inner ring are formed in polygonal shapes corresponding to each other, and each peripheral surface on the housing side and each peripheral surface on the inner ring side Are formed such that when facing each other, the gap between the surfaces increases toward the edge in the circumferential direction.

　本発明の揺動板式可変容量圧縮機によれば、回転主軸の回転時にハウジングの内周面と当該内周面と対面する内輪の外周面とを当接させて内輪の回動を阻止する構造において、ハウジングの内周面と内輪の外周面とを互いに対応する多角形状に形成し、ハウジング側周面と内輪側周面とが互いに正対したときに互いの面間の隙間が周方向の面端縁に向かうにつれて増大するよう形成したので、回転主軸の回転に伴って内輪が回動したとき内輪側周面とハウジング側周面とが周方向の端縁部領域で略面接触状態となり、従来の線接触状態と比較して内輪側周面からハウジング側周面に作用する面圧を軽減できハウジング周面の摩耗を抑制できる。また、内輪の軸方向への移動に伴う引っ掛かり等による過剰な摩耗の発生も抑制できる。従って、内輪回転阻止機構における耐摩耗性を向上することができる。 According to the oscillating plate type variable displacement compressor of the present invention, the structure that prevents the rotation of the inner ring by bringing the inner peripheral surface of the housing into contact with the outer peripheral surface of the inner ring facing the inner peripheral surface when the rotary main shaft rotates. The inner peripheral surface of the housing and the outer peripheral surface of the inner ring are formed in polygonal shapes corresponding to each other, and when the housing side peripheral surface and the inner ring side peripheral surface face each other, the gap between the surfaces is circumferential. Since it is formed so as to increase toward the surface edge, when the inner ring rotates with the rotation of the rotation main shaft, the inner ring side circumferential surface and the housing side circumferential surface are in a substantially surface contact state in the circumferential edge region. Compared with the conventional line contact state, the surface pressure acting on the housing side peripheral surface from the inner ring side peripheral surface can be reduced, and wear of the housing peripheral surface can be suppressed. In addition, it is possible to suppress the occurrence of excessive wear due to catching or the like accompanying the movement of the inner ring in the axial direction. Therefore, the wear resistance in the inner ring rotation prevention mechanism can be improved.

本発明の一実施形態に係る揺動板式可変容量圧縮機の基本構成例を示す断面図である。It is sectional drawing which shows the basic structural example of the rocking | fluctuation plate type variable capacity compressor which concerns on one Embodiment of this invention. 図１の揺動板式可変容量圧縮機の揺動板回転阻止機構を含む要部の分解斜視図である。It is a disassembled perspective view of the principal part containing the rocking | fluctuation plate rotation prevention mechanism of the rocking | fluctuation plate type variable capacity compressor of FIG. 図１の揺動板式可変容量圧縮機の一形態例を示し、（Ａ）は部分断面図、（Ｂ）は部分正面図である。1 shows an example of a swing plate type variable capacity compressor of FIG. 1, (A) is a partial sectional view, and (B) is a partial front view. 本発明の揺動板式可変容量圧縮機における内輪回転阻止機構の第１実施形態を示し、（Ａ）は内輪の斜視図、（Ｂ）はフロントハウジング側から見た内輪とハウジングによる内輪回転阻止機構部の図、（Ｃ）は（Ｂ）図の当接構造部の拡大図である。1 shows a first embodiment of an inner ring rotation prevention mechanism in a swing plate type variable displacement compressor of the present invention, (A) is a perspective view of the inner ring, and (B) is an inner ring rotation prevention mechanism by an inner ring and a housing as viewed from the front housing side. The figure of a part and (C) are the enlarged views of the contact structure part of the (B) figure. 本発明の揺動板式可変容量圧縮機における内輪回転阻止機構の第２実施形態を示し、（Ａ）は内輪の斜視図、（Ｂ）はフロントハウジング側から見た内輪とハウジングによる内輪回転阻止機構部の図、（Ｃ）は（Ｂ）図の当接構造部の拡大図である。2 shows a second embodiment of the inner ring rotation prevention mechanism in the swing plate type variable displacement compressor of the present invention, (A) is a perspective view of the inner ring, and (B) is an inner ring rotation prevention mechanism by the inner ring and the housing as seen from the front housing side. The figure of a part and (C) are the enlarged views of the contact structure part of the (B) figure. 本発明の揺動板式可変容量圧縮機における内輪回転阻止機構の第３実施形態を示し、（Ａ）は内輪の斜視図、（Ｂ）はフロントハウジング側から見た内輪とハウジングによる内輪回転阻止機構部の図、（Ｃ）は（Ｂ）図の当接構造部の拡大図である。3 shows a third embodiment of the inner ring rotation prevention mechanism in the swing plate type variable displacement compressor of the present invention, (A) is a perspective view of the inner ring, and (B) is an inner ring rotation prevention mechanism by the inner ring and the housing as seen from the front housing side. The figure of a part and (C) are the enlarged views of the contact structure part of the (B) figure. 本発明の揺動板式可変容量圧縮機における内輪回転阻止機構の第４実施形態を示し、（Ａ）は内輪の斜視図、（Ｂ）はフロントハウジング側から見た内輪とハウジングによる内輪回転阻止機構部の図、（Ｃ）は（Ｂ）図の当接構造部の拡大図である。4 shows a fourth embodiment of the inner ring rotation prevention mechanism in the swing plate type variable displacement compressor of the present invention, (A) is a perspective view of the inner ring, and (B) is an inner ring rotation prevention mechanism by the inner ring and the housing as seen from the front housing side. The figure of a part and (C) are the enlarged views of the contact structure part of the (B) figure. 本発明の揺動板式可変容量圧縮機における内輪回転阻止機構の第５実施形態を示し、（Ａ）は内輪の斜視図、（Ｂ）はフロントハウジング側から見た内輪とハウジングによる内輪回転阻止機構部の図、（Ｃ）は（Ｂ）図の当接構造部の拡大図である。FIG. 9 shows a fifth embodiment of an inner ring rotation prevention mechanism in the swing plate type variable displacement compressor of the present invention, (A) is a perspective view of the inner ring, and (B) is an inner ring rotation prevention mechanism by the inner ring and the housing as viewed from the front housing side. The figure of a part and (C) are the enlarged views of the contact structure part of the (B) figure. 本発明の揺動板式可変容量圧縮機における内輪回転阻止機構の第６実施形態を示し、（Ａ）はフロントハウジング側から見た内輪とハウジングによる内輪回転阻止機構部の図、（Ｂ）は（Ａ）図の当接構造部の拡大図である。6 shows a sixth embodiment of the inner ring rotation prevention mechanism in the swing plate type variable displacement compressor of the present invention, (A) is a view of the inner ring rotation prevention mechanism portion by the inner ring and the housing as viewed from the front housing side, (B) is ( A) It is an enlarged view of the contact structure part of a figure.

　以下、本発明の実施形態を図面に基づいて説明する。
　本発明に係る揺動板式可変容量圧縮機の全体基本構成例について図１～図３を参照して説明する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
An example of the overall basic configuration of a swing plate type variable displacement compressor according to the present invention will be described with reference to FIGS.

　図１は、本発明に係る揺動板式可変容量圧縮機の全体基本構成の一例であり、最大吐出容量時の運転状態を示している。図２は、図１の揺動板式可変容量圧縮機における揺動板回転阻止機構を含む要部の分解斜視図を示している。図３は、図１の揺動板式可変容量圧縮機における揺動板回転阻止機構の一形態例を示している。 FIG. 1 is an example of the entire basic configuration of a swing plate type variable displacement compressor according to the present invention, and shows an operating state at the maximum discharge capacity. FIG. 2 is an exploded perspective view of the main part including the rocking plate rotation prevention mechanism in the rocking plate type variable displacement compressor of FIG. FIG. 3 shows an example of a rocking plate rotation prevention mechanism in the rocking plate type variable displacement compressor of FIG.

　この揺動板式可変容量圧縮機１は、回転主軸と共に回転する斜板の回転主軸に対する傾斜角を可変して、斜板の回転に伴って回転主軸に対して揺動する揺動板の揺動幅を変更することにより、ピストンのストローク量を変更してシリンダボアからの冷媒吐出容量を可変するものである。 This oscillating plate type variable capacity compressor 1 varies the inclination angle of the swash plate that rotates with the rotating main shaft with respect to the rotating main shaft, and swings the oscillating plate that swings with respect to the rotating main shaft as the swash plate rotates. By changing the width, the stroke amount of the piston is changed to vary the refrigerant discharge capacity from the cylinder bore.

　図１において、揺動板式可変容量圧縮機１は、中央部に配置されたハウジング２と、その両側に配置されたフロントハウジング３及びリアハウジング４を有し、外部から回転駆動動力が入力される回転主軸５が、フロントハウジング３からハウジング２部分まで貫通して設けられている。回転主軸５は、フロントハウジング３側の軸受３３（ラジアル軸受）とハウジング側の軸受２２（ラジアル軸受）で回転可能に支持され、ロータ６が回転主軸５に一体回転可能に固定されている。ロータ６には、ヒンジ機構７を介して斜板８が変角可能に且つ回転主軸５と共に回転可能に連結されている。ハウジング２周縁部に配置された各シリンダボア９内には、それぞれピストン１０が往復動可能に挿入されており、ピストン１０は、コネクティングロッド１１を介して揺動板１２に連結されている。斜板８の回転に伴って揺動板１２が揺動することにより、コネクティングロッド１１を介してピストン１０が往復動される。このピストン１０の往復動に伴って、リアハウジング４の内部周縁部に形成された吸入室１３から被圧縮流体（例えば、冷媒ガス）が、バルブプレート１４に形成された吸入孔１５（吸入弁は図示省略）を通してシリンダボア９に吸入され、吸入された被圧縮流体は圧縮された後、圧縮流体が吐出孔１６（吐出弁は図示省略）を通してリアハウジング４の内部中央部に形成された吐出室１７内に吐出され、そこから外部回路へと送られる。 In FIG. 1, a rocking plate type variable capacity compressor 1 has a housing 2 disposed at the center, a front housing 3 and a rear housing 4 disposed on both sides thereof, and rotational driving power is input from the outside. A rotation main shaft 5 is provided so as to penetrate from the front housing 3 to the housing 2 portion. The rotation main shaft 5 is rotatably supported by a bearing 33 (radial bearing) on the front housing 3 side and a bearing 22 (radial bearing) on the housing side, and the rotor 6 is fixed to the rotation main shaft 5 so as to be integrally rotatable. A swash plate 8 is connected to the rotor 6 via a hinge mechanism 7 so that the swash plate 8 can be turned and can be rotated together with the rotary main shaft 5. A piston 10 is inserted into each cylinder bore 9 disposed on the peripheral edge of the housing 2 so as to be able to reciprocate. The piston 10 is connected to the swing plate 12 via a connecting rod 11. As the swash plate 8 rotates, the swing plate 12 swings, so that the piston 10 is reciprocated through the connecting rod 11. As the piston 10 reciprocates, a fluid to be compressed (for example, a refrigerant gas) from a suction chamber 13 formed in the inner peripheral edge of the rear housing 4 is sucked into a suction hole 15 (suction valve is a suction valve) formed in the valve plate 14. The compressed fluid sucked into the cylinder bore 9 is compressed through a discharge hole 16 (a discharge valve is not shown), and then the discharge chamber 17 formed in the center of the interior of the rear housing 4 is discharged. It is discharged into the inside and sent from there to an external circuit.

　前記揺動板１２は、回転が阻止された状態で揺動運動する必要がある。以下に、この揺動板１２の回転阻止機構を主体に、揺動板式可変容量圧縮機１の残りの部位について、図１及び図２を参照しながら説明する。 The oscillating plate 12 needs to oscillate while being prevented from rotating. Hereinafter, the remaining portion of the swing plate type variable displacement compressor 1 will be described with reference to FIGS.

　揺動板１２の回転阻止機構２１は、回転主軸５の軸方向に移動可能で後述する内輪回転阻止機構によって回転主軸５回りの回転が阻止されると共に、動力伝達用に設けられた複数のボール２５をガイドするための複数のガイド溝２６を有する内輪２７と、揺動板１２の揺動運動の揺動中心部材として機能し、回転主軸５上に軸受２３（ラジアル軸受）を介して回転主軸５に対し相対回転可能及び軸方向移動可能に設けられ、内輪２７と共に軸方向に移動可能に内輪２７に係合されたスリーブ２４と、斜板８に軸受２９（ラジアル軸受）を介して取付けられ、外周部に揺動板１２が固定連結され、斜板８の回転により揺動板１２を揺動させると共に、内輪２７の各ガイド溝２６に対向する位置にボール２５をガイドするための複数のガイド溝２８を有する外輪３０と、内輪２７及び外輪３０に形成された互いに対向するガイド溝２６、２８によって保持され、両ガイド溝２６、２８間で圧縮されることにより動力伝達を行う前述の複数のボール２５と、を備えて構成されている。そして、外輪３０は、互いのガイド溝２６，２８とボール２５との球面接触を介して内輪２７に対してスリーブ２４を中心に揺動可能である。また、内輪２７側からの回転阻止力がガイド溝２６，２８とボール２５との球面接触を介して外輪３０側に伝達される。ここで、前記ボール２５と、スリーブ２４が本発明の連結機構を構成している。尚、揺動板１２と斜板８との間及びロータ６とフロントハウジング３との間には、それぞれスラスト軸受３１、３２が介装されている。 The rotation prevention mechanism 21 of the swing plate 12 is movable in the axial direction of the rotation main shaft 5 and is prevented from rotating around the rotation main shaft 5 by an inner ring rotation prevention mechanism described later, and a plurality of balls provided for power transmission. An inner ring 27 having a plurality of guide grooves 26 for guiding 25 and a swing center member for swinging motion of the swing plate 12, and the rotating main shaft 5 via a bearing 23 (radial bearing) on the rotating main shaft 5. 5 is attached to the swash plate 8 via a bearing 29 (radial bearing) and a sleeve 24 engaged with the inner ring 27 so as to be rotatable relative to the inner ring 5 and movable in the axial direction. The swinging plate 12 is fixedly connected to the outer peripheral portion, and the swinging plate 12 is swung by the rotation of the swash plate 8 and a plurality of guides for guiding the ball 25 to positions facing the respective guide grooves 26 of the inner ring 27. Guide groove 8 and the plurality of balls described above that are held by

guide grooves

26 and 28 that are formed on the inner ring 27 and the outer ring 30 and that are opposed to each other and are compressed between the

guide grooves

26 and 28 to transmit power. 25. The outer ring 30 can swing around the sleeve 24 with respect to the inner ring 27 through spherical contact between the

guide grooves

26 and 28 and the ball 25. Further, the rotation preventing force from the inner ring 27 side is transmitted to the outer ring 30 side through spherical contact between the

guide grooves

26 and 28 and the ball 25. Here, the said ball | bowl 25 and the sleeve 24 comprise the connection mechanism of this invention.

Thrust bearings

31 and 32 are interposed between the swing plate 12 and the swash plate 8 and between the rotor 6 and the front housing 3, respectively.

　上記のように構成された揺動板１２の回転阻止機構２１においては、外輪３０は球面接触を介してスリーブ２４に揺動可能に支持され、スリーブ２４は回転主軸５に回転可能に且つ軸方向に移動可能に支持されていることにより、回転主軸５と揺動機構部全体との間の径方向ガタを小さくすることが可能であり、信頼性の向上、振動、騒音の低減が可能となる。 In the rotation prevention mechanism 21 of the swing plate 12 configured as described above, the outer ring 30 is supported by the sleeve 24 via a spherical contact so as to be swingable, and the sleeve 24 is rotatable about the rotary spindle 5 and axially. Movably supported, the radial play between the rotation main shaft 5 and the entire swinging mechanism portion can be reduced, and reliability can be improved and vibration and noise can be reduced. .

　また、上記実施形態では、回転主軸５は、軸受２２，３３（ラジアル軸受）で両持ち支持されているので、比較的小径の回転主軸５であっても十分に高い剛性を確保でき、回転主軸５の振れ回りも小さく抑えることが可能であり、容易に小型化を図ることが可能になると共に、信頼性の向上、振動、騒音の低減が可能となる。また、回転主軸５の振れ回りが小さく抑えられる結果、回転主軸５と共に回転される回転部位全体の振れ回りも小さく抑えられ、回転部全体の回転バランスは極めて良くなる。 In the above embodiment, since the rotary main shaft 5 is supported at both ends by the bearings 22 and 33 (radial bearings), sufficiently high rigidity can be ensured even if the rotary main shaft 5 has a relatively small diameter. 5 can be kept small, and it is possible to easily reduce the size, improve reliability, and reduce vibration and noise. Further, as a result of suppressing the swing of the rotating main shaft 5 to be small, the swing of the entire rotating part rotated together with the rotating main shaft 5 is also suppressed to be small, and the rotation balance of the entire rotating portion is extremely improved.

　また、上記実施形態では、内輪２７の内径側に形成された球面（凹球面）と、スリーブ２４の外径側に形成された球面（凸球面）との係合により、両者の間で相互支持が行われており、この支持部のクリアランスを調整することにより、動力伝達用として作用する複数のボール２５のガイド溝位置のバラツキによる内、外輪２７，３０の相対的な振れ回りを吸収することが可能であり、それによって一層ボール２５の均等で連続的な接触が可能となり、信頼性、振動、騒音面で一層有利となっている。 In the above-described embodiment, the spherical surface (concave spherical surface) formed on the inner diameter side of the inner ring 27 and the spherical surface (convex spherical surface) formed on the outer diameter side of the sleeve 24 are mutually supported. By adjusting the clearance of the support portion, the relative swing of the inner and

outer rings

27 and 30 due to variations in the guide groove positions of the plurality of balls 25 acting for power transmission can be absorbed. As a result, the balls 25 can be evenly and continuously in contact with each other, which is more advantageous in terms of reliability, vibration and noise.

　尚、上記実施形態では、外輪３０と揺動板１２とを別部材に構成し、それらを互いに固定する構成としたが、これらは一体に形成することもできる。この一体化により更なる部品点数の削減と、組立の容易化を図ることができる。 In the above-described embodiment, the outer ring 30 and the swing plate 12 are configured as separate members and fixed to each other. However, they can be integrally formed. This integration can further reduce the number of parts and facilitate assembly.

　図３は、揺動板１２の回転阻止機構２１において、内、外輪２７，３０の相対角度がゼロの状態を示している。図３（Ａ）に示すように、揺動板回転阻止機構２１の内輪２７及び外輪３０に形成されるガイド溝２６、２８が回転主軸５の中心軸に対して相対角度（３０～６０度の範囲内の相対角度）をもって配置されている。そして、一つのボールガイド４１を構成し、互いに対向する、内輪２７に形成されたガイド溝２６（ガイド溝２６の軸は４２で表示）と外輪３０に形成されたガイド溝２８（ガイド溝２８の軸は４３で表示）とが、内輪２７の軸と外輪３０の軸との相対角度がゼロの状態にて回転主軸５に垂直で且つ揺動板１２の揺動中心を通る平面４４に対し対称形態になるように配置されている。このガイド溝２６の軸４２とガイド溝２８の軸４３との交点上にボール２５が規制、支持される。また、図３（Ｂ）に示すように、揺動板回転阻止機構２１の複数のボールガイド４１のうち、隣り合った２つのボールガイドを一対とし、この一対のボールガイド４５におけるそれぞれのボールガイド４１が、換言すれば、この部分における内、外輪に形成されたガイド溝の軸４６が、互いに平行に配置されている構成とすることができる。この構成により、前述の如く、揺動板回転阻止機構部の回転方向ガタは、内、外輪２７，３０に設置された一組のガイド溝底間距離とボール球径の関係で概ね決まるため、クリアランスの設定、管理が容易となり、適正なクリアランスの設定によりガタを小さく抑えることが可能となる。そして、複数のボール２５は、各ボール２５を挟み込んで向き合ったガイド溝２６、２８間で圧縮方向に支持され動力伝達を行う。ボール２５は、向き合ったガイド溝２６、２８に抱き抱えられるように保持されて両ガイド溝２６、２８に接触するので、ボール２５とそれぞれのガイド溝２６、２８間の接触面積を十分に大きく確保できるようになり、接触面圧を低減することが可能になって、信頼性、振動、静粛性の面で極めて有利な構造となる。また、ボール２５の球径を小さくすることも可能で、揺動板回転阻止機構２１全体の小型化が可能となる。 FIG. 3 shows a state in which the relative angle between the inner and

outer rings

27 and 30 is zero in the rotation blocking mechanism 21 of the swing plate 12. As shown in FIG. 3A, the

guide grooves

26 and 28 formed in the inner ring 27 and the outer ring 30 of the swing plate rotation preventing mechanism 21 are at a relative angle (30 to 60 degrees) with respect to the central axis of the rotation main shaft 5. Relative angle within range). A guide groove 26 formed on the inner ring 27 (the axis of the guide groove 26 is indicated by 42) and a guide groove 28 formed on the outer ring 30 (the guide groove 28 of the guide groove 28) constitute one ball guide 41 and face each other. Is symmetrical with respect to a plane 44 that is perpendicular to the main spindle 5 and passes through the oscillation center of the oscillation plate 12 when the relative angle between the axis of the inner ring 27 and the axis of the outer ring 30 is zero. It is arranged to be in form. The ball 25 is regulated and supported on the intersection of the shaft 42 of the guide groove 26 and the shaft 43 of the guide groove 28. Further, as shown in FIG. 3B, of the plurality of ball guides 41 of the swing plate rotation preventing mechanism 21, two adjacent ball guides are paired, and each of the ball guides in the pair of ball guides 45. In other words, the guide groove shaft 46 formed in the outer ring in this portion can be configured in parallel with each other. With this configuration, as described above, the rotation direction backlash of the rocking plate rotation prevention mechanism is largely determined by the relationship between the distance between the bottom of the pair of guide grooves installed on the inner and

outer rings

27 and 30 and the ball ball diameter. Clearance can be easily set and managed, and play can be reduced by setting an appropriate clearance. The plurality of balls 25 are supported in the compression direction between the

guide grooves

26 and 28 facing each other with the balls 25 interposed therebetween, and transmit power. Since the ball 25 is held so as to be held by the opposing

guide grooves

26 and 28 and contacts both the

guide grooves

26 and 28, a sufficiently large contact area between the ball 25 and the

respective guide grooves

26 and 28 is ensured. As a result, the contact surface pressure can be reduced, and the structure is extremely advantageous in terms of reliability, vibration, and quietness. Further, the ball diameter of the ball 25 can be reduced, and the entire swing plate rotation prevention mechanism 21 can be downsized.

　また、回転主軸５を中心としたモーメントとして与えられるボール２５にかかる負荷は、実接触面の垂直抗力として発生する。モーメントの方向に対する接触面法線の傾きが小さいほど、接触荷重が小さくなり、上記の如く平行に配置された一対のボールガイド４５が、回転主軸５の中心軸５ａを含む平面に対し対称に配置されていることにより、換言すれば、内、外輪２７，３０に形成された２組のガイド溝の軸４６が回転主軸５の中心軸５ａを含む平面に対し対称に配置されていることにより、回転方向を選ばない揺動板回転阻止機構として、ボール接触荷重を最小とすることが可能である。 Also, a load applied to the ball 25 given as a moment about the rotation spindle 5 is generated as a normal force of the actual contact surface. The smaller the inclination of the contact surface normal with respect to the moment direction, the smaller the contact load, and the pair of ball guides 45 arranged in parallel as described above are arranged symmetrically with respect to the plane including the central axis 5a of the rotation main shaft 5. In other words, the shafts 46 of the two sets of guide grooves formed in the inner and

outer rings

27 and 30 are arranged symmetrically with respect to the plane including the central axis 5a of the rotation main shaft 5, As a rocking plate rotation prevention mechanism that does not select the rotation direction, it is possible to minimize the ball contact load.

　上記のような揺動板式可変容量圧縮機１において、回転主軸５の回転時に、ハウジング２の内周面と内輪２７の外周面とを互いに当接させる当接構造により内輪２７の回転を阻止する本発明の特徴的な内輪回転阻止機構が設けられている。 In the oscillating plate variable displacement compressor 1 as described above, the rotation of the inner ring 27 is prevented by a contact structure that abuts the inner peripheral surface of the housing 2 and the outer peripheral surface of the inner ring 27 when the rotary main shaft 5 rotates. A characteristic inner ring rotation prevention mechanism of the present invention is provided.

　以下に、本発明の内輪回転阻止機構の種々の実施形態について説明する。
　図４は、内輪回転阻止機構の第１実施形態を示し、（Ａ）は内輪２７の斜視図であり、（Ｂ）はフロントハウジング側から見た内輪２７とハウジング２による内輪回転阻止機構部の図であり（Ｃ）は（Ｂ）の当接構造部の拡大図を示している。尚、以下の図４～図９の各実施形態について同一要素には同一符号を付すものとする。 Various embodiments of the inner ring rotation prevention mechanism of the present invention will be described below.
4A and 4B show a first embodiment of the inner ring rotation prevention mechanism, in which FIG. 4A is a perspective view of the inner ring 27, and FIG. 4B is an inner ring rotation prevention mechanism portion of the inner ring 27 and the housing 2 viewed from the front housing side. It is a figure and (C) has shown the enlarged view of the contact structure part of (B). In the following embodiments shown in FIGS. 4 to 9, the same elements are denoted by the same reference numerals.

　図４（Ａ）～（Ｃ）に示すように、本実施形態の内輪２７は、外周面が略三角形状に形成された３つの周面から構成され、隣合う周面と周面のなす角は６０°である。また、ハウジング２の内周面も、内輪２７の外周面に対応させて略三角形状に形成された３つの周面から構成され、隣合う周面と周面のなす角は６０°である。内輪２７の各周面は同一の表面形状を有し、内輪２７の回転方向と反対側の端縁部２７ｃ側に形成した当接面２７Ａと非当接面２７Ｂとからなる。当接面２７Ａと非当接面２７Ｂは、ハウジング２の周面に対する間隔が非当接面２７Ｂの方が大きくなるように段差Ｈ（同図（Ｃ）参照）を有し、非当接面２７Ｂは鋳肌面であるが、当接面２７Ａは表面を加工した加工面であり、ハウジング２の周面に対して平行な平面部２７ａと、この平面部２７ａから周方向の端縁部２７ｃに向かうにつれハウジング２の周面から遠ざかるように、言い換えれば、ハウジング２の周面と内輪２７の周面とが正対したときに互いの面間の隙間が周方向の端縁部２７ｃに向かうにつれて増大するように傾斜させた平面からなる傾斜面２７ｂと、端縁部２７ｃと、により構成されている。当接面２７Ａの軸方向の長さＬ（（同図（Ａ）参照））は端面より１０～１５ｍｍであり、当接面２７Ａの平面部２７ａと非当接面２７Ｂの前記段差（高さの差）Ｈは０．５～２ｍｍである。また、傾斜面２７ｂは平面部２７ａに対する傾斜角θが１°以上５°未満の角度範囲で傾斜している。更に、当接面２７ａの周方向の端縁部２７ｃは傾斜面２７ｂに続く曲面となっている。尚、図中、５１は回転主軸５の貫通孔である。ここで、本明細書における「当接面」とは、内輪２７が回動したときにハウジング２の周面と接触する接触部を含む加工面全体を示し、ハウジング２側の周面と必ず接触することを示すものではない。 As shown in FIGS. 4A to 4C, the inner ring 27 of the present embodiment is composed of three peripheral surfaces whose outer peripheral surfaces are formed in a substantially triangular shape, and an angle formed between the adjacent peripheral surfaces and the peripheral surfaces. Is 60 °. The inner peripheral surface of the housing 2 is also composed of three peripheral surfaces formed in a substantially triangular shape so as to correspond to the outer peripheral surface of the inner ring 27, and the angle formed between the adjacent peripheral surfaces is 60 °. Each peripheral surface of the inner ring 27 has the same surface shape, and is composed of a contact surface 27A and a non-contact surface 27B formed on the side of the edge 27c opposite to the rotation direction of the inner ring 27. The contact surface 27A and the non-contact surface 27B have a step H (see FIG. 10C) so that the distance from the peripheral surface of the housing 2 is larger on the non-contact surface 27B. 27B is a casting surface, but the contact surface 27A is a processed surface obtained by processing the surface, and a flat surface portion 27a parallel to the peripheral surface of the housing 2, and an edge portion 27c in the circumferential direction from the flat surface portion 27a. The clearance between the surfaces of the housing 2 and the inner ring 27 faces toward the end edge 27c in the circumferential direction so as to move away from the peripheral surface of the housing 2 in other words. It is comprised by the inclined surface 27b which consists of a plane inclined so that it may increase, and the edge part 27c. The length L in the axial direction of the contact surface 27A (see FIG. 5A) is 10 to 15 mm from the end surface, and the step (height) between the flat portion 27a of the contact surface 27A and the non-contact surface 27B. The difference H) is 0.5 to 2 mm. Further, the inclined surface 27b is inclined in an angle range where the inclination angle θ with respect to the flat portion 27a is 1 ° or more and less than 5 °. Furthermore, the circumferential edge 27c of the contact surface 27a is a curved surface that follows the inclined surface 27b. In the figure, reference numeral 51 denotes a through hole of the rotary main shaft 5. Here, the “contact surface” in the present specification indicates the entire processing surface including a contact portion that comes into contact with the peripheral surface of the housing 2 when the inner ring 27 rotates, and is always in contact with the peripheral surface on the housing 2 side. It does not indicate what to do.

　かかる構成によれば、図４（Ｂ）において回転主軸５の回転に伴って内輪２７がハウジング２に対して時計回り（図中の矢印方向）に回動したとき、内輪２７の当接面２７Ａの傾斜面２７ｂがハウジング２の周面に略面接触の状態で当接して内輪２７の回転が阻止される。この場合、内輪２７の回動角と傾斜面２７ｂの傾斜角を略同じに設定することが望ましい。面接触は従来の線接触と比較し接触面積を大きく確保することができるため、ハウジング２周面に作用する内輪２７周面からの面圧を軽減でき、内輪２７（素材が鉄系（例えばクロムモリブデン鋼）である）より軟らかいハウジング２（素材がアルミ系である）の摩耗を抑制できる。加えて、内輪２７の傾斜面２７ｂに接続する端縁部２７ｃを曲面としているため、傾斜面２７ｂの周方向端部における局所的な線接触を抑制できると共に、内輪２７がハウジング２内で軸方向に移動した際の引っ掛かり等による過剰な摩耗の発生を抑制でき、しかも、内輪２７の軸方向の移動が滑らかとなるため容量制御特性も向上する。更に加えて、内輪２７を三角形状に形成したので、他の多角形状の場合に比べて、内輪２７の回転中心からハウジング２周面に当接する内輪２７端縁部までの距離が長いので、ハウジング２周面に対する当接時の面圧を小さくできる。以上から、ハウジング２内周面の摩耗を軽減でき、内輪回転阻止機構における耐摩耗性の向上を図ることができる。加えて、内輪２７の軸方向の移動が滑らかとなり、揺動板式可変容量圧縮機１の容量制御特性も向上できるようになる。
　尚、内輪２７がハウジング２に対して回動したとき、通常は、内輪２７側周面とハウジング２側周面とは回動方向と反対側の端縁部領域でのみ接触するので、当接面２７Ａは１つの周面において接触する端縁部側の１箇所でよい。 According to such a configuration, when the inner ring 27 rotates clockwise (in the direction of the arrow in the drawing) with respect to the housing 2 as the rotating main shaft 5 rotates in FIG. The inclined surface 27b comes into contact with the peripheral surface of the housing 2 in a substantially surface contact state to prevent the inner ring 27 from rotating. In this case, it is desirable to set the rotation angle of the inner ring 27 and the inclination angle of the inclined surface 27b to be substantially the same. Since the surface contact can secure a large contact area compared to the conventional line contact, the surface pressure from the peripheral surface of the inner ring 27 acting on the peripheral surface of the housing 2 can be reduced, and the inner ring 27 (the material is iron-based (for example, chromium) Molybdenum steel), which is softer than the housing 2 (the material is aluminum), can be suppressed. In addition, since the end edge portion 27c connected to the inclined surface 27b of the inner ring 27 is a curved surface, local line contact at the circumferential end portion of the inclined surface 27b can be suppressed, and the inner ring 27 is axial in the housing 2 The occurrence of excessive wear due to catching or the like at the time of the movement of the inner ring 27 can be suppressed, and the axial movement of the inner ring 27 becomes smooth, so that the capacity control characteristics are also improved. In addition, since the inner ring 27 is formed in a triangular shape, the distance from the center of rotation of the inner ring 27 to the edge of the inner ring 27 that contacts the circumferential surface of the housing is longer than in the case of other polygonal shapes. The surface pressure at the time of contact with the two circumferential surfaces can be reduced. As described above, the wear on the inner peripheral surface of the housing 2 can be reduced, and the wear resistance of the inner ring rotation prevention mechanism can be improved. In addition, the axial movement of the inner ring 27 becomes smooth, and the capacity control characteristics of the swing plate type variable capacity compressor 1 can be improved.
When the inner ring 27 is rotated with respect to the housing 2, normally, the inner ring 27 side circumferential surface and the housing 2 side circumferential surface are in contact with each other only in the edge region opposite to the rotation direction. The surface 27A may be one place on the edge side that contacts on one peripheral surface.

　図５は、内輪回転阻止機構の第２実施形態を示し、（Ａ）は内輪２７の斜視図であり、（Ｂ）はフロントハウジング側から見た内輪２７とハウジング２による内輪回転阻止機構部の図であり（Ｃ）は（Ｂ）の当接構造部の拡大図を示している。 5A and 5B show a second embodiment of the inner ring rotation prevention mechanism, wherein FIG. 5A is a perspective view of the inner ring 27, and FIG. 5B is an inner ring rotation prevention mechanism portion formed by the inner ring 27 and the housing 2 as viewed from the front housing side. It is a figure and (C) has shown the enlarged view of the contact structure part of (B).

　図５（Ａ）～（Ｃ）に示すように、本実施形態の内輪２７とハウジング２は、外周面と内周面が略三角形状に形成された３つの周面から構成され、隣合う周面と周面のなす角は６０°であることは図４の第１実施形態と同様である。第１実施形態と異なるのは、内輪２７の各周面に、両端縁部に亘って表面が加工された当接面２７Ａが形成されている点が異なる。この当接面２７Ａの内輪回転方向と反対側の端縁部２７ｃ側領域に、第１実施形態と同様に、ハウジング２の周面に対して平行な平面部２７ａと、この平面部２７ａに続く平面からなる傾斜面２７ｂ（傾斜角θが１°以上５°未満の角度範囲で傾斜）とが形成され、傾斜面２７ｂに続く端縁部２７ｃが曲面に形成されている。当接面２７Ａの軸方向の長さＬ（（同図（Ａ）参照））は端面より１０～１５ｍｍである。 As shown in FIGS. 5 (A) to (C), the inner ring 27 and the housing 2 of this embodiment are composed of three peripheral surfaces in which the outer peripheral surface and the inner peripheral surface are formed in a substantially triangular shape, and adjacent peripheral surfaces. The angle between the surface and the peripheral surface is 60 °, as in the first embodiment of FIG. The difference from the first embodiment is that a contact surface 27A whose surface is processed over both edge portions is formed on each peripheral surface of the inner ring 27. Similar to the first embodiment, a flat surface portion 27a parallel to the peripheral surface of the housing 2 is provided in the region on the side of the edge 27c opposite to the inner ring rotation direction of the contact surface 27A, and the flat surface portion 27a. A flat inclined surface 27b (inclined in an angle range where the inclination angle θ is 1 ° or more and less than 5 °) is formed, and an edge portion 27c following the inclined surface 27b is formed in a curved surface. The length L in the axial direction of the abutting surface 27A (see FIG. 5A) is 10 to 15 mm from the end surface.

　かかる構成によれば、回転主軸５の回転に伴って内輪２７がハウジング２に対して時計回り方向（図中の矢印方向）に回動したとき、内輪２７の当接面２７Ａの傾斜面２７ｂがハウジング２の周面に略面接触して内輪２７の回転が阻止されることは、第１実施形態と同じであり、第１実施形態と同様の作用効果を奏することができる。加えて、内輪２７の回動時に略面接触する端縁部２７ｃ側と反対側の端縁部領域におけるハウジング２周面と内輪２７の当接面２７Ａとの隙間を小さくできるため、内輪２７に逆方向の回動（反時計回り方向）動作が発生した際、内輪２７のがたつきを少なくすることができるという作用効果を有する。 According to this configuration, when the inner ring 27 rotates in the clockwise direction (the arrow direction in the drawing) with respect to the housing 2 as the rotary main shaft 5 rotates, the inclined surface 27b of the contact surface 27A of the inner ring 27 is The fact that the inner ring 27 is prevented from rotating by substantially contacting the peripheral surface of the housing 2 is the same as in the first embodiment, and the same effects as in the first embodiment can be achieved. In addition, since the gap between the peripheral surface of the housing 2 and the contact surface 27A of the inner ring 27 in the end edge region opposite to the side of the end edge 27c, which is substantially in surface contact with the inner ring 27, can be reduced. When a reverse rotation (counterclockwise direction) operation occurs, the inner ring 27 can be reduced in shakiness.

　図６は、内輪回転阻止機構の第３実施形態を示し、（Ａ）は内輪２７の斜視図であり、（Ｂ）はフロントハウジング側から見た内輪２７とハウジング２による内輪回転阻止機構部の図であり（Ｃ）は（Ｂ）の当接構造部の拡大図を示している。 6A and 6B show a third embodiment of the inner ring rotation prevention mechanism, wherein FIG. 6A is a perspective view of the inner ring 27, and FIG. 6B is an inner ring rotation prevention mechanism portion of the inner ring 27 and the housing 2 viewed from the front housing side. It is a figure and (C) has shown the enlarged view of the contact structure part of (B).

　図６（Ａ）～（Ｃ）に示すように、本実施形態の内輪回転阻止機構は、内輪２７の各周面の両端縁部領域に、それぞれ第１及び第２当接面２７Ａ，２７Ａ′を形成した点が図４に示す第１実施形態と異なる。内輪２７の回動方向（図６（Ｂ）の矢印方向）と反対側の端縁部２７ｃ側の第１当接面２７Ａは、第１実施形態と同様に、平面部２７ａと傾斜面２７ｂが形成され端縁部２７ｃを曲面としている。一方、反対側の端縁部領域に形成した第２当接面２７Ａ′は、第１当接面２７Ａの平面部２７ａと面一な平面が形成されているだけである。 As shown in FIGS. 6 (A) to 6 (C), the inner ring rotation prevention mechanism of the present embodiment has first and second contact surfaces 27A and 27A ′ in the edge region of each peripheral surface of the inner ring 27, respectively. 4 is different from the first embodiment shown in FIG. As in the first embodiment, the first contact surface 27A on the side of the edge 27c opposite to the direction of rotation of the inner ring 27 (the arrow direction in FIG. 6B) has a flat surface portion 27a and an inclined surface 27b. The formed edge 27c is a curved surface. On the other hand, the second contact surface 27A ′ formed in the opposite edge region is only formed with a flat surface that is flush with the flat portion 27a of the first contact surface 27A.

　かかる構成によれば、第１実施形態と同様の作用効果に加えて、第２実施形態と同様に、内輪２７の回動方向と反対側の端縁部領域におけるハウジング２周面と内輪２７の第２当接面２７Ａ′との隙間を小さくでき、内輪２７の逆方向回動（反時計回り方向）時に、内輪２７のがたつきを少なくすることができる。また、図５の第２実施形態と比較した場合、内輪２７の周面における当接面形成のための加工面積を小さくできるため、生産性を向上できる。 According to such a configuration, in addition to the same effects as in the first embodiment, the housing 2 peripheral surface and the inner ring 27 in the edge region opposite to the rotational direction of the inner ring 27 are the same as in the second embodiment. The gap with the second contact surface 27A ′ can be reduced, and rattling of the inner ring 27 can be reduced when the inner ring 27 rotates in the reverse direction (counterclockwise direction). Further, when compared with the second embodiment of FIG. 5, the processing area for forming the contact surface on the peripheral surface of the inner ring 27 can be reduced, so that productivity can be improved.

　図７は、内輪回転阻止機構の第４実施形態を示し、（Ａ）は内輪２７の斜視図であり、（Ｂ）はフロントハウジング側から見た内輪２７とハウジング２による内輪回転阻止機構部の図であり（Ｃ）は（Ｂ）の当接構造部の拡大図を示している。 7A and 7B show a fourth embodiment of the inner ring rotation prevention mechanism, wherein FIG. 7A is a perspective view of the inner ring 27, and FIG. 7B is an inner ring rotation prevention mechanism portion formed by the inner ring 27 and the housing 2 as viewed from the front housing side. It is a figure and (C) has shown the enlarged view of the contact structure part of (B).

　本実施形態は、当接面２７Ａの傾斜面２７ｂが平面ではなく曲面である点が図４に示す第１実施形態と異なるだけで、その他の構成は第１実施形態と同じである。かかる第４実施形態によれば、ハウジング２の周面に曲面の傾斜面２７ｂが接触するので、ハウジング周面に対して従来のエッジ状の端縁部が接触する局所的な線接触と比較してハウジング２周面の摩耗を抑制でき、第１実施形態と同様の作用効果が得られる。 This embodiment is the same as the first embodiment except that the inclined surface 27b of the contact surface 27A is not a flat surface but a curved surface, except for the first embodiment shown in FIG. According to the fourth embodiment, since the curved inclined surface 27b is in contact with the peripheral surface of the housing 2, it is compared with the local line contact in which the edge portion of the conventional edge contacts the peripheral surface of the housing. Thus, the wear on the peripheral surface of the housing 2 can be suppressed, and the same effect as the first embodiment can be obtained.

　図８は、内輪回転阻止機構の第５実施形態を示し、（Ａ）は内輪２７の斜視図であり、（Ｂ）はフロントハウジング側から見た内輪２７とハウジング２による内輪回転阻止機構部の図であり（Ｃ）は（Ｂ）の当接構造部の拡大図を示している。 8A and 8B show a fifth embodiment of the inner ring rotation prevention mechanism, wherein FIG. 8A is a perspective view of the inner ring 27, and FIG. 8B shows an inner ring rotation prevention mechanism portion of the inner ring 27 and the housing 2 as viewed from the front housing side. It is a figure and (C) has shown the enlarged view of the contact structure part of (B).

　本実施形態は、当接面２７Ａが第１実施形態等における平面部２７ａはなく、曲面からなる傾斜面２７ｂと端縁部２７ｃとで形成されている点で第１実施形態と異なる。その他の構成は第１実施形態と同じである。かかる第５実施形態によっても、ハウジング２内周面の摩耗を軽減でき、内輪回転阻止機構における耐摩耗性の向上を図ることができる。加えて、内輪２７の軸方向の移動が滑らかとなり、揺動板式可変容量圧縮機１の容量制御特性も向上できるようになる。 This embodiment is different from the first embodiment in that the contact surface 27A is not the flat surface portion 27a in the first embodiment or the like, but is formed by a curved inclined surface 27b and an end edge portion 27c. Other configurations are the same as those of the first embodiment. Also according to the fifth embodiment, the wear on the inner peripheral surface of the housing 2 can be reduced, and the wear resistance in the inner ring rotation prevention mechanism can be improved. In addition, the axial movement of the inner ring 27 becomes smooth, and the capacity control characteristics of the swing plate type variable capacity compressor 1 can be improved.

　図９は、内輪回転阻止機構の第６実施形態を示し、（Ａ）はフロントハウジング側から見た内輪２７とハウジング２による内輪回転阻止機構部の図であり（Ｂ）は（Ａ）の当接構造部の拡大図を示している。 9A and 9B show a sixth embodiment of the inner ring rotation prevention mechanism, wherein FIG. 9A is a view of the inner ring rotation prevention mechanism portion by the inner ring 27 and the housing 2 as viewed from the front housing side, and FIG. The enlarged view of a contact structure part is shown.

　本実施形態は、ハウジング２側に傾斜面を形成した例である。図９（Ａ）、（Ｂ）において、本実施形態の内輪２７とハウジング２は、外周面と内周面が略三角形状に形成された３つの周面から構成され、隣合う周面と周面のなす角は６０°であることは上記の各実施形態と同様である。本実施形態の内輪２７は、第２実施形態と同様に、各周面の両端縁部に亘って表面が加工された当接面２７Ａが形成されているが、この当接面２７Ａは、傾斜面はなく面一の平面部で形成されている。一方、ハウジング２の各周面２Ａは、内輪２７の当接面２７Ａと平行な平面部２ａと、この平面部２ａの一方の周方向の端縁部側に平面部２ａに続いて端縁部に向かうにつれ内輪２７の当接面２７Ａから遠ざかるように、言い換えれば、ハウジング２の周面２Ａと内輪２７の当接面２７Ａとが正対したときに互いの面間の隙間が周方向の端縁部に向かうにつれて増大するように、傾斜させた平面からなる傾斜面２ｂと、により構成されている。前記傾斜面２ｂは、隣接する平面部２ａに対する傾斜角θが１°以上５°未満の角度範囲で傾斜している。 This embodiment is an example in which an inclined surface is formed on the housing 2 side. 9 (A) and 9 (B), the inner ring 27 and the housing 2 of this embodiment are composed of three peripheral surfaces in which the outer peripheral surface and the inner peripheral surface are formed in a substantially triangular shape, and the adjacent peripheral surface and peripheral The angle formed by the surfaces is 60 °, as in the above embodiments. As in the second embodiment, the inner ring 27 of the present embodiment is formed with a contact surface 27A whose surface is processed across both edge portions of each peripheral surface. The contact surface 27A is inclined. There is no surface and it is formed by a flat surface portion. On the other hand, each peripheral surface 2A of the housing 2 has a flat surface portion 2a parallel to the contact surface 27A of the inner ring 27, and an end edge portion following the flat surface portion 2a on one peripheral edge side of the flat surface portion 2a. As the distance from the contact surface 27A of the inner ring 27 increases, the clearance between the surfaces of the housing 2 and the contact surface 27A of the inner ring 27 faces each other in the circumferential direction. It is comprised by the inclined surface 2b which consists of an inclined plane so that it may increase as it goes to an edge. The inclined surface 2b is inclined in an angle range in which the inclination angle θ with respect to the adjacent flat portion 2a is 1 ° or more and less than 5 °.

　かかる構成によれば、回転主軸５の回転に伴って内輪２７がハウジング２に対して時計回り（９図（Ａ）中の矢印方向）に回動したとき、内輪２７の当接面２７Ａがハウジング２の傾斜面２ｂに略面接触の状態で当接して内輪２７の回転が阻止される。この場合、内輪２７の回動角と傾斜面２ｂの傾斜角を略同じに設定することが望ましい。これにより、上記各実施形態と同様に、内輪２７より軟らかいハウジング２の摩耗を抑制でき、内輪回転阻止機構における耐摩耗性の向上を図ることができる。 According to such a configuration, when the inner ring 27 rotates clockwise (in the direction of the arrow in FIG. 9A) with respect to the housing 2 as the rotating main shaft 5 rotates, the contact surface 27A of the inner ring 27 becomes the housing. 2 is in contact with the second inclined surface 2b in a substantially surface contact state, and the rotation of the inner ring 27 is prevented. In this case, it is desirable to set the rotation angle of the inner ring 27 and the inclination angle of the inclined surface 2b to be substantially the same. Thereby, similarly to each said embodiment, abrasion of the housing 2 softer than the inner ring | wheel 27 can be suppressed, and the abrasion resistance in an inner ring | wheel rotation prevention mechanism can be improved.

　上述した各実施形態では、内輪とハウジングの形状を略三角形とした場合について示したが、他の多角形（例えば四角形等）でもよいことは言うまでもない。
　また、上述した各実施形態のハウジングと内輪により構成される内輪回転阻止機構は、回転主軸の回転方向が一方向のみを想定したものであるが、両回転方向に対応すべく、内輪又はハウジングの各周面の両端縁部領域に、同様な内輪側周面とハウジング周面の当接構造を設けてもよい。 In each of the above-described embodiments, the case where the inner ring and the housing are substantially triangular has been shown, but it is needless to say that other polygons (for example, a quadrangle or the like) may be used.
In the inner ring rotation prevention mechanism constituted by the housing and the inner ring of each embodiment described above, the rotation direction of the rotation main shaft is assumed to be only one direction. A similar contact structure between the inner ring side peripheral surface and the housing peripheral surface may be provided in both end edge regions of each peripheral surface.

１　　揺動板式可変容量圧縮機
２　　ハウジング
２Ａ　　ハウジング周面
２ａ　　傾斜面（ハウジング側）
５　　回転主軸
６　　ロータ
８　　斜板
９　　シリンダボア
１０　　ピストン
１２　　揺動板
２１　　揺動板の回転阻止機構
２４　　スリーブ
２５　　ボール
２６　　内輪のガイド溝
２７　　内輪
２７Ａ　　当接面
２７ａ　　平面部
２７ｂ　　傾斜面（内輪側）
２７ｃ　　端縁部
２８　　外輪のガイド溝
３０　　外輪 1 Oscillating plate type variable capacity compressor 2 Housing 2A Housing peripheral surface 2a Inclined surface (housing side)
5 Rotating main shaft 6 Rotor 8 Swash plate 9 Cylinder bore 10 Piston 12 Oscillating plate 21 Oscillating plate rotation prevention mechanism 24 Sleeve 25 Ball 26 Inner ring guide groove 27 Inner ring 27A Abutting surface 27a Flat portion 27b Inclined surface (inner ring side)
27c End edge portion 28 Outer ring guide groove 30 Outer ring

Claims

　回転主軸と共に回転する斜板と、シリンダボア内のピストンに連結され前記斜板の回転に伴って前記回転主軸に対して揺動してピストンを往復動させる揺動板と、前記回転主軸の回転時に前記揺動板の回転を阻止する揺動板回転阻止機構とを備え、前記回転主軸に対する斜板の傾斜角を可変して前記揺動板の揺動幅を変更し前記シリンダボアからの冷媒吐出容量を可変する揺動板式可変容量圧縮機であって、
　前記揺動板回転阻止機構を、前記回転主軸の軸方向に移動可能で内輪回転阻止機構によって前記回転主軸回りの回転が阻止される内輪と、前記斜板の回転により前記揺動板を揺動させる外輪と、前記内輪に対して前記外輪が揺動可能に且つ内輪の回転阻止力を外輪に伝達するように前記内輪と前記外輪とを連結する連結機構と、を備えて構成し、
　前記内輪回転阻止機構を、前記回転主軸の回転時に、ハウジングの内周面と当該内周面に対面させた前記内輪の外周面とを当接させる当接構造によるものにおいて、
　前記ハウジングの内周面と前記内輪の外周面とを互いに対応する多角形状に形成し、ハウジング側の各周面と内輪側の各周面とを、互いに正対したときに互いの面間の隙間が周方向の端縁部に向かうにつれて増大するよう形成したことを特徴とする揺動板式可変容量圧縮機。 A swash plate that rotates together with the rotation main shaft, a swing plate that is connected to a piston in a cylinder bore and swings with respect to the rotation main shaft as the swash plate rotates, and causes the piston to reciprocate; A rocking plate rotation blocking mechanism for blocking rotation of the rocking plate, and changing a rocking width of the rocking plate by changing an inclination angle of the swash plate with respect to the rotation main shaft, thereby discharging refrigerant from the cylinder bore Oscillating plate type variable capacity compressor,
The rocking plate rotation blocking mechanism is movable in the axial direction of the rotation main shaft, and an inner ring whose rotation around the rotation main shaft is blocked by the inner ring rotation blocking mechanism, and the rocking plate is rocked by the rotation of the swash plate. An outer ring to be configured, and a coupling mechanism that couples the inner ring and the outer ring so that the outer ring can swing relative to the inner ring and transmits the rotation preventing force of the inner ring to the outer ring,
The inner ring rotation prevention mechanism has a contact structure that abuts the inner peripheral surface of the housing and the outer peripheral surface of the inner ring facing the inner peripheral surface when the rotation main shaft rotates.
The inner peripheral surface of the housing and the outer peripheral surface of the inner ring are formed in a polygonal shape corresponding to each other, and each peripheral surface on the housing side and each peripheral surface on the inner ring side are opposed to each other when facing each other. An oscillating plate variable displacement compressor characterized in that the gap is formed so as to increase toward the end edge in the circumferential direction.
　ハウジング側の各周面と内輪側の各周面のどちらか一方に、正対する他方の面に対して端縁部に向かうにつれて遠ざかるように傾斜させた傾斜面を形成した請求項１に記載の揺動板式可変容量圧縮機。 2. The inclined surface according to claim 1, wherein an inclined surface is formed on one of each peripheral surface on the housing side and each peripheral surface on the inner ring side so as to move away from the other facing surface toward the end edge portion. Swing plate type variable capacity compressor.
　前記ハウジング側の各周面を平面部とし、前記内輪側の各周面に前記傾斜面を形成した請求項２に記載の揺動板式可変容量圧縮機。 3. The oscillating plate variable displacement compressor according to claim 2, wherein each peripheral surface on the housing side is a flat portion, and the inclined surface is formed on each peripheral surface on the inner ring side.
　前記傾斜面が、曲面である請求項２又は３に記載の揺動板式可変容量圧縮機。 The rocking plate type variable capacity compressor according to claim 2 or 3, wherein the inclined surface is a curved surface.
　前記傾斜面が、平面であって、前記端縁部に向かって１°以上５°未満の角度範囲で傾斜する請求項２又は３に記載の揺動板式可変容量圧縮機。 The oscillating plate variable displacement compressor according to claim 2 or 3, wherein the inclined surface is a flat surface and is inclined in an angle range of 1 ° or more and less than 5 ° toward the edge portion.
　前記傾斜面を形成した各周面の前記端縁部は、前記傾斜面に接続する曲面である請求項２～５のいずれか１つに記載の揺動板式可変容量圧縮機。 6. The oscillating plate variable displacement compressor according to claim 2, wherein the end edge portion of each peripheral surface forming the inclined surface is a curved surface connected to the inclined surface.
　前記ハウジングの内周面及び前記内輪の外周面を三角形状とした請求項１～６のいずれか１つに記載の揺動板式可変容量圧縮機。 The oscillating plate variable displacement compressor according to any one of claims 1 to 6, wherein an inner peripheral surface of the housing and an outer peripheral surface of the inner ring are triangular.
　前記連結機構は、前記内輪に形成された複数のガイド溝と当該内輪のガイド溝と対向する位置に形成された前記外輪の複数のガイド溝とにより保持され、対向する両ガイド溝間で圧縮されることにより動力伝達を行う複数のボールと、前記外輪を揺動可能に支持すると共に、前記回転主軸上に軸方向に移動可能に設けられ、前記内輪と共に軸方向に移動可能に当該内輪と係合したスリーブと、を備えて構成した請求項１～７のいずれか１つに記載の揺動板式可変容量圧縮機。 The coupling mechanism is held by a plurality of guide grooves formed in the inner ring and a plurality of guide grooves of the outer ring formed at positions facing the guide grooves of the inner ring, and is compressed between the opposed guide grooves. A plurality of balls that transmit power by supporting the outer ring so as to be swingable, and are provided so as to be movable in the axial direction on the rotating main shaft, and are associated with the inner ring so as to be movable in the axial direction together with the inner ring. The oscillating plate type variable displacement compressor according to any one of claims 1 to 7, comprising a combined sleeve.