JP5901446B2 - Rotary compressor - Google Patents

Rotary compressor Download PDF

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Publication number
JP5901446B2
JP5901446B2 JP2012142867A JP2012142867A JP5901446B2 JP 5901446 B2 JP5901446 B2 JP 5901446B2 JP 2012142867 A JP2012142867 A JP 2012142867A JP 2012142867 A JP2012142867 A JP 2012142867A JP 5901446 B2 JP5901446 B2 JP 5901446B2
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Japan
Prior art keywords
rotor
drive cylinder
drive
shaft
plate
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Expired - Fee Related
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JP2012142867A
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Japanese (ja)
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JP2014005795A (en
JP2014005795A5 (en
Inventor
善則 村瀬
善則 村瀬
章 稲垣
章 稲垣
石井　弘樹
弘樹 石井
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Denso Corp
Soken Inc
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Denso Corp
Nippon Soken Inc
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Application filed by Denso Corp, Nippon Soken Inc filed Critical Denso Corp
Priority to JP2012142867A priority Critical patent/JP5901446B2/en
Priority to CN201380033782.2A priority patent/CN104471250A/en
Priority to PCT/JP2013/067528 priority patent/WO2014003060A1/en
Priority to DE112013003254.6T priority patent/DE112013003254T5/en
Priority to US14/409,289 priority patent/US20150176583A1/en
Publication of JP2014005795A publication Critical patent/JP2014005795A/en
Publication of JP2014005795A5 publication Critical patent/JP2014005795A5/ja
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Publication of JP5901446B2 publication Critical patent/JP5901446B2/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/22—Rotary-piston pumps specially adapted for elastic fluids of internal-axis type with equidirectional movement of co-operating members at the points of engagement, or with one of the co-operating members being stationary, the inner member having more teeth or tooth equivalents than the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/02—Pumps characterised by combination with or adaptation to specific driving engines or motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/332—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps

Description

本発明は、回転型圧縮機に関するもので、特にエアコンなどの冷媒圧縮において、効率及び信頼性が高く、これらを両立させて小型化を図ることができるものである。   The present invention relates to a rotary compressor, and in particular, in compression of refrigerant such as an air conditioner, the efficiency and reliability are high.

低コスト、車両などへの搭載性の面から、圧縮機の小型化が必要となっている。小型化の手段として駆動用のモータ内部に圧縮部を配置することは、小型化の有用な手段である。このようなモータ内部に圧縮部を配置したものが、特許文献１に開示されている。この従来技術では、モータの回転子と一体の楕円形シリンダ８の方を、静止状態にあるピストン１７に対して、通常のローリングピストンとは逆に、回転するように構成している。これは、基本的には通常のローリングピストンといえるものなので、ベーンノーズがある。そして、バネとベーンが、回転するシリンダ部に配置されているため、高回転時に遠心力が作用し、バネ力に打ち勝つとベーンノーズとロータとの間に、隙間（ベーンの離脱）が発生して圧縮作動をしないため、性能低下が問題となり、高回転に不向きなものであった。また、遠心力に打ち勝つようバネ力を増加させると、ベーンノーズとロータ間の押し付け力が過大な状態で摺動することになり、ベーンノーズ部が焼き付くなど信頼性に問題があった。   From the viewpoint of low cost and mountability to vehicles, it is necessary to reduce the size of the compressor. Arranging the compression section inside the driving motor as a means for miniaturization is a useful means for miniaturization. Patent Document 1 discloses a configuration in which a compression unit is arranged inside such a motor. In this prior art, the elliptic cylinder 8 integral with the rotor of the motor is configured to rotate with respect to the piston 17 in a stationary state, as opposed to a normal rolling piston. This is basically a normal rolling piston, so there is a vane nose. And since the spring and vane are arranged in the rotating cylinder part, centrifugal force acts at the time of high rotation, and when the spring force is overcome, a gap (detachment of the vane) occurs between the vane nose and the rotor. Since the compression operation is not performed, the performance degradation becomes a problem and it is not suitable for high rotation. Further, when the spring force is increased so as to overcome the centrifugal force, the pressing force between the vane nose and the rotor slides in an excessively large state, and there is a problem in reliability such that the vane nose portion is seized.

一方、特許文献２においては、電動モータの回転子に一体化したシリンダ８に対して、偏心位置に設置した静止形ピストン１１との間を、ベーン部１３（仕切板）で圧縮室を形成したものが、開示されている。この従来技術も、基本的には通常のローリングピストンといえるものなので、上述の問題が生じていた。   On the other hand, in Patent Document 2, a compression chamber is formed by a vane portion 13 (partition plate) between a cylinder 8 integrated with a rotor of an electric motor and a stationary piston 11 installed at an eccentric position. Have been disclosed. Since this prior art is basically a normal rolling piston, the above-mentioned problem has occurred.

特公昭５３−４３６８２号公報Japanese Patent Publication No.53-43682 特公平０１−５４５６０号公報Japanese Patent Publication No. 01-54560

本発明は、上記問題に鑑み、効率及び信頼性が高く、両者が両立して小型化を図ることができる回転型圧縮機を提供するものである。   In view of the above problems, the present invention provides a rotary compressor that is highly efficient and reliable, and that can achieve both reductions in size.

上記課題を解決するために、請求項１の発明は、ケーシング（１）に固定されたシャフト（１２）の軸心（Ｏ１）周りに、回転自在なロータ（１１）と、前記シャフト（１２）とは偏心した回転中心（Ｏ２）で回転自在な駆動シリンダ（８）と、前記駆動シリンダ（８）又は前記ロータ（１１）のいずれか一方に対して揺動可能であって、他方に対しては摺動可能に設置され、前記駆動シリンダ（８）と前記ロータ（１１）とを回転連結する駆動プレート（１３）と、前記駆動シリンダ（８）の側面部を構成するサイドプレート（２７）と、を具備する回転型圧縮機構であって、前記駆動シリンダ（８）内面と前記ロータ（１１）外周が仕切り点（Ｃ）で接するように、前記シャフト（１２）の軸心（Ｏ１）に対して前記駆動シリンダ（８）の回転中心（Ｏ２）を偏心させ、前記仕切り点（Ｃ）と前記駆動プレート（１３）で仕切られた、前記駆動シリンダ（８）内面と前記ロータ（１１）外周との間の空間が、圧縮又は吸入を行う作動室（９、１０）であり、前記シャフト（１２）と前記ロータ（１１）に吸入通路（１７、２０）を設け吸入を行う作動室（１０）内に吸入を行い、作動室（１０）で圧縮した後前記サイドプレート（２７）に吐出弁部を設けて吐出を行うようにした回転型圧縮機構である。
冷媒を外径方向から吸入し、シャフト内から吐出させる構成にすると、高圧と低圧との間をチップシール等でシールする必要があるが、本発明の冷媒の流れによれば、シャフトが固定されて、シャフト内に冷媒が吸入される構成のため、シール等が必要なく、シールによる機械損失が低減される。 In order to solve the above problems, the invention of claim 1 is directed to a rotor (11) rotatable around an axis (O1) of a shaft (12) fixed to a casing (1), and the shaft (12). Is swingable with respect to either the drive cylinder (8) and the drive cylinder (8) or the rotor (11), which are rotatable at an eccentric rotation center (O2), and with respect to the other Is slidably installed, a drive plate (13) that rotationally connects the drive cylinder (8) and the rotor (11), and a side plate (27) that constitutes a side surface of the drive cylinder (8). , Wherein the inner surface of the drive cylinder (8) and the outer periphery of the rotor (11) are in contact with each other at a partition point (C) with respect to the axis (O1) of the shaft (12). The drive cylinder (8) The space between the inner surface of the drive cylinder (8) and the outer periphery of the rotor (11), which is decentered from the rotation center (O2) and partitioned by the partition point (C) and the drive plate (13), is compressed or a working chamber for suction (9, 10), the suction on the shaft (12) and said rotor (11) to the suction passage (17,20) is provided working chamber for suction (10) within working chamber It is a rotary compression mechanism in which the side plate (27) is provided with a discharge valve portion to perform discharge after being compressed in (10) .
When the refrigerant is sucked from the outer diameter direction and discharged from the shaft, it is necessary to seal between the high pressure and the low pressure with a chip seal or the like. However, according to the flow of the refrigerant of the present invention, the shaft is fixed. Thus, since the refrigerant is sucked into the shaft, a seal or the like is not necessary, and mechanical loss due to the seal is reduced.

なお、上記に付した符号は、後述する実施形態に記載の具体的実施態様との対応関係を示す一例である。   In addition, the code | symbol attached | subjected above is an example which shows a corresponding relationship with the specific embodiment as described in embodiment mentioned later.

本発明の第１実施形態を示す断面図である。It is sectional drawing which shows 1st Embodiment of this invention. 本発明の第１実施形態を示す詳細部分断面図である。It is a detailed fragmentary sectional view which shows 1st Embodiment of this invention. 本発明の第１実施形態の作動を示す説明図である。It is explanatory drawing which shows the action | operation of 1st Embodiment of this invention. 本発明の第１実施形態を示す断面図である。It is sectional drawing which shows 1st Embodiment of this invention.

以下、図面を参照して、本発明の一実施形態を説明する。各実施態様について、同一構成の部分には、同一の符号を付してその説明を省略する。以下の実施形態の説明においては、車両用エアコンの冷媒圧縮を例示として説明するが、必ずしもこれに限定されるものではなく、本発明は、広く家庭用や産業用の圧縮機に適用可能なものである。   Hereinafter, an embodiment of the present invention will be described with reference to the drawings. About each embodiment, the same code | symbol is attached | subjected to the part of the same structure, and the description is abbreviate | omitted. In the following description of the embodiment, refrigerant compression of a vehicle air conditioner will be described as an example. However, the present invention is not necessarily limited to this, and the present invention is widely applicable to household and industrial compressors. It is.

（第１実施形態）
図１、２に示すように、ケーシング１の内面には、電動モータの固定子２がはめ込まれて固定されている。ケーシング１は、締結ボルトなどで蓋４が取り付けられている。電動モータの回転子３は、駆動シリンダ８の外周に固定されているので、駆動シリンダ８は、シャフト１２回りに、電動モータの回転子３によって回転させられるようになっている。駆動シリンダ８は、円筒状のシリンダの両側に、サイドプレート２７、２７が、締結ボルト４１などで取り付けられていて、円筒状のシリンダとサイドプレートとをあわせて駆動シリンダ８を構成する。シャフト１２は、図１の右端でケーシング１に圧入されている。シャフト１２の左端部は蓋４に挿入や圧入されており、シャフト１２は回転しないようになっている。 (First embodiment)
As shown in FIGS. 1 and 2, the stator 2 of the electric motor is fitted and fixed to the inner surface of the casing 1. The lid 1 is attached to the casing 1 with fastening bolts or the like. Since the rotor 3 of the electric motor is fixed to the outer periphery of the drive cylinder 8, the drive cylinder 8 is rotated around the shaft 12 by the rotor 3 of the electric motor. The drive cylinder 8 has side plates 27 and 27 attached to both sides of the cylindrical cylinder with fastening bolts 41 and the like, and the cylindrical cylinder and the side plate constitute the drive cylinder 8. The shaft 12 is press-fitted into the casing 1 at the right end of FIG. The left end portion of the shaft 12 is inserted or press-fitted into the lid 4 so that the shaft 12 does not rotate.

この静止したシャフト１２に対して、モータの回転子３と駆動シリンダ８は一体化されて、ベアリング４２を介して、回転可能になっている。図２に示すように、圧縮機としてのロータ１１は、駆動プレート１３によって、駆動シリンダ８に連れ回りするようになっている。ここで、電動モータの回転子３の回転中心Ｏ２に対して、シャフト１２の軸心Ｏ１は偏心している。これら回転中心Ｏ２と軸心Ｏ１は、不動点である。ロータ１１は、シャフト１２に回転可能に嵌装されている。ロータ１１は、不動の軸心Ｏ１回りに、回転可能で、駆動プレート１３によって、駆動シリンダ８に連れ回りする。なお、本実施形態の駆動モータとしては、電動モータを使用しているが、ベルト伝動の場合に適用することも可能である。   The motor rotor 3 and the drive cylinder 8 are integrated with the stationary shaft 12 and can be rotated via a bearing 42. As shown in FIG. 2, the rotor 11 as a compressor is rotated around the drive cylinder 8 by a drive plate 13. Here, the axis O1 of the shaft 12 is eccentric with respect to the rotation center O2 of the rotor 3 of the electric motor. The rotation center O2 and the axis O1 are fixed points. The rotor 11 is rotatably fitted to the shaft 12. The rotor 11 is rotatable around a stationary axis O <b> 1 and is rotated around the drive cylinder 8 by the drive plate 13. In addition, although the electric motor is used as a drive motor of this embodiment, it is also possible to apply in the case of belt transmission.

駆動プレート１３の一端は、駆動シリンダ８に揺動自在となるように設置され、駆動プレート１３の他端は、ロータ１１の摺動溝２４に挿入されており、駆動シリンダ８の回転を駆動プレート１３によりロータ１１に伝達し、ロータ１１が回転を行う。駆動シリンダ８とロータ１１は、回転中常に仕切り点（接点）Ｃで接している。なお、駆動プレート１３の一端は、ロータ１１に揺動自在となるように設置され、駆動プレート１３の他端は、駆動シリンダ８の摺動溝２４に挿入されていても良い。   One end of the drive plate 13 is installed so as to be swingable with respect to the drive cylinder 8, and the other end of the drive plate 13 is inserted into the sliding groove 24 of the rotor 11. 13 is transmitted to the rotor 11, and the rotor 11 rotates. The drive cylinder 8 and the rotor 11 are always in contact at a partition point (contact point) C during rotation. One end of the drive plate 13 may be installed so as to be swingable with respect to the rotor 11, and the other end of the drive plate 13 may be inserted into the sliding groove 24 of the drive cylinder 8.

圧縮すべき冷媒ガスなどの圧縮媒体は、図１、２に示すように、吸入口１６から導入され、吸入通路１７を経て、シャフト開口１８、ロータ通路２０から、吸入側の作動室（吸入室）１０に導入される。シャフト開口１８とロータ通路２０は、常に全角度で連通している。シャフト開口１８の出口には、シャフト１２の一部の円周方向に、全周に亘って溝１９が形成されている。   As shown in FIGS. 1 and 2, a compression medium such as a refrigerant gas to be compressed is introduced from the suction port 16, passed through the suction passage 17, and from the shaft opening 18 and the rotor passage 20 to the suction side working chamber (suction chamber). ) 10. The shaft opening 18 and the rotor passage 20 always communicate with each other at all angles. A groove 19 is formed at the outlet of the shaft opening 18 over the entire circumference in the circumferential direction of a part of the shaft 12.

駆動シリンダ８の一方側に固着されたサイドプレート２７には、圧縮室吐出口２１が設けられており、外側にはリードバルブ２２（吐出弁部）が設置されている。リードバルブの代わりにその他のバルブ（ポペットバルブなど）であっても良い。もちろん、駆動シリンダ８の円筒状シリンダ外周に設けても良いが、遠心力の影響について配慮する必要がある。圧縮室吐出口２７とリードバルブ２２は、駆動シリンダ８の回転とともに、回転しながら圧縮ガスをケーシング内部の空間に吐出する。その後、ケーシング吐出口２３から外部に吐出する。   The side plate 27 fixed to one side of the drive cylinder 8 is provided with a compression chamber discharge port 21, and a reed valve 22 (discharge valve portion) is provided outside. Other valves (such as a poppet valve) may be used instead of the reed valve. Of course, it may be provided on the outer periphery of the cylindrical cylinder of the drive cylinder 8, but it is necessary to consider the influence of centrifugal force. The compression chamber discharge port 27 and the reed valve 22 discharge the compressed gas to the space inside the casing while rotating as the drive cylinder 8 rotates. Then, it discharges outside from the casing discharge port 23.

次に、駆動プレート１３について説明する。駆動プレート１３は、従来技術のローリングピストンにおける、ベーンに相当する部材である。すなわち、本実施形態では、駆動プレート１３は、圧縮室（圧縮側の作動室）９と吸入室１０とを仕切る部材であり、かつ、ロータ１１を駆動シリンダ８に連れ回りさせるための連結部材としての機能を有している。連結部材としての機能を果たすために、駆動プレート１３の頭部１３−１は、円筒面になっており、頭部１３−１の中心軸に対して、駆動プレート１３は、駆動シリンダ８に隙間１３−２が設けられて、揺動することができるようになっている。ロータ１１には、駆動シリンダ８の回転につれ、駆動プレート１３が摺動溝２４内を摺動する。これにより、連れまわり時に、駆動シリンダ８の回転中心Ｏ２と、ロータ１１の軸心Ｏ１との偏心を吸収することができる。   Next, the drive plate 13 will be described. The drive plate 13 is a member corresponding to a vane in a conventional rolling piston. That is, in the present embodiment, the drive plate 13 is a member that partitions the compression chamber (compression side working chamber) 9 and the suction chamber 10, and as a connecting member that rotates the rotor 11 with the drive cylinder 8. It has the function of In order to fulfill the function as a connecting member, the head 13-1 of the drive plate 13 has a cylindrical surface, and the drive plate 13 is spaced from the drive cylinder 8 with respect to the central axis of the head 13-1. 13-2 is provided so that it can swing. As the driving cylinder 8 rotates, the driving plate 13 slides in the sliding groove 24 on the rotor 11. Thereby, the eccentricity between the rotation center O2 of the drive cylinder 8 and the axis O1 of the rotor 11 can be absorbed during the rotation.

圧縮機構部は、ケーシング１に固定されたシャフト１２の軸心Ｏ１周りに、回転自在なロータ１１と、シャフト１２とは偏心した回転中心Ｏ２で回転自在な駆動シリンダ８と、駆動シリンダ８とロータ１１との間を連結する駆動プレート１３とから構成される。ロータ１１と駆動シリンダ８間の空間が、作動室となっている。この作動室は、駆動プレート１３により２分され、圧縮室９と吸入室１０とを形成する。駆動シリンダ８を回転駆動する電動モータ２、３により、駆動シリンダ８を回転させて、駆動シリンダ８とロータ１１間に形成された作動室のうち、駆動プレート１３の回転方向前方の圧縮室９で、吸入ガスを圧縮する。駆動シリンダ８とロータ１１間に形成された作動室は、駆動プレート１３と、駆動シリンダ８とロータ１１の接点である仕切り点Ｃで、仕切られている。駆動プレート１３の回転方向前方には、圧縮室９が形成され、後方には吸入室１０が形成される。   The compression mechanism includes a rotor 11 that is rotatable around an axis O1 of a shaft 12 fixed to the casing 1, a drive cylinder 8 that is rotatable at a rotation center O2 that is eccentric from the shaft 12, and a drive cylinder 8 and a rotor. 11 and a drive plate 13 that connects the two. A space between the rotor 11 and the drive cylinder 8 is a working chamber. This working chamber is divided into two by the drive plate 13 to form a compression chamber 9 and a suction chamber 10. The drive cylinder 8 is rotated by the electric motors 2 and 3 that rotationally drive the drive cylinder 8, and among the working chambers formed between the drive cylinder 8 and the rotor 11, in the compression chamber 9 in the forward direction of the drive plate 13 in the rotation direction. Compress the intake gas. The working chamber formed between the drive cylinder 8 and the rotor 11 is partitioned by a drive plate 13 and a partition point C that is a contact point between the drive cylinder 8 and the rotor 11. A compression chamber 9 is formed in front of the drive plate 13 in the rotational direction, and a suction chamber 10 is formed in the rear.

次に、上述の圧縮工程と吸引工程について、駆動シリンダの回転角θ（駆動プレート１３の位置）が９０°毎に、図３を参照して説明する。ここでは、分かりやすくするために、７２０°にして説明する。図３の（１）θ＝０°から再度（１）θ＝７２０°に至る順に説明する。（１）θ＝０°では、吸入が完了した状態である。駆動プレート１３と仕切り点Ｃとが一致するので、吸入室１０と圧縮室９が合体する。θ＝０°から駆動シリンダ８の回転角θが増大するにつれ、（２）〜（４）に見られるように、駆動プレート１３の回転方向前方側と仕切り点Ｃとの間が閉鎖されて、圧縮室９での圧縮が進行する。   Next, the above-described compression process and suction process will be described with reference to FIG. 3 for each rotation angle θ of the drive cylinder (position of the drive plate 13) of 90 °. Here, in order to make it easy to understand, 720 ° will be described. Description will be made in the order from (1) θ = 0 ° to (1) θ = 720 ° in FIG. (1) At θ = 0 °, the inhalation is completed. Since the drive plate 13 and the partition point C coincide with each other, the suction chamber 10 and the compression chamber 9 are combined. As the rotation angle θ of the drive cylinder 8 increases from θ = 0 °, as seen in (2) to (4), the front side in the rotation direction of the drive plate 13 and the partition point C are closed, Compression in the compression chamber 9 proceeds.

（５）θ＝３６０°で圧縮室９は消滅して、今度は、吸入室１０が、駆動プレート１３の回転方向後方と、仕切り点Ｃとの間に形成されて、（５）→（１）に至るまで吸入が進行して、圧縮工程と吸引工程が繰り返されて行く。以上７２０°にして説明したが、実際の圧縮工程と吸引工程は３６０°の１回転で同時に行われる。図３の（１）〜（５）において、駆動プレート１３の回転方向前方側と、仕切り点Ｃとの間の圧縮室９で、圧縮が進行すると同時に、駆動プレート１３の回転方向後方と、仕切り点Ｃとの間の吸入室１０で、吸入が進行していることが分かる。（１）や（５）では、駆動プレート１３と仕切り点Ｃとが一致するので、吸入室１０と圧縮室９が合体する。   (5) When θ = 360 °, the compression chamber 9 disappears, and this time, the suction chamber 10 is formed between the rear side in the rotational direction of the drive plate 13 and the partition point C, and (5) → (1 ), And the compression process and the suction process are repeated. Although the above description has been made at 720 °, the actual compression step and suction step are simultaneously performed in one rotation of 360 °. In (1) to (5) of FIG. 3, in the compression chamber 9 between the rotation direction front side of the drive plate 13 and the partition point C, at the same time as the compression progresses, the rotation direction rear of the drive plate 13 and the partition It can be seen that inhalation proceeds in the suction chamber 10 between the point C and the point C. In (1) and (5), since the drive plate 13 and the partition point C coincide with each other, the suction chamber 10 and the compression chamber 9 are combined.

以上説明したように、駆動シリンダ８の回転により圧縮作動を行うため、駆動シリンダ８を、電動モータの回転子３内に配置しているので、圧縮機として小型にすることができる。シャフト１２は回転しないので、シャフト１２に吸入口１６を設置して、ガスを吸入することができる。また、回転時に遠心力の影響を受けにくいサイドプレート２７に、圧縮室吐出口２７とリードバルブ２２が設けられている。本実施形態では、ベーンノーズ摺動部を持たないため、従来技術のようなベーンノーズ摺動部の離脱や焼き付きがなく、低回転から高回転まで、性能と信頼性を両立確保することができ、電動モータ回転子に内蔵した、小型な圧縮機を提供することができるものである。さらに、従来技術では圧縮室を形成するためにロータを偏心運動させる必要があって、高速回転時は圧縮機の振動悪化を招いていたが、本実施形態ではロータ１１は、不動の軸心Ｏ１において自転運動をするだけなので、圧縮機の振動悪化を防止できる。   As described above, since the compression operation is performed by the rotation of the drive cylinder 8, the drive cylinder 8 is disposed in the rotor 3 of the electric motor, so that the compressor can be downsized. Since the shaft 12 does not rotate, a suction port 16 can be installed in the shaft 12 to suck gas. Further, a compression chamber discharge port 27 and a reed valve 22 are provided on a side plate 27 that is not easily affected by centrifugal force during rotation. In this embodiment, since there is no vane nose sliding portion, there is no separation or seizure of the vane nose sliding portion as in the prior art, and both performance and reliability can be ensured from low rotation to high rotation. It is possible to provide a small compressor built in the motor rotor. Further, in the prior art, it is necessary to eccentrically move the rotor in order to form the compression chamber, and the vibration of the compressor is deteriorated during high-speed rotation. However, in this embodiment, the rotor 11 has a fixed axis O1. Since only the self-rotating motion in the compressor, the deterioration of the compressor vibration can be prevented.

本実施形態では、駆動プレート１３の頭部１３−１は、円筒面になっており、頭部１３−１の中心軸に対して、駆動プレート１３は、揺動することができるようになっている。これに対して、図４に示すように、頭部のない平板の駆動プレート１３にしても良い。この場合は、片側に円筒面を持つ２枚のシュー１３−３が、駆動プレート１３の端部を挟むように設置されている。その他は、図１、２と同じ構成となっている。ロータ１１に形成された摺動溝２４と駆動プレート１３の先端が接する点においては、駆動プレート側の先端がＲ形状を有している。また、ロータ１１に形成された摺動溝２４の先端と駆動プレート１３が接する点において、ロータ１１側の先端がＲ形状を有している。
駆動プレート１３の頭部１３−１は、図１、２のように駆動シリンダ８に設けても、ロータ１１に設置しても実施可能である。 In the present embodiment, the head 13-1 of the drive plate 13 has a cylindrical surface, and the drive plate 13 can swing with respect to the central axis of the head 13-1. Yes. On the other hand, as shown in FIG. 4, a flat drive plate 13 without a head may be used. In this case, two shoes 13-3 having a cylindrical surface on one side are installed so as to sandwich the end portion of the drive plate 13. The rest of the configuration is the same as in FIGS. At the point where the sliding groove 24 formed in the rotor 11 and the tip of the drive plate 13 contact each other, the tip on the drive plate side has an R shape. In addition, the tip on the rotor 11 side has an R shape in that the tip of the sliding groove 24 formed in the rotor 11 and the drive plate 13 are in contact with each other.
The head 13-1 of the drive plate 13 can be implemented by being provided on the drive cylinder 8 as shown in FIGS.

１ ケーシング
８ 駆動シリンダ
１１ ロータ
１２ シャフト
１３ 駆動プレート 1 Casing 8 Drive Cylinder 11 Rotor 12 Shaft 13 Drive Plate

Claims (5)

ケーシング（１）に固定されたシャフト（１２）の軸心（Ｏ１）周りに、回転自在なロータ（１１）と、前記シャフト（１２）とは偏心した回転中心（Ｏ２）で回転自在な駆動シリンダ（８）と、前記駆動シリンダ（８）又は前記ロータ（１１）のいずれか一方に対して揺動可能であって、他方に対しては摺動可能に設置され、前記駆動シリンダ（８）と前記ロータ（１１）とを回転連結する駆動プレート（１３）と、前記駆動シリンダ（８）の側面部を構成するサイドプレート（２７）と、を具備する回転型圧縮機構であって、
前記駆動シリンダ（８）内面と前記ロータ（１１）外周が仕切り点（Ｃ）で接するように、前記シャフト（１２）の軸心（Ｏ１）に対して前記駆動シリンダ（８）の回転中心（Ｏ２）を偏心させ、
前記仕切り点（Ｃ）と前記駆動プレート（１３）で仕切られた、前記駆動シリンダ（８）内面と前記ロータ（１１）外周との間の空間が、圧縮又は吸入を行う作動室（９、１０）であり、
前記シャフト（１２）と前記ロータ（１１）に吸入通路（１７、２０）を設け吸入を行う作動室（１０）内に吸入を行い、作動室（１０）で圧縮した後前記サイドプレート（２７）に吐出弁部を設けて吐出を行うようにした回転型圧縮機構。 Around the axis (O1) of the shaft (12) fixed to the casing (1), the rotor (11) is rotatable, and the drive cylinder is rotatable at the center of rotation (O2) where the shaft (12) is eccentric. (8) and the drive cylinder (8) or the rotor (11) is swingable with respect to the other, and is slidable with respect to the other. The drive cylinder (8) A rotary compression mechanism comprising: a drive plate (13) that rotationally connects the rotor (11); and a side plate (27) that constitutes a side surface of the drive cylinder (8),
The rotation center (O2) of the drive cylinder (8) with respect to the axis (O1) of the shaft (12) so that the inner surface of the drive cylinder (8) and the outer periphery of the rotor (11) are in contact with each other at a partition point (C). )
The space between the inner surface of the drive cylinder (8) and the outer periphery of the rotor (11), which is partitioned by the partition point (C) and the drive plate (13), compresses or sucks the working chamber (9, 10). ) And
A suction passage (17, 20) is provided in the shaft (12) and the rotor (11), the suction is performed in the working chamber (10) where the suction is performed, and the side plate (27) is compressed in the working chamber (10 ). A rotary compression mechanism in which a discharge valve portion is provided to perform discharge. 前記駆動シリンダ（８）を回転駆動したことを特徴とする請求項１に記載の回転型圧縮機構。   The rotary compression mechanism according to claim 1, wherein the drive cylinder (8) is rotationally driven. 前記駆動シリンダ（８）の外周に電動モータの回転子（３）を連結したことを特徴とする請求項２に記載の回転型圧縮機構。   The rotary compression mechanism according to claim 2, wherein a rotor (3) of an electric motor is connected to an outer periphery of the drive cylinder (8). 前記駆動プレート（１３）の揺動側が円筒面で構成されていることを特徴とする請求項１から３のいずれか１項に記載の圧縮機。 The compressor according to any one of claims 1 to 3 , wherein a rocking side of the drive plate (13) is formed of a cylindrical surface. 前記駆動プレート（１３）が平板で構成され、前記駆動プレート（１３）の揺動側を、片側が円筒面で構成された２つのシュー（１３−３）で挟み込んでいることを特徴とする請求項１から３のいずれか１項に記載の圧縮機。 The drive plate (13) is formed of a flat plate, and the swinging side of the drive plate (13) is sandwiched between two shoes (13-3) each having a cylindrical surface. Item 4. The compressor according to any one of Items 1 to 3 .
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