JP6289646B2 - Rotary compressor and heat pump apparatus equipped with the same - Google Patents

Rotary compressor and heat pump apparatus equipped with the same Download PDF

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JP6289646B2
JP6289646B2 JP2016544890A JP2016544890A JP6289646B2 JP 6289646 B2 JP6289646 B2 JP 6289646B2 JP 2016544890 A JP2016544890 A JP 2016544890A JP 2016544890 A JP2016544890 A JP 2016544890A JP 6289646 B2 JP6289646 B2 JP 6289646B2
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vane
compression
rotary compressor
force
permanent magnet
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JPWO2017090089A1 (en
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哲英 横山
哲英 横山
将吾 諸江
将吾 諸江
久範 鳥居
久範 鳥居
高橋　真一
真一 高橋
幹一朗 杉浦
幹一朗 杉浦
聡経 新井
聡経 新井
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Mitsubishi Electric Corp
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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
    • F04C18/30—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
    • F04C18/34—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—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 the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Description

本発明は、複数気筒の運転モードの切り替えにより能力変更が可能なロータリ式圧縮機と、このロータリ式圧縮機を搭載したヒートポンプ装置に関するものである。  The present invention relates to a rotary compressor whose capacity can be changed by switching operation modes of a plurality of cylinders, and a heat pump device equipped with the rotary compressor.

地球温暖化防止の観点から、１９９７年京都議定書に温室効果ガスの排出規制が盛り込まれ、２００５年国際法として発効された。二酸化炭素排出量の削減と省エネルギー化を図るため、空調冷熱分野では、従来の給湯暖房器に代わってヒートポンプ機器の普及促進と、ヒートポンプ機器の一層の高効率化が進められている。このような中で、従来から空調機や給湯機等のヒートポンプ機器では、冷媒圧縮機を用いた蒸気圧縮式冷凍サイクルが一般的である。  From the viewpoint of global warming prevention, greenhouse gas emission regulations were included in the 1997 Kyoto Protocol and came into effect as an international law in 2005. In order to reduce carbon dioxide emissions and save energy, in the air-conditioning / cooling field, in place of conventional hot water heaters, heat pump equipment is being promoted and heat pump equipment is being made more efficient. Under such circumstances, a vapor compression refrigeration cycle using a refrigerant compressor is generally used in heat pump devices such as an air conditioner and a water heater.

空調機器の省エネ規制強化が促進されているが、特に、最新の新規格では、従来規格より実負荷に近い運転条件で省エネ性能を評価する特徴がある。日本国内の省エネ性能の表示は、従来は、定格条件で冷暖平均ＣＯＰでの効率評価表示であったが、２０１１年より中間条件を加えた冷暖４条件のＣＯＰから算出するＡＰＦ（通年エネルギー消費効率）表示に変更となった。さらに、欧州では２０１２年から、低負荷条件に加えた冷房４条件、暖房４条件より、それぞれ、冷房ＳＥＥＲ、暖房ＳＣＯＰを評価算出する新規格で省エネ性能を表示する方法が採用されている。  Strengthening of energy-saving regulations for air-conditioning equipment is being promoted. In particular, the latest new standard is characterized by evaluating energy-saving performance under operating conditions closer to the actual load than conventional standards. The energy saving performance display in Japan used to be the efficiency evaluation display with the average cooling / heating COP under the rated conditions, but since 2011 the APF (Annual Energy Consumption Efficiency) calculated from the cooling / heating 4 conditions COP with intermediate conditions added since 2011 ) Changed to display. Furthermore, since 2012, a method of displaying energy saving performance with new standards for evaluating and calculating the cooling SEER and the heating SCOP from the cooling 4 condition and the heating 4 condition in addition to the low load condition has been adopted since 2012.

ここで、低負荷条件とは、外気温と室内温度との温度差が小さくて、室内温度一定に保つために必要な熱量が小さい条件である。蒸気圧縮機式冷凍サイクルの高圧（Ｐｄ）と低圧（Ｐｓ）との差異が小さい状態で、かつ、定常状態で必要な熱量も小さい状態（例えば、定格能力の２５％以下）である。運転開始時を除けば、定常運転時に必要な能力は定格条件の１０％から５０％程度であり、定格運転する時間よりも、低負荷条件から中間条件で運転する時間が長い。このため、通年の省エネ性能を実質的に評価するには、従来規格で評価対象外であった低負荷条件について、ＣＯＰを改善することが新たな課題となっている。  Here, the low load condition is a condition in which the temperature difference between the outside air temperature and the room temperature is small, and the amount of heat necessary to keep the room temperature constant is small. The difference between the high pressure (Pd) and the low pressure (Ps) of the vapor compressor refrigeration cycle is small, and the amount of heat required in the steady state is small (for example, 25% or less of the rated capacity). Except at the start of operation, the capacity required for steady operation is about 10% to 50% of the rated condition, and the time for operation from low load conditions to intermediate conditions is longer than the time for rated operation. For this reason, in order to substantially evaluate the energy saving performance throughout the year, it has become a new issue to improve COP for low load conditions that were not subject to evaluation in the conventional standards.

また、近年空調機は、立ち上げ時間の短縮や、低外気温環境での高暖房能力化が要求されるようになってきており、一定以上の定格能力が必要になっている。その一方で、住宅の高気密高断熱化が進んできたことにより定常運転時に必要な能力は小さくなり、必要な運転能力範囲が広がっている。そのため、より広い運転範囲、回転数範囲で高効率を維持することが要求されるようになり、従来のインバータによる回転数制御のみでは、低速の低負荷能力で高効率に維持することは難しくなっている。  In recent years, air conditioners have been required to have shorter rated time and higher heating capacity in a low outside air temperature environment, and a certain level of rated capacity is required. On the other hand, due to the advancement of high airtightness and high thermal insulation of houses, the required capacity during steady operation is reduced, and the required operating capacity range is expanded. For this reason, it is required to maintain high efficiency in a wider operation range and rotation speed range, and it is difficult to maintain high efficiency with low load capacity at low speed only by rotation speed control with a conventional inverter. ing.

そこで、機械的に排除容積を可変する手段（機械式容量制御）を用いた冷媒圧縮機が再び注目されている。
例えば、特許文献１には、二気筒ロータリ式圧縮機において、低負荷時に一方の圧縮部を非圧縮状態として冷媒循環流量を半減する構成が開示されている。この構成では、電動機の回転数を落とさずに運転できるので、圧縮機効率を向上させることができる。
その具体的な手段として、ブレード（ベーンと同義）背室の一方に常時圧縮作用をなすシリンダ室で圧縮された高圧ガスの一部を導入してブレード（ベーンと同義）の後端部（背面部）に高圧を付与し、ベーン先端部を偏心ローラ周壁に当接させる圧縮運転と、ブレード背室に低圧ガスを導いてブレード先端部を偏心ローラ周壁から離間させ永久磁石に保持させる非圧縮運転とに切り替える、圧力切換え手段を備えた二気筒ロータリ式圧縮機（休筒切替式圧縮機）が開示されている。ここで、背面部とは、ベーンの先端側、側面側、上下面側を除く、背面側全体をさす。後端部は、背面部の最も後端の位置をさす。背面部が並行平面であれば後端部と同義であるが凹凸や曲面形状のある場合は異なる位置である。Then, the refrigerant compressor using the means (mechanical capacity control) which mechanically varies the displacement volume has attracted attention again.
For example, Patent Document 1 discloses a configuration in which, in a two-cylinder rotary compressor, one refrigerant compression unit is in an uncompressed state at a low load to reduce the refrigerant circulation flow rate by half. In this configuration, since the operation can be performed without reducing the rotation speed of the electric motor, the compressor efficiency can be improved.
As a specific means, a part of the high-pressure gas compressed in the cylinder chamber that always performs a compression action is introduced into one of the blades (synonymous with vane) and the rear end (rear surface) of the blade (synonymous with vane). Compression operation in which a high pressure is applied to the blade) and the vane tip is brought into contact with the eccentric roller peripheral wall, and non-compression operation in which the low pressure gas is guided to the blade back chamber and the blade tip is separated from the eccentric roller peripheral wall and held by the permanent magnet. A two-cylinder rotary type compressor (cylinder changeover type compressor) provided with pressure switching means is disclosed. Here, the back surface portion means the entire back surface side excluding the tip side, the side surface, and the top and bottom surfaces of the vane. The rear end portion indicates the position of the rearmost end of the back surface portion. If the back part is a parallel plane, it is synonymous with the rear end part, but if it has irregularities or curved shapes, it is a different position.

特許文献２の実施の形態１には、シリンダと、該シリンダ内に偏心回転自在に収納された回転ピストンと、前記シリンダに設けられたベーン溝に往復移動可能に収納されたベーンと、を備えるロータリ式圧縮機において、前記ベーン溝内及び前記ベーンには磁石が設けられると共に、ベーン溝内の磁石と前記ベーンの磁石とは互いに反発するように配置する手段が開示されている。また、特許文献２の実施の形態２では、ベーンにおける回転ピストンに当接する近傍に磁石を配置し、当該磁石と回転ピストンとの間に発生する磁力によりベーンを回転ピストンに当接させる手段が開示されている。  Embodiment 1 of Patent Document 2 includes a cylinder, a rotary piston housed in the cylinder so as to be eccentrically rotatable, and a vane housed in a vane groove provided in the cylinder so as to be reciprocally movable. In the rotary compressor, a magnet is provided in the vane groove and in the vane, and means for disposing the magnet in the vane groove and the magnet of the vane so as to repel each other is disclosed. In Embodiment 2 of Patent Document 2, a magnet is disposed in the vicinity of the vane in contact with the rotating piston, and means for contacting the vane with the rotating piston by the magnetic force generated between the magnet and the rotating piston is disclosed. Has been.

特開２０１１−５８４８２号公報JP 2011-58482 A 特開２００７−６４１１０号公報JP 2007-64110 A

従来のロータリ式圧縮機のベーンは、低負荷条件でベーン背面に作用する圧力が低下し回転ピストン側（前方）に押し付ける力が小さくなり、最も前方に移動した下死点位置で回転ピストンの動きに追随せず、回転ピストンから離間する不安定現象（ベーン離間）を発生しやすく、信頼性と効率の低下を招くことが課題であった。
また、特許文献１に記載の二気筒ロータリ式圧縮機（休筒切替式圧縮機）の場合は、ベーンを前方に押し付ける圧縮バネがなくなり、さらに、ベーン背面部の後方に配置した永久磁石の吸引力により、下死点位置で回転ピストンから離間する不安定現象がいっそう発生しやすいことが課題であった。In a conventional rotary compressor vane, the pressure acting on the back of the vane is reduced under low load conditions, and the pressing force to the rotating piston side (front) is reduced, and the rotating piston moves at the bottom dead center position that has moved forward. The instability phenomenon (vane separation) that separates from the rotating piston is likely to occur, and the reliability and efficiency are lowered.
In addition, in the case of the two-cylinder rotary compressor described in Patent Document 1, there is no compression spring that presses the vane forward, and the permanent magnet disposed behind the vane back surface is attracted. The problem is that an unstable phenomenon of separating from the rotating piston at the bottom dead center position is more likely to occur due to the force.

特許文献２の実施の形態１に記載の二気筒ロータリ式圧縮機では、ベーンの背面部に設けた磁石と、ベーン溝内の後方に取り付けた磁石との反発力は、ベーンが後方に移動した状態では大きいが、ベーンが最も前方に移動する下死点位置では小さいため、ベーン離間の問題を解決できなかった。また、特許文献１のような休筒切替式圧縮機の場合には、元々ベーン背面部の後方に吸引する磁石が配置されているので、反発する磁石を配置することは困難であった。
特許文献２の実施の形態２に記載の二気筒ロータリ式圧縮機では、磁性材料の回転ピストンに金属粉が付着し、回転ピストンと接触し摺動する箇所が摩耗しやすくなり、耐久性の低下を招くことが課題であった。In the two-cylinder rotary compressor described in the first embodiment of Patent Document 2, the repulsive force between the magnet provided on the rear surface of the vane and the magnet attached to the rear in the vane groove causes the vane to move backward. Although it is large in the state, the vane separation problem cannot be solved because the vane is small at the bottom dead center position where the vane moves most forward. Further, in the case of the cylinder switching type compressor as in Patent Document 1, since the magnet to be attracted is originally arranged behind the vane back surface portion, it has been difficult to arrange the repelling magnet.
In the two-cylinder rotary compressor described in Embodiment 2 of Patent Document 2, metal powder adheres to the rotating piston made of magnetic material, and the portion that comes into contact with and slides on the rotating piston is likely to wear, resulting in a decrease in durability. It was a problem to invite.

本発明はこのような課題を解決するためになされたもので、低負荷時でも圧縮バネなしで、ベーンを安定に動作させて信頼性と効率の低下を招くことなく、運転モードを適切に切替えることが可能となり、高効率なロータリ式圧縮機、及びこれを搭載したヒートポンプ装置を得ることを目的とする。  The present invention has been made to solve such a problem. The operation mode is appropriately switched without causing a reduction in reliability and efficiency by stably operating the vane without a compression spring even at a low load. An object of the present invention is to obtain a highly efficient rotary compressor and a heat pump device equipped with the rotary compressor.

本発明に係るロータリ式圧縮機は、２つの圧縮部、電動機、及び、２つの前記圧縮部と前記電動機とを接続する駆動軸を備え、前記圧縮部のそれぞれが、吸入した冷媒を圧縮するシリンダ室、一方の端部が前記シリンダ室に連通したベーン溝、及び、前記ベーン溝の他方の端部に連通したベーン背室が形成されたシリンダと、前記駆動軸の回転によって前記シリンダ室内を偏心回転するリング形状のピストンと、前記シリンダ室の中心に向かう方向である前方と前記シリンダ室から遠ざかる方向である後方とに往復動自在に前記ベーン溝に挿入され、前記ピストンの外周面に先端部が当接した状態で前記シリンダ室を低圧と高圧に仕切り、背面部が前記ベーン背室に収容されたベーンと、を備えたロータリ式圧縮機であって、一方の前記圧縮部は、前記ベーンの前記背面部の後方に配置された第１永久磁石を有し、前記ベーンの前記先端部と前記背面部とに働く圧力の差により、前記ベーンに対して前方に作用する第１力と、前記第１永久磁石により前記ベーンを後方に吸引する第２力とによって、前記ベーンの前記先端部が前記ピストンの外周面に当接した圧縮運転状態と、前記ピストンの外周面から離間した前記ベーンを吸着固定した非圧縮運転状態とを切替える切替え機構を備え、さらに、前記ベーンが最も前方に移動する下死点位置において、前記ベーンを前方へ吸引する第３力が作用するように、前記ベーンの前記背面部よりも前方側に配置されたヨークを備え、前記ヨークは、前記駆動軸の軸方向において前記シリンダ室とは異なる位置に固定されているものである。 The rotary compressor according to the present invention includes two compression units, an electric motor, and a drive shaft that connects the two compression units and the electric motor, and each of the compression units compresses the sucked refrigerant. A cylinder in which a vane groove whose one end communicates with the cylinder chamber and a vane back chamber communicated with the other end of the vane groove are formed, and the cylinder chamber is eccentric by rotation of the drive shaft A ring-shaped piston that rotates, and is inserted into the vane groove so as to be able to reciprocate back and forth in a direction toward the center of the cylinder chamber and in a direction away from the cylinder chamber. A rotary compressor including a vane that partitions the cylinder chamber into a low pressure and a high pressure in a state in which the cylinder chamber is in contact, and a back surface portion of which is accommodated in the vane back chamber. Has a first permanent magnet disposed behind the back surface portion of the vane, and acts on the vane forward due to a difference in pressure acting on the tip portion and the back surface portion of the vane. A compression operation state in which the tip of the vane is in contact with the outer peripheral surface of the piston by one force and a second force that attracts the vane backward by the first permanent magnet, and from the outer peripheral surface of the piston. A switching mechanism for switching between the non-compression operation state in which the separated vane is adsorbed and fixed is provided, and a third force for sucking the vane forward acts at a bottom dead center position where the vane moves most forward. to include a yaw click disposed in front side of the rear portion of the vane, the yoke is one that is fixed to a position different from the cylinder chamber in the axial direction of the drive shaft.

本発明に係るロータリ式圧縮機によれば、低負荷時でも圧縮バネなしで、ベーンを安定に動作させて信頼性と効率の低下を招くことなく、運転モードを適切に切替えることが可能となり、高効率なロータリ式圧縮機、及びこれを搭載したヒートポンプ装置を得ることができる。  According to the rotary compressor according to the present invention, it is possible to appropriately switch the operation mode without causing a reduction in reliability and efficiency by stably operating the vane without a compression spring even at a low load, A highly efficient rotary compressor and a heat pump device equipped with the compressor can be obtained.

本発明の実施の形態１に係るロータリ式圧縮機１の構造を示す概略縦断面図である。It is a schematic longitudinal cross-sectional view which shows the structure of the rotary compressor 1 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る第２圧縮部２０の圧縮運転状態（第２ピストン２３が軸回転角１８０度の下死点位置）を示す概略横断面図（図１のＡ−Ａ断面）である。FIG. 1 is a schematic cross-sectional view (cross-section AA in FIG. 1) showing a compression operation state (the second piston 23 is at the bottom dead center position of the shaft rotation angle 180 degrees) of the second compression section 20 according to Embodiment 1 of the present invention. It is. 本発明の実施の形態１に係る第２圧縮部２０の圧縮運転状態（第２ピストン２３が軸回転角０度の上死点位置）を示す概略横断面図（図１のＡ−Ａ断面）である。Schematic cross-sectional view (A-A cross section of FIG. 1) showing the compression operation state of the second compression section 20 according to Embodiment 1 of the present invention (the second piston 23 is at the top dead center position of the shaft rotation angle 0 degree). It is. 本発明の実施の形態１に係る第２圧縮部２０の非圧縮運転状態（第２ピストン２３が吸着固定位置）を示す概略横断面図（図１のＡ−Ａ断面）である。It is a schematic cross-sectional view (AA cross section of FIG. 1) which shows the non-compression operation state (The 2nd piston 23 is an adsorption fixing position) of the 2nd compression part 20 which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角０度の上死点位置）を示す縦断面図である。It is a longitudinal cross-sectional view which shows the state (The top dead center position of the shaft rotation angle 0 degree) of the 2nd vane 24 at the time of the 2nd compression part 20 which concerns on Embodiment 1 of this invention in a compression driving | running state. 本発明の実施の形態１に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（第２力と第３力の切替え位置）を示す縦断面図である。It is a longitudinal cross-sectional view which shows the state (switching position of a 2nd force and a 3rd force) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 1 of this invention is a compression driving state. 本発明の実施の形態１に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角１８０度の下死点位置）を示す縦断面図である。It is a longitudinal cross-sectional view which shows the state (bottom dead center position of 180 degrees of shaft rotation angles) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 1 of this invention is a compression driving | running state. 本発明の実施の形態１に係るヨーク３３の平坦部３３ｂと第２ベーン２４の背面部２４ｃとの距離（背面ギャップ）に対する第２ベーン２４に作用する後方に吸引する磁力（第２力）との関係及び前方に吸引する磁力（第３力）との関係を示す図である。Magnetic force (second force) attracted backward acting on the second vane 24 with respect to the distance (rear gap) between the flat portion 33b of the yoke 33 and the rear portion 24c of the second vane 24 according to the first embodiment of the present invention. It is a figure which shows the relationship between these, and the magnetic force (3rd force) attracted | sucked ahead. 本発明の実施の形態１に係るヒートポンプ装置２００の基本構成を示す図である。It is a figure which shows the basic composition of the heat pump apparatus 200 which concerns on Embodiment 1 of this invention. 本発明の実施の形態２に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角０度の上死点位置）を示す縦断面図である。It is a longitudinal cross-sectional view which shows the state (The top dead center position of the shaft rotation angle of 0 degree | times) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 2 of this invention is a compression driving state. 本発明の実施の形態２に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角０度の上死点位置）を示す横断面図である。It is a cross-sectional view which shows the state (top dead center position of the shaft rotation angle 0 degree) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 2 of this invention is a compression driving state. 本発明の実施の形態２に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（第２力と第３力の切替え位置）を示す縦断面図である。It is a longitudinal cross-sectional view which shows the state (switching position of 2nd force and 3rd force) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 2 of this invention is a compression driving state. 本発明の実施の形態２に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（第２力と第３力の切替え位置）を示す横断面図である。It is a cross-sectional view which shows the state (switching position of 2nd force and 3rd force) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 2 of this invention is a compression driving state. 本発明の実施の形態２に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角１８０度の下死点位置）を示す縦断面図である。It is a longitudinal cross-sectional view which shows the state (bottom dead center position of 180 degrees of shaft rotation angles) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 2 of this invention is a compression driving | running state. 本発明の実施の形態２に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角１８０度の下死点位置）を示す横断面図である。It is a cross-sectional view which shows the state (bottom dead center position of 180 degrees of shaft rotation angles) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 2 of this invention is a compression driving state. 本発明の実施の形態３に係るロータリ式圧縮機１の構造を示す概略縦断面図である。It is a schematic longitudinal cross-sectional view which shows the structure of the rotary compressor 1 which concerns on Embodiment 3 of this invention. 本発明の実施の形態３に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角０度の上死点位置）を示す縦断面図である。It is a longitudinal cross-sectional view which shows the state (The top dead center position of the shaft rotation angle of 0 degree) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 3 of this invention is a compression driving state. 本発明の実施の形態３に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角０度の上死点位置）を示す横断面図である。It is a cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to Embodiment 3 of the present invention is in the compression operation state (top dead center position of the shaft rotation angle 0 degree). 本発明の実施の形態３に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（第２力と第３力の切替え位置）を示す縦断面図である。It is a longitudinal cross-sectional view which shows the state (switching position of a 2nd force and a 3rd force) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 3 of this invention is a compression driving state. 本発明の実施の形態３に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（第２力と第３力の切替え位置）を示す横断面図である。It is a cross-sectional view which shows the state (switching position of 2nd force and 3rd force) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 3 of this invention is a compression driving state. 本発明の実施の形態３に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角１８０度の下死点位置）を示す縦断面図である。It is a longitudinal cross-sectional view which shows the state (bottom dead center position of 180 degrees of shaft rotation angles) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 3 of this invention is a compression driving | running state. 本発明の実施の形態３に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角１８０度の下死点位置）を示す横断面図である。It is a cross-sectional view which shows the state (bottom dead center position of 180 degrees of shaft rotation angles) of the 2nd vane 24 when the 2nd compression part 20 which concerns on Embodiment 3 of this invention is a compression driving state.

以下、図面に基づいて、本発明に係るロータリ式圧縮機１、及びヒートポンプ装置２００の一例について説明する。以下では、まず、ヒートポンプ装置２００に備えられたロータリ式圧縮機１について説明する。なお、以下に示す図面では、各構成部材の大きさの関係が実際のものとは異なる場合がある。また、以下に示す断面図では、部品を指し示す引出線とハッチングとが重なり合い、引出線が指し示す部品が分かりづらくなることを防止するため、切断されて図示された部品にハッチングを施すことを省略している。したがって、以下の図においては、ハッチングが施されている部品は必ずしも切断されて図示された部品というわけではなく、部品形状を認識しづらい部品にハッチングが施されている。  Hereinafter, an example of the rotary compressor 1 and the heat pump device 200 according to the present invention will be described based on the drawings. Below, the rotary compressor 1 with which the heat pump apparatus 200 was equipped is demonstrated first. In the drawings shown below, the relationship between the sizes of the constituent members may be different from the actual ones. In addition, in the cross-sectional view shown below, in order to prevent the lead line and the hatch pointing to the part from overlapping and obscure the part pointed to by the lead line, it is omitted to hatch the part that is cut and illustrated. ing. Accordingly, in the following drawings, the hatched parts are not necessarily cut and illustrated, but are hatched on the parts whose shape is difficult to recognize.

実施の形態１．
図１は、本発明の実施の形態１に係るロータリ式圧縮機１の構造を示す概略縦断面図である。
図２は、本発明の実施の形態１に係る第２圧縮部２０の圧縮運転状態（第２ピストン２３が軸回転角１８０度の下死点位置）を示す概略横断面図（図１のＡ−Ａ断面）である。
図３は、本発明の実施の形態１に係る第２圧縮部２０の圧縮運転状態（第２ピストン２３が軸回転角０度の上死点位置）を示す概略横断面図（図１のＡ−Ａ断面）である。
図４は、本発明の実施の形態１に係る第２圧縮部２０の非圧縮運転状態（第２ピストン２３が吸着固定位置）を示す概略横断面図（図１のＡ−Ａ断面）である。
図５は、本発明の実施の形態１に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角０度の上死点位置）を示す縦断面図である。
図６は、本発明の実施の形態１に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（第２力と第３力の切替え位置）を示す縦断面図である。
図７は、本発明の実施の形態１に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角１８０度の下死点位置）を示す縦断面図である。
図８は、本発明の実施の形態１に係るヨーク３３の平坦部３３ｂと第２ベーン２４の背面部２４ｃとの距離（背面ギャップ）に対する第２ベーン２４に作用する後方に吸引する磁力（第２力）との関係及び前方に吸引する磁力（第３力）との関係を示す図である。
図９は、本発明の実施の形態１に係るヒートポンプ装置２００の基本構成を示す図である。
なお、図２〜図４に示す台形の破線は、第２ヨーク４３の取付位置を示している。Embodiment 1 FIG.
FIG. 1 is a schematic longitudinal sectional view showing the structure of a rotary compressor 1 according to Embodiment 1 of the present invention.
2 is a schematic cross-sectional view showing the compression operation state (the second piston 23 is at the bottom dead center position of the shaft rotation angle 180 degrees) of the second compression unit 20 according to Embodiment 1 of the present invention (A in FIG. 1). -A cross section).
3 is a schematic cross-sectional view showing the compression operation state of the second compression unit 20 according to Embodiment 1 of the present invention (the second piston 23 is at the top dead center position at an axial rotation angle of 0 degrees) (A in FIG. 1). -A cross section).
FIG. 4 is a schematic cross-sectional view (cross-section AA in FIG. 1) showing the non-compression operation state (the second piston 23 is at the suction fixing position) of the second compression unit 20 according to Embodiment 1 of the present invention. .
FIG. 5 is a longitudinal sectional view showing the state of the second vane 24 when the second compression unit 20 according to the first embodiment of the present invention is in the compression operation state (top dead center position at an axial rotation angle of 0 degrees).
FIG. 6 is a longitudinal sectional view showing the state of the second vane 24 (the switching position between the second force and the third force) when the second compression unit 20 according to Embodiment 1 of the present invention is in the compression operation state.
FIG. 7 is a longitudinal sectional view showing the state of the second vane 24 (the bottom dead center position of the shaft rotation angle of 180 degrees) when the second compression unit 20 according to Embodiment 1 of the present invention is in the compression operation state.
FIG. 8 shows the magnetic force (first force) acting on the second vane 24 with respect to the distance (back gap) between the flat portion 33b of the yoke 33 and the back surface portion 24c of the second vane 24 according to Embodiment 1 of the present invention. 2 force) and a relationship with a magnetic force (a third force) attracted forward.
FIG. 9 is a diagram showing a basic configuration of heat pump apparatus 200 according to Embodiment 1 of the present invention.
A trapezoidal broken line shown in FIGS. 2 to 4 indicates a mounting position of the second yoke 43.

［ロータリ式圧縮機１の基本構成と基本動作］
実施の形態１に係るロータリ式圧縮機１は、例えば空調機や給湯機等のヒートポンプ装置２００（図９を参照）の主要構成要素の一つとして利用され、ガス冷媒を圧縮し高温高圧状態にして蒸気圧縮式冷凍サイクル内に冷媒を循環させる役割をするものである。[Basic configuration and basic operation of the rotary compressor 1]
The rotary compressor 1 according to the first embodiment is used as one of main components of a heat pump device 200 (see FIG. 9) such as an air conditioner or a water heater, for example, and compresses a gas refrigerant into a high temperature and high pressure state. Thus, the refrigerant is circulated in the vapor compression refrigeration cycle.

図１に示すようにロータリ式圧縮機１は、密閉シェル３の内部空間７に、第１圧縮部１０及び第２圧縮部２０で構成された圧縮機構９９を備え、これら第１圧縮部１０及び第２圧縮部２０は駆動軸５を介して電動機８で駆動される。  As shown in FIG. 1, the rotary compressor 1 includes a compression mechanism 99 including a first compression unit 10 and a second compression unit 20 in the internal space 7 of the hermetic shell 3. The second compression unit 20 is driven by the electric motor 8 via the drive shaft 5.

密閉シェル３は、上端部及び下端部が閉塞された例えば円筒形状の密閉容器である。密閉シェル３の底部には、圧縮機構９９を潤滑する潤滑油が貯蔵される潤滑油貯蔵部３ａが設けられている。また、密閉シェル３の上部には、外部冷媒回路に導かれる圧縮機吐出管２が設けられている。  The hermetic shell 3 is, for example, a cylindrical hermetic container whose upper end and lower end are closed. At the bottom of the hermetic shell 3, there is provided a lubricating oil reservoir 3 a that stores lubricating oil that lubricates the compression mechanism 99. In addition, a compressor discharge pipe 2 led to an external refrigerant circuit is provided at the upper part of the hermetic shell 3.

電動機８は、インバータ制御等によって例えば回転周波数が可変であり、回転子８ａと固定子８ｂとを備えている。固定子８ｂは、略円筒形状に形成されており、外周部が密閉シェル３に例えば焼き嵌め等により固定されている。この固定子８ｂには、外部電源から電力供給されるコイルが巻回されている。回転子８ａは、略円筒形状をしており、固定子８ｂの内周面と所定の間隔を介して、固定子８ｂの内周部に配置されている。この回転子８ａには駆動軸５が固定されており、電動機８と圧縮機構９９とは、駆動軸５を介して接続された構成となっている。つまり、電動機８が回転することにより、圧縮機構９９には駆動軸５を介して回転動力が伝達されることとなる。  The electric motor 8 has, for example, a variable rotation frequency by inverter control or the like, and includes a rotor 8a and a stator 8b. The stator 8b is formed in a substantially cylindrical shape, and the outer peripheral portion is fixed to the sealed shell 3 by shrink fitting or the like. A coil that is supplied with electric power from an external power source is wound around the stator 8b. The rotor 8a has a substantially cylindrical shape, and is disposed on the inner peripheral portion of the stator 8b with a predetermined distance from the inner peripheral surface of the stator 8b. The drive shaft 5 is fixed to the rotor 8a, and the electric motor 8 and the compression mechanism 99 are connected via the drive shaft 5. That is, as the electric motor 8 rotates, the rotational power is transmitted to the compression mechanism 99 via the drive shaft 5.

駆動軸５は、該駆動軸５の上部を構成する長軸部５ａと、該駆動軸の下部を構成する短軸部５ｂと、これら長軸部５ａと短軸部５ｂとの間に形成された偏心ピン軸部５ｃ，５ｄと、中間軸部５ｅと、で構成されている。ここで、偏心ピン軸部５ｃは、その中心軸が長軸部５ａ及び短軸部５ｂの回転中心軸から所定距離だけ偏心した円筒形状をしており、後述する第１圧縮部１０の第１シリンダ室１２内に配置される。また、偏心ピン軸部５ｄは、その中心軸が長軸部５ａ及び短軸部５ｂの回転中心軸から所定距離だけ偏心した円筒形状をしており、後述する第２圧縮部２０の第２シリンダ室２２内に配置されるものである。  The drive shaft 5 is formed between a long shaft portion 5a constituting the upper portion of the drive shaft 5, a short shaft portion 5b constituting the lower portion of the drive shaft, and the long shaft portion 5a and the short shaft portion 5b. The eccentric pin shaft portions 5c and 5d and the intermediate shaft portion 5e are configured. Here, the eccentric pin shaft portion 5c has a cylindrical shape whose central axis is eccentric by a predetermined distance from the rotation center axes of the long shaft portion 5a and the short shaft portion 5b. Arranged in the cylinder chamber 12. Further, the eccentric pin shaft portion 5d has a cylindrical shape whose central axis is eccentric by a predetermined distance from the rotation center axes of the long shaft portion 5a and the short shaft portion 5b, and a second cylinder of the second compression portion 20 described later. It is arranged in the chamber 22.

また、偏心ピン軸部５ｃと偏心ピン軸部５ｄとは、位相が１８０度ずれて設けられている。これら偏心ピン軸部５ｃと偏心ピン軸部５ｄは、中間軸部５ｅによって接続されている。なお、中間軸部５ｅは、後述する中間仕切板４の貫通孔内に配置される。このように構成された駆動軸５は、長軸部５ａが第１支持部材６０の軸受部６０ａで回転自在に支持され、短軸部５ｂが第２支持部材７０の軸受部７０ａで回転自在に支持されている。
つまり、駆動軸５が回転した際に、第１シリンダ室１２及び第２シリンダ室２２内において、偏心ピン軸部５ｃ，５ｄが偏心回転運動する構成となっている。Further, the eccentric pin shaft portion 5c and the eccentric pin shaft portion 5d are provided with a phase difference of 180 degrees. The eccentric pin shaft portion 5c and the eccentric pin shaft portion 5d are connected by an intermediate shaft portion 5e. The intermediate shaft portion 5e is disposed in a through hole of the intermediate partition plate 4 described later. In the drive shaft 5 configured in this manner, the long shaft portion 5 a is rotatably supported by the bearing portion 60 a of the first support member 60, and the short shaft portion 5 b is freely rotatable by the bearing portion 70 a of the second support member 70. It is supported.
That is, when the drive shaft 5 rotates, the eccentric pin shaft portions 5c and 5d are configured to eccentrically rotate in the first cylinder chamber 12 and the second cylinder chamber 22.

第１圧縮部１０及び第２圧縮部２０は、それぞれ、第１シリンダ１１及び第２シリンダ２１、第１ピストン１３及び第２ピストン２３、並びに、第１ベーン１４及び第２ベーン２４等で構成される。第１シリンダ１１及び第２シリンダ２１は、それぞれ駆動軸５（より詳しくは、長軸部５ａ及び短軸部５ｂ）と略同心となる略円筒状の貫通孔が上下方向に貫通形成された平板部材である。第１シリンダ１１の貫通孔は、一方の端部が第１支持部材６０のフランジ部６０ｂにより閉塞され、他方の端部が中間仕切板４によって閉塞され、第１シリンダ室１２を形成している。また、第２シリンダ２１の貫通孔は、一方の端部が第２支持部材７０のフランジ部７０ｂにより閉塞され、他方の端部が中間仕切板４によって閉塞され、第２シリンダ室２２を形成している。  The 1st compression part 10 and the 2nd compression part 20 are constituted by the 1st cylinder 11 and the 2nd cylinder 21, the 1st piston 13 and the 2nd piston 23, the 1st vane 14, the 2nd vane 24, etc., respectively. The Each of the first cylinder 11 and the second cylinder 21 is a flat plate in which a substantially cylindrical through hole that is substantially concentric with the drive shaft 5 (more specifically, the long shaft portion 5a and the short shaft portion 5b) is vertically formed. It is a member. One end of the through hole of the first cylinder 11 is closed by the flange portion 60 b of the first support member 60, and the other end is closed by the intermediate partition plate 4 to form the first cylinder chamber 12. . The through hole of the second cylinder 21 is closed at one end by the flange portion 70 b of the second support member 70 and closed at the other end by the intermediate partition plate 4 to form the second cylinder chamber 22. ing.

第１シリンダ室１２及び第２シリンダ室２２内には、それぞれ、第１ピストン１３及び第２ピストン２３が設けられている。この第１ピストン１３及び第２ピストン２３は、それぞれリング状に形成されており、駆動軸５の偏心ピン軸部５ｃ，５ｄに摺動自在に設けられている。また、第１シリンダ１１及び第２シリンダ２１には、一方の端部がそれぞれ第１シリンダ室１２及び第２シリンダ室２２に連通し、第１シリンダ室１２及び第２シリンダ室２２の半径方向に延びる第１ベーン溝１９及び第２ベーン溝２９が形成されている。そして、第１ベーン溝１９及び第２ベーン溝２９には、それぞれ、第１シリンダ室１２及び第２シリンダ室２２の中心に向かう方向である前方と第１シリンダ室１２及び第２シリンダ室２２から遠ざかる方向である後方とに往復動自在に、第１ベーン１４及び第２ベーン２４が設けられている。第１ベーン１４及び第２ベーン２４の先端部１４ａ，２４ａがそれぞれ第１ピストン１３及び第２ピストン２３の外周部に当接することにより、第１シリンダ室１２及び第２シリンダ室２２は、それぞれ吸入室と圧縮室とに分割される。  A first piston 13 and a second piston 23 are provided in the first cylinder chamber 12 and the second cylinder chamber 22, respectively. The first piston 13 and the second piston 23 are each formed in a ring shape, and are slidably provided on the eccentric pin shaft portions 5 c and 5 d of the drive shaft 5. In addition, one end of each of the first cylinder 11 and the second cylinder 21 communicates with the first cylinder chamber 12 and the second cylinder chamber 22, respectively, and extends in the radial direction of the first cylinder chamber 12 and the second cylinder chamber 22. Extending first vane grooves 19 and second vane grooves 29 are formed. The first vane groove 19 and the second vane groove 29 are respectively formed from the front and the first cylinder chamber 12 and the second cylinder chamber 22 in the direction toward the center of the first cylinder chamber 12 and the second cylinder chamber 22. The 1st vane 14 and the 2nd vane 24 are provided so that reciprocation is possible to the back which is the direction which goes away. The tip portions 14a and 24a of the first vane 14 and the second vane 24 come into contact with the outer peripheral portions of the first piston 13 and the second piston 23, respectively, so that the first cylinder chamber 12 and the second cylinder chamber 22 are sucked respectively. It is divided into a chamber and a compression chamber.

また、第１シリンダ１１及び第２シリンダ２１には、それぞれ、第１ベーン溝１９及び第２ベーン溝２９の後端部と連通する位置、つまり第１ベーン１４及び第２ベーン２４の後端部１４ｂ，２４ｂを収容する第１ベーン背室１５及び第２ベーン背室２５が形成されている。この第１ベーン背室１５及び第２ベーン背室２５は、第１シリンダ１１及び第２シリンダ２１を上下方向に貫通するように設けられている。また、第１ベーン背室１５及び第２ベーン背室２５は密閉シェル３の内部空間７に一部開放されており、潤滑油貯蔵部３ａに貯留されている潤滑油が第１ベーン背室１５及び第２ベーン背室２５に流入できる構成となっている。第１ベーン背室１５及び第２ベーン背室２５に流入した潤滑油は、第１ベーン溝１９及び第２ベーン溝２９と第１ベーン１４及び第２ベーン２４の側面との間に流れ込み、両者の間の摺動抵抗を低減させる。後述のように、本実施の形態１に係るロータリ式圧縮機１は、圧縮機構９９で圧縮された冷媒が密閉シェル３の内部空間７に吐出される構成となっている。このため、第１ベーン背室１５及び第２ベーン背室２５は、密閉シェル３の内部空間７と同じ高圧雰囲気となる。  The first cylinder 11 and the second cylinder 21 are respectively connected to the rear end portions of the first vane groove 19 and the second vane groove 29, that is, the rear end portions of the first vane 14 and the second vane 24. A first vane back chamber 15 and a second vane back chamber 25 for accommodating 14b and 24b are formed. The first vane back chamber 15 and the second vane back chamber 25 are provided so as to penetrate the first cylinder 11 and the second cylinder 21 in the vertical direction. The first vane back chamber 15 and the second vane back chamber 25 are partially opened in the internal space 7 of the hermetic shell 3, and the lubricant stored in the lubricant storage section 3 a is used as the first vane back chamber 15. And it becomes the structure which can flow in into the 2nd vane back room 25. FIG. The lubricating oil that has flowed into the first vane back chamber 15 and the second vane back chamber 25 flows between the first vane groove 19 and the second vane groove 29 and the side surfaces of the first vane 14 and the second vane 24, To reduce the sliding resistance between. As described later, the rotary compressor 1 according to the first embodiment is configured such that the refrigerant compressed by the compression mechanism 99 is discharged into the internal space 7 of the sealed shell 3. For this reason, the first vane back chamber 15 and the second vane back chamber 25 have the same high-pressure atmosphere as the internal space 7 of the sealed shell 3.

第１シリンダ１１及び第２シリンダ２１には、それぞれ、ガス冷媒を第１シリンダ室１２及び第２シリンダ室２２に流入させるための吸入マフラ６が接続されている。吸入マフラ６は、容器６ｂ、流入管６ａ、流出管６ｃ，６ｄを備えている。容器６ｂは、冷凍サイクルを構成する蒸発器から流出した低圧の冷媒を貯留する。流入管６ａは、蒸発器から容器６ｂに低圧冷媒を導き、流出管６ｃ，６ｄは、それぞれ、容器６ｂに貯留された冷媒のうちのガス冷媒をシリンダ吸入流路１７，２７を経由して、第１シリンダ室１２及び第２シリンダ室２２に導く役割をする。  A suction muffler 6 for allowing a gas refrigerant to flow into the first cylinder chamber 12 and the second cylinder chamber 22 is connected to the first cylinder 11 and the second cylinder 21, respectively. The suction muffler 6 includes a container 6b, an inflow pipe 6a, and outflow pipes 6c and 6d. The container 6b stores the low-pressure refrigerant that has flowed out of the evaporator constituting the refrigeration cycle. The inflow pipe 6a guides the low-pressure refrigerant from the evaporator to the container 6b, and the outflow pipes 6c and 6d respectively pass the gas refrigerant out of the refrigerant stored in the container 6b via the cylinder suction channels 17 and 27. It plays a role of leading to the first cylinder chamber 12 and the second cylinder chamber 22.

また、第１シリンダ室１２及び第２シリンダ室２２には、内部で圧縮されたガス冷媒を吐出する吐出口１８，２８が形成されている。この吐出口１８，２８は第１支持部材６０及び第２支持部材７０のフランジ部６０ｂ，７０ｂに形成された貫通孔と連通しており、当該貫通孔には、第１シリンダ室１２及び第２シリンダ室２２内が所定の圧力以上となった際に開く開閉弁１８ａ，２８ａが設けられている。また、第１支持部材６０及び第２支持部材７０には、貫通孔を覆うように吐出マフラ６３，７３が取り付けられている。  The first cylinder chamber 12 and the second cylinder chamber 22 are formed with discharge ports 18 and 28 for discharging a gas refrigerant compressed inside. The discharge ports 18 and 28 communicate with through holes formed in the flange portions 60 b and 70 b of the first support member 60 and the second support member 70, and the first cylinder chamber 12 and the second cylinder holes are formed in the through holes. On-off valves 18a and 28a are provided that open when the inside of the cylinder chamber 22 becomes a predetermined pressure or higher. Further, discharge mufflers 63 and 73 are attached to the first support member 60 and the second support member 70 so as to cover the through holes.

［圧縮機構９９の第２圧縮部２０の切替え機構３１の基本構成と動作］
上記のように、第１圧縮部１０及び第２圧縮部２０の基本的な圧縮機構の構成は同じであるが、第２圧縮部２０には切替え機構３１が設置されている点で異なっている。
実施の形態１に係るロータリ式圧縮機１は、第２圧縮部２０に切替え機構３１を備えたことにより、第１圧縮部１０と第２圧縮部２０とを同時に圧縮運転する並列運転モードと、第１圧縮部１０が圧縮運転を行い、第２圧縮部２０が非圧縮運転となる単独運転モードとに切替え可能に構成される。
ここで、図１は、並列運転モード時、すなわち第１圧縮部１０及び第２圧縮部２０が圧縮運転状態の縦断面図を示している。また、図２と図３は、並列運転モードで、第２圧縮部２０が圧縮運転状態の第２ベーン２４の状態を示し、それぞれ、軸回転角１８０度の下死点位置と軸回転角０度の上死点位置を示す概略横断面図（図１のＡ−Ａ断面）である。図４は、第２圧縮部２０が非圧縮運転状態の第２ベーン２４の状態を示している。
以下、切替え機構３１の詳細な構成について説明する。[Basic Configuration and Operation of Switching Mechanism 31 of Second Compression Unit 20 of Compression Mechanism 99]
As described above, the basic compression mechanism configuration of the first compression unit 10 and the second compression unit 20 is the same, but the second compression unit 20 is different in that a switching mechanism 31 is installed. .
The rotary compressor 1 according to Embodiment 1 includes the switching mechanism 31 in the second compression unit 20, thereby performing a parallel operation mode in which the first compression unit 10 and the second compression unit 20 are simultaneously compressed. The first compression unit 10 performs a compression operation and the second compression unit 20 is configured to be switchable to a single operation mode in which a non-compression operation is performed.
Here, FIG. 1 shows a longitudinal sectional view in the parallel operation mode, that is, when the first compression unit 10 and the second compression unit 20 are in the compression operation state. 2 and 3 show the state of the second vane 24 in the parallel operation mode in which the second compression unit 20 is in the compression operation state. The bottom dead center position and the shaft rotation angle 0 are respectively set to the shaft rotation angle 180 degrees. It is a schematic cross-sectional view (AA cross section of FIG. 1) which shows the top dead center position. FIG. 4 shows the state of the second vane 24 when the second compression unit 20 is in the non-compression operation state.
Hereinafter, a detailed configuration of the switching mechanism 31 will be described.

［切替え機構３１の基本構成］
切替え機構３１は、第２ベーン背室２５の後方に設けられた第２シリンダ２１の収納室３７内に配置されている。そして、第２ベーン背室２５の後方側に永久磁石３２が配置され、永久磁石３２の前方側に第２ベーン２４に磁束密度を集中させるためのヨーク３３が取り付けられて主に構成されている。ヨーク３３は凹型形状の磁性材料で作製されており、凹型形状の底部分である平坦部３３ｂとこれに直立して前方側に突出する両腕部３３ａとで構成されている。
ここで、永久磁石３２が、本発明の第１永久磁石に相当する。[Basic configuration of switching mechanism 31]
The switching mechanism 31 is disposed in a storage chamber 37 of the second cylinder 21 provided behind the second vane back chamber 25. And the permanent magnet 32 is arrange | positioned in the back side of the 2nd vane back chamber 25, and the yoke 33 for concentrating magnetic flux density to the 2nd vane 24 is attached to the front side of the permanent magnet 32, and is mainly comprised. . The yoke 33 is made of a concave magnetic material, and is composed of a flat portion 33b that is a bottom portion of the concave shape and both arm portions 33a that stand upright and project forward.
Here, the permanent magnet 32 corresponds to the first permanent magnet of the present invention.

ヨーク３３の平坦部３３ｂの背面（後面）には直方体の永久磁石３２が張り付けられている。また、第２シリンダ２１が通常の圧縮動作時には、第２ピストン２３の上死点位置（図３の第２ピストン２３の位置、第２ピストン２３の軸回転角０度）で上記第２ベーン２４の後端部２４ｂが、ヨーク３３の凹型形状の両腕部３３ａの先端側内角付近に接近するようにヨーク３３が配置されている。なお、平坦部３３ｂの前面（第２ベーン２４の後端部２４ｂと対向する面）に、非磁性の薄い長方形平板で構成されたスペーサを取り付けてもよい。このようなスペーサを備えることにより、第２ベーン２４の後端部２４ｂが磁気吸引により吸着固定したときに、後端部２４ｂとヨーク３３の平坦部３３ｂとの距離（背面ギャップ）を一定に保って、吸引磁力のばらつきを小さくすることができる。  A rectangular parallelepiped permanent magnet 32 is attached to the back surface (rear surface) of the flat portion 33 b of the yoke 33. Further, when the second cylinder 21 is in a normal compression operation, the second vane 24 is at the top dead center position of the second piston 23 (the position of the second piston 23 in FIG. 3 and the shaft rotation angle of the second piston 23 is 0 degrees). The yoke 33 is disposed so that the rear end portion 24b approaches the vicinity of the front-end side inner corners of the concave arm portions 33a of the yoke 33. In addition, you may attach the spacer comprised by the nonmagnetic thin rectangular flat plate to the front surface (surface facing the rear-end part 24b of the 2nd vane 24) of the flat part 33b. By providing such a spacer, when the rear end portion 24b of the second vane 24 is attracted and fixed by magnetic attraction, the distance (rear gap) between the rear end portion 24b and the flat portion 33b of the yoke 33 is kept constant. Thus, variations in the attractive magnetic force can be reduced.

そして、第２ベーン２４に磁束を集中的に通過させるため、永久磁石３２とヨーク３３の周囲を非磁性材料である保持具３６で覆い、永久磁石３２とヨーク３３とを固定する。
また、永久磁石３２の背面側は磁性材料である第２シリンダ２１の外縁で囲まれている。もし、永久磁石３２と第２シリンダ２１の外縁との間に隙間が発生するならば、その隙間に磁性材料のシム３８を差し込んで調整する。In order to allow magnetic flux to pass through the second vane 24 in a concentrated manner, the permanent magnet 32 and the yoke 33 are covered with a holder 36 made of a nonmagnetic material, and the permanent magnet 32 and the yoke 33 are fixed.
The back side of the permanent magnet 32 is surrounded by the outer edge of the second cylinder 21 that is a magnetic material. If a gap is generated between the permanent magnet 32 and the outer edge of the second cylinder 21, a shim 38 of a magnetic material is inserted into the gap for adjustment.

［第２ベーン２４に作用する押付け力Ｆｐ（以下、本発明の第１力に相当）と吸引磁力Ｆｍ（以下、本発明の第２力に相当）］
第１ベーン１４及び第２ベーン２４には、先端部１４ａ，２４ａ側に吸入圧Ｐｓ（第１シリンダ室１２及び第２シリンダ室２２に吸入された低圧冷媒の圧力）が作用し、後端部１４ｂ，２４ｂを含む背面部１４ｃ，２４ｃには吐出圧Ｐｄ（密閉シェル３の内部空間７の圧力、つまり、圧縮機構９９で圧縮された高圧冷媒の圧力）が作用する。
ここで、背面部とは、ベーンの先端側、側面側及び上下面側を除く背面側全体をさす。後端部は、背面部の最も後端の位置をさす。背面部が並行平面であれば後端部と同義であるが凹凸や曲面形状のある場合は異なる位置である。[Pressing force Fp acting on the second vane 24 (hereinafter, equivalent to the first force of the present invention) and attractive magnetic force Fm (hereinafter, corresponding to the second force of the present invention)]
The first vane 14 and the second vane 24 are subjected to suction pressure Ps (pressure of the low-pressure refrigerant sucked into the first cylinder chamber 12 and the second cylinder chamber 22) on the front end portions 14a, 24a side, and the rear end portions The discharge pressure Pd (the pressure in the internal space 7 of the sealed shell 3, that is, the pressure of the high-pressure refrigerant compressed by the compression mechanism 99) acts on the back surface portions 14c and 24c including 14b and 24b.
Here, the back surface portion refers to the entire back surface side excluding the tip side, the side surface side, and the top and bottom surface sides of the vane. The rear end portion indicates the position of the rearmost end of the back surface portion. If the back part is a parallel plane, it is synonymous with the rear end part, but if it has irregularities or curved shapes, it is a different position.

このため、第１ベーン１４及び第２ベーン２４の双方には、先端部１４ａ，２４ａ及び背面部１４ｃ，２４ｃに作用する圧力の差（Ｐｄ−Ｐｓ）に応じて、第１ベーン１４及び第２ベーン２４を第１ピストン１３及び第２ピストン２３側へ押付ける押付け力Ｆｐが作用する。さらに、第１ベーン背室１５の後方には圧縮バネ４０が取り付けられており、差圧の押付け力に加えて、圧縮バネ４０の押付け力が第１ベーン１４に働くこととなる。例えば、起動時にはこの差圧（Ｐｄ−Ｐｓ）が小さいので圧縮バネ４０の押付け力により第１ベーン１４が第１ピストン１３に当接して圧縮動作をする。  Therefore, both the first vane 14 and the second vane 24 have the first vane 14 and the second vane 24 in accordance with the pressure difference (Pd−Ps) acting on the front end portions 14a and 24a and the back surface portions 14c and 24c. A pressing force Fp that presses the vane 24 toward the first piston 13 and the second piston 23 acts. Further, a compression spring 40 is attached to the rear of the first vane back chamber 15, and the pressing force of the compression spring 40 acts on the first vane 14 in addition to the pressing force of the differential pressure. For example, since the differential pressure (Pd−Ps) is small at the time of activation, the first vane 14 abuts on the first piston 13 by the pressing force of the compression spring 40 to perform the compression operation.

一方、第２ベーン背室２５の後方に圧縮バネ４０が取り付けられていないため、差圧による押付け力のみが第２ベーン２４を第２ピストン２３に押付け力Ｆｐとして働く。
圧縮運転過程では第１シリンダ１１及び第２シリンダ２１の内圧が変動し、押付け力Ｆｐの最大値Ｆｐｍａｘは、第２ピストン２３の軸回転角が０度付近（図３の状態で、第２ピストン２３が第２ベーン溝２９の中心軸に最接近した状態）のときに生じる。
このときの押付け力Ｆｐの最大値Ｆｐｍａｘは、
Ｆｐｍａｘ＝Ｐｄ（０度）×ベーン背面部面積−Ｐｓ（０度）×ベーン先端部面積となる。On the other hand, since the compression spring 40 is not attached to the rear of the second vane back chamber 25, only the pressing force due to the differential pressure works as the pressing force Fp for the second vane 24 to the second piston 23.
In the compression operation process, the internal pressures of the first cylinder 11 and the second cylinder 21 fluctuate, and the maximum value Fpmax of the pressing force Fp is such that the shaft rotation angle of the second piston 23 is around 0 degrees (in the state of FIG. This occurs when 23 is closest to the central axis of the second vane groove 29).
The maximum value Fpmax of the pressing force Fp at this time is
Fpmax = Pd (0 degree) × vane back surface area−Ps (0 degree) × vane tip area.

第２ベーン２４に作用する吸引磁力Ｆｍは、
Ｆｍ＝Ｂｇ２×Ｓ／（２×μ０）［Ｎ］
Ｂｇ：吸着面の磁束密度［Ｔ］
Ｓ：吸着面の面積［ｍ２］
μ０：真空中の透磁率
で表され、磁束密度は永久磁石３２からの距離にほぼ反比例して減少する。The attractive magnetic force Fm acting on the second vane 24 is
Fm = Bg 2 × S / (2 × μ 0 ) [N]
Bg: Magnetic flux density [T] on the attracting surface
S: Area of adsorption surface [m 2 ]
μ 0 : Permeability in vacuum, and the magnetic flux density decreases almost in inverse proportion to the distance from the permanent magnet 32.

まず、第２圧縮部２０が圧縮運転を行っている時における第２ピストン２３の軸回転角が０度のときの吸引磁力Ｆｍを第１吸引磁力Ｆｍ１とする。
このとき、押付け力Ｆｐｍａｘ＞第１吸引磁力Ｆｍ１の関係が成り立っている。すると、第２ベーン２４は上死点位置（図３、第２ピストン２３の軸回転角０度）から下死点位置（図２、第２ピストン２３の軸回転角１８０度）まで、第２ピストン２３の周面に当接しながら往復動し、圧縮運転状態が維持される。
一方、第２ベーン２４に作用する吸引磁力Ｆｍは、第２ピストン２３の軸回転角が０度付近のときに、第２ベーン２４の背面部２４ｃがヨーク３３の両腕部３３ａの前端部に最も接近（最短距離）するので最大となる。このときの吸引磁力Ｆｍが上記の第１吸引磁力Ｆｍ１となるように、永久磁石３２とヨーク３３、第２ベーン背室２５のまわりの切替え機構３１を設計する。First, the attractive magnetic force Fm when the second piston 23 is performing the compression operation and the shaft rotation angle of the second piston 23 is 0 degree is defined as a first attractive magnetic force Fm1.
At this time, the relationship of pressing force Fpmax> first attractive magnetic force Fm1 is established. Then, the second vane 24 moves from the top dead center position (FIG. 3, the shaft rotation angle of the second piston 23 to 0 degrees) to the bottom dead center position (FIG. 2, the shaft rotation angle of the second piston 23 is 180 degrees). While reciprocating while contacting the peripheral surface of the piston 23, the compression operation state is maintained.
On the other hand, the attractive magnetic force Fm acting on the second vane 24 is such that the back surface portion 24c of the second vane 24 is applied to the front end portions of both arm portions 33a of the yoke 33 when the axial rotation angle of the second piston 23 is around 0 degrees. Since it is closest (shortest distance), it becomes the maximum. The switching mechanism 31 around the permanent magnet 32, the yoke 33, and the second vane back chamber 25 is designed so that the attractive magnetic force Fm at this time becomes the first attractive magnetic force Fm1.

次に、第２ベーン２４の上死点位置（軸回転角０度）で第１吸引磁力Ｆｍ１が働いて、差圧の押付け力Ｆｐｍａｘ＜第１吸引磁力Ｆｍ１の関係が成り立つと、第２ベーン２４の先端部２４ａが第２ピストン２３の外周面から離間する。さらに、第２ベーン２４は磁気吸引力により吸着位置まで後方側に移動する（図４に示した第２ベーン２４の状態）。ヨーク３３が直方体形状の場合には、第２ベーン２４の後端部２４ｂ（ここでは背面部２４ｃと同義）とヨーク３３の平坦部３３ｂとの距離（背面ギャップ）が小さくなるほど、吸引磁力Ｆｍが急激に増加する。すなわち、第２ベーン２４の移動距離に対する吸引磁力Ｆｍの変化する割合（吸引磁力Ｆｍの勾配）は急激に大きくなる。そして、第２ベーン２４の後端部２４ｂがヨーク３３の平坦部３３ｂに着座し、永久磁石３２の磁気により吸着位置に固定される。このとき、ヨーク３３の平坦部３３ｂと、第２ベーン２４の後端部２４ｂとの距離は最短となる。  Next, when the first attractive magnetic force Fm1 works at the top dead center position (axial rotation angle 0 degree) of the second vane 24 and the relationship of the pressing force Fpmax of the differential pressure <the first attractive magnetic force Fm1 is established, the second vane The leading end 24 a of 24 is separated from the outer peripheral surface of the second piston 23. Further, the second vane 24 moves rearward to the adsorption position by the magnetic attractive force (the state of the second vane 24 shown in FIG. 4). When the yoke 33 has a rectangular parallelepiped shape, the attractive magnetic force Fm becomes smaller as the distance between the rear end portion 24b of the second vane 24 (here, synonymous with the back surface portion 24c) and the flat portion 33b of the yoke 33 (back surface gap) becomes smaller. Increases rapidly. That is, the rate of change of the attractive magnetic force Fm with respect to the moving distance of the second vane 24 (gradient of the attractive magnetic force Fm) increases rapidly. The rear end portion 24 b of the second vane 24 is seated on the flat portion 33 b of the yoke 33 and is fixed to the attracting position by the magnetism of the permanent magnet 32. At this time, the distance between the flat portion 33b of the yoke 33 and the rear end portion 24b of the second vane 24 is the shortest.

一方、ヨーク３３が凹型形状の場合において、第２ベーン２４の先端部２４ａが離間状態（磁石吸引途中）で働く第２吸引磁力Ｆｍ２は、第２ベーン２４の側面部がヨーク３３の凹型形状の両腕部３３ａの内壁に沿ってほぼ平行に移動するため、第２ベーン２４の移動距離に対して吸引磁力Ｆｍが変化する割合（吸引磁力Ｆｍの勾配）は、この区間でほぼ一定の値に保たれ、吸引磁力Ｆｍの勾配が非常に小さい区間（吸引磁力一定区間）が存在することが特徴である。  On the other hand, when the yoke 33 has a concave shape, the second attractive magnetic force Fm2 that works when the tip 24a of the second vane 24 is separated (while the magnet is being attracted) is such that the side surface of the second vane 24 has the concave shape of the yoke 33. Since the movement is almost parallel along the inner walls of both arms 33a, the rate of change of the attractive magnetic force Fm with respect to the moving distance of the second vane 24 (gradient of the attractive magnetic force Fm) is a substantially constant value in this section. This is characterized in that there is a section where the gradient of the attractive magnetic force Fm is very small (a constant attractive magnetic force section).

［第２ベーン２４の前方への吸引磁力発生部の基本構成と動作］
図５、図６、図７は、第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態示す縦断面図で、ぞれぞれ、軸回転角０度の上死点位置、第２力と第３力の切替え位置、軸回転角１８０度の下死点位置を示す。
本実施の形態１に係る第２圧縮部２０は、第２ベーン２４が最も前方（第２シリンダ室２２の中心側）に移動する下死点位置において、第２ベーン２４の背面部２４ｃよりも前方となる位置に配置された第２ヨーク４３を備えている。この第２ヨーク４３は、第２シリンダ２１の下側、つまり、駆動軸５の軸方向において第２シリンダ室２２とは異なる位置（高さ）に設けられている。換言すると、第２ヨーク４３は、駆動軸５の軸方向において第２シリンダ２１とは異なる位置（高さ）に設けられている。この第２ヨーク４３は、磁性材料のボルト４４で非磁性の保持具３６に取り付けてある。第２ヨーク４３は、第２ベーン２４の下面部と対向する先端部４３ａを備える。[Basic configuration and operation of the attractive magnetic force generating portion forward of the second vane 24]
5, 6, and 7 are longitudinal sectional views showing the state of the second vane 24 when the second compression unit 20 is in the compression operation state. The switching position between the second force and the third force, and the bottom dead center position of the shaft rotation angle of 180 degrees are shown.
The second compression unit 20 according to the first embodiment has a lower dead center position where the second vane 24 moves most forward (center side of the second cylinder chamber 22) than the back surface portion 24c of the second vane 24. A second yoke 43 is provided at the front position. The second yoke 43 is provided at a position (height) different from the second cylinder chamber 22 below the second cylinder 21, that is, in the axial direction of the drive shaft 5. In other words, the second yoke 43 is provided at a position (height) different from that of the second cylinder 21 in the axial direction of the drive shaft 5. The second yoke 43 is attached to the nonmagnetic holder 36 with a bolt 44 made of a magnetic material. The second yoke 43 includes a tip end portion 43 a that faces the lower surface portion of the second vane 24.

図３及び図５の軸回転角０度の上死点位置では、第２ベーン２４の背面部２４ｃの位置が、ボルト４４よりもヨーク３３の両腕部３３ａに接近する。このため、永久磁石３２からヨーク３３を通って、第２ベーン２４の背面部２４ｃに向かって磁束が流れ、第２シリンダ２１内を通過して、永久磁石３２に磁束が戻る（第２力）。  3 and 5, the position of the back surface portion 24 c of the second vane 24 is closer to the both arm portions 33 a of the yoke 33 than the bolts 44. Therefore, the magnetic flux flows from the permanent magnet 32 through the yoke 33 toward the back surface portion 24c of the second vane 24, passes through the second cylinder 21, and returns to the permanent magnet 32 (second force). .

特に、第２ベーン２４の背面部２４ｃに、透磁率の高い例えば円筒形状の金属材料（磁性材料）が圧入されており、ここがベーン吸引箇所４１として磁束を集中させる機能をする。つまり、ベーン吸引箇所４１に、後述の第３力等が集中的に作用する。ベーン吸引箇所４１を設ける場合、第２ベーン２４のベーン吸引箇所以外の部分は、ベーン吸引箇所４１よりも透磁率の低い材料で形成することができる。本実施の形態１では、第２ベーン２４のベーン吸引箇所以外の箇所を非磁性材料で形成している。ここで、第２ベーン２４は、圧縮運転時、軸回転角０度の上死点位置と軸回転角１８０度の下死点位置とを往復運動する。この際、第２ベーン２４の側面部は第２ベーン溝２９の壁面と摺動し、第２ベーン２４の上面部は中間仕切板４の下面部と摺動し、第２ベーン２４の下面部は、第２支持部材７０のフランジ部７０ｂの上面部と摺動する。本実施の形態１では、第２ベーン２４が最も前方に移動している軸回転角１８０度の下死点位置において、第２ベーン溝２９、中間仕切板４及びフランジ部７０ｂよりも外側（後方）となる位置に、ベーン吸引箇所４１を配置している。つまり、ベーン吸引箇所４１は、周囲の部材と摺動しない位置に配置されている。なお、ベーン吸引箇所４１を設ける場合、図２及び図７の軸回転角１８０度の下死点位置において、第２ヨーク４３の先端部４３ａの横方向位置を、ベーン吸引箇所４１と同位置あるいはベーン吸引箇所４１よりも前方（第２シリンダ室の中心より）に配置する。  In particular, for example, a cylindrical metal material (magnetic material) having a high magnetic permeability is press-fitted into the back surface portion 24 c of the second vane 24, and this functions as a vane suction portion 41 to concentrate the magnetic flux. That is, a third force, which will be described later, acts on the vane suction portion 41 in a concentrated manner. When the vane suction point 41 is provided, the portion of the second vane 24 other than the vane suction point can be formed of a material having a lower magnetic permeability than the vane suction point 41. In the first embodiment, portions other than the vane suction portion of the second vane 24 are formed of a nonmagnetic material. Here, during the compression operation, the second vane 24 reciprocates between a top dead center position with an axis rotation angle of 0 degrees and a bottom dead center position with an axis rotation angle of 180 degrees. At this time, the side surface portion of the second vane 24 slides with the wall surface of the second vane groove 29, the upper surface portion of the second vane 24 slides with the lower surface portion of the intermediate partition plate 4, and the lower surface portion of the second vane 24. Slides on the upper surface portion of the flange portion 70 b of the second support member 70. In the first embodiment, at the bottom dead center position of the shaft rotation angle of 180 degrees where the second vane 24 is moving most forward, it is outside (rearward) from the second vane groove 29, the intermediate partition plate 4 and the flange portion 70b. The vane suction point 41 is arranged at a position where That is, the vane suction portion 41 is disposed at a position where it does not slide with the surrounding members. When the vane suction point 41 is provided, the lateral position of the distal end portion 43a of the second yoke 43 is set at the same position as the vane suction point 41 at the bottom dead center position of the shaft rotation angle of 180 degrees in FIGS. It arrange | positions ahead of the vane suction location 41 (from the center of a 2nd cylinder chamber).

図６の第２力と第３力の切替え位置では、第２ベーン２４の背面部２４ｃからボルト４４までの距離と、第２ベーン２４の背面部２４ｃからヨーク３３の両腕部３３ａまでの距離とが、ほぼ同等になる。このため、永久磁石３２からヨーク３３を通って、第２ベーン２４の背面部２４ｃに向かう磁束と、永久磁石３２からボルト４４に向かう磁束とに分かれる。ボルト４４を通る磁束が第２ヨーク４３を通って再び第２ベーン２４に接近するように、第２ヨーク４３の先端部４３ａの形状を楔形の形状としてある。  6, the distance from the back surface portion 24c of the second vane 24 to the bolt 44, and the distance from the back surface portion 24c of the second vane 24 to both arms 33a of the yoke 33. Is almost equivalent. For this reason, the magnetic flux is divided into a magnetic flux from the permanent magnet 32 through the yoke 33 toward the back surface portion 24 c of the second vane 24 and a magnetic flux from the permanent magnet 32 toward the bolt 44. The shape of the tip 43a of the second yoke 43 is a wedge shape so that the magnetic flux passing through the bolt 44 passes through the second yoke 43 and again approaches the second vane 24.

図２及び図７の軸回転角１８０度の下死点位置では、第２ベーン２４の背面部２４ｃの位置がボルト４４よりもヨーク３３の両腕部３３ａから遠ざかる。一方で、第２ヨーク４３の先端部４３ａがベーン吸引箇所４１に接近するので、ボルト４４を通る磁束が流れやすくなり、第２ベーン２４を前方に吸引する磁力（第３力）が発生する。  2 and 7, the position of the back surface portion 24 c of the second vane 24 is farther from the both arms 33 a of the yoke 33 than the bolts 44. On the other hand, since the tip end portion 43a of the second yoke 43 approaches the vane suction point 41, the magnetic flux passing through the bolts 44 easily flows, and a magnetic force (third force) that attracts the second vane 24 forward is generated.

図８は、本発明の実施の形態１に係るヨーク３３の平坦部３３ｂと第２ベーン２４の背面部２４ｃとの距離（背面ギャップ）に対する第２ベーン２４に作用する後方に吸引する磁力（第２力）との関係及び前方に吸引する磁力（第３力）との関係を示す図である。
図５のベーン上死点位置（背面ギャップがＸ１）では、第２力により、第２ベーン２４に対して後方への強い吸引磁力（約７Ｎ）を発生する。図６の第２力と第３力の切替え位置（背面ギャップがＸ２）では、後方への吸引磁力（第２力）と前方への吸引磁力（第３力）がともに弱くなる。図７のベーン上死点位置（背面ギャップがＸ３）では、第３力により、前方への吸引磁力が（約３Ｎ）を発生する。FIG. 8 shows the magnetic force (first force) acting on the second vane 24 with respect to the distance (back gap) between the flat portion 33b of the yoke 33 and the back surface portion 24c of the second vane 24 according to Embodiment 1 of the present invention. 2 force) and a relationship with a magnetic force (a third force) attracted forward.
At the vane top dead center position (back gap is X1) in FIG. 5, a strong attractive magnetic force (about 7 N) in the backward direction is generated with respect to the second vane 24 by the second force. In the switching position of the second force and the third force in FIG. 6 (the back gap is X2), the backward attractive magnetic force (second force) and the forward attractive magnetic force (third force) are both weakened. At the vane top dead center position in FIG. 7 (the back gap is X3), a forward attractive magnetic force (about 3N) is generated by the third force.

このため、本実施の形態１に係るロータリ式圧縮機１においては、第２圧縮部２０が低負荷条件で圧縮運転を行う際、第２ベーン２４には、最も前方に移動した下死点位置において該第２ベーン２４を前方へ吸引する第３力が作用する。したがって、本実施の形態１に係るロータリ式圧縮機１においては、第２圧縮部２０が低負荷条件で圧縮運転を行う際、下死点位置において第２ベーン２４が第２ピストン２３から離間することを防止でき、ロータリ式圧縮機１の信頼性及び効率が低下することを防止できる。  For this reason, in the rotary compressor 1 according to the first embodiment, when the second compression unit 20 performs the compression operation under the low load condition, the second vane 24 has the bottom dead center position moved most forward. Then, a third force for sucking the second vane 24 forward acts. Therefore, in the rotary compressor 1 according to the first embodiment, when the second compression unit 20 performs the compression operation under the low load condition, the second vane 24 is separated from the second piston 23 at the bottom dead center position. This can be prevented, and the reliability and efficiency of the rotary compressor 1 can be prevented from decreasing.

［ヒートポンプ装置２００の基本構成］
図９は、本発明の実施の形態１に係るヒートポンプ装置２００の基本構成を示す図である。
ヒートポンプ装置２００は、図１と同様のロータリ式圧縮機１、四方弁２０１、室内側熱交換器２０２、減圧機構２０３及び室外側熱交換器２０４を有し、これらを冷媒回路配管２０７で接続して蒸気圧縮式冷凍サイクルを構成している。以下では、ヒートポンプ装置２００の一例として空調機用のヒートポンプ装置２００について説明する。[Basic configuration of heat pump apparatus 200]
FIG. 9 is a diagram showing a basic configuration of heat pump apparatus 200 according to Embodiment 1 of the present invention.
The heat pump device 200 has the same rotary compressor 1 as shown in FIG. 1, a four-way valve 201, an indoor heat exchanger 202, a decompression mechanism 203, and an outdoor heat exchanger 204, which are connected by a refrigerant circuit pipe 207. Constitutes a vapor compression refrigeration cycle. Below, the heat pump apparatus 200 for air conditioners is demonstrated as an example of the heat pump apparatus 200. FIG.

室内機Ｂには室内側熱交換器２０２が配置され、室外機Ａにはロータリ式圧縮機１、四方弁２０１、減圧機構２０３及び室外側熱交換器２０４が配置されている。
ヒートポンプ装置２００は、四方弁２０１により暖房運転及び冷房運転を切り替え可能となっている。暖房運転する場合には、四方弁２０１を図９の実線で示す暖房運転時経路２０１ａ側に接続する。これにより、ロータリ式圧縮機１で高温高圧状態に圧縮した冷媒ガスが室内側熱交換器２０２に流入し、室内側熱交換器２０２が放熱側熱交換器（凝縮器）として動作する。冷房運転する場合には、四方弁２０１を点線で示す冷房運転時経路２０１ｂ側に接続する。これにより、ロータリ式圧縮機１の吸入側が室内側熱交換器２０２に接続されて、室内側熱交換器２０２が吸熱側熱交換器（蒸発器）として動作する。The indoor unit B is provided with an indoor heat exchanger 202, and the outdoor unit A is provided with a rotary compressor 1, a four-way valve 201, a pressure reducing mechanism 203, and an outdoor heat exchanger 204.
The heat pump device 200 can be switched between a heating operation and a cooling operation by a four-way valve 201. When heating operation is performed, the four-way valve 201 is connected to the heating operation path 201a indicated by the solid line in FIG. Thereby, the refrigerant gas compressed into the high temperature and high pressure state by the rotary compressor 1 flows into the indoor heat exchanger 202, and the indoor heat exchanger 202 operates as a heat radiation side heat exchanger (condenser). When performing the cooling operation, the four-way valve 201 is connected to the cooling operation path 201b indicated by a dotted line. Thereby, the suction side of the rotary compressor 1 is connected to the indoor heat exchanger 202, and the indoor heat exchanger 202 operates as a heat absorption side heat exchanger (evaporator).

ロータリ式圧縮機１は、上述したように電動機８及び２つの圧縮部（第１圧縮部１０及び第２圧縮部２０）を有し、一方の圧縮部を非圧縮運転状態とする単独運転モードと、両方の圧縮部を圧縮運転状態とする通常の並列運転モードとが、ロータリ式圧縮機１の運転条件により受動的に切り替わる構造を有している。具体的には、上述したようにロータリ式圧縮機１の運転開始直後や、あるいは、ロータリ式圧縮機１が低負荷（室内と室外の温度差が小さい）で吸入圧と吐出圧の差圧が小さい状態では単独運転モードで運転を行う。あるいは、起動後しばらく経過し、定格負荷まで吐出圧が上昇して吸入圧との差圧が大きくなると、第２ベーン２４に作用する押付け力Ｆｐ（第１力）が大きくなって、並列運転モードに切り替わる。  As described above, the rotary compressor 1 includes the electric motor 8 and the two compression units (the first compression unit 10 and the second compression unit 20), and the single operation mode in which one compression unit is in a non-compression operation state. The normal parallel operation mode in which both compression units are in the compression operation state is passively switched depending on the operation condition of the rotary compressor 1. Specifically, as described above, immediately after the operation of the rotary compressor 1 is started, or when the rotary compressor 1 has a low load (the temperature difference between the room and the outside is small), the differential pressure between the suction pressure and the discharge pressure is increased. In the small state, the operation is performed in the single operation mode. Alternatively, when the discharge pressure rises to the rated load and the differential pressure from the suction pressure increases after a while after startup, the pressing force Fp (first force) acting on the second vane 24 increases, and the parallel operation mode Switch to

次に、ヒートポンプ装置２００に備えられたセンサ類について説明する。室内機Ｂには、室内温度を検出する温度センサ１７１と、室内側熱交換器２０２を通過する室内気流の噴出し口に温度センサ１７２が備えてある。温度センサ１７１，１７２で検知した信号は、後述のヒートポンプ能力制御装置１６０に入力されるようになっている。  Next, sensors provided in the heat pump apparatus 200 will be described. The indoor unit B includes a temperature sensor 171 that detects the indoor temperature, and a temperature sensor 172 at the outlet of the indoor airflow that passes through the indoor heat exchanger 202. The signals detected by the temperature sensors 171 and 172 are input to the heat pump capacity control device 160 described later.

なお、ヒートポンプ装置２００の制御に用いられるセンサは、図９に示したものに限定されず、室内側熱交換器２０２及び室外側熱交換器２０４の気流側または冷媒側に設けられた温度センサ、ロータリ式圧縮機１の吸入側及び吐出側に設けられた温度センサ及び圧力センサ等を必要に応じて適宜採用することができる。  In addition, the sensor used for control of the heat pump apparatus 200 is not limited to what was shown in FIG. 9, The temperature sensor provided in the airflow side or refrigerant | coolant side of the indoor side heat exchanger 202 and the outdoor side heat exchanger 204, A temperature sensor and a pressure sensor provided on the suction side and the discharge side of the rotary compressor 1 can be appropriately employed as necessary.

次に、ヒートポンプ装置２００に備えられた制御回路について説明する。室外機Ａは、交流電源１４０からの電源によりロータリ式圧縮機１の電動機８を駆動する電力を供給するインバータ駆動制御装置１５０と、この装置から取得したインバータ波形に基づいて運転モードを判別する検知判別手段１４５と、ヒートポンプ能力制御装置１６０とを備えている。インバータ駆動制御装置１５０、検知判別手段１４５、ヒートポンプ能力制御装置１６０には、各種制御を行うプログラムを記憶した記憶部や演算を行うＣＰＵ等の回路が内蔵されている。  Next, a control circuit provided in the heat pump apparatus 200 will be described. The outdoor unit A has an inverter drive control device 150 that supplies power for driving the electric motor 8 of the rotary compressor 1 by a power source from the AC power source 140, and a detection that determines the operation mode based on the inverter waveform acquired from the device. A determination unit 145 and a heat pump capacity control device 160 are provided. The inverter drive control device 150, the detection determination unit 145, and the heat pump capacity control device 160 incorporate a circuit such as a storage unit that stores programs for performing various controls and a CPU that performs calculations.

運転モードが、並列運転モードから単独運転モードに切り替わった瞬間は、電動機８の回転周波数が急激に増加（オーバシュート）するが、検知判別手段１４５により運転モードを検知判別すると、温度センサ１７２で検知した温度が、目標室温に近づくように電動機８の運転周波数を再度決定し、決定した運転周波数で電動機８が動作するようにインバータ駆動制御装置１５０を制御する。温度センサ１７２で検知した温度が、目標の室温（乾球）の変動幅が許容範囲（±１℃程度）に入るように調整する。  At the moment when the operation mode is switched from the parallel operation mode to the single operation mode, the rotational frequency of the electric motor 8 rapidly increases (overshoot). However, if the operation determination mode is detected by the detection determination unit 145, the temperature sensor 172 detects the operation mode. The operating frequency of the electric motor 8 is determined again so that the obtained temperature approaches the target room temperature, and the inverter drive control device 150 is controlled so that the electric motor 8 operates at the determined operating frequency. The temperature detected by the temperature sensor 172 is adjusted so that the fluctuation range of the target room temperature (dry bulb) falls within an allowable range (about ± 1 ° C.).

以上のように、本実施の形態１に係るロータリ式圧縮機１は、第２圧縮部２０に切替え機構３１を備えたことにより、第１圧縮部１０と第２圧縮部２０とを同時に圧縮運転する並列運転モードと、第１圧縮部１０が圧縮運転を行い、第２圧縮部２０が非圧縮運転となる単独運転モードとを行うことができる。また、本実施の形態１に係るロータリ式圧縮機１においては、第２圧縮部２０が低負荷条件で圧縮運転を行う際、下死点位置において第２ベーン２４が第２ピストン２３から離間することを防止でき、ロータリ式圧縮機１の信頼性及び効率が低下することを防止できる。すなわち、本実施の形態１に係るロータリ式圧縮機１は、低負荷時に複数のシリンダ室の運転モードを切替えて能力範囲を拡大した運転制御が、低負荷時にも安定に動作可能となる。したがって、ロータリ式圧縮機１の効率化と信頼性の向上を実現することができる。そして、このようなロータリ式圧縮機１を備えたヒートポンプ装置２００においても、効率化と信頼性の向上を実現することができる。  As described above, the rotary compressor 1 according to the first embodiment includes the switching mechanism 31 in the second compression unit 20 so that the first compression unit 10 and the second compression unit 20 are simultaneously compressed. The parallel operation mode to be performed and the single operation mode in which the first compression unit 10 performs the compression operation and the second compression unit 20 performs the non-compression operation can be performed. In the rotary compressor 1 according to the first embodiment, the second vane 24 is separated from the second piston 23 at the bottom dead center position when the second compression unit 20 performs the compression operation under the low load condition. This can be prevented, and the reliability and efficiency of the rotary compressor 1 can be prevented from decreasing. That is, the rotary compressor 1 according to the first embodiment can stably operate even when the load is low, with the operation control in which the operation range of the plurality of cylinder chambers is switched and the capacity range is expanded when the load is low. Therefore, it is possible to realize an increase in efficiency and reliability of the rotary compressor 1. And also in the heat pump apparatus 200 provided with such a rotary compressor 1, efficiency improvement and improvement in reliability can be realized.

また、本実施の形態１に係るロータリ式圧縮機１は、第２圧縮部２０に、第２ベーン２４が第２ピストン２３から離れた状態になったときに、第２ベーン２４を保持する凹型形状のヨーク３３を備えている。このため、本実施の形態１に係るロータリ式圧縮機１は、第２ベーン２４が第２ピストン２３の外周壁から離間した際に、第２ベーン２４の位置を安定に保つこともできる。  Further, the rotary compressor 1 according to the first embodiment has a concave type that holds the second vane 24 in the second compression unit 20 when the second vane 24 is separated from the second piston 23. A yoke 33 having a shape is provided. For this reason, the rotary compressor 1 according to the first embodiment can also keep the position of the second vane 24 stable when the second vane 24 is separated from the outer peripheral wall of the second piston 23.

なお、上記では、休筒状態（非圧縮運転状態）となる第２圧縮部２０を第１圧縮部１０の下方に配置した例を説明したが、休筒状態（非圧縮運転状態）となる第２圧縮部２０を第１圧縮部１０の上方に配置してもよい。  In addition, although the example which has arrange | positioned the 2nd compression part 20 which will be in a cylinder resting state (non-compression operation state) below the 1st compression part 10 was demonstrated above, it becomes the cylinder resting state (non-compression operation state). The two compression units 20 may be disposed above the first compression unit 10.

また、本実施の形態１では、密閉形高圧シェル形式（第１圧縮部１０及び第２圧縮部２０と電動機８とを同じ吐出圧の密閉シェル内に配置したもの）のロータリ式圧縮機を用いたヒートポンプ装置について説明したが、その他のシェル形式においても同様の構成を採用することができる。例えば、半密閉式のシェル形式の場合や、中間圧シェル形式及び低圧シェル形式の場合にも、ベーンを差圧によりピストンに押し付けて圧縮運転を行う形式の場合には、同様の効果を奏することができる。  Further, in the first embodiment, a rotary compressor of a hermetic type high-pressure shell type (in which the first compression unit 10, the second compression unit 20, and the electric motor 8 are arranged in a hermetic shell having the same discharge pressure) is used. Although the heat pump device has been described, the same configuration can be adopted in other shell types. For example, in the case of a semi-enclosed shell type, an intermediate pressure shell type, and a low pressure shell type, the same effect is obtained in the case of a type in which a vane is pressed against a piston by a differential pressure to perform a compression operation. Can do.

実施の形態２．
実施の形態２に係るロータリ式圧縮機１は、実施の形態１に係るロータリ式圧縮機１、圧縮機構９９及び第２圧縮部２０の基本構成及び基本動作と全く同様であるが、実施の形態１に係る圧縮機構９９のうちで、第２ベーン２４の前方への吸引磁力発生部の構成と動作について異なる点がある。
したがって、本実施の形態２では、実施の形態１に係るロータリ式圧縮機１と異なる部分についてのみ説明する。なお、本実施の形態２において、実施の形態１と同一の機能や構成については同一の符号を用いて述べることとする。Embodiment 2. FIG.
The rotary compressor 1 according to the second embodiment is the same as the basic configuration and basic operation of the rotary compressor 1, the compression mechanism 99, and the second compression unit 20 according to the first embodiment. In the compression mechanism 99 according to No. 1, there is a difference in the configuration and operation of the attractive magnetic force generation unit forward of the second vane 24.
Therefore, in this Embodiment 2, only a different part from the rotary compressor 1 which concerns on Embodiment 1 is demonstrated. In the second embodiment, the same functions and configurations as those of the first embodiment are described using the same reference numerals.

図１０は、本発明の実施の形態２に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角０度の上死点位置）を示す縦断面図である。
図１１は、本発明の実施の形態２に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角０度の上死点位置）を示す横断面図である。
図１２は、本発明の実施の形態２に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（第２力と第３力の切替え位置）を示す縦断面図である。
図１３は、本発明の実施の形態２に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（第２力と第３力の切替え位置）を示す横断面図である。
図１４は、本発明の実施の形態２に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角１８０度の下死点位置）を示す縦断面図である。
図１５は、本発明の実施の形態２に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角１８０度の下死点位置）を示す横断面図である。
なお、図１１、図１３及び図１５に示す台形の破線は、第２ヨーク４３の取付位置を示している。FIG. 10 is a longitudinal cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to Embodiment 2 of the present invention is in the compression operation state (top dead center position of the shaft rotation angle 0 degree).
FIG. 11 is a cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to the second embodiment of the present invention is in the compression operation state (top dead center position of the shaft rotation angle 0 degree).
FIG. 12 is a longitudinal sectional view showing the state of the second vane 24 when the second compression unit 20 according to Embodiment 2 of the present invention is in the compression operation state (switching position between the second force and the third force).
FIG. 13 is a cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to the second embodiment of the present invention is in the compression operation state (switching position between the second force and the third force).
FIG. 14 is a vertical cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to Embodiment 2 of the present invention is in the compression operation state (bottom dead center position of the shaft rotation angle of 180 degrees).
FIG. 15 is a cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to Embodiment 2 of the present invention is in the compression operation state (bottom dead center position of the shaft rotation angle 180 degrees).
In addition, the trapezoidal broken line shown in FIGS. 11, 13, and 15 indicates the mounting position of the second yoke 43.

［第２ベーン２４の前方への吸引磁力発生部の基本構成と動作］
本実施の形態２に係る第２ベーン２４は、底面部に凹形の切欠き部４５（非吸引部）が形成されている。そして、ベーン吸引箇所４１である透磁率の高い例えば円筒形状の金属材料（磁性材料）は、第２ベーン２４の背面部２４ｃ、より詳しくは切欠き部４５の後端部に設けられている。この位置は、ベーン吸引箇所４１と周囲の部材とが摺動しない位置である。[Basic configuration and operation of the attractive magnetic force generating portion forward of the second vane 24]
The second vane 24 according to the second embodiment has a concave notch 45 (non-suction portion) formed on the bottom surface. Further, for example, a cylindrical metal material (magnetic material) having a high magnetic permeability, which is the vane attracting portion 41, is provided at the back surface portion 24 c of the second vane 24, more specifically at the rear end portion of the notch portion 45. This position is a position where the vane suction point 41 and the surrounding members do not slide.

図１０及び図１１の軸回転角０度の上死点位置では、第２ベーン２４の背面部２４ｃの位置が、ボルト４４よりもヨーク３３の両腕部３３ａに接近する。このため、永久磁石３２からヨーク３３を通って、第２ベーン２４の背面部２４ｃに向かって磁束が流れ、第２シリンダ２１内を通過して、永久磁石３２に磁束が戻る（第２力）。  10 and 11, the position of the back surface portion 24 c of the second vane 24 is closer to the both arm portions 33 a of the yoke 33 than the bolt 44. Therefore, the magnetic flux flows from the permanent magnet 32 through the yoke 33 toward the back surface portion 24c of the second vane 24, passes through the second cylinder 21, and returns to the permanent magnet 32 (second force). .

図１２及び図１３の第２力と第３力の切替え位置では、第２ベーン２４の背面部２４ｃからボルト４４までの距離と、第２ベーン２４の背面部２４ｃからヨーク３３の両腕部３３ａまでの距離とが、ほぼ同等になる。このため、永久磁石３２からヨーク３３を通って、ベーンの背面部２４ｃに向かう磁束と、ボルト４４に向かう磁束とに分かれる。ボルト４４を通る磁束は、第２ヨーク４３を通って、再び第２ベーン２４に接近しようとするが、第２ベーン２４の底面部の切欠き部４５のため、大きな吸引磁力を発揮できない。  12 and 13, the distance from the back surface portion 24 c of the second vane 24 to the bolt 44 and the both arm portions 33 a of the yoke 33 from the back surface portion 24 c of the second vane 24. The distance to is almost the same. For this reason, the magnetic flux is divided into a magnetic flux directed from the permanent magnet 32 through the yoke 33 toward the vane back surface portion 24 c and a magnetic flux directed toward the bolt 44. The magnetic flux passing through the bolt 44 tries to approach the second vane 24 again through the second yoke 43, but cannot exert a large attractive magnetic force because of the notch 45 in the bottom surface of the second vane 24.

図１４及び図１５の軸回転角１８０度の下死点位置では、第２ベーン２４の背面部２４ｃの位置がボルト４４よりもヨーク３３の両腕部３３ａから遠ざかる。一方で、第２ヨーク４３の先端部４３ａが、切欠き部４５でなくベーン吸引箇所４１に接近するので、ボルト４４を通る磁束が流れやすくなり、第２ベーン２４を前方に吸引する磁力（第３力）が発生する。  14 and 15, the position of the back surface portion 24 c of the second vane 24 is farther from both the arm portions 33 a of the yoke 33 than the bolt 44. On the other hand, the tip 43a of the second yoke 43 approaches the vane suction point 41 instead of the notch 45, so that the magnetic flux passing through the bolts 44 flows easily, and the magnetic force (first force) attracts the second vane 24 forward. 3 forces) are generated.

以上のように、本実施の形態２に係るロータリ式圧縮機１においても、実施の形態１と同様、第２圧縮部２０に切替え機構３１を備えたことにより、第１圧縮部１０と第２圧縮部２０とを同時に圧縮運転する並列運転モードと、第１圧縮部１０が圧縮運転を行い、第２圧縮部２０が非圧縮運転となる単独運転モードとを行うことができる。また、本実施の形態２に係るロータリ式圧縮機１においても、実施の形態１と同様、第２圧縮部２０が低負荷条件で圧縮運転を行う際、下死点位置において第２ベーン２４が第２ピストン２３から離間することを防止でき、ロータリ式圧縮機１の信頼性及び効率が低下することを防止できる。すなわち、本実施の形態２に係るロータリ式圧縮機１においても、実施の形態１と同様、低負荷時に複数のシリンダ室の運転モードを切替えて能力範囲を拡大した運転制御が、低負荷時にも安定に動作可能となる。したがって、ロータリ式圧縮機１の効率化と信頼性の向上を実現することができる。そして、このようなロータリ式圧縮機１を備えたヒートポンプ装置２００においても、効率化と信頼性の向上を実現することができる。  As described above, also in the rotary compressor 1 according to the second embodiment, the switching mechanism 31 is provided in the second compression unit 20 as in the first embodiment. A parallel operation mode in which the compression unit 20 is simultaneously compressed and a single operation mode in which the first compression unit 10 performs a compression operation and the second compression unit 20 performs a non-compression operation can be performed. Also in the rotary compressor 1 according to the second embodiment, as in the first embodiment, when the second compression unit 20 performs the compression operation under the low load condition, the second vane 24 is located at the bottom dead center position. It can prevent separating from the 2nd piston 23, and can prevent that the reliability and efficiency of the rotary compressor 1 fall. That is, also in the rotary compressor 1 according to the second embodiment, as in the first embodiment, the operation control in which the operation range of the plurality of cylinder chambers is expanded by changing the operation mode at the time of low load is also achieved at the time of low load. Stable operation is possible. Therefore, it is possible to realize an increase in efficiency and reliability of the rotary compressor 1. And also in the heat pump apparatus 200 provided with such a rotary compressor 1, efficiency improvement and improvement in reliability can be realized.

実施の形態３．
実施の形態３に係るロータリ式圧縮機１は、実施の形態１に係るロータリ式圧縮機１、圧縮機構９９及び第２圧縮部２０の基本構成及び基本動作と全く同様であるが、実施の形態１に係る圧縮機構９９のうちで、第２ベーン２４の前方への吸引磁力発生部の構成と動作について異なる点がある。
したがって、本実施の形態３では、実施の形態１に係るロータリ式圧縮機１と異なる部分についてのみ説明する。なお、本実施の形態３において、実施の形態１と同一の機能や構成については同一の符号を用いて述べることとする。Embodiment 3 FIG.
The rotary compressor 1 according to the third embodiment is the same as the basic configuration and basic operation of the rotary compressor 1, the compression mechanism 99, and the second compression unit 20 according to the first embodiment. In the compression mechanism 99 according to No. 1, there is a difference in the configuration and operation of the attractive magnetic force generation unit forward of the second vane 24.
Therefore, in this Embodiment 3, only a different part from the rotary compressor 1 which concerns on Embodiment 1 is demonstrated. In the third embodiment, the same functions and configurations as those in the first embodiment are described using the same reference numerals.

図１６は、本発明の実施の形態３に係るロータリ式圧縮機１の構造を示す概略縦断面図である。
図１７は、本発明の実施の形態３に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角０度の上死点位置）を示す縦断面図である。
図１８は、本発明の実施の形態３に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角０度の上死点位置）を示す横断面図である。
図１９は、本発明の実施の形態３に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（第２力と第３力の切替え位置）を示す縦断面図である。
図２０は、本発明の実施の形態３に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（第２力と第３力の切替え位置）を示す横断面図である。
図２１は、本発明の実施の形態３に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角１８０度の下死点位置）を示す縦断面図である。
図２２は、本発明の実施の形態３に係る第２圧縮部２０が圧縮運転状態時の第２ベーン２４の状態（軸回転角１８０度の下死点位置）を示す横断面図である。FIG. 16 is a schematic longitudinal sectional view showing the structure of the rotary compressor 1 according to Embodiment 3 of the present invention.
FIG. 17 is a longitudinal cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to Embodiment 3 of the present invention is in the compression operation state (top dead center position at an axial rotation angle of 0 degrees).
FIG. 18 is a cross-sectional view showing the state of the second vane 24 when the second compression unit 20 according to the third embodiment of the present invention is in the compression operation state (top dead center position at an axial rotation angle of 0 degrees).
FIG. 19 is a longitudinal sectional view showing a state of the second vane 24 (a switching position between the second force and the third force) when the second compression unit 20 according to Embodiment 3 of the present invention is in the compression operation state.
FIG. 20 is a cross-sectional view illustrating the state of the second vane 24 (the switching position between the second force and the third force) when the second compression unit 20 according to Embodiment 3 of the present invention is in the compression operation state.
FIG. 21 is a longitudinal sectional view showing the state of the second vane 24 when the second compression unit 20 according to the third embodiment of the present invention is in the compression operation state (bottom dead center position of the shaft rotation angle of 180 degrees).
FIG. 22 is a cross-sectional view showing the state of the second vane 24 (the bottom dead center position of the shaft rotation angle 180 degrees) when the second compression unit 20 according to Embodiment 3 of the present invention is in the compression operation state.

［第２ベーン２４の前方への吸引磁力発生部の基本構成と動作］
本実施の形態３に係る第２ベーン２４は、第２ベーン２４の背面部２４ｃに、透磁率の高い金属材料（磁性材料）のベーン吸引箇所４１が設けられている。また、第２ベーン２４は、第２ベーン２４の底面部から下方へ向かって突設された突状ベーン吸引箇所４１ａを備えている。この突状ベーン吸引箇所４１ａは、後述のように第３力が働くベーン吸引箇所である。突状ベーン吸引箇所４１ａは、駆動軸５の軸方向において第２シリンダ室２２とは異なる位置（より詳しくは、第２シリンダ室２２よりも第２支持部材７０のフランジ部７０ｂ側であり、下死点位置において該フランジ部７０ｂよりも外側となる位置）に配置されている。換言すると、突状ベーン吸引箇所４１ａは、駆動軸５の軸方向において第２シリンダ２１とは異なる位置に配置されている。また、突状ベーン吸引箇所４１ａの当該位置は、突状ベーン吸引箇所４１ａと周囲の部材とが摺動しない位置である。[Basic configuration and operation of the attractive magnetic force generating portion forward of the second vane 24]
In the second vane 24 according to the third embodiment, a vane suction point 41 of a metal material (magnetic material) having a high magnetic permeability is provided on the back surface portion 24 c of the second vane 24. Further, the second vane 24 includes a protruding vane suction portion 41 a that protrudes downward from the bottom surface of the second vane 24. The protruding vane suction portion 41a is a vane suction portion where a third force acts as will be described later. The projecting vane suction portion 41a is located at a position different from the second cylinder chamber 22 in the axial direction of the drive shaft 5 (more specifically, on the flange portion 70b side of the second support member 70 relative to the second cylinder chamber 22, It is arranged at a position on the outside of the flange portion 70b) at the dead center position. In other words, the protruding vane suction portion 41 a is arranged at a position different from the second cylinder 21 in the axial direction of the drive shaft 5. Moreover, the said position of the protruding vane suction location 41a is a position where the protruding vane suction location 41a and a surrounding member do not slide.

また、本実施の形態３に係るロータリ式圧縮機１には、永久磁石３２とは別に、第２ベーン２４に対して第３力を発生させる第２永久磁石４２が設けられている。この第２永久磁石４２は、第２ベーン２４が最も前方に移動している軸回転角１８０度の下死点位置において、ベーン吸引箇所４１と対向する位置に設けられている。つまり、第２永久磁石４２は、第２ベーン２４が最も前方に移動する下死点位置において、第２ベーン２４の背面部２４ｃよりも前方となる位置に配置されている。また、第２永久磁石４２は、駆動軸５の軸方向において第２シリンダ室２２とは異なる位置（高さ）、より詳しくは第２支持部材７０のフランジ部７０ｂ側に配置されている。換言すると、第２永久磁石４２は、駆動軸５の軸方向において第２シリンダ２１とは異なる位置（高さ）に配置されている。さらに、本実施の形態３では、第２永久磁石４２は、フランジ部７０ｂよりも外側に配置されている。また、本実施の形態３では、第２永久磁石４２は、永久磁石３２と反発しあう向きに磁界を発生させる。  In addition, the rotary compressor 1 according to the third embodiment is provided with a second permanent magnet 42 that generates a third force with respect to the second vane 24, in addition to the permanent magnet 32. The second permanent magnet 42 is provided at a position facing the vane suction point 41 at the bottom dead center position of the shaft rotation angle of 180 degrees where the second vane 24 is moving most forward. That is, the second permanent magnet 42 is disposed at a position that is more forward than the back surface portion 24c of the second vane 24 at the bottom dead center position where the second vane 24 moves most forward. Further, the second permanent magnet 42 is disposed at a position (height) different from the second cylinder chamber 22 in the axial direction of the drive shaft 5, more specifically, on the flange portion 70 b side of the second support member 70. In other words, the second permanent magnet 42 is arranged at a position (height) different from the second cylinder 21 in the axial direction of the drive shaft 5. Furthermore, in the third embodiment, the second permanent magnet 42 is disposed outside the flange portion 70b. In the third embodiment, the second permanent magnet 42 generates a magnetic field in a direction repelling the permanent magnet 32.

このような第２永久磁石４２は、第２支持部材７０のフランジ部７０ｂに固定されている。本実施の形態３では、第２ベーン２４に磁束を集中的に通過させるため、第２永久磁石４２の周囲を非磁性材料である第２保持具４６で覆っている。このため、第２永久磁石４２は、第２保持具４６を介して、第２支持部材７０のフランジ部７０ｂに固定されている。また、本実施の形態３では、第２ベーン２４に磁束密度を集中させるため、第２永久磁石４２の後面部（突状ベーン吸引箇所４１ａと対向する箇所）、上面部及び底面部を除く位置が、第２ヨーク４３（磁性材料）で覆われている。  Such a second permanent magnet 42 is fixed to the flange portion 70 b of the second support member 70. In the third embodiment, the second permanent magnet 42 is covered with a second holder 46 made of a nonmagnetic material in order to allow the magnetic flux to pass through the second vane 24 in a concentrated manner. For this reason, the second permanent magnet 42 is fixed to the flange portion 70 b of the second support member 70 via the second holder 46. In the third embodiment, in order to concentrate the magnetic flux density on the second vane 24, the position of the second permanent magnet 42 excluding the rear surface portion (location facing the protruding vane suction location 41a), the top surface portion, and the bottom surface portion. Is covered with the second yoke 43 (magnetic material).

図１７及び図１８の軸回転角０度の上死点位置では、第２ベーン２４の背面部２４ｃとヨーク３３の両腕部３３ａとの間の距離が、第２ベーン２４の突状ベーン吸引箇所４１ａと第２永久磁石４２（第２ヨーク４３が設けられている場合には第２ヨーク４３）との間の距離よりも小さい。このため、永久磁石３２からヨーク３３を通って、ベーンの背面部２４ｃに向かって磁束が流れ、第２シリンダ２１内を通過して、永久磁石３２に磁束が戻る。つまり、第２ベーン２４には、該第２ベーン２４を後方へ吸引する第２力が働く。  17 and 18, the distance between the back surface portion 24c of the second vane 24 and both arm portions 33a of the yoke 33 is equal to the protruding vane suction of the second vane 24 at the top dead center position. The distance is smaller than the distance between the portion 41a and the second permanent magnet 42 (the second yoke 43 when the second yoke 43 is provided). For this reason, the magnetic flux flows from the permanent magnet 32 through the yoke 33 toward the back surface portion 24 c of the vane, passes through the second cylinder 21, and returns to the permanent magnet 32. That is, a second force that sucks the second vane 24 backward acts on the second vane 24.

図１９及び図２０の第２力と第３力の切替え位置では、第２ベーン２４の背面部２４ｃとヨーク３３の両腕部３３ａとの間の距離と、第２ベーン２４の突状ベーン吸引箇所４１ａと第２永久磁石４２（第２ヨーク４３が設けられている場合には第２ヨーク４３）との間の距離とが、ほぼ同等になる。このため、永久磁石３２からヨーク３３を通って、ベーンの背面部２４ｃに向かって磁束が流れ、第２シリンダ２１内を通過して、永久磁石３２に磁束が戻る（第２力）。これと同時に、第２永久磁石４２から第２ヨーク４３を通って、第２ベーン２４の突状ベーン吸引箇所４１ａに向かう磁束が発生して、第２ベーン２４を前方に吸引する磁力（第３力）も発生する。このため、図１９及び図２０の第２力と第３力の切替え位置では、第２ベーン２４を後方へ吸引する第２力と第２ベーン２４を前方へ吸引する第３力とが互いに打ち消し合う状態となる。  19 and 20, the distance between the back surface portion 24c of the second vane 24 and the arms 33a of the yoke 33, and the projecting vane suction of the second vane 24 at the position where the second force and the third force are switched. The distance between the portion 41a and the second permanent magnet 42 (the second yoke 43 when the second yoke 43 is provided) is substantially the same. For this reason, the magnetic flux flows from the permanent magnet 32 through the yoke 33 toward the back surface portion 24c of the vane, passes through the second cylinder 21, and returns to the permanent magnet 32 (second force). At the same time, a magnetic flux is generated from the second permanent magnet 42 through the second yoke 43 toward the protruding vane suction portion 41a of the second vane 24, and attracts the second vane 24 forward (third Force) is also generated. For this reason, in the switching position of the second force and the third force in FIGS. 19 and 20, the second force that sucks the second vane 24 backward and the third force that sucks the second vane 24 forward cancel each other. It will be in a fit state

図２１及び図２２の軸回転角１８０度の下死点位置では、第２ベーン２４の背面部２４ｃの位置がヨーク３３の両腕部３３ａから遠ざかる。一方で、第２ベーン２４の突状ベーン吸引箇所４１ａが、第２永久磁石４２（第２ヨーク４３が設けられている場合には第２ヨーク４３）に近づく。このため、第２永久磁石４２から第２ヨーク４３を通って、第２ベーン２４の突状ベーン吸引箇所４１ａに向かう磁束が発生して、第２ベーン２４を前方に吸引する磁力（第３力）が発生する。  21 and 22, the position of the back surface portion 24 c of the second vane 24 moves away from both arm portions 33 a of the yoke 33 at the bottom dead center position of the shaft rotation angle of 180 degrees. On the other hand, the protruding vane attracting portion 41a of the second vane 24 approaches the second permanent magnet 42 (the second yoke 43 when the second yoke 43 is provided). Therefore, a magnetic flux (third force) attracts the second vane 24 forward by generating a magnetic flux from the second permanent magnet 42 through the second yoke 43 toward the projecting vane suction portion 41a of the second vane 24. ) Occurs.

以上のように、本実施の形態３に係るロータリ式圧縮機１においても、実施の形態１と同様、第２圧縮部２０に切替え機構３１を備えたことにより、第１圧縮部１０と第２圧縮部２０とを同時に圧縮運転する並列運転モードと、第１圧縮部１０が圧縮運転を行い、第２圧縮部２０が非圧縮運転となる単独運転モードとを行うことができる。また、本実施の形態３に係るロータリ式圧縮機１においても、実施の形態１と同様、第２圧縮部２０が低負荷条件で圧縮運転を行う際、下死点位置において第２ベーン２４が第２ピストン２３から離間することを防止でき、ロータリ式圧縮機１の信頼性及び効率が低下することを防止できる。すなわち、本実施の形態３に係るロータリ式圧縮機１においても、実施の形態１と同様、低負荷時に複数のシリンダ室の運転モードを切替えて能力範囲を拡大した運転制御が、低負荷時にも安定に動作可能となる。したがって、ロータリ式圧縮機１の効率化と信頼性の向上を実現することができる。そして、このようなロータリ式圧縮機１を備えたヒートポンプ装置２００においても、効率化と信頼性の向上を実現することができる。  As described above, also in the rotary compressor 1 according to the third embodiment, since the second compression unit 20 includes the switching mechanism 31 as in the first embodiment, the first compression unit 10 and the second compression unit 10 are provided. A parallel operation mode in which the compression unit 20 is simultaneously compressed and a single operation mode in which the first compression unit 10 performs a compression operation and the second compression unit 20 performs a non-compression operation can be performed. In the rotary compressor 1 according to the third embodiment, as in the first embodiment, when the second compressor 20 performs the compression operation under a low load condition, the second vane 24 is located at the bottom dead center position. It can prevent separating from the 2nd piston 23, and can prevent that the reliability and efficiency of the rotary compressor 1 fall. That is, also in the rotary compressor 1 according to the third embodiment, similarly to the first embodiment, the operation control in which the operation range of the plurality of cylinder chambers is expanded by changing the operation mode at the time of low load is also achieved at the time of low load. Stable operation is possible. Therefore, it is possible to realize an increase in efficiency and reliability of the rotary compressor 1. And also in the heat pump apparatus 200 provided with such a rotary compressor 1, efficiency improvement and improvement in reliability can be realized.

１ ロータリ式圧縮機、２ 圧縮機吐出管、３ 密閉シェル、３ａ 潤滑油貯蔵部、４
中間仕切板、５ 駆動軸、５ａ 長軸部、５ｂ 短軸部、５ｃ 偏心ピン軸部、５ｄ 偏心ピン軸部、５ｅ 中間軸部、６ 吸入マフラ、６ａ 流入管、６ｂ 容器、６ｃ 流出管、６ｄ 流出管、７ 内部空間、８ 電動機、８ａ 回転子、８ｂ 固定子、１０ 第１圧縮部、１１ 第１シリンダ、１２ 第１シリンダ室、１３ 第１ピストン、１４ 第１ベーン、１４ａ 先端部、１４ｂ 後端部、１４ｃ 背面部、１５ 第１ベーン背室、１７ シリンダ吸入流路、１８ 吐出口、１８ａ 開閉弁、１９ 第１ベーン溝、２０
第２圧縮部、２１ 第２シリンダ、２２ 第２シリンダ室、２３ 第２ピストン、２４
第２ベーン、２４ａ 先端部、２４ｂ 後端部、２４ｃ 背面部、２５ 第２ベーン背室、２７ シリンダ吸入流路、２８ 吐出口、２８ａ 開閉弁、２９ 第２ベーン溝、３１ 切替え機構、３２ 永久磁石、３３ ヨーク、３３ａ 両腕部、３３ｂ 平坦部、３６ 保持具、３７ 収納室、３８ シム、４０ 圧縮バネ、４１ ベーン吸引箇所（磁性材料）、４１ａ 突状ベーン吸引箇所（磁性材料）、４２ 第２永久磁石、４３ 第２ヨーク（磁性材料）、４３ａ 先端部、４４ ボルト（磁性材料）、４５ 切欠き部（非吸引部）、４６ 第２保持具、６０ 第１支持部材、６０ａ 軸受部、６０ｂ フランジ部、６３ 吐出マフラ、７０ 第２支持部材、７０ａ 軸受部、７０ｂ フランジ部、７３
吐出マフラ、９９ 圧縮機構、１４０ 交流電源、１４５ 検知判別手段、１５０ インバータ駆動制御装置、１６０ ヒートポンプ能力制御装置、１７１ 温度センサ、１７２ 温度センサ、２００ ヒートポンプ装置、２０１ 四方弁、２０１ａ 暖房運転時経路、２０１ｂ 冷房運転時経路、２０２ 室内側熱交換器、２０３ 減圧機構、２０４ 室外側熱交換器、２０７ 冷媒回路配管、Ａ 室外機、Ｂ 室内機。DESCRIPTION OF SYMBOLS 1 Rotary type compressor, 2 Compressor discharge pipe, 3 Sealing shell, 3a Lubricating oil storage part, 4
Intermediate partition plate, 5 drive shaft, 5a long shaft portion, 5b short shaft portion, 5c eccentric pin shaft portion, 5d eccentric pin shaft portion, 5e intermediate shaft portion, 6 suction muffler, 6a inflow pipe, 6b container, 6c outflow pipe, 6d Outflow pipe, 7 Internal space, 8 Electric motor, 8a Rotor, 8b Stator, 10 1st compression part, 11 1st cylinder, 12 1st cylinder chamber, 13 1st piston, 14 1st vane, 14a Tip part, 14b Rear end portion, 14c Back surface portion, 15 First vane back chamber, 17 Cylinder suction flow path, 18 Discharge port, 18a Open / close valve, 19 First vane groove, 20
2nd compression part, 21 2nd cylinder, 22 2nd cylinder chamber, 23 2nd piston, 24
2nd vane, 24a tip part, 24b rear end part, 24c back part, 25 2nd vane back chamber, 27 cylinder suction flow path, 28 discharge port, 28a on-off valve, 29 2nd vane groove, 31 switching mechanism, 32 permanent Magnet, 33 Yoke, 33a Both arms, 33b Flat part, 36 Holder, 37 Storage chamber, 38 Shim, 40 Compression spring, 41 Vane suction location (magnetic material), 41a Projecting vane suction location (magnetic material), 42 Second permanent magnet, 43 Second yoke (magnetic material), 43a Tip, 44 bolt (magnetic material), 45 Notched portion (non-attracting portion), 46 Second holder, 60 First support member, 60a Bearing portion , 60b flange part, 63 discharge muffler, 70 second support member, 70a bearing part, 70b flange part, 73
Discharge muffler, 99 compression mechanism, 140 AC power supply, 145 detection discriminating means, 150 inverter drive control device, 160 heat pump capacity control device, 171 temperature sensor, 172 temperature sensor, 200 heat pump device, 201 four-way valve, 201a heating operation path, 201b Cooling operation path, 202 indoor heat exchanger, 203 pressure reducing mechanism, 204 outdoor heat exchanger, 207 refrigerant circuit piping, A outdoor unit, B indoor unit.

Claims (10)

２つの圧縮部、電動機、及び、２つの前記圧縮部と前記電動機とを接続する駆動軸を備え、
前記圧縮部のそれぞれが、
吸入した冷媒を圧縮するシリンダ室、一方の端部が前記シリンダ室に連通したベーン溝、及び、前記ベーン溝の他方の端部に連通したベーン背室が形成されたシリンダと、
前記駆動軸の回転によって前記シリンダ室内を偏心回転するリング形状のピストンと、
前記シリンダ室の中心に向かう方向である前方と前記シリンダ室から遠ざかる方向である後方とに往復動自在に前記ベーン溝に挿入され、前記ピストンの外周面に先端部が当接した状態で前記シリンダ室を低圧と高圧に仕切り、背面部が前記ベーン背室に収容されたベーンと、
を備えたロータリ式圧縮機であって、
一方の前記圧縮部は、
前記ベーンの前記背面部の後方に配置された第１永久磁石を有し、前記ベーンの前記先端部と前記背面部とに働く圧力の差により、前記ベーンに対して前方に作用する第１力と、前記第１永久磁石により前記ベーンを後方に吸引する第２力とによって、前記ベーンの前記先端部が前記ピストンの外周面に当接した圧縮運転状態と、前記ピストンの外周面から離間した前記ベーンを吸着固定した非圧縮運転状態とを切替える切替え機構を備え、
さらに、前記ベーンが最も前方に移動する下死点位置において、前記ベーンを前方へ吸引する第３力が作用するように、前記ベーンの前記背面部よりも前方側に配置されたヨークを備え、
前記ヨークは、前記駆動軸の軸方向において前記シリンダ室とは異なる位置に固定されているロータリ式圧縮機。 Two compression units, an electric motor, and a drive shaft that connects the two compression units and the electric motor,
Each of the compression sections
A cylinder chamber in which a refrigerant that has been sucked in is compressed, a vane groove with one end communicating with the cylinder chamber, and a cylinder formed with a vane back chamber communicating with the other end of the vane groove;
A ring-shaped piston that rotates eccentrically in the cylinder chamber by rotation of the drive shaft;
The cylinder is inserted into the vane groove so as to be reciprocally movable in a forward direction that is a direction toward the center of the cylinder chamber and a rearward direction that is a direction away from the cylinder chamber, and the tip is in contact with the outer peripheral surface of the piston. Dividing the chamber into a low pressure and a high pressure, and a vane whose back portion is accommodated in the vane back chamber;
A rotary compressor with
One of the compression units is
A first force that has a first permanent magnet disposed behind the back surface portion of the vane and acts forward on the vane due to a difference in pressure acting on the tip portion and the back surface portion of the vane. And a second driving force that attracts the vane backward by the first permanent magnet, and the compression operation state in which the tip end portion of the vane is in contact with the outer peripheral surface of the piston is separated from the outer peripheral surface of the piston. A switching mechanism for switching between the non-compression operation state in which the vane is adsorbed and fixed,
Further, the bottom dead center position in which the vane is moved most forward, as a third force for attracting said vane forward acts, the yaw click disposed in front side of the rear portion of the vane Prepared,
The yoke is a rotary compressor in which the yoke is fixed at a position different from the cylinder chamber in the axial direction of the drive shaft. ２つの圧縮部、電動機、及び、２つの前記圧縮部と前記電動機とを接続する駆動軸を備え、Two compression units, an electric motor, and a drive shaft that connects the two compression units and the electric motor,
前記圧縮部のそれぞれが、Each of the compression sections
吸入した冷媒を圧縮するシリンダ室、一方の端部が前記シリンダ室に連通したベーン溝、及び、前記ベーン溝の他方の端部に連通したベーン背室が形成されたシリンダと、A cylinder chamber in which a refrigerant that has been sucked in is compressed, a vane groove with one end communicating with the cylinder chamber, and a cylinder formed with a vane back chamber communicating with the other end of the vane groove;
前記駆動軸の回転によって前記シリンダ室内を偏心回転するリング形状のピストンと、A ring-shaped piston that rotates eccentrically in the cylinder chamber by rotation of the drive shaft;
前記シリンダ室の中心に向かう方向である前方と前記シリンダ室から遠ざかる方向である後方とに往復動自在に前記ベーン溝に挿入され、前記ピストンの外周面に先端部が当接した状態で前記シリンダ室を低圧と高圧に仕切り、背面部が前記ベーン背室に収容されたベーンと、The cylinder is inserted into the vane groove so as to be reciprocally movable in a forward direction that is a direction toward the center of the cylinder chamber and a rearward direction that is a direction away from the cylinder chamber, and the tip is in contact with the outer peripheral surface of the piston. Dividing the chamber into a low pressure and a high pressure, and a vane whose back portion is accommodated in the vane back chamber;
を備えたロータリ式圧縮機であって、A rotary compressor with
一方の前記圧縮部は、One of the compression units is
前記ベーンの前記背面部の後方に配置された第１永久磁石を有し、前記ベーンの前記先端部と前記背面部とに働く圧力の差により、前記ベーンに対して前方に作用する第１力と、前記第１永久磁石により前記ベーンを後方に吸引する第２力とによって、前記ベーンの前記先端部が前記ピストンの外周面に当接した圧縮運転状態と、前記ピストンの外周面から離間した前記ベーンを吸着固定した非圧縮運転状態とを切替える切替え機構を備え、A first force that has a first permanent magnet disposed behind the back surface portion of the vane and acts forward on the vane due to a difference in pressure acting on the tip portion and the back surface portion of the vane. And a second driving force that attracts the vane backward by the first permanent magnet, and the compression operation state in which the tip end portion of the vane is in contact with the outer peripheral surface of the piston is separated from the outer peripheral surface of the piston. A switching mechanism for switching between the non-compression operation state in which the vane is adsorbed and fixed,
さらに、前記ベーンが最も前方に移動する下死点位置において、前記ベーンを前方へ吸引する第３力が作用するように、前記ベーンの前記背面部よりも前方側に配置された第２永久磁石を備え、Further, a second permanent magnet disposed on the front side of the back surface of the vane so that a third force for sucking the vane forward acts at a bottom dead center position where the vane moves most forward. With
前記第１永久磁石及び前記第２永久磁石は、別々の永久磁石であり、The first permanent magnet and the second permanent magnet are separate permanent magnets,
前記第２永久磁石は、前記駆動軸の軸方向において前記シリンダとは異なる位置に固定されているロータリ式圧縮機。The second permanent magnet is a rotary compressor fixed at a position different from the cylinder in the axial direction of the drive shaft. 前記第１永久磁石は前記シリンダに固定されている請求項１または請求項２に記載のロータリ式圧縮機。 The rotary compressor according to claim 1 or 2 , wherein the first permanent magnet is fixed to the cylinder. 前記駆動軸を回転自在に支持する軸受部と、前記シリンダ室の端部を閉塞するフランジ部とを有する支持部材を備え、
前記第２永久磁石は、前記支持部材に固定されている請求項２に記載のロータリ式圧縮機。 A support member having a bearing portion that rotatably supports the drive shaft, and a flange portion that closes an end portion of the cylinder chamber;
The rotary compressor according to claim 2 , wherein the second permanent magnet is fixed to the support member. 前記第２永久磁石は、前記駆動軸の軸方向において前記シリンダ室よりも前記支持部材側であり、前記支持部材より外側となる位置に配置されている請求項４に記載のロータリ式圧縮機。 5. The rotary compressor according to claim 4 , wherein the second permanent magnet is disposed at a position closer to the support member than the cylinder chamber in the axial direction of the drive shaft and outside the support member. 前記第１永久磁石及び前記第２永久磁石は、反発しあう向きに磁界を発生する請求項２、請求項４、請求項５のいずれか一項に記載のロータリ式圧縮機。 The rotary compressor according to any one of claims 2, 4, and 5 , wherein the first permanent magnet and the second permanent magnet generate a magnetic field in a repulsive direction. 前記第３力が働く前記ベーンは、磁性材料で形成されて前記第３力が働くベーン吸引箇所を備え、
該ベーン吸引箇所は、前記ベーン溝と摺動しない位置に配置されている請求項１〜請求項６のいずれか一項に記載のロータリ式圧縮機。 The vane acting with the third force includes a vane suction portion formed of a magnetic material and acting with the third force,
The rotary compressor according to any one of claims 1 to 6 , wherein the vane suction portion is disposed at a position that does not slide with the vane groove. 前記第３力が働く前記ベーンは、磁性材料で形成されて前記第３力が働くベーン吸引箇所を備え、
前記ベーン吸引箇所は、前記駆動軸の軸方向において前記シリンダ室よりも前記支持部材側で、前記下死点位置において前記支持部材より外側となる位置であり、周囲の部材と摺動しない位置に配置されている請求項４または請求項５に記載のロータリ式圧縮機。 The vane acting with the third force includes a vane suction portion formed of a magnetic material and acting with the third force,
The vane suction location is a position that is closer to the support member than the cylinder chamber in the axial direction of the drive shaft and outside the support member at the bottom dead center position, and does not slide with surrounding members. The rotary compressor according to claim 4 or 5 , wherein the rotary compressor is arranged. 前記第３力が働く前記ベーンは、前記ベーン吸引箇所以外が非磁性材料で形成されている請求項７又は請求項８に記載のロータリ式圧縮機。 The rotary compressor according to claim 7 or 8 , wherein the vane on which the third force acts is formed of a nonmagnetic material except for the vane suction portion. 請求項１〜請求項９のいずれか一項に記載のロータリ式圧縮機と、凝縮器と、減圧機構と、蒸発器とを備えたヒートポンプ装置。 A heat pump device comprising the rotary compressor according to any one of claims 1 to 9 , a condenser, a decompression mechanism, and an evaporator.
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