JP5263213B2 - Rotary compressor - Google Patents

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JP5263213B2
JP5263213B2 JP2010082621A JP2010082621A JP5263213B2 JP 5263213 B2 JP5263213 B2 JP 5263213B2 JP 2010082621 A JP2010082621 A JP 2010082621A JP 2010082621 A JP2010082621 A JP 2010082621A JP 5263213 B2 JP5263213 B2 JP 5263213B2
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cylinder
suction
vane
circumferential direction
groove
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順也 田中
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Fujitsu General Ltd
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Description

本発明は、冷凍装置や空気調和機等の冷凍サイクルに使用されるロータリ圧縮機に関する。   The present invention relates to a rotary compressor used in a refrigeration cycle such as a refrigeration apparatus or an air conditioner.

２シリンダロータリ圧縮機の圧縮機筐体（密閉ケース）の耐圧強度は、アキュムレータに接続される第１、第２の連通管が挿入される第１、第２の連通孔（吸込用貫通孔）の間が最も弱い。第１、第２の連通孔間の距離を大きくすることにより、耐圧強度は強くなる。   The pressure resistance strength of the compressor casing (sealed case) of the two-cylinder rotary compressor is determined by the first and second communication holes (suction through holes) into which the first and second communication pipes connected to the accumulator are inserted. Between is the weakest. By increasing the distance between the first and second communication holes, the pressure strength is increased.

従来、密閉ケース内の軸方向に第１、第２の圧縮機構を設けると共にその密閉ケースに第１、第２の吸込用貫通孔を設けた密閉型圧縮機において、第１、第２のシリンダブロックに形成された第１、第２のブレード溝及び第１、第２のシリンダ室に開口する第１、第２の吸込口の周方向位置は同じとし、その第１、第２の吸込口から前記密閉ケースまでの、第１、第２のシリンダブロックの第１、第２の吸込通路の周方向角度を異なる角度とすることにより、前記第１、第２の吸込用貫通孔を密閉ケースの周方向にずらして形成したものが開示されている（特許文献１の第３図参照）。   2. Description of the Related Art Conventionally, in a hermetic compressor in which first and second compression mechanisms are provided in the axial direction in a hermetic case and the first and second suction through holes are provided in the hermetic case, the first and second cylinders The first and second suction ports formed in the block and the first and second suction ports that open to the first and second cylinder chambers have the same circumferential position, and the first and second suction ports are the same. The first and second suction through-holes are sealed case by changing the circumferential angles of the first and second suction passages of the first and second cylinder blocks from the first to the second sealing case to different angles. Are formed so as to be shifted in the circumferential direction (see FIG. 3 of Patent Document 1).

また、密閉ケース内の軸方向に第１、第２の圧縮機構を設けると共にその密閉ケースに第１、第２の吸込用貫通孔を設けた密閉型圧縮機において、第１のシリンダブロックに対して第２のシリンダブロックを周方向に回転させて設置して、第１、第２の吸込通路の周方向角度を異なる角度とすることにより、前記第１、第２の吸込用貫通孔を密閉ケースの周方向にずらして形成したものが開示されている（特許文献１の第４図参照）。   In the hermetic compressor in which the first and second compression mechanisms are provided in the axial direction in the hermetic case and the first and second suction through holes are provided in the hermetic case, The first and second suction through-holes are hermetically sealed by rotating the second cylinder block in the circumferential direction and setting the circumferential angles of the first and second suction passages to different angles. The one formed by shifting in the circumferential direction of the case is disclosed (see FIG. 4 of Patent Document 1).

特開平２−１２３２９３号公報（第２頁、第３図、第４図）Japanese Patent Laid-Open No. 2-123293 (2nd page, FIG. 3, FIG. 4)

しかしながら、上記特許文献１の第３図に記載された従来の技術によれば、第１、第２のシリンダ室に開口する第１、第２の吸込口から密閉ケースまでの第１、第２の吸込通路の周方向角度（シリンダ室への入射角度）を異なる角度とするので、第１、第２の吸込口の周方向開口幅が異なってしまう。シリンダ容積は、ローラが吸入口の開口部を通過完了したときの位置で決まるため、第１、第２のシリンダ間で吸入口の周方向開口幅が異なると、シリンダ容積が異なってしまい、第１、第２のシリンダの圧縮荷重と吐出ガス流量がアンバランスとなり、圧縮機の振動や騒音が増大する、という問題がある。   However, according to the conventional technique described in FIG. 3 of Patent Document 1, the first and second suction ports from the first and second suction ports opened to the first and second cylinder chambers to the sealed case are provided. Since the circumferential angle (incident angle to the cylinder chamber) of the suction passage is different, the circumferential opening widths of the first and second suction ports are different. Since the cylinder volume is determined by the position when the roller has completed passing through the opening of the suction port, if the circumferential opening width of the suction port differs between the first and second cylinders, the cylinder volume will be different. There is a problem that the compression load and the discharge gas flow rate of the first and second cylinders become unbalanced and the vibration and noise of the compressor increase.

また、上記特許文献１の第４図に記載された従来の技術によれば、第１、第２のシリンダ容積を同じにすることができるが、第１、第２のシリンダの回転位相差が１８０°ではなくなってしまう。そのため、ローラ遠心力、圧縮荷重、吐出ガス流量のアンバランスを生じ、同じく、圧縮機の振動や騒音が増大する、という問題がある。   Further, according to the conventional technique described in FIG. 4 of Patent Document 1, the first and second cylinder volumes can be made the same, but the rotational phase difference between the first and second cylinders is the same. It will not be 180 °. Therefore, the roller centrifugal force, the compression load, and the discharge gas flow rate are unbalanced, and similarly, there is a problem that the vibration and noise of the compressor increase.

本発明は、上記に鑑みてなされたものであって、第１、第２の吸込用貫通孔（連通孔）を密閉ケース（圧縮機筐体）の周方向にずらして形成することができ、かつ、ローラ（ピストン）遠心力、圧縮荷重、吐出ガス流量のアンバランスを生じることのないロータリ圧縮機を得ることを目的とする。   The present invention has been made in view of the above, and can be formed by shifting the first and second suction through holes (communication holes) in the circumferential direction of the sealed case (compressor housing), And it aims at obtaining the rotary compressor which does not produce imbalance of roller (piston) centrifugal force, compression load, and discharge gas flow rate.

上述した課題を解決し、目的を達成するために、本発明は、第１の張出し部に第１の吸入孔及び第１のベーン溝が設けられた環状の第１のシリンダと、回転軸の第１の偏芯部に保持され前記第１のシリンダの内壁に沿って該第１のシリンダ内を公転する第１の環状ピストンと、前記第１のベーン溝内から前記第１のシリンダ内に突出して前記第１の環状ピストンに当接する第１のベーンと、を備えて成る第１の圧縮部と、前記第１の圧縮部に積層され、第２の張出し部に第２の吸入孔及び第２のベーン溝が設けられた環状の第２のシリンダと、前記回転軸の第２の偏芯部に保持され前記第２のシリンダの内壁に沿って該第２のシリンダ内を公転する第２の環状ピストンと、前記第２のベーン溝内から前記第２のシリンダ内に突出して前記第２の環状ピストンに当接する第２のベーンと、を備えて成る第２の圧縮部と、前記第１の圧縮部及び第２の圧縮部を収容する密閉された圧縮機筐体と、を備えるロータリ圧縮機において、前記第１、第２のベーン溝と周方向に所定の角度を成すように、前記第１の吸入孔を前記第１の張出し部に放射状に形成し、前記第１の吸入孔と周方向同一位置に、周方向の開口幅が前記第１の吸入孔の内径と同一であって径方向に所定の深さの軸方向の第２の吸入溝を前記第２の張出し部に放射状に形成し、前記第２の吸入孔を、前記第１、第２のベーン溝と周方向に前記所定の角度より大きい角度を成すように、かつ、前記第２の吸入溝の底部に連通するように、前記第２の張出し部に形成し、前記第１、第２の吸入孔の夫々に連通する、前記圧縮機筐体に形成された第１、第２の連通孔を互いに周方向にずらして形成したことを特徴とする。   In order to solve the above-described problems and achieve the object, the present invention provides an annular first cylinder in which a first suction hole and a first vane groove are provided in a first projecting portion, and a rotating shaft. A first annular piston held by a first eccentric part and revolving in the first cylinder along an inner wall of the first cylinder; and from the first vane groove into the first cylinder. A first vane that protrudes and abuts against the first annular piston, and is stacked on the first compression portion, and a second suction hole and An annular second cylinder provided with a second vane groove, and a second cylinder revolved along the inner wall of the second cylinder held by the second eccentric portion of the rotating shaft. Two annular pistons and the second vane groove protruding from the second vane groove into the second cylinder. A second compression section comprising a second vane in contact with the annular piston; and a rotary compressor comprising a hermetically sealed compressor housing that houses the first compression section and the second compression section. In the machine, the first suction holes are formed radially in the first overhanging portion so as to form a predetermined angle with the first and second vane grooves in the circumferential direction, and the first suction holes and At the same position in the circumferential direction, an axial second suction groove having a circumferential opening width equal to the inner diameter of the first suction hole and having a predetermined depth in the radial direction is radially formed in the second overhanging portion. The second suction hole is communicated with the first and second vane grooves so as to form an angle larger than the predetermined angle in the circumferential direction and to the bottom of the second suction groove. As described above, the compressor housing is formed in the second projecting portion and communicates with each of the first and second suction holes. First it was formed by shifting the second communicating hole in one another circumferentially formed characterized.

本発明にかかるロータリ圧縮機は、第１、第２の吸込用貫通孔（連通孔）を密閉ケース（圧縮機筐体）の周方向にずらして形成することができ、かつ、ローラ（ピストン）遠心力、圧縮荷重、吐出ガス流量のアンバランスを生じることはない、という効果を奏する。   The rotary compressor according to the present invention can be formed by shifting the first and second suction through-holes (communication holes) in the circumferential direction of the hermetic case (compressor housing), and a roller (piston). There is an effect that an unbalance of centrifugal force, compressive load, and discharge gas flow rate does not occur.

図１は、本発明にかかるロータリ圧縮機の実施例の第１の圧縮部を示す横断面図である。FIG. 1 is a cross-sectional view showing a first compression section of an embodiment of a rotary compressor according to the present invention. 図２は、実施例の第２の圧縮部を示す横断面図である。FIG. 2 is a cross-sectional view showing a second compression unit of the embodiment.

以下に、本発明にかかるロータリ圧縮機の実施例を図面に基づいて詳細に説明する。なお、この実施例によりこの発明が限定されるものではない。   Embodiments of a rotary compressor according to the present invention will be described below in detail with reference to the drawings. Note that the present invention is not limited to the embodiments.

図１は、本発明にかかるロータリ圧縮機の実施例の第１の圧縮部を示す横断面図であり、図２は、実施例の第２の圧縮部の横断面図である。   FIG. 1 is a cross-sectional view showing a first compression section of an embodiment of a rotary compressor according to the present invention, and FIG. 2 is a cross-sectional view of a second compression section of the embodiment.

図１及び図２に示すように、実施例のロータリ圧縮機１は、密閉された縦置き円筒状の圧縮機筐体１０の下部に設置された圧縮部１２と、圧縮機筐体の上部に設置され、回転軸１５を介して圧縮部１２を駆動するモータ（図示せず）と、を備えている。   As shown in FIGS. 1 and 2, the rotary compressor 1 according to the embodiment includes a compression unit 12 installed at a lower portion of a sealed vertical cylindrical compressor housing 10 and an upper portion of the compressor housing. And a motor (not shown) that drives the compressor 12 via the rotary shaft 15.

圧縮部１２は、第１の圧縮部１２Ｓと、第１の圧縮部１２Ｓと並列に設置され第１の圧縮部１２Ｓの上側に積層された第２の圧縮部１２Ｔと、を備えている。第１、第２の圧縮部１２Ｓ、１２Ｔは、第１、第２の吸入孔１３５Ｓ、１３５Ｔ、第１、第２のベーン溝１２８Ｓ、１２８Ｔ及び第１、第２の背圧室１２９Ｓ、１２９Ｔを設けるための第１、第２の張出し部１２２Ｓ、１２２Ｔを有する環状の第１、第２のシリンダ１２１Ｓ、１２１Ｔを備えている。   The compression unit 12 includes a first compression unit 12S and a second compression unit 12T that is installed in parallel with the first compression unit 12S and stacked on the upper side of the first compression unit 12S. The first and second compression portions 12S and 12T include first and second suction holes 135S and 135T, first and second vane grooves 128S and 128T, and first and second back pressure chambers 129S and 129T, respectively. Annular first and second cylinders 121S and 121T having first and second overhang portions 122S and 122T for provision are provided.

第１、第２のシリンダ１２１Ｓ、１２１Ｔには、モータと同心に、円形の第１、第２のシリンダ内壁１２３Ｓ、１２３Ｔが形成されている。第１、第２のシリンダ内壁１２３Ｓ、１２３Ｔ内には、シリンダ内径よりも小さい外径の環状の第１、第２の環状ピストン１２５Ｓ、１２５Ｔが夫々配置され、第１、第２のシリンダ内壁１２３Ｓ、１２３Ｔと、第１、第２の環状ピストン１２５Ｓ、１２５Ｔとの間に、冷媒ガスを吸入し圧縮して吐出する第１、第２の作動室１３０Ｓ、１３０Ｔ（圧縮空間）が形成される。   In the first and second cylinders 121S and 121T, circular first and second cylinder inner walls 123S and 123T are formed concentrically with the motor. In the first and second cylinder inner walls 123S and 123T, annular first and second annular pistons 125S and 125T having an outer diameter smaller than the cylinder inner diameter are disposed, respectively, and the first and second cylinder inner walls 123S are disposed. , 123T and the first and second annular pistons 125S, 125T are formed with first and second working chambers 130S, 130T (compression spaces) for sucking, compressing and discharging the refrigerant gas.

第１、第２のシリンダ１２１Ｓ、１２１Ｔには、第１、第２のシリンダ内壁１２３Ｓ、１２３Ｔから径方向に、シリンダ高さ全域に亘る第１、第２のベーン溝１２８Ｓ、１２８Ｔが形成され、第１、第２のベーン溝１２８Ｓ、１２８Ｔ内に、夫々平板状の第１、第２のベーン１２７Ｓ、１２７Ｔが嵌合されている。   The first and second cylinders 121S and 121T are formed with first and second vane grooves 128S and 128T extending from the first and second cylinder inner walls 123S and 123T in the radial direction over the entire cylinder height, Flat plate-like first and second vanes 127S and 127T are fitted in the first and second vane grooves 128S and 128T, respectively.

第１、第２のベーン溝１２８Ｓ、１２８Ｔの奥部には、第１、第２のスプリング（図示せず）が配置されている。常時は、この第１、第２のスプリングの反発力により、第１、第２のベーン１２７Ｓ、１２７Ｔが、第１、第２のベーン溝１２８Ｓ、１２８Ｔ内から第１、第２の作動室１３０Ｓ、１３０Ｔ内に突出し、その先端が、第１、第２の環状ピストン１２５Ｓ、１２５Ｔの外周面に当接し、第１、第２のベーン１２７Ｓ、１２７Ｔにより、第１、第２の作動室１３０Ｓ、１３０Ｔ（圧縮空間）が、第１、第２の吸入室１３１Ｓ、１３１Ｔと、第１、第２の圧縮室１３３Ｓ、１３３Ｔとに区画される。   First and second springs (not shown) are disposed in the inner portions of the first and second vane grooves 128S and 128T. Normally, due to the repulsive force of the first and second springs, the first and second vanes 127S and 127T are moved from the first and second vane grooves 128S and 128T into the first and second working chambers 130S. , 130T, the tips of which contact the outer peripheral surfaces of the first and second annular pistons 125S, 125T, and the first and second working chambers 130S, 130T, by the first and second vanes 127S, 127T. 130T (compression space) is partitioned into first and second suction chambers 131S and 131T and first and second compression chambers 133S and 133T.

また、第１、第２のシリンダ１２１Ｓ、１２１Ｔには、第１、第２のベーン溝１２８Ｓ、１２８Ｔの奥部と圧縮機筐体内とを連通して、第１、第２のベーン１２７Ｓ、１２７Ｔに、圧縮された吐出冷媒ガスの圧力により背圧をかける第１、第の２背圧室１２９Ｓ、１２９Ｔが形成されている。   The first and second cylinders 121S and 121T are communicated with the inner portions of the first and second vane grooves 128S and 128T and the inside of the compressor housing, so that the first and second vanes 127S and 127T are communicated with each other. In addition, first and second back pressure chambers 129S and 129T for applying a back pressure by the pressure of the compressed discharged refrigerant gas are formed.

第１、第２のシリンダ１２１Ｓ、１２１Ｔの第１、第２の張出し部１２２Ｓ、１２２Ｔには、第１、第２の吸入室１３１Ｓ、１３１Ｔに外部から冷媒を吸入するために、第１、第２の吸入室１３１Ｓ、１３１Ｔと外部とを連通させる第１、第２の吸入孔１３５Ｓ、１３５Ｔが設けられている。   The first and second overhanging portions 122S and 122T of the first and second cylinders 121S and 121T are provided with a first and a second in order to suck the refrigerant from the outside into the first and second suction chambers 131S and 131T. First and second suction holes 135S and 135T are provided for communicating the two suction chambers 131S and 131T with the outside.

また、第１のシリンダ１２１Ｓと第２のシリンダ１２１Ｔの間には、中間仕切板（図示せず）が設置され、第１のシリンダ１２１Ｓの第１の作動室１３０Ｓと第２のシリンダ１２１Ｔの第２の作動室１３０Ｔとを区画している。第１のシリンダ１２１Ｓの下端部には、下端板（図示せず）が設置され、第１のシリンダ１２１Ｓの第１の作動室１３０Ｓを閉塞している。また、第２のシリンダ１２１Ｔの上端部には、上端板（図示せず）が設置され、第２のシリンダ１２１Ｔの第２の作動室１３０Ｔを閉塞している。   Further, an intermediate partition plate (not shown) is installed between the first cylinder 121S and the second cylinder 121T, and the first working chamber 130S of the first cylinder 121S and the second cylinder 121T of the second cylinder 121T. 2 working chambers 130T. A lower end plate (not shown) is installed at the lower end of the first cylinder 121S, and closes the first working chamber 130S of the first cylinder 121S. An upper end plate (not shown) is installed at the upper end of the second cylinder 121T, and closes the second working chamber 130T of the second cylinder 121T.

回転軸１５は、互いに１８０°位相をずらして偏心させた第１の偏芯部１５２Ｓと第２の偏芯部１５２Ｔとを備え、第１の偏芯部１５２Ｓは、第１の圧縮部１２Ｓの第１の環状ピストン１２５Ｓを回転自在に保持し、第２の偏芯部１５２Ｔは、第２の圧縮部１２Ｔの第２の環状ピストン１２５Ｔを回転自在に保持している。   The rotating shaft 15 includes a first eccentric portion 152S and a second eccentric portion 152T that are deviated from each other by 180 degrees in phase, and the first eccentric portion 152S is the first eccentric portion 152S. The first annular piston 125S is rotatably held, and the second eccentric part 152T rotatably holds the second annular piston 125T of the second compression part 12T.

回転軸１５が回転すると、第１、第２の環状ピストン１２５Ｓ、１２５Ｔが、第１、第２のシリンダ内壁１２３Ｓ、１２３Ｔに沿って第１、第２のシリンダ１２１Ｓ、１２１Ｔ内を反時計回りに公転し、これに追随して第１、第２のベーン１２７Ｓ、１２７Ｔが往復運動する。この第１、第２の環状ピストン１２５Ｓ、１２５Ｔ及び第１、第２のベーン１２７Ｓ、１２７Ｔの運動により、第１、第２の吸入室１３１Ｓ、１３１Ｔ及び第１、第２の圧縮室１３３Ｓ、１３３Ｔの容積が連続的に変化し、圧縮部１２は、連続的に冷媒ガスを吸入し圧縮して第１、第２の吐出孔１９０Ｓ、１９０Ｔから圧縮機筐体１０内へ吐出する。   When the rotary shaft 15 rotates, the first and second annular pistons 125S and 125T rotate counterclockwise in the first and second cylinders 121S and 121T along the first and second cylinder inner walls 123S and 123T. Revolving and following this, the first and second vanes 127S and 127T reciprocate. Due to the movement of the first and second annular pistons 125S and 125T and the first and second vanes 127S and 127T, the first and second suction chambers 131S and 131T and the first and second compression chambers 133S and 133T are obtained. The compressor 12 continuously sucks and compresses the refrigerant gas and discharges it into the compressor housing 10 through the first and second discharge holes 190S and 190T.

次に、実施例のロータリ圧縮機１の特徴的な構成について説明する。図１に示すように、第１の吸入孔１３５Ｓは、第１のベーン溝１２８Ｓと所定角度α（例えば、１８°）を成すように、第１の張出し部１２２Ｓに放射状に筒として形成されている。第１の吸入孔１３５Ｓ及び圧縮機筐体１０の第１の連通孔１０１Ｓには、第１の吸入管１０４Ｓの一端が挿嵌され、第１の吸入管１０４Ｓの他端には、一端がアキュムレータに接続された第１の低圧連絡管（図示せず）の他端が挿嵌される。   Next, a characteristic configuration of the rotary compressor 1 of the embodiment will be described. As shown in FIG. 1, the first suction holes 135S are radially formed as cylinders in the first overhanging portion 122S so as to form a predetermined angle α (for example, 18 °) with the first vane groove 128S. Yes. One end of the first suction pipe 104S is inserted into the first suction hole 135S and the first communication hole 101S of the compressor housing 10, and the other end of the first suction pipe 104S is connected to one end of the accumulator. The other end of the first low-pressure connecting pipe (not shown) connected to is inserted.

図２に示すように、第２の吸入溝１３７Ｔは、第１の吸入孔１３５Ｓと周方向同一位置に（第１、第２のベーン溝１２８Ｓ、１２８Ｔと所定角度α（例えば、１８°）を成すように）、周方向の開口幅Ｋが第１の吸入孔１３５Ｓの内径Ｋ（図１参照）と同一となるように、径方向に所定の深さに、軸方向に貫通するように、第２の張出し部１２２Ｔに放射状に形成されている。   As shown in FIG. 2, the second suction groove 137T has a predetermined angle α (for example, 18 °) with the first suction hole 135S at the same circumferential position (the first and second vane grooves 128S and 128T). So that the opening width K in the circumferential direction is the same as the inner diameter K (see FIG. 1) of the first suction hole 135S so as to penetrate the axial direction to a predetermined depth in the radial direction. The second overhang portion 122T is formed radially.

第２の吸入孔１３５Ｔは、第１、第２のベーン溝１２８Ｓ、１２８Ｔと周方向に所定の角度α（例えば、１８°）より大きい角度β（例えば、６０°）を成すように、かつ、第２の吸入溝１３７Ｔの底部に連通するように、第２の張出し部１２２Ｔに形成されている。その結果、図１及び図２に示すように、第１、第２の吸入孔１３５Ｓ、１３５Ｔの夫々に連通する、圧縮機筐体１０に形成される第１、第２の連通孔１０１Ｓ、１０１Ｔは、互いに周方向にずらして形成される。   The second suction hole 135T forms an angle β (for example, 60 °) larger than a predetermined angle α (for example, 18 °) with the first and second vane grooves 128S, 128T in the circumferential direction, and The second overhang portion 122T is formed so as to communicate with the bottom of the second suction groove 137T. As a result, as shown in FIGS. 1 and 2, the first and second communication holes 101S and 101T formed in the compressor housing 10 communicate with the first and second suction holes 135S and 135T, respectively. Are formed so as to be shifted from each other in the circumferential direction.

第２の吸入孔１３５Ｔ及び圧縮機筐体１０の第２の連通孔１０１Ｔには、第２の吸入管１０４Ｔの一端が挿嵌され、第２の吸入管１０４Ｔの他端には、一端がアキュムレータに接続された第２の低圧連絡管（図示せず）の他端が挿嵌される。中間仕切板と上端板で第２の吸入溝１３７Ｔの軸方向の面が閉塞されるので、第２の吸入溝１３７Ｔは、吸入口の一部として機能する。   One end of the second suction pipe 104T is inserted into the second suction hole 135T and the second communication hole 101T of the compressor housing 10, and one end is an accumulator at the other end of the second suction pipe 104T. The other end of the second low-pressure connecting pipe (not shown) connected to the is inserted. Since the axial surface of the second suction groove 137T is closed by the intermediate partition plate and the upper end plate, the second suction groove 137T functions as a part of the suction port.

以上説明したように、実施例のロータリ圧縮機１は、第１、第２の連通孔１０１Ｓ、１０１Ｔを圧縮機筐体１０の周方向にずらして形成することができる。また、第２の吸入溝１３７Ｔは、第１の吸入孔１３５Ｓと周方向同一位置に、周方向の開口幅Ｋが第１の吸入孔１３５Ｓの内径Ｋ（図１参照）と同一となるように、径方向に所定の深さに、軸方向に貫通するように、第２の張出し部１２２Ｔに放射状に形成されているので、ピストン遠心力、圧縮荷重、吐出ガス流量のアンバランスを生じることはない。   As described above, the rotary compressor 1 according to the embodiment can be formed by shifting the first and second communication holes 101 </ b> S and 101 </ b> T in the circumferential direction of the compressor housing 10. The second suction groove 137T is located at the same position in the circumferential direction as the first suction hole 135S, and the opening width K in the circumferential direction is the same as the inner diameter K (see FIG. 1) of the first suction hole 135S. Since the second overhanging portion 122T is formed radially so as to penetrate in the axial direction to a predetermined depth in the radial direction, an unbalance of the piston centrifugal force, the compressive load, and the discharge gas flow rate is generated. Absent.

シリンダの内周側から径方向に穴加工をすることは難しいが、実施例では、第２のシリンダ１２１Ｔの内周側から、径方向に所定の深さに、軸方向に貫通するように、第２の吸入溝１３７Ｔを第２の張出し部１２２Ｔに放射状に形成するので、機械加工が容易である。   Although it is difficult to make a hole in the radial direction from the inner peripheral side of the cylinder, in the embodiment, from the inner peripheral side of the second cylinder 121T, it penetrates in the axial direction to a predetermined depth in the radial direction. Since the second suction groove 137T is formed radially on the second overhanging portion 122T, machining is easy.

なお、以上説明した実施例のロータリ圧縮機１では、第２のシリンダ１２１Ｔにのみ第２の吸入溝１３７Ｔを形成したが、第１のシリンダ１２１Ｓの第１の吸入孔１３５Ｓの内周側にも、第２の吸入溝１３７Ｔと同じ形状の第１の吸入溝（図示せず）を形成してもよい。このようにすれば、第１、第２の吸入室１３１Ｓ、１３１Ｔの吸入部の開口形状が同一となるので、実施例のロータリ圧縮機１よりも吐出ガス流量のアンバランスが生じ難くなる。   In the rotary compressor 1 of the embodiment described above, the second suction groove 137T is formed only in the second cylinder 121T, but also on the inner peripheral side of the first suction hole 135S of the first cylinder 121S. A first suction groove (not shown) having the same shape as the second suction groove 137T may be formed. In this way, since the opening shapes of the suction portions of the first and second suction chambers 131S and 131T are the same, an imbalance in the discharge gas flow rate is less likely to occur than in the rotary compressor 1 of the embodiment.

また、実施例は、２シリンダロータリ圧縮機１について説明したが、本発明を２段圧縮ロータリ圧縮機に適用する場合は、実施例の第２の圧縮部１２Ｔの構成を低断側圧縮部（第１の圧縮部）に適用し、第２の圧縮部１２Ｔより機械構造強度が高い実施例の第１の圧縮部１２Ｓの構成を、高圧となる高段側圧縮部（第２の圧縮部）に適用するのがよい。   Moreover, although the Example demonstrated the 2-cylinder rotary compressor 1, when applying this invention to a two-stage compression rotary compressor, the structure of the 2nd compression part 12T of an Example is made into the low side compression part ( The first compression unit 12S is applied to the first compression unit) and has a mechanical structure strength higher than that of the second compression unit 12T. The configuration of the first compression unit 12S is a high-stage compression unit (second compression unit) that has a high pressure. It is good to apply to.

以上のように、本発明にかかるロータリ圧縮機は、冷凍装置や空気調和機等の冷凍サイクルに使用されるロータリ圧縮機に適している。   As described above, the rotary compressor according to the present invention is suitable for a rotary compressor used in a refrigeration cycle such as a refrigeration apparatus or an air conditioner.

１ ロータリ圧縮機
１２ 圧縮部
１５ 回転軸
１２Ｓ 第１の圧縮部
１２Ｔ 第２の圧縮部
１０１Ｓ 第１の連通孔
１０１Ｔ 第２の連通孔
１０４Ｓ 第１の連通管
１０４Ｔ 第２の連通管
１２１Ｓ 第１のシリンダ
１２１Ｔ 第２のシリンダ
１２２Ｓ 第１の張出し部
１２２Ｔ 第２の張出し部
１２３Ｓ 第１のシリンダ内壁
１２３Ｔ 第２のシリンダ内壁
１２５Ｓ 第１の環状ピストン
１２５Ｔ 第２の環状ピストン
１２７Ｓ 第１のベーン
１２７Ｔ 第２のベーン
１２８Ｓ 第１のベーン溝
１２８Ｔ 第２のベーン溝
１２９Ｓ 第１の背圧室
１２９Ｔ 第２の背圧室
１３０Ｓ 第１の作動室
１３０Ｔ 第２の作動室
１３１Ｓ 第１の吸入室
１３１Ｔ 第２の吸入室
１３３Ｓ 第１の圧縮室
１３３Ｔ 第２の圧縮室
１３５Ｓ 第１の吸入孔
１３５Ｔ 第２の吸入孔
１３７Ｔ 第２の吸入溝
１５２Ｓ 第１の偏芯部
１５２Ｔ 第２の偏芯部
１９０Ｓ 第１の吐出孔
１９０Ｔ 第２の吐出孔 DESCRIPTION OF SYMBOLS 1 Rotary compressor 12 Compression part 15 Rotating shaft 12S 1st compression part 12T 2nd compression part 101S 1st communication hole 101T 2nd communication hole 104S 1st communication pipe 104T 2nd communication pipe 121S 1st Cylinder 121T 2nd cylinder 122S 1st overhang part 122T 2nd overhang part 123S 1st cylinder inner wall 123T 2nd cylinder inner wall 125S 1st annular piston 125T 2nd annular piston 127S 1st vane 127T 2nd Vane 128S first vane groove 128T second vane groove 129S first back pressure chamber 129T second back pressure chamber 130S first working chamber 130T second working chamber 131S first suction chamber 131T second Suction chamber 133S First compression chamber 133T Second compression chamber 135S First suction hole 135T Second suction Hole 137T Second suction groove 152S First eccentric part 152T Second eccentric part 190S First discharge hole 190T Second discharge hole

Claims (3)

第１の張出し部に第１の吸入孔及び第１のベーン溝が設けられた環状の第１のシリンダと、回転軸の第１の偏芯部に保持され前記第１のシリンダの内壁に沿って該第１のシリンダ内を公転する第１の環状ピストンと、前記第１のベーン溝内から前記第１のシリンダ内に突出して前記第１の環状ピストンに当接する第１のベーンと、を備えて成る第１の圧縮部と、
前記第１の圧縮部に積層され、第２の張出し部に第２の吸入孔及び第２のベーン溝が設けられた環状の第２のシリンダと、前記回転軸の第２の偏芯部に保持され前記第２のシリンダの内壁に沿って該第２のシリンダ内を公転する第２の環状ピストンと、前記第２のベーン溝内から前記第２のシリンダ内に突出して前記第２の環状ピストンに当接する第２のベーンと、を備えて成る第２の圧縮部と、
前記第１の圧縮部及び第２の圧縮部を収容する密閉された圧縮機筐体と、
を備えるロータリ圧縮機において、
前記第１、第２のベーン溝と周方向に所定の角度を成すように、前記第１の吸入孔を前記第１の張出し部に放射状に形成し、
前記第１の吸入孔と周方向同一位置に、周方向の開口幅が前記第１の吸入孔の内径と同一であって径方向に所定の深さの軸方向の第２の吸入溝を前記第２の張出し部に放射状に形成し、前記第２の吸入孔を、前記第１、第２のベーン溝と周方向に前記所定の角度より大きい角度を成すように、かつ、前記第２の吸入溝の底部に連通するように、前記第２の張出し部に形成し、
前記第１、第２の吸入孔の夫々に連通する、前記圧縮機筐体に形成された第１、第２の連通孔を互いに周方向にずらして形成したことを特徴とするロータリ圧縮機。 An annular first cylinder in which a first suction hole and a first vane groove are provided in the first overhang portion, and a first eccentric portion of the rotating shaft, which is held along the inner wall of the first cylinder. A first annular piston that revolves in the first cylinder, and a first vane that protrudes from the first vane groove into the first cylinder and contacts the first annular piston. A first compression section comprising:
An annular second cylinder that is stacked on the first compression portion and has a second suction hole and a second vane groove provided on the second overhang portion, and a second eccentric portion of the rotating shaft. A second annular piston which is held and revolves along the inner wall of the second cylinder, and projects from the second vane groove into the second cylinder and protrudes into the second cylinder; A second vane that abuts the piston, and a second compression part,
A hermetically sealed compressor housing that houses the first compression section and the second compression section;
A rotary compressor comprising:
Forming the first suction holes radially in the first overhanging portion so as to form a predetermined angle in the circumferential direction with the first and second vane grooves;
An axial second suction groove having a circumferential opening width equal to the inner diameter of the first suction hole and a predetermined depth in the radial direction is provided at the same circumferential position as the first suction hole. The second overhanging portion is formed radially, and the second suction hole is formed at an angle larger than the predetermined angle in the circumferential direction with the first and second vane grooves, and the second Forming the second overhanging portion so as to communicate with the bottom of the suction groove;
A rotary compressor characterized in that the first and second communication holes formed in the compressor casing that communicate with the first and second suction holes are shifted from each other in the circumferential direction. 第１の張出し部に第１の吸入孔及び第１のベーン溝が設けられた環状の第１のシリンダと、回転軸の第１の偏芯部に保持され前記第１のシリンダの内壁に沿って該第１のシリンダ内を公転する第１の環状ピストンと、前記第１のベーン溝内から前記第１のシリンダ内に突出して前記第１の環状ピストンに当接する第１のベーンと、を備えて成る第１の圧縮部と、
前記第１の圧縮部に積層され、第２の張出し部に第２の吸入孔及び第２のベーン溝が設けられた環状の第２のシリンダと、前記回転軸の第２の偏芯部に保持され前記第２のシリンダの内壁に沿って該第２のシリンダ内を公転する第２の環状ピストンと、前記第２のベーン溝内から前記第２のシリンダ内に突出して前記第２の環状ピストンに当接する第２のベーンと、を備えて成る第２の圧縮部と、
前記第１の圧縮部及び第２の圧縮部を収容する密閉された圧縮機筐体と、
を備えるロータリ圧縮機において、
前記第１、第２のベーン溝と周方向に所定の角度を成すように、径方向に所定の深さの軸方向の第１、第２の吸入溝を前記第１、第２の張出し部に夫々放射状に形成し、
前記第１の吸入孔を、前記第１、第２のベーン溝と周方向に前記所定の角度を成すように、かつ、前記第１の吸入溝の底部に連通するように、前記第１の張出し部に放射状に形成し、
前記第２の吸入孔を、前記第１、第２のベーン溝と周方向に前記所定の角度より大きい角度を成すように、かつ、前記第２の吸入溝の底部に連通するように、前記第２の張出し部に形成し、
前記第１、第２の吸入孔の夫々に連通する、前記圧縮機筐体に形成された第１、第２の連通孔を互いに周方向にずらして形成したことを特徴とするロータリ圧縮機。 An annular first cylinder in which a first suction hole and a first vane groove are provided in the first overhang portion, and a first eccentric portion of the rotating shaft, which is held along the inner wall of the first cylinder. A first annular piston that revolves in the first cylinder, and a first vane that protrudes from the first vane groove into the first cylinder and contacts the first annular piston. A first compression section comprising:
An annular second cylinder that is stacked on the first compression portion and has a second suction hole and a second vane groove provided on the second overhang portion, and a second eccentric portion of the rotating shaft. A second annular piston which is held and revolves along the inner wall of the second cylinder, and projects from the second vane groove into the second cylinder and protrudes into the second cylinder; A second vane that abuts the piston, and a second compression part,
A hermetically sealed compressor housing that houses the first compression section and the second compression section;
A rotary compressor comprising:
The first and second overhanging portions are provided with axially first and second suction grooves having a predetermined depth in the radial direction so as to form a predetermined angle in the circumferential direction with the first and second vane grooves. Each formed radially,
The first suction hole is formed to form the predetermined angle in the circumferential direction with the first and second vane grooves, and to communicate with the bottom of the first suction groove. Formed radially on the overhang,
The second suction hole is communicated with the first and second vane grooves so as to form an angle larger than the predetermined angle in the circumferential direction and to communicate with the bottom of the second suction groove. Formed in the second overhang,
A rotary compressor characterized in that the first and second communication holes formed in the compressor casing that communicate with the first and second suction holes are shifted from each other in the circumferential direction. 第１の張出し部に第１の吸入孔及び第１のベーン溝が設けられた環状の第１のシリンダと、回転軸の第１の偏芯部に保持され前記第１のシリンダの内壁に沿って該第１のシリンダ内を公転する第１の環状ピストンと、前記第１のベーン溝内から前記第１のシリンダ内に突出して前記第１の環状ピストンに当接する第１のベーンと、を備えて成る第１の圧縮部と、
前記第１の圧縮部に積層され、第２の張出し部に第２の吸入孔及び第２のベーン溝が設けられた環状の第２のシリンダと、前記回転軸の第２の偏芯部に保持され前記第２のシリンダの内壁に沿って該第２のシリンダ内を公転する第２の環状ピストンと、前記第２のベーン溝内から前記第２のシリンダ内に突出して前記第２の環状ピストンに当接する第２のベーンと、を備えて成る第２の圧縮部と、
前記第１の圧縮部及び第２の圧縮部を収容する密閉された圧縮機筐体と、
を備える２段圧縮ロータリ圧縮機において、
前記第１、第２のベーン溝と周方向に所定の角度を成すように、高段側である前記第２の吸入孔を前記第２の張出し部に放射状に形成し、
前記第２の吸入孔と周方向同一位置に、周方向の開口幅が前記第２の吸入孔の内径と同一であって径方向に所定の深さの軸方向の低段側である第１の吸入溝を前記第１の張出し部に放射状に形成し、
低段側である前記第１の吸入孔を、前記第１、第２のベーン溝と周方向に前記所定の角度より大きい角度を成すように、かつ、前記第１の吸入溝の底部に連通するように、前記第１の張出し部に形成し、
前記第１、第２の吸入孔の夫々に連通する、前記圧縮機筐体に形成された第１、第２の連通孔を互いに周方向にずらして形成したことを特徴とするロータリ圧縮機。 An annular first cylinder in which a first suction hole and a first vane groove are provided in the first overhang portion, and a first eccentric portion of the rotating shaft, which is held along the inner wall of the first cylinder. A first annular piston that revolves in the first cylinder, and a first vane that protrudes from the first vane groove into the first cylinder and contacts the first annular piston. A first compression section comprising:
An annular second cylinder that is stacked on the first compression portion and has a second suction hole and a second vane groove provided on the second overhang portion, and a second eccentric portion of the rotating shaft. A second annular piston which is held and revolves along the inner wall of the second cylinder, and projects from the second vane groove into the second cylinder and protrudes into the second cylinder; A second vane that abuts the piston, and a second compression part,
A hermetically sealed compressor housing that houses the first compression section and the second compression section;
A two-stage compression rotary compressor comprising:
Forming the second suction holes on the high-stage side radially in the second overhanging portion so as to form a predetermined angle in the circumferential direction with the first and second vane grooves;
The first suction port is located at the same position in the circumferential direction as the second suction hole, and the opening width in the circumferential direction is the same as the inner diameter of the second suction hole and is the lower side in the axial direction with a predetermined depth in the radial direction Are formed radially in the first overhang,
The first suction hole, which is on the lower stage side, communicates with the first and second vane grooves so as to form an angle larger than the predetermined angle in the circumferential direction and to the bottom of the first suction groove. So as to form on the first overhang,
A rotary compressor characterized in that the first and second communication holes formed in the compressor casing that communicate with the first and second suction holes are shifted from each other in the circumferential direction.
JP2010082621A 2010-03-31 2010-03-31 Rotary compressor Expired - Fee Related JP5263213B2 (en)

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JP5471992B2 (en) * 2010-09-09 2014-04-16 株式会社富士通ゼネラル Rotary compressor
JP6324091B2 (en) * 2014-01-31 2018-05-16 三菱電機株式会社 Hermetic compressor
CN103883530B (en) * 2014-03-17 2017-06-06 安徽美芝精密制造有限公司 Rotary compressor and its cylinder

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JP4877054B2 (en) * 2007-04-27 2012-02-15 株式会社富士通ゼネラル Rotary compressor

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