JP6840173B2 - Compressor - Google Patents

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JP6840173B2
JP6840173B2 JP2018565162A JP2018565162A JP6840173B2 JP 6840173 B2 JP6840173 B2 JP 6840173B2 JP 2018565162 A JP2018565162 A JP 2018565162A JP 2018565162 A JP2018565162 A JP 2018565162A JP 6840173 B2 JP6840173 B2 JP 6840173B2
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refrigerant
compressor
suction
suction muffler
muffler
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JPWO2018142536A1 (en
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亮 濱田
亮 濱田
幹一朗 杉浦
幹一朗 杉浦
貴也 木本
貴也 木本
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/065—Noise dampening volumes, e.g. muffler chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/96—Preventing, counteracting or reducing vibration or noise

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

Description

本発明は、冷媒を圧縮して吐出する圧縮機に関するものである。 The present invention relates to a compressor that compresses and discharges a refrigerant.

ハイドロフルオロオレフィンは、従来冷媒として用いられているＲ４１０Ａ冷媒又はＲ３２冷媒と比較してＧＷＰ（地球温暖化係数）が小さく、地球温暖化への対策に用いる冷媒として有望な冷媒である。そこで、ハイドロフルオロオレフィンを主体とした動作冷媒を用いた圧縮機が提案されている（例えば、特許文献１参照）。 Hydrofluoroolefin has a smaller GWP (global warming potential) than the R410A refrigerant or R32 refrigerant conventionally used as a refrigerant, and is a promising refrigerant as a refrigerant used as a countermeasure against global warming. Therefore, a compressor using an operating refrigerant mainly composed of hydrofluoroolefin has been proposed (see, for example, Patent Document 1).

特開２０１２−５７５０３号公報Japanese Unexamined Patent Publication No. 2012-57503

上述したように、ハイドロフルオロオレフィンは、従来の冷媒であるＲ４１０又はＲ３２冷媒と比較してＧＷＰが小さく、地球温暖化への対策に用いる冷媒として有望な冷媒である。しかし、ハイドロフルオロオレフィンを圧縮機の動作冷媒とした場合、ハイドロフルオロオレフィンはＲ３２冷媒と比較して音速が小さい。そのため、従来の圧縮機でハイドロフルオロオレフィンを動作させた場合、吸入マフラーと冷媒動作音との共鳴による共鳴周波数が低周波数帯に遷移する。低周波数帯の動作音は、圧縮機の周囲に取り付ける遮音材の効果が薄く、圧縮機の静音性が悪化するという問題点がある。 As described above, hydrofluoroolefin has a smaller GWP than the conventional refrigerants R410 or R32, and is a promising refrigerant as a refrigerant used as a countermeasure against global warming. However, when hydrofluoroolefin is used as the operating refrigerant of the compressor, the sound velocity of hydrofluoroolefin is lower than that of R32 refrigerant. Therefore, when the hydrofluoroolefin is operated by a conventional compressor, the resonance frequency due to the resonance between the intake muffler and the operating sound of the refrigerant shifts to the low frequency band. The operating noise in the low frequency band has a problem that the effect of the sound insulating material attached around the compressor is weak and the quietness of the compressor is deteriorated.

本発明は、上記のよう課題を解決するためになされたもので、ハイドロフルオロオレフィンを動作冷媒として用いても吸入マフラーと冷媒動作音との共鳴による静音性の悪化を抑制する圧縮機を提供するものである。 The present invention has been made to solve the above problems, and provides a compressor that suppresses deterioration of quietness due to resonance between the suction muffler and the operating noise of the refrigerant even when hydrofluoroolefin is used as the operating refrigerant. It is a thing.

本発明に係る圧縮機は、圧縮機構部を内蔵した密閉容器と、圧縮機構部に接続された吸入管と、吸入管に接続された吸入マフラーと、吸入マフラーに接続され、冷媒を吸入マフラーに供給するための供給管と、を備え、吸入マフラーの内部空間において、吸入マフラーの供給管接続部と吸入管接続部との間の距離Ｌ「ｍｍ」が、１００［ｍｍ］＜Ｌ＜３００［ｍｍ］の範囲に形成されており、Ｒ１２３４ｙｆ冷媒とＲ３２冷媒とを主成分として含む混合冷媒を動作冷媒とし、動作冷媒全体に対するＲ１２３４ｙｆの割合をα［ｗｔ％］としたとき、下記の式３、式５、および式６のいずれか１つの式を満足し、供給管接続部が、吸入マフラーの長手方向軸に対して偏心するように配設されているものである。

Figure 0006840173
Figure 0006840173
Figure 0006840173
 The compressor according to the present invention has a closed container having a built-in compression mechanism, a suction pipe connected to the compression mechanism, a suction muffler connected to the suction pipe, and a suction muffler connected to the refrigerant into a suction muffler. A supply pipe for supplying is provided, and in the internal space of the suction muffler, the distance L "mm" between the supply pipe connecting portion and the suction pipe connecting portion of the suction muffler is 100 [mm] <L <300 [. mm] range are formed in the, and operates the refrigerant mixed refrigerant containing as a main component and R1234yf refrigerant and R32 refrigerant, when the ratio of R1234yf to the entire operation refrigerant was alpha [wt%], the formula 3 below, It satisfies any one of the formulas 5 and 6, and the supply pipe connection portion is arranged so as to be eccentric with respect to the longitudinal axis of the suction muffler.
Figure 0006840173
Figure 0006840173
Figure 0006840173

圧縮機は、動作冷媒全体に対するＲ１２３４ｙｆ冷媒の割合α［ｗｔ％］と、吸入マフラーの内部空間における吸入マフラーの供給管接続部と吸入管接続部との間の距離Ｌ「ｍｍ」とが、上記の式３〜式６のいずれか１つの式を満足することにより、圧縮機の騒音が小さい周波数又は遮音材の効果が発揮されやすい周波数に共鳴点を配置させることができる。そのため、圧縮機は、吸入マフラーと冷媒動作音との共鳴による騒音を効果的に抑制することができる。その結果、ハイドロフルオロオレフィンを動作冷媒とした圧縮機の静音性を向上させることができる。 In the compressor, the ratio α [wt%] of the R1234yf refrigerant to the entire operating refrigerant and the distance L “mm” between the supply pipe connection portion and the suction pipe connection portion of the suction muffler in the internal space of the suction muffler are as described above. By satisfying any one of the equations 3 to 6, the resonance point can be arranged at a frequency where the noise of the compressor is small or a frequency at which the effect of the sound insulating material is easily exhibited. Therefore, the compressor can effectively suppress the noise caused by the resonance between the suction muffler and the operating noise of the refrigerant. As a result, the quietness of the compressor using hydrofluoroolefin as the operating refrigerant can be improved.

本発明の実施の形態１に係る圧縮機の内部を示す内部構成図である。It is an internal block diagram which shows the inside of the compressor which concerns on Embodiment 1 of this invention. 本発明の実施の形態１に係る圧縮機の圧縮機構部を示す縦断面図である。It is a vertical sectional view which shows the compression mechanism part of the compressor which concerns on Embodiment 1 of this invention. 図２のＡ−Ａ線断面図である。FIG. 2 is a cross-sectional view taken along the line AA of FIG. 図２のＢ−Ｂ線断面図である。FIG. 2 is a cross-sectional view taken along the line BB of FIG. 周波数帯域における一般的な圧縮機単体の騒音を示す折れ線図である。It is a line chart which shows the noise of a general compressor alone in a frequency band. 周波数帯域における遮音材の効果を示す折れ線図である。It is a line chart which shows the effect of a sound insulation material in a frequency band. 周波数帯域における遮音材を備えた一般的な圧縮機単体の騒音を示す折れ線図である。It is a line chart which shows the noise of a general compressor alone provided with a sound insulation material in a frequency band. 周波数帯域におけるマフラー効果Ｅ［ｄＢ］を示す折れ線図である。It is a line chart which shows the muffler effect E [dB] in a frequency band. 冷媒全体に対するＲ１２３４ｙｆの割合α［ｗｔ％］と、音速ｃ［ｍｍ／ｓ］との関係を表す図である。It is a figure which shows the relationship between the ratio α [wt%] of R1234yf with respect to the whole refrigerant, and the sound velocity c [mm / s]. 吸入マフラーの概略化した側面図である。It is a schematic side view of the inhalation muffler. 吸入マフラーの概略化した平面図である。It is a schematic plan view of the suction muffler. 吸入マフラーの変形例の概略化した平面図である。It is the schematic plan view of the modification of the suction muffler. 吸入マフラーの他の変形例の概略化した平面図である。It is a schematic plan view of another modification of the suction muffler.

実施の形態１．
図１は、本発明の実施の形態１に係る圧縮機の内部を示す内部構成図である。以下の説明において、圧縮機として、圧縮機構部に２つの円筒シリンダを有するツインロータリー式の圧縮機１００を例に説明する。図１に示すように、圧縮機１００は、圧縮機構部３を内蔵した密閉容器１を備える。また、圧縮機１００は、密閉容器１の内部に、電動機部２を備える。さらに、圧縮機１００は、圧縮機構部３に接続された吸入管１５と、吸入管１５に接続された吸入マフラー１４と、吸入マフラー１４に接続され、冷媒を吸入マフラー１４に供給するための供給管１９とを備える。Embodiment 1.
FIG. 1 is an internal configuration diagram showing the inside of the compressor according to the first embodiment of the present invention. In the following description, as the compressor, a twin rotary type compressor 100 having two cylindrical cylinders in the compression mechanism portion will be described as an example. As shown in FIG. 1, the compressor 100 includes a closed container 1 having a compression mechanism unit 3 built therein. Further, the compressor 100 includes an electric motor unit 2 inside the closed container 1. Further, the compressor 100 is connected to the suction pipe 15 connected to the compression mechanism unit 3, the suction muffler 14 connected to the suction pipe 15, and the suction muffler 14, and supplies the refrigerant to the suction muffler 14. A tube 19 is provided.

密閉容器１は、有底円筒形状の下部密閉容器１３と、下部密閉容器１３の上部の開口を塞ぐ上部密閉容器１２とで構成されている。密閉容器１は、下部密閉容器１３と上部密閉容器１２との接続部分が溶接により固定され、密閉状態が保たれている。 The closed container 1 is composed of a bottom closed cylindrical lower closed container 13 and an upper closed container 12 that closes the upper opening of the lower closed container 13. In the closed container 1, the connecting portion between the lower closed container 13 and the upper closed container 12 is fixed by welding, and the closed state is maintained.

下部密閉容器１３には、吸入管１５が接続されており、吸入管１５には、後述する吸入マフラー１４が取り付けられている。吸入管１５は、圧縮機構部３に接続され、吸入マフラー１４を介して流入するガス冷媒を圧縮機構部３内に送り込むための接続管である。なお、下部密閉容器１３には、圧縮機構部３に供給される潤滑油が貯留される給油機構が設けられていてもよい。 A suction pipe 15 is connected to the lower closed container 13, and a suction muffler 14 described later is attached to the suction pipe 15. The suction pipe 15 is a connecting pipe connected to the compression mechanism unit 3 and for sending the gas refrigerant flowing in through the suction muffler 14 into the compression mechanism unit 3. The lower closed container 13 may be provided with an oil supply mechanism for storing the lubricating oil supplied to the compression mechanism unit 3.

上部密閉容器１２には、回転軸３１の軸延長線上に吐出管４が接続されている。吐出管４は、密閉容器１に取り付けられ、圧縮機構部３によって圧縮された冷媒を密閉容器１の外部に吐出するための管である。なお、吐出管の内径は常に一定の大きさに形成されている。また、吐出管４は、密閉容器１に設けられていればよく、必ずしも回転軸３１の軸延長線上に配設されていなくてもよい。上部密閉容器１２には、さらに密閉容器１内の電動機部２と電気的に接続するための気密端子１６と、気密端子１６を保護するためのカバーが取り付けられるロッド１７とが設けられている。 A discharge pipe 4 is connected to the upper closed container 12 on a shaft extension line of the rotating shaft 31. The discharge pipe 4 is a pipe attached to the closed container 1 and for discharging the refrigerant compressed by the compression mechanism unit 3 to the outside of the closed container 1. The inner diameter of the discharge pipe is always formed to have a constant size. Further, the discharge pipe 4 may be provided in the closed container 1 and may not necessarily be arranged on the axis extension line of the rotating shaft 31. The upper airtight container 12 is further provided with an airtight terminal 16 for electrically connecting to the electric motor portion 2 in the airtight container 1 and a rod 17 to which a cover for protecting the airtight terminal 16 is attached.

電動機部２は、下部密閉容器１３に固定された固定子２１と、固定子２１の内周側に回転自在に設けられた回転子２２とを備えている。回転子２２の中心部には回転軸３１が固定されている。固定子２１は、例えば、焼き嵌め、溶接など各種固定法により密閉容器１の下部密閉容器１３に固定されている。固定子２１は、リード線１８により気密端子１６と電気的に接続されている。 The electric motor unit 2 includes a stator 21 fixed to the lower airtight container 13 and a rotor 22 rotatably provided on the inner peripheral side of the stator 21. A rotating shaft 31 is fixed to the center of the rotor 22. The stator 21 is fixed to the lower closed container 13 of the closed container 1 by various fixing methods such as shrink fitting and welding. The stator 21 is electrically connected to the airtight terminal 16 by a lead wire 18.

図２は、本発明の実施の形態１に係る圧縮機の圧縮機構部を示す縦断面図である。図３は、図２のＡ−Ａ線断面図である。図４は、図２のＢ−Ｂ線断面図である。図２〜図４を用いて、圧縮機構部３の構成について説明する。なお、図３及び図４では、偏心軸部３１ｃと偏心軸部３１ｄとの図示を省略している。 FIG. 2 is a vertical cross-sectional view showing a compression mechanism portion of the compressor according to the first embodiment of the present invention. FIG. 3 is a cross-sectional view taken along the line AA of FIG. FIG. 4 is a cross-sectional view taken along the line BB of FIG. The configuration of the compression mechanism unit 3 will be described with reference to FIGS. 2 to 4. In addition, in FIGS. 3 and 4, the illustration of the eccentric shaft portion 31c and the eccentric shaft portion 31d is omitted.

圧縮機構部３は、密閉容器１に収容され、密閉容器１内に流入する冷媒を圧縮するものである。圧縮機構部３は、２つの円筒シリンダを有するツインロータリー式の圧縮機構であり、圧縮機構部３は、密閉容器１内において、電動機部２の下方に配置され、下部密閉容器１３に固定されている。圧縮機構部３は、回転軸３１と、主軸受３２と、副軸受３３と、第１の円筒シリンダ３４ａと、第１のローリングピストン３５ａと、第２の円筒シリンダ３４ｂと、第２のローリングピストン３５ｂと、仕切板３６と、を備えている。 The compression mechanism unit 3 is housed in the closed container 1 and compresses the refrigerant flowing into the closed container 1. The compression mechanism unit 3 is a twin rotary type compression mechanism having two cylindrical cylinders, and the compression mechanism unit 3 is arranged below the electric motor unit 2 in the airtight container 1 and fixed to the lower airtight container 13. There is. The compression mechanism 3 includes a rotating shaft 31, a main bearing 32, an auxiliary bearing 33, a first cylindrical cylinder 34a, a first rolling piston 35a, a second cylindrical cylinder 34b, and a second rolling piston. It includes a 35b and a partition plate 36.

回転軸３１は、電動機部２の回転子２２と連結されて電動機部２の回転力を圧縮機構部３に伝達する。回転軸３１は、電動機部２の回転子２２に固定される主軸部３１ａと、軸方向において主軸部３１ａと反対側に設けられている副軸部３１ｂと、を備える。また、回転軸３１は、主軸部３１ａと副軸部３１ｂとの間に設けられ、第１のローリングピストン３５ａに挿入される偏心軸部３１ｃと、第２のローリングピストン３５ｂに挿入される偏心軸部３１ｄと、を備える。偏心軸部３１ｃと偏心軸部３１ｄとは、所定の位相差（例えば、１８０°）を設けて配置されている。回転軸３１は、主軸部３１ａが主軸受３２により回転自在に支持され、副軸部３１ｂが副軸受３３により回転自在に支持されている。 The rotating shaft 31 is connected to the rotor 22 of the electric motor unit 2 and transmits the rotational force of the electric motor unit 2 to the compression mechanism unit 3. The rotating shaft 31 includes a main shaft portion 31a fixed to the rotor 22 of the electric motor portion 2 and an auxiliary shaft portion 31b provided on the side opposite to the main shaft portion 31a in the axial direction. Further, the rotating shaft 31 is provided between the main shaft portion 31a and the sub-shaft portion 31b, and the eccentric shaft portion 31c inserted into the first rolling piston 35a and the eccentric shaft inserted into the second rolling piston 35b. A unit 31d and the like. The eccentric shaft portion 31c and the eccentric shaft portion 31d are arranged with a predetermined phase difference (for example, 180 °). In the rotary shaft 31, the main shaft portion 31a is rotatably supported by the main bearing 32, and the sub-shaft portion 31b is rotatably supported by the sub-bearing 33.

主軸受３２は、第１の円筒シリンダ３４ａの両端部の一方（電動機部２側）の端面を閉塞する閉塞部材である。主軸受３２と、第１の円筒シリンダ３４ａとは別物品として成形され、組み立てられている。副軸受３３は、第２の円筒シリンダ３４ｂの両端部の一方（軸方向において電動機部２と反対側）の端面を閉塞する閉塞部材である。副軸受３３と、第２の円筒シリンダ３４ｂとは別物品として成形され、組み立てられている。 The main bearing 32 is a closing member that closes one end surface (on the motor portion 2 side) of both end portions of the first cylindrical cylinder 34a. The main bearing 32 and the first cylindrical cylinder 34a are molded and assembled as separate articles. The auxiliary bearing 33 is a closing member that closes one end surface of both ends of the second cylindrical cylinder 34b (the side opposite to the motor portion 2 in the axial direction). The auxiliary bearing 33 and the second cylindrical cylinder 34b are molded and assembled as separate articles.

第１の円筒シリンダ３４ａは、略円筒形状に形成され、回転軸３１の軸方向において、その略円筒形状の両端面が主軸受３２と仕切板３６とで閉塞されており、図３に示すように第１の円筒シリンダ３４ａの内部空間に密閉された室４０ａが形成されている。この室４０ａには、図２に示す回転軸３１の偏心軸部３１ｃと、偏心軸部３１ｃに回転自在に嵌合する第１のローリングピストン３５ａとが収容されている。また、図３に示すように第１の円筒シリンダ３４ａには、第１のベーン摺動溝４１ａが径方向に形成されている。この第１のベーン摺動溝４１ａ内に、第１のベーン３７ａが設けられている。また、圧縮機構部３の第１の円筒シリンダ３４ａには、冷媒を吸入するための第１の吸入ポート４２ａが設けられている。第１の吸入ポート４２ａは、第１の円筒シリンダ３４ａの径方向に形成されている。第１の吸入ポート４２ａは、前述した吸入管１５が接続されて、第１の円筒シリンダ３４ａの室４０ａ内に冷媒を導く経路となる。 The first cylindrical cylinder 34a is formed in a substantially cylindrical shape, and both end faces of the substantially cylindrical shape are closed by a main bearing 32 and a partition plate 36 in the axial direction of the rotating shaft 31, as shown in FIG. A sealed chamber 40a is formed in the internal space of the first cylindrical cylinder 34a. The chamber 40a houses an eccentric shaft portion 31c of the rotating shaft 31 shown in FIG. 2 and a first rolling piston 35a that rotatably fits into the eccentric shaft portion 31c. Further, as shown in FIG. 3, a first vane sliding groove 41a is formed in the first cylindrical cylinder 34a in the radial direction. A first vane 37a is provided in the first vane sliding groove 41a. Further, the first cylindrical cylinder 34a of the compression mechanism unit 3 is provided with a first suction port 42a for sucking the refrigerant. The first suction port 42a is formed in the radial direction of the first cylindrical cylinder 34a. The first suction port 42a is a path to which the suction pipe 15 described above is connected to guide the refrigerant into the chamber 40a of the first cylindrical cylinder 34a.

第１のローリングピストン３５ａは、図２に示す回転軸３１の偏心軸部３１ｃに装着され、回転軸３１が回転することによって室４０ａ内を偏心回転し、外周に押圧された第１のベーン３７ａと共に圧縮室を構成して、吸入動作と圧縮動作を行う。図３に戻り、第１のベーン３７ａは、付勢手段（図示せず）によって第１のローリングピストン３５ａに押接されている。第１のベーン３７ａは、偏心軸部３１ｃの回転に伴い、第１のローリングピストン３５ａに当接しながら、第１のベーン摺動溝４１ａ内を往復運動する。第１のベーン３７ａは、第１のベーン摺動溝４１ａ内を往復運動して、第１の円筒シリンダ３４ａと第１のローリングピストン３５ａとの間に形成される空間を吸入室と圧縮室とに仕切っている。 The first rolling piston 35a is mounted on the eccentric shaft portion 31c of the rotating shaft 31 shown in FIG. 2, and the rotation of the rotating shaft 31 causes the eccentric rotation in the chamber 40a and the first vane 37a pressed to the outer periphery. A compression chamber is formed together with the suction operation and the compression operation. Returning to FIG. 3, the first vane 37a is pressed against the first rolling piston 35a by an urging means (not shown). The first vane 37a reciprocates in the first vane sliding groove 41a while abutting on the first rolling piston 35a as the eccentric shaft portion 31c rotates. The first vane 37a reciprocates in the first vane sliding groove 41a to form a space formed between the first cylindrical cylinder 34a and the first rolling piston 35a as a suction chamber and a compression chamber. It is divided into.

第２の円筒シリンダ３４ｂは、略円筒形状に形成され、回転軸３１の軸方向において、その略円筒形状の両端面が副軸受３３と仕切板３６とで閉塞されており、図４に示すように第２の円筒シリンダ３４ｂの内部空間に密閉された室４０ｂが形成されている。この室４０ｂには、図２に示す回転軸３１の偏心軸部３１ｄと、偏心軸部３１ｄに回転自在に嵌合する第２のローリングピストン３５ｂとが収容されている。また、図４に示すように第２の円筒シリンダ３４ｂには、第２のベーン摺動溝４１ｂが径方向に形成されている。この第２のベーン摺動溝４１ｂ内に、第２のベーン３７ｂが設けられている。また、圧縮機構部３の第２の円筒シリンダ３４ｂには、冷媒を吸入するための第２の吸入ポート４２ｂが設けられている。第２の吸入ポート４２ｂは、第２の円筒シリンダ３４ｂの径方向に形成されている。第２の吸入ポート４２ｂは、前述した吸入管１５が接続されて、第２の円筒シリンダ３４ｂの室４０ｂ内に冷媒を導く経路となる。 The second cylindrical cylinder 34b is formed in a substantially cylindrical shape, and both end faces of the substantially cylindrical shape are closed by an auxiliary bearing 33 and a partition plate 36 in the axial direction of the rotating shaft 31, as shown in FIG. A sealed chamber 40b is formed in the internal space of the second cylindrical cylinder 34b. The chamber 40b accommodates an eccentric shaft portion 31d of the rotating shaft 31 shown in FIG. 2 and a second rolling piston 35b that is rotatably fitted to the eccentric shaft portion 31d. Further, as shown in FIG. 4, a second vane sliding groove 41b is formed in the second cylindrical cylinder 34b in the radial direction. A second vane 37b is provided in the second vane sliding groove 41b. Further, the second cylindrical cylinder 34b of the compression mechanism unit 3 is provided with a second suction port 42b for sucking the refrigerant. The second suction port 42b is formed in the radial direction of the second cylindrical cylinder 34b. The second suction port 42b is connected to the suction pipe 15 described above and serves as a path for guiding the refrigerant into the chamber 40b of the second cylindrical cylinder 34b.

第２のローリングピストン３５ｂは、図２に示す回転軸３１の偏心軸部３１ｄに装着され、回転軸３１が回転することによって室４０ｂ内を偏心回転し、外周に押圧された第２のベーン３７ｂと共に圧縮室を構成して、吸入動作と圧縮動作を行う。図４に戻り、第２のベーン３７ｂは、付勢手段（図示せず）によって第２のローリングピストン３５ｂに押接されている。第２のベーン３７ｂは、偏心軸部３１ｄの回転に伴い、第２のローリングピストン３５ｂに当接しながら、第２のベーン摺動溝４１ｂ内を往復運動する。第２のベーン３７ｂは、第２のベーン摺動溝４１ｂ内を往復運動して、第２の円筒シリンダ３４ｂと第２のローリングピストン３５ｂとの間に形成される空間を吸入室と圧縮室とに仕切っている。 The second rolling piston 35b is mounted on the eccentric shaft portion 31d of the rotating shaft 31 shown in FIG. 2, and the rotation of the rotating shaft 31 causes the eccentric rotation in the chamber 40b and the second vane 37b pressed to the outer periphery. A compression chamber is formed together with the suction operation and the compression operation. Returning to FIG. 4, the second vane 37b is pressed against the second rolling piston 35b by an urging means (not shown). The second vane 37b reciprocates in the second vane sliding groove 41b while abutting on the second rolling piston 35b as the eccentric shaft portion 31d rotates. The second vane 37b reciprocates in the second vane sliding groove 41b to form a space formed between the second cylindrical cylinder 34b and the second rolling piston 35b as a suction chamber and a compression chamber. It is divided into.

仕切板３６は、図２に示すように、第１の円筒シリンダ３４ａと第２の円筒シリンダ３４ｂとの間に設けられている。仕切板３６は、回転軸３１の軸方向において、第１の円筒シリンダ３４ａの両端部の一方（電動機部２と反対側）の端面と、第２の円筒シリンダ３４ｂの両端部の一方（電動機部２側）の端面とを閉塞する閉塞部材である。 As shown in FIG. 2, the partition plate 36 is provided between the first cylindrical cylinder 34a and the second cylindrical cylinder 34b. The partition plate 36 has one end face of one end of the first cylindrical cylinder 34a (opposite side of the electric motor portion 2) and one end surface of both end portions of the second cylindrical cylinder 34b (electric motor portion) in the axial direction of the rotating shaft 31. It is a closing member that closes the end face of (2 side).

吸入マフラー１４は、圧縮機構部３に吸入される冷媒の流動騷音を減少させるものである。図１に示すように、吸入マフラー１４は、吸入管１５に接続され、吸入管１５を介して圧縮機構部３に接続されている。吸入マフラー１４は、吸入マフラー１４の頂部１４ａに、吸入マフラー１４の内部空間Ｍ１に冷媒を供給するための供給管１９が接続されており、吸入マフラー１４の底部１４ｂに、吸入管１５が接続されている。吸入マフラー１４の頂部１４ａに設けられた吸入マフラー１４と供給管１９との接続部を供給管接続部１４ａ１と称し、吸入マフラー１４の底部１４ｂに設けられた吸入マフラー１４と吸入管１５との接続部を吸入管接続部１４ｂ１と称する。吸入マフラー１４の内部空間Ｍ１において、供給管接続部１４ａ１と、吸入管接続部１４ｂ１との間の距離を距離Ｌと称する。 The suction muffler 14 reduces the flow noise of the refrigerant sucked into the compression mechanism unit 3. As shown in FIG. 1, the suction muffler 14 is connected to the suction pipe 15 and is connected to the compression mechanism unit 3 via the suction pipe 15. In the suction muffler 14, a supply pipe 19 for supplying a refrigerant to the internal space M1 of the suction muffler 14 is connected to the top 14a of the suction muffler 14, and a suction pipe 15 is connected to the bottom 14b of the suction muffler 14. ing. The connection between the suction muffler 14 and the supply pipe 19 provided on the top 14a of the suction muffler 14 is referred to as the supply pipe connection 14a1, and the connection between the suction muffler 14 and the suction pipe 15 provided on the bottom 14b of the suction muffler 14 The portion is referred to as a suction pipe connecting portion 14b1. In the internal space M1 of the suction muffler 14, the distance between the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 is referred to as a distance L.

次に、上記のように構成された圧縮機１００の動作について説明する。圧縮機１００は、電動機部２が駆動することによって、回転軸３１が回転する。回転軸３１が回転することにより、回転軸３１の偏心軸部３１ｃ及び偏心軸部３１ｄが回転する。偏心軸部３１ｃに取り付けられた第１のローリングピストン３５ａは、第１の円筒シリンダ３４ａ内で偏芯回転し、偏心軸部３１ｄに取り付けられた第２のローリングピストン３５ｂは、第２の円筒シリンダ３４ｂ内で偏芯回転する。 Next, the operation of the compressor 100 configured as described above will be described. In the compressor 100, the rotating shaft 31 is rotated by driving the electric motor unit 2. As the rotating shaft 31 rotates, the eccentric shaft portion 31c and the eccentric shaft portion 31d of the rotating shaft 31 rotate. The first rolling piston 35a attached to the eccentric shaft portion 31c rotates eccentrically in the first cylindrical cylinder 34a, and the second rolling piston 35b attached to the eccentric shaft portion 31d is a second cylindrical cylinder. Eccentric rotation within 34b.

第１のローリングピストン３５ａが第１の円筒シリンダ３４ａ内で回転すると、圧縮機１００外の冷媒回路から供給管１９を通じて吸入マフラー１４に供給された低圧の冷媒が吸入管１５から第１の円筒シリンダ３４ａ内に供給される。また、第２のローリングピストン３５ｂが第２の円筒シリンダ３４ｂ内で回転すると、圧縮機１００外の冷媒回路から供給管１９を通じて吸入マフラー１４に供給された低圧の冷媒が吸入管１５から第２の円筒シリンダ３４ｂ内に供給される。 When the first rolling piston 35a rotates in the first cylindrical cylinder 34a, the low-pressure refrigerant supplied from the refrigerant circuit outside the compressor 100 to the suction muffler 14 through the supply pipe 19 is transferred from the suction pipe 15 to the first cylindrical cylinder. It is supplied in 34a. Further, when the second rolling piston 35b rotates in the second cylindrical cylinder 34b, the low-pressure refrigerant supplied from the refrigerant circuit outside the compressor 100 to the suction muffler 14 through the supply pipe 19 is transferred from the suction pipe 15 to the second. It is supplied into the cylindrical cylinder 34b.

回転軸３１の回転により、回転軸３１の偏心軸部３１ｃを覆う第１のローリングピストン３５ａが、第１の円筒シリンダ３４ａ内にて偏芯回転することで、第１のベーン３７ａにより区切られた第１の円筒シリンダ３４ａ内の圧縮室容量が連続的に変化する。すなわち、第１のローリングピストン３５ａが回転することによって、室４０ａにおいて、第１の円筒シリンダ３４ａと、第１のローリングピストン３５ａと、第１のベーン３７ａとで囲まれた空間の体積が小さくなって冷媒が圧縮される。 Due to the rotation of the rotating shaft 31, the first rolling piston 35a covering the eccentric shaft portion 31c of the rotating shaft 31 is eccentrically rotated in the first cylindrical cylinder 34a, and is separated by the first vane 37a. The compression chamber capacity in the first cylindrical cylinder 34a changes continuously. That is, as the first rolling piston 35a rotates, the volume of the space surrounded by the first cylindrical cylinder 34a, the first rolling piston 35a, and the first vane 37a in the chamber 40a becomes smaller. The refrigerant is compressed.

また、回転軸３１の回転により、回転軸３１の偏心軸部３１ｄを覆う第２のローリングピストン３５ｂが、第２の円筒シリンダ３４ｂ内にて偏芯回転することで、第２のベーン３７ｂにより区切られた第２の円筒シリンダ３４ｂ内の圧縮室容量が連続的に変化する。すなわち、第２のローリングピストン３５ｂが回転することによって、室４０ｂにおいて、第２の円筒シリンダ３４ｂと、第２のローリングピストン３５ｂと、第２のベーン３７ｂとで囲まれた空間の体積が小さくなって冷媒が圧縮される。 Further, due to the rotation of the rotating shaft 31, the second rolling piston 35b covering the eccentric shaft portion 31d of the rotating shaft 31 is eccentrically rotated in the second cylindrical cylinder 34b, and is separated by the second vane 37b. The capacity of the compression chamber in the second cylindrical cylinder 34b is continuously changed. That is, the rotation of the second rolling piston 35b reduces the volume of the space surrounded by the second cylindrical cylinder 34b, the second rolling piston 35b, and the second vane 37b in the chamber 40b. The refrigerant is compressed.

圧縮室には所定の圧力以上になると解放される吐出弁（図示せず）が設けられており、高圧の冷媒ガスは所定の圧力以上になると室４０ａ及び室４０ｂから密閉容器１内へ吐出される。圧縮された冷媒ガスは電動機部２のすきまを通り、吐出管４から圧縮機１００外の冷媒回路内に吐出される。密閉容器１の下部には冷凍機油が蓄えられ、回転軸３１の給油機構（図示せず）により各部に油を供給することで圧縮機構部３の潤滑を保っている。なお、圧縮機に封入する冷凍機油に、冷凍機油全体の重量に対して０．５〜２［ｗｔ％］の極圧添加剤を添加してもよい。これにより、Ｒ１１２３冷媒動作時の回転軸と軸受の焼き付きをさらに抑制することができる。 The compression chamber is provided with a discharge valve (not shown) that is released when the pressure exceeds a predetermined pressure, and the high-pressure refrigerant gas is discharged from the chamber 40a and the chamber 40b into the closed container 1 when the pressure exceeds a predetermined pressure. To. The compressed refrigerant gas passes through the gap of the electric motor unit 2 and is discharged from the discharge pipe 4 into the refrigerant circuit outside the compressor 100. Refrigerating machine oil is stored in the lower part of the closed container 1, and the lubrication of the compression mechanism portion 3 is maintained by supplying oil to each portion by the oil supply mechanism (not shown) of the rotating shaft 31. An extreme pressure additive of 0.5 to 2 [wt%] may be added to the refrigerating machine oil sealed in the compressor with respect to the total weight of the refrigerating machine oil. As a result, seizure of the rotating shaft and the bearing during the operation of the R1123 refrigerant can be further suppressed.

次に、上述し圧縮機１００に用いられる動作冷媒の特性について述べる。圧縮機１００の動作冷媒は、Ｒ３２冷媒とハイドロフルオロオレフィンの１種であるＲ１２３４ｙｆ冷媒とを混合した混合冷媒を用いる。なお、混合冷媒のＧＷＰは５００未満であることが望ましく、１００未満であることがさらに望ましい。表１に、Ｒ１２３４ｙｆ冷媒と従来の冷媒として用いられているＲ３２冷媒の物性値について示す。圧縮機の運転条件は、一般的な圧縮機の吸入条件の内、冷媒の音速が最小のときの条件（凝縮温度ＣＴ＝−１０［℃］、スーパーヒートＳＨ＝０［ｄｅｇ］）と、冷媒の音速が最大のときの条件（凝縮温度ＣＴ＝１５［℃］、スーパーヒートＳＨ＝１０［ｄｅｇ］）とを考慮したものである。 Next, the characteristics of the operating refrigerant used in the compressor 100 described above will be described. As the operating refrigerant of the compressor 100, a mixed refrigerant in which R32 refrigerant and R1234yf refrigerant, which is one of hydrofluoroolefins, are mixed is used. The GWP of the mixed refrigerant is preferably less than 500, and more preferably less than 100. Table 1 shows the physical property values of the R1234yf refrigerant and the R32 refrigerant used as the conventional refrigerant. The operating conditions of the compressor are the conditions when the sound velocity of the refrigerant is the minimum (condensation temperature CT = -10 [° C.], super heat SH = 0 [deg]) among the general compressor suction conditions, and the refrigerant. The conditions when the sound velocity of the above is maximum (condensation temperature CT = 15 [° C.], super heat SH = 10 [deg]) are taken into consideration.

Figure 0006840173
Figure 0006840173

表１から、Ｒ１２３４ｙｆ冷媒は、従来の冷媒であるＲ３２冷媒と比較して音速が小さい事がわかる。冷媒の音速ｃ［ｍ／ｓ］が小さくなると、吸入マフラー１４の共鳴周波数ｆ［Ｈｚ］が、低周波数帯に遷移することになる。低周波数帯の動作音は、圧縮機の周囲に取り付ける遮音材の効果が薄く、圧縮機の静音性が悪化する。そのため、Ｒ１２３４ｙｆ冷媒を動作冷媒として用いる圧縮機は、従来の冷媒であるＲ３２冷媒と比較して圧縮機の静音性が悪化する場合がある。 From Table 1, it can be seen that the sound velocity of the R1234yf refrigerant is lower than that of the conventional refrigerant R32 refrigerant. When the sound velocity c [m / s] of the refrigerant becomes small, the resonance frequency f [Hz] of the suction muffler 14 shifts to the low frequency band. As for the operating noise in the low frequency band, the effect of the sound insulating material attached around the compressor is weak, and the quietness of the compressor deteriorates. Therefore, in a compressor using the R1234yf refrigerant as the operating refrigerant, the quietness of the compressor may be deteriorated as compared with the conventional refrigerant R32 refrigerant.

一般的に、音の共鳴点では大きな騒音が発生する。そこで、共鳴以外の圧縮機の騒音が生じている圧縮機の騒音が小さい周波数に共鳴点を配置させることで圧縮機全体の騒音を低減させることができる。また、遮音材の効果が発揮されやすい周波数に共鳴点を配置させることで圧縮機全体の騒音を低減させることができる。 Generally, loud noise is generated at the resonance point of sound. Therefore, the noise of the entire compressor can be reduced by arranging the resonance points at frequencies where the noise of the compressor other than the resonance is generated. Further, the noise of the entire compressor can be reduced by arranging the resonance points at frequencies at which the effect of the sound insulating material is likely to be exhibited.

図５は、周波数帯域における一般的な圧縮機単体の騒音を示す折れ線図である。図５で示す圧縮機の運転条件は、Ｒ３２冷媒の単体冷媒を動作冷媒とし、凝縮温度を５２［℃］、蒸発温度を５［℃］、圧縮機の回転数を６０［ｒｐｓ］としたものである。図５に示すように、圧縮機単体の騒音［ｄＢ］は、一般に、９００［Ｈｚ］未満ではほぼ単調増加し、９００［Ｈｚ］以上で横ばいとなる。したがって、圧縮機１００の共鳴周波数ｆ［Ｈｚ］を９００［Ｈｚ］未満にすることで、圧縮機１００全体の騒音を低減することができる。 FIG. 5 is a line chart showing the noise of a general compressor alone in the frequency band. The operating conditions of the compressor shown in FIG. 5 are that the single refrigerant of the R32 refrigerant is used as the operating refrigerant, the condensation temperature is 52 [° C.], the evaporation temperature is 5 [° C.], and the rotation speed of the compressor is 60 [rps]. Is. As shown in FIG. 5, the noise [dB] of the compressor alone generally increases almost monotonously below 900 [Hz] and becomes flat above 900 [Hz]. Therefore, by setting the resonance frequency f [Hz] of the compressor 100 to less than 900 [Hz], the noise of the entire compressor 100 can be reduced.

図６は、周波数帯域における遮音材の効果を示す折れ線図である。図６に示すように、遮音材の効果［ｄＢ］は、一般に、１０００［Ｈｚ］以上で効果が大きくなる。したがって、共鳴周波数ｆ［Ｈｚ］を１０００［Ｈｚ］より大きくすることで、遮音材の効果を適用することができ、圧縮機１００全体の騒音を低減することができる。 FIG. 6 is a polygonal diagram showing the effect of the sound insulating material in the frequency band. As shown in FIG. 6, the effect [dB] of the sound insulating material is generally large at 1000 [Hz] or higher. Therefore, by making the resonance frequency f [Hz] larger than 1000 [Hz], the effect of the sound insulating material can be applied, and the noise of the entire compressor 100 can be reduced.

図７は、周波数帯域における遮音材を備えた一般的な圧縮機単体の騒音を示す折れ線図である。図７に示すように、圧縮機単体の騒音［ｄＢ］は、一般に、９００［Ｈｚ］以上１０００［Ｈｚ］以下の範囲で最大となる。したがって、圧縮機１００の共鳴周波数ｆ［Ｈｚ］を９００［Ｈｚ］未満にするか、あるいは、１０００［Ｈｚ］より大きくすることで圧縮機１００全体の騒音を低減することができる。 FIG. 7 is a polygonal diagram showing the noise of a general compressor alone provided with a sound insulating material in the frequency band. As shown in FIG. 7, the noise [dB] of the compressor alone is generally maximum in the range of 900 [Hz] or more and 1000 [Hz] or less. Therefore, the noise of the compressor 100 as a whole can be reduced by setting the resonance frequency f [Hz] of the compressor 100 to less than 900 [Hz] or making it larger than 1000 [Hz].

ここで、吸入マフラー１４のマフラー効果Ｅ［ｄＢ］は、吸入マフラー１４の内部空間Ｍ１における供給管接続部１４ａ１と吸入管接続部１４ｂ１との間の距離を距離Ｌ「ｍｍ」、吸入周波数をｆ［Ｈｚ］、音速をｃ［ｍｍ／ｓ］とすると下記式１で表される。

Figure 0006840173
Here, the muffler effect E [dB] of the suction muffler 14 is such that the distance between the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 in the internal space M1 of the suction muffler 14 is the distance L "mm" and the suction frequency is f. When [Hz] and the sound velocity are c [mm / s], it is expressed by the following equation 1.
Figure 0006840173

吸入マフラー１４のマフラー効果Ｅ［ｄＢ］が小さくなる共鳴周波数ｆ［Ｈｚ］は、ｓｉｎ（＊）の＊がπ、２π、３π・・・のときである。そこで、吸入マフラー１４のマフラー効果Ｅ［ｄＢ］が小さくなる共鳴周波数ｆ［Ｈｚ］は下記式２で表される。なお、式２において、ｎはｎ次の共鳴を表す。

Figure 0006840173
The resonance frequency f [Hz] at which the muffler effect E [dB] of the suction muffler 14 becomes small is when the * of sin (*) is π, 2π, 3π, and so on. Therefore, the resonance frequency f [Hz] at which the muffler effect E [dB] of the suction muffler 14 becomes small is expressed by the following equation 2. In Equation 2, n represents nth-order resonance.
Figure 0006840173

図８は、周波数帯域におけるマフラー効果Ｅ［ｄＢ］を示す折れ線図である。図８で示す圧縮機の運転条件は、凝縮温度ＣＴを５２［℃］、蒸発温度ＥＴを−１０［℃］、サブクールＳＣを５［ｄｅｇ］、スーパーヒートＳＨを０［ｄｅｇ］、吸入マフラー１４の内部空間Ｍ１における供給管接続部１４ａ１と吸入管接続部１４ｂ１との間の距離Ｌ「ｍｍ」を３００［ｍｍ］としたものである。図８に示す実線は、Ｒ１２３４ｙｆ冷媒のマフラー効果Ｅ［ｄＢ］を表すものである。なお、Ｒ１２３４ｙｆ冷媒の音速ｃ［ｍ／ｓ］は、１３５．８［ｍ／ｓ］である。図８に示す破線は、Ｒ３２冷媒のマフラー効果Ｅ［ｄＢ］を表すものである。なお、Ｒ３２冷媒の音速ｃ［ｍ／ｓ］は、２１１．５［ｍ／ｓ］である。 FIG. 8 is a line chart showing the muffler effect E [dB] in the frequency band. The operating conditions of the compressor shown in FIG. 8 are: condensation temperature CT is 52 [° C.], evaporation temperature ET is -10 [° C.], subcool SC is 5 [deg], superheat SH is 0 [deg], and suction muffler 14 The distance L "mm" between the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 in the internal space M1 of the above is set to 300 [mm]. The solid line shown in FIG. 8 represents the muffler effect E [dB] of the R1234yf refrigerant. The sound velocity c [m / s] of the R1234yf refrigerant is 135.8 [m / s]. The broken line shown in FIG. 8 represents the muffler effect E [dB] of the R32 refrigerant. The sound velocity c [m / s] of the R32 refrigerant is 211.5 [m / s].

一般の吸入マフラーは、吸入マフラーの内部空間における供給管接続部と吸入管接続部との間の距離Ｌ「ｍｍ」が、１００［ｍｍ］＜Ｌ＜３００［ｍｍ］の範囲にあるように形成されている。そこで、Ｒ１２３４ｙｆ冷媒とＲ３２冷媒との混合冷媒を圧縮機の動作冷媒として使用するときには、吸入マフラーの内部空間における供給管接続部と吸入管接続部との間の距離Ｌ「ｍｍ」が、１００［ｍｍ］＜Ｌ＜３００［ｍｍ］にあることを考慮すればよい。そして、吸入マフラーの内部空間における供給管接続部と吸入管接続部との間の距離Ｌ「ｍｍ」が、１００［ｍｍ］＜Ｌ＜３００［ｍｍ］にあることを考慮すると、共鳴周波数ｆ［Ｈｚ］は、騒音の生成に影響を与える２次又は３次又は４次の共鳴周波数を考慮すればよい。 The general suction muffler is formed so that the distance L "mm" between the supply pipe connection portion and the suction pipe connection portion in the internal space of the suction muffler is in the range of 100 [mm] <L <300 [mm]. Has been done. Therefore, when a mixed refrigerant of R1234yf refrigerant and R32 refrigerant is used as the operating refrigerant of the compressor, the distance L "mm" between the supply pipe connection portion and the suction pipe connection portion in the internal space of the suction muffler is 100 [. It may be considered that mm] <L <300 [mm]. Considering that the distance L "mm" between the supply pipe connection portion and the suction pipe connection portion in the internal space of the suction muffler is 100 [mm] <L <300 [mm], the resonance frequency f [ Hz] may take into account the second-order, third-order, or fourth-order resonance frequencies that affect the generation of noise.

図９は、冷媒全体に対するＲ１２３４ｙｆの割合α［ｗｔ％］と、音速ｃ［ｍｍ／ｓ］との関係を表す図である。図９において、実線はｃ１＝−７７６α＋２１５７００を表す。また、破線はｃ２＝−７５７α＋２１１５００を表す。実線で表されている音速ｃ１［ｍｍ／ｓ］は、上記の表１に表す冷媒の音速が最大のときの圧縮機の運転条件に基づく音速である。また、破線で表されている音速ｃ２［ｍｍ／ｓ］は、上記の表１に表す冷媒の音速が最小のときの圧縮機の運転条件に基づく音速である。 FIG. 9 is a diagram showing the relationship between the ratio α [wt%] of R1234yf to the entire refrigerant and the speed of sound c [mm / s]. In FIG. 9, the solid line represents c1 = −776α + 215700. The broken line represents c2 = -757α + 211500. The sound velocity c1 [mm / s] represented by the solid line is the sound velocity based on the operating conditions of the compressor when the sound velocity of the refrigerant shown in Table 1 above is maximum. The sound velocity c2 [mm / s] represented by the broken line is the sound velocity based on the operating conditions of the compressor when the sound velocity of the refrigerant shown in Table 1 above is the minimum.

上記の記載に基づき、２次又は３次又は４次（ｎ=２、３、４）の共鳴周波数ｆ「Ｈｚ」が、ｆ＜９００［Ｈｚ］又は１０００［Ｈｚ］＜ｆとなる条件式は以下のように定められる。 Based on the above description, the conditional expression in which the resonance frequency f "Hz" of the second, third or fourth order (n = 2, 3, 4) is f <900 [Hz] or 1000 [Hz] <f is It is defined as follows.

圧縮機１００は、吸入マフラー１４の内部空間Ｍ１における供給管接続部１４ａ１と吸入管接続部１４ｂ１との間の距離Ｌ「ｍｍ」が、１００［ｍｍ］＜Ｌ＜３００［ｍｍ］の範囲に形成されており、Ｒ１２３４ｙｆ冷媒とＲ３２冷媒とを主成分として含む混合冷媒を動作冷媒とし、動作冷媒全体に対するＲ１２３４ｙｆの割合をα［ｗｔ％］としたとき、下記の式３〜式６のいずれか１つの式を満足する。

Figure 0006840173
Figure 0006840173
Figure 0006840173
Figure 0006840173
 In the compressor 100, the distance L "mm" between the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 in the internal space M1 of the suction muffler 14 is formed in the range of 100 [mm] <L <300 [mm]. When the mixed refrigerant containing the R1234yf refrigerant and the R32 refrigerant as the main components is used as the operating refrigerant and the ratio of R1234yf to the entire operating refrigerant is α [wt%], any one of the following equations 3 to 6 is used. Satisfy one formula.
Figure 0006840173
Figure 0006840173
Figure 0006840173
Figure 0006840173

式３は、冷媒の音速が音速ｃ２の場合に、２次の共鳴周波数ｆ［Ｈｚ］が、１０００［Ｈｚ］より大きい範囲に位置していることを表している。式４は、冷媒の音速が音速ｃ１の場合に、２次の共鳴周波数ｆ［Ｈｚ］が、９００［Ｈｚ］未満の範囲に位置し、かつ、冷媒の音速が音速ｃ２の場合に、３次の共鳴周波数ｆ［Ｈｚ］が、１０００［Ｈｚ］より大きい範囲に位置していることを表している。式５は、冷媒の音速が音速ｃ１の場合に、３次の共鳴周波数ｆ［Ｈｚ］が、９００［Ｈｚ］未満の範囲に位置し、かつ、冷媒の音速が音速ｃ２の場合に、４次の共鳴周波数ｆ［Ｈｚ］が、１０００［Ｈｚ］より大きい範囲に位置していることを表している。式６は、冷媒の音速が音速ｃ１の場合に、共鳴周波数ｆ［Ｈｚ］が、９００［Ｈｚ］未満の範囲に位置することを表している。 Equation 3 represents that the second-order resonance frequency f [Hz] is located in a range larger than 1000 [Hz] when the sound velocity of the refrigerant is the speed of sound c2. In Equation 4, when the sound velocity of the refrigerant is sound velocity c1, the secondary resonance frequency f [Hz] is located in the range of less than 900 [Hz], and when the sound velocity of the refrigerant is sound velocity c2, the third order is Indicates that the resonance frequency f [Hz] of is located in a range larger than 1000 [Hz]. In Equation 5, when the sound velocity of the refrigerant is sound velocity c1, the third-order resonance frequency f [Hz] is located in the range of less than 900 [Hz], and when the sound velocity of the refrigerant is sound velocity c2, the fourth order is Indicates that the resonance frequency f [Hz] of is located in a range larger than 1000 [Hz]. Equation 6 represents that the resonance frequency f [Hz] is located in the range of less than 900 [Hz] when the sound velocity of the refrigerant is the speed of sound c1.

圧縮機１００は、Ｒ１２３４ｙｆ冷媒の割合α［ｗｔ％］と、吸入マフラー１４の内部空間Ｍ１における供給管接続部１４ａ１と吸入管接続部１４ｂ１との間の距離Ｌ「ｍｍ」が、上記の式３〜式６のいずれか１つの式を満足することにより、圧縮機の騒音が小さい周波数又は遮音材の効果が発揮されやすい周波数に共鳴点を配置させることができる。そのため、圧縮機は、吸入マフラーと冷媒動作音との共鳴による騒音を効果的に抑制することができる。その結果、ハイドロフルオロオレフィンを動作冷媒とした圧縮機の静音性を向上させることができる。 In the compressor 100, the ratio α [wt%] of the R1234yf refrigerant and the distance L “mm” between the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 in the internal space M1 of the suction muffler 14 are the above equation 3 By satisfying any one of the equations (6) to (6), the resonance point can be arranged at a frequency where the noise of the compressor is small or a frequency at which the effect of the sound insulating material is easily exhibited. Therefore, the compressor can effectively suppress the noise caused by the resonance between the suction muffler and the operating noise of the refrigerant. As a result, the quietness of the compressor using hydrofluoroolefin as the operating refrigerant can be improved.

実施の形態２.
図１０は、吸入マフラーの概略化した側面図である。図１１は、吸入マフラーの概略化した平面図である。図１〜図９の圧縮機と同一の構成を有する部位には同一の符号を付してその説明を省略する。供給管接続部１４ａ１と吸入管接続部１４ｂ１との配設位置について特定する実施の形態２を説明する。図１０及び図１１に示すように、供給管接続部１４ａ１と吸入管接続部１４ｂ１の少なくとも一方が、吸入マフラー１４の長手方向軸Ｙに対して偏心するように配設されている。Embodiment 2.
FIG. 10 is a schematic side view of the inhalation muffler. FIG. 11 is a schematic plan view of the suction muffler. Parts having the same configuration as the compressor of FIGS. 1 to 9 are designated by the same reference numerals, and the description thereof will be omitted. The second embodiment for specifying the arrangement position of the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 will be described. As shown in FIGS. 10 and 11, at least one of the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 is arranged so as to be eccentric with respect to the longitudinal axis Y of the suction muffler 14.

図１２は、吸入マフラーの変形例の概略化した平面図である。図１２は、供給管接続部１４ａ１又は吸入管接続部１４ｂ１が複数配設されている場合を示すものである。供給管接続部１４ａ１が複数配設されている場合には、各供給管接続部１４ａ１の中心を結ぶ線分Ｐの法線方向Ｎに、線分Ｐの中心点Ｐ１を偏心させて配置する。また、吸入管接続部１４ｂ１が複数配設されている場合には、各吸入管接続部１４ｂ１の中心を結ぶ線分Ｑの法線方向Ｎに、線分Ｑの中心点Ｑ１を偏心させて配置する。 FIG. 12 is a schematic plan view of a modified example of the suction muffler. FIG. 12 shows a case where a plurality of supply pipe connecting portions 14a1 or suction pipe connecting portions 14b1 are arranged. When a plurality of supply pipe connecting portions 14a1 are arranged, the center point P1 of the line segment P is arranged eccentrically in the normal direction N of the line segment P connecting the centers of the supply pipe connecting portions 14a1. When a plurality of suction pipe connecting portions 14b1 are arranged, the center point Q1 of the line segment Q is eccentrically arranged in the normal direction N of the line segment Q connecting the centers of the suction pipe connecting portions 14b1. To do.

圧縮機１００は、吸入マフラーと冷媒動作音との共鳴による騒音を効果的に抑制するために、Ｒ１２３４ｙｆ冷媒の割合α［ｗｔ％］によっては吸入マフラー１４の底部１４ｂと頂部１４ａの長さを大きくすることで距離Ｌ「ｍｍ」を確保する場合がある。しかし、吸入マフラー１４の底部１４ｂと頂部１４ａの長さは、実質的には圧縮機１００を搭載する冷凍サイクル装置の内部空間等によって制約を受ける場合がある。そこで、供給管接続部１４ａ１と吸入管接続部１４ｂ１の少なくとも一方が、吸入マフラー１４の長手方向軸Ｙに対して偏心するように配設するものである。供給管接続部１４ａ１と吸入管接続部１４ｂ１の少なくとも一方が、吸入マフラー１４の長手方向軸Ｙに対して偏心することで適切な距離Ｌ「ｍｍ」の長さを確保することができる。 In the compressor 100, in order to effectively suppress the noise caused by the resonance between the suction muffler and the operating noise of the refrigerant, the lengths of the bottom 14b and the top 14a of the suction muffler 14 are increased depending on the ratio α [wt%] of the R1234yf refrigerant. By doing so, the distance L "mm" may be secured. However, the lengths of the bottom 14b and the top 14a of the suction muffler 14 may be substantially restricted by the internal space of the refrigeration cycle device on which the compressor 100 is mounted. Therefore, at least one of the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 is arranged so as to be eccentric with respect to the longitudinal axis Y of the suction muffler 14. An appropriate distance L "mm" can be secured by eccentricity of at least one of the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 with respect to the longitudinal axis Y of the suction muffler 14.

また、圧縮機１００は、Ｒ１２３４ｙｆ冷媒の割合α［ｗｔ％］と、吸入マフラー１４の内部空間Ｍ１における供給管接続部１４ａ１と吸入管接続部１４ｂ１との間の距離Ｌ「ｍｍ」が、上記の式３〜式６のいずれか１つの式を満足することにより、圧縮機の騒音が小さい周波数又は遮音材の効果が発揮されやすい周波数に共鳴点を配置させることができる。そのため、圧縮機は、吸入マフラーと冷媒動作音との共鳴による騒音を効果的に抑制することができる。その結果、ハイドロフルオロオレフィンを動作冷媒とした圧縮機の静音性を向上させることができる。 Further, in the compressor 100, the ratio α [wt%] of the R1234yf refrigerant and the distance L “mm” between the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 in the internal space M1 of the suction muffler 14 are as described above. By satisfying any one of the formulas 3 to 6, the resonance point can be arranged at a frequency where the noise of the compressor is small or a frequency at which the effect of the sound insulating material is easily exhibited. Therefore, the compressor can effectively suppress the noise caused by the resonance between the suction muffler and the operating noise of the refrigerant. As a result, the quietness of the compressor using hydrofluoroolefin as the operating refrigerant can be improved.

図１３は、吸入マフラーの他の変形例の概略化した平面図である。図１３に示すように、圧縮機１００は、吸入マフラー１４が平面視で長円形状に形成されており、吸入マフラー１４の長円形状の長軸Ｊに沿って、供給管接続部１４ａ１と吸入管接続部１４ｂ１の少なくとも一方が配設されているものである。あるいは、圧縮機１００は、吸入マフラー１４が平面視で長円形状に形成されており、長円形状の長軸Ｊに沿って、供給管接続部１４a１と吸入管接続部１４ｂ１とが並んで配設されているものである。 FIG. 13 is a schematic plan view of another modification of the suction muffler. As shown in FIG. 13, in the compressor 100, the suction muffler 14 is formed in an oval shape in a plan view, and the supply pipe connecting portion 14a1 and the suction are sucked along the oval long axis J of the suction muffler 14. At least one of the pipe connecting portions 14b1 is arranged. Alternatively, in the compressor 100, the suction muffler 14 is formed in an oval shape in a plan view, and the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 are arranged side by side along the long axis J of the oval shape. It is installed.

圧縮機１００は、吸入マフラーと冷媒動作音との共鳴による騒音を効果的に抑制するために、Ｒ１２３４ｙｆ冷媒の割合α［ｗｔ％］によっては吸入マフラー１４の底部１４ｂと頂部１４ａの長さを大きくすることで距離Ｌ「ｍｍ」を確保する場合がある。しかし、吸入マフラー１４の底部１４ｂと頂部１４ａの長さは、実質的には圧縮機１００を搭載する冷凍サイクル装置の内部空間等によって制約を受ける場合がある。圧縮機１００は、吸入マフラー１４が平面視で長円形状に形成されており、吸入マフラー１４の長円形状の長軸Ｊに沿って、供給管接続部１４ａ１と吸入管接続部１４ｂ１の少なくとも一方が配設されているものである。圧縮機１００は、吸入マフラー１４の長円形状と、供給管接続部１４ａ１と吸入管接続部１４ｂ１の少なくとも一方を偏心して配設することで適切な距離Ｌ「ｍｍ」の長さを確保することができる。あるいは、圧縮機１００は、吸入マフラー１４が平面視で長円形状に形成されており、長円形状の長軸Ｊに沿って、供給管接続部１４a１と吸入管接続部１４ｂ１とが並んで配設されているものである。圧縮機１００は、吸入マフラー１４の長円形状と、長円形状の長軸Ｊに沿って、供給管接続部１４a１と吸入管接続部１４ｂ１とが並んで配設することで適切な距離Ｌ「ｍｍ」の長さを確保することができる。 In the compressor 100, in order to effectively suppress the noise caused by the resonance between the suction muffler and the operating noise of the refrigerant, the lengths of the bottom 14b and the top 14a of the suction muffler 14 are increased depending on the ratio α [wt%] of the R1234yf refrigerant. By doing so, the distance L "mm" may be secured. However, the lengths of the bottom 14b and the top 14a of the suction muffler 14 may be substantially restricted by the internal space of the refrigeration cycle device on which the compressor 100 is mounted. In the compressor 100, the suction muffler 14 is formed in an oval shape in a plan view, and at least one of the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 is formed along the oval long axis J of the suction muffler 14. Is arranged. The compressor 100 secures an appropriate distance L "mm" by eccentrically arranging the oval shape of the suction muffler 14 and at least one of the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1. Can be done. Alternatively, in the compressor 100, the suction muffler 14 is formed in an oval shape in a plan view, and the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 are arranged side by side along the long axis J of the oval shape. It is installed. In the compressor 100, the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 are arranged side by side along the oval shape of the suction muffler 14 and the long axis J of the oval shape, so that an appropriate distance L " A length of "mm" can be secured.

また、圧縮機１００は、Ｒ１２３４ｙｆ冷媒の割合α［ｗｔ％］と、吸入マフラー１４の内部空間Ｍ１における供給管接続部１４ａ１と吸入管接続部１４ｂ１との間の距離Ｌ「ｍｍ」が、上記の式３〜式６のいずれか１つの式を満足することにより、圧縮機の騒音が小さい周波数又は遮音材の効果が発揮されやすい周波数に共鳴点を配置させることができる。そのため、圧縮機は、吸入マフラーと冷媒動作音との共鳴による騒音を効果的に抑制することができる。その結果、ハイドロフルオロオレフィンを動作冷媒とした圧縮機の静音性を向上させることができる。 Further, in the compressor 100, the ratio α [wt%] of the R1234yf refrigerant and the distance L “mm” between the supply pipe connecting portion 14a1 and the suction pipe connecting portion 14b1 in the internal space M1 of the suction muffler 14 are as described above. By satisfying any one of the formulas 3 to 6, the resonance point can be arranged at a frequency where the noise of the compressor is small or a frequency at which the effect of the sound insulating material is easily exhibited. Therefore, the compressor can effectively suppress the noise caused by the resonance between the suction muffler and the operating noise of the refrigerant. As a result, the quietness of the compressor using hydrofluoroolefin as the operating refrigerant can be improved.

また、Ｒ１２３４ｙｆ冷媒は、圧縮機１００を動作させるための流量が多いため、吸入マフラー１４から圧縮機構部３に流れる液冷媒の量が増加する場合がある。また、圧縮機構部３に液冷媒が流入すると、液圧縮状態となることから圧縮機の故障の原因となる場合がある。そこで、吸入マフラー１４を平面視で長円形状に形成する。圧縮機１００は、吸入マフラー１４の上壁の形状を平面視で長円形状に形成することで吸入マフラー１４の容積を確保することができる。その結果、吸入マフラー１４に貯留できる液冷媒の量を増加することができ、圧縮機構部３に液冷媒が流入することを防ぐことができる。 Further, since the R1234yf refrigerant has a large flow rate for operating the compressor 100, the amount of the liquid refrigerant flowing from the suction muffler 14 to the compression mechanism unit 3 may increase. Further, when the liquid refrigerant flows into the compression mechanism unit 3, the liquid is compressed, which may cause a failure of the compressor. Therefore, the suction muffler 14 is formed into an oval shape in a plan view. The compressor 100 can secure the volume of the suction muffler 14 by forming the shape of the upper wall of the suction muffler 14 into an oval shape in a plan view. As a result, the amount of the liquid refrigerant that can be stored in the suction muffler 14 can be increased, and the liquid refrigerant can be prevented from flowing into the compression mechanism unit 3.

なお、本発明の実施の形態は、上記実施の形態１〜２に限定されず、種々の変更を加えることができる。例えば、本発明の実施の形態に係る圧縮機１００は、圧縮機構部３に２つの円筒シリンダを有するツインロータリー式の圧縮機であるが、シングルロータリー式の圧縮機であってもよい。 The embodiment of the present invention is not limited to the above-described first and second embodiments, and various modifications can be made. For example, the compressor 100 according to the embodiment of the present invention is a twin rotary type compressor having two cylindrical cylinders in the compression mechanism unit 3, but may be a single rotary type compressor.

１ 密閉容器、２ 電動機部、３ 圧縮機構部、４ 吐出管、１２ 上部密閉容器、１３ 下部密閉容器、１４ 吸入マフラー、１４ａ 頂部、１４ａ１ 供給管接続部、１４ｂ 底部、１４ｂ１ 吸入管接続部、１５ 吸入管、１６ 気密端子、１７ ロッド、１８ リード線、１９ 供給管、２１ 固定子、２２ 回転子、３１ 回転軸、３１ａ 主軸部、３１ｂ 副軸部、３１ｃ 偏心軸部、３１ｄ 偏心軸部、３２ 主軸受、３３ 副軸受、３４ａ 第１の円筒シリンダ、３４ｂ 第２の円筒シリンダ、３５ａ 第１のローリングピストン、３５ｂ 第２のローリングピストン、３６ 仕切板、３７ａ 第１のベーン、３７ｂ 第２のベーン、４０ａ 室、４０ｂ 室、４１ａ 第１のベーン摺動溝、４１ｂ 第２のベーン摺動溝、４２ａ 第１の吸入ポート、４２ｂ 第２の吸入ポート、１００ 圧縮機。 1 Closed container, 2 Electric unit, 3 Compressor mechanism, 4 Discharge pipe, 12 Upper closed container, 13 Lower closed container, 14 Suction muffler, 14a Top, 14a1 Supply pipe connection, 14b Bottom, 14b1 Suction pipe connection, 15 Suction pipe, 16 airtight terminal, 17 rod, 18 lead wire, 19 supply pipe, 21 stator, 22 rotor, 31 rotating shaft, 31a main shaft, 31b sub-shaft, 31c eccentric shaft, 31d eccentric shaft, 32 Main bearing, 33 auxiliary bearing, 34a first cylindrical cylinder, 34b second cylindrical cylinder, 35a first rolling piston, 35b second rolling piston, 36 partition plate, 37a first vane, 37b second vane , 40a chamber, 40b chamber, 41a first vane sliding groove, 41b second vane sliding groove, 42a first suction port, 42b second suction port, 100 compressor.

Claims (6)

圧縮機構部を内蔵した密閉容器と、
前記圧縮機構部に接続された吸入管と、
前記吸入管に接続された吸入マフラーと、
前記吸入マフラーに接続され、冷媒を前記吸入マフラーに供給するための供給管と、
を備え、
前記吸入マフラーの内部空間において、前記吸入マフラーの供給管接続部と吸入管接続部との間の距離Ｌ「ｍｍ」が、１００［ｍｍ］＜Ｌ＜３００［ｍｍ］の範囲に形成されており、
Ｒ１２３４ｙｆ冷媒とＲ３２冷媒とを主成分として含む混合冷媒を動作冷媒とし、動作冷媒全体に対するＲ１２３４ｙｆの割合をα［ｗｔ％］としたとき、下記の式３、式５、および式６のいずれか１つの式を満足し、
前記供給管接続部が、前記吸入マフラーの長手方向軸に対して偏心するように配設されている圧縮機。
Figure 0006840173
Figure 0006840173
Figure 0006840173
 A closed container with a built-in compression mechanism and
The suction pipe connected to the compression mechanism and
With the suction muffler connected to the suction pipe,
A supply pipe connected to the suction muffler and for supplying the refrigerant to the suction muffler,
With
In the internal space of the suction muffler, the distance L "mm" between the supply pipe connection portion and the suction pipe connection portion of the suction muffler is formed in the range of 100 [mm] <L <300 [mm]. ,
When a mixed refrigerant containing R1234yf refrigerant and R32 refrigerant as main components is used as the operating refrigerant and the ratio of R1234yf to the entire operating refrigerant is α [wt%] , any one of the following formulas 3, 5, and 6 is used. Satisfy the two formulas,
A compressor in which the supply pipe connection portion is arranged so as to be eccentric with respect to the longitudinal axis of the suction muffler.
Figure 0006840173
Figure 0006840173
Figure 0006840173
 前記吸入管接続部が、前記吸入マフラーの長手方向軸に対して偏心するように配設されている請求項１に記載の圧縮機。 The compressor according to claim 1, wherein the suction pipe connecting portion is arranged so as to be eccentric with respect to the longitudinal axis of the suction muffler. 前記吸入マフラーが平面視で長円形状に形成されており、長円形状の長軸に沿って、前記供給管接続部と前記吸入管接続部の少なくとも一方が配設されている請求項２に記載の圧縮機。 Said suction muffler is formed in an oval shape in plan view, along the long axis of the oval, in claim 2 in which at least one of the suction pipe connecting portion and the supply pipe connecting portion is arranged The compressor described. 前記吸入マフラーが平面視で長円形状に形成されており、長円形状の長軸に沿って、前記供給管接続部と前記吸入管接続部とが並んで配設されている請求項２に記載の圧縮機。 It said suction muffler is formed in an oval shape in plan view, along the long axis of the oval, in claim 2 in which said supply pipe connecting portion and the suction pipe connecting portion is juxtaposed The compressor described. 前記動作冷媒のＧＷＰが５００未満である請求項１〜４のいずれか１項に記載の圧縮機。 The compressor according to any one of claims 1 to 4 , wherein the GWP of the operating refrigerant is less than 500. 前記動作冷媒のＧＷＰが１００未満である請求項１〜５のいずれか１項に記載の圧縮機。 The compressor according to any one of claims 1 to 5 , wherein the GWP of the operating refrigerant is less than 100.
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