JP2014145318A

JP2014145318A - Rotary compressor

Info

Publication number: JP2014145318A
Application number: JP2013014873A
Authority: JP
Inventors: Junya Tanaka; 順也田中
Original assignee: Fujitsu General Ltd
Current assignee: Fujitsu General Ltd
Priority date: 2013-01-29
Filing date: 2013-01-29
Publication date: 2014-08-14

Abstract

PROBLEM TO BE SOLVED: To provide a rotary compressor having improved compressor efficiency by inhibiting suction refrigerant and refrigerant gas being compressed from being heated by refrigerant gas passing through a refrigerant passage.SOLUTION: In the rotary compressor, refrigerant passages 336 provided in a first and second cylinders 121S, 121T are arranged within a range of phase angles 270°-360° from positions of vane grooves 128S, 128T in the revolving direction of an annular piston, radially outward of discharge valve grooves 163S, 163T which are provided in lower and upper end plates for storing discharge valve parts, respectively.

Description

本発明は、例えば、空気調和機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 for an air conditioner, for example.

図７は、従来のロータリ圧縮機の圧縮部の冷媒通路を示す縦断面図であり、図８は、従来の第１、第２シリンダの冷媒通路を示す平面図である。図７及び図８に示すように、従来のロータリ圧縮機では、第１の圧縮部１２Ｓで圧縮された高温の冷媒ガスは、下マフラー室１８０Ｓ内に吐出され、下端板１６０Ｓ、第１シリンダ１２１Ｓ、中間仕切板１４０、第２シリンダ１２１Ｔ及び上端板１６０Ｔを貫くように設けられた冷媒通路１３６を通って上マフラー室１８０Ｔ内に吐出され、第２の圧縮部１２Ｔで圧縮されて上マフラー室１８０Ｔ内に吐出された冷媒ガスと合流し、圧縮機筐体１０内に吐出される。 FIG. 7 is a longitudinal sectional view showing a refrigerant passage of a compression portion of a conventional rotary compressor, and FIG. 8 is a plan view showing a refrigerant passage of conventional first and second cylinders. As shown in FIGS. 7 and 8, in the conventional rotary compressor, the high-temperature refrigerant gas compressed by the first compressor 12S is discharged into the lower muffler chamber 180S, and the lower end plate 160S and the first cylinder 121S. Then, the refrigerant is discharged into the upper muffler chamber 180T through the refrigerant passage 136 provided so as to pass through the intermediate partition plate 140, the second cylinder 121T, and the upper end plate 160T, and is compressed by the second compression unit 12T to be compressed in the upper muffler chamber 180T. The refrigerant gas discharged into the interior merges and is discharged into the compressor housing 10.

冷媒通路１３６は、下、上端板１６０Ｓ、１６０Ｔに設けられている第１、第２吐出弁溝１６３Ｓ、１６３Ｔ、第１、第２ベーン溝１２８Ｓ、１２８Ｔ、第１、第２吸入孔１３５Ｓ、１３５Ｔ、第１、第２の圧縮部１２Ｓ、１２Ｔ固定用のねじ孔（又はボルト通し孔）１２１ａなどの配置位置には配置することができない。また、冷媒通路１３６は、下、上マフラー室１８０Ｓ、１８０Ｔ内に開口させなければならないので、下、上マフラーカバー１７０Ｓ、１７０Ｔの内側に設ける必要がある。そのため、冷媒通路１３６の配置可能位置は限定され、図８に示すように、第１、第２ベーン溝１２８Ｓ、１２８Ｔの反対側の、スペースの空いている場所に配置されている。 The refrigerant passage 136 has first and second discharge valve grooves 163S and 163T, first and second vane grooves 128S and 128T, and first and second suction holes 135S and 135T provided in the lower and upper end plates 160S and 160T. The first and second compression portions 12S and 12T cannot be arranged at the arrangement positions such as screw holes (or bolt through holes) 121a for fixing. Further, since the refrigerant passage 136 must be opened in the lower and upper muffler chambers 180S and 180T, it is necessary to provide the refrigerant passage 136 inside the lower and upper muffler covers 170S and 170T. Therefore, the arrangement | positioning position of the refrigerant path 136 is limited, and as shown in FIG. 8, it arrange | positions in the place where the space is vacant on the opposite side of the 1st, 2nd vane grooves 128S and 128T.

従来、上記と同様の冷媒通路を有するロータリ圧縮機として、例えば、特許文献１、２が開示されている。 Conventionally, for example, Patent Documents 1 and 2 are disclosed as rotary compressors having the same refrigerant passage as described above.

特開平０８−２３２８７７号公報Japanese Patent Application Laid-Open No. 08-232877 実開平０２−１１４７９０号公報Japanese Utility Model Publication No. 02-114790

第１、第２シリンダ１２１Ｓ、１２１Ｔの第１、第２シリンダ内周面１２３Ｓ、１２３Ｔの温度は、圧縮開始前の低温の冷媒ガスが吸入される第１、第２吸入孔１３５Ｓ、１３５Ｔ近傍では比較的低温であるが、圧縮が進むにつれて冷媒温度が上昇し、圧縮終了の第１、第２吐出孔１９０Ｓ、１９０Ｔ近傍で高温となる。第１、第２ベーン溝１２８Ｓ、１２８Ｔの反対側は、第１、第２吸入孔１３５Ｓ、１３５Ｔと第１、第２吐出孔１９０Ｓ、１９０Ｔの中間位置であり、この位置での第１、第２シリンダ内周面１２３Ｓ、１２３Ｔ温度は、第１、第２吸入孔１３５Ｓ、１３５Ｔ近傍の温度と第１、第２吐出孔１９０Ｓ、１９０Ｔ近傍の温度の中間の温度となる。 The temperatures of the first and second cylinder inner peripheral surfaces 123S and 123T of the first and second cylinders 121S and 121T are in the vicinity of the first and second suction holes 135S and 135T where the low-temperature refrigerant gas before the start of compression is sucked. Although the temperature is relatively low, the refrigerant temperature rises as the compression proceeds, and becomes high in the vicinity of the first and second discharge holes 190S and 190T after the compression. Opposite sides of the first and second vane grooves 128S and 128T are intermediate positions of the first and second suction holes 135S and 135T and the first and second discharge holes 190S and 190T. The temperatures of the two cylinder inner peripheral surfaces 123S and 123T are intermediate between temperatures near the first and second suction holes 135S and 135T and temperatures near the first and second discharge holes 190S and 190T.

下端板１６０Ｓの第１吐出孔１９０Ｓから吐出された高温の冷媒ガスは、下マフラー室１８０Ｓに入ると下マフラーカバー１７０Ｓの壁面を通して下マフラーカバー１７０Ｓ外周部の油溜めに放熱されてやや温度が低下するものの、高温状態のまま冷媒通路１３６内を流れる。そのため、冷媒通路１３６の壁面温度は、第１、第２シリンダ１２１Ｓ、１２１Ｔの第１、第２ベーン溝１２８Ｓ、１２８Ｔの反対側の第１、第２シリンダ内周面１２３Ｓ、１２３Ｔの温度よりも高くなる。 When the high-temperature refrigerant gas discharged from the first discharge hole 190S of the lower end plate 160S enters the lower muffler chamber 180S, it is radiated to the oil sump at the outer periphery of the lower muffler cover 170S through the wall surface of the lower muffler cover 170S, and the temperature slightly decreases. However, it flows in the refrigerant passage 136 in a high temperature state. Therefore, the wall surface temperature of the refrigerant passage 136 is higher than the temperatures of the first and second cylinder inner peripheral surfaces 123S and 123T on the opposite side of the first and second vane grooves 128S and 128T of the first and second cylinders 121S and 121T. Get higher.

それ故、冷媒通路１３６が、第１、第２シリンダ１２１Ｓ、１２１Ｔの第１、第２ベーン溝１２８Ｓ、１２８Ｔの反対側に配置されていると、冷媒通路を流れる冷媒ガスが、第１、第２ベーン溝１２８Ｓ、１２８Ｔの反対側の第１、第２シリンダ内周面１２３Ｓ、１２３Ｔの温度を上昇させ、吸入冷媒や圧縮途中の冷媒ガスを加熱し、体積効率を低下させ、圧縮動力を増加させ、圧縮機効率を低下させる、という問題がある。 Therefore, when the refrigerant passage 136 is disposed on the opposite side of the first and second vane grooves 128S and 128T of the first and second cylinders 121S and 121T, the refrigerant gas flowing through the refrigerant passage is changed into the first and second The temperature of the first and second cylinder inner peripheral surfaces 123S and 123T on the opposite side of the two vane grooves 128S and 128T is raised, the suction refrigerant and the refrigerant gas being compressed are heated, the volume efficiency is lowered, and the compression power is increased. There is a problem of reducing the compressor efficiency.

本発明は、上記に鑑みてなされたものであって、冷媒通路を流れる冷媒ガスによる吸入冷媒や圧縮途中の冷媒ガスの加熱を抑え、圧縮機効率を向上させた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 an object of the present invention is to obtain a rotary compressor that suppresses heating of refrigerant sucked by refrigerant gas flowing in a refrigerant passage and refrigerant gas during compression and improves compressor efficiency. And

上述した課題を解決し、目的を達成するために、本発明は、上部に冷媒の吐出部が設けられ下部に冷媒の吸入部が設けられ密閉された縦置き円筒状の圧縮機筐体と、前記圧縮機筐体の下部に配置され、環状の第１、第２シリンダと、軸受部及び吐出弁部を有し前記第１、第２シリンダの端部を閉塞する下、上端板と、前記第１、第２シリンダ間に配置され両者間を仕切る中間仕切板と、前記軸受部に支持された回転軸の偏芯部に嵌合され前記第１、第２シリンダのシリンダ内周面に沿って該シリンダ内を公転し前記シリンダ内周面との間に作動室を形成する第１、第２環状ピストンと、前記第１、第２シリンダのベーン溝内から前記作動室内に突出して前記第１、第２環状ピストンに当接し該作動室を吸入室と圧縮室とに区画する第１、第２ベーンと、前記圧縮機筐体の内部に連通するマフラー吐出孔を有し前記上端板の吐出弁部を覆って前記上端板との間に上マフラー室を形成する上マフラーカバーと、前記下端板の吐出弁部を覆って前記下端板との間に下マフラー室を形成する下マフラーカバーと、前記下、上端板及び第１、第２シリンダ及び中間仕切板を貫通し上、下マフラー室間を連通させる冷媒通路と、を備え、前記吸入部を通して冷凍サイクルの低圧側から冷媒を吸入し、前記圧縮機筐体内を通して前記吐出部から冷媒を吐出する圧縮部と、前記圧縮機筐体の上部に設置され、前記回転軸を介して前記圧縮部を駆動するモータと、を備えるロータリ圧縮機において、前記第１、第２シリンダに設けられる冷媒通路を、ベーン溝位置から環状ピストンの公転方向に、位相角度２７０°以上３６０°以下の範囲内に配置する。 In order to solve the above-described problems and achieve the object, the present invention includes a vertically-placed cylindrical compressor housing that is provided with a refrigerant discharge portion at the top and a refrigerant suction portion at the bottom and is sealed, A lower upper end plate disposed at a lower portion of the compressor housing, having annular first and second cylinders, a bearing portion and a discharge valve portion, and closing the end portions of the first and second cylinders; An intermediate partition plate arranged between the first and second cylinders and partitioning between the two and the eccentric part of the rotating shaft supported by the bearing part is fitted along the inner peripheral surface of the first and second cylinders. The first and second annular pistons that revolve inside the cylinder and form a working chamber between the inner circumferential surface of the cylinder, and the first and second cylinders protrude from the vane grooves into the working chamber and the first 1. First and second abutting against the second annular piston and dividing the working chamber into a suction chamber and a compression chamber An upper muffler cover having a muffler discharge hole communicating with the interior of the compressor housing and covering a discharge valve portion of the upper end plate to form an upper muffler chamber between the upper end plate and the lower end A lower muffler cover that covers the discharge valve portion of the plate and forms a lower muffler chamber with the lower end plate; and an upper and lower muffler chamber that penetrates the lower, upper end plate, the first and second cylinders, and the intermediate partition plate A refrigerant passage that communicates with each other, a compressor that sucks refrigerant from the low-pressure side of the refrigeration cycle through the suction portion, and discharges the refrigerant from the discharge portion through the compressor housing, and a compressor housing A rotary compressor having a motor installed at an upper portion and driving the compression unit via the rotary shaft, wherein the refrigerant passage provided in the first and second cylinders is moved from the vane groove position to the revolving direction of the annular piston. The phase Placed in degrees 270 ° or 360 ° in the following range.

本発明によれば、冷媒通路を通過する冷媒ガスによる吸入冷媒や圧縮途中の冷媒ガスの加熱を抑え、圧縮機効率を向上させることができる、という効果を奏する。 According to the present invention, there is an effect that it is possible to improve the efficiency of the compressor by suppressing the heating of the refrigerant sucked by the refrigerant gas passing through the refrigerant passage and the refrigerant gas being compressed.

図１は、本発明に係るロータリ圧縮機の実施例を示す縦断面図である。FIG. 1 is a longitudinal sectional view showing an embodiment of a rotary compressor according to the present invention. 図２は、実施例１の第１、第２の圧縮部を示す平面図である。FIG. 2 is a plan view illustrating first and second compression units according to the first embodiment. 図３は、実施例１の第１、第２シリンダの冷媒通路を示す平面図である。FIG. 3 is a plan view illustrating the refrigerant passages of the first and second cylinders of the first embodiment. 図４は、実施例２の第１、第２シリンダの冷媒通路を示す平面図である。FIG. 4 is a plan view illustrating the refrigerant passages of the first and second cylinders of the second embodiment. 図５は、実施例２の吐出弁部を示す縦断面図である。FIG. 5 is a longitudinal sectional view showing the discharge valve portion of the second embodiment. 図６は、従来の吐出弁部を示す縦断面図である。FIG. 6 is a longitudinal sectional view showing a conventional discharge valve portion. 図７は、従来のロータリ圧縮機の圧縮部の冷媒通路を示す縦断面図である。FIG. 7 is a longitudinal sectional view showing a refrigerant passage of a compression portion of a conventional rotary compressor. 図８は、従来の第１、第２シリンダの冷媒通路を示す平面図である。FIG. 8 is a plan view showing the refrigerant passages of the conventional first and second cylinders.

以下に、本発明に係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、本発明に係るロータリ圧縮機の実施例を示す縦断面図であり、図２は、実施例１の第１、第２の圧縮部を示す平面図である。 FIG. 1 is a longitudinal sectional view showing an embodiment of a rotary compressor according to the present invention, and FIG. 2 is a plan view showing first and second compression portions of the embodiment 1. FIG.

図１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の下部に配置された圧縮部１２と、圧縮機筐体１０の上部に配置され、回転軸１５を介して圧縮部１２を駆動するモータ１１と、を備えている。 As shown in FIG. 1, the rotary compressor 1 according to the embodiment is disposed at a lower portion of a sealed vertical cylindrical compressor housing 10 and an upper portion of the compressor housing 10. And a motor 11 that drives the compression unit 12 via the rotary shaft 15.

モータ１１のステータ１１１は、円筒状に形成され、圧縮機筐体１０の内周面に焼きばめされて固定されている。モータ１１のロータ１１２は、円筒状のステータ１１１の内部に配置され、モータ１１と圧縮部１２とを機械的に接続する回転軸１５に焼きばめされて固定されている。 The stator 111 of the motor 11 is formed in a cylindrical shape, and is fixed by being shrink-fitted on the inner peripheral surface of the compressor housing 10. The rotor 112 of the motor 11 is disposed inside the cylindrical stator 111 and is fixed by being shrink-fitted to a rotating shaft 15 that mechanically connects the motor 11 and the compression unit 12.

圧縮部１２は、第１の圧縮部１２Ｓと、第１の圧縮部１２Ｓと並列に配置され第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。図２に示すように、第１、第２の圧縮部１２Ｓ、１２Ｔは、第１、第２側方張出部１２２Ｓ、１２２Ｔに、放射状に第１、第２吸入孔１３５Ｓ、１３５Ｔ、第１、第２ベーン溝１２８Ｓ、１２８Ｔが設けられた環状の第１、第２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 arranged in parallel with the first compression unit 12S and stacked on the upper side of the first compression unit 12S. As shown in FIG. 2, the first and second compression parts 12S and 12T are arranged on the first and second side projecting parts 122S and 122T in a radial manner with the first and second suction holes 135S and 135T, , Annular first and second cylinders 121S and 121T provided with second vane grooves 128S and 128T are provided.

図２に示すように、第１、第２シリンダ１２１Ｓ、１２１Ｔには、モータ１１の回転軸１５と同心に、円形の第１、第２シリンダ内周面１２３Ｓ、１２３Ｔが形成されている。第１、第２シリンダ内周面１２３Ｓ、１２３Ｔ内には、シリンダ内径よりも小さい外径の第１、第２環状ピストン１２５Ｓ、１２５Ｔが夫々配置され、第１、第２シリンダ内周面１２３Ｓ、１２３Ｔと、第１、第２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作動室１３０Ｓ、１３０Ｔが形成される。 As shown in FIG. 2, circular first and second cylinder inner peripheral surfaces 123 </ b> S and 123 </ b> T are formed in the first and second cylinders 121 </ b> S and 121 </ b> T concentrically with the rotating shaft 15 of the motor 11. In the first and second cylinder inner peripheral surfaces 123S and 123T, first and second annular pistons 125S and 125T having an outer diameter smaller than the cylinder inner diameter are arranged, respectively, and the first and second cylinder inner peripheral surfaces 123S, Between the 123T and the first and second annular pistons 125S and 125T, there are formed first and second working chambers 130S and 130T for sucking, compressing and discharging the refrigerant gas.

第１、第２シリンダ１２１Ｓ、１２１Ｔには、第１、第２シリンダ内周面１２３Ｓ、１２３Ｔから径方向に、シリンダ高さ全域に亘る第１、第２ベーン溝１２８Ｓ、１２８Ｔが形成され、第１、第２ベーン溝１２８Ｓ、１２８Ｔ内に、夫々平板状の第１、第２ベーン１２７Ｓ、１２７Ｔが、摺動自在に嵌合されている。 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 circumferential surfaces 123S and 123T in the radial direction over the entire cylinder height. In the first and second vane grooves 128S and 128T, flat plate-like first and second vanes 127S and 127T are slidably fitted.

図２に示すように、第１、第２ベーン溝１２８Ｓ、１２８Ｔの奥部には、第１、第２シリンダ１２１Ｓ、１２１Ｔの外周部から第１、第２ベーン溝１２８Ｓ、１２８Ｔに連通するように第１、第２スプリング穴１２４Ｓ、１２４Ｔが形成されている。第１、第２スプリング穴１２４Ｓ、１２４Ｔには、第１、第２ベーン１２７Ｓ、１２７Ｔの背面を押圧するベーンスプリング（図示せず）が挿入されている。ロータリ圧縮機１の起動時は、このベーンスプリングの反発力により、第１、第２ベーン１２７Ｓ、１２７Ｔが、第１、第２ベーン溝１２８Ｓ、１２８Ｔ内から第１、第２作動室１３０Ｓ、１３０Ｔ内に突出し、その先端が、第１、第２環状ピストン１２５Ｓ、１２５Ｔの外周面に当接し、第１、第２ベーン１２７Ｓ、１２７Ｔにより、第１、第２作動室１３０Ｓ、１３０Ｔが、第１、第２吸入室１３１Ｓ、１３１Ｔと、第１、第２圧縮室１３３Ｓ、１３３Ｔとに区画される。 As shown in FIG. 2, the first and second vane grooves 128S and 128T are communicated with the first and second vane grooves 128S and 128T from the outer periphery of the first and second cylinders 121S and 121T at the back of the first and second vane grooves 128S and 128T. First and second spring holes 124S and 124T are formed. Vane springs (not shown) that press the back surfaces of the first and second vanes 127S and 127T are inserted into the first and second spring holes 124S and 124T. When the rotary compressor 1 is started, the first and second vanes 127S and 127T are moved from the first and second vane grooves 128S and 128T to the first and second working chambers 130S and 130T by the repulsive force of the vane springs. The first and second working chambers 130S and 130T are moved to the first and second working chambers 130S and 130T by the first and second vanes 127S and 127T, respectively. The second suction chambers 131S and 131T and the first and second compression chambers 133S and 133T are partitioned.

また、第１、第２シリンダ１２１Ｓ、１２１Ｔには、第１、第２ベーン溝１２８Ｓ、１２８Ｔの奥部と圧縮機筐体１０内とを、図１に示す開口部Ｒで連通して圧縮機筐体１０内の圧縮された冷媒ガスを導入し、第１、第２ベーン１２７Ｓ、１２７Ｔに、冷媒ガスの圧力により背圧をかける第１、第２圧力導入路１２９Ｓ、１２９Ｔが形成されている。 In addition, the first and second cylinders 121S and 121T communicate with the inner portions of the first and second vane grooves 128S and 128T and the interior of the compressor housing 10 through the opening R shown in FIG. First and second pressure introducing passages 129S and 129T are formed in which the compressed refrigerant gas in the housing 10 is introduced and back pressure is applied to the first and second vanes 127S and 127T by the pressure of the refrigerant gas. .

第１、第２シリンダ１２１Ｓ、１２１Ｔには、第１、第２吸入室１３１Ｓ、１３１Ｔに外部から冷媒を吸入するために、第１、第２吸入室１３１Ｓ、１３１Ｔと外部とを連通させる第１、第２吸入孔１３５Ｓ、１３５Ｔが設けられている。 In the first and second cylinders 121S and 121T, the first and second suction chambers 131S and 131T communicate with the outside in order to suck the refrigerant from the outside into the first and second suction chambers 131S and 131T. Second suction holes 135S and 135T are provided.

また、図１に示すように、第１シリンダ１２１Ｓと第２シリンダ１２１Ｔとの間には、中間仕切板１４０が配置され、第１シリンダ１２１Ｓの第１作動室１３０Ｓと第２シリンダ１２１Ｔの第２作動室１３０Ｔとを区画、閉塞している。第１シリンダ１２１Ｓの下端部には、下端板１６０Ｓが配置され、第１シリンダ１２１Ｓの第１作動室１３０Ｓを閉塞している。また、第２シリンダ１２１Ｔの上端部には、上端板１６０Ｔが配置され、第２シリンダ１２１Ｔの第２作動室１３０Ｔを閉塞している。 Further, as shown in FIG. 1, an intermediate partition plate 140 is disposed between the first cylinder 121S and the second cylinder 121T, and the first working chamber 130S of the first cylinder 121S and the second of the second cylinder 121T. The working chamber 130T is partitioned and closed. A lower end plate 160S is disposed 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 160T is disposed at the upper end portion of the second cylinder 121T, and closes the second working chamber 130T of the second cylinder 121T.

下端板１６０Ｓには、副軸受部１６１Ｓが形成され、副軸受部１６１Ｓに、回転軸１５の副軸部１５１が回転自在に支持されている。上端板１６０Ｔには、主軸受部１６１Ｔが形成され、主軸受部１６１Ｔに、回転軸１５の主軸部１５３が回転自在に支持されている。 A sub-bearing portion 161S is formed on the lower end plate 160S, and the sub-shaft portion 151 of the rotary shaft 15 is rotatably supported by the sub-bearing portion 161S. A main bearing portion 161T is formed on the upper end plate 160T, and the main shaft portion 153 of the rotary shaft 15 is rotatably supported by the main bearing portion 161T.

回転軸１５は、互いに１８０°位相をずらして偏心させた第１偏心部１５２Ｓと第２偏心部１５２Ｔとを備え、第１偏心部１５２Ｓは、第１の圧縮部１２Ｓの第１環状ピストン１２５Ｓに回転自在に嵌合し、第２偏心部１５２Ｔは、第２の圧縮部１２Ｔの第２環状ピストン１２５Ｔに回転自在に嵌合している。 The rotating shaft 15 includes a first eccentric portion 152S and a second eccentric portion 152T that are eccentric with a phase difference of 180 ° from each other. The first eccentric portion 152S is connected to the first annular piston 125S of the first compression portion 12S. The second eccentric portion 152T is rotatably fitted to the second annular piston 125T of the second compression portion 12T.

回転軸１５が回転すると、第１、第２環状ピストン１２５Ｓ、１２５Ｔが、第１、第２シリンダ内周面１２３Ｓ、１２３Ｔに沿って第１、第２シリンダ１２１Ｓ、１２１Ｔ内を図２の反時計回りに公転し、これに追随して第１、第２ベーン１２７Ｓ、１２７Ｔが往復運動する。この第１、第２環状ピストン１２５Ｓ、１２５Ｔ及び第１、第２ベーン１２７Ｓ、１２７Ｔの運動により、第１、第２吸入室１３１Ｓ、１３１Ｔ及び第１、第２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吐出する。 When the rotary shaft 15 rotates, the first and second annular pistons 125S and 125T move in the first and second cylinders 121S and 121T along the first and second cylinder inner peripheral surfaces 123S and 123T in the counterclockwise direction of FIG. Revolving around, the first and second vanes 127S and 127T reciprocate following this. Due to the movement of the first and second annular pistons 125S and 125T and the first and second vanes 127S and 127T, the volumes of the first and second suction chambers 131S and 131T and the first and second compression chambers 133S and 133T are continuous. The compressor 12 continuously sucks, compresses and discharges the refrigerant gas.

図１に示すように、下端板１６０Ｓの下側には、下マフラーカバー１７０Ｓが配置され、下端板１６０Ｓとの間に下マフラー室１８０Ｓを形成している。そして、第１の圧縮部１２Ｓは、下マフラー室１８０Ｓに開口している。すなわち、下端板１６０Ｓの第１ベーン１２７Ｓ近傍には、第１シリンダ１２１Ｓの第１圧縮室１３３Ｓと下マフラー室１８０Ｓとを連通する第１吐出孔１９０Ｓ（図２参照）が設けられ、第１吐出孔１９０Ｓには、圧縮された冷媒ガスの逆流を防止するリード弁型の第１吐出弁２００Ｓが配置されている。 As shown in FIG. 1, a lower muffler cover 170S is arranged below the lower end plate 160S, and a lower muffler chamber 180S is formed between the lower end plate 160S and the lower muffler cover 170S. And the 1st compression part 12S is opened to lower muffler room 180S. That is, a first discharge hole 190S (see FIG. 2) that connects the first compression chamber 133S of the first cylinder 121S and the lower muffler chamber 180S is provided in the vicinity of the first vane 127S of the lower end plate 160S. In the hole 190S, a reed valve type first discharge valve 200S for preventing the backflow of the compressed refrigerant gas is disposed.

下マフラー室１８０Ｓは、環状に形成された１つの室であり、第１の圧縮部１２Ｓの吐出側を、下端板１６０Ｓ、第１シリンダ１２１Ｓ、中間仕切板１４０、第２シリンダ１２１Ｔ及び上端板１６０Ｔを貫通する冷媒通路３３６（図２参照）を通して上マフラー室１８０Ｔ内に連通させる連通路の一部である。下マフラー室１８０Ｓは、吐出冷媒ガスの圧力脈動を低減させる。また、第１吐出弁２００Ｓに重ねて、第１吐出弁２００Ｓの撓み開弁量を制限するための第１吐出弁押さえ２０１Ｓが、第１吐出弁２００Ｓとともにリベットにより固定されている。第１吐出弁２００Ｓ及び第１吐出弁押さえ２０１Ｓは、下端板１６０Ｓの第１吐出弁部２０２Ｓを構成している。第１吐出弁部２０２Ｓは、下端板１６０Ｓに形成された第１吐出弁溝１６３Ｓ内に収容されている。第１吐出孔１９０Ｓは、第１吐出弁溝１６３Ｓの底部に設けられている。冷媒通路３３６の詳細については後述する。 The lower muffler chamber 180S is one chamber formed in an annular shape, and the lower end plate 160S, the first cylinder 121S, the intermediate partition plate 140, the second cylinder 121T, and the upper end plate 160T are arranged on the discharge side of the first compression unit 12S. Is a part of the communication path that communicates with the upper muffler chamber 180T through the refrigerant path 336 (see FIG. 2). The lower muffler chamber 180S reduces the pressure pulsation of the discharged refrigerant gas. In addition, a first discharge valve presser 201S for limiting the amount of flexure opening of the first discharge valve 200S is fixed to the first discharge valve 200S together with the first discharge valve 200S by a rivet. The first discharge valve 200S and the first discharge valve presser 201S constitute a first discharge valve portion 202S of the lower end plate 160S. The first discharge valve portion 202S is accommodated in a first discharge valve groove 163S formed in the lower end plate 160S. The first discharge hole 190S is provided at the bottom of the first discharge valve groove 163S. Details of the refrigerant passage 336 will be described later.

図１に示すように、上端板１６０Ｔの上側には、上マフラーカバー１７０Ｔが配置され、上端板１６０Ｔとの間に上マフラー室１８０Ｔを形成している。上端板１６０Ｔの第２ベーン１２７Ｔ近傍には、第２シリンダ１２１Ｔの第２圧縮室１３３Ｔと上マフラー室１８０Ｔとを連通する第２吐出孔１９０Ｔ（図２参照）が設けられ、第２吐出孔１９０Ｔには、圧縮された冷媒ガスの逆流を防止するリード弁型の第２吐出弁２００Ｔが配置されている。また、第２吐出弁２００Ｔに重ねて、第２吐出弁２００Ｔの撓み開弁量を制限するための第２吐出弁押さえ２０１Ｔが、第２吐出弁２００Ｔとともにリベットにより固定されている。上マフラー室１８０Ｔは、吐出冷媒の圧力脈動を低減させる。第２吐出弁２００Ｔ及び第２吐出弁押さえ２０１Ｔは、上端板１６０Ｔの第２吐出弁部２０２Ｔを構成している。第２吐出弁部２０２Ｔは、上端板１６０Ｔに形成された第２吐出弁溝１６３Ｔ内に収容されている。第２吐出孔１９０Ｔは、第２吐出弁溝１６３Ｔの底部に設けられている。上端板１６０Ｔの主軸受部１６１Ｔと上マフラーカバー１７０Ｔの上端部との間には間隙が設けられ、この間隙がマフラー吐出孔１７１となっている。 As shown in FIG. 1, an upper muffler cover 170T is arranged above the upper end plate 160T, and an upper muffler chamber 180T is formed between the upper end plate 160T and the upper muffler cover 170T. In the vicinity of the second vane 127T of the upper end plate 160T, a second discharge hole 190T (see FIG. 2) that communicates the second compression chamber 133T of the second cylinder 121T and the upper muffler chamber 180T is provided, and the second discharge hole 190T. Is provided with a reed valve type second discharge valve 200T for preventing the backflow of the compressed refrigerant gas. In addition, a second discharge valve presser 201T for limiting the deflection opening amount of the second discharge valve 200T is fixed to the second discharge valve 200T by a rivet together with the second discharge valve 200T. The upper muffler chamber 180T reduces the pressure pulsation of the discharged refrigerant. The second discharge valve 200T and the second discharge valve presser 201T constitute a second discharge valve portion 202T of the upper end plate 160T. The second discharge valve portion 202T is accommodated in a second discharge valve groove 163T formed in the upper end plate 160T. The second discharge hole 190T is provided at the bottom of the second discharge valve groove 163T. A gap is provided between the main bearing portion 161T of the upper end plate 160T and the upper end portion of the upper muffler cover 170T, and this gap serves as a muffler discharge hole 171.

第１シリンダ１２１Ｓ、下端板１６０Ｓ、下マフラーカバー１７０Ｓ、第２シリンダ１２１Ｔ、上端板１６０Ｔ、上マフラーカバー１７０Ｔ及び中間仕切板１４０は、複数の通しボルト１７５等により一体に締結されている。通しボルト１７５等により一体に締結された圧縮部１２のうち、上端板１６０Ｔの外周部が、圧縮機筐体１０にスポット溶接により固着され、圧縮部１２を圧縮機筐体１０に固定している。 The first cylinder 121S, the lower end plate 160S, the lower muffler cover 170S, the second cylinder 121T, the upper end plate 160T, the upper muffler cover 170T, and the intermediate partition plate 140 are integrally fastened by a plurality of through bolts 175 and the like. Out of the compression portion 12 that is integrally fastened by a through bolt 175 or the like, the outer peripheral portion of the upper end plate 160T is fixed to the compressor housing 10 by spot welding, and the compression portion 12 is fixed to the compressor housing 10. .

円筒状の圧縮機筐体１０の外周壁には、軸方向に離間して下部から順に、第１、第２貫通孔１０１、１０２が、第１、第２吸入管１０４、１０５を通すために設けられている。また、圧縮機筐体１０の外側部には、独立した円筒状の密閉容器からなるアキュムレータ２５が、アキュムホルダー２５２及びアキュムバンド２５３により保持されている。 The first and second through holes 101 and 102 are passed through the outer peripheral wall of the cylindrical compressor housing 10 in order from the lower part in the axial direction so as to pass the first and second suction pipes 104 and 105. Is provided. In addition, an accumulator 25 formed of an independent cylindrical sealed container is held by an accumulator holder 252 and an accumulator band 253 on the outer side of the compressor housing 10.

アキュムレータ２５の天部中心には、冷凍サイクルの蒸発器に接続するシステム接続管２５５が接続され、アキュムレータ２５の底部に設けられた底部貫通孔２５７には、一端がアキュムレータ２５の内部上方まで延設され、他端が、第１、第２吸入管１０４、１０５の他端に接続される第１、第２低圧連絡管３１Ｓ、３１Ｔが接続されている。 A system connection tube 255 connected to the evaporator of the refrigeration cycle is connected to the center of the top of the accumulator 25, and one end of the bottom through hole 257 provided at the bottom of the accumulator 25 extends to the upper part inside the accumulator 25. The other ends of the first and second suction pipes 104 and 105 are connected to the first and second low-pressure communication pipes 31S and 31T.

冷凍サイクルの低圧冷媒をアキュムレータ２５を介して第１、第２の圧縮部１２Ｓ、１２Ｔに導く第１、第２低圧連絡管３１Ｓ、３１Ｔは、吸入部としての第１、第２吸入管１０４、１０５を介して第１、第２シリンダ１２１Ｓ、１２１Ｔの第１、第２吸入孔１３５Ｓ、１３５Ｔ（図２参照）に接続されている。すなわち、第１、第２吸入孔１３５Ｓ、１３５Ｔは、冷凍サイクルの蒸発器に並列に接続されている。 The first and second low-pressure connecting pipes 31S and 31T that guide the low-pressure refrigerant of the refrigeration cycle to the first and second compression parts 12S and 12T through the accumulator 25 are the first and second suction pipes 104, The first and second cylinders 121S and 121T are connected to the first and second suction holes 135S and 135T (see FIG. 2) via the 105. That is, the first and second suction holes 135S and 135T are connected in parallel to the evaporator of the refrigeration cycle.

圧縮機筐体１０の天部には、冷凍サイクルと接続し高圧冷媒ガスを冷凍サイクルの凝縮器側に吐出する吐出部としての吐出管１０７が接続されている。すなわち、第１、第２吐出孔１９０Ｓ、１９０Ｔは、冷凍サイクルの凝縮器に接続されている。 Connected to the top of the compressor housing 10 is a discharge pipe 107 that is connected to the refrigeration cycle and discharges high-pressure refrigerant gas to the condenser side of the refrigeration cycle. That is, the first and second discharge holes 190S and 190T are connected to the condenser of the refrigeration cycle.

圧縮機筐体１０内には、およそ第２シリンダ１２１Ｔの高さまで潤滑油が封入されている。また、潤滑油は、回転軸１５の下部に挿入された羽根ポンプ（図示せず）により、回転軸１５の下端部に取付けられた給油パイプ１６から吸上げられ、圧縮部１２を循環し、摺動部品の潤滑を行なうと共に、圧縮部１２の微小隙間のシールをしている。 Lubricating oil is sealed in the compressor housing 10 up to the height of the second cylinder 121T. Further, the lubricating oil is sucked up from the oil supply pipe 16 attached to the lower end portion of the rotating shaft 15 by a blade pump (not shown) inserted in the lower portion of the rotating shaft 15, circulates through the compressing portion 12, and slides. The moving parts are lubricated and a minute gap in the compression portion 12 is sealed.

次に、図３を参照して、実施例１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３は、実施例１の第１、第２シリンダの冷媒通路を示す平面図である。 Next, a characteristic configuration of the rotary compressor 1 according to the first embodiment will be described with reference to FIG. FIG. 3 is a plan view illustrating the refrigerant passages of the first and second cylinders of the first embodiment.

図３に示すように、実施例１の冷媒通路３３６は、第１、第２シリンダ１２１Ｓ、１２１Ｔ、中間仕切板１４０及び上、下端板１６０Ｓ、１６０Ｔに設けられ、第１、第２ベーン溝１２８Ｓ、１２８Ｔ位置から第１、第２環状ピストン１２５Ｓ、１２５Ｔの公転方向（図２に示す第１、第２環状ピストン１２５Ｓ、１２５Ｔの反時計回り方向）に、位相角度２７０°以上３６０°以下の範囲内（すなわち、第１、第２ベーン溝１２８Ｓ、１２８Ｔ位置から時計回り方向に９０°の範囲内）に配置されている。 As shown in FIG. 3, the refrigerant passage 336 of the first embodiment is provided in the first and second cylinders 121S and 121T, the intermediate partition plate 140, and the upper and lower end plates 160S and 160T, and the first and second vane grooves 128S. , A phase angle of 270 ° to 360 ° in the revolving direction of the first and second annular pistons 125S and 125T (the counterclockwise direction of the first and second annular pistons 125S and 125T shown in FIG. 2) from the 128T position. It is arranged inside (that is, within a range of 90 ° in the clockwise direction from the position of the first and second vane grooves 128S and 128T).

また、冷媒通路３３６は、第１、第２吐出弁部２０２Ｓ、２０２Ｔ（図１参照）を収容する第１、第２吐出弁溝１６３Ｓ、１６３Ｔの径方向外方で、かつ、第１、第２マフラー室１８０Ｓ、１８０Ｔの範囲内に配置されている。なお、冷媒通路３３６の配置位置に配置されていた第１、第２の圧縮部１２Ｓ、１２Ｔ固定用のねじ孔（又はボルト通し孔）３２１ａは、第１、第２側方張出部１２２Ｓ、１２２Ｔに設けられている。 The refrigerant passage 336 is radially outward of the first and second discharge valve grooves 163S and 163T that house the first and second discharge valve portions 202S and 202T (see FIG. 1), and the first and second The two muffler chambers 180S and 180T are disposed within the range. Note that the first and second compression portions 12S and 12T fixing screw holes (or bolt through holes) 321a arranged at the position where the refrigerant passage 336 is arranged include the first and second laterally extending portions 122S, 122T.

実施例１の冷媒通路３３６は、第１、第２ベーン溝１２８Ｓ、１２８Ｔ位置から時計回り方向に９０°の範囲内に配置されているので、冷媒通路３３６を通る冷媒ガスの温度よりも、第１、第２吐出孔１９０Ｓ、１９０Ｔ近傍の第１、第２圧縮室１３３Ｓ、１３３Ｔの第１、第２シリンダ内周面１２３Ｓ、１２３Ｔの温度が高い。そのため、冷媒通路３３６を通る冷媒ガスが、第１、第２シリンダ内周面１２３Ｓ、１２３Ｔの温度を上昇させることはなく、圧縮機効率が低下することはない。 Since the refrigerant passage 336 according to the first embodiment is disposed within a range of 90 ° in the clockwise direction from the first and second vane grooves 128S and 128T, the refrigerant passage 336 is more than the temperature of the refrigerant gas passing through the refrigerant passage 336. 1. The temperature of the first and second cylinder inner peripheral surfaces 123S and 123T of the first and second compression chambers 133S and 133T in the vicinity of the first and second discharge holes 190S and 190T is high. Therefore, the refrigerant gas passing through the refrigerant passage 336 does not increase the temperature of the first and second cylinder inner peripheral surfaces 123S and 123T, and the compressor efficiency does not decrease.

図４は、実施例２の第１、第２シリンダの冷媒通路を示す平面図であり、図５は、実施例２の吐出弁部を示す縦断面図であり、図６は、従来の吐出弁部を示す縦断面図である。図４に示すように、実施例２の冷媒通路４３６は、第１、第２シリンダ１２１Ｓ、１２１Ｔ、中間仕切板１４０及び上、下端板１６０Ｓ、１６０Ｔに設けられ、第１、第２ベーン溝１２８Ｓ、１２８Ｔ位置から第１、第２環状ピストン１２５Ｓ、１２５Ｔの公転方向（図２に示す第１、第２環状ピストン１２５Ｓ、１２５Ｔの反時計回り方向）に、位相角度２７０°以上３６０°以下の範囲内（すなわち、第１、第２ベーン溝１２８Ｓ、１２８Ｔ位置から時計回り方向に９０°の範囲内）に配置されている。 FIG. 4 is a plan view showing refrigerant passages of the first and second cylinders of Example 2, FIG. 5 is a longitudinal sectional view showing a discharge valve portion of Example 2, and FIG. 6 is a conventional discharge. It is a longitudinal cross-sectional view which shows a valve part. As shown in FIG. 4, the refrigerant passage 436 of the second embodiment is provided in the first and second cylinders 121S and 121T, the intermediate partition plate 140, and the upper and lower end plates 160S and 160T, and the first and second vane grooves 128S. , A phase angle of 270 ° to 360 ° in the revolving direction of the first and second annular pistons 125S and 125T (the counterclockwise direction of the first and second annular pistons 125S and 125T shown in FIG. 2) from the 128T position. It is arranged inside (that is, within a range of 90 ° in the clockwise direction from the position of the first and second vane grooves 128S and 128T).

実施例２の冷媒通路４３６は、第１、第２吐出弁部２０２Ｓ、２０２Ｔを収容する第１、第２吐出弁溝１６３Ｓ、１６３Ｔを、図３に示す、第１、第２ベーン溝１２８Ｓ、１２８Ｔ位置から時計回り方向に９０°の範囲内から、図４に示す、第１、第２シリンダ１２１Ｓ、１２１Ｔの第１、第２吸入孔１３５Ｓ、１３５Ｔ側に配置替えし、第１、第２吐出弁溝１６３Ｓ、１６３Ｔを配置替えした空きスペースに配置されている。 The refrigerant passage 436 according to the second embodiment includes first and second discharge valve grooves 163S and 163T that house the first and second discharge valve portions 202S and 202T. From the range of 90 ° in the clockwise direction from the 128T position, the first and second suction holes 135S and 135T of the first and second cylinders 121S and 121T shown in FIG. The discharge valve grooves 163S and 163T are arranged in empty spaces where the arrangement is changed.

ただし、第１、第２吐出弁溝１６３Ｓ、１６３Ｔを、第１、第２吸入孔１３５Ｓ、１３５Ｔ側に配置替えすると、図６に示すように、第１、第２吐出弁溝１６３Ｓ、１６３Ｔの底部は、肉厚ｔ_１が薄いため、下、上マフラー室１８０Ｓ、１８０Ｔから第１、第２吸入室１３１Ｓ、１３１Ｔ側への伝熱量が増大し、第１、第２吸入室１３１Ｓ、１３１Ｔ内の冷媒ガスを加熱してしまう、という問題がある。また、肉厚ｔ_１が薄いと、高圧の下、上マフラー室１８０Ｓ、１８０Ｔと低圧の第１、第２吸入室１３１Ｓ、１３１Ｔの圧力差により、第１、第２吐出弁溝１６３Ｓ、１６３Ｔの底部の弾性変形量が増加し、第１、第２環状ピストン１２５Ｓ、１２５Ｔとの摺動隙間が減少し、第１、第２環状ピストン１２５Ｓ、１２５Ｔが焼付くおそれがある。 However, if the first and second discharge valve grooves 163S and 163T are rearranged on the first and second suction holes 135S and 135T side, as shown in FIG. 6, the first and second discharge valve grooves 163S and 163T bottom, since the thickness _{t 1} is thin, bottom, upper muffler chamber 180S, the first from the 180T, the second suction chamber 131S, the amount of heat transferred to the 131T side increases, the first and second suction chamber 131S, the 131T There is a problem that the refrigerant gas is heated. Further, when the thickness _{t 1} is thin, under high pressure, the upper muffler chamber 180S, the first 180T and the low pressure, the second suction chamber 131S, the pressure difference between the 131T, first, second discharge valve groove 163S, the 163T The amount of elastic deformation at the bottom increases, the sliding gap between the first and second annular pistons 125S and 125T decreases, and the first and second annular pistons 125S and 125T may be seized.

上記問題の対策として、図５に示すように、第１、第２吐出弁溝１６３Ｓ、１６３Ｔの底部（第１、第２吐出弁部２０２Ｓ、２０２Ｔの固定側の底部）の肉厚ｔ_２を厚くするとよい。このとき、第１、第２吐出弁部２０２Ｓ、２０２Ｔの固定側の高さと第１、第２吐出孔１９０Ｓ、１９０Ｔの弁座高さが異なってしまうため、第１、第２吐出弁４００Ｓ、４００Ｔ及び第１、第２吐出弁押さえ４０１Ｓ、４０１Ｔ（第１、第２吐出弁部４０２Ｓ、４０２Ｔ）を段状に形成する。 As a countermeasure for the above problem, as shown in FIG. 5, the thickness t ₂ of the bottom portions of the first and second discharge valve grooves 163S and 163T (the bottom portions on the fixed side of the first and second discharge valve portions 202S and 202T) is set. It should be thick. At this time, the height of the first and second discharge valve portions 202S and 202T on the fixed side is different from the height of the valve seats of the first and second discharge holes 190S and 190T, so the first and second discharge valves 400S and 400T. And the 1st, 2nd discharge valve holding | suppressing 401S, 401T (1st, 2nd discharge valve part 402S, 402T) is formed in step shape.

実施例２の冷媒通路４３６は、第１、第２ベーン溝１２８Ｓ、１２８Ｔ位置から時計回り方向に９０°の範囲内に配置されているので、冷媒通路４３６を通る冷媒ガスの温度よりも、冷媒通路４３６近傍の第１、第２圧縮室１３３Ｓ、１３３Ｔの第１、第２シリンダ内周面１２３Ｓ、１２３Ｔの温度が高い。そのため、冷媒通路４３６を通る冷媒ガスが、第１、第２シリンダ内周面１２３Ｓ、１２３Ｔの温度を上昇させることはなく、圧縮機効率が低下することはない。 Since the refrigerant passage 436 according to the second embodiment is disposed in a range of 90 ° in the clockwise direction from the first and second vane grooves 128S and 128T, the refrigerant passage 436 has a refrigerant temperature higher than that of the refrigerant gas passing through the refrigerant passage 436. The temperatures of the first and second cylinder inner peripheral surfaces 123S and 123T of the first and second compression chambers 133S and 133T in the vicinity of the passage 436 are high. Therefore, the refrigerant gas passing through the refrigerant passage 436 does not increase the temperature of the first and second cylinder inner peripheral surfaces 123S and 123T, and the compressor efficiency does not decrease.

１ロータリ圧縮機
１０圧縮機筐体
１１モータ
１２圧縮部
１５回転軸
１６給油パイプ
２５アキュムレータ
３１Ｓ第１低圧連絡管（低圧連絡管）
３１Ｔ第２低圧連絡管（低圧連絡管）
１０１第１貫通孔（貫通孔）
１０２第２貫通孔（貫通孔）
１０４第１吸入管（吸入管、吸入部）
１０５第２吸入管（吸入管、吸入部）
１０７吐出管（吐出部）
１１１ステータ
１１２ロータ
１２Ｓ第１の圧縮部（圧縮部）
１２Ｔ第２の圧縮部（圧縮部）
１２１Ｓ第１シリンダ（シリンダ）
１２１Ｔ第２シリンダ（シリンダ）
１２１ａ，３２１ａねじ孔
１２２Ｓ第１側方張出部（側方張出部）
１２２Ｔ第２側方張出部（側方張出部）
１２３Ｓ第１シリンダ内周面（シリンダ内周面）
１２３Ｔ第２シリンダ内周面（シリンダ内周面）
１２４Ｓ第１スプリング穴（スプリング穴）
１２４Ｔ第２スプリング穴（スプリング穴）
１２５Ｓ第１環状ピストン（環状ピストン）
１２５Ｔ第２環状ピストン（環状ピストン）
１２７Ｓ第１ベーン（ベーン）
１２７Ｔ第２ベーン（ベーン）
１２８Ｓ第１ベーン溝（ベーン溝）
１２８Ｔ第２ベーン溝（ベーン溝）
１２９Ｓ第１圧力導入路（圧力導入路）
１２９Ｔ第２圧力導入路（圧力導入路）
１３０Ｓ第１作動室（作動室）
１３０Ｔ第２作動室（作動室）
１３１Ｓ第１吸入室（吸入室）
１３１Ｔ第２吸入室（吸入室）
１３３Ｓ第１圧縮室（圧縮室）
１３３Ｔ第２圧縮室（圧縮室）
１３５Ｓ第１吸入孔（吸入孔）
１３５Ｔ第２吸入孔（吸入孔）
１３６，３３６，４３６冷媒通路
１４０中間仕切板
１５１副軸部
１５２Ｓ第１偏心部（偏心部）
１５２Ｔ第２偏心部（偏心部）
１５３主軸部
１６０Ｓ下端板（端板）
１６０Ｔ上端板（端板）
１６１Ｓ副軸受部（軸受部）
１６１Ｔ主軸受部（軸受部）
１６３Ｓ第１吐出弁溝
１６３Ｔ第２吐出弁溝
１７０Ｓ下マフラーカバー（マフラーカバー）
１７０Ｔ上マフラーカバー（マフラーカバー）
１７１マフラー吐出孔
１７５通しボルト
１８０Ｓ下マフラー室（マフラー室）
１８０Ｔ上マフラー室（マフラー室）
１９０Ｓ第１吐出孔（吐出孔）
１９０Ｔ第２吐出孔（吐出孔）
２００Ｓ，４００Ｓ第１吐出弁（吐出弁）
２００Ｔ，４００Ｔ第２吐出弁（吐出弁）
２０１Ｓ，４０１Ｓ第１吐出弁押さえ（吐出弁押さえ）
２０１Ｔ，４０１Ｔ第２吐出弁押さえ（吐出弁押さえ）
２０２Ｓ，４０２Ｓ第１吐出弁部
２０２Ｔ，４０２Ｔ第２吐出弁部
２５２アキュムホルダー
２５３アキュムバンド
２５５システム接続管
Ｒ第１、第２圧力導入路の開口部
DESCRIPTION OF SYMBOLS 1 Rotary compressor 10 Compressor housing | casing 11 Motor 12 Compression part 15 Rotating shaft 16 Oil supply pipe 25 Accumulator 31S 1st low-pressure connection pipe (low-pressure connection pipe)
31T Second low pressure connection pipe (low pressure connection pipe)
101 First through hole (through hole)
102 Second through hole (through hole)
104 1st suction pipe (suction pipe, suction part)
105 Second suction pipe (suction pipe, suction part)
107 Discharge pipe (discharge section)
111 Stator 112 Rotor 12S 1st compression part (compression part)
12T 2nd compression part (compression part)
121S 1st cylinder (cylinder)
121T 2nd cylinder (cylinder)
121a, 321a Screw hole 122S First lateral overhang (side overhang)
122T Second lateral overhang (side overhang)
123S 1st cylinder inner peripheral surface (cylinder inner peripheral surface)
123T 2nd cylinder inner surface (cylinder inner surface)
124S 1st spring hole (spring hole)
124T Second spring hole (spring hole)
125S first annular piston (annular piston)
125T second annular piston (annular piston)
127S 1st vane (vane)
127T 2nd vane (vane)
128S 1st vane groove (vane groove)
128T 2nd vane groove (vane groove)
129S First pressure introduction path (pressure introduction path)
129T Second pressure introduction path (pressure introduction path)
130S 1st working chamber (working chamber)
130T second working chamber (working chamber)
131S First suction chamber (suction chamber)
131T Second suction chamber (suction chamber)
133S 1st compression chamber (compression chamber)
133T Second compression chamber (compression chamber)
135S 1st suction hole (suction hole)
135T 2nd suction hole (suction hole)
136, 336, 436 Refrigerant passage 140 Intermediate partition plate 151 Sub shaft portion 152S First eccentric portion (eccentric portion)
152T second eccentric part (eccentric part)
153 Main shaft portion 160S Lower end plate (end plate)
160T Top plate (end plate)
161S Sub bearing part (bearing part)
161T Main bearing (bearing)
163S First discharge valve groove 163T Second discharge valve groove 170S Lower muffler cover (muffler cover)
170T Upper muffler cover (muffler cover)
171 Muffler discharge hole 175 Through bolt 180S Lower muffler chamber (muffler chamber)
180T Upper muffler room (muffler room)
190S 1st discharge hole (discharge hole)
190T Second discharge hole (discharge hole)
200S, 400S 1st discharge valve (discharge valve)
200T, 400T Second discharge valve (discharge valve)
201S, 401S First discharge valve presser (discharge valve presser)
201T, 401T Second discharge valve presser (discharge valve presser)
202S, 402S 1st discharge valve part 202T, 402T 2nd discharge valve part 252 Accum holder 253 Accum band 255 System connection pipe R Opening part of 1st, 2nd pressure introduction path

Claims

A vertically-placed cylindrical compressor housing which is provided with a refrigerant discharge part at the top and a refrigerant suction part at the bottom and sealed;
A lower upper end plate disposed at a lower portion of the compressor housing, having annular first and second cylinders, a bearing portion and a discharge valve portion, and closing the end portions of the first and second cylinders; An intermediate partition plate arranged between the first and second cylinders and partitioning between the two and the eccentric part of the rotating shaft supported by the bearing part is fitted along the inner peripheral surface of the first and second cylinders. The first and second annular pistons that revolve inside the cylinder and form a working chamber between the cylinder inner peripheral surface and the vane groove provided in the first and second cylinders project into the working chamber. The first and second vanes contacting the first and second annular pistons and partitioning the working chamber into a suction chamber and a compression chamber, and a muffler discharge hole communicating with the interior of the compressor housing. Upper muffler that covers the discharge valve portion of the upper end plate and forms an upper muffler chamber with the upper end plate A bar, a lower muffler cover that covers the discharge valve portion of the lower end plate and forms a lower muffler chamber between the lower end plate, the lower, upper end plate, the first and second cylinders, and the intermediate partition plate. A refrigerant passage that communicates between the upper and lower muffler chambers, and a compressor that sucks refrigerant from the low-pressure side of the refrigeration cycle through the suction part and discharges the refrigerant from the discharge part through the compressor housing;
A motor that is installed in an upper part of the compressor housing and drives the compression unit via the rotating shaft;
A rotary compressor comprising:
A rotary compressor, wherein the refrigerant passages provided in the first and second cylinders are arranged within a range of a phase angle of 270 ° to 360 ° in a revolving direction of the annular piston from a vane groove position.

The refrigerant passage provided in the first and second cylinders is disposed radially outwardly from a discharge valve groove that is provided in the lower and upper end plates and accommodates the discharge valve portion. Rotary compressor.

2. The rotary compressor according to claim 1, wherein a discharge valve groove that is provided in the lower and upper end plates and accommodates the discharge valve portion is disposed on a suction hole side provided in the first and second cylinders. .