JP2014145317A - Rotary compressor - Google Patents

Rotary compressor Download PDF

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JP2014145317A
JP2014145317A JP2013014872A JP2013014872A JP2014145317A JP 2014145317 A JP2014145317 A JP 2014145317A JP 2013014872 A JP2013014872 A JP 2013014872A JP 2013014872 A JP2013014872 A JP 2013014872A JP 2014145317 A JP2014145317 A JP 2014145317A
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plate
muffler
chamber
compressor
compression
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JP6111695B2 (en
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Junya Tanaka
順也 田中
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Fujitsu General Ltd
株式会社富士通ゼネラル
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Abstract

PROBLEM TO BE SOLVED: To provide a rotary compressor which suppresses the vibration of a bypass pipe with no possibility of deforming a muffler cover and no production of oxidized scales.SOLUTION: In the rotary compressor, a refrigerant passage 136 includes L-shaped lower and upper end plate communication holes provided in lower and upper end plates 160S, 160T, and consisting of vertical holes 136S, 136T communicated with muffler chambers 180S, 180T and lateral holes 136A, 136T communicating the vertical holes 136S, 136T with the lateral sides of the lower and upper end plates 160S, 160T, respectively, and a bypass pipe 136K whose ends are pressed and fixed into the lateral holes 136A, 136B of the lower and upper end plates 160S, 160T and which are arranged outside a compression part 12.

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.
従来、ロータリ圧縮機の起動時や外気温が低いときの低速運転など、ΔT(圧縮機底部の潤滑油温−吐出冷媒の凝縮温度)が小さくなる運転条件では、圧縮機底部(油溜め)の潤滑油中への冷媒溶け込み量が増え、油粘度が低下し、冷媒圧縮部の摺動性が悪化して圧縮機の信頼性が損なわれる。   Conventionally, under operating conditions where ΔT (lubricating oil temperature at the bottom of the compressor−condensation temperature of the discharged refrigerant) is low, such as when the rotary compressor is started up or when the outside air temperature is low, the compressor bottom (oil sump) The amount of refrigerant dissolved in the lubricating oil increases, the oil viscosity decreases, the slidability of the refrigerant compression section deteriorates, and the reliability of the compressor is impaired.
油溜めの潤滑油の熱は、圧縮機筐体と圧縮機脚部を通して圧縮機外部に放熱されるため、圧縮室から吐出された直後の冷媒ガスに比べて油溜めの潤滑油は温度が低い。そこで、圧縮室から下マフラー室に吐出された高温の冷媒ガスを上マフラー室に導く冷媒通路を圧縮部(シリンダなど)には設けず、下マフラー室と上マフラー室を連通するバイパス管を圧縮部の外部に設ける(例えば、特許文献1参照)。この従来の技術によれば、バイパス管を流れる冷媒ガスが油溜めの潤滑油温を上昇させ、ΔTを大きくすることができる。   The heat of the oil in the oil sump is radiated to the outside of the compressor through the compressor housing and the compressor legs, so the temperature of the oil in the sump is lower than that of the refrigerant gas immediately after being discharged from the compression chamber. . Therefore, a compression passage (cylinder, etc.) is not provided in the compression section (cylinder, etc.) to guide the high-temperature refrigerant gas discharged from the compression chamber to the lower muffler chamber, and the bypass pipe that connects the lower muffler chamber and the upper muffler chamber is compressed. It is provided outside the unit (for example, see Patent Document 1). According to this conventional technique, the refrigerant gas flowing through the bypass pipe can raise the temperature of the lubricating oil in the oil sump and increase ΔT.
また、この従来の技術によれば、バイパス管を圧縮部の外部に設けているので、バイパス管を流れる冷媒ガスが圧縮部の温度を上昇させることはない。そのため、圧縮部内の吸入冷媒や圧縮途中の冷媒ガスが加熱されて圧縮機効率が低下するのを防ぐことができる。   Moreover, according to this prior art, since the bypass pipe is provided outside the compression section, the refrigerant gas flowing through the bypass pipe does not raise the temperature of the compression section. Therefore, it is possible to prevent the compressor efficiency from being lowered due to heating of the suction refrigerant in the compression section and the refrigerant gas being compressed.
また、従来、副軸受部及び下マフラーカバーは潤滑油に浸かっているうえに、冷媒ガスよりも高温となるモータからも遠い。これに対して、主軸受部及び上マフラーカバーは潤滑油に浸かっておらず、モータにも近い。そのため、副軸受部に比較して主軸受部は、温度が高くなる。   Conventionally, the sub-bearing portion and the lower muffler cover are immersed in the lubricating oil and further away from the motor that is hotter than the refrigerant gas. On the other hand, the main bearing portion and the upper muffler cover are not immersed in the lubricating oil and are close to the motor. Therefore, the temperature of the main bearing portion is higher than that of the auxiliary bearing portion.
上記の従来の技術によれば、バイパス管で冷却された冷媒ガスが上マフラー室に流入するので、上マフラー室の温度が低下し、上マフラー室内にある上軸受部の温度も低下する。そのため、上軸受部から圧縮部への伝熱量が低下し、吸入冷媒や圧縮途中の冷媒ガスの加熱が抑えられ、圧縮機効率の低下を防止することができる。   According to the above conventional technique, the refrigerant gas cooled by the bypass pipe flows into the upper muffler chamber, so that the temperature of the upper muffler chamber is lowered and the temperature of the upper bearing portion in the upper muffler chamber is also lowered. As a result, the amount of heat transferred from the upper bearing portion to the compression portion is reduced, and heating of the suction refrigerant and refrigerant gas during compression is suppressed, and a reduction in compressor efficiency can be prevented.
特開2003−97477号公報(図1)Japanese Patent Laying-Open No. 2003-97477 (FIG. 1)
しかしながら、上記従来の技術によれば、バイパス管を、薄板をプレス加工した下、上マフラーカバーの側部に接続している。薄板に、バイパス管を圧入により接続することは難しい。そのため、溶接によりバイパス管を接続しなければならないが、溶接時にマフラーカバーが変形しやすく、マフラーカバーと端板との密着性が悪くなり、ガス漏れが発生する、という問題がある。   However, according to the above-described conventional technique, the bypass pipe is connected to the side portion of the upper muffler cover while the thin plate is pressed. It is difficult to connect the bypass pipe to the thin plate by press fitting. Therefore, the bypass pipe must be connected by welding, but there is a problem that the muffler cover is easily deformed during welding, the adhesion between the muffler cover and the end plate is deteriorated, and gas leakage occurs.
また、バイパス管は、下、上マフラーカバーを圧縮部に取付けた後に、下、上マフラーカバーに溶接されるが、溶接時に発生する酸化スケールなどがマフラーカバー内部に残留すると、除去することは難しい。この酸化スケールなどが圧縮機の運転時に圧縮部に入り込むと、圧縮部の異常摩耗やロックに至る可能性がある。また、薄板製のマフラーカバーにバイパス管を接続すると、バイパス管が振動しやすくなり、その振動がマフラーカバーに伝達されて騒音が増大する、という問題がある。   In addition, the bypass pipe is welded to the lower and upper muffler covers after the lower and upper muffler covers are attached to the compression section, but it is difficult to remove if the oxidized scale, etc. generated during welding remain inside the muffler cover. . If this oxide scale or the like enters the compression section during operation of the compressor, it may lead to abnormal wear or locking of the compression section. In addition, when a bypass pipe is connected to a thin plate muffler cover, the bypass pipe is likely to vibrate, and the vibration is transmitted to the muffler cover to increase noise.
本発明は、上記に鑑みてなされたものであって、マフラーカバーが変形するおそれがなく、酸化スケールなどが発生することがなく、バイパス管の振動を抑え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 in which the muffler cover is not likely to be deformed, oxide scale is not generated, and vibration of the bypass pipe is suppressed. To do.
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配置され、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、前記冷媒通路は、前記下、上端板に設けられ、マフラー室に連通する縦孔と該縦孔を前記下、上端板の側部に連通させる横孔とからなるL字形の端板連通孔と、前記下、上端板の夫々の横孔に夫々の端部が圧入固定され前記圧縮部の外部に配置されたバイパス管と、を備えることを特徴とする。   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 a refrigerant passage that communicates between the upper and lower muffler chambers, A compressor that sucks refrigerant from the low-pressure side and discharges the refrigerant from the discharge part through the compressor casing, and a motor that is disposed at the top of the compressor casing and drives the compressor via the rotating shaft The refrigerant passage is provided in the lower and upper end plates, and includes a vertical hole that communicates with the muffler chamber and a horizontal hole that communicates the vertical hole with a side portion of the lower and upper end plates. L-shaped end plate communication hole and front Lower, characterized in that it comprises a bypass pipe ends of the respective next hole of each of the upper end plate is press-fitted is arranged outside the compression unit.
本発明によれば、マフラーカバーが変形するおそれがなく、酸化スケールなどが発生することがなく、バイパス管の振動を抑えたロータリ圧縮機が得られる、という効果を奏する。   According to the present invention, it is possible to obtain a rotary compressor in which the muffler cover is not likely to be deformed, oxide scales and the like are not generated, and vibration of the bypass pipe is suppressed.
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、実施例の第1、第2の圧縮部を示す平面図である。FIG. 2 is a plan view showing the first and second compression units of the embodiment. 図3は、実施例1のバイパス管を備える圧縮部を示す縦断面図である。FIG. 3 is a longitudinal sectional view illustrating a compression unit including the bypass pipe according to the first embodiment. 図4は、実施例2のバイパス管を備える圧縮部を示す縦断面図である。FIG. 4 is a longitudinal cross-sectional view illustrating a compression unit including the bypass pipe according to the second embodiment.
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.
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 second operation of the first working chamber 130S of the first cylinder 121S and the second cylinder 121T. The 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、冷媒通路としてのバイパス管136K(図3参照)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。バイパス管136Kの詳細については後述する。   The lower muffler chamber 180S is a single chamber formed in an annular shape, and communicates the discharge side of the first compression unit 12S into the upper muffler chamber 180T through a bypass pipe 136K (see FIG. 3) as a refrigerant passage. Part of the passage. 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 bypass pipe 136K 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のバイパス管を備える圧縮部を示す縦断面図である。   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 longitudinal sectional view illustrating a compression unit including the bypass pipe according to the first embodiment.
図3に示すように、実施例1の冷媒通路136は、下端板160Sに設けられ下マフラー室180Sに連通する縦孔136Sと縦孔136Sを下端板160Sの側部に連通させる横孔136AとからなるL字形の下端板連通孔と、上端板160Tに設けられ上マフラー室180Tに連通する縦孔136Tと縦孔136Tを上端板160Tの側部に連通させる横孔136BとからなるL字形の上端板連通孔と、下、上端板160S、160Tの夫々の横孔136A、136Bに夫々の端部が圧入固定され圧縮部12の外部に配置されたバイパス管136Kと、を備えてなる。   As shown in FIG. 3, the refrigerant passage 136 according to the first embodiment includes a vertical hole 136S provided in the lower end plate 160S and communicating with the lower muffler chamber 180S, and a horizontal hole 136A communicating the vertical hole 136S with the side portion of the lower end plate 160S. An L-shaped lower end plate communication hole, a vertical hole 136T provided in the upper end plate 160T and communicating with the upper muffler chamber 180T, and a horizontal hole 136B connecting the vertical hole 136T to the side of the upper end plate 160T. The upper end plate communication hole, and a bypass pipe 136K disposed at the outside of the compression unit 12 with the respective end portions being press-fitted and fixed in the horizontal holes 136A and 136B of the lower and upper end plates 160S and 160T, respectively.
実施例1の冷媒通路136は、バイパス管136Kの両端部を、厚板状の下、上端板160S、160Tの側部の横孔136A、136Bに圧入固定し、バイパス管136Kを圧縮部12の外部に配置したので、下、上マフラーカバー170S、170Tが変形することはなく、溶接時の酸化スケールなどが発生することもなく、バイパス管136Kが振動することもない。   In the refrigerant passage 136 according to the first embodiment, both end portions of the bypass pipe 136K are press-fitted and fixed to the lateral holes 136A and 136B on the side portions of the upper end plates 160S and 160T under the thick plate shape, and the bypass pipe 136K is Since it is arranged outside, the lower and upper muffler covers 170S and 170T are not deformed, oxide scales are not generated during welding, and the bypass pipe 136K is not vibrated.
図4は、実施例2のバイパス管を備える圧縮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336は、下端板160Sに設けられ下マフラー室180Sに連通する縦孔336Sと縦孔336Sを下端板160Sの側部に連通させる横孔336AとからなるL字形の端板連通孔と、上端板160Tに設けられ上マフラー室180Tに連通する縦孔336Tと縦孔336Tを上端板160Tの側部に連通させる横孔336BとからなるL字形の端板連通孔と、下、上端板160S、160Tの夫々の横孔336A、336Bに夫々の端部が圧入固定され圧縮部12の外部に配置されたバイパス管336Kと、を備えてなる。バイパス管336Kは、中間部が圧縮機筐体10の底部の油溜めに配置され、油溜め内で螺旋巻きされ、潤滑油への放熱区間を長くしている。   FIG. 4 is a longitudinal cross-sectional view illustrating a compression unit including the bypass pipe according to the second embodiment. As shown in FIG. 4, the refrigerant passage 336 of the second embodiment includes a vertical hole 336S provided in the lower end plate 160S and communicating with the lower muffler chamber 180S, and a horizontal hole 336A communicating the vertical hole 336S with the side portion of the lower end plate 160S. An L-shaped end plate communication hole, a vertical hole 336T provided in the upper end plate 160T and communicating with the upper muffler chamber 180T, and a horizontal hole 336B connecting the vertical hole 336T to the side of the upper end plate 160T. An end plate communication hole, and a bypass pipe 336K disposed at the outside of the compression portion 12 with the respective end portions being press-fitted and fixed in the horizontal holes 336A and 336B of the lower and upper end plates 160S and 160T, respectively. The bypass pipe 336 </ b> K is disposed in the oil sump at the bottom of the compressor housing 10 and is spirally wound in the oil sump to lengthen the heat dissipation section for the lubricating oil.
実施例2の冷媒通路336は、バイパス管336Kの両端部を、厚板状の下、上端板160S、160Tの側部の横孔336A、336Bに圧入固定し、バイパス管336Kを圧縮部12の外部に配置したので、下、上マフラーカバー170S、170Tが変形することはなく、溶接時の酸化スケールなどが発生することもなく、バイパス管336Kの振動がマフラーカバーに伝達されることもない。   In the refrigerant passage 336 of the second embodiment, both end portions of the bypass pipe 336K are press-fitted and fixed to the lateral holes 336A and 336B on the side portions of the upper end plates 160S and 160T under the thick plate shape, and the bypass pipe 336K is Since it is arranged outside, the lower and upper muffler covers 170S and 170T are not deformed, no oxide scale is generated during welding, and the vibration of the bypass pipe 336K is not transmitted to the muffler cover.
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)
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 冷媒通路
136S,136T、336S,336T 縦孔
136A,136B,336A、336B 横孔
136K、336K バイパス管
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)
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 第1吐出弁(吐出弁)
200T 第2吐出弁(吐出弁)
201S 第1吐出弁押さえ(吐出弁押さえ)
201T 第2吐出弁押さえ(吐出弁押さえ)
202S 第1吐出弁部
202T 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)
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 Refrigerant passage 136S, 136T, 336S, 336T Vertical hole 136A, 136B, 336A, 336B Horizontal hole 136K, 336K Bypass pipe 140 Intermediate partition plate 151 Subshaft part 152S First eccentric part (eccentric part)
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)
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 1st discharge valve (discharge valve)
200T Second discharge valve (discharge valve)
201S First discharge valve presser (discharge valve presser)
201T Second discharge valve presser (discharge valve presser)
202S 1st discharge valve part 202T 2nd discharge valve part 252 Accum holder 253 Accum band 255 System connection pipe R Opening part of 1st, 2nd pressure introduction path

Claims (2)

  1. 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シリンダに設けられた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配置され、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、
    前記冷媒通路は、
    前記下、上端板に設けられ、マフラー室に連通する縦孔と該縦孔を前記下、上端板の側部に連通させる横孔とからなるL字形の下、上端板連通孔と、
    前記下、上端板の夫々の横孔に夫々の端部が圧入固定され前記圧縮部の外部に配置されたバイパス管と、
    を備えることを特徴とするロータリ圧縮機。
    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 And a lower muffler cover that covers a discharge valve portion of the lower end plate and forms a lower muffler chamber between the lower end plate and a refrigerant passage that communicates between the upper and lower muffler chambers. A compressor that sucks refrigerant from the low-pressure side of the refrigeration cycle through the unit, and discharges refrigerant from the discharge unit through the compressor housing;
    A motor that is disposed at the top of the compressor housing and drives the compression unit via the rotating shaft;
    A rotary compressor comprising:
    The refrigerant passage is
    An L-shaped lower upper end plate communicating hole provided in the lower upper end plate and comprising a vertical hole communicating with the muffler chamber and a horizontal hole communicating the vertical hole with a side portion of the lower upper end plate;
    The lower and the bypass pipes, each end of which is press-fitted and fixed to each lateral hole of the upper end plate, and disposed outside the compression unit,
    A rotary compressor comprising:
  2. 前記バイパス管は、中間部が前記圧縮機筐体の底部に配置されていることを特徴とする請求項1に記載のロータリ圧縮機。
    The rotary compressor according to claim 1, wherein an intermediate portion of the bypass pipe is disposed at a bottom portion of the compressor casing.
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