JP5201045B2 - 2-stage compression rotary compressor - Google Patents

2-stage compression rotary compressor Download PDF

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JP5201045B2
JP5201045B2 JP2009072896A JP2009072896A JP5201045B2 JP 5201045 B2 JP5201045 B2 JP 5201045B2 JP 2009072896 A JP2009072896 A JP 2009072896A JP 2009072896 A JP2009072896 A JP 2009072896A JP 5201045 B2 JP5201045 B2 JP 5201045B2
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健史 上田
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Fujitsu General Ltd
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Description

本発明は、空気調和機の冷凍サイクルに使用される２段圧縮ロータリ圧縮機（以下、単に「ロータリ圧縮機」ともいう。）に関する。   The present invention relates to a two-stage compression rotary compressor (hereinafter also simply referred to as “rotary compressor”) used in a refrigeration cycle of an air conditioner.

一般に、２段圧縮ロータリ圧縮機は、密閉された円筒状の圧縮機筐体内部に、低段側圧縮部及び高段側圧縮部と、低段側圧縮部及び高段側圧縮部を駆動するモータと、を備え、圧縮機本体筐体の側方にアキュムレータを備えている。   Generally, a two-stage compression rotary compressor drives a low-stage compression section and a high-stage compression section, and a low-stage compression section and a high-stage compression section inside a sealed cylindrical compressor casing. And an accumulator on the side of the compressor body housing.

従来、密閉容器内にモータと、該モータにて駆動される低段側圧縮部及び高段側圧縮部を備え、前記低段側圧縮部で圧縮され、吐出された冷媒ガスを前記高段側圧縮部に吸引し、圧縮して吐出する２段圧縮ロータリ圧縮機において、前記高段側圧縮部の吐出孔を前記低段側吐出孔よりも小さくした２段圧縮ロータリ圧縮機が開示されている（例えば、特許文献１参照）。   Conventionally, a sealed container is provided with a motor, a low-stage compression section and a high-stage compression section driven by the motor, and the refrigerant gas compressed and discharged by the low-stage compression section is discharged to the high-stage side. In a two-stage compression rotary compressor that sucks into a compression section and compresses and discharges the two-stage compression rotary compressor, the discharge hole of the high-stage compression section is smaller than the low-stage discharge hole. (For example, refer to Patent Document 1).

特開２００２−９８０８１号公報JP 2002-98081 A

しかしながら、上記従来の技術によれば、低段側圧縮部及び高段側圧縮部の吐出弁の厚さを同一とし、低段側吐出孔を高段側吐出孔より大きくすると、吐出孔が大きくなった分、低段側吐出弁の差圧受圧面積が大きくなる。そのため、低段側吐出弁の凹み変形量が大きくなり、低段側吐出弁が吐出孔のエッジ部と高面圧で当接し、低段側吐出弁及びエッジ部の磨耗が早まって耐久性が低下する、という問題があった。   However, according to the above conventional technique, when the thickness of the discharge valve of the low-stage compression section and the high-stage compression section is the same, and the low-stage discharge hole is larger than the high-stage discharge hole, the discharge hole becomes large. Therefore, the differential pressure receiving area of the low stage side discharge valve is increased. Therefore, the amount of dent deformation on the low-stage discharge valve increases, the low-stage discharge valve abuts against the edge of the discharge hole with high surface pressure, and wear of the low-stage discharge valve and edge is accelerated and durability is increased. There was a problem of lowering.

また、低段側圧縮部及び高段側圧縮部の吐出弁厚さが同一で、高段側圧縮部よりも低段側圧縮部の方が吐出孔径が大きいため、高段側吐出弁に対して低段側吐出弁の閉じ遅れが発生し、吐出された冷媒がマフラー室から圧縮室へ逆流しやすくなり、圧縮効率が低下する、という問題があった。   Also, the discharge valve thickness of the low-stage compression section and the high-stage compression section is the same, and the discharge hole diameter of the low-stage compression section is larger than that of the high-stage compression section. As a result, there is a problem in that the closing delay of the low-stage discharge valve occurs, the discharged refrigerant easily flows back from the muffler chamber to the compression chamber, and the compression efficiency decreases.

本発明は、上記に鑑みてなされたものであって、低段側圧縮部の低段側吐出弁の変形を抑えて低段側吐出弁の耐久性を向上させるとともに、低段側吐出弁の閉じ遅れを防止して圧縮効率を向上することができる２段圧縮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 while suppressing the deformation of the low-stage discharge valve of the low-stage compression section, the durability of the low-stage discharge valve is improved, and the low-stage discharge valve It is an object of the present invention to obtain a two-stage compression rotary compressor that can prevent the closing delay and improve the compression efficiency.

上述した課題を解決し、目的を達成するために、本発明は、低段側圧縮部、高段側圧縮部及び該低段側、高段側圧縮部を駆動するモータを圧縮機筺体内に収容し、前記低段側圧縮部で圧縮され吐出された冷媒を前記高段側圧縮部に吸入し、さらに圧縮して吐出する２段圧縮ロータリ圧縮機において、前記高段側圧縮部の高段側吐出孔を前記低段側圧縮部の低段側吐出孔よりも小さくし、前記低段側吐出孔の出口側に設置されたリード弁型の低段側吐出弁の厚さを、前記高段側吐出孔の出口側に設置されたリード弁型の高段側吐出弁の厚さより厚くしたことを特徴とする。
In order to solve the above-described problems and achieve the object, the present invention includes a low-stage compression section, a high-stage compression section, and a motor for driving the low-stage compression section and the high-stage compression section in the compressor housing. In the two-stage compression rotary compressor that stores, sucks the refrigerant compressed and discharged by the low-stage compression section into the high-stage compression section, and further compresses and discharges the refrigerant, the high-stage of the high-stage compression section The side discharge hole is made smaller than the low stage side discharge hole of the low stage side compression portion, and the thickness of the reed valve type low stage side discharge valve installed on the outlet side of the low stage side discharge hole is set to the high level. It is characterized by being thicker than the thickness of the reed valve type high- stage discharge valve installed on the outlet side of the stage-side discharge hole .

本発明にかかる２段圧縮ロータリ圧縮機は、低段側吐出弁の厚さを、高段側吐出弁の厚さより厚くしたことにより、低段側吐出弁の変形量を抑えて吐出弁の耐久性を向上することができる、という効果を奏する。また、低段側吐出弁の閉じ遅れを防止して圧縮効率を向上することができる。   In the two-stage compression rotary compressor according to the present invention, the thickness of the low-stage side discharge valve is made larger than the thickness of the high-stage side discharge valve, so that the deformation amount of the low-stage side discharge valve is suppressed and the durability of the discharge valve is improved. The effect that it can improve property is produced. Further, it is possible to improve the compression efficiency by preventing the closing delay of the low-stage discharge valve.

図１は、本発明にかかる２段圧縮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 two-stage compression rotary compressor according to the present invention. 図２は、実施例の２段圧縮ロータリ圧縮機の低段側圧縮部及び高段側圧縮部の横断面図である。FIG. 2 is a cross-sectional view of the low-stage compression section and the high-stage compression section of the two-stage compression rotary compressor of the embodiment. 図３は、図１のＡ−Ａ線に沿う横断面図である。FIG. 3 is a cross-sectional view taken along line AA in FIG. 図４は、実施例の２段圧縮ロータリ圧縮機の低段側端板の横断面図である。FIG. 4 is a cross-sectional view of the low-stage end plate of the two-stage compression rotary compressor of the embodiment. 図５は、図４のＣ−Ｃ線に沿う断面図である。FIG. 5 is a cross-sectional view taken along the line CC of FIG. 図６は、図１のＢ−Ｂ線に沿う横断面図である。6 is a cross-sectional view taken along line BB in FIG. 図７は、実施例の２段圧縮ロータリ圧縮機の高段側端板の横断面図である。FIG. 7 is a cross-sectional view of the high-stage end plate of the two-stage compression rotary compressor of the embodiment. 図８は、図７のＤ−Ｄ線に沿う断面図である。8 is a cross-sectional view taken along the line DD of FIG. 図９は、実施例の２段圧縮ロータリ圧縮機の側面図である。FIG. 9 is a side view of the two-stage compression rotary compressor of the embodiment.

以下に、本発明にかかる２段圧縮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 two-stage compression rotary compressor according to the present invention will be described below in detail with reference to the drawings. Note that the present invention is not limited to the embodiments.

図１は、本発明にかかる２段圧縮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２段圧縮ロータリ圧縮機の低段側圧縮部及び高段側圧縮部の横断面図であり、図３は、図１のＡ−Ａ線に沿う横断面図であり、図４は、実施例の２段圧縮ロータリ圧縮機の低段側端板の横断面図であり、図５は、図４のＣ−Ｃ線に沿う断面図であり、図６は、図１のＢ−Ｂ線に沿う横断面図であり、図７は、実施例の２段圧縮ロータリ圧縮機の高段側端板の横断面図であり、図８は、図７のＤ−Ｄ線に沿う断面図であり、図９は、実施例の２段圧縮ロータリ圧縮機の側面図である。   FIG. 1 is a longitudinal sectional view showing an embodiment of a two-stage compression rotary compressor according to the present invention. FIG. 2 shows a low-stage compression section and a high-stage compression section of the two-stage compression rotary compressor of the embodiment. 3 is a cross-sectional view taken along line AA in FIG. 1, and FIG. 4 is a cross-sectional view of the low-stage side end plate of the two-stage compression rotary compressor of the embodiment. 5 is a cross-sectional view taken along line CC in FIG. 4, FIG. 6 is a cross-sectional view taken along line BB in FIG. 1, and FIG. 7 is a two-stage compression rotary according to the embodiment. FIG. 8 is a cross-sectional view of the high-stage end plate of the compressor, FIG. 8 is a cross-sectional view taken along the line DD in FIG. 7, and FIG. 9 is a side view of the two-stage compression rotary compressor of the embodiment. is there.

図１に示すように、実施例の２段圧縮ロータリ圧縮機１は、密閉された円筒状の圧縮機筐体１０の内部に、圧縮部１２と、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 two-stage compression rotary compressor 1 of the embodiment includes a compression unit 12 and a motor 11 that drives the compression unit 12 in a sealed cylindrical compressor housing 10. I have.

モータ１１のステータ１１１は、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、ステータ１１１の中央部に配置され、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 fixed by being shrink-fitted on the inner peripheral surface of the compressor housing 10. The rotor 112 of the motor 11 is disposed at the center of the 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、低段側圧縮部１２Ｌと、低段側圧縮部１２Ｌに直列に接続され低段側圧縮部１２Ｌの上側に積層されて設置された高段側圧縮部１２Ｈと、を備えて成る。図２に示すように、低段側圧縮部１２Ｌは、短い円筒状の低段側シリンダ１２１Ｌを備え、高段側圧縮部１２Ｈは、短い円筒状の高段側シリンダ１２１Ｈを備えている。   The compression unit 12 includes a low-stage compression unit 12L, and a high-stage compression unit 12H connected in series to the low-stage compression unit 12L and stacked and installed on the upper side of the low-stage compression unit 12L. Become. As shown in FIG. 2, the low-stage compression section 12L includes a short cylindrical low-stage cylinder 121L, and the high-stage compression section 12H includes a short cylindrical high-stage cylinder 121H.

低段側シリンダ１２１Ｌ及び高段側シリンダ１２１Ｈには、夫々モータ１１と同芯に、低段側、高段側シリンダ内壁１２３Ｌ、１２３Ｈが形成されている。夫々のシリンダ内壁１２３Ｌ、１２３Ｈ内には、低段、高段シリンダ内径よりも小さい外径の円筒状の低段側、高段側ピストン１２５Ｌ，１２５Ｈが夫々配置され、夫々のシリンダ内壁１２３Ｌ、１２３Ｈと、低段側、高段側ピストン１２５Ｌ、１２５Ｈの間に、冷媒を吸入し圧縮して吐出する低段側、高段側作動室１３０Ｌ、１３０Ｈ（圧縮空間）が形成される。   The low-stage cylinder 121L and the high-stage cylinder 121H are respectively provided with inner walls 123L and 123H on the low-stage side and the high-stage side that are concentric with the motor 11. In each of the cylinder inner walls 123L and 123H, cylindrical low-stage and high-stage pistons 125L and 125H having outer diameters smaller than the inner diameters of the low-stage and high-stage cylinders are arranged, respectively, and the respective cylinder inner walls 123L and 123H are arranged. The low-stage side and high-stage side working chambers 130L and 130H (compression spaces) are formed between the low-stage side and high-stage side pistons 125L and 125H.

低段、高段シリンダ１２１Ｌ、１２１Ｈには、低段、高段シリンダ内壁１２３Ｌ、１２３Ｈから径方向に、シリンダ高さ全域に亘る低段側、高段側ベーン溝が形成され、この溝内に、板状の低段側、高段側ベーン１２７Ｌ、１２７Ｈが嵌合されている。低段側、高段側ベーン１２７Ｌ、１２７Ｈの圧縮機筐体１０側には、低段側、高段側スプリング１２９Ｌ、１２９Ｈが装着されている。   The low-stage and high-stage cylinders 121L and 121H have low-stage and high-stage vane grooves extending from the low-stage and high-stage cylinder inner walls 123L and 123H in the radial direction over the entire cylinder height. The plate-like low stage side and high stage vanes 127L and 127H are fitted. Low-stage and high-stage springs 129L and 129H are mounted on the compressor housing 10 side of the low-stage and high-stage vanes 127L and 127H.

この低段側、高段側スプリング１２９Ｌ、１２９Ｈの反撥力により、低段側、高段側ベーン１２７Ｌ、１２７Ｈの先端が、低段側、高段側ピストン１２５Ｌ、１２５Ｈの外周面に押し付けられ、低段側、高段側ベーン１２７Ｌ、１２７Ｈにより、低段側、高段側作動室１３０Ｌ、１３０Ｈが、低段側、高段側吸入室１３１Ｌ、１３１Ｈと、低段側、高段側圧縮室１３３Ｌ、１３３Ｈとに区画される。   Due to the repulsive force of the low-stage and high-stage springs 129L and 129H, the tips of the low-stage and high-stage vanes 127L and 127H are pressed against the outer peripheral surfaces of the low-stage and high-stage pistons 125L and 125H. The low-stage and high-stage vanes 127L and 127H make the low-stage and high-stage working chambers 130L and 130H into the low-stage and high-stage suction chambers 131L and 131H, and the low-stage and high-stage compression chambers. It is partitioned into 133L and 133H.

低段側、高段側シリンダ１２１Ｌ、１２１Ｈには、低段側、高段側吸入室１３１Ｌ、１３１Ｈに冷媒を吸入するために、低段側、高段側吸入室１３１Ｌ、１３１Ｈに連通する低段側、高段側吸入孔１３５Ｌ、１３５Ｈが設けられ、低段側シリンダ１２１Ｌの低段側吸入孔１３５Ｌ、高段側シリンダ１２１Ｈの高段側吸入孔１３５Ｈ及び後述する低段側マフラー吐出孔２１０Ｌは同一周方向に向けて設けられている。   The low-stage and high-stage cylinders 121L and 121H are connected to the low-stage and high-stage suction chambers 131L and 131H in order to suck the refrigerant into the low-stage and high-stage suction chambers 131L and 131H. Stage-side and high-stage side suction holes 135L and 135H are provided. The low-stage side suction hole 135L of the low-stage side cylinder 121L, the high-stage side suction hole 135H of the high-stage side cylinder 121H, and a low-stage side muffler discharge hole 210L described later. Are provided in the same circumferential direction.

また、低段側シリンダ１２１Ｌと高段側シリンダ１２１Ｈとの間には、中間仕切板１４０が設置され、低段側シリンダ１２１Ｌの低段作動室１３０Ｌと高段側シリンダ１２１Ｈの高段作動室１３０Ｈとを区画している。低段側シリンダ１２１Ｌの下側には、低段側端板１６０Ｌが設置され、低段側シリンダ１２１Ｌの低段作動室１３０Ｌの下部を閉塞している。また、高段側シリンダ１２１Ｈの上側には、高段側端板１６０Ｈが設置され、高段側シリンダ１２１Ｈの高段作動室１３０Ｈの上部を閉塞している。   Further, an intermediate partition plate 140 is installed between the low stage side cylinder 121L and the high stage side cylinder 121H, and the low stage working chamber 130L of the low stage side cylinder 121L and the high stage working chamber 130H of the high stage side cylinder 121H. And is divided. A low-stage end plate 160L is installed below the low-stage cylinder 121L, and closes the lower part of the low-stage working chamber 130L of the low-stage cylinder 121L. A high stage end plate 160H is installed above the high stage cylinder 121H, and closes the upper part of the high stage working chamber 130H of the high stage cylinder 121H.

低段側端板１６０Ｌには、下軸受け部１６１Ｌが形成され、下軸受け部１６１Ｌに、回転軸１５の下部１５１が回転自在に支持されている。また、高段側端板１６０Ｈには、上軸受け部１６１Ｈが形成され、上軸受け部１６１Ｈに、回転軸１５の中間部１５３が回転自在に支持されている。   A lower bearing portion 161L is formed on the lower stage end plate 160L, and a lower portion 151 of the rotating shaft 15 is rotatably supported by the lower bearing portion 161L. Further, the upper stage end plate 160H is formed with an upper bearing portion 161H, and an intermediate portion 153 of the rotating shaft 15 is rotatably supported by the upper bearing portion 161H.

回転軸１５は、互いに１８０°位相をずらして偏芯させた低段側偏芯部１５２Ｌと高段側偏芯部１５２Ｈとを備え、低段側偏芯部１５２Ｌは、低段側圧縮部１２Ｌの低段側ピストン１２５Ｌを回転自在に保持し、高段側偏芯部１５２Ｈは、高段側圧縮部１２Ｈの高段側ピストン１２５Ｈを回転自在に保持している。   The rotating shaft 15 includes a low-stage eccentric portion 152L and a high-stage eccentric portion 152H that are eccentric with a phase difference of 180 ° from each other, and the low-stage eccentric portion 152L includes the low-stage-side eccentric portion 152L. The low stage side piston 125L is rotatably held, and the high stage side eccentric part 152H rotatably holds the high stage side piston 125H of the high stage side compression part 12H.

回転軸１５が回転すると、低段側、高段側ピストン１２５Ｌ、１２５Ｈが、低段側、高段側シリンダ内壁１２３Ｌ、１２３Ｈに沿って低段側、高段側シリンダ１２１Ｌ、１２１Ｈ内を公転し、これに追随して低段側、高段側ベーン１２７Ｌ、１２７Ｈが往復運動する。この低段側、高段側ピストン１２５Ｌ、１２５Ｈ及び低段側、高段側ベーン１２７Ｌ、１２７Ｈの運動により、低段側、高段側吸入室１３１Ｌ、１３１Ｈ及び低段側、高段側圧縮室１３３Ｌ、１３３Ｈの容積が連続的に変化し、圧縮部１２は、連続的に冷媒を吸入し、圧縮して吐出する。   When the rotary shaft 15 rotates, the low-stage and high-stage pistons 125L and 125H revolve in the low-stage and high-stage cylinders 121L and 121H along the low-stage and high-stage cylinder inner walls 123L and 123H. Following this, the low stage side and high stage side vanes 127L and 127H reciprocate. Due to the movement of the low-stage and high-stage pistons 125L and 125H and the low-stage and high-stage vanes 127L and 127H, the low-stage and high-stage suction chambers 131L and 131H and the low-stage and high-stage compression chambers are moved. The volumes of 133L and 133H change continuously, and the compression unit 12 continuously sucks the refrigerant, compresses it, and discharges it.

低段側端板１６０Ｌの下側には、低段側マフラーカバー１７０Ｌが設置され、低段側端板１６０Ｌとの間に低段側マフラー室１８０Ｌを形成している。そして、低段側圧縮部１２Ｌの吐出部は、低段側マフラー室１８０Ｌに開口している。すなわち、低段側端板１６０Ｌには、低段側シリンダ１２１Ｌの低段側圧縮室１３３Ｌと低段側マフラー室１８０Ｌとを連通する低段側吐出孔１９０Ｌが設けられ、低段側吐出孔１９０Ｌの出口側には、圧縮された冷媒の逆流を防止する低段側吐出弁２００Ｌが設置されている。   Below the low stage side end plate 160L, a low stage side muffler cover 170L is installed, and a low stage side muffler chamber 180L is formed between the low stage side end plate 160L. And the discharge part of the low stage side compression part 12L is opened to the low stage side muffler chamber 180L. That is, the low-stage end plate 160L is provided with a low-stage discharge hole 190L that connects the low-stage compression chamber 133L and the low-stage muffler chamber 180L of the low-stage cylinder 121L. A low-stage discharge valve 200L for preventing the backflow of the compressed refrigerant is installed on the outlet side.

実施例では、低段側吐出孔１９０Ｌの孔径を、後述の高段側吐出孔１９０Ｈの孔径よりも大きくしている。低段側吐出孔１９０Ｌの孔径を大きくすることにより、高段側圧縮部１２Ｈよりも冷媒の体積流量が大きい低段側圧縮部１２Ｌの流量抵抗を小さくすることができる。   In the embodiment, the hole diameter of the low-stage discharge hole 190L is larger than the hole diameter of the high-stage discharge hole 190H described later. By increasing the hole diameter of the low-stage discharge hole 190L, the flow resistance of the low-stage compression section 12L having a larger volume flow rate of refrigerant than that of the high-stage compression section 12H can be reduced.

図３及び図４に示すように、低段側マフラー室１８０Ｌは、環状に連通された１つの室であり、低段側圧縮部１２Ｌの吐出側と高段側圧縮部１２Ｈの吸入側とを連通する中間連通路の一部である。低段側マフラー室１８０Ｌは、吐出冷媒の圧力脈動を低減させる。   As shown in FIGS. 3 and 4, the low-stage muffler chamber 180L is a single chamber communicated in an annular shape. The low-stage muffler chamber 180L is connected to the discharge side of the low-stage compression section 12L and the suction side of the high-stage compression section 12H. It is a part of the intermediate communication path that communicates. The low-stage muffler chamber 180L reduces the pressure pulsation of the discharged refrigerant.

また、図４及び図５に示すように、低段側吐出弁２００Ｌの上には、低段側吐出弁２００Ｌの撓み開弁量を制限するための低段側吐出弁押さえ２０１Ｌが、低段側吐出弁２００Ｌとともにリベット２０３により固定されている。また、低段側端板１６０Ｌの外周壁部には、低段側マフラー室１８０Ｌ内の冷媒を吐出する低段側マフラー吐出孔２１０Ｌが設けられている。低段側マフラー吐出孔２１０Ｌは、圧縮部１２の低段側吸入孔１３５Ｌ、高段側吸入孔１３５Ｈと圧縮機筐体１０の周方向の同一位相位置に、径方向に設けられている。   Further, as shown in FIGS. 4 and 5, a low-stage discharge valve presser 201L for limiting the amount of deflection opening of the low-stage discharge valve 200L is provided on the low-stage discharge valve 200L. The rivet 203 is fixed together with the side discharge valve 200L. In addition, a low-stage muffler discharge hole 210L that discharges the refrigerant in the low-stage muffler chamber 180L is provided on the outer peripheral wall portion of the low-stage end plate 160L. The low-stage muffler discharge hole 210 </ b> L is provided in the radial direction at the same phase position in the circumferential direction of the low-stage suction hole 135 </ b> L and the high-stage suction hole 135 </ b> H of the compression unit 12.

高段側端板１６０Ｈの上側には、高段側マフラーカバー１７０Ｈが設置され、高段側端板１６０Ｈとの間に高段側マフラー室１８０Ｈを形成している。図６、図７及び図８に示すように、高段側端板１６０Ｈには、高段側シリンダ１２１Ｈの高段側圧縮室１３３Ｈと高段側マフラー室１８０Ｈとを連通する高段側吐出孔１９０Ｈが設けられ、高段側吐出孔１９０Ｈの出口側には、圧縮された冷媒の逆流を防止する高段側吐出弁２００Ｈが設置されている。また、高段側吐出弁２００Ｈの上には、高段側吐出弁２００Ｈの撓み開弁量を制限するために、高段側吐出弁押さえ２０１Ｈが、高段側吐出弁２００Ｈとともにリベット２０３により固定されている。高段側マフラー室１８０Ｈは、吐出冷媒の圧力脈動を低減させる。   A high stage side muffler cover 170H is installed above the high stage side end plate 160H, and a high stage side muffler chamber 180H is formed between the high stage side end plate 160H. As shown in FIGS. 6, 7 and 8, the high-stage end plate 160H has a high-stage discharge hole that communicates the high-stage compression chamber 133H and the high-stage muffler chamber 180H of the high-stage cylinder 121H. 190H is provided, and on the outlet side of the high-stage discharge hole 190H, a high-stage discharge valve 200H that prevents the backflow of the compressed refrigerant is installed. Further, on the high-stage discharge valve 200H, a high-stage discharge valve presser 201H is fixed by the rivet 203 together with the high-stage discharge valve 200H in order to limit the deflection opening amount of the high-stage discharge valve 200H. Has been. The high-stage muffler chamber 180H reduces the pressure pulsation of the discharged refrigerant.

高段側マフラー室１８０Ｈの吐出部は、圧縮機筐体１０内に連通している。圧縮機筐体１０の天部には、冷凍サイクルの高圧側と接続し、高圧冷媒を冷凍サイクル側に吐出する吐出管１０７が接続されている。   The discharge part of the high-stage muffler chamber 180H communicates with the compressor housing 10. Connected to the top of the compressor housing 10 is a discharge pipe 107 that is connected to the high-pressure side of the refrigeration cycle and discharges high-pressure refrigerant to the refrigeration cycle side.

低段側シリンダ１２１Ｌ、低段側端板１６０Ｌ、低段側マフラーカバー１７０Ｌ、高段側シリンダ１２１Ｈ、高段側端板１６０Ｈ、高段側マフラーカバー１７０Ｈ及び中間仕切板１４０は、図示しないボルトにより一体に締結されている。ボルトにより一体に締結された圧縮部１２のうち、高段側端板１６０Ｈ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 low stage side cylinder 121L, the low stage side end plate 160L, the low stage side muffler cover 170L, the high stage side cylinder 121H, the high stage side end plate 160H, the high stage side muffler cover 170H, and the intermediate partition plate 140 are formed by bolts not shown. It is fastened together. Of the compression part 12 integrally fastened by bolts, the outer peripheral part of the high-stage end plate 160H is fixed to the compressor casing 10 by spot welding, and the compression part 12 is fixed to the compressor casing 10. .

図１に示すように、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、第３連通孔１０１、１０２、１０３が、圧縮機筐体１０の略同一周方向位置に設けられている。   As shown in FIG. 1, the first, second, and third communication holes 101, 102, and 103 are formed on the outer peripheral wall of the cylindrical compressor housing 10 in order from the lower part in the axial direction. The casing 10 is provided at substantially the same circumferential position.

図１又は図９に示すように、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。アキュムレータ２５の天部中心には、冷凍サイクルの低圧側と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の底部中心に設けられた底部連通孔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、他端が低段側吸入管１０４の他端に接続される低圧連絡管３１が接続されている。   As shown in FIG. 1 or FIG. 9, an accumulator 25 made 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. A system connection pipe 255 connected to the low pressure side of the refrigeration cycle is connected to the center of the top of the accumulator 25, and one end of the bottom communication hole 257 provided at the center of the bottom of the accumulator 25 extends to the upper inside of the accumulator 25. A low-pressure connection pipe 31 is connected, the other end of which is connected to the other end of the low-stage suction pipe 104.

冷凍サイクルの低圧冷媒をアキュムレータ２５を介して低段側圧縮部１２Ｌに導く低圧連絡管３１は、第２連通孔１０２及び低段側吸入管１０４を介して低段側シリンダ１２１Ｌの低段側吸入孔１３５Ｌに接続されている。   The low-pressure communication pipe 31 that guides the low-pressure refrigerant of the refrigeration cycle to the low-stage compression unit 12L via the accumulator 25 is connected to the low-stage suction of the low-stage cylinder 121L via the second communication hole 102 and the low-stage suction pipe 104. It is connected to the hole 135L.

低段側マフラー室１８０Ｌの低段側マフラー吐出孔２１０Ｌには、第１連通孔１０１を通して低段側吐出管１０５の一端が接続され、高段側シリンダ１２１Ｈの高段側吸入孔１３５Ｈには、第３連通孔１０３を通して高段側吸入管１０６の一端が接続され、低段側吐出管１０５の他端と高段側吸入管１０６の他端とは、中間連絡管２３により接続されている。低圧連絡管３１と中間連絡管２３とは、互いに干渉しないように曲げ形成されている。   One end of the low-stage side discharge pipe 105 is connected to the low-stage side muffler discharge hole 210L of the low-stage side muffler chamber 180L through the first communication hole 101, and the high-stage side suction hole 135H of the high-stage side cylinder 121H includes One end of the high stage side suction pipe 106 is connected through the third communication hole 103, and the other end of the low stage side discharge pipe 105 and the other end of the high stage side suction pipe 106 are connected by the intermediate communication pipe 23. The low-pressure connecting pipe 31 and the intermediate connecting pipe 23 are bent so as not to interfere with each other.

圧縮機筺体１０内には、およそ高段側シリンダ１２１Ｈの高さまで潤滑油が封入されており、潤滑油は、回転軸１５の下部に挿入された図示しない羽根ポンプにより圧縮部１２を循環し、摺動部品の潤滑及び微小隙間によって圧縮冷媒の圧縮空間を区画している箇所のシールをしている。   Lubricating oil is sealed in the compressor housing 10 up to the height of the high-stage cylinder 121H, and the lubricating oil circulates through the compression unit 12 by a blade pump (not shown) inserted in the lower portion of the rotating shaft 15, Sealing is performed at locations where the compression space of the compressed refrigerant is partitioned by lubrication of sliding parts and minute gaps.

実施例の２段圧縮ロータリ圧縮機１においては、上述のように、低段側圧縮部１２Ｌの低段側吐出孔１９０Ｌの孔径を、高段側圧縮部１２Ｈの高段側吐出孔１９０Ｈの孔径よりも大きくしている。また、耐磨耗鋼板（例えば、スウェーデン鋼）製の低段側吐出弁２００Ｌの厚さを、高段側吐出弁２００Ｈの厚さより厚くしている。   In the two-stage compression rotary compressor 1 of the embodiment, as described above, the hole diameter of the low-stage discharge hole 190L of the low-stage compression section 12L is set to the hole diameter of the high-stage discharge hole 190H of the high-stage compression section 12H. Is bigger than. Further, the thickness of the low-stage discharge valve 200L made of a wear-resistant steel plate (for example, Swedish steel) is made thicker than the thickness of the high-stage discharge valve 200H.

一般に、ロータリ圧縮機の吐出弁に用いられる耐磨耗鋼板の板厚は、０．２５７ｍｍ、０．３０５ｍｍ、０．３８１ｍｍ、０．４０６ｍｍ、０．４５７ｍｍ及び０．５０８ｍｍの６種類である。板厚０．２５７ｍｍのものは、単段圧縮ロータリ圧縮機や２シリンダー型ロータリ圧縮機のような比較的小形のロータリ圧縮機に用いられ、板厚０．５０８ｍｍのものは、比較的大形のロータリ圧縮機に用いられ、通常の２段圧縮ロータリ圧縮機に用いられるのは、板厚０．３０５ｍｍ、０．３８１ｍｍ、０．４０６ｍｍ、０．４５７ｍｍの４種類である。板厚が薄いと高段側圧縮室１３３Ｈの圧力が所定の圧力に達する前に開いてしまい、板厚が厚いと低段側圧縮室１３３Ｌの圧力が所定の圧力に達しても開かないからである。   In general, the thicknesses of wear-resistant steel plates used for discharge valves of rotary compressors are six types: 0.257 mm, 0.305 mm, 0.381 mm, 0.406 mm, 0.457 mm, and 0.508 mm. A plate having a thickness of 0.257 mm is used for a relatively small rotary compressor such as a single-stage compression rotary compressor or a two-cylinder rotary compressor, and a plate having a thickness of 0.508 mm is relatively large. There are four types of plate thicknesses of 0.305 mm, 0.381 mm, 0.406 mm, and 0.457 mm that are used in a rotary compressor and in a normal two-stage compression rotary compressor. If the plate thickness is thin, it opens before the pressure in the high-stage compression chamber 133H reaches the predetermined pressure, and if the plate thickness is thick, it does not open even if the pressure in the low-stage compression chamber 133L reaches the predetermined pressure. is there.

そこで、例えば、高段側吐出弁２００Ｈの板厚を、０．３０５ｍｍとしたとき、低段側吐出弁２００Ｌの板厚を、１ランク上の板厚０．３８１ｍｍ（厚さ１．２５倍）とする。また、高段側吐出弁２００Ｈの板厚を、０．３８１ｍｍとし、低段側吐出弁２００Ｌの板厚を、２ランク上の板厚０．４５７ｍｍ（厚さ１．２０倍）としてもよいし、高段側吐出弁２００Ｈの板厚を、０．３０５ｍｍとし、低段側吐出弁２００Ｌの板厚を、３ランク上の板厚０．４５７ｍｍ（厚さ１．５０倍）としてもよい。一般的には、低段側吐出弁２００Ｌの板厚を、高段側吐出弁２００Ｈの板厚の１．２倍〜１．５倍の厚さとするのがよい。   Therefore, for example, when the plate thickness of the high-stage discharge valve 200H is 0.305 mm, the plate thickness of the low-stage discharge valve 200L is 0.381 mm (thickness 1.25 times) one rank higher. And Alternatively, the plate thickness of the high-stage discharge valve 200H may be 0.381 mm, and the plate thickness of the low-stage discharge valve 200L may be 0.457 mm (1.20 times thick) on the second rank. The plate thickness of the high stage discharge valve 200H may be 0.305 mm, and the plate thickness of the low stage discharge valve 200L may be 0.457 mm (thickness 1.50 times) on three ranks. In general, the plate thickness of the low-stage discharge valve 200L is preferably 1.2 to 1.5 times the plate thickness of the high-stage discharge valve 200H.

このように、低段側吐出弁２００Ｌの厚さを、高段側吐出弁２００Ｈの厚さより厚くすることにより、低段側吐出弁２００Ｌの撓み変形量を抑え、低段側吐出弁２００Ｌの耐久性を向上することができる。また、低段側吐出弁２００Ｌの厚さを厚くすることにより、低段側吐出弁２００Ｌの閉弁速度を速くして圧縮効率を向上することができる。   Thus, by making the thickness of the low stage side discharge valve 200L thicker than the thickness of the high stage side discharge valve 200H, the amount of bending deformation of the low stage side discharge valve 200L is suppressed, and the durability of the low stage side discharge valve 200L is maintained. Can be improved. Further, by increasing the thickness of the low-stage discharge valve 200L, the valve closing speed of the low-stage discharge valve 200L can be increased to improve the compression efficiency.

また、回転数可変型の２段圧縮ロータリ圧縮機１の場合、高速回転時、すなわち循環冷媒流量が大きいときには、吐出孔における流路抵抗がより大きくなるため、低段側吐出孔１９０Ｌの孔径を高段側吐出孔１９０Ｈの孔径よりも大きくすれば、高段側圧縮部１２Ｈよりも冷媒の体積流量が大きい低段側圧縮部１２Ｌの流量抵抗を小さくすることができる。また、低段側吐出弁２００Ｌの厚さを厚くすることにより、閉弁速度が速くなって圧縮効率を向上することができる。   Further, in the case of the two-stage compression rotary compressor 1 with a variable rotation speed, when the high-speed rotation is performed, that is, when the circulating refrigerant flow rate is large, the flow path resistance at the discharge hole becomes larger. If the diameter is larger than the hole diameter of the high-stage discharge hole 190H, the flow resistance of the low-stage compression section 12L having a larger volume flow rate of refrigerant than the high-stage compression section 12H can be reduced. Further, by increasing the thickness of the low-stage discharge valve 200L, the valve closing speed can be increased and the compression efficiency can be improved.

以上のように、本発明にかかる２段圧縮ロータリ圧縮機は、空気調和機に有用である。   As described above, the two-stage compression rotary compressor according to the present invention is useful for an air conditioner.

１ ２段圧縮ロータリ圧縮機（ロータリ圧縮機）
１０ 圧縮機筺体
１１ モータ
１２ 圧縮部
１５ 回転軸
２３ 中間連絡管
２５ アキュムレータ
３１ 低圧連絡管
１０１ 第１連通孔
１０２ 第２連通孔
１０３ 第３連通孔
１０４ 低段側吸入管
１０５ 低段側吐出管
１０６ 高段側吸入管
１０７ 吐出管
１１１ ステータ
１１２ ロータ
１２Ｌ 低段側圧縮部
１２Ｈ 高段側圧縮部
１２１Ｌ 低段側シリンダ
１２１Ｈ 高段側シリンダ
１２３Ｌ 低段側シリンダ内壁
１２３Ｈ 高段側シリンダ内壁
１２５Ｌ 低段側ピストン
１２５Ｈ 高段側ピストン
１２７Ｌ 低段側ベーン
１２７Ｈ 高段側ベーン
１２９Ｌ 低段側スプリング
１２９Ｈ 高段側スプリング
１３０Ｌ 低段側作動室
１３０Ｈ 高段側作動室
１３１Ｌ 低段側吸入室
１３１Ｈ 高段側吸入室
１３３Ｌ 低段側圧縮室
１３３Ｈ 高段側圧縮室
１３５Ｌ 低段側吸入孔
１３５Ｈ 高段側吸入孔
１４０ 中間仕切板
１５１ 下部
１５２Ｌ 低段側偏芯部
１５２Ｈ 高段側偏芯部
１５３ 中間部
１６０Ｌ 低段側端板
１６０Ｈ 高段側端板
１６１Ｌ 下軸受け部
１６１Ｈ 上軸受け部
１７０Ｌ 低段側マフラーカバー
１７０Ｈ 高段側マフラーカバー
１８０Ｌ 低段側マフラー室
１８０Ｈ 高段側マフラー室
１９０Ｌ 低段側吐出孔
１９０Ｈ 高段側吐出孔
２００Ｌ 低段側吐出弁
２００Ｈ 高段側吐出弁
２０１Ｌ 低段側吐出弁押さえ
２０１Ｈ 高段側吐出弁押さえ
２０３ リベット
２１０Ｌ 低段側マフラー吐出孔
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
２５７ 底部連通孔 1 2-stage rotary compressor (rotary compressor)
DESCRIPTION OF SYMBOLS 10 Compressor housing | casing 11 Motor 12 Compression part 15 Rotating shaft 23 Intermediate connection pipe 25 Accumulator 31 Low pressure connection pipe 101 1st communication hole 102 2nd communication hole 103 3rd communication hole 104 Low stage side intake pipe 105 Low stage side discharge pipe 106 High stage suction pipe 107 Discharge pipe 111 Stator 112 Rotor 12L Low stage compression section 12H High stage compression section 121L Low stage cylinder 121H High stage cylinder 123L Low stage cylinder inner wall 123H High stage cylinder inner wall 125L Low stage side Piston 125H High stage side piston 127L Low stage side vane 127H High stage side vane 129L Low stage side spring 129H High stage side spring 130L Low stage side working chamber 130H High stage side working chamber 131L Low stage side suction chamber 131H High stage side suction chamber 133L Low stage compression chamber 133H High stage compression chamber 135 Low stage side suction hole 135H High stage side suction hole 140 Intermediate partition plate 151 Lower 152L Low stage side eccentric part 152H High stage side eccentric part 153 Middle part 160L Low stage side end plate 160H High stage side end plate 161L Lower bearing part 161H Upper bearing portion 170L Low stage side muffler cover 170H High stage side muffler cover 180L Low stage side muffler chamber 180H High stage side muffler chamber 190L Low stage side discharge hole 190H High stage side discharge hole 200L Low stage side discharge valve 200H High stage side Discharge valve 201L Low stage discharge valve holder 201H High stage discharge valve holder 203 Rivet 210L Low stage muffler discharge hole 252 Accum holder 253 Accum band 255 System connection pipe 257 Bottom communication hole

Claims (3)

低段側圧縮部、高段側圧縮部及び該低段側、高段側圧縮部を駆動するモータを圧縮機筺体内に収容し、前記低段側圧縮部で圧縮され吐出された冷媒を前記高段側圧縮部に吸入し、さらに圧縮して吐出する２段圧縮ロータリ圧縮機であって、前記高段側圧縮部の高段側吐出孔を前記低段側圧縮部の低段側吐出孔よりも小さくしたものにおいて、
前記低段側吐出孔の出口側に設置されたリード弁型の低段側吐出弁の厚さを、前記高段側吐出孔の出口側に設置されたリード弁型の高段側吐出弁の厚さより厚くしたことを特徴とする２段圧縮ロータリ圧縮機。 A low-stage compression section, a high-stage compression section, and a motor that drives the low-stage compression section and the high-stage compression section are housed in a compressor housing, and the refrigerant compressed and discharged by the low-stage compression section is A two-stage compression rotary compressor that sucks into a high-stage side compression section, and further compresses and discharges the high-stage-side compression section. Smaller than
The thickness of the reed valve type low-stage discharge valve installed on the outlet side of the low-stage side discharge hole is the thickness of the reed valve type high-stage side discharge valve installed on the outlet side of the high-stage side discharge hole . A two-stage compression rotary compressor characterized by being thicker than the thickness. 円筒状の低段側シリンダと、該低段側シリンダの下側を閉塞する低段側端板と、該低段側端板の下側を閉塞して該低段側端板との間に低段側マフラー室を形成する低段側マフラーカバーと、前記低段側シリンダの上側を閉塞する中間仕切板と、モータにより回転駆動される回転軸の低段側偏芯部に保持され前記低段側シリンダの低段側シリンダ内壁に沿って該低段側シリンダ内を公転し前記低段側シリンダ内壁との間に低段側作動室を形成する低段側ピストンと、前記低段側シリンダの低段側ベーン溝内から前記低段側作動室内に突出して前記低段側ピストンに当接し、前記低段側作動室を低段側吸入室と低段側圧縮室とに区画する低段側ベーンと、前記低段側端板に設けられ前記低段側圧縮室と前記低段側マフラー室とを連通する低段側吐出孔と、該低段側吐出孔の出口側に設置されたリード弁型の低段側吐出弁と、を備えて成る低段側圧縮部と、
前記中間仕切板を介して前記低段側圧縮部に積層され、円筒状の高段側シリンダと、該高段側シリンダの上側を閉塞する高段側端板と、前記高段側端板の上側を閉塞して該高段側端板との間に高段側マフラー室を形成する高段側マフラーカバーと、前記モータにより回転駆動される回転軸の高段側偏芯部に保持され前記高段側シリンダの高段側シリンダ内壁に沿って該高段側シリンダ内を公転し前記高段側シリンダ内壁との間に高段側作動室を形成する高段側ピストンと、前記高段側シリンダの高段側ベーン溝内から前記高段側作動室内に突出して前記高段側ピストンに当接し、前記高段側作動室を高段側吸入室と高段側圧縮室とに区画する高段側ベーンと、前記高段側端板に設けられ前記高段側圧縮室と前記高段側マフラー室とを連通する前記低段側吐出孔より小さい高段側吐出孔と、該高段側吐出孔の出口側に設置されたリード弁型の高段側吐出弁と、を備えて成る高段側圧縮部と、
前記低段側圧縮部、高段側圧縮部及びモータを収容する密閉された圧縮機筐体と、
前記圧縮機筐体の側方に配置されたアキュムレータと、
前記低段側吸入室に連通する低段側吸入孔を、前記アキュムレータを介して冷凍サイクルの低圧側に連通させる低圧連絡管と、
前記低段側マフラー室を、前記高段側吸入室に連通する高段側吸入孔に連通させる中間連絡管と、
前記高段側マフラー室を、前記圧縮機筐体内を介して前記冷凍サイクルの高圧側に連通させる吐出管と、
を備える２段圧縮ロータリ圧縮機において、
前記低段側吐出弁の厚さを、前記高段側吐出弁の厚さより厚くしたことを特徴とする２段圧縮ロータリ圧縮機。 Between the cylindrical low-stage side cylinder, the low-stage side end plate that closes the lower side of the low-stage side cylinder, and the lower side end plate that closes the lower side of the low-stage side end plate The low stage side muffler cover that forms the low stage side muffler chamber, the intermediate partition plate that closes the upper side of the low stage side cylinder, and the low stage side eccentric part of the rotary shaft that is driven to rotate by a motor are used to hold the low stage side muffler cover. A low-stage piston that revolves in the low-stage cylinder along a low-stage cylinder inner wall of the stage-side cylinder and forms a low-stage working chamber between the low-stage cylinder inner wall and the low-stage cylinder; A low stage that protrudes from the low stage side vane groove into the low stage side working chamber and contacts the low stage side piston, and divides the low stage side working chamber into a low stage side suction chamber and a low stage side compression chamber. A low-stage side discharge that is provided on the low-side end plate and communicates with the low-stage compression chamber and the low-stage muffler chamber. A hole, a lead valve type low-stage discharge valve installed in the outlet side of the low-stage discharge hole, a low-stage compressing section consisting comprise,
A cylindrical high-stage cylinder, a high-stage end plate that closes an upper side of the high-stage cylinder, and a high-stage end plate that are stacked on the low-stage compression portion via the intermediate partition plate. A high stage muffler cover that closes the upper side and forms a high stage side muffler chamber with the high stage side end plate, and is held by a high stage side eccentric part of a rotary shaft that is driven to rotate by the motor. A high-stage piston that revolves in the high-stage cylinder along a high-stage cylinder inner wall of the high-stage cylinder and forms a high-stage working chamber with the high-stage cylinder inner wall; and the high-stage side A high portion that projects from the high-stage vane groove of the cylinder into the high-stage working chamber and abuts against the high-stage piston, and divides the high-stage working chamber into a high-stage suction chamber and a high-stage compression chamber. A stage-side vane is provided on the high-stage end plate and communicates with the high-stage compression chamber and the high-stage muffler chamber. Serial and smaller high-stage side discharge hole low-stage discharge hole, a high-stage compressing section consisting comprises a reed valve type of the high-stage discharge valve installed on the outlet side of the high-stage discharge hole, and
A hermetically sealed compressor housing that houses the low-stage compression section, the high-stage compression section, and the motor;
An accumulator disposed on the side of the compressor housing;
A low-pressure communication pipe that communicates the low-stage side suction hole communicating with the low-stage side suction chamber to the low-pressure side of the refrigeration cycle via the accumulator;
An intermediate connecting pipe that communicates the low-stage muffler chamber with a high-stage suction hole that communicates with the high-stage suction chamber;
A discharge pipe for communicating the high-stage muffler chamber with the high-pressure side of the refrigeration cycle through the compressor housing;
A two-stage compression rotary compressor comprising:
The two-stage compression rotary compressor characterized in that the thickness of the low-stage discharge valve is made larger than the thickness of the high-stage discharge valve. 前記低段側吐出弁の厚さを、前記高段側吐出弁の厚さの１．２〜１．５倍の厚さとしたことを特徴とする請求項１又は２に記載の２段圧縮ロータリ圧縮機。   The two-stage compression rotary according to claim 1 or 2, wherein the thickness of the low-stage discharge valve is 1.2 to 1.5 times the thickness of the high-stage discharge valve. Compressor.
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