JP2013096281A - Rotary compressor - Google Patents

Rotary compressor Download PDF

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Publication number
JP2013096281A
JP2013096281A JP2011238714A JP2011238714A JP2013096281A JP 2013096281 A JP2013096281 A JP 2013096281A JP 2011238714 A JP2011238714 A JP 2011238714A JP 2011238714 A JP2011238714 A JP 2011238714A JP 2013096281 A JP2013096281 A JP 2013096281A
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Prior art keywords
piston
shaft
eccentric
partition plate
eccentric portion
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JP2013096281A5 (en
JP5606422B2 (en
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Toshitsune Arai
聡経 新井
Masao Tani
谷　　真男
Koichi Sato
幸一 佐藤
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Priority to JP2011238714A priority Critical patent/JP5606422B2/en
Priority to CZ2012-581A priority patent/CZ305970B6/en
Priority to KR1020120100289A priority patent/KR101393968B1/en
Priority to CN201210346923.3A priority patent/CN103089630B/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/063—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them
    • F04C18/07—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents with coaxially-mounted members having continuously-changing circumferential spacing between them having crankshaft-and-connecting-rod type drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/0021—Systems for the equilibration of forces acting on the pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/40—Electric motor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps
    • Y10S417/902—Hermetically sealed motor pump unit

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

Abstract

PROBLEM TO BE SOLVED: To provide a rotary compressor capable of achieving high power and high efficiency while securing reliability of a crank shaft.SOLUTION: In a two-cylinder rotary compressor 100, an outer diameter of an intermediate shaft 4e is formed toward an outer peripheral side from an outer circumferential surface of an oppositely eccentric side of a main-shaft-side eccentric part 4c and a counter-shaft-side eccentric part 4d. A partition 10 is divided into a plurality of pieces by a cross section passing through a through hole formed on the partition 10. An inner diameter 10a of the through hole of the partition 10 is formed to be larger than the outer diameter of the intermediate shaft 4e and smaller than outer diameters of the main-shaft-side eccentric part 4c and the counter-shaft-side eccentric part 4d.

Description

この発明は、空気調和機や冷蔵庫等の冷凍空調装置の冷凍サイクルに用いられる、冷媒ガスの圧縮を行う回転圧縮機に関するものである。   The present invention relates to a rotary compressor for compressing refrigerant gas used in a refrigeration cycle of a refrigerating and air-conditioning apparatus such as an air conditioner or a refrigerator.

複数の圧縮室のそれぞれによって低圧の冷媒ガスを高圧の冷媒ガスに圧縮する多気筒回転圧縮機や、低圧の冷媒ガスを複数の圧縮室で順次圧縮していき、高圧の冷媒ガスを生成する多段回転圧縮機が知られている。このような複数の圧縮室を有する圧縮機においては、クランク軸に、シリンダ内に配置される複数の偏芯部と、隣接する偏芯部の間に設けられた中間軸を備えている。そして、このような圧縮機には、偏芯部の偏芯量を大きくとって高出力化や高効率化を図ったものが従来より提案されており、例えば、「クランク軸２ａの１８０゜対向の偏芯部を異なる直径ｄ０１，ｄ０２で形成し、かつ、クランク軸２ａの上端板側の外径ｄ１と下端板側の外径ｄ２を異なる径とし、仕切り板４の中央孔を小径側偏芯部のみを挿通し得る大きさにして、偏芯量を大きくする。」というものが提案されている（例えば、特許文献１参照）。   A multi-cylinder rotary compressor that compresses low-pressure refrigerant gas into high-pressure refrigerant gas by each of a plurality of compression chambers, or a multi-stage that generates high-pressure refrigerant gas by sequentially compressing low-pressure refrigerant gas in the plurality of compression chambers A rotary compressor is known. In such a compressor having a plurality of compression chambers, a crankshaft is provided with a plurality of eccentric parts arranged in a cylinder and an intermediate shaft provided between adjacent eccentric parts. For such a compressor, a compressor having a large eccentricity of the eccentric portion and achieving high output and high efficiency has been proposed. For example, “the crankshaft 2a is opposed to 180 °. Are formed with different diameters d01 and d02, and the outer diameter d1 on the upper end plate side and the outer diameter d2 on the lower end plate side of the crankshaft 2a are different from each other, and the central hole of the partition plate 4 is formed on the smaller diameter side. The amount of eccentricity is increased so that only the core portion can be inserted (see, for example, Patent Document 1).

特開平５−１０２７９号公報（要約、図２）Japanese Patent Laid-Open No. 5-10279 (summary, FIG. 2)

しかしながら、特許文献１に記載の２気筒回転圧縮機においては、各偏芯部の外径が異なっているので、冷媒ガスを圧縮する際にクランク軸の偏芯部に作用するガス負荷が、各偏芯部によって異ってしまう。このため、クランク軸の力の釣り合いがアンバランスとなり、本来は打ち消しあうべき回転方向のモーメントが打ち消されず回転方向に強く作用することになる。したがって、特許文献１に記載の２気筒回転圧縮機は、クランク軸の信頼性が低下し、圧縮機に異常な振動や騒音が発生してしまうという課題があった。   However, in the two-cylinder rotary compressor described in Patent Document 1, since the outer diameter of each eccentric portion is different, the gas load acting on the eccentric portion of the crankshaft when compressing the refrigerant gas is different from each other. It depends on the eccentric part. For this reason, the balance of the force of the crankshaft becomes unbalanced, and the moment in the rotational direction that should be canceled out does not cancel out, but acts strongly in the rotational direction. Therefore, the two-cylinder rotary compressor described in Patent Document 1 has a problem in that the reliability of the crankshaft is lowered, and abnormal vibration and noise are generated in the compressor.

この発明は、上記のような課題を解決するためになされたもので、クランク軸の信頼性を確保しつつも、高出力化や高効率化を可能とする回転圧縮機を提供することを目的とする。   The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a rotary compressor that can achieve high output and high efficiency while ensuring the reliability of the crankshaft. And

この発明に係る回転圧縮機は、固定子及び回転子を有する電動機と、前記回転子に固定された主軸、前記主軸の軸方向の反対側に設けられた副軸、前記主軸と前記副軸との間に所定の位相差を設けて形成された複数の偏芯部、並びに隣接する前記偏芯部の間に設けられた中間軸を有し、前記電動機により駆動されるクランク軸と、円筒状の貫通孔が形成され、該貫通孔に前記偏芯部が配置されて圧縮室が形成される複数のシリンダと、内部に前記中間軸が配置される円筒状の貫通孔が形成され、隣接する前記シリンダの圧縮室の間を仕切る仕切板と、を備えた回転圧縮機であって、
前記中間軸の外周面は、前記偏芯部の反偏芯側の外周面よりも外周側に形成され、前記仕切板は、該仕切板に形成された貫通孔を通る断面によって複数に分割されており、前記仕切板の貫通孔の内径は、前記中間軸の外径よりも大きく、且つ、前記偏芯部の外径よりも小さく形成されているものである。 A rotary compressor according to the present invention includes a motor having a stator and a rotor, a main shaft fixed to the rotor, a sub shaft provided on the opposite side of the main shaft in the axial direction, the main shaft and the sub shaft. A plurality of eccentric parts formed with a predetermined phase difference between them, an intermediate shaft provided between the adjacent eccentric parts, a crankshaft driven by the electric motor, and a cylindrical shape A plurality of cylinders in which the eccentric portion is arranged to form a compression chamber and a cylindrical through hole in which the intermediate shaft is arranged are formed adjacent to each other. A rotary compressor provided with a partition plate for partitioning between the compression chambers of the cylinder,
The outer peripheral surface of the intermediate shaft is formed on the outer peripheral side with respect to the outer peripheral surface on the anti-eccentric side of the eccentric portion, and the partition plate is divided into a plurality of sections through a through hole formed in the partition plate. The inner diameter of the through hole of the partition plate is larger than the outer diameter of the intermediate shaft and smaller than the outer diameter of the eccentric portion.

また、この発明に係る回転圧縮機は、固定子及び回転子を有する電動機と、前記回転子に固定された主軸、前記主軸の軸方向の反対側に設けられた副軸、前記主軸と前記副軸との間に所定の位相差を設けて形成された複数の偏芯部、並びに隣接する前記偏芯部の間に設けられた中間軸を有し、前記電動機により駆動されるクランク軸と、前記偏芯部に嵌合する複数のピストンと、円筒状の貫通孔が形成され、該貫通孔に前記偏芯部及び前記ピストンが配置されて圧縮室が形成される複数のシリンダと、内部に前記中間軸が配置される円筒状の貫通孔が形成され、隣接する前記シリンダの圧縮室の間を仕切る仕切板と、を備えた回転圧縮機であって、
前記中間軸の外周面は、前記偏芯部の反偏芯側の外周面よりも外周側に形成され、前記仕切板は、該仕切板に形成された貫通孔を通る断面によって複数に分割されており、前記仕切板の貫通孔の内径は、前記中間軸の外径よりも大きく、且つ、前記偏芯部の外径よりも小さく形成され、前記ピストンの反偏芯側の外周面は、前記仕切板の貫通孔の内径よりも外周側に形成されているものである。 The rotary compressor according to the present invention includes an electric motor having a stator and a rotor, a main shaft fixed to the rotor, a sub shaft provided on the opposite side of the main shaft in the axial direction, the main shaft and the sub shaft A plurality of eccentric portions formed with a predetermined phase difference between the shaft and an intermediate shaft provided between the adjacent eccentric portions, and a crankshaft driven by the electric motor; A plurality of pistons that fit into the eccentric part, a cylindrical through hole is formed, a plurality of cylinders in which the eccentric part and the piston are arranged in the through hole to form a compression chamber, and inside A rotary compressor having a cylindrical through-hole in which the intermediate shaft is disposed and a partition plate for partitioning between the compression chambers of the adjacent cylinders;
The outer peripheral surface of the intermediate shaft is formed on the outer peripheral side with respect to the outer peripheral surface on the anti-eccentric side of the eccentric portion, and the partition plate is divided into a plurality of sections through a through hole formed in the partition plate. The inner diameter of the through hole of the partition plate is larger than the outer diameter of the intermediate shaft and smaller than the outer diameter of the eccentric part, and the outer peripheral surface of the piston on the side opposite to the eccentric side is It is formed in the outer peripheral side rather than the internal diameter of the through-hole of the said partition plate.

この発明に係る回転圧縮機においては、中間軸の外周面は、偏芯部の反偏芯側の外周面よりも外周側に形成され、仕切板は、該仕切板に形成された貫通孔を通る断面によって複数に分割されており、仕切板の貫通孔の内径は、中間軸の外径よりも大きく、且つ、偏芯部の外径よりも小さく形成されている。このため、各偏芯部の偏芯量を大きくとって、回転圧縮機の高出力化や高効率化を図ることができる。そして、この発明に係る回転圧縮機は、各偏芯部の外径を異ならせることなく各偏芯部の偏芯量を大きくとれるので、冷媒ガスを圧縮する際に各偏芯部に作用するガス負荷を略同等にでき、回転方向のモーメントを打ち消し合うことができる。したがって、この発明に係る回転圧縮機は、クランク軸の信頼性を確保しつつ、且つ高出力化や高効率化が可能となる。   In the rotary compressor according to the present invention, the outer peripheral surface of the intermediate shaft is formed on the outer peripheral side with respect to the outer peripheral surface on the anti-eccentric side of the eccentric portion, and the partition plate has a through hole formed in the partition plate. The through-hole of the partition plate is formed to be larger than the outer diameter of the intermediate shaft and smaller than the outer diameter of the eccentric portion. For this reason, the eccentric amount of each eccentric part can be taken large, and high output and high efficiency of a rotary compressor can be achieved. Since the rotary compressor according to the present invention can increase the eccentric amount of each eccentric portion without changing the outer diameter of each eccentric portion, it acts on each eccentric portion when compressing the refrigerant gas. The gas load can be made substantially equal, and the moment in the rotational direction can be canceled out. Therefore, the rotary compressor according to the present invention can achieve high output and high efficiency while ensuring the reliability of the crankshaft.

この発明の実施の形態１を示す図で、２気筒回転圧縮機１００の縦断面図。BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows Embodiment 1 of this invention, and a longitudinal cross-sectional view of the 2-cylinder rotary compressor 100. この発明の実施の形態１を示す図で、２気筒回転圧縮機１００の圧縮機構部３の縦断面図。BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows Embodiment 1 of this invention, and a longitudinal cross-sectional view of the compression mechanism part 3 of the 2-cylinder rotary compressor 100. この発明の実施の形態１を示す図で、２気筒回転圧縮機１００の圧縮機構部３の縦断面図。BRIEF DESCRIPTION OF THE DRAWINGS It is a figure which shows Embodiment 1 of this invention, and a longitudinal cross-sectional view of the compression mechanism part 3 of the 2-cylinder rotary compressor 100. この発明の実施の形態１を示す図で、図２のＺ−Ｚ断面図。FIG. 3 shows the first embodiment of the present invention, and is a ZZ sectional view of FIG. 2. この発明の実施の形態１を示す図で、第１のピストン１１ａの内径の軸方向両端に逃がし形状１１ａ−１を設けた場合の、第１のピストン１１ａのクランク軸４への組み付け手順を示す図。FIG. 5 is a diagram showing the first embodiment of the present invention, and shows a procedure for assembling the first piston 11a to the crankshaft 4 when relief shapes 11a-1 are provided at both axial ends of the inner diameter of the first piston 11a. Figure. この発明の実施の形態１を示す図で、図５と図７とを比較した図（図６（ａ）が比較例、図６（ｂ）が本実施の形態）。FIG. 6 shows the first embodiment of the present invention, and is a diagram comparing FIG. 5 and FIG. 7 (FIG. 6 (a) is a comparative example, and FIG. 6 (b) is the present embodiment). 比較例を示す図で、第１のピストン１１ａのクランク軸４への組み付け手順を示す図。It is a figure which shows a comparative example, and is a figure which shows the assembly | attachment procedure to the crankshaft 4 of the 1st piston 11a. この発明の実施の形態２を示す図で、２気筒回転圧縮機１００の圧縮機構部３の縦断面図。FIG. 5 is a diagram illustrating a second embodiment of the present invention, and is a longitudinal sectional view of a compression mechanism section 3 of a two-cylinder rotary compressor 100.

実施の形態１．
図１乃至図６は実施の形態１を示す図で、図１は２気筒回転圧縮機１００の縦断面図、図２及び図３は２気筒回転圧縮機１００の圧縮機構部３の縦断面図、図４は図２のＺ−Ｚ断面図、図５は第１のピストン１１ａの内径の軸方向両端に逃がし形状１１ａ−１を設けた場合の、第１のピストン１１ａのクランク軸４への組み付け手順を示す図、図６は図５と図７とを比較した図（図６（ａ）が比較例、図６（ｂ）が本実施の形態）である。
以下、図１〜図６を用いて、本実施の形態１に係る２気筒回転圧縮機１００について説明する。 Embodiment 1 FIG.
1 to 6 are diagrams showing the first embodiment. FIG. 1 is a longitudinal sectional view of a two-cylinder rotary compressor 100. FIGS. 2 and 3 are longitudinal sectional views of a compression mechanism unit 3 of the two-cylinder rotary compressor 100. FIG. 4 is a ZZ cross-sectional view of FIG. 2, and FIG. 5 is a view of the first piston 11a to the crankshaft 4 when relief shapes 11a-1 are provided at both axial ends of the inner diameter of the first piston 11a. FIGS. 6A and 6B are diagrams showing an assembling procedure. FIGS. 6A and 6B are diagrams comparing FIGS. 5 and 7 (FIG. 6A is a comparative example, and FIG. 6B is the present embodiment).
Hereinafter, the two-cylinder rotary compressor 100 according to the first embodiment will be described with reference to FIGS.

図１により、２気筒回転圧縮機１００の構成を説明する。２気筒回転圧縮機１００は、高圧雰囲気の密閉容器１内に、固定子２ａと回転子２ｂとからなる電動機２と、電動機２により駆動される圧縮機構部３とを収納している。   The configuration of the two-cylinder rotary compressor 100 will be described with reference to FIG. The two-cylinder rotary compressor 100 houses an electric motor 2 composed of a stator 2 a and a rotor 2 b and a compression mechanism unit 3 driven by the electric motor 2 in a sealed container 1 in a high-pressure atmosphere.

電動機２の回転力は、クランク軸４を介して圧縮機構部３に伝達される。   The rotational force of the electric motor 2 is transmitted to the compression mechanism unit 3 via the crankshaft 4.

クランク軸４は、電動機２の回転子２ｂに固定される主軸４ａと、主軸４ａの反対側に設けられる副軸４ｂと、主軸４ａと副軸４ｂとの間に所定の位相差（例えば、１８０°）を設けて形成される主軸側偏芯部４ｃ及び副軸側偏芯部４ｄと、これらの主軸側偏芯部４ｃと副軸側偏芯部４ｄとの間に設けられる中間軸４ｅとを有する。   The crankshaft 4 has a predetermined phase difference (for example, 180) between the main shaft 4a fixed to the rotor 2b of the electric motor 2, the sub shaft 4b provided on the opposite side of the main shaft 4a, and the main shaft 4a and the sub shaft 4b. And the intermediate shaft 4e provided between the main shaft side eccentric portion 4c and the sub shaft side eccentric portion 4d. Have

主軸受６は、クランク軸４の主軸４ａに摺動のためのクリアランスを持って嵌合され、回転自在に主軸４ａを軸支する。   The main bearing 6 is fitted to the main shaft 4a of the crankshaft 4 with a clearance for sliding, and rotatably supports the main shaft 4a.

また、副軸受７は、クランク軸４の副軸４ｂに摺動のためのクリアランスを持って嵌合され、回転自在に副軸４ｂを軸支する。   The auxiliary bearing 7 is fitted to the auxiliary shaft 4b of the crankshaft 4 with a clearance for sliding, and rotatably supports the auxiliary shaft 4b.

圧縮機構部３は、主軸４ａ側の第１のシリンダ８と、副軸４ｂ側の第２のシリンダ９とを備える。   The compression mechanism unit 3 includes a first cylinder 8 on the main shaft 4a side and a second cylinder 9 on the sub shaft 4b side.

第１のシリンダ８は、円筒状の貫通孔を有し、この貫通孔に、クランク軸４の主軸側偏芯部４ｃに回転自在に嵌合する第１のピストン１１ａが設けられる。さらに、主軸側偏芯部４ｃの回転に従って往復運動する第１のベーン（図示せず）が設けられる。   The first cylinder 8 has a cylindrical through hole, and a first piston 11 a that is rotatably fitted to the main shaft side eccentric portion 4 c of the crankshaft 4 is provided in the through hole. Further, a first vane (not shown) that reciprocates according to the rotation of the main shaft side eccentric portion 4c is provided.

クランク軸４の主軸側偏芯部４ｃに回転自在に嵌合する第１のピストン１１ａ、第１のベーンを収納した第１のシリンダ８の貫通孔の軸方向両端面を、主軸受６と仕切板１０とで閉塞して圧縮室を形成する。   A first piston 11 a that is rotatably fitted to the main shaft side eccentric portion 4 c of the crankshaft 4, and both axial end surfaces of the through hole of the first cylinder 8 that houses the first vane are partitioned from the main bearing 6. A compression chamber is formed by closing with the plate 10.

第１のシリンダ８は、密閉容器１の内周部に固定される。   The first cylinder 8 is fixed to the inner periphery of the sealed container 1.

第２のシリンダ９も、円筒状の貫通孔を有し、この貫通孔に、クランク軸４の副軸側偏芯部４ｄに回転自在に嵌合する第２のピストン１１ｂが設けられる。さらに、副軸側偏芯部４ｄの回転に従って往復運動する第２のベーン（図示せず）が設けられる。   The second cylinder 9 also has a cylindrical through-hole, and a second piston 11 b that is rotatably fitted to the countershaft side eccentric portion 4 d of the crankshaft 4 is provided in the through-hole. Further, a second vane (not shown) that reciprocates according to the rotation of the countershaft side eccentric portion 4d is provided.

クランク軸４の副軸側偏芯部４ｄに回転自在に嵌合する第２のピストン１１ｂ、第２のベーンを収納した第２のシリンダ９の貫通孔の軸方向両端面を、副軸受７と仕切板１０とで閉塞して圧縮室を形成する。   A second piston 11b that is rotatably fitted to the sub-shaft side eccentric portion 4d of the crankshaft 4 and both axial end surfaces of the through hole of the second cylinder 9 that houses the second vane are connected to the sub-bearing 7 A compression chamber is formed by closing with the partition plate 10.

圧縮機構部３は、第１のシリンダ８と主軸受６とをボルト締結し、また第２のシリンダ９と副軸受７とをボルト締結した後、仕切板１０をそれらの間に挟んで、主軸受６の外側から第２のシリンダ９、及び副軸受７の外側から第１のシリンダ８まで軸方向にボルト締結し固定する。   The compression mechanism unit 3 is bolted to the first cylinder 8 and the main bearing 6, and is bolted to the second cylinder 9 and the auxiliary bearing 7, and then the partition plate 10 is sandwiched between them, The bolts are fastened and fixed in the axial direction from the outside of the bearing 6 to the second cylinder 9 and from the outside of the auxiliary bearing 7 to the first cylinder 8.

図１で図示しているボルト１２は、主軸受６の外側から第２のシリンダ９まで軸方向に締結し固定するボルトの一部である。   The bolt 12 illustrated in FIG. 1 is a part of a bolt that is fastened and fixed in the axial direction from the outside of the main bearing 6 to the second cylinder 9.

また、図１で図示しているボルト１３は、第２のシリンダ９と副軸受７とを締結するボルトの一部である。   Further, the bolt 13 illustrated in FIG. 1 is a part of a bolt that fastens the second cylinder 9 and the auxiliary bearing 7.

密閉容器１に隣接してアキュムレータ４０が設けられる。吸入連結管２１、吸入連結管２２は夫々第１のシリンダ８、第２のシリンダ９とアキュムレータ４０とを連結する。   An accumulator 40 is provided adjacent to the sealed container 1. The suction connection pipe 21 and the suction connection pipe 22 connect the first cylinder 8 and the second cylinder 9 to the accumulator 40, respectively.

第１のシリンダ８、第２のシリンダ９で圧縮された冷媒ガスは、密閉容器１に吐出され、吐出管２３から冷凍空調装置の冷凍サイクルへ送り出される。   The refrigerant gas compressed in the first cylinder 8 and the second cylinder 9 is discharged into the sealed container 1 and sent out from the discharge pipe 23 to the refrigeration cycle of the refrigeration air conditioner.

また、電動機２へは、ガラス端子２４からリード線２５を経由して電力が供給される。   Electric power is supplied to the electric motor 2 from the glass terminal 24 via the lead wire 25.

図示はしないが、密閉容器１内の底部には、圧縮機構部３の各摺動部を潤滑する潤滑油（冷凍機油）が貯留されている。   Although not shown, lubricating oil (refrigeration machine oil) that lubricates each sliding portion of the compression mechanism unit 3 is stored at the bottom of the sealed container 1.

圧縮機構部３の各摺動部への潤滑油の供給は、密閉容器１底部に溜められた潤滑油をクランク軸４の回転による遠心力によりクランク軸４の内径４ｆに沿って上昇させ、クランク軸４に設けられた給油孔２０より行なう。図１の例は、給油孔２０が４箇所に形成されている。夫々の給油孔２０から、主軸４ａと主軸受６、主軸側偏芯部４ｃと第１のピストン１１ａ、副軸側偏芯部４ｄと第２のピストン１１ｂ及び副軸４ｂと副軸受７の間の摺動部に潤滑油が供給される。   The supply of the lubricating oil to each sliding portion of the compression mechanism unit 3 is performed by raising the lubricating oil stored in the bottom of the sealed container 1 along the inner diameter 4f of the crankshaft 4 by the centrifugal force generated by the rotation of the crankshaft 4. It is carried out from an oil supply hole 20 provided in the shaft 4. In the example of FIG. 1, the oil supply holes 20 are formed at four locations. From the respective oil supply holes 20, the main shaft 4 a and the main bearing 6, the main shaft side eccentric portion 4 c and the first piston 11 a, the sub shaft side eccentric portion 4 d and the second piston 11 b, the sub shaft 4 b and the sub bearing 7 are provided. Lubricating oil is supplied to the sliding portion.

クランク軸４は、運転中の圧縮ガス負荷による撓みを抑えるよう、ヤング率１５０ＧＰａ以上の素材を使用する。さらに、運転時の振動を抑えるために、主軸側偏芯部４ｃと副軸側偏芯部４ｄは、略同一形状（同一直径、同一軸方向長さ）、略同一偏芯量とし、回転時の遠心力のバランスを保っている。   The crankshaft 4 uses a material having a Young's modulus of 150 GPa or more so as to suppress bending due to a compressed gas load during operation. Furthermore, in order to suppress vibration during operation, the main shaft side eccentric portion 4c and the sub shaft side eccentric portion 4d have substantially the same shape (same diameter, same length in the same axial direction) and substantially the same amount of eccentricity. The balance of centrifugal force is maintained.

ここで、本実施の形態１では、以下の理由により、主軸側偏芯部４ｃの反偏芯側外周面を、主軸４ａの外周面よりも軸中心側になるように形成している。そして、副軸４ｂの外径を主軸４ａの外径よりも細く形成し、副軸側偏芯部４ｄの反偏芯側外周面を、副軸４ｂの外周面よりも外周側（反軸中心側）になるように形成している。   Here, in the first embodiment, the anti-eccentric side outer peripheral surface of the main shaft side eccentric portion 4c is formed to be closer to the axial center side than the outer peripheral surface of the main shaft 4a for the following reason. Then, the outer diameter of the sub-shaft 4b is formed to be smaller than the outer diameter of the main shaft 4a, and the anti-eccentric outer peripheral surface of the sub-shaft side eccentric portion 4d is arranged on the outer peripheral side (the anti-axial center) of the sub-shaft 4b. Side).

上述のように、副軸側偏芯部４ｄは主軸側偏芯部４ｃと同一形状、同一偏芯量となっている。このため、副軸４ｂの外径が主軸４ａの外径と同一の場合、主軸側偏芯部４ｃの反偏芯側外周面を主軸４ａの外周面よりも軸中心側になるように形成すると、副軸側偏芯部４ｄの反偏芯側外周面も副軸４ｂの外周面よりも軸中心側になる。すると、副軸４ｂ側から第１のピストン１１ａ及び第２のピストン１１ｂを取り付けようとした場合、第１のピストン１１ａ及び第２のピストン１１ｂに副軸側偏芯部４ｄを挿入することができなくなる。つまり、第１のピストン１１ａ及び第２のピストン１１ｂを主軸側偏芯部４ｃ及び副軸側偏芯部４ｄに取り付けることができなくなる。そのため、本実施の形態１では副軸側偏芯部４ｄの反偏芯側外周面を副軸４ｂの外周面よりも外周側に形成し、第１のピストン１１ａ及び第２のピストン１１ｂの取り付けを可能にしている。また、第１のピストン１１ａ及び第２のピストン１１ｂの取り付けに影響しない主軸４ａは、クランク軸４の強度を確保するため、その外径を副軸４ｂの外径よりも大きくしている。   As described above, the countershaft side eccentric portion 4d has the same shape and the same amount of eccentricity as the main shaft side eccentric portion 4c. For this reason, when the outer diameter of the sub-shaft 4b is the same as the outer diameter of the main shaft 4a, the anti-eccentric outer peripheral surface of the main shaft-side eccentric portion 4c is formed so as to be closer to the shaft center side than the outer peripheral surface of the main shaft 4a. The counter eccentric side outer peripheral surface of the sub shaft side eccentric portion 4d is also closer to the shaft center side than the outer peripheral surface of the sub shaft 4b. Then, when it is going to attach the 1st piston 11a and the 2nd piston 11b from the subshaft 4b side, the subshaft side eccentric part 4d can be inserted in the 1st piston 11a and the 2nd piston 11b. Disappear. That is, the first piston 11a and the second piston 11b cannot be attached to the main shaft side eccentric portion 4c and the sub shaft side eccentric portion 4d. Therefore, in Embodiment 1, the counter eccentric side outer peripheral surface of the sub shaft side eccentric portion 4d is formed on the outer peripheral side with respect to the outer peripheral surface of the sub shaft 4b, and the first piston 11a and the second piston 11b are attached. Is possible. Further, the main shaft 4a that does not affect the attachment of the first piston 11a and the second piston 11b has an outer diameter larger than that of the auxiliary shaft 4b in order to ensure the strength of the crankshaft 4.

また、本実施の形態１では、クランク軸４（より詳しくは中間軸４ｅ）の強度を確保しつつ主軸側偏芯部４ｃ及び副軸側偏芯部４ｄの偏芯量を大きくとるため、図２〜図４に示す形状としている。以下、図２〜図４を用いて、仕切板１０の貫通孔の内径１０ａ、主軸側偏芯部４ｃ及び副軸側偏芯部４ｄの外径、中間軸４ｅの外径、並びに、主軸側偏芯部４ｃ及び副軸側偏芯部４ｄの反偏芯側外周面位置の関係について説明する。   In the first embodiment, the eccentric amount of the main shaft side eccentric portion 4c and the sub shaft side eccentric portion 4d is increased while securing the strength of the crankshaft 4 (more specifically, the intermediate shaft 4e). 2 to 4 as shown in FIG. Hereinafter, the inner diameter 10a of the through hole of the partition plate 10, the outer diameter of the main shaft side eccentric portion 4c and the sub shaft side eccentric portion 4d, the outer diameter of the intermediate shaft 4e, and the main shaft side will be described with reference to FIGS. The relationship between the eccentric part 4c and the counter eccentric side outer peripheral surface position of the auxiliary shaft side eccentric part 4d will be described.

図２に示すように、仕切板１０は、貫通孔の内径１０ａが直径Ｄｍｐとなっている。そして、この直径Ｄｍｐは、副軸側偏芯部４ｄ及び主軸側偏芯部４ｃの外径Ｄｐよりも小さく形成されている。
つまり、
Ｄｍｐ＜Ｄｐ…（１）
となっている。 As shown in FIG. 2, in the partition plate 10, the inner diameter 10a of the through hole is a diameter Dmp. The diameter Dmp is smaller than the outer diameter Dp of the sub-shaft side eccentric portion 4d and the main shaft side eccentric portion 4c.
That means
Dmp <Dp (1)
It has become.

ここで、仮に仕切板１０が一体部品で形成されているとする。中間軸４ｅは仕切板１０に形成された貫通孔の内部に配置されるため、例えば副軸４ｂ及び副軸側偏芯部４ｄを仕切板１０の貫通孔に通し、仕切板１０を中間軸４ｅの位置に配置する必要がある。しかしながら、本実施の形態１ではＤｍｐ＜Ｄｐとなっているため、副軸側偏芯部４ｄを仕切板１０の貫通孔に通すことができず、仕切板１０を中間軸４ｅの位置に配置することができない。そこで、図４に示すように、本実施の形態１では、貫通孔を通る断面で仕切板を２つ（第１の分割板１０ｂ、第２の分割板１０ｃ）に分割している。中間軸４ｅを挟み込むようにして第１の分割板１０ｂ及び第２の分割板１０ｃを配置することにより、Ｄｍｐ＜Ｄｐとなっていても、仕切板１０を中間軸４ｅの位置に配置することができる。なお、仕切板１０の分割数は、２つに限らず、例えば３つ以上としても勿論よい。   Here, it is assumed that the partition plate 10 is formed as an integral part. Since the intermediate shaft 4e is disposed inside a through hole formed in the partition plate 10, for example, the sub shaft 4b and the sub shaft side eccentric portion 4d are passed through the through hole of the partition plate 10, and the partition plate 10 is passed through the intermediate shaft 4e. It is necessary to arrange in the position. However, since Dmp <Dp in the first embodiment, the countershaft side eccentric portion 4d cannot be passed through the through hole of the partition plate 10, and the partition plate 10 is disposed at the position of the intermediate shaft 4e. I can't. Therefore, as shown in FIG. 4, in the first embodiment, the partition plate is divided into two (first divided plate 10b and second divided plate 10c) in a cross section passing through the through hole. By arranging the first divided plate 10b and the second divided plate 10c so as to sandwich the intermediate shaft 4e, the partition plate 10 can be arranged at the position of the intermediate shaft 4e even if Dmp <Dp. it can. Of course, the number of divisions of the partition plate 10 is not limited to two, but may be three or more, for example.

つまり、仕切板１０を複数に分割して形成することで、副軸側偏芯部４ｄ及び主軸側偏芯部４ｃの偏芯量を大きくとっても、一体部品の仕切板１０の場合には大きくなってしまう内径１０ａを小さくすることができる。仕切板１０の内径が小さいと、副軸側偏芯部４ｄ及び主軸側偏芯部４ｃにそれぞれ第２のピストン１１ｂ及び第１のピストン１１ａを挿入して圧縮室を形成した場合に、第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の外周面と仕切板１０の内径との距離を長く確保できる。このため、冷媒ガスの圧縮工程において低圧となっている第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の外周面近傍と、圧縮室から吐出された冷媒ガス空間と連通し高圧となっている仕切板１０の内径１０ａ内と、のシール長さを大きく確保することができる。したがって、高圧となっている仕切板１０の内径１０ａ内から低圧となっている第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の外周面近傍へ高圧の冷媒ガスが漏れることを減少させることができる。   In other words, by dividing the partition plate 10 into a plurality of parts, even if the eccentric amounts of the countershaft side eccentric portion 4d and the main shaft side eccentric portion 4c are increased, the partition plate 10 is an integral part. It is possible to reduce the inner diameter 10a. When the inner diameter of the partition plate 10 is small, the second piston 11b and the first piston 11a are inserted into the sub-shaft side eccentric portion 4d and the main shaft-side eccentric portion 4c, respectively, to form the second compression chamber. It is possible to secure a long distance between the outer peripheral surface of the piston 11b and the first piston 11a on the opposite eccentric side and the inner diameter of the partition plate 10. For this reason, in the refrigerant gas compression step, the second piston 11b and the vicinity of the outer surface of the first piston 11a opposite to the eccentric side, the refrigerant gas space discharged from the compression chamber, and the high pressure communicate with each other. A large seal length can be ensured between the inner diameter 10a of the partition plate 10 formed. Accordingly, the high-pressure refrigerant gas is less leaked from the inner diameter 10a of the partition plate 10 having a high pressure to the vicinity of the outer peripheral surface of the second piston 11b having a low pressure and the first piston 11a on the side opposite to the eccentric side. Can be made.

また図３及び下記式（２）に示すように、本実施の形態１では、中間軸４ｅの外周面の半径Ｒｃは、中間軸４ｅの軸中心（つまり、主軸４ａ及び副軸４ｂの軸中心）から第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の内周面までの距離Ｒｐ−ｅよりも大きくなっている。換言すると、中間軸４ｅの外周面の半径Ｒｃは、中間軸４ｅの軸中心から副軸側偏芯部４ｄ及び主軸側偏芯部４ｃの反偏芯側の外周面までの距離Ｒｐ−ｅよりも大きくなっている。
Ｒｃ＞Ｒｐ−ｅ…（２）
つまり、中間軸４ｅの外周面は、第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の内周面よりも外周側に形成されている。換言すると、中間軸４ｅの外周面は、副軸側偏芯部４ｄ及び主軸側偏芯部４ｃの反偏芯側の外周面よりも外周側に形成されている。
なお、中間軸４ｅは仕切板１０の内径１０ａの内部に配置されるため、
Ｒｃ＜Ｄｍｐ／２…（３）
となっている。 As shown in FIG. 3 and the following formula (2), in the first embodiment, the radius Rc of the outer peripheral surface of the intermediate shaft 4e is the axial center of the intermediate shaft 4e (that is, the axial center of the main shaft 4a and the sub shaft 4b). ) To the inner peripheral surface of the second piston 11b and the first piston 11a on the side opposite to the eccentricity Rp-e. In other words, the radius Rc of the outer peripheral surface of the intermediate shaft 4e is based on the distance Rp-e from the center of the intermediate shaft 4e to the outer peripheral surface of the sub-shaft side eccentric portion 4d and the main shaft side eccentric portion 4c on the opposite eccentric side. Is also getting bigger.
Rc> Rp-e (2)
That is, the outer peripheral surface of the intermediate shaft 4e is formed on the outer peripheral side with respect to the inner peripheral surfaces on the opposite eccentric side of the second piston 11b and the first piston 11a. In other words, the outer peripheral surface of the intermediate shaft 4e is formed on the outer peripheral side with respect to the outer peripheral surface of the countershaft side eccentric portion 4d and the main shaft side eccentric portion 4c on the opposite eccentric side.
Since the intermediate shaft 4e is arranged inside the inner diameter 10a of the partition plate 10,
Rc <Dmp / 2 (3)
It has become.

このように中間軸４ｅを構成することで、中間軸４ｅの外径を大きくすることができ、クランク軸４の剛性を高くすることができる。このため、冷媒ガスを圧縮する工程でクランク軸４に働くガス荷重によってクランク軸４が変形することを軽減できるので、主軸受６及び副軸受７内での油膜の状態も良好に保つことができ、クランク軸４の信頼性を高くすることができる。   By configuring the intermediate shaft 4e in this way, the outer diameter of the intermediate shaft 4e can be increased, and the rigidity of the crankshaft 4 can be increased. For this reason, since it is possible to reduce the deformation of the crankshaft 4 due to the gas load acting on the crankshaft 4 in the process of compressing the refrigerant gas, the state of the oil film in the main bearing 6 and the sub-bearing 7 can be maintained well. The reliability of the crankshaft 4 can be increased.

したがって、本実施の形態１のように構成された２気筒回転圧縮機１００は、クランク軸４の信頼性を確保しつつ、主軸側偏芯部４ｃ及び副軸側偏芯部４ｄの偏芯量を大きくとって圧縮室の排除容積を拡大でき、２気筒回転圧縮機１００の高出力化が可能となる。   Therefore, the two-cylinder rotary compressor 100 configured as in the first embodiment secures the reliability of the crankshaft 4, and the eccentric amount of the main shaft side eccentric portion 4c and the sub shaft side eccentric portion 4d. As a result, the displacement volume of the compression chamber can be increased, and the output of the two-cylinder rotary compressor 100 can be increased.

また、言い換えれば、同じ出力を得るのに圧縮室の容積を小さくでき、２気筒回転圧縮機１００の小型軽量化が可能となる。   In other words, the volume of the compression chamber can be reduced to obtain the same output, and the two-cylinder rotary compressor 100 can be reduced in size and weight.

さらに言い換えれば、圧縮室の容積を変更しない場合には、圧縮室の軸方向高さが扁平となる分だけ、つまり第１のシリンダ８及び第２のシリンダ９の厚みが薄くなる分だけ、これら第１のシリンダ８及び第２のシリンダ９のシリンダ内径と第１のピストン１１ａ及び第２のピストン１１ｂの外径をより大きくできる。このため、第１のシリンダ８及び第２のシリンダ９のシリンダ内径と第１のピストン１１ａ及び第２のピストン１１ｂとのシール部を長く確保でき、圧縮効率を改善することができる。   In other words, when the volume of the compression chamber is not changed, the axial height of the compression chamber is flattened, that is, the thickness of the first cylinder 8 and the second cylinder 9 is thinned. The cylinder inner diameters of the first cylinder 8 and the second cylinder 9 and the outer diameters of the first piston 11a and the second piston 11b can be made larger. For this reason, the cylinder inner diameters of the first cylinder 8 and the second cylinder 9 and the seal portion between the first piston 11a and the second piston 11b can be secured long, and the compression efficiency can be improved.

ところで、本実施の形態１に係る２気筒回転圧縮機１００に、圧縮機構部３の軸方向長さを短くする工夫をさらに施してもよい。このとき、例えば第１のピストン１１ａを副軸４ｂ側から取り付けようとすると、圧縮機構部３の軸方向長さを短くする際に第１のピストン１１ａ及び第２のピストン１１ｂの軸方向長さを変更しない場合、つまり、圧縮室の軸方向高さを変更しない場合、第１のピストン１１ａが中間軸４ｅを通過できなくなることが懸念される。この懸念事項を解消するには、主軸側偏芯部４ｃ及び副軸側偏芯部４ｄのうちの少なくとも一方の軸方向長さを短くする下記の方法や、中間軸４ｅの軸方向長さを短くする下記の方法が考えられる。   Incidentally, the two-cylinder rotary compressor 100 according to the first embodiment may be further devised to shorten the axial length of the compression mechanism unit 3. At this time, for example, if the first piston 11a is to be attached from the side of the auxiliary shaft 4b, the axial lengths of the first piston 11a and the second piston 11b when the axial length of the compression mechanism portion 3 is shortened. If it is not changed, that is, if the axial height of the compression chamber is not changed, there is a concern that the first piston 11a cannot pass through the intermediate shaft 4e. In order to eliminate this concern, the following method of shortening the axial length of at least one of the main shaft side eccentric portion 4c and the sub shaft side eccentric portion 4d, or the axial length of the intermediate shaft 4e can be reduced. The following method of shortening can be considered.

図示はしないが、主軸側偏芯部４ｃ及び副軸側偏芯部４ｄのうちの少なくとも一方の軸方向長さを短くする方法とは、主軸側偏芯部４ｃ及び副軸側偏芯部４ｄのうちの少なくとも一方の軸方向長さを、当該偏芯部に取り付けられるピストン（第１のピストン１１ａ及び第２のピストン１１ｂ）の長さよりも短くする方法である。この場合、軸方向長さを短くする偏芯部は、中間軸４ｅ側を削って軸方向の長さを短くする。   Although not shown, the method of shortening the axial length of at least one of the main shaft side eccentric portion 4c and the sub shaft side eccentric portion 4d is the main shaft side eccentric portion 4c and the sub shaft side eccentric portion 4d. In this method, the axial length of at least one of the pistons is made shorter than the lengths of the pistons (the first piston 11a and the second piston 11b) attached to the eccentric part. In this case, the eccentric portion that shortens the axial length shortens the axial length by scraping the intermediate shaft 4e side.

第１のピストン１１ａの軸方向長さよりも、中間軸４ｅの軸方向長さが長ければ、第１のピストン１１ａを主軸側偏芯部４ｃに組み付けることができる。   If the axial length of the intermediate shaft 4e is longer than the axial length of the first piston 11a, the first piston 11a can be assembled to the main shaft side eccentric portion 4c.

つまり、中間軸４ｅの軸方向長さが、第１のピストン１１ａを主軸側偏芯部４ｃに組み付けることができる略最小寸法となるように、主軸側偏芯部４ｃ及び副軸側偏芯部４ｄのうちの少なくとも一方の軸方向長さを、当該偏芯部に取り付けられるピストン（第１のピストン１１ａ及び第２のピストン１１ｂ）の長さよりも短くする。それにより、第１のピストン１１ａ及び第２のピストン１１ｂの軸方向長さを変更せずに圧縮機構部３の軸方向長さを短くできる。   That is, the main shaft side eccentric portion 4c and the sub shaft side eccentric portion are such that the axial length of the intermediate shaft 4e is substantially the minimum dimension that allows the first piston 11a to be assembled to the main shaft side eccentric portion 4c. The axial length of at least one of 4d is made shorter than the lengths of the pistons (first piston 11a and second piston 11b) attached to the eccentric portion. Thereby, the axial direction length of the compression mechanism part 3 can be shortened, without changing the axial direction length of the 1st piston 11a and the 2nd piston 11b.

圧縮機構部３の軸方向長さを短くする他の方法は、図５に示すように、第１のピストン１１ａの軸方向の長さより中間軸４ｅの軸方向長さを短くし、第１のピストン１１ａを主軸側偏芯部４ｃに組み付け可能にするために、第１のピストン１１ａの内径の軸方向両端面に逃がし形状１１ａ−１を設ける方法である。逃がし形状１１ａ−１は、傾斜、段差等で形成する。   As shown in FIG. 5, another method for shortening the axial length of the compression mechanism section 3 is to shorten the axial length of the intermediate shaft 4e from the axial length of the first piston 11a, In order to allow the piston 11a to be assembled to the main shaft side eccentric portion 4c, a relief shape 11a-1 is provided on both axial end surfaces of the inner diameter of the first piston 11a. The relief shape 11a-1 is formed with an inclination, a step or the like.

図５により、第１のピストン１１ａを主軸側偏芯部４ｃに組み付ける手順を説明する。
（１）図５（ａ）に示すように、第１のピストン１１ａを、副軸４ｂ、副軸側偏芯部４ｄをくぐらせて、第１のピストン１１ａの軸方向の一端を主軸側偏芯部４ｃに当接させる。
（２）次に、図５（ｂ）に示すように、第１のピストン１１ａを傾ける（図５（ｂ）では反時計方向）。
（３）そして、図５（ｃ）に示すように、主軸側偏芯部４ｃの偏芯方向に、傾いた状態のまま移動させる。第１のピストン１１ａの内径が、主軸側偏芯部４ｃの反偏芯方向の外周面に当接するまで傾いた状態のまま移動させる。
（４）最後に、第１のピストン１１ａを主軸側偏芯部４ｃに挿入する。 The procedure for assembling the first piston 11a to the main shaft side eccentric portion 4c will be described with reference to FIG.
(1) As shown in FIG. 5 (a), the first piston 11a is passed through the sub shaft 4b and the sub shaft side eccentric portion 4d so that one end of the first piston 11a in the axial direction is displaced from the main shaft side. It abuts on the core 4c.
(2) Next, as shown in FIG. 5 (b), the first piston 11a is tilted (counterclockwise in FIG. 5 (b)).
(3) Then, as shown in FIG. 5 (c), the main shaft side eccentric portion 4c is moved while being inclined in the eccentric direction. The first piston 11a is moved while being inclined until the inner diameter of the first piston 11a abuts on the outer circumferential surface of the main shaft side eccentric portion 4c in the anti-eccentric direction.
(4) Finally, the first piston 11a is inserted into the main shaft side eccentric portion 4c.

第１のピストン１１ａの内径の軸方向両端面に逃がし形状１１ａ−１を設けることによる効果を説明する前に、図７により、主軸側偏芯部４ｃ及び副軸側偏芯部４ｄのうちの少なくとも一方の軸方向長さ、又は中間軸４ｅの軸方向長さを短くしない比較例について説明する。   Before describing the effect of providing the relief shape 11a-1 on both axial end surfaces of the inner diameter of the first piston 11a, FIG. 7 shows that the main shaft side eccentric portion 4c and the sub shaft side eccentric portion 4d are A comparative example in which at least one axial length or the axial length of the intermediate shaft 4e is not shortened will be described.

図７に示す比較例の組み立て手順は、以下に示すとおりである。
（１）図７（ａ）に示すように、第１のピストン１１ａを、副軸４ｂ、副軸側偏芯部４ｄをくぐらせて、第１のピストン１１ａの軸方向の一端を主軸側偏芯部４ｃに当接させる。
（２）図７（ｂ）に示すように、第１のピストン１１ａを、中間軸４ｅにおいて主軸側偏芯部４ｃ側に移動する。
（３）図７（ｃ）に示すように、第１のピストン１１ａを、主軸側偏芯部４ｃに挿入する。 The assembly procedure of the comparative example shown in FIG. 7 is as follows.
(1) As shown in FIG. 7 (a), the first piston 11a is passed through the sub shaft 4b and the sub shaft side eccentric portion 4d, and one end of the first piston 11a in the axial direction is displaced from the main shaft side. It abuts on the core 4c.
(2) As shown in FIG. 7B, the first piston 11a is moved to the main shaft side eccentric portion 4c side in the intermediate shaft 4e.
(3) As shown in FIG. 7C, the first piston 11a is inserted into the main shaft side eccentric portion 4c.

図６は、図５に示した第１のピストン１１ａの内径の軸方向両端面に逃がし形状１１ａ−１を設けた本実施の形態と、図７に示す比較例とを比較した図である。図６（ａ）が図７（ｃ）相当図で、図６（ｂ）が図５（ｄ）相当図である。   FIG. 6 is a diagram comparing the present embodiment in which the relief shape 11a-1 is provided on both axial end surfaces of the inner diameter of the first piston 11a shown in FIG. 5 and the comparative example shown in FIG. FIG. 6A is a view corresponding to FIG. 7C, and FIG. 6B is a view corresponding to FIG.

図５に示した第１のピストン１１ａの内径の軸方向両端面に逃がし形状１１ａ−１を設けたクランク軸４は、中間軸４ｅの軸方向の長さが、比較例の中間軸４ｅの軸方向の長さよりも、寸法ｄだけ短い。そのため、圧縮機構部３の軸方向の長さを、寸法ｄだけ短縮できる。   The crankshaft 4 provided with the relief shape 11a-1 on both axial end surfaces of the inner diameter of the first piston 11a shown in FIG. 5 has the axial length of the intermediate shaft 4e that is the axis of the intermediate shaft 4e of the comparative example. The dimension d is shorter than the length in the direction. Therefore, the axial length of the compression mechanism unit 3 can be shortened by the dimension d.

主軸側偏芯部４ｃ及び副軸側偏芯部４ｄのうちの少なくとも一方の軸方向長さを、当該偏芯部に取り付けられるピストン（第１のピストン１１ａ及び第２のピストン１１ｂ）の長さよりも短くする方法、又は第１のピストン１１ａの軸方向の長さより中間軸４ｅの軸方向長さを短くし、第１のピストン１１ａを主軸側偏芯部４ｃに組み付け可能にするために、第１のピストン１１ａの内径の軸方向両端面に逃がし形状１１ａ−１を設ける方法によれば、上記のように、圧縮機構部をコンパクトに設計できるという利点がある。   The axial length of at least one of the main shaft side eccentric portion 4c and the sub shaft side eccentric portion 4d is determined from the lengths of the pistons (the first piston 11a and the second piston 11b) attached to the eccentric portion. In order to shorten the axial length of the intermediate shaft 4e to be shorter than the axial length of the first piston 11a so that the first piston 11a can be assembled to the main shaft side eccentric portion 4c. According to the method of providing the relief shape 11a-1 on both axial end surfaces of the inner diameter of one piston 11a, there is an advantage that the compression mechanism can be designed compactly as described above.

さらに、圧縮ガス負荷の作用点であるクランク軸４の主軸側偏芯部４ｃ又は副軸側偏芯部４ｄと、支持点となる主軸受６又は副軸受７までの間隔を小さくできるため、同一ガス負荷においてもクランク軸４の撓みを抑制できる。クランク軸４の撓みが大きくなると、主軸受６又は副軸受７に対するクランク軸４の傾きが大きくなり、片当たりが生じる。しかし、クランク軸４の撓みの抑制により片当たりを抑制し、主軸受６又は副軸受７の信頼性を向上することができる。   Furthermore, the distance between the main shaft side eccentric portion 4c or the sub shaft side eccentric portion 4d of the crankshaft 4 which is the operating point of the compressed gas load and the main bearing 6 or the sub bearing 7 serving as a support point can be reduced. The bending of the crankshaft 4 can be suppressed even under a gas load. When the bending of the crankshaft 4 is increased, the inclination of the crankshaft 4 with respect to the main bearing 6 or the sub-bearing 7 is increased, and one-sided contact occurs. However, by suppressing the bending of the crankshaft 4, it is possible to suppress the contact with each other and improve the reliability of the main bearing 6 or the sub-bearing 7.

なお、主軸側偏芯部４ｃ及び副軸側偏芯部４ｄのうちの少なくとも一方の軸方向長さを、当該偏芯部に取り付けられるピストン（第１のピストン１１ａ及び第２のピストン１１ｂ）の長さよりも短くする方法と、第１のピストン１１ａの軸方向の長さより中間軸４ｅの軸方向長さを短くし、第１のピストン１１ａを主軸側偏芯部４ｃに組み付け可能にするために、第１のピストン１１ａの内径の軸方向両端面に逃がし形状１１ａ−１を設ける方法とを組み合わせて実施してもよい。これにより、第１のピストン１１ａの主軸側偏芯部４ｃへの組み付けを、さらに容易に行うことができる。   It should be noted that the axial length of at least one of the main shaft side eccentric portion 4c and the sub shaft side eccentric portion 4d is set to the piston (first piston 11a and second piston 11b) attached to the eccentric portion. To shorten the axial length of the intermediate shaft 4e from the axial length of the first piston 11a and to make the first piston 11a assembled to the main shaft side eccentric portion 4c. A method of providing the relief shape 11a-1 on both axial end surfaces of the inner diameter of the first piston 11a may be combined. Thereby, the assembly | attachment to the main axis | shaft side eccentric part 4c of the 1st piston 11a can be performed still more easily.

以上、本実施の形態１のように構成された２気筒回転圧縮機１００においては、仕切板１０の内径１０ａの直径Ｄｍｐを副軸側偏芯部４ｄ及び主軸側偏芯部４ｃの外径Ｄｐよりも小さく形成し、中間軸４ｅの外周面を第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の内周面よりも外周側（換言すると、副軸側偏芯部４ｄ及び主軸側偏芯部４ｃの反偏芯側の外周面よりも外周側）に形成している。このため、クランク軸４の信頼性を確保しつつ、２気筒回転圧縮機１００の高出力化や高効率化が可能となる。   As described above, in the two-cylinder rotary compressor 100 configured as in the first embodiment, the diameter Dmp of the inner diameter 10a of the partition plate 10 is set to the outer diameter Dp of the auxiliary shaft side eccentric portion 4d and the main shaft side eccentric portion 4c. Smaller than the inner peripheral surface of the second piston 11b and the first piston 11a on the side opposite to the eccentric side (in other words, the sub-shaft side eccentric portion 4d and the main shaft). It is formed on the outer peripheral side of the outer eccentric surface of the side eccentric portion 4c on the side opposite to the eccentric side. For this reason, high output and high efficiency of the two-cylinder rotary compressor 100 can be achieved while ensuring the reliability of the crankshaft 4.

なお、本実施の形態１では、各圧縮室の吸入冷媒の圧力及び吐出冷媒の圧力が同じ２気筒回転圧縮機を例に説明したが、低段側の圧縮室で低圧の冷媒ガスを中圧の冷媒ガスに圧縮し、高段側の圧縮室で中圧の冷媒ガスを高圧の冷媒ガスに圧縮する２段回転圧縮機に本発明を実施することも勿論可能である。また、圧縮室の数も２つに限定されるものではなく、３つ以上の圧縮機を有する多気筒回転圧縮機や多段回転圧縮機に本発明を実施することも勿論可能である。また、本実施の形態１では密閉容器１内が高圧の吐出冷媒となる高圧シェル型の圧縮機を例に説明したが、密閉容器１内が低圧の吸入冷媒となる低圧シェル型の圧縮機に本発明を実施することも勿論可能である。   In the first embodiment, a two-cylinder rotary compressor in which the pressure of the suction refrigerant and the pressure of the discharge refrigerant in each compression chamber are the same has been described as an example. It is of course possible to implement the present invention in a two-stage rotary compressor that compresses the refrigerant gas into a high-pressure refrigerant gas and compresses the medium-pressure refrigerant gas into the high-pressure refrigerant gas in the high-stage compression chamber. Further, the number of compression chambers is not limited to two, and it is of course possible to implement the present invention in a multi-cylinder rotary compressor or a multistage rotary compressor having three or more compressors. In the first embodiment, the high-pressure shell type compressor in which the inside of the sealed container 1 is a high-pressure discharge refrigerant has been described as an example. However, the low-pressure shell type compressor in which the inside of the sealed container 1 is a low-pressure suction refrigerant is described. Of course, it is possible to implement the present invention.

実施の形態２．
実施の形態１では、仕切板１０の内径１０ａと第１のピストン１１ａ及び第２のピストン１１ｂとの関係について特に言及しなかった。仕切板１０の内径１０ａと第１のピストン１１ａ及び第２のピストン１１ｂとは、例えば次のような関係となるように形成すればよい。なお、本実施の形態２で特に記述しない項目については実施の形態１と同様とし、同一の機能や構成については同一の符号を用いて述べることとする。 Embodiment 2. FIG.
In Embodiment 1, the relationship between the inner diameter 10a of the partition plate 10 and the first piston 11a and the second piston 11b is not particularly mentioned. What is necessary is just to form the internal diameter 10a of the partition plate 10, the 1st piston 11a, and the 2nd piston 11b so that it may become the following relationships, for example. Note that items not particularly described in the second embodiment are the same as those in the first embodiment, and the same functions and configurations are described using the same reference numerals.

図８は実施の形態２を示す図で、２気筒回転圧縮機１００の圧縮機構部３の縦断面図である。
図８に示すように、中間軸４ｅの軸中心から仕切板１０の内径１０ａの内周面までの距離（つまり、仕切板１０の内径１０ａの半径）をＲｃ、中間軸４ｅの軸中心から第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の内周面までの距離をＲｐ−ｅ、中間軸４ｅの軸中心から第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の外周面までの距離をＲｒ−ｅとすると、
Ｒｍｐ＞Ｒｐ−ｅ…（４）
Ｒｍｐ＜Ｒｒ−ｅ…（５）
となっている。
つまり、第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の内周面は、仕切板１０の内径１０ａよりも、中間軸４ｅの軸中心側に配置されている。また、第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の外周面は、仕切板１０の内径１０ａよりも外周側に配置されている。 FIG. 8 shows the second embodiment and is a longitudinal sectional view of the compression mechanism section 3 of the two-cylinder rotary compressor 100.
As shown in FIG. 8, the distance from the center of the intermediate shaft 4e to the inner peripheral surface of the inner diameter 10a of the partition plate 10 (that is, the radius of the inner diameter 10a of the partition plate 10) is Rc, and the distance from the center of the intermediate shaft 4e is Rp-e, the distance from the center of the intermediate shaft 4e to the anti-eccentric side of the second piston 11b and the first piston 11a. If the distance to the outer peripheral surface is Rr-e,
Rmp> Rp-e (4)
Rmp <Rr-e (5)
It has become.
That is, the inner peripheral surfaces of the second piston 11b and the first piston 11a on the side opposite to the eccentric side are arranged closer to the center side of the intermediate shaft 4e than the inner diameter 10a of the partition plate 10. Further, the outer peripheral surfaces of the second piston 11 b and the first piston 11 a on the opposite eccentric side are arranged on the outer peripheral side with respect to the inner diameter 10 a of the partition plate 10.

なお、仕切板１０は、実施の形態１と同様に、複数の分割板に分割されている。また、仕切板１０の内径１０ａの直径Ｄｍｐと副軸側偏芯部４ｄ及び主軸側偏芯部４ｃの外径Ｄｐとの関係、中間軸４ｅの外周面と第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の内周面との関係、及び、中間軸４ｅと仕切板１０の内径１０ａとの関係等も、実施の形態１で示した式（１）〜式（３）と同様である。   Note that the partition plate 10 is divided into a plurality of divided plates, as in the first embodiment. Further, the relationship between the diameter Dmp of the inner diameter 10a of the partition plate 10 and the outer diameter Dp of the auxiliary shaft side eccentric portion 4d and the main shaft side eccentric portion 4c, the outer peripheral surface of the intermediate shaft 4e, the second piston 11b, and the first piston The relationship with the inner peripheral surface of the piston 11a on the side opposite to the eccentricity, the relationship between the intermediate shaft 4e and the inner diameter 10a of the partition plate 10 and the like are also the same as the equations (1) to (3) shown in the first embodiment. It is the same.

以上、このように構成された２気筒回転圧縮機１００においては、仕切板１０を複数に分割して形成することで、副軸側偏芯部４ｄ及び主軸側偏芯部４ｃの偏芯量を大きくとっても、一体部品の仕切板１０の場合には大きくなってしまう内径１０ａを小さくすることができる。仕切板１０の内径が小さいと、副軸側偏芯部４ｄ及び主軸側偏芯部４ｃにそれぞれ第２のピストン１１ｂ及び第１のピストン１１ａを挿入して圧縮室を形成した場合に、第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の外周面と仕切板１０の内径との距離を長く確保できる。このため、冷媒ガスの圧縮工程において低圧となっている第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の外周面近傍と、圧縮室から吐出された冷媒ガス空間と連通し高圧となっている仕切板１０の内径１０ａ内と、のシール長さを大きく確保することができる。したがって、実施の形態１と同様に、高圧となっている仕切板１０の内径１０ａ内から低圧となっている第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の外周面近傍へ高圧の冷媒ガスが漏れることを減少させることができる。   As described above, in the two-cylinder rotary compressor 100 configured as described above, the partition plate 10 is divided into a plurality of parts so that the eccentric amounts of the sub-shaft side eccentric portion 4d and the main shaft-side eccentric portion 4c are reduced. Even if it is large, the inner diameter 10a which becomes large in the case of the partition plate 10 of an integral part can be reduced. When the inner diameter of the partition plate 10 is small, the second piston 11b and the first piston 11a are inserted into the sub-shaft side eccentric portion 4d and the main shaft-side eccentric portion 4c, respectively, to form the second compression chamber. It is possible to secure a long distance between the outer peripheral surface of the piston 11b and the first piston 11a on the opposite eccentric side and the inner diameter of the partition plate 10. For this reason, in the refrigerant gas compression step, the second piston 11b and the vicinity of the outer surface of the first piston 11a opposite to the eccentric side, the refrigerant gas space discharged from the compression chamber, and the high pressure communicate with each other. A large seal length can be ensured between the inner diameter 10a of the partition plate 10 formed. Therefore, as in the first embodiment, the high pressure is applied from the inside of the inner diameter 10a of the partition plate 10 having a high pressure to the vicinity of the outer peripheral surface of the second piston 11b having a low pressure and the anti-eccentric side of the first piston 11a. The leakage of the refrigerant gas can be reduced.

このとき、第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の外周面を仕切板１０の内径１０ａよりも外周側に配置しているので、冷媒ガスの圧縮工程において低圧となっている第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の外周面近傍と、圧縮室から吐出された冷媒ガス空間と連通し高圧となっている仕切板１０の内径１０ａ内と、のシール長さを確実に確保することができる。したがって、高圧となっている仕切板１０の内径１０ａ内から低圧となっている第２のピストン１１ｂ及び第１のピストン１１ａの反偏芯側の外周面近傍へ高圧の冷媒ガスが漏れることを確実に減少させることができる。   At this time, since the outer peripheral surfaces of the second piston 11b and the first piston 11a on the opposite eccentric side are arranged on the outer peripheral side with respect to the inner diameter 10a of the partition plate 10, the pressure becomes low in the refrigerant gas compression process. Between the outer peripheral surface of the second piston 11b and the first piston 11a opposite to the eccentric side, and the inner diameter 10a of the partition plate 10 communicating with the refrigerant gas space discharged from the compression chamber and having a high pressure. The seal length can be ensured reliably. Therefore, it is ensured that the high-pressure refrigerant gas leaks from the inner diameter 10a of the partition plate 10 that is at a high pressure to the vicinity of the outer peripheral surface of the second piston 11b that is at a low pressure and the anti-eccentric side of the first piston 11a. Can be reduced.

したがって、本実施の形態２のように構成された２気筒回転圧縮機１００においても、クランク軸４の信頼性を確保しつつ、２気筒回転圧縮機１００の高出力化や高効率化が可能となる。   Therefore, even in the two-cylinder rotary compressor 100 configured as in the second embodiment, it is possible to increase the output and the efficiency of the two-cylinder rotary compressor 100 while ensuring the reliability of the crankshaft 4. Become.

１ 密閉容器、２ 電動機、２ａ 固定子、２ｂ 回転子、３ 圧縮機構部、４ クランク軸、４ａ 主軸、４ｂ 副軸、４ｃ 主軸側偏芯部、４ｄ 副軸側偏芯部、４ｅ 中間軸、４ｅ−１ 第１の中間軸、４ｅ−２ 第２の中間軸、４ｆ 内径、６ 主軸受、７ 副軸受、８ 第１のシリンダ、９ 第２のシリンダ、１０ 仕切板、１０ａ 内径、１０ｂ 第１の分割板、１０ｃ 第２の分割板、１１ａ 第１のピストン、１１ａ−１ 逃がし形状、１１ｂ 第２のピストン、１２ ボルト、１３ ボルト、２０ 給油孔、２１ 吸入連結管、２２ 吸入連結管、２３ 吐出管、２４ ガラス端子、２５ リード線、４０ アキュムレータ、１００ ２気筒回転圧縮機。   DESCRIPTION OF SYMBOLS 1 Airtight container, 2 Electric motor, 2a Stator, 2b Rotor, 3 Compression mechanism part, 4 Crankshaft, 4a Main shaft, 4b Secondary shaft, 4c Main shaft side eccentric part, 4d Subshaft side eccentric part, 4e Intermediate shaft, 4e-1 first intermediate shaft, 4e-2 second intermediate shaft, 4f inner diameter, 6 main bearing, 7 auxiliary bearing, 8 first cylinder, 9 second cylinder, 10 partition plate, 10a inner diameter, 10b first 1 divided plate, 10c second divided plate, 11a first piston, 11a-1 relief shape, 11b second piston, 12 bolt, 13 bolt, 20 oil supply hole, 21 suction connection tube, 22 suction connection tube, 23 discharge pipe, 24 glass terminal, 25 lead wire, 40 accumulator, 100 2-cylinder rotary compressor.

Claims (3)

固定子及び回転子を有する電動機と、
前記回転子に固定された主軸、前記主軸の軸方向の反対側に設けられた副軸、前記主軸と前記副軸との間に所定の位相差を設けて形成された複数の偏芯部、並びに隣接する前記偏芯部の間に設けられた中間軸を有し、前記電動機により駆動されるクランク軸と、
円筒状の貫通孔が形成され、該貫通孔に前記偏芯部が配置されて圧縮室が形成される複数のシリンダと、
内部に前記中間軸が配置される円筒状の貫通孔が形成され、隣接する前記シリンダの圧縮室の間を仕切る仕切板と、
を備えた回転圧縮機であって、
前記中間軸の外周面は、前記偏芯部の反偏芯側の外周面よりも外周側に形成され、
前記仕切板は、該仕切板に形成された貫通孔を通る断面によって複数に分割されており、
前記仕切板の貫通孔の内径は、前記中間軸の外径よりも大きく、且つ、前記偏芯部の外径よりも小さく形成されていることを特徴とする回転圧縮機。 An electric motor having a stator and a rotor;
A main shaft fixed to the rotor, a sub shaft provided on the opposite side of the main shaft in the axial direction, a plurality of eccentric portions formed with a predetermined phase difference between the main shaft and the sub shaft; And an intermediate shaft provided between the adjacent eccentric portions, and a crankshaft driven by the electric motor,
A plurality of cylinders in which a cylindrical through hole is formed, and the eccentric portion is disposed in the through hole to form a compression chamber;
A cylindrical through hole in which the intermediate shaft is disposed is formed, and a partition plate for partitioning between the compression chambers of the adjacent cylinders;
A rotary compressor comprising:
The outer peripheral surface of the intermediate shaft is formed on the outer peripheral side with respect to the outer peripheral surface on the anti-eccentric side of the eccentric portion,
The partition plate is divided into a plurality of sections through a through hole formed in the partition plate,
The rotary compressor according to claim 1, wherein an inner diameter of the through hole of the partition plate is larger than an outer diameter of the intermediate shaft and smaller than an outer diameter of the eccentric portion. 固定子及び回転子を有する電動機と、
前記回転子に固定された主軸、前記主軸の軸方向の反対側に設けられた副軸、前記主軸と前記副軸との間に所定の位相差を設けて形成された複数の偏芯部、並びに隣接する前記偏芯部の間に設けられた中間軸を有し、前記電動機により駆動されるクランク軸と、
前記偏芯部に嵌合する複数のピストンと、
円筒状の貫通孔が形成され、該貫通孔に前記偏芯部及び前記ピストンが配置されて圧縮室が形成される複数のシリンダと、
内部に前記中間軸が配置される円筒状の貫通孔が形成され、隣接する前記シリンダの圧縮室の間を仕切る仕切板と、
を備えた回転圧縮機であって、
前記中間軸の外周面は、前記偏芯部の反偏芯側の外周面よりも外周側に形成され、
前記仕切板は、該仕切板に形成された貫通孔を通る断面によって複数に分割されており、
前記仕切板の貫通孔の内径は、前記中間軸の外径よりも大きく、且つ、前記偏芯部の外径よりも小さく形成され、
前記ピストンの反偏芯側外周面は、前記仕切板の貫通孔の内径よりも外周側に形成されていることを特徴とする回転圧縮機。 An electric motor having a stator and a rotor;
A main shaft fixed to the rotor, a sub shaft provided on the opposite side of the main shaft in the axial direction, a plurality of eccentric portions formed with a predetermined phase difference between the main shaft and the sub shaft; And an intermediate shaft provided between the adjacent eccentric portions, and a crankshaft driven by the electric motor,
A plurality of pistons fitted to the eccentric part;
A plurality of cylinders in which a cylindrical through hole is formed, and the eccentric portion and the piston are arranged in the through hole to form a compression chamber;
A cylindrical through hole in which the intermediate shaft is disposed is formed, and a partition plate for partitioning between the compression chambers of the adjacent cylinders;
A rotary compressor comprising:
The outer peripheral surface of the intermediate shaft is formed on the outer peripheral side with respect to the outer peripheral surface on the anti-eccentric side of the eccentric portion,
The partition plate is divided into a plurality of sections through a through hole formed in the partition plate,
The inner diameter of the through hole of the partition plate is larger than the outer diameter of the intermediate shaft and smaller than the outer diameter of the eccentric part,
2. The rotary compressor according to claim 1, wherein the outer circumferential surface of the piston on the side opposite to the eccentric side is formed on the outer circumferential side of the inner diameter of the through hole of the partition plate. 前記クランク軸は、ヤング率が１５０ＧＰａ以上の材料で形成されていることを特徴とする請求項１又は請求項２に記載の回転圧縮機。   The rotary compressor according to claim 1 or 2, wherein the crankshaft is made of a material having a Young's modulus of 150 GPa or more.
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