JP2016186285A - Rotary Compressor - Google Patents

Rotary Compressor Download PDF

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Publication number
JP2016186285A
JP2016186285A JP2015067242A JP2015067242A JP2016186285A JP 2016186285 A JP2016186285 A JP 2016186285A JP 2015067242 A JP2015067242 A JP 2015067242A JP 2015067242 A JP2015067242 A JP 2015067242A JP 2016186285 A JP2016186285 A JP 2016186285A
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Prior art keywords
stator
compressor
cylinder
end plate
compression
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JP6477137B2 (en
Inventor
駒井　裕二
Yuji Komai
裕二 駒井
尚哉 両角
Naoya Morozumi
尚哉 両角
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Fujitsu General Ltd
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Fujitsu General Ltd
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Priority to JP2015067242A priority Critical patent/JP6477137B2/en
Priority to AU2016201894A priority patent/AU2016201894B2/en
Priority to US15/080,328 priority patent/US20160281717A1/en
Priority to EP16162407.7A priority patent/EP3073118A1/en
Priority to CN201610177100.0A priority patent/CN106014992B/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
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • 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
    • F04C23/02—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • 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
    • F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D3/00—Axial-flow pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/20—Manufacture essentially without removing material
    • F04C2230/23—Manufacture essentially without removing material by permanently joining parts together
    • F04C2230/231—Manufacture essentially without removing material by permanently joining parts together by welding
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance

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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 obtain a rotary compressor that causes no compressive strain in a stator of a motor arranged in a compressor casing, has high motor efficiency and is suppressed in cost increase.SOLUTION: A rotary compressor comprises a compressor casing, a compression part that is arranged in the compressor casing, compresses a refrigerant sucked in through a suction part and discharges the same from a discharge part, and a motor that is arranged in the compressor casing and drives the compression part via a rotating shaft. In the rotary compressor, representing the inner diameter of a body part of the compressor casing as φDm, the outer diameter of an upper end plate of the compression part as φDb, and the outer diameter of a stator or the motor as φDs, the φDm, φDb and φDs are set to satisfy two inequalities of -0.05 mm≤φDm-φDb≤0.05 mm and 0.1 mm≤φDm-φDs≤0.2 mm. Plural portions circumferentially spaced of the outer peripheral part of the upper end plate and the outer peripheral part of the stator are spot-welded to the body part of the compressor casing.SELECTED DRAWING: Figure 5

Description

本発明は、空気調和機や冷凍機などに用いられるロータリ圧縮機に関する。   The present invention relates to a rotary compressor used for an air conditioner, a refrigerator, and the like.

ロータリ圧縮機では、圧縮機筐体内に配置されるモータのステータに圧縮歪みが生じると、ステータの磁化特性が劣化して鉄損が増加し、モータの効率が低下する。   In the rotary compressor, when compression distortion occurs in the stator of the motor disposed in the compressor casing, the magnetization characteristics of the stator deteriorate, the iron loss increases, and the efficiency of the motor decreases.

例えば、特許文献１には、密閉容器と、前記密閉容器に配置され、ステータとロータとを少なくとも含むモータと、前記ロータで駆動されるシャフトを少なくとも含む圧縮機構とを備え、前記圧縮機構の外径は前記固定子の外径より大きく、前記密閉容器と前記ステータの外径との間に挿入され、前記ステータの外周に締り嵌めで固定され、前記密閉容器に３箇所で溶接されるリング状の固定部材をさらに備える圧縮機が記載されている。   For example, Patent Document 1 includes an airtight container, a motor that is disposed in the airtight container and includes at least a stator and a rotor, and a compression mechanism that includes at least a shaft driven by the rotor. A diameter larger than the outer diameter of the stator, inserted between the sealed container and the outer diameter of the stator, fixed to the outer periphery of the stator with an interference fit, and welded to the sealed container at three locations A compressor further comprising a fixing member is described.

また、特許文献１には、密閉容器と、前記密閉容器に配置され、ステータとロータとを少なくとも含むモータと、前記ロータで駆動されるシャフトを少なくとも含む圧縮機構とを備え、前記圧縮機構の外径は前記ステータの外径より大きく、前記密閉容器の一部が絞り加工され、該絞り加工された部分が前記ステータに当接する絞り部をさらに備え、該絞り部と前記ステータとがレーザー溶接により固定される圧縮機が記載されている。   Patent Document 1 includes a sealed container, a motor disposed in the sealed container and including at least a stator and a rotor, and a compression mechanism including at least a shaft driven by the rotor. The diameter is larger than the outer diameter of the stator, a part of the hermetic container is drawn, and the drawn part further includes a drawn part that contacts the stator, and the drawn part and the stator are joined by laser welding. A fixed compressor is described.

また、特許文献２には、環状のステータと、前記ステータの内部空間に回転自在に配置されたロータと、前記ステータおよびロータを収納する筒状部を含む密閉容器と、前記ステータの外周面と前記筒状部の内周面との間に０．０１〜０．３０ｍｍの隙間を確保した状態で、前記ステータと前記筒状部とを周方向に３箇所以上のスポット溶接によって固定した圧縮機が記載されている。この圧縮機の圧縮機構は、マウンティングプレートにネジ止めされ、マウンティングプレートは、密閉容器の筒状部にスポット溶接されている。   Further, Patent Document 2 discloses an annular stator, a rotor rotatably disposed in the internal space of the stator, a sealed container including a cylindrical portion that houses the stator and the rotor, and an outer peripheral surface of the stator. The compressor which fixed the said stator and the said cylindrical part by the spot welding of three or more places in the circumferential direction in the state which ensured the clearance of 0.01-0.30 mm between the internal peripheral surfaces of the said cylindrical part. Is described. The compression mechanism of this compressor is screwed to the mounting plate, and the mounting plate is spot welded to the cylindrical portion of the sealed container.

特開２０１０−２５５６２３号公報JP 2010-255623 A 特開２００８−２４８８８９号公報JP 2008-248889 A

しかしながら、特許文献１に記載された、密閉容器と固定子の外径との間に挿入され、前記固定子の外周に締り嵌めで固定され、密閉容器に３箇所で溶接されるリング状の固定部材を備える圧縮機は、リング状の固定部材が固定子の外周に締り嵌めで固定されるので、固定子に圧縮歪みが生じ、モータの効率が低下するという問題がある。また、固定部材を用いる分、コストアップとなるという問題がある。   However, the ring-shaped fixing described in Patent Document 1 is inserted between the sealed container and the outer diameter of the stator, is fixed to the outer periphery of the stator with an interference fit, and is welded to the sealed container at three locations. The compressor including the members has a problem in that since the ring-shaped fixing member is fixed to the outer periphery of the stator by an interference fit, compression distortion occurs in the stator, and the efficiency of the motor decreases. Further, there is a problem that the cost is increased by using the fixing member.

また、特許文献１に記載された、密閉容器の一部が絞り加工され、該絞り加工された部分がステータに当接する絞り部を備え、該絞り部と前記ステータとがレーザー溶接により固定される圧縮機は、密閉容器の一部を絞り加工するので、その分、コストアップとなる、という問題がある。   Further, a part of the sealed container described in Patent Document 1 is drawn, and the drawn part includes a drawn part that comes into contact with the stator, and the drawn part and the stator are fixed by laser welding. Since the compressor draws a part of the sealed container, there is a problem that the cost increases accordingly.

また、特許文献２に記載された圧縮機は、ステータと筒状部との間に０．０１〜０．３０ｍｍの半径隙間を確保した状態で、前記ステータと前記筒状部とを周方向に３箇所以上のスポット溶接によって固定され、圧縮機構がマウンティングプレートにネジ止めされ、マウンティングプレートが、密閉容器の筒状部にスポット溶接されている。そのため、ステータと筒状部との間に０．３０ｍｍの半径隙間を設けた場合には、半径隙間が大きすぎ、ステータを筒状部に対して芯出しする必要があり組立工数が増大するという問題がある。また、圧縮機構がマウンティングプレートを介して筒状部に固定されているので、マウンティングプレートの分、コストアップとなる、という問題がある。   Moreover, the compressor described in patent document 2 is the state which ensured the radial gap of 0.01-0.30 mm between the stator and the cylindrical part, and made the said stator and the said cylindrical part into the circumferential direction. It is fixed by spot welding at three or more locations, the compression mechanism is screwed to the mounting plate, and the mounting plate is spot welded to the cylindrical portion of the sealed container. Therefore, when a 0.30 mm radial gap is provided between the stator and the cylindrical part, the radial gap is too large, and it is necessary to center the stator with respect to the cylindrical part, which increases the number of assembly steps. There's a problem. In addition, since the compression mechanism is fixed to the cylindrical portion via the mounting plate, there is a problem that the cost is increased by the amount of the mounting plate.

本発明は、圧縮機筐体内に配置されるモータのステータに圧縮歪みが生じることがなく、モータの効率が高く、コストアップを抑えたロータリ圧縮機を得ることを目的とする。   An object of the present invention is to obtain a rotary compressor in which compression distortion does not occur in a stator of a motor disposed in a compressor housing, the motor efficiency is high, and cost increase is suppressed.

本発明は、上部に冷媒の吐出部が設けられ、下部に冷媒の吸入部が設けられると共に潤滑油が貯留される密閉された縦置きの圧縮機筐体と、該圧縮機筐体内に配置され、環状のシリンダと該シリンダの端部を閉塞する上端板及び下端板とを有し、前記吸入部から吸入した冷媒を前記シリンダで圧縮して前記吐出部から吐出する圧縮部と、前記圧縮機筐体内に配置され、円筒状のステータと回転軸に固定され前記ステータ内で回転するロータとを有し、前記回転軸を介して前記圧縮部を駆動するモータと、を備えるロータリ圧縮機において、前記圧縮機筐体の胴部の内径をφＤｍ、前記圧縮部の上端板の外径をφＤｂ、前記モータのステータの外径をφＤｓとするとき、−０．０５ｍｍ≦φＤｍ−φＤｂ≦０．０５ｍｍ、及び、０．１ｍｍ≦φＤｍ−φＤｓ≦０．２ｍｍの二つの式を満たすように、前記φＤｍ、φＤｂ及びφＤｓを設定するとともに、前記上端板の外周部及び前記ステータの外周部の夫々の周方向に離間した複数箇所を前記圧縮機筐体の胴部にスポット溶接したことを特徴とする。   The present invention includes a vertically disposed compressor housing in which a refrigerant discharge portion is provided at an upper portion, a refrigerant suction portion is provided in a lower portion and lubricating oil is stored, and the compressor housing is disposed in the compressor housing. A compressor having an annular cylinder and an upper end plate and a lower end plate for closing the end of the cylinder, and compressing the refrigerant sucked from the suction portion by the cylinder and discharging the refrigerant from the discharge portion; and the compressor In a rotary compressor comprising: a cylindrical stator, a cylindrical stator and a rotor that is fixed to a rotation shaft and rotates within the stator; and a motor that drives the compression unit via the rotation shaft. When the inner diameter of the body of the compressor housing is φDm, the outer diameter of the upper end plate of the compressor is φDb, and the outer diameter of the stator of the motor is φDs, −0.05 mm ≦ φDm−φDb ≦ 0.05 mm And 0.1 mm ≦ φDm The φDm, φDb, and φDs are set so as to satisfy the two formulas of φDs ≦ 0.2 mm, and the outer peripheral portion of the upper end plate and the outer peripheral portion of the stator are compressed at a plurality of locations separated in the circumferential direction. It is characterized by spot welding to the body of the machine casing.

本発明は、圧縮機筐体の胴部の内径をφＤｍ、圧縮部の上端板の外径をφＤｂ、モータのステータの外径をφＤｓとするとき、−０．０５ｍｍ≦φＤｍ−φＤｂ≦０．０５ｍｍ、及び、０．１ｍｍ≦φＤｍ−φＤｓ≦０．２ｍｍの二つの式を満たすように、φＤｍ、φＤｂ及びφＤｓを設定するとともに、上端板の外周部及びステータの外周部の夫々の周方向に離間した複数箇所を圧縮機筐体の胴部にスポット溶接したので、圧縮機筐体内に配置されるモータのステータに圧縮歪みが生じることがなく、ステータの磁化特性が劣化しないので、モータの効率が高く、コストアップを抑えることができる。   In the present invention, when the inner diameter of the body of the compressor housing is φDm, the outer diameter of the upper end plate of the compression section is φDb, and the outer diameter of the stator of the motor is φDs, −0.05 mm ≦ φDm−φDb ≦ 0. ΦDm, φDb, and φDs are set so as to satisfy two formulas of 05 mm and 0.1 mm ≦ φDm−φDs ≦ 0.2 mm, and in the circumferential direction of the outer peripheral portion of the upper end plate and the outer peripheral portion of the stator. Since the plurality of spaced apart spots are spot welded to the body of the compressor casing, the stator of the motor disposed in the compressor casing does not undergo compressive strain, and the magnetizing characteristics of the stator do not deteriorate. The cost can be suppressed.

図１は、本発明に係るロータリ圧縮機の実施例を示す縦断面図である。FIG. 1 is a longitudinal sectional view showing an embodiment of a rotary compressor according to the present invention. 図２は、実施例のロータリ圧縮機の第１の圧縮部及び第２の圧縮部の上から見た横断面図である。FIG. 2 is a cross-sectional view of the rotary compressor of the embodiment as viewed from above the first compression unit and the second compression unit. 図３は、実施例のロータリ圧縮機のステータとロータの組立前を示す縦断面図である。FIG. 3 is a longitudinal sectional view showing the stator and the rotor before assembly of the rotary compressor of the embodiment. 図４は、実施例のロータリ圧縮機のステータとロータの組立後を示す縦断面図である。FIG. 4 is a longitudinal sectional view showing a state after assembly of the stator and the rotor of the rotary compressor of the embodiment. 図５は、実施例のロータリ圧縮機の圧縮部及びステータと圧縮機筐体の胴部の嵌合前を示す縦断面図である。FIG. 5 is a longitudinal cross-sectional view showing a state before the compression portion of the rotary compressor and the stator and the body portion of the compressor housing of the embodiment are fitted. 図６は、実施例のロータリ圧縮機の圧縮部及びステータと圧縮機筐体の胴部の嵌合後を示す縦断面図である。FIG. 6 is a longitudinal cross-sectional view showing the compression portion of the rotary compressor and the stator after the fitting of the body portion of the compressor housing of the embodiment. 図７は、図６のＡ−Ａ線に沿う横断面図である。FIG. 7 is a cross-sectional view taken along line AA in FIG. 図８は、図６のＢ−Ｂ線に沿う横断面図である。FIG. 8 is a cross-sectional view taken along line BB in FIG.

以下に、本発明を実施するための形態（実施例）につき、図面を参照しつつ詳細に説明する。   EMBODIMENT OF THE INVENTION Below, the form (Example) for implementing this invention is demonstrated in detail, referring drawings.

図１は、本発明に係るロータリ圧縮機の実施例を示す縦断面図である。図２は、実施例のロータリ圧縮機の第１の圧縮部及び第２の圧縮部の上から見た横断面図である。   FIG. 1 is a longitudinal sectional view showing an embodiment of a rotary compressor according to the present invention. FIG. 2 is a cross-sectional view of the rotary compressor of the embodiment as viewed from above the first compression unit and the second compression unit.

図１に示すように、ロータリ圧縮機１は、密閉された縦置き円筒状の圧縮機筐体１０の下部に配置された圧縮部１２と、圧縮機筐体１０の上部に配置され、回転軸１５を介して圧縮部１２を駆動するモータ１１と、を備えている。   As shown in FIG. 1, the rotary compressor 1 includes a compression unit 12 disposed at a lower portion of a hermetically sealed cylindrical compressor housing 10 and an upper portion of the compressor housing 10. And a motor 11 that drives the compression unit 12 via 15.

モータ１１のステータ１１１は、円筒状に形成され、圧縮機筐体１０の胴部１０Ａの内周面にスポット溶接されて固定される。本発明のロータリ圧縮機１の特徴的な構成である圧縮機筐体１０の胴部１０Ａとステータ１１１との寸法関係及び組立方法については後述する。ロータ１１２は、円筒状のステータ１１１の内部に配置され、モータ１１と圧縮部１２とを機械的に接続する回転軸１５に焼きばめされて固定されている。   The stator 111 of the motor 11 is formed in a cylindrical shape, and is fixed by spot welding to the inner peripheral surface of the body portion 10 </ b> A of the compressor housing 10. A dimensional relationship between the body portion 10A of the compressor housing 10 and the stator 111, which is a characteristic configuration of the rotary compressor 1 of the present invention, and an assembling method will be described later. The rotor 112 is disposed inside the cylindrical stator 111 and is fixed by being shrink-fitted to a rotating shaft 15 that mechanically connects the motor 11 and the compression unit 12.

圧縮部１２は、第１の圧縮部１２Ｓと第２の圧縮部１２Ｔとを備えており、第２の圧縮部１２Ｔは、第１の圧縮部１２Ｓの上側に配置されている。図２に示すように、第１の圧縮部１２Ｓは、環状の第１シリンダ１２１Ｓを備えている。第１シリンダ１２１Ｓは、環状の外周から張り出した第１側方張出部１２２Ｓを備え、第１側方張出部１２２Ｓには、第１吸入孔１３５Ｓと第１ベーン溝１２８Ｓが放射状に設けられている。また、第２の圧縮部１２Ｔは、環状の第２シリンダ１２１Ｔを備えている。第２シリンダ１２１Ｔは、環状の外周から張り出した第２側方張出部１２２Ｔを備え、第２側方張出部１２２Ｔには、第２吸入孔１３５Ｔと第２ベーン溝１２８Ｔが放射状に設けられている。   The compression unit 12 includes a first compression unit 12S and a second compression unit 12T, and the second compression unit 12T is disposed on the upper side of the first compression unit 12S. As shown in FIG. 2, the first compression unit 12S includes an annular first cylinder 121S. The first cylinder 121S includes a first lateral projecting portion 122S projecting from an annular outer periphery, and the first lateral projecting portion 122S is provided with first suction holes 135S and first vane grooves 128S radially. ing. The second compression unit 12T includes an annular second cylinder 121T. The second cylinder 121T includes a second lateral projecting portion 122T projecting from an annular outer periphery, and the second lateral projecting portion 122T is provided with second suction holes 135T and second vane grooves 128T radially. ing.

図２に示すように、第１シリンダ１２１Ｓには、モータ１１の回転軸１５と同心に、円形の第１シリンダ内壁１２３Ｓが形成されている。第１シリンダ内壁１２３Ｓ内には、第１シリンダ１２１Ｓの内径よりも小さい外径の第１環状ピストン１２５Ｓが配置され、第１シリンダ内壁１２３Ｓと第１環状ピストン１２５Ｓとの間に、冷媒を吸入し圧縮して吐出する第１シリンダ室１３０Ｓが形成される。第２シリンダ１２１Ｔには、モータ１１の回転軸１５と同心に、円形の第２シリンダ内壁１２３Ｔが形成されている。第２シリンダ内壁１２３Ｔ内には、第２シリンダ１２１Ｔの内径よりも小さい外径の第２環状ピストン１２５Ｔが配置され、第２シリンダ内壁１２３Ｔと第２環状ピストン１２５Ｔとの間に、冷媒を吸入し圧縮して吐出する第２シリンダ室１３０Ｔが形成される。   As shown in FIG. 2, a circular first cylinder inner wall 123 </ b> S is formed in the first cylinder 121 </ b> S concentrically with the rotating shaft 15 of the motor 11. A first annular piston 125S having an outer diameter smaller than the inner diameter of the first cylinder 121S is disposed in the first cylinder inner wall 123S, and the refrigerant is sucked between the first cylinder inner wall 123S and the first annular piston 125S. A first cylinder chamber 130S for compressing and discharging is formed. In the second cylinder 121T, a circular second cylinder inner wall 123T is formed concentrically with the rotating shaft 15 of the motor 11. A second annular piston 125T having an outer diameter smaller than the inner diameter of the second cylinder 121T is disposed in the second cylinder inner wall 123T, and the refrigerant is sucked between the second cylinder inner wall 123T and the second annular piston 125T. A second cylinder chamber 130T that discharges after compression is formed.

第１シリンダ１２１Ｓには、第１シリンダ内壁１２３Ｓから径方向に、シリンダ高さ全域に亘る第１ベーン溝１２８Ｓが形成され、第１ベーン溝１２８Ｓ内に、平板状の第１ベーン１２７Ｓが、摺動自在に嵌合されている。第２シリンダ１２１Ｔには、第２シリンダ内壁１２３Ｔから径方向に、シリンダ高さ全域に亘る第２ベーン溝１２８Ｔが形成され、第２ベーン溝１２８Ｔ内に、平板状の第２ベーン１２７Ｔが、摺動自在に嵌合されている。   The first cylinder 121S is formed with a first vane groove 128S extending in the radial direction from the first cylinder inner wall 123S over the entire cylinder height. A flat plate-like first vane 127S is slid in the first vane groove 128S. It is movably fitted. The second cylinder 121T is formed with a second vane groove 128T extending in the radial direction from the second cylinder inner wall 123T over the entire cylinder height, and a flat plate-like second vane 127T is slid in the second vane groove 128T. It is movably fitted.

図２に示すように、第１ベーン溝１２８Ｓの径方向外側には、第１側方張出部１２２Ｓの外周部から第１ベーン溝１２８Ｓに連通するように第１スプリング穴１２４Ｓが形成されている。第１スプリング穴１２４Ｓには、第１ベーン１２７Ｓの背面を押圧する第１ベーンスプリング１２６Ｓ（図１参照）が挿入されている。第２ベーン溝１２８Ｔの径方向外側には、第２側方張出部１２２Ｔの外周部から第２ベーン溝１２８Ｔに連通するように第２スプリング穴１２４Ｔが形成されている。第２スプリング穴１２４Ｔには、第２ベーン１２７Ｔの背面を押圧する第２ベーンスプリング１２６Ｔ（図１参照）が挿入されている。   As shown in FIG. 2, a first spring hole 124S is formed on the outer side in the radial direction of the first vane groove 128S so as to communicate with the first vane groove 128S from the outer peripheral portion of the first laterally extending portion 122S. Yes. A first vane spring 126S (see FIG. 1) that presses the back surface of the first vane 127S is inserted into the first spring hole 124S. A second spring hole 124T is formed on the radially outer side of the second vane groove 128T so as to communicate with the second vane groove 128T from the outer peripheral portion of the second laterally extending portion 122T. A second vane spring 126T (see FIG. 1) that presses the back surface of the second vane 127T is inserted into the second spring hole 124T.

ロータリ圧縮機１の起動時は、この第１ベーンスプリング１２６Ｓの反発力により、第１ベーン１２７Ｓが、第１ベーン溝１２８Ｓ内から第１シリンダ室１３０Ｓ内に突出し、その先端が、第１環状ピストン１２５Ｓの外周面に当接し、第１ベーン１２７Ｓにより、第１シリンダ室１３０Ｓが、第１吸入室１３１Ｓと、第１圧縮室１３３Ｓとに区画される。また、同様に、第２ベーンスプリング１２６Ｔの反発力により、第２ベーン１２７Ｔが、第２ベーン溝１２８Ｔ内から第２シリンダ室１３０Ｔ内に突出し、その先端が、第２環状ピストン１２５Ｔの外周面に当接し、第２ベーン１２７Ｔにより、第２シリンダ室１３０Ｔが、第２吸入室１３１Ｔと、第２圧縮室１３３Ｔとに区画される。   When the rotary compressor 1 is started, the first vane 127S protrudes from the first vane groove 128S into the first cylinder chamber 130S by the repulsive force of the first vane spring 126S, and the tip thereof is the first annular piston. The first cylinder chamber 130S is partitioned into a first suction chamber 131S and a first compression chamber 133S by the first vane 127S in contact with the outer peripheral surface of 125S. Similarly, due to the repulsive force of the second vane spring 126T, the second vane 127T protrudes from the second vane groove 128T into the second cylinder chamber 130T, and the tip of the second vane 127T extends to the outer peripheral surface of the second annular piston 125T. The second cylinder chamber 130T is partitioned into a second suction chamber 131T and a second compression chamber 133T by the second vane 127T.

また、第１シリンダ１２１Ｓには、第１ベーン溝１２８Ｓの径方向外側と圧縮機筐体１０内とを開口部Ｒ（図１参照）で連通して圧縮機筐体１０内の圧縮された冷媒を導入し、第１ベーン１２７Ｓに冷媒の圧力により背圧をかける第１圧力導入路１２９Ｓが形成されている。なお、圧縮機筐体１０内の圧縮された冷媒は、第１スプリング穴１２４Ｓからも導入される。また、第２シリンダ１２１Ｔには、第２ベーン溝１２８Ｔの径方向外側と圧縮機筐体１０内とを開口部Ｒ（図１参照）で連通して圧縮機筐体１０内の圧縮された冷媒を導入し、第２ベーン１２７Ｔに冷媒の圧力により背圧をかける第２圧力導入路１２９Ｔが形成されている。なお、圧縮機筐体１０内の圧縮された冷媒は、第２スプリング穴１２４Ｔからも導入される。   In addition, the first cylinder 121S communicates the radially outer side of the first vane groove 128S with the inside of the compressor casing 10 through the opening R (see FIG. 1), and the compressed refrigerant in the compressor casing 10 is compressed. And a first pressure introduction path 129S is formed in which back pressure is applied to the first vane 127S by the refrigerant pressure. The compressed refrigerant in the compressor housing 10 is also introduced from the first spring hole 124S. In addition, the second cylinder 121T communicates the radially outer side of the second vane groove 128T with the inside of the compressor casing 10 through an opening R (see FIG. 1), and the compressed refrigerant in the compressor casing 10 is compressed. , And a second pressure introduction path 129T is formed in which back pressure is applied to the second vane 127T by the refrigerant pressure. The compressed refrigerant in the compressor housing 10 is also introduced from the second spring hole 124T.

第１シリンダ１２１Ｓの第１側方張出部１２２Ｓには、第１吸入室１３１Ｓに外部から冷媒を吸入するために、第１吸入室１３１Ｓと外部とを連通させる第１吸入孔１３５Ｓが設けられている。第２シリンダ１２１Ｔの第２側方張出部１２２Ｔには、第２吸入室１３１Ｔに外部から冷媒を吸入するために、第２吸入室１３１Ｔと外部とを連通させる第２吸入孔１３５Ｔが設けられている。第１吸入孔１３５Ｓ及び第２吸入孔１３５Ｔの断面は円形である。   The first side overhanging portion 122S of the first cylinder 121S is provided with a first suction hole 135S that allows the first suction chamber 131S to communicate with the outside in order to suck the refrigerant from the outside into the first suction chamber 131S. ing. The second side overhanging portion 122T of the second cylinder 121T is provided with a second suction hole 135T that allows the second suction chamber 131T to communicate with the outside in order to suck the refrigerant from the outside into the second suction chamber 131T. ing. The cross section of the first suction hole 135S and the second suction hole 135T is circular.

また、図１に示すように、第１シリンダ１２１Ｓと第２シリンダ１２１Ｔの間には、中間仕切板１４０が配置され、第１シリンダ１２１Ｓの第１シリンダ室１３０Ｓ（図２参照）と第２シリンダ１２１Ｔの第２シリンダ室１３０Ｔ（図２参照）とを仕切っている。中間仕切板１４０は、第１シリンダ１２１Ｓの上端部と第２シリンダ１２１Ｔの下端部を閉塞している。   Further, as shown in FIG. 1, an intermediate partition plate 140 is disposed between the first cylinder 121S and the second cylinder 121T, and the first cylinder chamber 130S (see FIG. 2) of the first cylinder 121S and the second cylinder. The second cylinder chamber 130T (see FIG. 2) of 121T is partitioned. The intermediate partition plate 140 closes the upper end portion of the first cylinder 121S and the lower end portion of the second cylinder 121T.

第１シリンダ１２１Ｓの下端部には、下端板１６０Ｓが配置され、第１シリンダ１２１Ｓの第１シリンダ室１３０Ｓを閉塞している。また、第２シリンダ１２１Ｔの上端部には、上端板１６０Ｔが配置され、第２シリンダ１２１Ｔの第２シリンダ室１３０Ｔを閉塞している。下端板１６０Ｓは、第１シリンダ１２１Ｓの下端部を閉塞し、上端板１６０Ｔは、第２シリンダ１２１Ｔの上端部を閉塞している。   A lower end plate 160S is disposed at the lower end of the first cylinder 121S and closes the first cylinder chamber 130S of the first cylinder 121S. An upper end plate 160T is disposed at the upper end of the second cylinder 121T, and closes the second cylinder chamber 130T of the second cylinder 121T. The lower end plate 160S closes the lower end portion of the first cylinder 121S, and the upper end plate 160T closes the upper end portion of the second cylinder 121T.

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

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

回転軸１５が回転すると、第１環状ピストン１２５Ｓが、第１シリンダ内壁１２３Ｓに沿って第１シリンダ１２１Ｓ内を図２の時計回りに公転し、これに追随して第１ベーン１２７Ｓが往復運動する。この第１環状ピストン１２５Ｓ及び第１ベーン１２７Ｓの運動により、第１吸入室１３１Ｓ及び第１圧縮室１３３Ｓ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。また、回転軸１５が回転すると、第２環状ピストン１２５Ｔが、第２シリンダ内壁１２３Ｔに沿って第２シリンダ１２１Ｔ内を図２の時計回りに公転し、これに追随して第２ベーン１２７Ｔが往復運動する。この第２環状ピストン１２５Ｔ及び第２ベーン１２７Ｔの運動により、第２吸入室１３１Ｔ及び第２圧縮室１３３Ｔ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 first annular piston 125S revolves in the first cylinder 121S in the clockwise direction in FIG. 2 along the first cylinder inner wall 123S, and the first vane 127S reciprocates following this. . Due to the movement of the first annular piston 125S and the first vane 127S, the volumes of the first suction chamber 131S and the first compression chamber 133S continuously change, and the compression unit 12 continuously sucks and compresses the refrigerant. Discharge. When the rotary shaft 15 rotates, the second annular piston 125T revolves in the second cylinder 121T in the clockwise direction of FIG. 2 along the second cylinder inner wall 123T, and the second vane 127T reciprocates following this. Exercise. By the movement of the second annular piston 125T and the second vane 127T, the volumes of the second suction chamber 131T and the second compression chamber 133T are continuously changed, and the compression unit 12 continuously sucks and compresses the refrigerant. Discharge.

図１に示すように、下端板１６０Ｓの下側には、下端板カバー１７０Ｓが配置され、下端板１６０Ｓとの間に下マフラー室１８０Ｓを形成している。そして、第１の圧縮部１２Ｓは、下マフラー室１８０Ｓに開口している。すなわち、下端板１６０Ｓの第１ベーン１２７Ｓ近傍には、第１シリンダ１２１Ｓの第１圧縮室１３３Ｓと下マフラー室１８０Ｓとを連通する第１吐出孔１９０Ｓ（図２参照）が設けられ、第１吐出孔１９０Ｓには、圧縮された冷媒の逆流を防止する図示しないリード弁型の第１吐出弁が配置されている。   As shown in FIG. 1, a lower end plate cover 170S is disposed below the lower end plate 160S, and a lower muffler chamber 180S is formed between the lower end plate 160S and the lower end plate cover 170S. And the 1st compression part 12S is opened to lower muffler room 180S. That is, a first discharge hole 190S (see FIG. 2) that connects the first compression chamber 133S of the first cylinder 121S and the lower muffler chamber 180S is provided in the vicinity of the first vane 127S of the lower end plate 160S. A reed valve type first discharge valve (not shown) that prevents the backflow of the compressed refrigerant is disposed in the hole 190S.

下マフラー室１８０Ｓは、環状に形成された１つの室であり、第１の圧縮部１２Ｓの吐出側を、下端板１６０Ｓ、第１シリンダ１２１Ｓ、中間仕切板１４０、第２シリンダ１２１Ｔ及び上端板１６０Ｔを貫通する冷媒通路１３６（図２参照）を通して上マフラー室１８０Ｔ内に連通させる連通路の一部である。下マフラー室１８０Ｓは、吐出冷媒の圧力脈動を低減させる。また、第１吐出弁に重ねて、第１吐出弁の撓み開弁量を制限するための図示しない第１吐出弁押さえが、第１吐出弁とともにリベットにより固定されている。第１吐出孔１９０Ｓ、第１吐出弁及び第１吐出弁押さえは、下端板１６０Ｓの第１吐出弁部を構成している。   The lower muffler chamber 180S is one chamber formed in an annular shape, and the lower end plate 160S, the first cylinder 121S, the intermediate partition plate 140, the second cylinder 121T, and the upper end plate 160T are arranged on the discharge side of the first compression unit 12S. This is a part of the communication passage that communicates with the upper muffler chamber 180T through the refrigerant passage 136 (see FIG. 2) that passes through the upper muffler chamber. The lower muffler chamber 180S reduces the pressure pulsation of the discharged refrigerant. In addition, a first discharge valve presser (not shown) for limiting the amount of deflection opening of the first discharge valve is fixed to the first discharge valve by a rivet together with the first discharge valve. The first discharge hole 190S, the first discharge valve, and the first discharge valve presser constitute a first discharge valve portion of the lower end plate 160S.

図１に示すように、上端板１６０Ｔの上側には、上端板カバー１７０Ｔが配置され、上端板１６０Ｔとの間に上マフラー室１８０Ｔを形成している。上端板１６０Ｔの第２ベーン１２７Ｔ近傍には、第２シリンダ１２１Ｔの第２圧縮室１３３Ｔと上マフラー室１８０Ｔとを連通する第２吐出孔１９０Ｔ（図２参照）が設けられ、第２吐出孔１９０Ｔには、圧縮された冷媒の逆流を防止する図示しないリード弁型の第２吐出弁が配置されている。また、第２吐出弁に重ねて、第２吐出弁の撓み開弁量を制限するための図示しない第２吐出弁押さえが、第２吐出弁とともにリベットにより固定されている。上マフラー室１８０Ｔは、吐出冷媒の圧力脈動を低減させる。第２吐出孔１９０Ｔ、第２吐出弁及び第２吐出弁押さえは、上端板１６０Ｔの第２吐出弁部を構成している。   As shown in FIG. 1, an upper end plate cover 170T is arranged above the upper end plate 160T, and an upper muffler chamber 180T is formed between the upper end plate 160T and the upper end plate cover 170T. In the vicinity of the second vane 127T of the upper end plate 160T, a second discharge hole 190T (see FIG. 2) that communicates the second compression chamber 133T of the second cylinder 121T and the upper muffler chamber 180T is provided, and the second discharge hole 190T. Is provided with a reed valve type second discharge valve (not shown) for preventing the backflow of the compressed refrigerant. In addition, a second discharge valve presser (not shown) for limiting the amount of deflection opening of the second discharge valve is fixed to the second discharge valve by a rivet together with the second discharge valve. The upper muffler chamber 180T reduces the pressure pulsation of the discharged refrigerant. The second discharge hole 190T, the second discharge valve, and the second discharge valve presser constitute a second discharge valve portion of the upper end plate 160T.

下端板カバー１７０Ｓ、下端板１６０Ｓ、第１シリンダ１２１Ｓ及び中間仕切板１４０は、下側から挿通されて第２シリンダ１２１Ｔに設けられたメネジにネジ込まれた複数の通しボルト１７５により第２シリンダ１２１Ｔに締結される。上端板カバー１７０Ｔ及び上端板１６０Ｔは、上側から挿通されて第２シリンダ１２１Ｔに設けられたメネジにネジ込まれた通しボルト１７４により第２シリンダ１２１Ｔに締結される。複数の通しボルト１７４，１７５等により一体に締結された下端板カバー１７０Ｓ、下端板１６０Ｓ、第１シリンダ１２１Ｓ、中間仕切板１４０、第２シリンダ１２１Ｔ、上端板１６０Ｔ及び上端板カバー１７０Ｔは、圧縮部１２を構成している。圧縮部１２のうち、上端板１６０Ｔの外周部が、圧縮機筐体１０の胴部１０Ａにスポット溶接１６３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。上端板１６０Ｔと胴部１０Ａとの寸法関係については後述する。   The lower end plate cover 170S, the lower end plate 160S, the first cylinder 121S, and the intermediate partition plate 140 are inserted into the second cylinder 121T by a plurality of through bolts 175 that are inserted from below and screwed into female screws provided in the second cylinder 121T. To be concluded. The upper end plate cover 170T and the upper end plate 160T are fastened to the second cylinder 121T by through bolts 174 that are inserted from above and screwed into female screws provided in the second cylinder 121T. The lower end plate cover 170S, the lower end plate 160S, the first cylinder 121S, the intermediate partition plate 140, the second cylinder 121T, the upper end plate 160T, and the upper end plate cover 170T integrally fastened by a plurality of through bolts 174, 175, etc. 12 is constituted. The outer peripheral portion of the upper end plate 160 </ b> T is fixed to the body portion 10 </ b> A of the compressor housing 10 by spot welding 163, and the compression portion 12 is fixed to the compressor housing 10. The dimensional relationship between the upper end plate 160T and the trunk portion 10A will be described later.

冷媒回路の低圧冷媒は、図示しないアキュムレータ及び第１シリンダ１２１Ｓの第１吸入孔１３５Ｓ（図２参照）を介して第１の圧縮部１２Ｓに導かれる。また、冷媒回路の低圧冷媒は、図示しないアキュムレータ及び第２シリンダ１２１Ｔの第２吸入孔１３５Ｔ（図２参照）を介して第２の圧縮部１２Ｔに導かれる。すなわち、第１吸入孔１３５Ｓ及び第２吸入孔１３５Ｔは、冷媒回路の蒸発器に並列に接続されている。   The low-pressure refrigerant in the refrigerant circuit is guided to the first compression unit 12S via an accumulator (not shown) and the first suction hole 135S (see FIG. 2) of the first cylinder 121S. Further, the low-pressure refrigerant in the refrigerant circuit is guided to the second compression portion 12T through an accumulator (not shown) and the second suction hole 135T (see FIG. 2) of the second cylinder 121T. That is, the first suction hole 135S and the second suction hole 135T are connected in parallel to the evaporator of the refrigerant circuit.

圧縮機筐体１０の天部には、冷媒回路と接続し高圧冷媒を冷媒回路の凝縮器側に吐出する吐出部としての吐出管１０７が接続されている。すなわち、第１吐出孔１９０Ｓ及び第２吐出孔１９０Ｔは、冷媒回路の凝縮器に接続されている。   Connected to the top of the compressor housing 10 is a discharge pipe 107 that is connected to the refrigerant circuit and discharges high-pressure refrigerant to the condenser side of the refrigerant circuit. That is, the first discharge hole 190S and the second discharge hole 190T are connected to the condenser of the refrigerant circuit.

圧縮機筐体１０内には、およそ第２シリンダ１２１Ｔの高さまで潤滑油が封入されている。また、潤滑油は、回転軸１５の下部に挿入される図示しないポンプ羽根により、回転軸１５の下端部に取付けられた給油パイプ１６から吸上げられ、圧縮部１２を循環し、摺動部品（第１環状ピストン１２５Ｓ及び第２環状ピストン１２５Ｔ）の潤滑を行なうとともに、圧縮部１２の微小隙間のシールをする。   Lubricating oil is sealed in the compressor housing 10 up to the height of the second cylinder 121T. The lubricating oil is sucked up from an oil supply pipe 16 attached to the lower end of the rotating shaft 15 by a pump blade (not shown) inserted into the lower portion of the rotating shaft 15, circulates through the compressing portion 12, and slides ( The first annular piston 125S and the second annular piston 125T) are lubricated and a minute gap in the compression portion 12 is sealed.

次に、図３〜図８を参照して実施例のロータリ圧縮機１の特徴的な構成について説明する。図３は、実施例のロータリ圧縮機のステータとロータの組立前を示す縦断面図である。図４は、実施例のロータリ圧縮機のステータとロータの組立後を示す縦断面図である。図５は、実施例のロータリ圧縮機の圧縮部及びステータと圧縮機筐体の胴部の嵌合前を示す縦断面図である。図６は、実施例のロータリ圧縮機の圧縮部及びステータと圧縮機筐体の胴部の嵌合後を示す縦断面図である。図７は、図６のＡ−Ａ線に沿う横断面図である。図８は、図６のＢ−Ｂ線に沿う横断面図である。   Next, a characteristic configuration of the rotary compressor 1 according to the embodiment will be described with reference to FIGS. FIG. 3 is a longitudinal sectional view showing the stator and the rotor before assembly of the rotary compressor of the embodiment. FIG. 4 is a longitudinal sectional view showing a state after assembly of the stator and the rotor of the rotary compressor of the embodiment. FIG. 5 is a longitudinal cross-sectional view showing a state before the compression portion of the rotary compressor and the stator and the body portion of the compressor housing of the embodiment are fitted. FIG. 6 is a longitudinal cross-sectional view showing the compression portion of the rotary compressor and the stator after the fitting of the body portion of the compressor housing of the embodiment. FIG. 7 is a cross-sectional view taken along line AA in FIG. FIG. 8 is a cross-sectional view taken along line BB in FIG.

図３に示すように、モータ１１のロータ１１２の外径φＤｒは、ステータ１１１の内径φＤｔよりも１．４ｍｍ小さく形成されていて、ロータ１１２の外周面とステータ１１１の内周面との間の隙間は０．７ｍｍとなっている。ロータ１１２とステータ１１１とを芯出しするギャップゲージ２００のシム２０１の厚さは、ロータ１１２の外周面とステータ１１１の内周面との間の隙間０．７ｍｍより０．１ｍｍ薄く、０．６ｍｍとなっている。   As shown in FIG. 3, the outer diameter φDr of the rotor 112 of the motor 11 is 1.4 mm smaller than the inner diameter φDt of the stator 111, and is between the outer peripheral surface of the rotor 112 and the inner peripheral surface of the stator 111. The gap is 0.7 mm. The thickness of the shim 201 of the gap gauge 200 that centers the rotor 112 and the stator 111 is 0.1 mm thinner than the gap 0.7 mm between the outer peripheral surface of the rotor 112 and the inner peripheral surface of the stator 111, and is 0.6 mm. It has become.

図５に示すように、モータ１１のステータ１１１の外径φＤｓは、圧縮部１２の上端板１６０Ｔの外径φＤｂよりも小さく形成されている（φＤｓ＜φＤｂ）。また、圧縮機筐体１０の胴部１０Ａの内径φＤｍは、ステータ１１１の外径φＤｓよりも０．１ｍｍ〜０．２ｍｍ大きく形成されている（０．１ｍｍ≦φＤｍ−φＤｓ≦０．２ｍｍ）。また、胴部１０Ａの内径φＤｍは、上端板１６０Ｔの外径φＤｂに対して−０．０５ｍｍ〜＋０．０５ｍｍの範囲に形成されている（−０．０５ｍｍ≦φＤｍ−φＤｂ≦０．０５ｍｍ）。図７及び図８に示すように、胴部１０Ａは、鋼板を巻いて端部同士を突合せ溶接により溶接して円筒形に形成したものであり、内径φＤｍの寸法精度及び真円度は、深絞り加工や機械加工されたものに比べて低い（図７及び図８に突合せ溶接部位１６５を示す）。   As shown in FIG. 5, the outer diameter φDs of the stator 111 of the motor 11 is formed smaller than the outer diameter φDb of the upper end plate 160T of the compression portion 12 (φDs <φDb). Further, the inner diameter φDm of the body portion 10A of the compressor housing 10 is formed to be 0.1 mm to 0.2 mm larger than the outer diameter φDs of the stator 111 (0.1 mm ≦ φDm−φDs ≦ 0.2 mm). Further, the inner diameter φDm of the body portion 10A is formed in a range of −0.05 mm to +0.05 mm with respect to the outer diameter φDb of the upper end plate 160T (−0.05 mm ≦ φDm−φDb ≦ 0.05 mm). As shown in FIGS. 7 and 8, the body portion 10A is formed by winding a steel plate and welding the end portions by butt welding to form a cylindrical shape. The dimensional accuracy and roundness of the inner diameter φDm are as follows. It is lower than that which has been drawn or machined (a butt weld site 165 is shown in FIGS. 7 and 8).

次に、圧縮機筐体１０の胴部１０Ａ内に、回転軸１５により接続されたモータ１１及び圧縮部１２を固定する方法を説明する。図３及び図４に示すように、モータ１１を組立てるときは、底部に円形の凹部２１１を有する円筒形の組立治具２１０の上端部にステータ１１１を載置し、ステータ１１１の上部には、外周部に複数のシム２０１が取付けられたギャップゲージ２００をセットする。   Next, a method for fixing the motor 11 and the compression unit 12 connected by the rotary shaft 15 in the body 10A of the compressor housing 10 will be described. As shown in FIGS. 3 and 4, when assembling the motor 11, the stator 111 is placed on the upper end of a cylindrical assembly jig 210 having a circular recess 211 at the bottom. A gap gauge 200 having a plurality of shims 201 attached to the outer periphery is set.

回転軸１５にロータ１１２が固定された圧縮部１２を、ロータ１１２を下側にして下降させ、回転軸１５の端部をギャップゲージ２００の上側凸部２０２に当接させる。圧縮部１２をさらに下降させると、ロータ１１２は、ギャップゲージ２００のシム２０１にガイドされてステータ１１１内に挿入され、ギャップゲージ２００を下方に押し込む。図４に示すように、ギャップゲージ２００の下側凸部２０３が組立治具２１０の凹部２１１に嵌合すると、ロータ１１２がステータ１１１内に完全に挿入されてシム２０１により芯出しされ、モータ１１が組立てられる。   The compression part 12 having the rotor 112 fixed to the rotating shaft 15 is lowered with the rotor 112 facing downward, and the end of the rotating shaft 15 is brought into contact with the upper convex part 202 of the gap gauge 200. When the compression unit 12 is further lowered, the rotor 112 is guided by the shim 201 of the gap gauge 200 and inserted into the stator 111, and pushes the gap gauge 200 downward. As shown in FIG. 4, when the lower convex portion 203 of the gap gauge 200 is fitted into the concave portion 211 of the assembly jig 210, the rotor 112 is completely inserted into the stator 111 and centered by the shim 201. Are assembled.

次に、図５及び図６に示すように、組立治具２１０上にモータ１１及び圧縮部１２が載置された状態で、圧縮機筐体１０の胴部１０Ａを圧縮部１２の上端板１６０Ｔ及びモータ１１のステータ１１１に嵌合する。胴部１０Ａの内径φＤｍは、上端板１６０Ｔの外径φＤｂに対して−０．０５ｍｍ〜０．０５ｍｍとなっているので、胴部１０Ａと上端板１６０Ｔとの嵌合は、一般的な圧入や焼嵌めに比べて軽い圧入か軽い焼嵌めとする。胴部１０Ａの内径φＤｍは、ステータ１１１の外径φＤｓよりも０．１ｍｍ〜０．２ｍｍ大きく形成されているので、胴部１０Ａとステータ１１１との嵌合は、非接触か又は圧縮力がかからない片側接触で行うことができる。図６に示すように、胴部１０Ａを、下端が組立治具２１０の段部２１２に当接するまで下降させ、嵌合作業を終了する。この状態で、胴部１０Ａの内周部とステータ１１１の外周部との間には、０．０５ｍｍ〜０．１０ｍｍの隙間が形成され、かつ、ステータ１１１とロータ１１２とは芯出しされた状態にある。   Next, as shown in FIGS. 5 and 6, with the motor 11 and the compression unit 12 placed on the assembly jig 210, the body 10 </ b> A of the compressor housing 10 is moved to the upper end plate 160 </ b> T of the compression unit 12. And fitted to the stator 111 of the motor 11. Since the inner diameter φDm of the trunk portion 10A is −0.05 mm to 0.05 mm with respect to the outer diameter φDb of the upper end plate 160T, fitting between the trunk portion 10A and the upper end plate 160T can be performed by general press-fitting or Compared with shrink fitting, it should be light press-fit or light shrink fitting. Since the inner diameter φDm of the trunk portion 10A is formed to be 0.1 mm to 0.2 mm larger than the outer diameter φDs of the stator 111, the fitting between the trunk portion 10A and the stator 111 is non-contact or does not require a compressive force. Can be done with one side contact. As shown in FIG. 6, the body portion 10 </ b> A is lowered until the lower end comes into contact with the step portion 212 of the assembly jig 210, and the fitting operation is completed. In this state, a gap of 0.05 mm to 0.10 mm is formed between the inner peripheral portion of the body portion 10A and the outer peripheral portion of the stator 111, and the stator 111 and the rotor 112 are centered. It is in.

次に、図６〜図８を参照して、圧縮機筐体１０の胴部１０Ａに対する圧縮部１２の上端板１６０Ｔ及びモータ１１のステータ１１１の固定方法を説明する。胴部１０Ａには、上端板１６０Ｔが嵌合された位置、及びステータ１１１の圧縮部１２側位置と反圧縮部１２側位置に、周方向に互いに１２０°離間して三つの孔１６４が夫々設けられている（孔１６４は三つ以上としてもよい）。この孔１６４に溶接ワイヤを挿入し、スポット溶接により、胴部１０Ａと上端板１６０Ｔを先に溶接し、次に、胴部１０Ａとステータ１１１の圧縮部１２側位置及び反圧縮部１２側位置を溶接する。圧縮部１２側位置の溶接と反圧縮部１２側位置の溶接は、どちらを先に行ってもよい。図６にスポット溶接部位１６３を示す（孔１６４はスポット溶接により完全に埋められ、圧縮された冷媒の圧力に耐える）。その後、ギャップゲージ２００を取り外す。   Next, a method of fixing the upper end plate 160T of the compression unit 12 and the stator 111 of the motor 11 to the body 10A of the compressor housing 10 will be described with reference to FIGS. The body portion 10A is provided with three holes 164 spaced from each other by 120 ° in the circumferential direction at the position where the upper end plate 160T is fitted and at the compression portion 12 side position and the anti-compression portion 12 side position of the stator 111. (The number of holes 164 may be three or more). A welding wire is inserted into the hole 164, and the barrel portion 10A and the upper end plate 160T are welded first by spot welding. Next, the position of the barrel portion 10A and the stator 111 on the compression portion 12 side and the position on the anti-compression portion 12 side are determined. Weld. Either the compression part 12 side position welding or the anti-compression part 12 side position welding may be performed first. FIG. 6 shows a spot weld site 163 (the hole 164 is completely filled by spot welding to withstand the pressure of the compressed refrigerant). Thereafter, the gap gauge 200 is removed.

胴部１０Ａと上端板１６０Ｔを先に溶接して圧縮部１２及びギャップゲージ２００により芯出しされたモータ１１を胴部１０Ａ内で位置決め固定し、次に、芯出しされた状態で、かつ、胴部１０Ａから径方向の圧縮力を受けない状態で、ステータ１１１を胴部１０Ａに直接溶接するので、ステータ１１１に圧縮歪みが生じることがなく、ステータの磁化特性が劣化して鉄損が増加することもなく、モータ１１の効率が高く、コストアップを抑えることができる。   The body 11A and the upper end plate 160T are first welded, and the motor 11 centered by the compression unit 12 and the gap gauge 200 is positioned and fixed in the body 10A. Next, in the centered state, the body 11 Since the stator 111 is directly welded to the body portion 10A without receiving the radial compressive force from the portion 10A, the stator 111 is not subjected to compressive strain, the magnetization characteristics of the stator are deteriorated, and the iron loss is increased. In addition, the efficiency of the motor 11 is high, and the cost increase can be suppressed.

また、ステータ１１１の圧縮部１２側位置と反圧縮部１２側位置を胴部１０Ａにスポット溶接して固定するので、ロータリ圧縮機１が落下などの衝撃を受けても、積層した鋼板をカシメて形成したステータ１１１の、圧縮部１２側溶接位置と反圧縮部１２側溶接位置との間のカシメが外れてステータ１１１が破損することはない。なお、図８に示すように、上端板１６０Ｔのスポット溶接部位１６３の周方向位置、ステータ１１１の圧縮部１２側のスポット溶接部位１６３の周方向位置、及び、ステータ１１１の反圧縮部１２側のスポット溶接部位１６３の周方向位置を、夫々周方向に位相をずらすようにすれば、溶接部位が軸方向に一直線上に並ばないので、比較的に強度が弱い溶接部位間の距離が長くなり、胴部１０Ａの強度が弱くならない。また、胴部１０Ａの内周部とステータ１１１の外周部との間の最大隙間は、０．１０ｍｍであるので、溶接によるスパッタが圧縮機筐体１０内に侵入することはない。   Further, since the compression portion 12 side position and the anti-compression portion 12 side position of the stator 111 are fixed by spot welding to the body portion 10A, even if the rotary compressor 1 receives an impact such as dropping, the laminated steel plates should be caulked. The formed stator 111 is not caulked between the welding position on the compression part 12 side and the welding position on the anti-compression part 12 side and the stator 111 is not damaged. In addition, as shown in FIG. 8, the circumferential position of the spot welded part 163 of the upper end plate 160T, the circumferential position of the spot welded part 163 on the compression part 12 side of the stator 111, and the anti-compression part 12 side of the stator 111 If the circumferential position of the spot welded part 163 is shifted in the circumferential direction, the welded parts do not line up in a straight line in the axial direction, so the distance between welded parts with relatively low strength increases. The strength of the trunk portion 10A does not become weak. Further, since the maximum gap between the inner peripheral portion of the body portion 10A and the outer peripheral portion of the stator 111 is 0.10 mm, spatter due to welding does not enter the compressor housing 10.

胴部１０Ａに圧縮部１２及びモータ１１を溶接固定した後、図１に示すように、胴部１０Ａに底部１０Ｃ及び天部１０Ｂを全周溶接すれば、ロータリ圧縮機１の組立が完了する。なお、本発明は、単シリンダ式ロータリ圧縮機及び２段圧縮式ロータリ圧縮機に適用することができる。   After the compression portion 12 and the motor 11 are welded and fixed to the barrel portion 10A, as shown in FIG. 1, the assembly of the rotary compressor 1 is completed by welding the bottom portion 10C and the top portion 10B to the barrel portion 10A. The present invention can be applied to a single cylinder type rotary compressor and a two-stage compression type rotary compressor.

以上、実施例を説明したが、前述した内容により実施例が限定されるものではない。また、前述した構成要素には、当業者が容易に想定できるもの、実質的に同一のもの、いわゆる均等の範囲のものが含まれる。さらに、前述した構成要素は適宜組み合わせることが可能である。さらに、実施例の要旨を逸脱しない範囲で構成要素の種々の省略、置換及び変更のうち少なくとも１つを行うことができる。   Although the embodiments have been described above, the embodiments are not limited to the above-described contents. In addition, the above-described constituent elements include those that can be easily assumed by those skilled in the art, those that are substantially the same, and those in a so-called equivalent range. Furthermore, the above-described components can be appropriately combined. Furthermore, at least one of various omissions, substitutions, and changes of the components can be made without departing from the scope of the embodiments.

１ ロータリ圧縮機
１０ 圧縮機筐体
１０Ａ 胴部
１０Ｂ 天部
１０Ｃ 底部
１１ モータ
１２ 圧縮部
１５ 回転軸
１６ 給油パイプ
１０７ 吐出管（吐出部）
１１１ ステータ
１１２ ロータ
１２Ｓ 第１の圧縮部（圧縮部）
１２Ｔ 第２の圧縮部（圧縮部）
１２１Ｓ 第１シリンダ（シリンダ）
１２１Ｔ 第２シリンダ（シリンダ）
１２２Ｓ 第１側方張出部（側方張出部）
１２２Ｔ 第２側方張出部（側方張出部）
１２３Ｓ 第１シリンダ内壁（シリンダ内壁）
１２３Ｔ 第２シリンダ内壁（シリンダ内壁）
１２４Ｓ 第１スプリング穴（スプリング穴）
１２４Ｔ 第２スプリング穴（スプリング穴）
１２５Ｓ 第１環状ピストン（環状ピストン）
１２５Ｔ 第２環状ピストン（環状ピストン）
１２６Ｓ 第１ベーンスプリング（ベーンスプリング）
１２６Ｔ 第２ベーンスプリング（ベーンスプリング）
１２７Ｓ 第１ベーン（ベーン）
１２７Ｔ 第２ベーン（ベーン）
１２８Ｓ 第１ベーン溝（ベーン溝）
１２８Ｔ 第２ベーン溝（ベーン溝）
１２９Ｓ 第１圧力導入路（圧力導入路）
１２９Ｔ 第２圧力導入路（圧力導入路）
１３０Ｓ 第１シリンダ室（シリンダ室）
１３０Ｔ 第２シリンダ室（シリンダ室）
１３１Ｓ 第１吸入室（吸入室）
１３１Ｔ 第２吸入室（吸入室）
１３３Ｓ 第１圧縮室（圧縮室）
１３３Ｔ 第２圧縮室（圧縮室）
１３５Ｓ 第１吸入孔（吸入孔）
１３５Ｔ 第２吸入孔（吸入孔）
１３６ 冷媒通路
１４０ 中間仕切板
１５１ 副軸部
１５２Ｓ 第１偏心部（偏心部）
１５２Ｔ 第２偏心部（偏心部）
１５３ 主軸部
１６０Ｓ 下端板（端板）
１６０Ｔ 上端板（端板）
１６１Ｓ 副軸受部（軸受部）
１６１Ｔ 主軸受部（軸受部）
１６３ スポット溶接部位
１６４ 孔
１６５ 突合せ溶接部位
１７０Ｓ 下端板カバー
１７０Ｔ 上端板カバー
１７４ 通しボルト
１７５ 通しボルト
１８０Ｓ 下マフラー室
１８０Ｔ 上マフラー室
１９０Ｓ 第１吐出孔（吐出弁部）
１９０Ｔ 第２吐出孔（吐出弁部）
２００ ギャップゲージ
２０１ シム
２０２ 上側凸部
２０３ 下側凸部
２１０ 組立治具
２１１ 凹部
２１２ 段部 DESCRIPTION OF SYMBOLS 1 Rotary compressor 10 Compressor housing | casing 10A Body part 10B Top part 10C Bottom part 11 Motor 12 Compression part 15 Rotating shaft 16 Oil supply pipe 107 Discharge pipe (discharge part)
111 Stator 112 Rotor 12S 1st compression part (compression part)
12T 2nd compression part (compression part)
121S 1st cylinder (cylinder)
121T 2nd cylinder (cylinder)
122S first lateral overhang (side overhang)
122T Second lateral overhang (side overhang)
123S 1st cylinder inner wall (cylinder inner wall)
123T 2nd cylinder inner wall (cylinder inner wall)
124S 1st spring hole (spring hole)
124T Second spring hole (spring hole)
125S first annular piston (annular piston)
125T second annular piston (annular piston)
126S 1st vane spring (vane spring)
126T 2nd vane spring (vane spring)
127S 1st vane (vane)
127T 2nd vane (vane)
128S 1st vane groove (vane groove)
128T 2nd vane groove (vane groove)
129S First pressure introduction path (pressure introduction path)
129T Second pressure introduction path (pressure introduction path)
130S 1st cylinder chamber (cylinder chamber)
130T Second cylinder chamber (cylinder chamber)
131S First suction chamber (suction chamber)
131T Second suction chamber (suction chamber)
133S 1st compression chamber (compression chamber)
133T Second compression chamber (compression chamber)
135S 1st suction hole (suction hole)
135T 2nd suction hole (suction hole)
136 Refrigerant passage 140 Intermediate partition plate 151 Secondary shaft portion 152S First eccentric portion (eccentric portion)
152T second eccentric part (eccentric part)
153 Main shaft portion 160S Lower end plate (end plate)
160T Top plate (end plate)
161S Sub bearing part (bearing part)
161T Main bearing (bearing)
163 Spot welding part 164 hole 165 Butt welding part 170S Lower end plate cover 170T Upper end plate cover 174 Through bolt 175 Through bolt 180S Lower muffler chamber 180T Upper muffler chamber 190S First discharge hole (discharge valve part)
190T 2nd discharge hole (discharge valve part)
200 Gap gauge 201 Shim 202 Upper convex part 203 Lower convex part 210 Assembly jig 211 Concave part 212 Step part

Claims (3)

上部に冷媒の吐出部が設けられ、下部に冷媒の吸入部が設けられると共に潤滑油が貯留される密閉された縦置きの圧縮機筐体と、
該圧縮機筐体内に配置され、環状のシリンダと該シリンダの端部を閉塞する上端板及び下端板とを有し、前記吸入部から吸入した冷媒を前記シリンダで圧縮して前記吐出部から吐出する圧縮部と、
前記圧縮機筐体内に配置され、円筒状のステータと回転軸に固定され前記ステータ内で回転するロータとを有し、前記回転軸を介して前記圧縮部を駆動するモータと、
を備えるロータリ圧縮機において、
前記圧縮機筐体の胴部の内径をφＤｍ、前記圧縮部の上端板の外径をφＤｂ、前記モータのステータの外径をφＤｓとするとき、−０．０５ｍｍ≦φＤｍ−φＤｂ≦０．０５ｍｍ、及び、０．１ｍｍ≦φＤｍ−φＤｓ≦０．２ｍｍの二つの式を満たすように、前記φＤｍ、φＤｂ及びφＤｓを設定するとともに、前記上端板の外周部及び前記ステータの外周部の夫々の周方向に離間した複数箇所を前記圧縮機筐体の胴部にスポット溶接したことを特徴とするロータリ圧縮機。 A hermetic vertical compressor housing in which a refrigerant discharge part is provided at the upper part, a refrigerant suction part is provided in the lower part and lubricating oil is stored;
An annular cylinder and an upper end plate and a lower end plate that close the end of the cylinder are disposed in the compressor casing, and the refrigerant sucked from the suction portion is compressed by the cylinder and discharged from the discharge portion. A compression unit to perform,
A motor disposed in the compressor housing, having a cylindrical stator and a rotor fixed to a rotating shaft and rotating in the stator, and driving the compression unit via the rotating shaft;
A rotary compressor comprising:
When the inner diameter of the body of the compressor housing is φDm, the outer diameter of the upper end plate of the compressor is φDb, and the outer diameter of the stator of the motor is φDs, −0.05 mm ≦ φDm−φDb ≦ 0.05 mm And φDm, φDb, and φDs are set so as to satisfy the two expressions of 0.1 mm ≦ φDm−φDs ≦ 0.2 mm, and the outer periphery of the upper end plate and the outer periphery of the stator A rotary compressor characterized in that a plurality of locations separated in a direction are spot-welded to the body of the compressor casing. 前記モータのステータと前記圧縮機筐体の胴部とのスポット溶接は、前記圧縮部の上端板と前記胴部とのスポット溶接の後に行われることを特徴とする請求項１に記載のロータリ圧縮機。   2. The rotary compression according to claim 1, wherein spot welding of the stator of the motor and the body portion of the compressor housing is performed after spot welding of the upper end plate of the compression portion and the body portion. Machine. 前記モータのステータと前記圧縮機筐体の胴部とのスポット溶接は、該ステータと前記モータのロータが芯出しされた状態で行われることを特徴とする請求項２に記載のロータリ圧縮機。   3. The rotary compressor according to claim 2, wherein spot welding of the stator of the motor and the body portion of the compressor housing is performed in a state where the stator and the rotor of the motor are centered.
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