JP2003129981A - Rotary compressor - Google Patents
Rotary compressorInfo
- Publication number
- JP2003129981A JP2003129981A JP2001323769A JP2001323769A JP2003129981A JP 2003129981 A JP2003129981 A JP 2003129981A JP 2001323769 A JP2001323769 A JP 2001323769A JP 2001323769 A JP2001323769 A JP 2001323769A JP 2003129981 A JP2003129981 A JP 2003129981A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- rotary
- support member
- cylinder
- electric element
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- 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
- 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
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【0001】[0001]
【発明の属する技術分野】本発明は、密閉容器内に電動
要素と、この電動要素にて駆動される回転圧縮要素を設
けて成るロータリコンプレッサに関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary compressor including an electric element and a rotary compression element driven by the electric element in a closed container.
【0002】[0002]
【従来の技術】従来のこの種ロータリコンプレッサ、例
えば内部中間圧型多段(二段)圧縮式のロータリコンプ
レッサでは、第1の回転圧縮要素に冷媒ガスがシリンダ
(第1のシリンダ)の低圧室側に吸入され、ローラとベ
ーンの動作により圧縮されて中間圧となりシリンダの高
圧室側より吐出消音室を経て密閉容器内に吐出される。
そして、この密閉容器内の中間圧の冷媒ガスは第2の回
転圧縮要素のシリンダ(第2のシリンダ)の低圧室側に
吸入され、ローラとベーンの動作により2段目の圧縮が
行なわれて高温高圧の冷媒ガスとなり、高圧室側より吐
出消音室を経て放熱器に流入し、放熱した後、膨張弁で
絞られて蒸発器で吸熱し、第1の回転圧縮要素に吸入さ
れるサイクルを繰り返す。2. Description of the Related Art In a conventional rotary compressor of this kind, for example, an internal intermediate pressure type multi-stage (two-stage) compression type rotary compressor, refrigerant gas is introduced into a first rotary compression element on the low pressure chamber side of a cylinder (first cylinder). It is sucked and compressed by the operation of the roller and the vane to become an intermediate pressure, and is discharged from the high pressure chamber side of the cylinder through the discharge muffling chamber into the closed container.
Then, the intermediate pressure refrigerant gas in the closed container is sucked into the low pressure chamber side of the cylinder (second cylinder) of the second rotary compression element, and the second stage compression is performed by the operation of the roller and the vane. It becomes high-temperature and high-pressure refrigerant gas, flows from the high-pressure chamber side into the radiator through the discharge muffling chamber, radiates heat, is squeezed by the expansion valve, absorbs heat in the evaporator, and is sucked into the first rotary compression element. repeat.
【0003】係るロータリコンプレッサに、高低圧差の
大きい冷媒、例えば炭酸ガスの一例としての二酸化炭素
(CO2)を冷媒として用いた場合、吐出冷媒圧力は高
圧となる第2の回転圧縮要素で12MPaGに達し、一
方、低段側となる第1の回転圧縮要素で8MPaG(中
間圧)となる(第1の回転圧縮要素の吸込圧力は4MP
a)。When a refrigerant having a large difference in high pressure and low pressure, for example, carbon dioxide (CO 2 ) as an example of carbon dioxide gas is used as a refrigerant in the rotary compressor, the pressure of the discharged refrigerant becomes 12 MPaG in the second rotary compression element which becomes high pressure. On the other hand, the pressure becomes 8 MPaG (intermediate pressure) in the first rotary compression element on the low stage side (the suction pressure of the first rotary compression element is 4 MP).
a).
【0004】[0004]
【発明が解決しようとする課題】このようなロータリコ
ンプレッサのシリンダの開口面は、内部に吐出消音室を
構成する支持部材にて閉塞されるが、この支持部材中央
には電動要素の回転軸の軸受けも構成される。そして、
この軸受けと回転軸間に、給油が不十分な状況でも良好
な摺動性能を保持でき、高負荷時の高いPV値(単位面
積当たりに加わる荷重)に対しても高い耐摩耗性能を有
するカーボン製のブッシュを設ければ、ロータリコンプ
レッサの耐久性を著しく改善することができるが、係る
カーボン製のブッシュは高価であり、部品コストが高騰
してしまう欠点があった。The opening surface of the cylinder of such a rotary compressor is closed by a support member which constitutes a discharge muffling chamber, and the center of this support member is the rotary shaft of the electric element. Bearings are also configured. And
Carbon that can maintain good sliding performance between this bearing and the rotating shaft even in the case of insufficient lubrication and has high wear resistance against a high PV value (load applied per unit area) under high load. Although the durability of the rotary compressor can be remarkably improved by providing a bush made of carbon, the carbon bush is expensive and has a drawback that the cost of parts increases.
【0005】本発明は、係る従来技術の課題を解決する
ために成されたものであり、軸受けと回転軸間に設けら
れるカーボン製ブッシュに起因するコストの高騰を最小
限に抑えたロータリコンプレッサを提供することを目的
とする。The present invention has been made in order to solve the problems of the prior art, and provides a rotary compressor which minimizes the cost increase caused by the carbon bush provided between the bearing and the rotary shaft. The purpose is to provide.
【0006】[0006]
【課題を解決するための手段】即ち、請求項1の発明の
ロータリコンプレッサは、密閉容器内に電動要素と、こ
の電動要素にて駆動される回転圧縮要素を設けて成るも
のであって、回転圧縮要素を構成するための単一若しく
は複数のシリンダと、シリンダの電動要素とは反対側の
開口面を閉塞すると共に、電動要素の回転軸の軸受けを
有する第1の支持部材と、シリンダの電動要素側の開口
面を閉塞すると共に、回転軸の軸受けを有する第2の支
持部材とを備え、第1及び第2の支持部材のうちの何れ
か一方の軸受け内に、当該軸受けと回転軸との間に介在
するカーボン製ブッシュを設けたことを特徴とする。That is, a rotary compressor according to the invention of claim 1 comprises an electric element and a rotary compression element driven by the electric element in a hermetically sealed container. A single or a plurality of cylinders for constructing the compression element, a first support member having a bearing for a rotary shaft of the electric element and closing the opening surface of the cylinder on the side opposite to the electric element, and the electric cylinder. A second support member having a bearing for the rotary shaft is provided while closing the opening surface on the element side, and the bearing and the rotary shaft are provided in the bearing of either one of the first and second support members. It is characterized in that a carbon bush interposed between them is provided.
【0007】請求項2の発明のロータリコンプレッサ
は、上記において第1の支持部材の軸受け内にブッシュ
を設けたことを特徴とする。The rotary compressor according to a second aspect of the present invention is characterized in that the bush is provided in the bearing of the first support member.
【0008】請求項3の発明のロータリコンプレッサ
は、密閉容器内に電動要素と、この電動要素にて駆動さ
れる第1及び第2の回転圧縮要素を備え、第1の回転圧
縮要素で圧縮されたガスを密閉容器内に吐出し、更にこ
の吐出された中間圧のガスを第2の回転圧縮要素で圧縮
するものであって、第1及び第2の回転圧縮要素をそれ
ぞれ構成するための第1及び第2のシリンダと、第1の
シリンダの開口面を閉塞すると共に、電動要素の回転軸
の軸受けを有する第1の支持部材と、第2のシリンダの
開口面を閉塞すると共に、回転軸の軸受けを有する第2
の支持部材とを備え、第1及び第2の支持部材のうちの
何れか一方の軸受け内に、当該軸受けと回転軸との間に
介在するカーボン製ブッシュを設けたことを特徴とす
る。A rotary compressor according to a third aspect of the present invention is provided with an electric element and first and second rotary compression elements driven by the electric element in a hermetic container, and is compressed by the first rotary compression element. The compressed gas is discharged into the closed container, and the discharged intermediate-pressure gas is compressed by the second rotary compression element. The first and second rotary compression elements are respectively formed. The first and second cylinders, the opening surface of the first cylinder, and the first support member having a bearing for the rotating shaft of the electric element, and the opening surface of the second cylinder, and the rotating shaft Second with bearing of
Of the first and second support members, and a carbon bush interposed between the bearing and the rotary shaft is provided in the bearing of one of the first and second support members.
【0009】請求項4の発明のロータリコンプレッサ
は、上記において第2の支持部材の軸受け内にブッシュ
を設けたことを特徴とする。The rotary compressor according to a fourth aspect of the present invention is characterized in that the bush is provided in the bearing of the second support member.
【0010】請求項5の発明のロータリコンプレッサ
は、上記各発明において回転圧縮要素は、CO2ガスを
冷媒として圧縮することを特徴とする。The rotary compressor according to a fifth aspect of the present invention is characterized in that, in each of the above aspects, the rotary compression element compresses CO 2 gas as a refrigerant.
【0011】請求項1の発明によれば、密閉容器内に電
動要素と、この電動要素にて駆動される回転圧縮要素を
設けて成るロータリコンプレッサにおいて、回転圧縮要
素を構成するための単一若しくは複数のシリンダと、シ
リンダの電動要素とは反対側の開口面を閉塞すると共
に、電動要素の回転軸の軸受けを有する第1の支持部材
と、シリンダの電動要素側の開口面を閉塞すると共に、
回転軸の軸受けを有する第2の支持部材とを備え、第1
及び第2の支持部材のうちの何れか一方の軸受け内に、
当該軸受けと回転軸との間に介在するカーボン製ブッシ
ュを設けたので、両方の支持部材の軸受け内にそれぞれ
ブッシュを設ける場合に比較して部品コストの低減を図
ることが可能となる。According to the first aspect of the present invention, in a rotary compressor having an electric element and a rotary compression element driven by the electric element in a closed container, a single or a rotary compression element is provided. While closing a plurality of cylinders, an opening surface of the cylinder on the side opposite to the electric element, closing a first support member having a bearing of a rotating shaft of the electric element, and an opening surface of the cylinder on the electric element side,
A second supporting member having a bearing for the rotating shaft,
And in the bearing of either one of the second support member,
Since the carbon bush interposed between the bearing and the rotary shaft is provided, it is possible to reduce the cost of parts as compared with the case where the bushes are provided in the bearings of both support members.
【0012】特に、請求項2の発明の如く第1の支持部
材の軸受け内にブッシュを設け、シリンダの電動要素側
で回転軸との接触面積が大きくなる第2の支持部材の軸
受け内には設けないようにすれば、受圧面積が小さく単
位面積当たりに加わる荷重が大きくなる第1の支持部材
の軸受けにおける摺動性能を保持し、耐久性能を維持し
ながら、受圧面積が大きく単位面積当たりに加わる荷重
が比較的小さくなる第2の支持部材の軸受けのブッシュ
を削除してコストの削減を図ることが可能となるもので
ある。In particular, as in the second aspect of the invention, a bush is provided in the bearing of the first supporting member, and the contact area with the rotary shaft on the electric element side of the cylinder is large. If it is not provided, the pressure receiving area is small and the load applied per unit area is large. The sliding performance of the bearing of the first support member is maintained and durability is maintained, while the pressure receiving area is large and the load per unit area is large. The cost can be reduced by eliminating the bushing of the bearing of the second support member, which makes the load applied relatively small.
【0013】また、請求項3の発明によれば、密閉容器
内に電動要素と、この電動要素にて駆動される第1及び
第2の回転圧縮要素を備え、第1の回転圧縮要素で圧縮
されたガスを密閉容器内に吐出し、更にこの吐出された
中間圧のガスを第2の回転圧縮要素で圧縮するロータリ
コンプレッサにおいて、第1及び第2の回転圧縮要素を
それぞれ構成するための第1及び第2のシリンダと、第
1のシリンダの開口面を閉塞すると共に、電動要素の回
転軸の軸受けを有する第1の支持部材と、第2のシリン
ダの開口面を閉塞すると共に、回転軸の軸受けを有する
第2の支持部材とを備え、第1及び第2の支持部材のう
ちの何れか一方の軸受け内に、当該軸受けと回転軸との
間に介在するカーボン製ブッシュを設けたので、両方の
支持部材の軸受け内にそれぞれブッシュを設ける場合に
比較して部品コストの低減を図ることが可能となる。According to the third aspect of the present invention, the closed container is provided with the electric element and the first and second rotary compression elements driven by the electric element, and the first rotary compression element compresses the electric element. In the rotary compressor that discharges the discharged gas into the closed container and further compresses the discharged intermediate-pressure gas by the second rotary compression element, the first and second rotary compression elements are respectively configured. The first and second cylinders, the opening surface of the first cylinder, and the first support member having a bearing for the rotating shaft of the electric element, and the opening surface of the second cylinder, and the rotating shaft And a second support member having a bearing, and a carbon bush interposed between the bearing and the rotary shaft is provided in the bearing of one of the first and second support members. , Bearings for both support members Compared with the case where each providing the bushing becomes possible to reduce the parts cost.
【0014】特に、請求項4の発明の如く第2の支持部
材の軸受け内にブッシュを設け、密閉容器内の圧力以下
となる第1のシリンダの開口面を閉塞する第1の支持部
材の軸受け内には設けないようにすれば、密閉容器内よ
りも圧力が高くなる第2のシリンダの開口面を閉塞し、
圧力差による給油が困難となる第2の支持部材の軸受け
における摺動性能を保持し、耐久性能を維持しながら、
圧力差による給油に問題の無い第1の支持部材の軸受け
のブッシュを削除してコストの削減を図ることが可能と
なるものである。In particular, the bearing of the first support member is provided with a bush in the bearing of the second support member so as to close the opening surface of the first cylinder at a pressure equal to or lower than the pressure in the closed container. If it is not provided inside, the opening surface of the second cylinder whose pressure becomes higher than that inside the closed container is closed,
While maintaining the sliding performance in the bearing of the second support member where it becomes difficult to refuel due to the pressure difference and maintaining the durability performance,
The bush of the bearing of the first supporting member, which has no problem in refueling due to the pressure difference, can be eliminated to reduce the cost.
【0015】更に、請求項5の如きCO2ガスを冷媒と
して用い、密閉容器内が極めて高圧となる場合に、コン
プレッサの耐久性能の維持に著しい効果を奏するもので
ある。Further, when the CO 2 gas as claimed in claim 5 is used as the refrigerant and the pressure in the closed container becomes extremely high, the durability of the compressor is remarkably maintained.
【0016】[0016]
【発明の実施の形態】次に、図面に基づき本発明の実施
形態を詳述する。図1は本発明のロータリコンプレッサ
の一実施例として、第1及び第2の回転圧縮要素32、
34を備えた内部中間圧型多段(二段)圧縮式のロータ
リコンプレッサ10の縦断面図を示している。DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 shows, as an embodiment of the rotary compressor of the present invention, first and second rotary compression elements 32,
FIG. 2 is a vertical cross-sectional view of an internal intermediate pressure type multi-stage (two-stage) compression rotary compressor 10 provided with 34.
【0017】この図において、10は二酸化炭素(CO
2)を冷媒として使用する内部中間圧型多段(二段)圧
縮式のロータリコンプレッサで、このロータリコンプレ
ッサ10は鋼板からなる円筒状の密閉容器12と、この
密閉容器12の内部空間の上側に配置収納された電動要
素14及びこの電動要素14の下側に配置され、電動要
素14の回転軸16により駆動される第1の回転圧縮要
素32(1段目)及び第2の回転圧縮要素34(2段
目)からなる回転圧縮機構部18にて構成されている。
この場合、第2の回転圧縮要素34の排除容積は第1の
回転圧縮要素32の排除容積よりも小さく設定されてい
る。In this figure, 10 is carbon dioxide (CO
2 ) is an internal intermediate pressure type multi-stage (two-stage) compression type rotary compressor that uses 2 ) as a refrigerant. The rotary compressor 10 is a cylindrical closed container 12 made of steel plate, and is arranged and stored above the internal space of the closed container 12. And the first rotary compression element 32 (first stage) and the second rotary compression element 34 (2) arranged below the electric element 14 and driven by the rotary shaft 16 of the electric element 14. The rotary compression mechanism section 18 is composed of a step.
In this case, the excluded volume of the second rotary compression element 34 is set smaller than the excluded volume of the first rotary compression element 32.
【0018】密閉容器12は底部をオイル溜めTとし、
電動要素14と回転圧縮機構部18を収納する容器本体
12Aと、この容器本体12Aの上部開口を閉塞する略
椀状のエンドキャップ(蓋体)12Bとで構成されてい
る。このエンドキャップ12Bの上面中心には円形の取
付孔12Dが形成されており、この取付孔12Dには電
動要素14に電力を供給するためのターミナル(配線を
省略)20が取り付けられている。The closed container 12 has an oil reservoir T at the bottom,
It is composed of a container body 12A that houses the electric element 14 and the rotary compression mechanism portion 18, and a substantially bowl-shaped end cap (lid) 12B that closes the upper opening of the container body 12A. A circular mounting hole 12D is formed in the center of the upper surface of the end cap 12B, and a terminal (wiring is omitted) 20 for supplying electric power to the electric element 14 is mounted in the mounting hole 12D.
【0019】この場合、ターミナル20の周囲のエンド
キャップ12Bには、座押成形によって所定曲率の段差
部12Cが環状に形成されている。また、ターミナル2
0は電気的端子139が貫通して取り付けられた円形の
ガラス部20Aと、このガラス部20Aの周囲に形成さ
れ、斜め外下方に鍔状に張り出した金属製の取付部20
Bとから構成されている。そして、ターミナル20は、
そのガラス部20Aを下側から取付孔12Dに挿入して
上側に臨ませ、取付部20Bを取付孔12Dの周縁に当
接させた状態でエンドキャップ12Bの取付孔12D周
縁に取付部20Bを溶接することで、エンドキャップ1
2Bに固定されている。In this case, the end cap 12B around the terminal 20 is formed with a stepped portion 12C having a predetermined curvature in an annular shape by press forming. Also, Terminal 2
Reference numeral 0 denotes a circular glass portion 20A to which the electrical terminal 139 is attached and is attached, and a metal attaching portion 20 formed around the glass portion 20A and protruding obliquely outward and downward to form a brim.
It is composed of B and. And terminal 20
The glass portion 20A is inserted into the mounting hole 12D from the lower side so as to face the upper side, and the mounting portion 20B is welded to the peripheral edge of the mounting hole 12D of the end cap 12B with the mounting portion 20B being in contact with the peripheral edge of the mounting hole 12D. By doing, end cap 1
It is fixed to 2B.
【0020】電動要素14は、密閉容器12の上部空間
の内周面に沿って環状に取り付けられたステータ22
と、このステータ22の内側に若干の間隙を設けて挿入
配置されたロータ24とからなる。このロータ24は中
心を通り鉛直方向に延びる回転軸16に固定されてい
る。The electric element 14 is a stator 22 mounted in an annular shape along the inner peripheral surface of the upper space of the closed container 12.
And a rotor 24 inserted and arranged inside the stator 22 with a slight gap. The rotor 24 is fixed to the rotating shaft 16 that extends vertically through the center.
【0021】ステータ22は、ドーナッツ状の電磁鋼板
を積層した積層体26と、この積層体26の歯部に直巻
き(集中巻き)方式により巻装されたステータコイル2
8を有している。また、ロータ24もステータ22と同
様に電磁鋼板の積層体30で形成され、この積層体30
内に永久磁石MGを挿入して構成されている。The stator 22 includes a laminated body 26 in which donut-shaped electromagnetic steel sheets are laminated, and a stator coil 2 wound around the teeth of the laminated body 26 by a direct winding (concentrated winding) method.
Have eight. The rotor 24 is also formed of a laminated body 30 of electromagnetic steel plates, like the stator 22.
A permanent magnet MG is inserted therein.
【0022】前記第1の回転圧縮要素32と第2の回転
圧縮要素34との間には中間仕切板36が挟持されてい
る。即ち、第2の回転圧縮要素34と第1の回転圧縮要
素34は、中間仕切板36と、この中間仕切板36の上
下に配置されたシリンダ38(第2のシリンダ)、シリ
ンダ40(第1のシリンダ)と、この上下シリンダ3
8、40内を180度の位相差を有して回転軸16に設
けた上下偏心部42、44に嵌合されて偏心回転する上
下ローラ46、48と、この上下ローラ46、48に当
接して上下シリンダ38、40内をそれぞれ低圧室側と
高圧室側に区画する後述する上下ベーン(図示せず)
と、上シリンダ38(第2のシリンダ)の上側(電動要
素14側)の開口面及び下シリンダ40(第1のシリン
ダ)の下側(電動要素14とは反対側)の開口面を閉塞
して回転軸16の軸受けを兼用する支持部材としての上
部支持部材54(第2の支持部材)及び下部支持部材5
6(第1の支持部材)にて構成される。An intermediate partition plate 36 is sandwiched between the first rotary compression element 32 and the second rotary compression element 34. That is, the second rotary compression element 34 and the first rotary compression element 34 include the intermediate partition plate 36, and the cylinders 38 (second cylinders) and the cylinders 40 (first cylinder) arranged above and below the intermediate partition plate 36. Cylinder) and this upper and lower cylinder 3
Upper and lower rollers 46 and 48 which are fitted into upper and lower eccentric portions 42 and 44 provided on the rotary shaft 16 and have an eccentric rotation with a phase difference of 180 degrees inside the reference numerals 8 and 40, and contact the upper and lower rollers 46 and 48. Upper and lower vanes (not shown) described later that divide the insides of the upper and lower cylinders 38 and 40 into the low pressure chamber side and the high pressure chamber side, respectively.
And the upper cylinder 38 (second cylinder) upper opening surface (electric element 14 side) and the lower cylinder 40 (first cylinder) lower opening surface (opposite the electric element 14) opening surface. Upper support member 54 (second support member) and lower support member 5 as support members that also serve as bearings for the rotary shaft 16.
6 (first support member).
【0023】上部支持部材54および下部支持部材56
には、吸込ポート161、162にて上下シリンダ3
8、40の内部とそれぞれ連通する吸込通路58、60
と、凹陥した吐出消音室62、64が形成されると共
に、これら両吐出消音室62、64の開口部はそれぞれ
カバーにより閉塞される。即ち、吐出消音室62はカバ
ーとしての上部カバー66、吐出消音室64はカバーと
しての下部カバー68にて閉塞される。Upper support member 54 and lower support member 56
The suction ports 161 and 162 at the upper and lower cylinders 3.
Suction passages 58, 60 communicating with the insides of 8, 40, respectively.
Then, the recessed discharge silencing chambers 62 and 64 are formed, and the openings of the discharge silencing chambers 62 and 64 are closed by covers. That is, the discharge muffling chamber 62 is closed by the upper cover 66 as a cover, and the discharge muffling chamber 64 is closed by the lower cover 68 as a cover.
【0024】この場合、上部支持部材54(第2の支持
部材)の中央には電動要素14方向に突出する長軸受け
となる軸受け54Aが起立形成されており、この軸受け
54A内面には筒状のブッシュ122が装着されてい
る。このブッシュ122は、回転軸16と軸受け54A
間に介在し、当該ブッシュ122の内面が回転軸16に
摺動自在に接触している。ブッシュ122は給油が不十
分な状況でも良好な摺動性を保持できる耐摩耗性の高い
カーボン材料にて構成されている。また、下部支持部材
56の中央には軸受け54Aと比較して短軸受けとなる
軸受け56Aが貫通形成されているが、この軸受け56
A内面にはブッシュは装着されておらず、軸受け56A
の内面が直接回転軸16に摺動自在に当接している。こ
れにより、回転軸16は、回転圧縮機構部18の電動要
素14側(上側)ではブッシュ122を介して上部支持
部材54の軸受け54Aに保持され、電動要素14と反
対側(下側)では下部支持部材56の軸受け56Aに直
接保持される。In this case, at the center of the upper support member 54 (second support member), a bearing 54A serving as a long bearing protruding toward the electric element 14 is formed upright, and a cylindrical shape is formed on the inner surface of the bearing 54A. The bush 122 is attached. The bush 122 includes a rotary shaft 16 and a bearing 54A.
The bush 122 is interposed therebetween, and the inner surface of the bush 122 slidably contacts the rotating shaft 16. The bush 122 is made of a carbon material having high wear resistance, which can maintain good slidability even under insufficient lubrication. Further, a bearing 56A, which is a short bearing as compared with the bearing 54A, is formed at the center of the lower support member 56 so as to penetrate therethrough.
A bush is not attached to the inner surface of A, and the bearing 56A
The inner surface of is directly slidably in contact with the rotary shaft 16. As a result, the rotary shaft 16 is held by the bearing 54A of the upper support member 54 via the bush 122 on the electric element 14 side (upper side) of the rotary compression mechanism portion 18 and on the lower side (lower side) opposite to the electric element 14. It is directly held by the bearing 56A of the support member 56.
【0025】下部カバー68はドーナッツ状の円形鋼板
から構成されており、周辺部の4カ所を主ボルト129
・・・によって下から下部支持部材56に固定され、第
1の回転圧縮要素32の下シリンダ40内部と連通する
吐出消音室64の下面開口部を閉塞する。この主ボルト
129・・・の先端は上部支持部材54に螺合する。The lower cover 68 is made of a donut-shaped circular steel plate, and the main bolts 129 are provided at four peripheral portions.
Is fixed to the lower support member 56 from below by closing the lower surface opening of the discharge muffling chamber 64 that communicates with the inside of the lower cylinder 40 of the first rotary compression element 32. The tips of the main bolts 129 ... Are screwed into the upper support member 54.
【0026】尚、吐出消音室64と密閉容器12内にお
ける上部カバー66の電動要素14側は、上下シリンダ
38、40や中間仕切板36を貫通する孔である図示し
ない連通路にて連通されている。この連通路の上端には
中間吐出管121が立設されており、この中間吐出管1
21は上方の電動要素14のステータ22に巻装された
相隣接するステータコイル28、28間の隙間に指向し
ている。The discharge muffler chamber 64 and the electric element 14 side of the upper cover 66 in the closed container 12 are communicated with each other by a communication passage (not shown) which is a hole penetrating the upper and lower cylinders 38, 40 and the intermediate partition plate 36. There is. An intermediate discharge pipe 121 is provided upright on the upper end of the communication passage.
21 is directed to the gap between the adjacent stator coils 28, 28 wound around the stator 22 of the upper electric element 14.
【0027】また、上部カバー66は第2の回転圧縮要
素34の上シリンダ38内部と連通する吐出消音室62
の上面開口部を閉塞し、密閉容器12内を吐出消音室6
2と電動要素14側とに仕切る。この上部カバー66は
周辺部が4本の主ボルト78・・・により、上から上部
支持部材54に固定されている。この主ボルト78・・
・の先端は下部支持部材56に螺合する。Further, the upper cover 66 communicates with the inside of the upper cylinder 38 of the second rotary compression element 34 and the discharge muffling chamber 62.
The upper part of the upper surface of the container is closed, and the inside of the closed container 12 is discharged and silenced.
2 and the electric element 14 side. The peripheral portion of the upper cover 66 is fixed to the upper support member 54 from above by four main bolts 78 ... This main bolt 78 ...
The tip of mark is screwed to the lower support member 56.
【0028】次に、上シリンダ38の下側の開口面及び
下シリンダ40の上側の開口面を閉塞する中間仕切板3
6内には、上シリンダ38内の吸込側に対応する位置
に、外周面から内周面に至り、外周面と内周面とを連通
して給油路を構成する貫通孔131が穿設されており、
この貫通孔131の外周面側に封止材132を圧入して
外周面側の開口を封止している。また、この貫通孔13
1の中途部には上側に延在する連通孔133が穿設され
ている。Next, the intermediate partition plate 3 for closing the lower opening surface of the upper cylinder 38 and the upper opening surface of the lower cylinder 40.
6, a through hole 131 is formed at a position corresponding to the suction side in the upper cylinder 38 from the outer peripheral surface to the inner peripheral surface and connects the outer peripheral surface and the inner peripheral surface to form an oil supply passage. And
A sealing material 132 is press-fitted on the outer peripheral surface side of the through hole 131 to seal the outer peripheral surface side opening. Also, this through hole 13
A communication hole 133 extending upward is bored in the middle of 1.
【0029】一方、上シリンダ38の吸込ポート161
(吸込側)には中間仕切板36の連通孔133に連通す
る連通孔134が穿設されている。また、回転軸16内
には軸中心に鉛直方向のオイル孔(図示せず)と、この
オイル孔に連通する横方向の給油孔82、84(回転軸
16の上下偏心部42、44にも形成されている)が形
成されており、中間仕切板36の貫通孔131の内周面
側の開口は、これらの給油孔82、84を介して前記オ
イル孔に連通している。On the other hand, the suction port 161 of the upper cylinder 38
A communication hole 134 that communicates with the communication hole 133 of the intermediate partition plate 36 is formed on the (suction side). Further, an oil hole (not shown) in the vertical direction about the shaft center in the rotary shaft 16, and lateral oil supply holes 82, 84 communicating with the oil hole (also in the vertical eccentric parts 42, 44 of the rotary shaft 16). Is formed), the opening on the inner peripheral surface side of the through hole 131 of the intermediate partition plate 36 communicates with the oil hole via these oil supply holes 82, 84.
【0030】後述する如く密閉容器12内は中間圧とな
るため、2段目で高圧となる上シリンダ38内にはオイ
ルの供給が困難となるが、中間仕切板36を係る構成と
したことにより、密閉容器12内底部のオイル溜めTか
ら汲み上げられて前記オイル孔を上昇し、給油孔82、
84から出たオイルは、中間仕切板36の貫通孔131
に入り、連通孔133、134から上シリンダ38の吸
込側(吸込ポート161)に供給されるようになる。As will be described later, since the inside pressure of the closed container 12 becomes an intermediate pressure, it becomes difficult to supply the oil into the upper cylinder 38 which becomes a high pressure in the second stage. , Is pumped up from the oil reservoir T at the bottom of the closed container 12 to move up through the oil hole,
The oil discharged from 84 is the through hole 131 of the intermediate partition plate 36.
Then, the gas is supplied from the communication holes 133 and 134 to the suction side (suction port 161) of the upper cylinder 38.
【0031】ところで、回転軸16と一体に180度の
位相差を持って形成される上下偏心部42、44の相互
間を連結する連結部90は、その断面形状を回転軸16
の円形断面より断面積を大きくして剛性を持たせるため
に非円形状の例えばラグビーボール状とされている。即
ち、回転軸16に設けた上下偏心部42、44を連結す
る連結部90の断面形状は上下偏心部42、44の偏心
方向に直交する方向でその肉厚を大きくしている。By the way, the connecting portion 90 which connects the upper and lower eccentric portions 42 and 44 integrally formed with the rotating shaft 16 with a phase difference of 180 degrees has a sectional shape of the rotating shaft 16.
The non-circular shape, for example, a rugby ball shape, has a larger cross-sectional area than the circular cross-section and has rigidity. That is, the cross-sectional shape of the connecting portion 90 that connects the vertical eccentric portions 42 and 44 provided on the rotary shaft 16 has a large thickness in the direction orthogonal to the eccentric direction of the vertical eccentric portions 42 and 44.
【0032】これにより、回転軸16に一体に設けられ
た上下偏心部42、44を連結する連結部90の断面積
が大きくし、断面2次モーメントを増加させて強度(剛
性)を増し、耐久性と信頼性を向上させている。特に、
使用圧力の高い冷媒を2段圧縮する場合、高低圧の圧力
差が大きいために回転軸16にかかる荷重も大きくなる
が、連結部90の断面積を大きくしてその強度(剛性)
を増し、回転軸16が弾性変形してしまうのを防止して
いる。As a result, the cross-sectional area of the connecting portion 90 which connects the vertical eccentric portions 42 and 44 integrally provided on the rotary shaft 16 is increased, and the second moment of area is increased to increase the strength (rigidity) and durability. It improves the reliability and reliability. In particular,
When the refrigerant having a high working pressure is compressed in two stages, the load applied to the rotating shaft 16 is large because the pressure difference between the high pressure and the low pressure is large, but the cross-sectional area of the connecting portion 90 is increased to increase its strength (rigidity).
Therefore, the rotation shaft 16 is prevented from being elastically deformed.
【0033】そして、この場合冷媒としては地球環境に
やさしく、可燃性および毒性等を考慮して自然冷媒であ
る炭酸ガスの一例としての前記二酸化炭素(CO2)を
使用し、潤滑油としてのオイルは、例えば鉱物油(ミネ
ラルオイル)、アルキルベンゼン油、エーテル油、エス
テル油等既存のオイルが使用される。In this case, carbon dioxide (CO 2 ) as an example of carbon dioxide, which is a natural refrigerant, is used as the refrigerant in consideration of flammability, toxicity, etc. As the oil, existing oils such as mineral oil, alkylbenzene oil, ether oil and ester oil are used.
【0034】密閉容器12の容器本体12Aの側面に
は、上部支持部材54と下部支持部材56の吸込通路5
8、60、吐出消音室62及び上部カバー66の上側
(電動要素14の下端に略対応する位置)に対応する位
置に、スリーブ141、142、143及び144がそ
れぞれ溶接固定されている。スリーブ141と142は
上下に隣接すると共に、スリーブ143はスリーブ14
1の略対角線上にある。また、スリーブ144はスリー
ブ141と略90度ずれた位置にある。The suction passage 5 of the upper support member 54 and the lower support member 56 is provided on the side surface of the container body 12A of the closed container 12.
The sleeves 141, 142, 143, and 144 are welded and fixed to the positions corresponding to the upper side of the discharge silencer chamber 62 and the upper cover 66 (the position substantially corresponding to the lower end of the electric element 14). The sleeves 141 and 142 are vertically adjacent to each other, and the sleeve 143 is
1 is on a substantially diagonal line. Further, the sleeve 144 is located at a position displaced from the sleeve 141 by approximately 90 degrees.
【0035】そして、スリーブ141内には上シリンダ
38に冷媒ガスを導入するための冷媒導入管92の一端
が挿入接続され、この冷媒導入管92の一端は上シリン
ダ38の吸込通路58に連通される。この冷媒導入管9
2は密閉容器12の上側を通過してスリーブ144に至
り、他端はスリーブ144内に挿入接続されて密閉容器
12内に連通する。Then, one end of a refrigerant introducing pipe 92 for introducing a refrigerant gas into the upper cylinder 38 is inserted and connected in the sleeve 141, and one end of the refrigerant introducing pipe 92 is communicated with the suction passage 58 of the upper cylinder 38. It This refrigerant introduction pipe 9
2 passes through the upper side of the closed container 12 to reach the sleeve 144, and the other end is inserted and connected in the sleeve 144 to communicate with the closed container 12.
【0036】また、スリーブ142内には下シリンダ4
0に冷媒ガスを導入するための冷媒導入管94の一端が
挿入接続され、この冷媒導入管94の一端は下シリンダ
40の吸込通路60に連通される。また、スリーブ14
3内には冷媒吐出管96が挿入接続され、この冷媒吐出
管96の一端は吐出消音室62に連通される。In the sleeve 142, the lower cylinder 4
One end of a refrigerant introduction pipe 94 for introducing the refrigerant gas to 0 is inserted and connected, and one end of this refrigerant introduction pipe 94 is communicated with the suction passage 60 of the lower cylinder 40. Also, the sleeve 14
A refrigerant discharge pipe 96 is inserted into and connected to the inside of the nozzle 3, and one end of the refrigerant discharge pipe 96 communicates with the discharge muffling chamber 62.
【0037】また、スリーブ141、143、144の
外面周囲には配管接続用のカプラが係合可能な鍔部15
1が形成されており、スリーブ142の外面には配管接
続用のネジ溝152が形成されている。これにより、ス
リーブ141、143、144にはロータリコンプレッ
サ10の製造工程における完成検査で気密試験を行う場
合に試験用配管のカプラを鍔部151に容易に接続でき
るようになると共に、スリーブ142にはネジ溝152
を使用して試験用配管を容易にネジ止めできるようにな
る。特に、上下で隣接するスリーブ141と142は、
一方のスリーブ141に鍔部151が、他方のスリーブ
142にネジ溝152が形成されていることで、狭い空
間で試験用配管を各スリーブ141、142に接続可能
となる。A flange portion 15 is formed around the outer surfaces of the sleeves 141, 143, 144 so that a coupler for pipe connection can be engaged.
1 is formed, and a thread groove 152 for pipe connection is formed on the outer surface of the sleeve 142. As a result, the sleeves 141, 143, 144 can be easily connected to the flange 151 while the coupler of the test pipe is easily connected to the sleeve 142 when the air tightness test is performed in the completion inspection in the manufacturing process of the rotary compressor 10. Screw groove 152
You can easily screw the test pipe with. In particular, the upper and lower sleeves 141 and 142 are
Since the flange 151 is formed on one sleeve 141 and the thread groove 152 is formed on the other sleeve 142, the test pipe can be connected to each sleeve 141, 142 in a narrow space.
【0038】そして、実施例のロータリコンプレッサ1
0は図2に示すような給湯装置153の冷媒回路に使用
される。即ち、ロータリコンプレッサ10の冷媒吐出管
96は水加熱用のガスクーラ154の入口に接続され
る。このガスクーラ154が給湯装置153の図示しな
い貯湯タンクに設けられる。ガスクーラ154を出た配
管は減圧装置としての膨張弁156を経て蒸発器157
の入口に至り、蒸発器157の出口は冷媒導入管94に
接続される。また、冷媒導入管92の中途部からは除霜
回路を構成するデフロスト管158が分岐し、流路制御
装置としての電磁弁159を介してガスクーラ154の
入口に至る冷媒吐出管96に接続されている。The rotary compressor 1 of the embodiment
0 is used in the refrigerant circuit of the water heater 153 as shown in FIG. That is, the refrigerant discharge pipe 96 of the rotary compressor 10 is connected to the inlet of the gas cooler 154 for heating water. The gas cooler 154 is provided in a hot water storage tank (not shown) of the hot water supply device 153. The pipe exiting the gas cooler 154 is passed through an expansion valve 156 as a pressure reducing device and then an evaporator 157.
And the outlet of the evaporator 157 is connected to the refrigerant introduction pipe 94. Further, a defrost pipe 158 forming a defrosting circuit branches from a middle portion of the refrigerant introduction pipe 92, and is connected to a refrigerant discharge pipe 96 reaching an inlet of the gas cooler 154 via an electromagnetic valve 159 as a flow path control device. There is.
【0039】以上の構成で次に動作を説明する。尚、加
熱運転では電磁弁159は閉じているものとする。ター
ミナル20および図示されない配線を介して電動要素1
4のステータコイル28に通電されると、電動要素14
が起動してロータ24が回転する。この回転により回転
軸16と一体に設けた上下偏心部42、44に嵌合され
た上下ローラ46、48が上下シリンダ38、40内を
偏心回転する。The operation of the above configuration will be described below. In the heating operation, the solenoid valve 159 is closed. Electric element 1 via terminal 20 and wiring not shown
When the stator coil 28 of No. 4 is energized, the electric element 14
Starts and the rotor 24 rotates. By this rotation, the upper and lower rollers 46 and 48 fitted in the upper and lower eccentric portions 42 and 44 integrally provided with the rotating shaft 16 eccentrically rotate in the upper and lower cylinders 38 and 40.
【0040】これにより、冷媒導入管94および下部支
持部材56に形成された吸込通路60を経由して吸込ポ
ート162から下シリンダ40の低圧室側に吸入された
低圧(一段目吸入圧LP:4MPaG)の冷媒ガスは、
ローラ48とベーンの動作により圧縮されて中間圧(M
P1:8MPaG)となり下シリンダ40の高圧室側よ
り下部支持部材56に形成された吐出消音室64に吐出
され、連通路63を経て中間吐出管121から密閉容器
12内に吐出される。As a result, the low pressure (first stage suction pressure LP: 4 MPaG) sucked from the suction port 162 to the low pressure chamber side of the lower cylinder 40 via the suction passage 60 formed in the refrigerant introduction pipe 94 and the lower support member 56. ) The refrigerant gas is
The intermediate pressure (M
P1: 8 MPaG) and is discharged from the high pressure chamber side of the lower cylinder 40 to the discharge muffling chamber 64 formed in the lower support member 56, and is discharged from the intermediate discharge pipe 121 into the closed container 12 through the communication passage 63.
【0041】このとき、中間吐出管121は上方の電動
要素14のステータ22に巻装された相隣接するステー
タコイル28、28間の隙間に指向しているので、未だ
比較的温度の低い冷媒ガスを電動要素14方向に積極的
に供給できるようになり、電動要素14の温度上昇が抑
制されるようになる。また、これによって、密閉容器1
2内は中間圧(MP1)となる。At this time, since the intermediate discharge pipe 121 is directed to the gap between the adjacent stator coils 28, 28 wound around the stator 22 of the electric element 14 above, the refrigerant gas having a relatively low temperature is still present. Can be positively supplied in the direction of the electric element 14, and the temperature rise of the electric element 14 can be suppressed. Moreover, by this, the closed container 1
The inside of 2 becomes an intermediate pressure (MP1).
【0042】そして、密閉容器12内の中間圧の冷媒ガ
スは、スリーブ144から出て(中間吐出圧は前記MP
1)冷媒導入管92及び上部支持部材54に形成された
吸込通路58を経由して吸込ポート161から上シリン
ダ38の低圧室側に吸入される(2段目吸入圧MP
2)。吸入された中間圧の冷媒ガスは、ローラ46とベ
ーンの動作により2段目の圧縮が行なわれて高温高圧の
冷媒ガスとなり(2段目吐出圧HP:12MPaG)、
高圧室側から上部支持部材54に形成された吐出消音室
62、冷媒吐出管96を経由してガスクーラ154内に
流入する。このときの冷媒温度は略+100℃まで上昇
しており、係る高温高圧の冷媒ガスは放熱して、貯湯タ
ンク内の水を加熱し、約+90℃の温水を生成する。The intermediate pressure refrigerant gas in the closed container 12 is discharged from the sleeve 144 (the intermediate discharge pressure is equal to the above-mentioned MP value).
1) The refrigerant is introduced into the low pressure chamber side of the upper cylinder 38 from the suction port 161 through the refrigerant introduction pipe 92 and the suction passage 58 formed in the upper support member 54 (second-stage suction pressure MP
2). The sucked intermediate-pressure refrigerant gas is compressed in the second stage by the operation of the roller 46 and the vane to become high-temperature high-pressure refrigerant gas (second-stage discharge pressure HP: 12 MPaG).
The gas flows into the gas cooler 154 from the high-pressure chamber side via the discharge muffling chamber 62 formed in the upper support member 54 and the refrigerant discharge pipe 96. At this time, the refrigerant temperature has risen to approximately + 100 ° C, and the high-temperature and high-pressure refrigerant gas radiates heat to heat the water in the hot water storage tank to generate hot water of approximately + 90 ° C.
【0043】一方、ガスクーラ154において冷媒自体
は冷却され、ガスクーラ154を出る。そして、膨張弁
156で減圧された後、蒸発器157に流入して蒸発
し、アキュムレータ(図示せず)を経て冷媒導入管94
から第1の回転圧縮要素32内に吸い込まれるサイクル
を繰り返す。On the other hand, the refrigerant itself is cooled in the gas cooler 154 and exits the gas cooler 154. Then, after being decompressed by the expansion valve 156, it flows into the evaporator 157 and evaporates, and passes through an accumulator (not shown), and then the refrigerant introduction pipe 94.
To cycle into the first rotary compression element 32 from.
【0044】特に、低外気温の環境ではこのような加熱
運転で蒸発器157には着霜が成長する。その場合には
電磁弁159を開放し、膨張弁156は全開状態として
蒸発器157の除霜運転を実行する。これにより、密閉
容器12内の中間圧の冷媒(第2の回転圧縮要素34か
ら吐出された少量の高圧冷媒を含む)は、デフロスト管
158を通ってガスクーラ154に至る。この冷媒の温
度は+50〜+60℃程であり、ガスクーラ154では
放熱せず、当初は逆に冷媒が熱を吸収するかたちとな
る。そして、ガスクーラ154から出た冷媒は膨張弁1
56を通過し、蒸発器157に至るようになる。即ち、
蒸発器157には略中間圧の比較的温度の高い冷媒が減
圧されずに実質的に直接供給されるかたちとなり、これ
によって、蒸発器157は加熱され、除霜されることに
なる。In particular, in an environment of low outside temperature, such heating operation causes frost to grow on the evaporator 157. In that case, the solenoid valve 159 is opened, the expansion valve 156 is fully opened, and the evaporator 157 is defrosted. As a result, the medium-pressure refrigerant (including a small amount of high-pressure refrigerant discharged from the second rotary compression element 34) in the closed container 12 reaches the gas cooler 154 through the defrost pipe 158. The temperature of this refrigerant is about +50 to + 60 ° C., and the gas cooler 154 does not dissipate heat, but the refrigerant initially absorbs heat. The refrigerant discharged from the gas cooler 154 is the expansion valve 1
It passes through 56 and reaches the evaporator 157. That is,
The evaporator 157 is substantially directly supplied with the refrigerant having a substantially intermediate pressure and having a relatively high temperature without being decompressed, whereby the evaporator 157 is heated and defrosted.
【0045】このようなロータリコンプレッサ10の運
転中、偏心部44下方の回転軸16は下部支持部材56
の軸受け56A内で摺動しながら回転することになる
が、1段目の第1の回転圧縮要素32のシリンダ40内
の圧力は密閉容器12内の中間圧以下であるので、オイ
ル溜めTからは円滑に軸受け56Aと回転軸16間にオ
イルが進入でき、摺動性に問題は生じない。During the operation of the rotary compressor 10 as described above, the rotary shaft 16 below the eccentric portion 44 has the lower support member 56.
Although it rotates while sliding in the bearing 56A of the above, since the pressure in the cylinder 40 of the first rotary compression element 32 of the first stage is equal to or lower than the intermediate pressure in the closed container 12, The oil can smoothly enter between the bearing 56A and the rotary shaft 16 and there is no problem in the slidability.
【0046】一方、2段目の第2の回転圧縮要素34の
シリンダ38内は密閉容器12内よりも高い高圧となる
ため、偏心部42上方の回転軸16が摺動しながら回転
する上部支持部材54の軸受け54A内には圧力差でオ
イルが進入し難くなるが、軸受け54Aにおいては、そ
の内部に設けられたカーボン製のブッシュ122内で回
転軸16は摺動しながら回転することになるため、摺動
性に問題は生じない。On the other hand, since the pressure inside the cylinder 38 of the second rotary compression element 34 of the second stage is higher than that inside the closed container 12, the upper support that the rotating shaft 16 above the eccentric portion 42 rotates while sliding. Although it is difficult for oil to enter the bearing 54A of the member 54 due to the pressure difference, in the bearing 54A, the rotating shaft 16 rotates while sliding in the carbon bush 122 provided therein. Therefore, there is no problem in slidability.
【0047】そして、軸受け56A内には上述の如くブ
ッシュを設けないことにより、比較的高価なブッシュを
削除し、部品コストの削減を図ることが可能となる。By not providing the bush in the bearing 56A as described above, it is possible to eliminate the relatively expensive bush and reduce the cost of parts.
【0048】ここで、上記実施例では軸受け54A内に
ブッシュ122を設け、軸受け56A内にはブッシュを
設けないようにしてコストの削減を図ったが、各圧縮要
素の吸込・吐出の圧力によっては、図3に示す如く逆に
軸受け56A内にカーボン製のブッシュ123を設けて
軸受け56Aと回転軸16間に介在させ、軸受け54A
内には設けないようにしてもよい。Here, in the above embodiment, the bush 122 is provided in the bearing 54A and the bush is not provided in the bearing 56A to reduce the cost. However, depending on the suction / discharge pressure of each compression element. On the contrary, as shown in FIG. 3, a bush 123 made of carbon is provided in the bearing 56A so as to be interposed between the bearing 56A and the rotary shaft 16, and the bearing 54A.
It may not be provided inside.
【0049】係る構成によれば、短軸受けであって受圧
面積が小さく、単位面積当たりに加わる荷重が大きくな
る軸受け56Aにおける摺動性能を保持し、耐久性能を
維持しながら、受圧面積が大きく単位面積当たりに加わ
る荷重が比較的小さくなる軸受け54Aのブッシュを削
除してコストの削減を図ることが可能となる。According to this structure, the bearing 56A, which is a short bearing and has a small pressure receiving area and a large load applied per unit area, retains the sliding performance and maintains the durability performance, while the pressure receiving area is large. It is possible to reduce the cost by deleting the bush of the bearing 54A in which the load applied per area is relatively small.
【0050】このとき、下部カバー68の内径は下部支
持部材56の内径よりも小さくし、ブッシュ123の下
縁を下部カバー68により保持して、ブッシュ123の
脱落を防止するとよい。At this time, the inner diameter of the lower cover 68 may be smaller than the inner diameter of the lower support member 56, and the lower edge of the bush 123 may be held by the lower cover 68 to prevent the bush 123 from falling off.
【0051】尚、ロータリコンプレッサとしては実施例
の如き内部中間圧型多段圧縮式のロータリコンプレッサ
に限らず、請求項1、請求項2では単一シリンダのロー
タリコンプレッサにも有効である。また、実施例ではロ
ータリコンプレッサ10を給湯装置153の冷媒回路に
用いたが、これに限らず、室内の暖房用などに用いても
本発明は有効である。The rotary compressor is not limited to the internal intermediate pressure type multi-stage compression type rotary compressor as in the embodiment, but is also effective for a single cylinder rotary compressor in claims 1 and 2. Further, although the rotary compressor 10 is used in the refrigerant circuit of the hot water supply device 153 in the embodiment, the present invention is not limited to this and is also effective when used for heating the room.
【0052】[0052]
【発明の効果】以上詳述した如く請求項1の発明によれ
ば、密閉容器内に電動要素と、この電動要素にて駆動さ
れる回転圧縮要素を設けて成るロータリコンプレッサに
おいて、回転圧縮要素を構成するための単一若しくは複
数のシリンダと、シリンダの電動要素とは反対側の開口
面を閉塞すると共に、回転軸の軸受けを有する第1の支
持部材と、シリンダの電動要素側の開口面を閉塞すると
共に、電動要素の回転軸の軸受けを有する第2の支持部
材とを備え、第1及び第2の支持部材のうちの何れか一
方の軸受け内に、当該軸受けと回転軸との間に介在する
カーボン製ブッシュを設けたので、両方の支持部材の軸
受け内にそれぞれブッシュを設ける場合に比較して部品
コストの低減を図ることが可能となる。As described above in detail, according to the invention of claim 1, in a rotary compressor having an electric element and a rotary compression element driven by the electric element in a closed container, the rotary compression element is provided. A single or a plurality of cylinders for constituting the cylinder, an opening surface of the cylinder on the side opposite to the electric element, and a first support member having a bearing of the rotary shaft and an opening surface of the cylinder on the electric element side are closed. A second support member that is closed and has a bearing for the rotating shaft of the electric element, and is provided in either one of the first and second supporting members between the bearing and the rotating shaft. Since the intervening carbon bush is provided, the cost of parts can be reduced as compared with the case where the bushes are provided in the bearings of both support members.
【0053】特に、請求項2の発明の如く第1の支持部
材の軸受け内にブッシュを設け、シリンダの電動要素側
で回転軸との接触面積が大きくなる第2の支持部材の軸
受け内には設けないようにすれば、受圧面積が小さく単
位面積当たりに加わる荷重が大きくなる第1の支持部材
の軸受けにおける摺動性能を保持し、耐久性能を維持し
ながら、受圧面積が大きく単位面積当たりに加わる荷重
が比較的小さくなる第2の支持部材の軸受けのブッシュ
を削除してコストの削減を図ることが可能となるもので
ある。Particularly, as in the second aspect of the present invention, a bush is provided in the bearing of the first support member, and the contact area with the rotary shaft on the electric element side of the cylinder is increased. If it is not provided, the pressure receiving area is small and the load applied per unit area is large. The sliding performance of the bearing of the first support member is maintained and durability is maintained, while the pressure receiving area is large and the load per unit area is large. The cost can be reduced by eliminating the bushing of the bearing of the second support member, which makes the load applied relatively small.
【0054】また、請求項3の発明によれば、密閉容器
内に電動要素と、この電動要素にて駆動される第1及び
第2の回転圧縮要素を備え、第1の回転圧縮要素で圧縮
されたガスを密閉容器内に吐出し、更にこの吐出された
中間圧のガスを第2の回転圧縮要素で圧縮するロータリ
コンプレッサにおいて、第1及び第2の回転圧縮要素を
それぞれ構成するための第1及び第2のシリンダと、第
1のシリンダの開口面を閉塞すると共に、電動要素の回
転軸の軸受けを有する第1の支持部材と、第2のシリン
ダの開口面を閉塞すると共に、回転軸の軸受けを有する
第2の支持部材とを備え、第1及び第2の支持部材のう
ちの何れか一方の軸受け内に、当該軸受けと回転軸との
間に介在するカーボン製ブッシュを設けたので、両方の
支持部材の軸受け内にそれぞれブッシュを設ける場合に
比較して部品コストの低減を図ることが可能となる。According to the third aspect of the present invention, the closed container is provided with the electric element and the first and second rotary compression elements driven by the electric element, and the first rotary compression element is used for compression. In the rotary compressor that discharges the discharged gas into the closed container and further compresses the discharged intermediate-pressure gas by the second rotary compression element, the first and second rotary compression elements are respectively configured. The first and second cylinders, the opening surface of the first cylinder, and the first support member having a bearing for the rotating shaft of the electric element, and the opening surface of the second cylinder, and the rotating shaft A second support member having a bearing, and a carbon bush interposed between the bearing and the rotary shaft is provided in the bearing of one of the first and second support members. , Bearings for both support members Compared with the case where each providing the bushing becomes possible to reduce the parts cost.
【0055】特に、請求項4の発明の如く第2の支持部
材の軸受け内にブッシュを設け、密閉容器内の圧力以下
となる第1のシリンダの開口面を閉塞する第1の支持部
材の軸受け内には設けないようにすれば、密閉容器内よ
りも圧力が高くなる第2のシリンダの開口面を閉塞し、
圧力差による給油が困難となる第2の支持部材の軸受け
における摺動性能を保持し、耐久性能を維持しながら、
圧力差による給油に問題の無い第1の支持部材の軸受け
のブッシュを削除してコストの削減を図ることが可能と
なるものである。In particular, the bearing of the first support member is provided with a bush in the bearing of the second support member so as to close the opening surface of the first cylinder at which the pressure in the sealed container is equal to or lower than the pressure in the sealed container. If it is not provided inside, the opening surface of the second cylinder whose pressure becomes higher than that inside the closed container is closed,
While maintaining the sliding performance in the bearing of the second support member where it becomes difficult to refuel due to the pressure difference and maintaining the durability performance,
The bush of the bearing of the first supporting member, which has no problem in refueling due to the pressure difference, can be eliminated to reduce the cost.
【0056】更に、請求項5の如きCO2ガスを冷媒と
して用い、密閉容器内が極めて高圧となる場合に、コン
プレッサの耐久性能の維持に著しい効果を奏するもので
ある。Further, when the CO 2 gas as claimed in claim 5 is used as the refrigerant and the pressure inside the closed container becomes extremely high, the durability of the compressor is remarkably maintained.
【図1】本発明の実施例のロータリコンプレッサの縦断
面図である。FIG. 1 is a vertical sectional view of a rotary compressor according to an embodiment of the present invention.
【図2】図1のロータリコンプレッサを適用した給湯装
置の冷媒回路図である。FIG. 2 is a refrigerant circuit diagram of a hot water supply device to which the rotary compressor of FIG. 1 is applied.
【図3】本発明のもう一つの実施例のロータリコンプレ
ッサの縦断面図である。FIG. 3 is a vertical sectional view of a rotary compressor according to another embodiment of the present invention.
10 ロータリコンプレッサ 12 密閉容器 14 電動要素 16 回転軸 18 回転圧縮機構部 20 ターミナル 32 第1の回転圧縮要素 34 第2の回転圧縮要素 36 中間仕切板 38、40 シリンダ 39、41 吐出ポート 42 偏心部 44 偏心部 46 ローラ 48 ローラ 54 上部支持部材 54A 軸受け 56 下部支持部材 56A 軸受け 62 吐出消音室 64 吐出消音室 66 上部カバー 68 下部カバー 92、94 冷媒導入管 96 冷媒吐出管 122、123 ブッシュ 10 Rotary compressor 12 airtight container 14 Electric elements 16 rotation axes 18 Rotary compression mechanism 20 terminals 32 First rotary compression element 34 Second rotary compression element 36 Intermediate partition plate 38, 40 cylinders 39, 41 Discharge port 42 Eccentric part 44 Eccentric part 46 Laura 48 Roller 54 Upper support member 54A bearing 56 Lower support member 56A bearing 62 Discharge silencer 64 discharge silencer 66 Top cover 68 Lower cover 92,94 Refrigerant introduction pipe 96 Refrigerant discharge pipe 122, 123 bush
フロントページの続き (72)発明者 松本 兼三 大阪府守口市京阪本通2丁目5番5号 三 洋電機株式会社内 (72)発明者 松浦 大 大阪府守口市京阪本通2丁目5番5号 三 洋電機株式会社内 (72)発明者 里 和哉 大阪府守口市京阪本通2丁目5番5号 三 洋電機株式会社内 (72)発明者 斎藤 隆泰 大阪府守口市京阪本通2丁目5番5号 三 洋電機株式会社内 (72)発明者 江原 俊行 大阪府守口市京阪本通2丁目5番5号 三 洋電機株式会社内 (72)発明者 今井 悟 大阪府守口市京阪本通2丁目5番5号 三 洋電機株式会社内 (72)発明者 小田 淳志 大阪府守口市京阪本通2丁目5番5号 三 洋電機株式会社内 (72)発明者 佐藤 孝 大阪府守口市京阪本通2丁目5番5号 三 洋電機株式会社内 (72)発明者 松森 裕之 大阪府守口市京阪本通2丁目5番5号 三 洋電機株式会社内 Fターム(参考) 3H029 AA04 AA09 AA13 AB03 BB32 CC05 CC07 CC09 CC16 CC17Continued front page (72) Inventor Kenzo Matsumoto 2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture Within Yo Denki Co., Ltd. (72) Inventor Dai Matsuura 2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture Within Yo Denki Co., Ltd. (72) Inventor Kazuya Sato 2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture Within Yo Denki Co., Ltd. (72) Inventor Takayasu Saito 2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture Within Yo Denki Co., Ltd. (72) Inventor Toshiyuki Ehara 2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture Within Yo Denki Co., Ltd. (72) Inventor Satoru Imai 2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture Within Yo Denki Co., Ltd. (72) Inventor Atsushi Oda 2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture Within Yo Denki Co., Ltd. (72) Inventor Takashi Sato 2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture Within Yo Denki Co., Ltd. (72) Inventor Hiroyuki Matsumori 2-5-3 Keihan Hondori, Moriguchi City, Osaka Prefecture Within Yo Denki Co., Ltd. F term (reference) 3H029 AA04 AA09 AA13 AB03 BB32 CC05 CC07 CC09 CC16 CC17
Claims (5)
て駆動される回転圧縮要素を設けて成るロータリコンプ
レッサにおいて、 前記回転圧縮要素を構成するための単一若しくは複数の
シリンダと、 シリンダの前記電動要素とは反対側の開口面を閉塞する
と共に、前記電動要素の回転軸の軸受けを有する第1の
支持部材と、 シリンダの前記電動要素側の開口面を閉塞すると共に、
前記回転軸の軸受けを有する第2の支持部材とを備え、 前記第1及び第2の支持部材のうちの何れか一方の軸受
け内に、当該軸受けと前記回転軸との間に介在するカー
ボン製ブッシュを設けたことを特徴とするロータリコン
プレッサ。1. A rotary compressor comprising an electric element and a rotary compression element driven by the electric element in a closed container, wherein a single or a plurality of cylinders for constituting the rotary compression element, and a cylinder. And a first support member having a bearing of a rotating shaft of the electric element, and an opening surface of the cylinder on the electric element side,
A second support member having a bearing for the rotary shaft, wherein carbon is interposed between the bearing and the rotary shaft in the bearing of one of the first and second support members. A rotary compressor characterized by having a bush.
ッシュを設けたことを特徴とする請求項1のロータリコ
ンプレッサ。2. The rotary compressor according to claim 1, wherein the bush is provided in a bearing of the first support member.
て駆動される第1及び第2の回転圧縮要素を備え、前記
第1の回転圧縮要素で圧縮されたガスを前記密閉容器内
に吐出し、更にこの吐出された中間圧のガスを前記第2
の回転圧縮要素で圧縮するロータリコンプレッサにおい
て、 前記第1及び第2の回転圧縮要素をそれぞれ構成するた
めの第1及び第2のシリンダと、 前記第1のシリンダの開口面を閉塞すると共に、前記電
動要素の回転軸の軸受けを有する第1の支持部材と、 前記第2のシリンダの開口面を閉塞すると共に、前記回
転軸の軸受けを有する第2の支持部材とを備え、 前記第1及び第2の支持部材のうちの何れか一方の軸受
け内に、当該軸受けと前記回転軸との間に介在するカー
ボン製ブッシュを設けたことを特徴とするロータリコン
プレッサ。3. A hermetic container is provided with an electric element and first and second rotary compression elements driven by the electric element, and gas compressed by the first rotary compression element is contained in the hermetic container. Is discharged to the second, and the discharged intermediate pressure gas is discharged to the second
In the rotary compressor for compressing with the rotary compression element, the first and second cylinders for configuring the first and second rotary compression elements, respectively, and closing the opening surface of the first cylinder, A first support member having a bearing for the rotary shaft of the electric element; and a second support member closing the opening surface of the second cylinder and having the bearing for the rotary shaft. A rotary compressor characterized in that a carbon bush interposed between the bearing and the rotary shaft is provided in the bearing of one of the two supporting members.
ッシュを設けたことを特徴とする請求項3のロータリコ
ンプレッサ。4. The rotary compressor according to claim 3, wherein the bush is provided in a bearing of the second support member.
として圧縮することを特徴とする請求項1、請求項2、
請求項3又は請求項4のロータリコンプレッサ。5. The rotary compression element compresses CO 2 gas as a refrigerant, wherein the rotary compression element compresses CO 2 gas as a refrigerant.
The rotary compressor according to claim 3 or 4.
Priority Applications (31)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2001323769A JP2003129981A (en) | 2001-10-22 | 2001-10-22 | Rotary compressor |
US10/225,442 US7128540B2 (en) | 2001-09-27 | 2002-08-22 | Refrigeration system having a rotary compressor |
EP06013468A EP1703130B1 (en) | 2001-09-27 | 2002-09-10 | Rotary vane compressor and defroster |
EP04030239A EP1522733A3 (en) | 2001-09-27 | 2002-09-10 | Rotary vane compressor with vane holding plug |
ES06013468T ES2398963T3 (en) | 2001-09-27 | 2002-09-10 | Rotary vane compressor and defroster |
EP06013471A EP1703133A3 (en) | 2001-09-27 | 2002-09-10 | Rotary vane compressor |
ES06013467T ES2398363T3 (en) | 2001-09-27 | 2002-09-10 | Rotary vane compressor |
EP06013470A EP1703132B1 (en) | 2001-09-27 | 2002-09-10 | Rotary vane compressor |
EP02256240A EP1298324A3 (en) | 2001-09-27 | 2002-09-10 | Rotary vane compressor with vane holding plug |
EP06013469A EP1703131A3 (en) | 2001-09-27 | 2002-09-10 | Rotary vane compressor |
EP04030233A EP1517041A3 (en) | 2001-09-27 | 2002-09-10 | Rotary vane compressor with vane holding plug |
ES06013470T ES2398245T3 (en) | 2001-09-27 | 2002-09-10 | Rotary vane compressor |
EP04030238A EP1517036A3 (en) | 2001-09-27 | 2002-09-10 | A high pressure pump for an internal-combustion engine |
EP06013467A EP1703129B1 (en) | 2001-09-27 | 2002-09-10 | Rotary vane compressor |
CNB2006100743724A CN100425842C (en) | 2001-09-27 | 2002-09-26 | Compressor |
KR1020020058289A KR20030028388A (en) | 2001-09-27 | 2002-09-26 | Compressor, method for manufacturing the compressor, defroster of refrigerant circuit, and refrigeration unit |
US10/747,285 US7174725B2 (en) | 2001-09-27 | 2003-12-30 | Compressor, method for manufacturing the compressor, defroster of refrigerant circuit, and refrigeration unit |
US10/747,288 US20040151603A1 (en) | 2001-09-27 | 2003-12-30 | Compressor, method for manufacturing the compressor, defroster of refrigerant circuit, and refrigeration unit |
US10/790,181 US7435062B2 (en) | 2001-09-27 | 2004-03-02 | Compressor, method for manufacturing the compressor, defroster of refrigerant circuit, and refrigeration unit |
US10/790,085 US7435063B2 (en) | 2001-09-27 | 2004-03-02 | Compressor, method for manufacturing the compressor, defroster of refrigerant circuit, and refrigeration unit |
US11/377,402 US7302803B2 (en) | 2001-09-27 | 2006-03-17 | Compressor, method for manufacturing the compressor, defroster of refrigerant circuit, and refrigerant unit |
US11/896,347 US7837449B2 (en) | 2001-09-27 | 2007-08-31 | Compressor, method for manufacturing the compressor, defroster of refrigerant circuit, and refrigerant unit |
US11/896,346 US7762792B2 (en) | 2001-09-27 | 2007-08-31 | Compressor |
KR1020080067907A KR100892839B1 (en) | 2001-09-27 | 2008-07-14 | Closed type electric compressor |
KR1020080067904A KR100862822B1 (en) | 2001-09-27 | 2008-07-14 | Rotary compressor |
KR1020080067906A KR20080071956A (en) | 2001-09-27 | 2008-07-14 | Rotary compressor |
KR1020080067910A KR100892840B1 (en) | 2001-09-27 | 2008-07-14 | Compressor |
KR1020080067905A KR100892838B1 (en) | 2001-09-27 | 2008-07-14 | Rotary compressor |
KR1020080067919A KR20080071961A (en) | 2001-09-27 | 2008-07-14 | Refrigeration unit |
KR1020080067914A KR20080071959A (en) | 2001-09-27 | 2008-07-14 | Compressor |
KR1020080067917A KR100892841B1 (en) | 2001-09-27 | 2008-07-14 | Defroster of refrigerant circuit |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2001323769A JP2003129981A (en) | 2001-10-22 | 2001-10-22 | Rotary compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
JP2003129981A true JP2003129981A (en) | 2003-05-08 |
Family
ID=19140610
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2001323769A Pending JP2003129981A (en) | 2001-09-27 | 2001-10-22 | Rotary compressor |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2003129981A (en) |
-
2001
- 2001-10-22 JP JP2001323769A patent/JP2003129981A/en active Pending
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