JP2003222091A - Multistage compression type rotary compressor - Google Patents
Multistage compression type rotary compressorInfo
- Publication number
- JP2003222091A JP2003222091A JP2002021338A JP2002021338A JP2003222091A JP 2003222091 A JP2003222091 A JP 2003222091A JP 2002021338 A JP2002021338 A JP 2002021338A JP 2002021338 A JP2002021338 A JP 2002021338A JP 2003222091 A JP2003222091 A JP 2003222091A
- Authority
- JP
- Japan
- Prior art keywords
- compression element
- pressure
- rotary compression
- discharge
- rotary
- 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.)
- Granted
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、第１の回転圧縮要
素で圧縮されて吐出された冷媒ガスを第２の回転圧縮要
素に吸引し、圧縮して吐出する多段圧縮式ロータリコン
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 multi-stage compression type rotary compressor which sucks a refrigerant gas compressed by a first rotary compression element and discharged into a second rotary compression element, and compresses and discharges the refrigerant gas. is there.
【０００２】[0002]
【従来の技術】従来この種の多段圧縮式ロータリコンプ
レッサ、特に内部中間圧型多段圧縮式ロータリコンプレ
ッサでは、第１の回転圧縮要素の吸込ポートから冷媒ガ
スがシリンダ内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
側より吐出ポート、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の回転圧縮要素の吸込ポートからシリンダの低圧室
側に吸入され、ローラとベーンの回転により２段目の圧
縮が行われて高温高圧の冷媒ガスとなり、高圧室側より
吐出ポート、吐出消音室を経て外部の放熱器に流入する
構成とされている。2. Description of the Related Art Conventionally, in a multi-stage compression type rotary compressor of this type, particularly in an internal intermediate pressure type multi-stage compression type rotary compressor, a refrigerant gas is sucked from a suction port of a first rotary compression element to a low pressure chamber side in a cylinder, Then, it is compressed by the operation of the vane and becomes an intermediate pressure, and is discharged from the high pressure chamber side of the cylinder into the closed container through the discharge port and the discharge muffling chamber. Then, the intermediate-pressure refrigerant gas in the closed container is sucked into the low-pressure chamber side of the cylinder from the suction port of the second rotary compression element, and the second stage compression is performed by the rotation of the roller and the vane, so that high-temperature high-pressure It becomes a refrigerant gas, and is configured to flow from the high-pressure chamber side into the external radiator via the discharge port and the discharge muffling chamber.
【０００３】係る多段圧縮式ロータリコンプレッサにお
いて、第１及び第２の回転圧縮要素の吐出消音室には、
シリンダ内で圧縮されて吐出消音室に吐出された冷媒の
逆流を防ぐために吐出弁が設けられており、この吐出弁
により吐出ポートが開閉される。In such a multi-stage compression rotary compressor, the discharge muffling chambers of the first and second rotary compression elements include:
A discharge valve is provided to prevent backflow of the refrigerant compressed in the cylinder and discharged to the discharge muffling chamber, and the discharge valve opens and closes the discharge port.
【０００４】ここで、高低圧差の大きい冷媒、例えば二
酸化炭素を冷媒として用いた場合、吐出冷媒圧力は図８
に示すように高圧ＨＰとなる第２の回転圧縮要素で１２
ＭＰａＧ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ＭＰ）となる（第１の回転圧縮
要素の吸入圧力ＬＰは４ＭＰａＧ）。その結果、２段目
の段差圧（第２の回転圧縮要素の吸入圧力ＭＰと第２の
回転圧縮要素の吐出圧力ＨＰの差）は４ＭＰａＧと大き
くなる。また、外気温が低く冷媒の蒸発温度が低くなる
と第１の回転圧縮要素の回転圧縮要素の吐出圧力ＭＰが
低くなってしまうため、２段目の段差圧（第２の回転圧
縮要素の吸入圧力ＭＰと第２の回転圧縮要素の吐出圧力
ＨＰ）がさらに大きくなる。Here, when a refrigerant having a large difference in high pressure and low pressure, for example, carbon dioxide is used as the refrigerant, the discharge refrigerant pressure is as shown in FIG.
The second rotary compression element that produces high pressure HP as shown in
The pressure reaches 8 MPaG (intermediate pressure MP) at the first rotary compression element on the low stage side (the suction pressure LP of the first rotary compression element is 4 MPaG). As a result, the step pressure of the second stage (difference between the suction pressure MP of the second rotary compression element and the discharge pressure HP of the second rotary compression element) increases to 4 MPaG. Further, when the outside air temperature is low and the evaporation temperature of the refrigerant is low, the discharge pressure MP of the rotary compression element of the first rotary compression element becomes low, so the step pressure of the second stage (the suction pressure of the second rotary compression element). MP and the discharge pressure HP of the second rotary compression element are further increased.
【０００５】[0005]
【発明が解決しようとする課題】このように２段目の段
差圧が大きくなると、第２の回転圧縮要素の吐出弁内外
の圧力差が過大となり、この圧力差によって第２の回転
圧縮要素の吐出弁等が破損してしまう問題があった。When the step pressure of the second stage becomes large in this way, the pressure difference between the inside and the outside of the discharge valve of the second rotary compression element becomes excessive, and this pressure difference causes the second rotary compression element to move. There was a problem that the discharge valve etc. was damaged.
【０００６】本発明は、係る技術的課題を解決するため
に成されたものであり、２段目の段差圧によって生じる
第２の回転圧縮要素の吐出弁等の破損故障を未然に回避
することができる多段圧縮式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 above technical problem, and avoids damage to the discharge valve of the second rotary compression element caused by the step pressure of the second stage. An object of the present invention is to provide a multi-stage compression rotary compressor capable of achieving the above.
【０００７】[0007]
【課題を解決するための手段】即ち、本発明では密閉容
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
縮された中間圧の冷媒ガスを第２の回転圧縮要素に吸引
し、圧縮して吐出するものであって、第１の回転圧縮要
素で圧縮された中間圧の冷媒ガスの通過経路と第２の回
転圧縮要素の冷媒吐出側とを連通する連通路と、この連
通路を開閉する弁装置とを備え、当該弁装置は、中間圧
の冷媒ガスと第２の回転圧縮要素の冷媒吐出側の冷媒ガ
スとの圧力差が所定の上限値以上になった場合、連通路
を開放するようにしたので、第２の回転圧縮要素の吐出
圧力と吸込圧力との圧力差、即ち、２段目の段差圧を所
定の上限値より低く抑えることができるようになる。That is, according to the present invention, an electric element and first and second rotary compression elements driven by the electric element are provided in a closed container, and compression is performed by the first rotary compression element. The intermediate pressure refrigerant gas is sucked into the second rotary compression element, compressed and discharged, and the intermediate pressure refrigerant gas compressed by the first rotary compression element passes through the second rotary compression element and the second rotary compression element. The rotary compression element includes a communication passage that communicates with the refrigerant discharge side of the rotary compression element, and a valve device that opens and closes the communication passage. The valve device includes an intermediate pressure refrigerant gas and a refrigerant discharge side refrigerant of the second rotary compression element. When the pressure difference with the gas exceeds the predetermined upper limit value, the communication passage is opened. Therefore, the pressure difference between the discharge pressure and the suction pressure of the second rotary compression element, that is, the second step The pressure can be suppressed below a predetermined upper limit value.
【０００８】これにより、第２の回転圧縮要素の吐出弁
の破損等の故障発生を未然に回避することができるよう
になるものである。As a result, it is possible to avoid occurrence of a failure such as breakage of the discharge valve of the second rotary compression element.
【０００９】請求項２の発明では上記に加えて、第２の
回転圧縮要素を構成するシリンダと、このシリンダ内で
圧縮された冷媒ガスを吐出する吐出消音室とを備え、第
１の回転圧縮要素で圧縮された中間圧の冷媒ガスを密閉
容器内に吐出し、第２の回転圧縮要素はこの密閉容器内
の中間圧の冷媒ガスを吸引すると共に、連通路は吐出消
音室を画成する壁内に形成して密閉容器内と吐出消音室
とを連通し、弁装置は前記壁内に設けているので、第１
の回転圧縮要素で圧縮された中間圧の冷媒ガスの通過経
路と第２の回転圧縮要素の冷媒吐出側とを連通する連通
路、及び、連通路を開閉する弁装置を第２の回転圧縮要
素の壁内に集約することができるようになる。In addition to the above, the second aspect of the present invention is provided with a cylinder that constitutes a second rotary compression element, and a discharge muffling chamber that discharges the refrigerant gas compressed in this cylinder. The intermediate pressure refrigerant gas compressed by the element is discharged into the closed container, the second rotary compression element sucks the intermediate pressure refrigerant gas in the closed container, and the communication passage defines the discharge muffling chamber. Since the valve device is formed inside the wall to communicate the inside of the closed container with the discharge silencing chamber, and the valve device is provided inside the wall,
The second rotary compression element includes a communication passage that communicates the passage of the intermediate-pressure refrigerant gas compressed by the rotary compression element with the refrigerant discharge side of the second rotary compression element, and a valve device that opens and closes the communication passage. Will be able to be integrated into the walls of.
【００１０】これにより、構造の簡素化と全体寸法の小
型化を実現することができるようになるものである。As a result, the structure can be simplified and the overall size can be reduced.
【００１１】[0011]
【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は本発明の多段圧縮式ロータリコン
プレッサの実施例として、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（２段）圧縮式ロ
ータリコンプレッサの縦断面図である。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will now be described in detail with reference to the drawings. FIG. 1 is a vertical sectional view of an internal intermediate pressure type multi-stage (two-stage) compression rotary compressor provided with first and second rotary compression elements 32 and 34 as an embodiment of the multi-stage compression rotary compressor of the present invention.
【００１２】図１において、１０は二酸化炭素を冷媒と
する内部中間圧型多段圧縮式ロータリコンプレッサで、
この多段圧縮式ロータリコンプレッサ１０は、鋼板から
なる円筒状の容器本体１２Ａ、及びこの容器本体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とで形成される密閉容器１２と、この密閉容器１
２の容器本体１２Ａの内部空間の上側に配置収納された
電動要素１４と、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とにより構成さ
れている。尚、密閉容器１２は底部をオイル溜めとす
る。また、前記エンドキャップ１２Ｂの上面中心には円
形の取付孔１２Ｄが形成され、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。In FIG. 1, reference numeral 10 denotes an internal intermediate pressure type multi-stage compression rotary compressor using carbon dioxide as a refrigerant,
The multi-stage compression rotary compressor 10 includes a cylindrical container body 12A made of a steel plate and the container body 12A.
Bowl-shaped end cap (lid) that closes the upper opening of the
12B and a closed container 12, and this closed container 1
The electric element 14 arranged and housed above the inner space of the container body 12A of No. 2 and arranged below the electric element 14.
A first rotary compression element 32 (first stage) and a second rotary compression element 34 driven by the rotary shaft 16 of the electric element 14.
(Second stage) and the rotary compression mechanism portion 18. The closed container 12 has an oil reservoir at the bottom. A circular mounting hole 12D is formed at 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.
【００１３】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の内側に若干の間隔を設けて挿入
設置されたロータ２４とからなる。そして、このロータ
２４には鉛直方向に延びる回転軸１６が固定されてい
る。The electric element 14 has 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 installed inside the stator 22 with a slight gap. The rotary shaft 16 extending in the vertical direction is fixed to the rotor 24.
【００１４】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）方式によって巻装されたステータコイル
２８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３
０内に永久磁石ＭＧを挿入して形成されている。The stator 22 has a laminated body 26 in which donut-shaped electromagnetic steel sheets are laminated, and a stator coil 28 wound around the teeth of the laminated body 26 by a direct winding (concentrated winding) method. Similarly to the stator 22, the rotor 24 is also formed of a laminated body 30 of electromagnetic steel plates.
It is formed by inserting a permanent magnet MG into the zero.
【００１５】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１の回転圧縮要素３２と第２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、シリンダ４０と、この上
下シリンダ３８、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４
６、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上下ベーン５０、５２
と、上シリンダ３８の上側の開口面及び下シリンダ４０
の下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及び下部支持部材
５６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 first rotary compression element 32 and the second rotary compression element 34 include an intermediate partition plate 36, cylinders 38 and cylinders 40 arranged above and below the intermediate partition plate 36, and inside the upper and lower cylinders 38 and 40. And the upper and lower rollers 46 and 48 which are fitted to the upper and lower eccentric portions 42 and 44 provided on the rotary shaft 16 with a phase difference of 180 degrees and rotate eccentrically.
Upper and lower vanes 50, 52 that abut the upper and lower cylinders 38, 40 by abutting the upper and lower cylinders 48, respectively
And the upper opening surface of the upper cylinder 38 and the lower cylinder 40.
The lower opening surface is closed, and the upper support member 54 and the lower support member 56 function as support members that also serve as bearings for the rotary shaft 16.
【００１６】また、図４乃至図７に示す如く、上部支持
部材５４及び下部支持部材５６には、吸込ポート１６
１、１６２にて上下シリンダ３８、４０の内部とそれぞ
れ連通する吸込通路５８、６０と、上部支持部材５４及
び下部支持部材５６の凹陥部を壁としてのカバーによっ
て閉塞することにより形成された吐出消音室６２、６４
とが設けられている。即ち、吐出消音室６２は吐出消音
室６２を画成する壁としての上部カバー６６、吐出消音
室６４は吐出消音室６４を画成する壁としての下部カバ
ー６８にて閉塞される。Further, as shown in FIGS. 4 to 7, the suction port 16 is provided in the upper support member 54 and the lower support member 56.
The discharge muffling formed by closing the suction passages 58 and 60 communicating with the insides of the upper and lower cylinders 38 and 40, respectively, and the recessed portions of the upper support member 54 and the lower support member 56 with a cover as a wall. Chamber 62, 64
And are provided. That is, the discharge silencing chamber 62 is closed by an upper cover 66 as a wall defining the discharge silencing chamber 62, and the discharge silencing chamber 64 is closed by a lower cover 68 as a wall defining the discharge silencing chamber 64.
【００１７】この場合、上部支持部材５４の中央には軸
受け５４Ａが起立形成されている。また、下部支持部材
５６の中央には軸受け５６Ａが貫通形成されており、回
転軸１６は上部支持部材５４の軸受け５４Ａと下部支持
部材５６の軸受け５６Ａに保持されている。In this case, a bearing 54A is formed upright in the center of the upper support member 54. A bearing 56A is formed through the center of the lower support member 56, and the rotary shaft 16 is held by the bearing 54A of the upper support member 54 and the bearing 56A of the lower support member 56.
【００１８】また、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、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を画成す
るもので、これは周辺部の主ボルト１２９・・・によっ
て下から下部支持部材５６に固定され、この主ボルト１
２９・・・の先端は上部支持部材５４に螺合する。図４
は下部支持部材５６の下面を示しており、１２８は吐出
消音室６４内において吐出ポート４１を開閉する第１の
回転圧縮要素３２の吐出弁である。The lower cover 68 is made of a donut-shaped circular steel plate, and defines a discharge muffling chamber 64 which communicates with the inside of the lower cylinder 40 of the first rotary compression element 32, and this surrounds the peripheral portion. Is fixed to the lower support member 56 from below by the main bolts 129 ...
The tips of 29 ... Are screwed into the upper support member 54. Figure 4
Shows the lower surface of the lower support member 56, and 128 is the discharge valve of the first rotary compression element 32 that opens and closes the discharge port 41 in the discharge muffling chamber 64.
【００１９】そして、第１の回転圧縮要素３２の吐出消
音室６４と密閉容器１２内とは連通路にて連通してお
り、この連通路は上部カバー６６、上下シリンダ３８、
４０、中間仕切板３６を貫通する図示しない孔である。
この場合、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１２１から密閉容器１２内に
中間圧の冷媒が吐出される。The discharge muffling chamber 64 of the first rotary compression element 32 and the inside of the hermetically sealed container 12 communicate with each other through a communication passage, which communicates with the upper cover 66, the upper and lower cylinders 38,
40, a hole (not shown) penetrating the intermediate partition plate 36.
In this case, an intermediate discharge pipe 121 is provided upright on the upper end of the communication passage, and the intermediate-pressure refrigerant is discharged from the intermediate discharge pipe 121 into the closed container 12.
【００２０】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内部と吐出ポート３９にて連通
する吐出消音室６２を画成し、この上部カバー６６の上
側には、上部カバー６６と所定間隔を存して、電動要素
１４が設けられている。当該上部カバー６６は、図５に
示す如く前記上部支持部材５４の軸受け５４Ａが貫通す
る孔が形成された略ドーナッツ状の円形鋼板から構成さ
れており、周辺部が主ボルト７８・・・により固定され
ている。このため、この主ボルト７８・・・の先端は下
部支持部材５６に螺合するものである。尚、図５におい
て１２７は吐出消音室６２内において吐出ポート３９を
開閉する第２の回転圧縮要素３４の吐出弁である。Further, the upper cover 66 defines a discharge muffling chamber 62 which communicates with the inside of the upper cylinder 38 of the second rotary compression element 34 at the discharge port 39. Above the upper cover 66, the upper cover 66 is provided. The electric element 14 is provided at a predetermined interval. As shown in FIG. 5, the upper cover 66 is made of a substantially donut-shaped circular steel plate having a hole through which the bearing 54A of the upper support member 54 passes, and its peripheral portion is fixed by main bolts 78 ... Has been done. Therefore, the tips of the main bolts 78 ... Are screwed into the lower support member 56. In FIG. 5, reference numeral 127 is a discharge valve of the second rotary compression element 34 that opens and closes the discharge port 39 in the discharge muffling chamber 62.
【００２１】ここで、吐出弁１２７、１２８は縦長略矩
形状の金属板からなる弾性部材にて構成されており、吐
出弁１２７、１２８の一側は吐出ポート３９、４１に当
接して密閉すると共に、他側は吐出ポート３９、４１と
所定の間隔を存して設けられた図示しないネジで固定さ
れている。吐出弁１２７、１２８は、吐出ポート３９、
４１に一定の付勢力で当接し、弾性力で吐出ポート３
９、４１を開閉可能に閉塞する。Here, the discharge valves 127 and 128 are composed of elastic members made of a vertically elongated substantially rectangular metal plate, and one side of the discharge valves 127 and 128 is brought into contact with the discharge ports 39 and 41 to seal them. At the same time, the other side is fixed to the discharge ports 39 and 41 with a screw (not shown) provided at a predetermined interval. The discharge valves 127 and 128 are the discharge ports 39,
41 is contacted with a constant biasing force, and the discharge port 3 is elastically pressed.
9 and 41 are closed so that they can be opened and closed.
【００２２】また、第２の回転圧縮要素３４の上部カバ
ー６６内には、本発明の連通路２００が設けられてい
る。当該連通路２００は、第１の回転圧縮要素３２で圧
縮された中間圧の冷媒ガスの通過経路である密閉容器１
２内と第２の回転圧縮要素の冷媒吐出側の吐出消音室６
２とを連通する通路であり、図２に示すように水平に延
在する第１の通路２０１の一端が密閉容器１２内に連通
しており、第１の通路２０１の他端は弁装置収納室２０
２に連通している。この弁装置収納室２０２は、上部カ
バー６６を鉛直方向に貫通する孔であり、弁装置収納室
２０２の上面は密閉容器１２に開口すると共に、下面は
吐出消音室６２に開口している。また、この弁装置収納
室２０２の上下開口はそれぞれ封止材２０３、２０４に
より塞がれている。In the upper cover 66 of the second rotary compression element 34, the communication passage 200 of the present invention is provided. The communication passage 200 is a closed container 1 that is a passage for the intermediate-pressure refrigerant gas compressed by the first rotary compression element 32.
A discharge muffling chamber 6 in the inside of 2 and on the refrigerant discharge side of the second rotary compression element
2, a first passage 201 that extends horizontally as shown in FIG. 2 communicates with the inside of the closed container 12, and the other end of the first passage 201 accommodates the valve device. Room 20
It communicates with 2. The valve device storage chamber 202 is a hole that penetrates the upper cover 66 in the vertical direction, and the upper surface of the valve device storage chamber 202 is open to the closed container 12 and the lower surface is opened to the discharge muffling chamber 62. The upper and lower openings of the valve device housing chamber 202 are closed by sealing materials 203 and 204, respectively.
【００２３】そして、弁装置収納室２０２の下部に設け
られた封止材２０４には、弁装置収納室２０２と吐出消
音室６２とを連通する第２の通路２０５が設けられてい
る。これら第１の通路２０１、弁装置収納室２０２及び
第２の通路２０５によって連通路２００が構成される。
更に、この連通路２００の弁装置収納室２０２内には球
状の弁装置２０７が収納されており、この弁装置２０７
の上面には伸縮自在なスプリング２０６（付勢部材）の
一端が当接して設けられている。このスプリング２０６
の他端は、上側の封止材２０３に固定され、弁装置２０
７は係るスプリング２０６により常時下側に向けて付勢
され、常には第２の通路２０５を閉塞している。A second passage 205 that connects the valve device housing chamber 202 and the discharge muffling chamber 62 is provided in the sealing material 204 provided in the lower portion of the valve device housing chamber 202. The first passage 201, the valve device accommodating chamber 202, and the second passage 205 form a communication passage 200.
Further, a spherical valve device 207 is housed in the valve device housing chamber 202 of the communication passage 200.
One end of an elastic spring 206 (biasing member) is provided in contact with the upper surface of the. This spring 206
The other end of the valve device 20 is fixed to the upper sealing material 203 and
7 is always urged downward by the spring 206, and normally closes the second passage 205.
【００２４】更に、密閉容器１２内の中間圧の冷媒が第
１の通路２０１から弁装置収納室２０２内に流入し、弁
装置２０７を下側に向けて付勢すると共に、吐出消音室
６２内の高圧の冷媒が下側の封止材２０４に設けられた
第２の通路２０５から弁装置収納室２０２内に流入して
弁装置２０７の下面から弁装置２０７を上側に向けて付
勢する構造とされている。Further, the intermediate pressure refrigerant in the closed container 12 flows from the first passage 201 into the valve device accommodating chamber 202, urges the valve device 207 downward, and the discharge silencer chamber 62. The high-pressure refrigerant flows into the valve device housing chamber 202 from the second passage 205 provided in the lower sealing material 204, and urges the valve device 207 upward from the lower surface of the valve device 207. It is said that.
【００２５】このように弁装置２０７は、スプリング２
０６が当接する側、即ち上側から中間圧の冷媒ガスとス
プリング２０６により下側に向けて付勢され、反対側か
らは高圧の冷媒ガスにより上側に向けて付勢される。そ
して、常には弁装置２０７の下面は第２の通路２０５に
当接して密閉しており、これによって連通路２００は弁
装置２０７により閉塞されている。As described above, the valve device 207 has the spring 2
06 is urged downward from the contacting side, that is, from the upper side by the intermediate pressure refrigerant gas and the spring 206, and from the opposite side by the high pressure refrigerant gas toward the upper side. The lower surface of the valve device 207 is always in contact with the second passage 205 and is hermetically sealed, whereby the communication passage 200 is closed by the valve device 207.
【００２６】尚、スプリング２０６の付勢力は、密閉容
器１２内の中間圧の冷媒ガスと吐出消音室６２内の高圧
の冷媒ガスの圧力差が上限値である例えば８ＭＰａＧに
達した場合に、第１の通路２０５に当接して密閉してい
た弁装置２０７が第２の通路２０５から流入する高圧の
冷媒ガスにより上方に押し上げられるように設定されて
いるものとする。従って、上記圧力差が８ＭＰａＧ（上
限値）以上に開いた場合、弁装置収納室２０２を介して
第１の通路２０１と第２の通路２０５が連通し、吐出消
音室６２内の高圧の冷媒ガスが密閉容器１２内に流出す
る。そして、上記圧力差が８ＭＰａＧ未満まで縮まる
と、スプリング２０６は弁装置２０７を第２の通路２０
５に当接させて密閉し、第１の通路２０１と第２の通路
２０５は弁装置２０７によって塞がれることとなる。こ
れにより、２段目の段差圧が過大となることを未然に回
避する。The urging force of the spring 206 is the first when the pressure difference between the intermediate pressure refrigerant gas in the closed container 12 and the high pressure refrigerant gas in the discharge muffling chamber 62 reaches an upper limit value, for example, 8 MPaG. It is assumed that the valve device 207 that is in contact with and sealed in the first passage 205 is set to be pushed upward by the high-pressure refrigerant gas flowing from the second passage 205. Therefore, when the pressure difference is opened to 8 MPaG (upper limit value) or more, the first passage 201 and the second passage 205 communicate with each other through the valve device storage chamber 202, and the high pressure refrigerant gas in the discharge muffling chamber 62 is communicated. Flow out into the closed container 12. Then, when the pressure difference is reduced to less than 8 MPaG, the spring 206 causes the valve device 207 to move to the second passage 20.
5, the first passage 201 and the second passage 205 are closed by the valve device 207. This prevents the step pressure in the second step from becoming excessive.
【００２７】前述の如く冷媒としては地球環境にやさし
く、可燃性及び毒性等を考慮して自然冷媒である前記二
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。As described above, carbon dioxide (CO2) which is a natural refrigerant in consideration of flammability and toxicity is used as the refrigerant, and the oil as the lubricating oil is, for example, mineral oil (mineral oil). ), Alkylbenzene oil, ether oil, ester oil, and other existing oils are used.
【００２８】以上の構成で次に動作を説明する。ターミ
ナル２０及び図示されない配線を介して電動要素１４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１
６と一体に設けられた上下偏心部４２、４４に嵌合され
て上下ローラ４６、４８が上下シリンダ３８、４０内を
偏心回転する。Next, the operation of the above configuration will be described. When the stator coil 28 of the electric element 14 is energized via the terminal 20 and wiring (not shown), the electric element 14 is activated and the rotor 24 rotates. Rotation axis 1 by this rotation
The upper and lower rollers 46 and 48 are fitted in the upper and lower eccentric portions 42 and 44 integrally provided with the motor 6, and eccentrically rotate in the upper and lower cylinders 38 and 40.
【００２９】これにより、下部支持部材５６に形成され
た吸込通路６０を経由して図５に示すように吸込ポート
１６２から下シリンダ４０の低圧室側に吸入された低圧
の冷媒は、下ローラ４８と下ベーン５２の動作により圧
縮されて中間圧となり下シリンダ４０の高圧室側より吐
出ポート４１、下部支持部材５６に形成された吐出消音
室６４から図示しない連通路を経て中間吐出管１２１か
ら密閉容器１２内に吐出される。As a result, the low-pressure refrigerant 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 lower support member 56 as shown in FIG. And the operation of the lower vane 52 to become an intermediate pressure, which is sealed from the high pressure chamber side of the lower cylinder 40 from the discharge port 41 and the discharge muffling chamber 64 formed in the lower support member 56 through the communication passage (not shown) to the intermediate discharge pipe 121. It is discharged into the container 12.
【００３０】そして、密閉容器１２内の中間圧の冷媒ガ
スは、図示しない冷媒通路を通って、上部支持部材５４
に形成された吸込通路５８を経由して図７に示すように
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。吸入された中間圧の冷媒ガスは、上ローラ４６
と上べーン５２の動作により２段目の圧縮が行われて高
温高圧の冷媒ガスとなり、高圧室側から吐出ポート３９
を通り上部支持部材５４に形成された吐出消音室６２に
吐出される。The intermediate pressure refrigerant gas in the closed container 12 passes through a refrigerant passage (not shown) and passes through the upper support member 54.
As shown in FIG. 7, the air is sucked from the suction port 161 to the low pressure chamber side of the upper cylinder 38 via the suction passage 58 formed in the upper cylinder 38. The intermediate-pressure refrigerant gas that has been sucked in is transferred to the upper roller 46.
And the operation of the upper vane 52, the second stage compression is performed to form high-temperature high-pressure refrigerant gas, and the discharge port 39 is discharged from the high-pressure chamber side.
Is discharged to the discharge muffling chamber 62 formed in the upper support member 54.
【００３１】このとき、密閉容器１２内の中間圧の冷媒
ガスと吐出消音室６２内の高圧の冷媒ガスの圧力差が８
ＭＰａＧ未満であれば、前述の如く弁装置２０７は弁装
置収納室２０２内の第２の通路２０５に当接して密閉す
るため、連通路２００は開放されることなく、吐出消音
室６２に吐出された高圧の冷媒ガスは図示しない冷媒通
路を通って全て多段圧縮式ロータリコンプレッサ１０の
外部に設けられた図示しない放熱器に流入する。At this time, the pressure difference between the intermediate pressure refrigerant gas in the closed container 12 and the high pressure refrigerant gas in the discharge muffling chamber 62 is 8
If it is less than MPaG, the valve device 207 abuts and seals the second passage 205 in the valve device housing chamber 202 as described above, so that the communication passage 200 is discharged to the discharge muffling chamber 62 without being opened. The high-pressure refrigerant gas flows through a refrigerant passage (not shown) into a radiator (not shown) provided outside the multi-stage compression rotary compressor 10.
【００３２】放熱器に流入した冷媒はここで放熱して加
熱作用を発揮する。放熱器を出た冷媒は図示しない減圧
装置で減圧された後、これも図示しない蒸発器に入り、
そこで蒸発する。そして、最終的には第１の回転圧縮要
素３２の吸込通路６０に吸い込まれる循環を繰り返す。The refrigerant flowing into the radiator radiates heat here and exerts a heating effect. The refrigerant discharged from the radiator is decompressed by a decompression device (not shown), and then enters the evaporator (not shown).
There it evaporates. Then, finally, the circulation that is sucked into the suction passage 60 of the first rotary compression element 32 is repeated.
【００３３】ここで、外気温が低下して前記蒸発器にお
ける冷媒の蒸発温度が低くなると、前述の如く第１の回
転圧縮要素３２から密閉容器１２内に吐出される冷媒の
圧力（中間圧）も上がり難くなる。このようにして密閉
容器１２内の中間圧の冷媒ガスと吐出消音室６２内の高
圧の冷媒ガスの圧力差が８ＭＰａＧに達した場合、吐出
消音室６２内の圧力により第２の通路２０５に当接して
いる弁装置２０７はスプリング２０６に抗して押し上げ
られ、第２の通路２０５から離れるため、第１の通路２
０１と第２の通路２０５が連通し、高圧の冷媒ガスが中
間圧側の密閉容器１２内に流れ込む。そして、両者の圧
力差が８ＭＰａＧ未満まで低下すると、弁装置２０７は
第２の通路２０５に当接して密閉し、これにより第２の
通路２０５は弁装置２０７により塞がれる。Here, when the outside air temperature decreases and the evaporation temperature of the refrigerant in the evaporator decreases, the pressure (intermediate pressure) of the refrigerant discharged from the first rotary compression element 32 into the closed container 12 as described above. Is also difficult to rise. In this way, when the pressure difference between the medium pressure refrigerant gas in the closed container 12 and the high pressure refrigerant gas in the discharge muffling chamber 62 reaches 8 MPaG, the pressure in the discharge muffling chamber 62 causes the second passage 205 to contact. The valve device 207 in contact with the first passage 2 is pushed up against the spring 206 and is separated from the second passage 205.
01 and the second passage 205 communicate with each other, and the high-pressure refrigerant gas flows into the closed container 12 on the intermediate pressure side. Then, when the pressure difference between the two decreases to less than 8 MPaG, the valve device 207 abuts and seals the second passage 205, whereby the second passage 205 is closed by the valve device 207.
【００３４】このように、密閉容器１２内に電動要素１
４と、この電動要素１４にて駆動される第１及び第２の
回転圧縮要素３２、３４を備え、第１の回転圧縮要素３
２で圧縮された中間圧の冷媒ガスを第２の回転圧縮要素
３４に吸引し、圧縮して吐出するものであって、第１の
回転圧縮要素３２で圧縮された中間圧の冷媒ガスの通過
経路と第２の回転圧縮要素３４の冷媒吐出側とを連通す
る連通路２００と、この連通路２００を開閉する弁装置
２０７とを備え、当該弁装置２０７は、中間圧の冷媒ガ
スと第２の回転圧縮要素３４の冷媒吐出側の冷媒ガスと
の圧力差が所定の上限値である８ＭＰａＧ以上になった
場合、連通路２００を開放するものとしているので、２
段目の段差圧を上限値より低く抑え、第２の回転圧縮要
素３４の吐出弁１２８の破損を未然に回避することがで
きるようになる。In this way, the electric element 1 is placed in the closed container 12.
4 and the first and second rotary compression elements 32, 34 driven by the electric element 14, and the first rotary compression element 3
The intermediate pressure refrigerant gas compressed in 2 is sucked into the second rotary compression element 34, compressed and discharged, and the intermediate pressure refrigerant gas compressed in the first rotary compression element 32 passes through. The communication device includes a communication passage 200 that connects the passage and the refrigerant discharge side of the second rotary compression element 34, and a valve device 207 that opens and closes the communication passage 200. The valve device 207 includes the intermediate-pressure refrigerant gas and the second refrigerant gas. When the pressure difference between the rotary compression element 34 and the refrigerant gas on the refrigerant discharge side becomes equal to or higher than the predetermined upper limit value of 8 MPaG, the communication passage 200 is supposed to be opened.
It is possible to prevent the step pressure of the second step from becoming lower than the upper limit value and to prevent the discharge valve 128 of the second rotary compression element 34 from being damaged.
【００３５】また、第２の回転圧縮要素３４を構成する
上シリンダ３８と、この上シリンダ３８内で圧縮された
冷媒ガスを吐出する吐出消音室６２と、この吐出消音室
６２を画成する壁としての上部カバー６６とを備え、連
通路２００は上部カバー６６内に形成され、密閉容器１
２内と吐出消音室６２とを連通すると共に、弁装置２０
７は上部カバー６６内に設けているので、連通路２００
を複雑な構造とすることなく、２段目の段差圧を抑える
ことができるようになる。An upper cylinder 38 constituting the second rotary compression element 34, a discharge muffling chamber 62 for discharging the refrigerant gas compressed in the upper cylinder 38, and a wall defining the discharge muffling chamber 62. And a communication path 200 is formed in the upper cover 66.
2 and the discharge muffling chamber 62 are communicated with each other, and the valve device 20
7 is provided in the upper cover 66, the communication passage 200
It becomes possible to suppress the step pressure of the second step without having a complicated structure.
【００３６】実施例はいずれも回転軸１６を縦置型とし
た多段圧縮式ロータリコンプレッサ１０について説明し
たが、この発明は回転軸を横置型とした多段圧縮式ロー
タリコンプレッサにも適応できることは言うまでもな
い。In each of the embodiments, the multistage compression rotary compressor 10 in which the rotary shaft 16 is arranged vertically is explained, but it goes without saying that the present invention can be applied to the multistage compression rotary compressor in which the rotary shaft 16 is arranged horizontally.
【００３７】また、多段圧縮式ロータリコンプレッサを
第１及び第２の回転圧縮要素を備えた２段圧縮式ロータ
リコンプレッサで説明したが、これに限らず回転圧縮要
素を３段、４段或いはそれ以上の回転圧縮要素を備えた
多段圧縮式ロータリコンプレッサに適応しても差し支え
ない。Although the multi-stage compression rotary compressor has been described as the two-stage compression rotary compressor having the first and second rotary compression elements, it is not limited to this, and the rotary compression elements may be three stages, four stages or more. The present invention can be applied to a multi-stage compression type rotary compressor including the rotary compression element.
【００３８】尚、実施例では弁装置２０７を球状の弁装
置としたが、これに限らず、図３に示すような円筒状の
弁装置２１７としても差し支えない。この場合、弁装置
２１７は弁装置収納室２０２の壁面に当接し密閉するよ
うに設けられており、通常、第１の通路２０１と第２の
通路２０５の間の弁装置収納室２０２内に位置して、連
通路２００を閉塞している。そして、圧力差が８ＭＰａ
Ｇを越えた場合、弁装置２１７が第１の通路２０１の上
方に押し上げられることにより第１の通路２０１と第２
の通路２０５が連通し、高圧の冷媒ガスが中間圧の密閉
容器１２内に流れ込む。そして、両者の圧力差が８ＭＰ
ａＧ未満になると弁装置２１７は第１の通路２０１の下
方に戻り、第１の通路２０１と第２の通路２０５は弁装
置２１７により塞がれる。Although the valve device 207 is a spherical valve device in the embodiment, the invention is not limited to this, and a cylindrical valve device 217 as shown in FIG. 3 may be used. In this case, the valve device 217 is provided so as to come into contact with the wall surface of the valve device housing chamber 202 to be hermetically sealed, and is normally located in the valve device housing chamber 202 between the first passage 201 and the second passage 205. Then, the communication passage 200 is closed. And the pressure difference is 8 MPa
When G is exceeded, the valve device 217 is pushed up above the first passage 201 so that the first passage 201 and the second passage 201
Passage 205 communicates with each other, and high-pressure refrigerant gas flows into the intermediate-pressure closed container 12. And the pressure difference between both is 8MP
When it becomes less than aG, the valve device 217 returns to the lower side of the first passage 201, and the first passage 201 and the second passage 205 are closed by the valve device 217.
【００３９】[0039]
【発明の効果】以上詳述した如く本発明によれば、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
圧縮された中間圧の冷媒ガスを第２の回転圧縮要素に吸
引し、圧縮して吐出するものであって、第１の回転圧縮
要素で圧縮された中間圧の冷媒ガスの通過経路と第２の
回転圧縮要素の冷媒吐出側とを連通する連通路と、この
連通路を開閉する弁装置とを備え、当該弁装置は、中間
圧の冷媒ガスと第２の回転圧縮要素の冷媒吐出側の冷媒
ガスとの圧力差が所定の上限値以上になった場合、連通
路を開放するようにしたので、第２の回転圧縮要素の吐
出圧力と吸込圧力との圧力差、即ち、２段目の段差圧を
所定の上限値より低く抑えることができるようになる。As described above in detail, according to the present invention, the electric element in the closed container and the first element driven by the electric element are provided.
And a second rotary compression element, which sucks the intermediate-pressure refrigerant gas compressed by the first rotary compression element into the second rotary compression element, compresses it, and discharges it. A communication passage that communicates the passage of the intermediate-pressure refrigerant gas compressed by the compression element with the refrigerant discharge side of the second rotary compression element, and a valve device that opens and closes the communication passage. When the pressure difference between the intermediate pressure refrigerant gas and the refrigerant gas on the refrigerant discharge side of the second rotary compression element exceeds a predetermined upper limit value, the communication passage is opened. The pressure difference between the discharge pressure and the suction pressure, that is, the step pressure of the second step can be suppressed below a predetermined upper limit value.
【００４０】これにより、第２の回転圧縮要素の吐出弁
の破損等の故障発生を未然に回避することができるよう
になるものである。As a result, it becomes possible to avoid occurrence of a failure such as breakage of the discharge valve of the second rotary compression element.
【００４１】請求項２の発明によれば、上記に加えて第
２の回転圧縮要素を構成するシリンダと、このシリンダ
内で圧縮された冷媒ガスを吐出する吐出消音室とを備
え、第１の回転圧縮要素で圧縮された中間圧の冷媒ガス
を密閉容器内に吐出し、第２の回転圧縮要素はこの密閉
容器内の中間圧の冷媒ガスを吸引すると共に、連通路は
吐出消音室を画成する壁内に形成して密閉容器内と吐出
消音室とを連通し、弁装置は前記壁内に設けているの
で、第１の回転圧縮要素で圧縮された中間圧の冷媒ガス
の通過経路と第２の回転圧縮要素の冷媒吐出側とを連通
する連通路、及び、連通路を開閉する弁装置を第２の回
転圧縮要素のカバー内に集約することができるようにな
る。According to the second aspect of the present invention, in addition to the above, a cylinder forming a second rotary compression element, and a discharge muffling chamber for discharging the refrigerant gas compressed in this cylinder are provided, and the first The intermediate-pressure refrigerant gas compressed by the rotary compression element is discharged into the closed container, the second rotary compression element sucks the intermediate-pressure refrigerant gas inside the closed container, and the communication passage defines the discharge muffling chamber. Since the valve device is formed in the closed wall to connect the inside of the closed container and the discharge silencing chamber, and the valve device is provided in the wall, the passage of the intermediate-pressure refrigerant gas compressed by the first rotary compression element. The communication passage that communicates with the refrigerant discharge side of the second rotary compression element and the valve device that opens and closes the communication passage can be integrated in the cover of the second rotary compression element.
【００４２】これにより、構造の簡素化と全体寸法の小
型化を実現することができるようになるものである。As a result, the structure can be simplified and the overall size can be reduced.
【図１】本発明の実施例の多段圧縮式ロータリコンプレ
ッサの縦断面図である。FIG. 1 is a vertical sectional view of a multi-stage compression rotary compressor according to an embodiment of the present invention.
【図２】図１の多段圧縮式ロータリコンプレッサの第２
の回転圧縮要素の連通路部分の拡大断面図である。FIG. 2 is a second part of the multi-stage compression rotary compressor shown in FIG.
FIG. 3 is an enlarged cross-sectional view of a communication passage portion of the rotary compression element of FIG.
【図３】他の実施例の多段圧縮式ロータリコンプレッサ
の第２の回転圧縮要素の連通路部分の拡大断面図であ
る。FIG. 3 is an enlarged cross-sectional view of a communication passage portion of a second rotary compression element of a multi-stage compression rotary compressor of another embodiment.
【図４】図１の多段圧縮式ロータリコンプレッサの下部
支持部材支持部材の下面図である。4 is a bottom view of a lower support member support member of the multi-stage compression rotary compressor of FIG. 1. FIG.
【図５】図１の多段圧縮式ロータリコンプレッサの上部
支持部材及び上部カバーの上面図である。5 is a top view of an upper support member and an upper cover of the multi-stage compression rotary compressor of FIG. 1. FIG.
【図６】図１の多段圧縮式ロータリコンプレッサの下シ
リンダの下面図である。6 is a bottom view of a lower cylinder of the multi-stage compression rotary compressor of FIG. 1. FIG.
【図７】図１の多段圧縮式ロータリコンプレッサの下シ
リンダの下面図である。7 is a bottom view of the lower cylinder of the multi-stage compression rotary compressor of FIG. 1. FIG.
【図８】外気温度と各圧力の関係を示す図である。FIG. 8 is a diagram showing a relationship between outside air temperature and each pressure.
１０ 多段圧縮式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 ２２ ステータ ２４ ロータ ２６ 積層体 ２８ ステータコイル ３０ 積層体 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 ５４ 上部支持部材 ６２、６４ 吐出消音室 ６６ 上部カバー １２７、１２８ 吐出弁 ２００ 連通路 ２０１ 第１の通路 ２０２ 弁装置収納室 ２０３、２０４ 封止材 ２０５ 第２の通路 ２０６ スプリング ２０７ 弁装置 10 Multi-stage compression rotary compressor 12 airtight container 14 Electric elements 16 rotation axes 18 Rotary compression mechanism 20 terminals 22 Stator 24 rotor 26 laminate 28 Stator coil 30 stacks 32 First rotary compression element 34 Second rotary compression element 36 Intermediate partition plate 38, 40 cylinders 54 Upper support member 62, 64 Discharge muffler 66 Top cover 127, 128 discharge valve 200 passages 201 First passage 202 Valve device storage room 203,204 sealing material 205 second passage 206 spring 207 valve device
───────────────────────────────────────────────────── フロントページの続き (72)発明者 只野 昌也 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 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 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 Ｆターム(参考） 3H029 AA04 AA09 AA13 AB03 BB47 BB53 CC09 CC13 CC25 CC28 ─────────────────────────────────────────────────── ─── Continued front page (72) Inventor Masaya Tadano 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 Dai Matsuura 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. F-term (reference) 3H029 AA04 AA09 AA13 AB03 BB47 BB53 CC09 CC13 CC25 CC28
Claims (2)
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中間圧の冷媒ガスを前
記第２の回転圧縮要素に吸引し、圧縮して吐出する多段
圧縮式ロータリコンプレッサにおいて、 前記第１の回転圧縮要素で圧縮された中間圧の冷媒ガス
の通過経路と前記第２の回転圧縮要素の冷媒吐出側とを
連通する連通路と、該連通路を開閉する弁装置とを備
え、 該弁装置は、前記中間圧の冷媒ガスと前記第２の回転圧
縮要素の冷媒吐出側の冷媒ガスとの圧力差が所定の上限
値以上になった場合、前記連通路を開放することを特徴
とする多段圧縮式ロータリコンプレッサ。1. A hermetically sealed container comprising an electric element and first and second rotary compression elements driven by the electric element, wherein an intermediate pressure refrigerant gas compressed by the first rotary compression element is provided. A multi-stage compression rotary compressor that sucks into the second rotary compression element, compresses and discharges the medium, and a passage path of the intermediate-pressure refrigerant gas compressed by the first rotary compression element and the second rotary compression element. And a valve device that opens and closes the communication passage, wherein the valve device includes the intermediate-pressure refrigerant gas and the refrigerant gas on the refrigerant discharge side of the second rotary compression element. The multi-stage compression rotary compressor, wherein the communication passage is opened when the pressure difference between the pressure and the pressure exceeds a predetermined upper limit value.
ンダと、 該シリンダ内で圧縮された冷媒ガスを吐出する吐出消音
室とを備え、 前記第１の回転圧縮要素で圧縮された中間圧の冷媒ガス
は前記密閉容器内に吐出され、前記第２の回転圧縮要素
は該密閉容器内の中間圧の冷媒ガスを吸引すると共に、 前記連通路は前記吐出消音室を画成する壁内に形成さ
れ、前記密閉容器内と吐出消音室とを連通し、前記弁装
置は前記壁内に設けられることを特徴とする請求項１の
多段圧縮式ロータリコンプレッサ。2. An intermediate pressure compressed by the first rotary compression element, comprising: a cylinder that constitutes the second rotary compression element; and a discharge muffling chamber that discharges a refrigerant gas compressed in the cylinder. Of the refrigerant gas is discharged into the closed container, the second rotary compression element sucks the intermediate-pressure refrigerant gas in the closed container, and the communication passage is inside the wall that defines the discharge silencing chamber. 2. The multi-stage compression rotary compressor according to claim 1, wherein the multi-stage compression type rotary compressor is formed so as to communicate the inside of the closed container and the discharge silencing chamber, and the valve device is provided inside the wall.
Priority Applications (16)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002021338A JP3762708B2 (en) | 2002-01-30 | 2002-01-30 | Multistage rotary compressor |
| CN 200610006025 CN1807896B (en) | 2001-11-30 | 2002-08-28 | Multi-stage compression type rotary compressor |
| CN 200610006023 CN1807895B (en) | 2001-11-30 | 2002-08-28 | Multistage compression type rotary compressor |
| CN02142300A CN1423055A (en) | 2001-11-30 | 2002-08-28 | Revolving compressor, its manufacturing method and defrosting device using said compressor |
| TW91123073A TW564289B (en) | 2001-11-30 | 2002-10-07 | Multiple stage compression type rotary compressor and method for making same |
| EP02257800A EP1316730A3 (en) | 2001-11-30 | 2002-11-13 | Rotary compressor |
| US10/305,775 US6892454B2 (en) | 2001-11-30 | 2002-11-27 | Rotary compressor, method for manufacturing the same, and defroster for refrigerant circuit |
| KR1020020075257A KR100893464B1 (en) | 2001-11-30 | 2002-11-29 | Multi-stage compression type rotary compressor manufacturing method |
| US10/916,273 US7008199B2 (en) | 2001-11-30 | 2004-08-11 | Rotary compressor, method for manufacturing the same, and defroster for refrigerant circuit |
| US10/916,272 US7101161B2 (en) | 2001-11-30 | 2004-08-11 | Rotary compressor, method for manufacturing the same, and defroster for refrigerant circuit |
| US10/916,200 US7168257B2 (en) | 2001-11-30 | 2004-08-11 | Rotary compressor, method for manufacturing the same, and defroster for refrigerant circuit |
| US10/916,271 US6974314B2 (en) | 2001-11-30 | 2004-08-11 | Rotary compressor, method for manufacturing the same, and defroster for refrigerant circuit |
| KR1020080062256A KR100862825B1 (en) | 2001-11-30 | 2008-06-30 | Defroster of refrigerant circuit |
| KR1020080062250A KR100862824B1 (en) | 2001-11-30 | 2008-06-30 | Multi-stage compression type rotary compressor |
| KR1020080062187A KR100862823B1 (en) | 2001-11-30 | 2008-06-30 | Multi-stage compression type rotary compressor |
| KR1020080062188A KR20080066905A (en) | 2001-11-30 | 2008-06-30 | Multi-stage compression type rotary compressor manufacturing method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002021338A JP3762708B2 (en) | 2002-01-30 | 2002-01-30 | Multistage rotary compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2003222091A true JP2003222091A (en) | 2003-08-08 |
| JP3762708B2 JP3762708B2 (en) | 2006-04-05 |
Family
ID=27744608
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2002021338A Expired - Fee Related JP3762708B2 (en) | 2001-11-30 | 2002-01-30 | Multistage rotary compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3762708B2 (en) |
-
2002
- 2002-01-30 JP JP2002021338A patent/JP3762708B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JP3762708B2 (en) | 2006-04-05 |
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