JP2000171108A - Rotary compressor and refrigerating circuit using it - Google Patents
Rotary compressor and refrigerating circuit using itInfo
- Publication number
- JP2000171108A JP2000171108A JP10344367A JP34436798A JP2000171108A JP 2000171108 A JP2000171108 A JP 2000171108A JP 10344367 A JP10344367 A JP 10344367A JP 34436798 A JP34436798 A JP 34436798A JP 2000171108 A JP2000171108 A JP 2000171108A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerant
- compression
- rotary compressor
- cooling
- temperature
- 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
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
- F04C2210/261—Carbon dioxide (CO2)
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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、二酸化炭素を冷媒
として用いたロータリ圧縮機に関する。The present invention relates to a rotary compressor using carbon dioxide as a refrigerant.
【０００２】[0002]
【従来の技術】従来、ロータリ圧縮機は種々の技術分野
に用いられ、冷媒を圧縮する圧縮手段やこの圧縮手段を
駆動するための駆動手段であるモータ等を有して、これ
らが密閉ケース内に収納された構成となっている。2. Description of the Related Art Conventionally, rotary compressors have been used in various technical fields, and have a compression means for compressing a refrigerant and a motor as a driving means for driving the compression means. It is configured to be stored in.
【０００３】このようなロータリ圧縮機においては、こ
れまで冷媒としてＲ−２２等の塩素を含む冷媒（以下、
特定フロンガスと記載する）が用いられていたが、この
Ｒ−２２冷媒はオゾン層を破壊する原因となることが判
明し規制対象となった。In such a rotary compressor, a refrigerant containing chlorine such as R-22 (hereinafter, referred to as a refrigerant) has been used.
However, this R-22 refrigerant was found to be a cause of destruction of the ozone layer, and was subject to regulation.
【０００４】そこで、特定フロンガスに代わる冷媒の研
究開発が盛んに行われている。かかる冷媒には、二酸化
炭素冷媒等がある。[0004] Therefore, research and development of a refrigerant replacing the specific Freon gas have been actively conducted. Such refrigerants include carbon dioxide refrigerants.
【０００５】[0005]
【発明が解決しようとする課題】しかしながら、特定フ
ロンガスを用いることを前提とした従来構造のロータリ
圧縮機に二酸化炭素冷媒を用いると、従来に比べて冷媒
の最低圧力が約６倍（約３０〜４０ｋｇ／ｃｍ2Ｇ）、
最高圧力が約４倍（約１５０ｋｇ／ｃｍ2Ｇ）となって
差圧が大きくなると共に、最高圧力や最高温度が非常に
高くなる問題がある。However, when a carbon dioxide refrigerant is used in a rotary compressor having a conventional structure on the assumption that a specific Freon gas is used, the minimum pressure of the refrigerant is about six times (about 30 to 30 times) as compared with the conventional one. 40 kg / cm 2 G),
There is a problem that the maximum pressure becomes about four times (about 150 kg / cm 2 G), the differential pressure becomes large, and the maximum pressure and the maximum temperature become extremely high.
【０００６】このためロータリ圧縮機を構成するシリン
ダや密閉ケース等の部材の耐圧特性、耐熱特性及び潤滑
油の熱特性を含めた基本設計をやり直す必要が生じると
共に、このようなロータリ圧縮機を用いた冷凍回路の設
計変更が必要となってコストアップの要因となってい
る。For this reason, it is necessary to redo the basic design including the pressure resistance characteristics, heat resistance characteristics, and thermal characteristics of the lubricating oil of the members such as the cylinder and the closed case that constitute the rotary compressor, and use such a rotary compressor. This requires a change in the design of the refrigeration circuit, which is a factor in increasing costs.
【０００７】またシリンダや密閉ケース等における耐圧
及び耐熱の問題が解決しても、冷媒の圧力が高くなる構
成の場合には、圧縮手段を駆動するための駆動手段の負
荷が大きくなり（消費電力が大きくなる）、従来に比べ
て冷凍効率が低下してしまう問題がある。Further, even if the problems of pressure resistance and heat resistance in a cylinder, a closed case, etc. are solved, in the case of a structure in which the pressure of the refrigerant is high, the load of the driving means for driving the compression means increases (power consumption). Refrigeration efficiency is reduced as compared with the related art.
【０００８】そこで、本発明は、二酸化炭素冷媒を用い
た場合であっても、従来の基本設計を略そのまま適用で
きると共に冷凍効率の低下を抑制したロータリ圧縮機及
びそれを用いた冷凍回路を提供することを目的とする。Therefore, the present invention provides a rotary compressor and a refrigeration circuit using the same, in which a conventional basic design can be applied almost as it is and a decrease in refrigeration efficiency is suppressed even when a carbon dioxide refrigerant is used. The purpose is to do.
【０００９】[0009]
【課題を解決するための手段】上記課題を解決するた
め、請求項１にかかる発明は、圧縮室を縮小させて、該
圧縮室内の冷媒を圧縮する圧縮手段と、該圧縮手段を駆
動する駆動手段とを有したロータリ圧縮機において、圧
縮手段が、圧縮室を備えた圧縮要素を連結管により複数
直列接続して形成され、かつ、各圧縮要素における冷媒
の最高温度及び最高圧力が所定温度及び所定圧力以上に
ならないように機外から冷却用冷媒を減圧して圧縮室に
注入する冷媒温度調節手段を有して、冷媒として二酸化
炭素冷媒を用いた場合であっても、従来の基本設計を略
そのまま適用できるようにすると共に冷凍効率の低下を
抑制したことを特徴とする。According to a first aspect of the present invention, there is provided a compressor for reducing the size of a compression chamber and compressing a refrigerant in the compression chamber, and a drive for driving the compression means. Means, the compression means is formed by connecting a plurality of compression elements having compression chambers in series by a connecting pipe, and the maximum temperature and the maximum pressure of the refrigerant in each compression element are a predetermined temperature and Having a refrigerant temperature control means for decompressing the cooling refrigerant from outside the machine and injecting it into the compression chamber so as not to exceed a predetermined pressure, even when using a carbon dioxide refrigerant as the refrigerant, the conventional basic design It is characterized by being able to be applied almost as it is and suppressing a decrease in refrigeration efficiency.
【００１０】請求項２にかかる発明は、冷媒温度調節手
段が、減圧器を備えて、該減圧器により冷却用冷媒を減
圧することにより当該冷却用冷媒の温度を下げて圧縮室
に注入することにより、冷媒として二酸化炭素冷媒を用
いた場合であっても、容易に従来の基本設計を略そのま
ま適用できるようにすると共に冷凍効率の低下を抑制し
たことを特徴とする。According to a second aspect of the present invention, the refrigerant temperature adjusting means includes a decompressor, and the pressure of the cooling refrigerant is reduced by the decompressor to lower the temperature of the cooling refrigerant and inject it into the compression chamber. Thus, even when a carbon dioxide refrigerant is used as the refrigerant, the conventional basic design can be easily applied substantially as it is, and a decrease in refrigeration efficiency is suppressed.
【００１１】請求項３にかかる発明は、冷媒を圧縮する
請求項１又は２記載のロータリ圧縮機と、冷媒を冷却す
る冷却用熱交換器と、冷媒を減圧する減圧器と、冷媒を
加熱する加熱用熱交換器とが接続されて、基本設計を変
更することなく二酸化炭素冷媒を用いた冷凍回路を構成
し、その際に従来の基本設計を略そのまま適用できるよ
うにすると共に冷凍効率の低下を抑制したことを特徴と
する。According to a third aspect of the present invention, there is provided the rotary compressor according to the first or second aspect of compressing the refrigerant, a cooling heat exchanger for cooling the refrigerant, a decompressor for reducing the pressure of the refrigerant, and heating the refrigerant. A heat exchanger for heating is connected to form a refrigeration circuit using carbon dioxide refrigerant without changing the basic design.In this case, the conventional basic design can be applied almost as it is, and the refrigeration efficiency decreases. Is suppressed.
【００１２】[0012]
【発明の実施の形態】本発明の実施の形態を図を参照し
て説明する。図１はロータリ圧縮機１０の側断面図で、
本発明にかかるロータリ圧縮機１０は駆動手段であるモ
ータ１１、このモータ１１の下方に設けられた圧縮手段
１２等を有して、これらが密閉ケース１３内に収納され
て冷媒として二酸化炭素冷媒が用いられている。DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a side sectional view of the rotary compressor 10,
The rotary compressor 10 according to the present invention has a motor 11 as a driving means, a compression means 12 provided below the motor 11, and the like. These are housed in a closed case 13, and a carbon dioxide refrigerant is used as a refrigerant. Used.
【００１３】なお、密閉ケース１３の底部には潤滑油１
４が貯留しており、圧縮手段１２における摺動部等を潤
滑するようになっている。The lubricating oil 1 is provided at the bottom of the closed case 13.
4 for lubricating a sliding portion or the like in the compression means 12.
【００１４】圧縮手段１２は、前段圧縮要素２０と後段
圧縮要素３０とから構成され、各圧縮要素２０，３０に
は吸入管２１，３１及び吐出管２２，３２が設けられる
と共に、連結管４０により前段圧縮要素２０の吐出管２
２と後段圧縮要素３０の吸入管３１とが連結されてい
る。The compression means 12 comprises a first-stage compression element 20 and a second-stage compression element 30. Each of the compression elements 20, 30 is provided with suction pipes 21, 31 and discharge pipes 22, 32. Discharge pipe 2 of pre-stage compression element 20
2 and the suction pipe 31 of the rear compression element 30 are connected.
【００１５】従って、機外から供給された冷媒は前段圧
縮要素２０と後段圧縮要素３０とで順次圧縮されて機外
に吐出されることになる。Therefore, the refrigerant supplied from outside the machine is sequentially compressed by the first-stage compression element 20 and the second-stage compression element 30 and discharged outside the machine.
【００１６】前段圧縮要素２０と後段圧縮要素３０とは
略同じ構成で、各圧縮要素２０，３０は円筒状のシリン
ダ２３，３３内にローラ２４，３４が配設されている。
このローラ２４，３４は円筒状に形成され、その内側に
クランク２５，３５が配設されると共に、ローラ２４，
３４の外側面に図示しないベーンが当接している。The first-stage compression element 20 and the second-stage compression element 30 have substantially the same configuration. Each of the compression elements 20 and 30 has rollers 24 and 34 disposed in cylindrical cylinders 23 and 33, respectively.
The rollers 24 and 34 are formed in a cylindrical shape, and cranks 25 and 35 are disposed inside the rollers 24 and 34.
A vane (not shown) is in contact with the outer side surface of 34.
【００１７】クランク２５，３５はモータ１１の回転軸
１５に固着して（又は一体形成されて）設けられている
ので、クランク２５，３５の回転によりローラ２４，３
４は偏心回転運動するようになる。Since the cranks 25 and 35 are fixed to (or integrally formed with) the rotating shaft 15 of the motor 11, the rotation of the cranks 25 and 35 causes the rollers 24 and 3 to rotate.
4 makes eccentric rotational movement.
【００１８】このときローラ２４，３４における外側面
の一端がシリンダ２３，３３と常に最小隙間で保持され
るので、シリンダ２３，３３とローラ２４，３４との間
に形成される空間は三日月状となる。At this time, one end of the outer surface of each of the rollers 24 and 34 is always held at a minimum clearance with the cylinders 23 and 33, so that the space formed between the cylinders 23 and 33 and the rollers 24 and 34 has a crescent shape. Become.
【００１９】そして、ベーンがローラ２４，３４の外側
面に当接しているので、このベーンにより三日月状の空
間は図示しない吸気室と圧縮室とに区画される。Since the vane is in contact with the outer surfaces of the rollers 24 and 34, the vane divides the crescent-shaped space into an intake chamber and a compression chamber (not shown).
【００２０】シリンダ２３，３３の内径及びローラ２
４，３４の外径は変化しないので、ローラ２４，３４が
回転しても三日月状空間の容積は常に一定である。しか
しローラ２４，３４が回転するに伴い、ローラ２４，３
４とシリンダ２３，３３との最小隙間の位置が変化する
ため三日月状空間の向きが変化する。Inner diameter of cylinders 23 and 33 and roller 2
Since the outer diameters of the rollers 4 and 34 do not change, the volume of the crescent-shaped space is always constant even when the rollers 24 and 34 rotate. However, as the rollers 24, 34 rotate, the rollers 24, 3
Since the position of the minimum gap between the cylinder 4 and the cylinders 23 and 33 changes, the direction of the crescent-shaped space changes.
【００２１】一方、ベーンはローラ２４，３４の外側面
に常に当接するようにシリンダ２３，３３の半径方向に
出入りする。On the other hand, the vanes move in and out in the radial direction of the cylinders 23 and 33 so as to always contact the outer surfaces of the rollers 24 and 34.
【００２２】従って、このベーンにより三日月状空間が
区画されて形成される吸気室と圧縮室との容積比は、ロ
ーラ２４，３４の回転に従い変化し、吸気室の容積が拡
張すると、圧縮室の容積は縮小する。Accordingly, the volume ratio between the suction chamber and the compression chamber formed by dividing the crescent-shaped space by the vane changes according to the rotation of the rollers 24 and 34. When the volume of the suction chamber is expanded, the volume of the compression chamber is reduced. The volume shrinks.
【００２３】吸気室には図示しない吸気口が連通し、ま
た圧縮室には図示しない吐出口が連通しており、ローラ
２４，３４が吸気口を横切ることにより吸気室は吐出口
と連通するようになって、吸気室が圧縮室に変る。An intake port (not shown) communicates with the intake chamber, and a discharge port (not shown) communicates with the compression chamber. When the rollers 24 and 34 cross the intake port, the intake chamber communicates with the discharge port. , The intake chamber changes to a compression chamber.
【００２４】吐出口には図示しない吐出バルブが設けら
れており、圧縮室の縮小に伴い冷媒が圧縮されて、この
吐出バルブで規定される吐出圧に達すると冷媒が吐出さ
れる。A discharge valve (not shown) is provided at the discharge port. The refrigerant is compressed as the compression chamber is reduced, and is discharged when the discharge pressure specified by the discharge valve is reached.
【００２５】なお、前段圧縮要素２０のローラ２４と後
段圧縮要素３０のローラ３４とは、各ローラ２４，３４
が偏心回転運動することにより発生する振動が相殺され
るように、回転位相が１８０度ずれて設けられている。
即ち、クランク２５とクランク３５とは、回転軸１５を
中心に対称に設けられている。The rollers 24 of the first-stage compression element 20 and the rollers 34 of the second-stage compression element 30 are respectively
The rotation phases are shifted by 180 degrees so that the vibrations generated by the eccentric rotational movement are offset.
That is, the crank 25 and the crank 35 are provided symmetrically about the rotation shaft 15.
【００２６】以上が圧縮要素２０，３０の共通構成であ
るが、後段圧縮要素３０にはさらに冷媒温度調節手段で
ある冷媒注入装置５０が設けられて、圧縮室における冷
媒の温度及び圧力を調節するようになっている。The above is the common configuration of the compression elements 20 and 30, but the post-stage compression element 30 is further provided with a refrigerant injection device 50 as a refrigerant temperature adjusting means for adjusting the temperature and pressure of the refrigerant in the compression chamber. It has become.
【００２７】冷媒注入装置５０は、後段圧縮要素３０の
圧縮室と連通する冷媒注入口５１、この冷媒注入口５１
に連結された冷媒注入管５２、この冷媒注入管５２を流
れる冷媒（この冷媒を特に、冷却用冷媒と記載する）を
減圧するキャピラリチューブ等からなる減圧機構５３、
冷媒注入管５２に冷却用冷媒を流すか否かを制御する電
磁弁等の開閉弁５４が設けられている。The refrigerant injection device 50 has a refrigerant injection port 51 communicating with the compression chamber of the rear compression element 30,
A pressure reducing mechanism 53 composed of a capillary tube or the like for depressurizing a refrigerant flowing through the refrigerant injection tube 52 (this refrigerant is particularly referred to as a cooling refrigerant).
An on-off valve 54 such as an electromagnetic valve that controls whether or not the cooling refrigerant flows through the refrigerant injection pipe 52 is provided.
【００２８】そして、冷媒の温度が所定温度より高くな
らないように開閉弁５４が開かれると、冷却用冷媒が減
圧機構５３で減圧されながら冷媒注入管５２を流動して
冷媒注入口５１から圧縮室に注入される。When the on-off valve 54 is opened so that the temperature of the refrigerant does not become higher than the predetermined temperature, the cooling refrigerant flows through the refrigerant injection pipe 52 while being depressurized by the decompression mechanism 53, and flows from the refrigerant injection port 51 to the compression chamber. Is injected into.
【００２９】これにより冷却用冷媒は、吸入管３１から
吸気された圧縮室の冷媒と混じってこの圧縮室内の冷媒
の温度を下げる。冷媒の温度が下がることは、冷媒の圧
力も下がることを意味する。As a result, the cooling refrigerant mixes with the refrigerant in the compression chamber sucked from the suction pipe 31 to lower the temperature of the refrigerant in the compression chamber. Decreasing the temperature of the refrigerant means that the pressure of the refrigerant also decreases.
【００３０】なお、冷却用冷媒が減圧機構５３を通過す
ることにより減圧されるが、この減圧により冷却用冷媒
の温度が下がるので、効率的に圧縮室内の冷媒の温度及
び圧力を下げることが可能になる。Although the cooling refrigerant is depressurized by passing through the pressure reducing mechanism 53, the temperature of the cooling refrigerant is reduced by the decompression, so that the temperature and pressure of the refrigerant in the compression chamber can be efficiently reduced. become.
【００３１】ところで冷媒注入口５１は、冷媒が圧縮さ
れ始めた後に冷却用冷媒を注入するように設けることが
好ましい。これは圧縮開始前（吸気室が圧縮室に変る
前）に冷却用冷媒を注入すると、圧力バランスの関係か
ら注入された冷却用冷媒が吸入管３１から流出してしま
うのを防止するためである。Incidentally, it is preferable that the refrigerant injection port 51 is provided so that the cooling refrigerant is injected after the refrigerant starts to be compressed. This is to prevent the injected cooling refrigerant from flowing out of the suction pipe 31 due to the pressure balance when the cooling refrigerant is injected before the start of compression (before the intake chamber is changed to the compression chamber). .
【００３２】このような構成により、冷媒の最高圧力及
び最高温度を抑えることができロータリ圧縮機１０を構
成する各部材の耐圧、耐熱評価を含めた基本設計をやり
直す必要が無くなると共に、冷媒の圧力が予め設定され
た圧力よりも大きくなることはないので、冷凍効率の低
下を抑制することが可能になる。With such a configuration, the maximum pressure and the maximum temperature of the refrigerant can be suppressed, so that it is not necessary to redo the basic design including the pressure resistance and the heat resistance evaluation of each member constituting the rotary compressor 10, and the refrigerant pressure can be reduced. Does not become higher than a preset pressure, so that a decrease in refrigeration efficiency can be suppressed.
【００３３】図２はかかるロータリ圧縮機１０を空気調
和機に適用した際の冷凍回路図で、室内に配設される室
内機Ａ、室外に配設される室外機Ｂを主要構成とし、室
内機Ａは冷媒と室内空気とを熱交換させる室内熱交換器
１９等を有している。FIG. 2 is a refrigeration circuit diagram when such a rotary compressor 10 is applied to an air conditioner. The indoor unit A disposed indoors and the outdoor unit B disposed outdoors are main components. The machine A has an indoor heat exchanger 19 for exchanging heat between the refrigerant and the indoor air.
【００３４】また室外機Ｂは、上記ロータリ圧縮機１
０、冷媒と外気とを熱交換させる室外熱交換器１７、冷
媒を減圧する減圧器１８、冷媒の循環路を切替える四方
弁１６等を有し、室外熱交換器１７と減圧器１８との間
の配管に冷媒注入管５２が接続されている。The outdoor unit B includes the rotary compressor 1
0, an outdoor heat exchanger 17 for exchanging heat between the refrigerant and the outside air, a decompressor 18 for depressurizing the refrigerant, a four-way valve 16 for switching the circulation path of the refrigerant, and the like, between the outdoor heat exchanger 17 and the decompressor 18 A refrigerant injection pipe 52 is connected to the pipe.
【００３５】そして、冷房運転する時は、冷媒がロータ
リ圧縮機１０、室外熱交換器１７、減圧器１８、室内熱
交換器１９を循環するように循環路を切換える。During the cooling operation, the circulation path is switched so that the refrigerant circulates through the rotary compressor 10, the outdoor heat exchanger 17, the pressure reducer 18, and the indoor heat exchanger 19.
【００３６】この場合、冷媒は室外熱交換器１７で熱交
換して冷却され（冷却用熱交換器として作用する）、室
内熱交換器１９で熱交換して加熱される（加熱用熱交換
器として作用する）。In this case, the refrigerant is cooled by exchanging heat in the outdoor heat exchanger 17 (acting as a cooling heat exchanger), and is heated by exchanging heat in the indoor heat exchanger 19 (heating heat exchanger). Acts as).
【００３７】これにより、ロータリ圧縮機１０で圧縮さ
れた冷媒は、室外熱交換器１７で外気と熱交換して冷媒
の温度が下がり、減圧器１８で減圧されて室内機Ａに供
給される。Thus, the refrigerant compressed by the rotary compressor 10 exchanges heat with the outside air in the outdoor heat exchanger 17 to lower the temperature of the refrigerant, and is decompressed by the decompressor 18 and supplied to the indoor unit A.
【００３８】このとき冷媒注入管５２の開閉弁５４が開
かれていると、減圧器１８に供給される冷媒の一部がこ
の冷媒注入管５２を介して、後段圧縮要素３０に供給さ
れ、ロータリ圧縮機１０を含め冷凍回路内での冷媒の最
高温度及び最高圧力が所定圧力及び温度範囲に保たれよ
うになる。At this time, when the on-off valve 54 of the refrigerant injection pipe 52 is open, a part of the refrigerant supplied to the decompressor 18 is supplied to the subsequent compression element 30 via the refrigerant injection pipe 52, The maximum temperature and the maximum pressure of the refrigerant in the refrigeration circuit including the compressor 10 are maintained in a predetermined pressure and temperature range.
【００３９】室内機Ａに供給された冷媒は、室内熱交換
器１９で室内空気と熱交換して、室内空気を冷却して室
外機Ｂに戻りサイクルが１巡する。The refrigerant supplied to the indoor unit A exchanges heat with the indoor air in the indoor heat exchanger 19, cools the indoor air, returns to the outdoor unit B, and goes through one cycle.
【００４０】また暖房運転をする時は、冷媒がロータリ
圧縮機１０、室内熱交換器１９、減圧器１８、室外熱交
換器１７を循環するように循環路を切換える。In the heating operation, the circulation path is switched so that the refrigerant circulates through the rotary compressor 10, the indoor heat exchanger 19, the decompressor 18, and the outdoor heat exchanger 17.
【００４１】この場合、冷媒は室内熱交換器１９で熱交
換して冷却され（冷却用熱交換器として作用）、室外熱
交換器１７で熱交換して加熱される（加熱用熱交換器と
して作用）。In this case, the refrigerant is cooled by exchanging heat in the indoor heat exchanger 19 (acting as a cooling heat exchanger) and is heated by exchanging heat in the outdoor heat exchanger 17 (as a heating heat exchanger). Action).
【００４２】これにより、ロータリ圧縮機１０で圧縮さ
れた冷媒は、室内熱交換器１９で室内空気と熱交換して
この室内空気を加熱して室外機Ｂに供給される。Thus, the refrigerant compressed by the rotary compressor 10 exchanges heat with the indoor air in the indoor heat exchanger 19 to heat the indoor air and is supplied to the outdoor unit B.
【００４３】室外機Ｂに供給された冷媒は、減圧器１８
により減圧され、室外熱交換器１７で外気と熱交換して
ロータリ圧縮機１０に戻りサイクルが１巡する。The refrigerant supplied to the outdoor unit B is supplied to the decompressor 18
, Heat exchanges with the outside air in the outdoor heat exchanger 17, and the flow returns to the rotary compressor 10 to make one cycle.
【００４４】このとき冷媒注入管５２の開閉弁５４が開
かれていると、室外熱交換器１７に供給される冷媒の一
部がこの冷媒注入管５２を介して、後段圧縮要素３０に
供給され、ロータリ圧縮機１０を含め冷凍回路内での冷
媒の最高温度及び最高圧力は所定の圧力範囲及び温度範
囲に保たれるようになっている。At this time, when the on-off valve 54 of the refrigerant injection pipe 52 is open, a part of the refrigerant supplied to the outdoor heat exchanger 17 is supplied to the latter compression element 30 via the refrigerant injection pipe 52. The maximum temperature and the maximum pressure of the refrigerant in the refrigeration circuit including the rotary compressor 10 are maintained in predetermined pressure ranges and temperature ranges.
【００４５】[0045]
【発明の効果】以上説明したように請求項１にかかる発
明によれば、圧縮室を備えた圧縮要素を連結管により複
数直列接続して圧縮手段を形成し、かつ、各圧縮要素に
おける冷媒の最高温度及び最高圧力が所定温度及び所定
圧力以上にならないように機外から冷却用冷媒を減圧し
て圧縮室に注入する冷媒温度調節手段を設けたので、冷
媒として二酸化炭素冷媒を用いた場合であっても、従来
の基本設計を略そのまま適用できるようにすると共に冷
凍効率の低下を抑制することが可能になる。As described above, according to the first aspect of the present invention, a plurality of compression elements each having a compression chamber are connected in series by a connecting pipe to form compression means, and the refrigerant in each compression element is formed. Since the refrigerant temperature control means for reducing the pressure of the cooling refrigerant from outside the machine and injecting the refrigerant into the compression chamber so that the maximum temperature and the maximum pressure do not exceed the predetermined temperature and the predetermined pressure is provided, when a carbon dioxide refrigerant is used as the refrigerant, Even if there is, it becomes possible to apply the conventional basic design as it is, and to suppress a decrease in refrigeration efficiency.
【００４６】請求項２にかかる発明によれば、冷媒温度
調節手段に減圧器を設けたので該減圧器により冷却用冷
媒を減圧し冷却用冷媒の温度を下げて圧縮室に注入する
ようにしたので、冷媒として二酸化炭素冷媒を用いた場
合であっても、容易に従来の基本設計を略そのまま適用
できるようにすると共に冷凍効率の低下を抑制したこと
を特徴とする。According to the second aspect of the present invention, since the decompressor is provided in the refrigerant temperature control means, the cooling refrigerant is depressurized by the decompressor to lower the temperature of the cooling refrigerant and inject the refrigerant into the compression chamber. Therefore, even when a carbon dioxide refrigerant is used as the refrigerant, the conventional basic design can be easily applied substantially as it is, and a decrease in refrigeration efficiency is suppressed.
【００４７】請求項３にかかる発明によれば、冷媒音戸
町清酒団を備えたロータリ圧縮機と、冷媒を冷却する冷
却用熱交換器と、冷媒を減圧する減圧器と、冷媒を加熱
する加熱用熱交換器とが接続されて冷凍回路を形成した
ので、基本設計を変更することなく二酸化炭素冷媒を用
いた冷凍回路が容易に構成できると共に冷凍効率の低下
が抑制できる。According to the third aspect of the present invention, a rotary compressor provided with a refrigerant Ondocho Sakedan, a cooling heat exchanger for cooling the refrigerant, a decompressor for depressurizing the refrigerant, and a heating device for heating the refrigerant Since the refrigeration circuit is formed by being connected to the heat exchanger for use, a refrigeration circuit using a carbon dioxide refrigerant can be easily configured without changing the basic design, and a decrease in refrigeration efficiency can be suppressed.
【図１】本発明の実施の形態の説明に適用されるロータ
リ圧縮機の断面図である。FIG. 1 is a sectional view of a rotary compressor applied to a description of an embodiment of the present invention.
【図２】図１のロータリ圧縮機を空気調和機に適用した
ときの冷凍回路図である。FIG. 2 is a refrigeration circuit diagram when the rotary compressor of FIG. 1 is applied to an air conditioner.
１０ ロータリ圧縮機 １２ 圧縮手段 １７ 室外熱交換器 １８ 減圧器 １９ 室内熱交換器 ２０ 前段圧縮要素 ２１，３１ 吸入管 ２２，３２ 吐出管 ２３，３３ シリンダ ２４，３４ ローラ ２５，３５ クランク ３０ 後段圧縮要素 ４０ 連結管 ５０ 冷媒注入装置 ５１ 冷媒注入口 ５２ 冷媒注入管 ５３ 減圧機構 ５４ 開閉弁 DESCRIPTION OF SYMBOLS 10 Rotary compressor 12 Compression means 17 Outdoor heat exchanger 18 Decompressor 19 Indoor heat exchanger 20 Pre-compression element 21, 31 Suction pipe 22, 32 Discharge pipe 23, 33 Cylinder 24, 34 Roller 25, 35 Crank 30 Post-compression element 40 connecting pipe 50 refrigerant injection device 51 refrigerant injection port 52 refrigerant injection pipe 53 pressure reducing mechanism 54 on-off valve
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.7 識別記号 ＦＩ テーマコート゛(参考） Ｆ２５Ｂ 1/00 ３２１ Ｆ２５Ｂ 1/00 ３２１Ｎ (72)発明者 間 誠 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 西川 剛弘 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 坂本 泰生 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 AA05 AA09 AA13 AA21 AB03 BB12 BB13 BB42 BB47 CC24 CC47 ──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. 7 Identification code FI Theme coat ゛ (Reference) F25B 1/00 321 F25B 1/00 321N (72) Inventor Makoto Ma Ma 2-5 Keihanhondori, Moriguchi-shi, Osaka No. 5 Sanyo Electric Co., Ltd. (72) Inventor Takehiro Nishikawa 2-5-5 Keihan Hondori, Moriguchi-shi, Osaka 2-72 Sanyo Electric Co., Ltd. 3-5-5 Sanyo Electric Co., Ltd. (72) Inventor Yasuo Sakamoto 2-5-5 Keihanhondori, Moriguchi-shi, Osaka F-term in Sanyo Electric Co., Ltd. 3H029 AA05 AA09 AA13 AA21 AB03 BB12 BB13 BB42 BB47 CC24 CC47
Claims (3)
を圧縮する圧縮手段と、該圧縮手段を駆動する駆動手段
とを有したロータリ圧縮機において、 前記圧縮手段が、前記圧縮室を備えた圧縮要素を連結管
により複数直列接続して形成され、かつ、各圧縮要素に
おける冷媒の最高温度及び最高圧力が所定温度及び所定
圧力以上にならないように機外から冷却用冷媒を減圧し
て前記圧縮室に注入する冷媒温度調節手段を有すること
を特徴とするロータリ圧縮機。1. A rotary compressor having compression means for reducing a compression chamber to compress refrigerant in the compression chamber, and driving means for driving the compression means, wherein the compression means A plurality of compression elements provided are formed by connecting a plurality of compression elements in series by a connecting pipe, and the cooling refrigerant is depressurized from outside the machine so that the maximum temperature and the maximum pressure of the refrigerant in each compression element do not exceed the predetermined temperature and the predetermined pressure. A rotary compressor having a refrigerant temperature adjusting means for injecting the refrigerant into the compression chamber.
ューブを備えて、該キャピラリチューブにより冷却用冷
媒を減圧して当該冷却用冷媒の温度を下げた後に前記圧
縮室に注入することを特徴とする請求項１記載のロータ
リ圧縮機。2. The refrigerant temperature adjusting means includes a capillary tube, and the pressure of the cooling refrigerant is reduced by the capillary tube to lower the temperature of the cooling refrigerant, and then the refrigerant is injected into the compression chamber. The rotary compressor according to claim 1.
ータリ圧縮機と、冷媒を冷却する冷却用熱交換器と、冷
媒を減圧する減圧器と、冷媒を加熱する加熱用熱交換器
とが接続されてなることを特徴とする冷凍回路。3. The rotary compressor according to claim 1, which compresses the refrigerant, a cooling heat exchanger that cools the refrigerant, a decompressor that decompresses the refrigerant, and a heating heat exchanger that heats the refrigerant. Is connected to the refrigeration circuit.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10344367A JP2000171108A (en) | 1998-12-03 | 1998-12-03 | Rotary compressor and refrigerating circuit using it |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10344367A JP2000171108A (en) | 1998-12-03 | 1998-12-03 | Rotary compressor and refrigerating circuit using it |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2000171108A true JP2000171108A (en) | 2000-06-23 |
Family
ID=18368697
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10344367A Pending JP2000171108A (en) | 1998-12-03 | 1998-12-03 | Rotary compressor and refrigerating circuit using it |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2000171108A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004294059A (en) * | 2001-07-02 | 2004-10-21 | Sanyo Electric Co Ltd | Heat pump equipment |
| JPWO2003004948A1 (en) * | 2001-07-02 | 2004-10-28 | 三洋電機株式会社 | Heat pump equipment |
| KR100793477B1 (en) * | 2001-01-18 | 2008-01-14 | 마츠시타 덴끼 산교 가부시키가이샤 | Enclosed compressor |
| US7861541B2 (en) | 2004-07-13 | 2011-01-04 | Tiax Llc | System and method of refrigeration |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63243481A (en) * | 1987-03-31 | 1988-10-11 | Toshiba Corp | Scroll compressor |
| JPH0681786A (en) * | 1992-09-04 | 1994-03-22 | Toshiba Corp | Two-stage compression type rotary compressor |
| JPH07318179A (en) * | 1994-05-26 | 1995-12-08 | Toshiba Corp | Sealed compressor, and freezer and air conditioner including the compressor |
| JPH10115470A (en) * | 1996-08-22 | 1998-05-06 | Nippon Soken Inc | Steam compression type regrigeration cycle |
-
1998
- 1998-12-03 JP JP10344367A patent/JP2000171108A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63243481A (en) * | 1987-03-31 | 1988-10-11 | Toshiba Corp | Scroll compressor |
| JPH0681786A (en) * | 1992-09-04 | 1994-03-22 | Toshiba Corp | Two-stage compression type rotary compressor |
| JPH07318179A (en) * | 1994-05-26 | 1995-12-08 | Toshiba Corp | Sealed compressor, and freezer and air conditioner including the compressor |
| JPH10115470A (en) * | 1996-08-22 | 1998-05-06 | Nippon Soken Inc | Steam compression type regrigeration cycle |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100793477B1 (en) * | 2001-01-18 | 2008-01-14 | 마츠시타 덴끼 산교 가부시키가이샤 | Enclosed compressor |
| JP2004294059A (en) * | 2001-07-02 | 2004-10-21 | Sanyo Electric Co Ltd | Heat pump equipment |
| JPWO2003004948A1 (en) * | 2001-07-02 | 2004-10-28 | 三洋電機株式会社 | Heat pump equipment |
| US6880352B2 (en) | 2001-07-02 | 2005-04-19 | Sanyo Electric Co., Ltd. | Heat pump device |
| US7861541B2 (en) | 2004-07-13 | 2011-01-04 | Tiax Llc | System and method of refrigeration |
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