JP2010127563A - Refrigerating system - Google Patents

Refrigerating system Download PDF

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JP2010127563A
JP2010127563A JP2008304079A JP2008304079A JP2010127563A JP 2010127563 A JP2010127563 A JP 2010127563A JP 2008304079 A JP2008304079 A JP 2008304079A JP 2008304079 A JP2008304079 A JP 2008304079A JP 2010127563 A JP2010127563 A JP 2010127563A
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refrigerant
gas
expander
compressor
liquid
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Hiroshi Oide
宏 大出
Shunichi Hashimoto
俊一 橋本
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Sanden Corp
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Sanden Corp
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Priority to JP2008304079A priority Critical patent/JP2010127563A/en
Priority to PCT/JP2009/006424 priority patent/WO2010061624A1/en
Publication of JP2010127563A publication Critical patent/JP2010127563A/en
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    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • 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
    • F25B2400/23—Separators
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerating system capable of sufficiently cooling a refrigerant supplied to an expansion device to liquefy the refrigerant and of improving a coefficient of performance (COP) and refrigerating capacity, even when a refrigerating cycle uses the refrigerant in a supercritical state. <P>SOLUTION: An internal heat exchange element (30) is provided astride the piping between a radiator (13) and the expansion device (18) and the piping between an evaporator (20) and a compressor (10), and an accumulator (40) is interposed in the piping between the internal heat exchange element (30) and the compressor (10) on the downstream side from the internal heat exchange element (30). <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、冷凍システムに係り、詳しくは超臨界で冷媒を使用する冷凍サイクルにおいて高効率を実現する技術に関する。   The present invention relates to a refrigeration system, and more particularly to a technique for realizing high efficiency in a refrigeration cycle that uses a refrigerant in a supercritical state.

一般に、冷凍サイクルは、圧縮機、放熱器（凝縮器）、膨張器、蒸発器（吸熱器）がそれぞれ管路で連結され、管路内を冷媒が相変化しながら流れるように構成されている。即ち、冷凍サイクルは、圧縮機で圧縮された冷媒が放熱器を経て放熱して液化し、膨張器で膨張させられた冷媒が蒸発器を経て吸熱して気化するよう構成されている。
また、近年では、従来多用されていたフロンに代えて環境を配慮した種々の冷媒が使用されており、このような冷媒として例えば二酸化炭素（ＣＯ２）等が公知である。 In general, a refrigeration cycle is configured such that a compressor, a radiator (condenser), an expander, and an evaporator (heat absorber) are connected to each other by pipes, and refrigerant flows through the pipes while changing phase. . That is, the refrigeration cycle is configured such that the refrigerant compressed by the compressor dissipates heat and liquefies through the radiator, and the refrigerant expanded by the expander absorbs heat through the evaporator and is vaporized.
In recent years, various refrigerants in consideration of the environment have been used in place of Freon, which has been frequently used in the past, and for example, carbon dioxide (CO 2 ) is known as such a refrigerant.

ところで、上記ＣＯ２を含め、冷媒は、外気温が高いと放熱器を経て液化したはずの冷媒の一部が膨張器に至るまでの間に気化し、所謂フラッシュガスを発生し易いという性質を有している。このようにフラッシュガスが発生し易いと、蒸発器において有効に作用する液状の冷媒量が減少したり圧損が増大したりして吸熱効率が悪くなり、成績係数（ＣＯＰ）ひいては冷凍能力が悪化し好ましいことではない。 By the way, the refrigerant including CO 2 has a property that when the outside air temperature is high, a part of the refrigerant that should have been liquefied through the radiator is vaporized before reaching the expander, and so-called flash gas is easily generated. Have. If flash gas is easily generated in this way, the amount of liquid refrigerant that effectively acts in the evaporator decreases or the pressure loss increases, resulting in poor endothermic efficiency, resulting in poor coefficient of performance (COP) and, consequently, refrigeration capacity. It is not preferable.

そこで、例えば放熱器と蒸発器との間に第１及び第２の二つの膨張器を備えるとともにこれら二つの膨張器間に気液分離器を備え、気液分離器で分離された気体状の冷媒を圧縮機に供給する一方、液状の冷媒を第２の膨張器に供給するように図ったガスインジェクションサイクル（エコノマイザーサイクル）が知られている（例えば、特許文献１、２参照）。   Therefore, for example, the first and second two expanders are provided between the radiator and the evaporator, and the gas-liquid separator is provided between the two expanders, and the gaseous state separated by the gas-liquid separator is provided. There is known a gas injection cycle (economizer cycle) in which a refrigerant is supplied to a compressor while a liquid refrigerant is supplied to a second expander (see, for example, Patent Documents 1 and 2).

そして、特許文献１に開示の技術では、放熱器から第１の膨張器に供給される冷媒を過冷却させるべく、放熱器と第１の膨張器との間に内部熱交換器を設け、気液分離器を経た気体状の冷媒で第１の膨張器に供給される冷媒を冷却するようにしている。
また、特許文献２に開示の技術では、気液分離器から第２の膨張器に供給される冷媒を過冷却させるべく、気液分離器と第２の膨張器との間に内部熱交換器を設けるとともに蒸発器と当該内部熱交換器との間に別の第２の気液分離器を設け、蒸発器を出て当該第２の気液分離器を経た気体状の冷媒で第２の膨張器に供給される冷媒を冷却するようにしている。
特開平１１−６３６９４号公報 特開２００１−１１６３７６号公報 In the technique disclosed in Patent Document 1, an internal heat exchanger is provided between the radiator and the first expander in order to supercool the refrigerant supplied from the radiator to the first expander. The refrigerant supplied to the first expander is cooled by the gaseous refrigerant that has passed through the liquid separator.
In the technique disclosed in Patent Document 2, an internal heat exchanger is provided between the gas-liquid separator and the second expander so as to supercool the refrigerant supplied from the gas-liquid separator to the second expander. And another second gas-liquid separator is provided between the evaporator and the internal heat exchanger, and the second gas-liquid refrigerant exits the evaporator and passes through the second gas-liquid separator. The refrigerant supplied to the expander is cooled.
Japanese Patent Laid-Open No. 11-63694 JP 2001-116376 A

しかしながら、上記特許文献１に開示の技術においては、放熱器と第１の膨張器との間の冷媒を内部熱交換器で冷却するようにしているものの、このような構成では冷媒が気液分離器から第２の膨張器に至るまでに依然としてフラッシュガスを発生し兼ねず、好ましいとは言い難い。
一方、効率よく冷媒のエネルギを活用するためには、蒸発器後の冷媒は過熱度ゼロが理想であるところ、現実には環境条件の変動等により必ずや液状の冷媒が蒸発器から流出するもので、特許文献２によれば第２の気液分離器がアキュムレータとして機能することで液状の冷媒の圧縮機への循環が防止されている。 However, in the technique disclosed in Patent Document 1, the refrigerant between the radiator and the first expander is cooled by the internal heat exchanger, but in such a configuration, the refrigerant is separated into gas and liquid. The flash gas may still be generated from the vessel to the second expander, which is not preferable.
On the other hand, in order to efficiently use the energy of the refrigerant, the superheat degree of the refrigerant after the evaporator is ideally zero. In reality, however, liquid refrigerant always flows out of the evaporator due to changes in environmental conditions. According to Patent Document 2, the second gas-liquid separator functions as an accumulator, so that the circulation of liquid refrigerant to the compressor is prevented.

ところが、このような特許文献２の構成では、内部熱交換器において第２の気液分離器を経た気体状の冷媒（ガス冷媒）のみによって熱交換を行うため、顕熱利用となり、液状の冷媒が全く活用されず、内部熱交換器において潜熱利用ができないという問題がある。このように顕熱利用だけであると、冷媒を十分に過冷却できず、やはり冷媒が第２の膨張器に至るまでにフラッシュガスを発生し兼ねず、好ましいことではない。   However, in such a configuration of Patent Document 2, heat exchange is performed only with the gaseous refrigerant (gas refrigerant) that has passed through the second gas-liquid separator in the internal heat exchanger, so that sensible heat is utilized and the liquid refrigerant is used. Is not utilized at all, and there is a problem that latent heat cannot be used in the internal heat exchanger. Thus, the use of only sensible heat is not preferable because the refrigerant cannot be sufficiently subcooled and flash gas may be generated before the refrigerant reaches the second expander.

また、上記特許文献１、２では、蒸発器が一つである場合についてのみ開示されているが、蒸発器を並列に複数設けた場合、分岐部に至るまでにフラッシュガスが発生してしまうと冷媒を各蒸発器に均等に分流させることが困難となり、分流のバランスが崩れ、各蒸発器間で吸熱性能にばらつきが生じるという問題もある。
本発明は、上記の課題を解決するためになされたもので、その目的とするところは、超臨界で冷媒を使用する冷凍サイクルであっても、膨張器に供給される冷媒を十分に冷却して液状にでき、成績係数（ＣＯＰ）ひいては冷凍能力の向上を図ることの可能な冷凍システムを提供することにある。 Moreover, in the said patent documents 1 and 2, although it is disclosed only about the case where there is one evaporator, when a plurality of evaporators are provided in parallel, flash gas will be generated before reaching the branch section. There is also a problem that it is difficult to evenly distribute the refrigerant to each evaporator, the balance of the flow is lost, and the endothermic performance varies among the evaporators.
The present invention has been made to solve the above-described problems, and the object of the present invention is to sufficiently cool the refrigerant supplied to the expander even in a refrigeration cycle that uses a refrigerant in a supercritical state. An object of the present invention is to provide a refrigeration system that can be made liquid and can improve the coefficient of performance (COP) and thus the refrigeration capacity.

上記の目的を達成するべく、請求項１の冷凍システムは、冷媒を圧縮する圧縮機と、該圧縮機で昇圧された冷媒を冷却する放熱器と、該放熱器で冷却された冷媒を減圧膨張させる膨張器と、該膨張器で減圧された冷媒を蒸発させる蒸発器とを順次配管接続してなる冷凍システムであって、前記放熱器と前記膨張器との間の配管と前記蒸発器と前記圧縮機との間の配管とに跨いで設けられ、前記放熱器から前記膨張器に向かう冷媒と前記蒸発器から前記圧縮機に向かう冷媒との間で熱交換を行う内部熱交換要素と、前記内部熱交換要素と前記圧縮機との間の配管に介装され、液状の冷媒を貯留するアキュムレータとを備えたことを特徴とする。   In order to achieve the above object, a refrigeration system according to claim 1 includes a compressor for compressing a refrigerant, a radiator for cooling the refrigerant pressurized by the compressor, and decompressing and expanding the refrigerant cooled by the radiator. And an evaporator for evaporating the refrigerant decompressed by the expander in order by piping, the piping between the radiator and the expander, the evaporator, and the evaporator An internal heat exchange element that is provided across the piping between the compressor and performs heat exchange between the refrigerant from the radiator toward the expander and the refrigerant from the evaporator toward the compressor; An accumulator is provided which is interposed in a pipe between an internal heat exchange element and the compressor and stores a liquid refrigerant.

請求項２の冷凍システムでは、請求項１において、前記冷媒は超臨界で使用するものであることを特徴とする。
請求項３の冷凍システムでは、請求項１または２において、前記圧縮機は第１圧縮機と該第１圧縮機の下流側に直列に接続された第２圧縮機とからなるとともに前記膨張器は第１膨張器と該第１膨張器の下流側に直列に接続された第２膨張器とからなり、前記第１膨張器と前記第２膨張器との間に介装され、冷媒の気液分離を行って液状の冷媒を前記第２膨張器に供給する気液分離器と、該気液分離器と前記第１圧縮機及び前記第２圧縮機間の管路とを連結して設けられ、前記気液分離器で分離された気体状の冷媒をインジェクションガスとして前記第２圧縮機に供給するガスインジェクション管路とを備え、前記内部熱交換要素は、前記気液分離器と前記第２膨張器との間に介装されていることを特徴とする。 The refrigeration system according to claim 2 is characterized in that, in claim 1, the refrigerant is used in a supercritical state.
According to a third aspect of the present invention, in the first or second refrigeration system, the compressor includes a first compressor and a second compressor connected in series on the downstream side of the first compressor, and the expander is A first expander and a second expander connected in series downstream of the first expander, interposed between the first expander and the second expander, and a gas-liquid refrigerant A gas-liquid separator that performs separation and supplies a liquid refrigerant to the second expander; and the gas-liquid separator and a pipe line between the first compressor and the second compressor are connected to each other. A gas injection pipe for supplying the gaseous refrigerant separated by the gas-liquid separator to the second compressor as an injection gas, and the internal heat exchange element includes the gas-liquid separator and the second It is characterized by being interposed between the inflator.

請求項４の冷凍システムでは、請求項１または２において、前記圧縮機は一つであり、前記第１膨張器と前記第２膨張器との間に介装され、冷媒の気液分離を行って液状の冷媒を前記第２膨張器に供給する気液分離器と、該気液分離器と前記圧縮機の圧縮中間圧部とを連通して設けられ、前記気液分離器で分離された気体状の冷媒をインジェクションガスとして前記圧縮機の圧縮中間圧部に供給するガスインジェクション管路とを備え、前記内部熱交換要素は、前記気液分離器と前記第２膨張器との間に介装されていることを特徴とする。   A refrigeration system according to a fourth aspect of the present invention is the refrigeration system according to the first or second aspect, wherein the number of the compressors is one, and the compressor is interposed between the first expander and the second expander to perform gas-liquid separation of the refrigerant. The gas-liquid separator that supplies liquid refrigerant to the second expander, and the gas-liquid separator and the compression intermediate pressure portion of the compressor are provided in communication with each other and separated by the gas-liquid separator. A gas injection conduit for supplying a gaseous refrigerant as an injection gas to the compression intermediate pressure portion of the compressor, and the internal heat exchange element is interposed between the gas-liquid separator and the second expander. It is equipped with.

請求項５の冷凍システムでは、請求項３または４において、前記気液分離器からの液状の冷媒を一時的に貯留する受液器を備え、該受液器は、前記気液分離器と一体に設けられていることを特徴とする。
請求項６の冷凍システムでは、請求項１または２において、前記蒸発器は複数からなるとともに前記膨張器は複数からなり、前記内部熱交換要素から前記膨張器及び前記蒸発器を経て再び前記内部熱交換要素に向かう管路は複数の分岐管路に分岐し合流しており、前記複数の蒸発器は、互いに並列となるよう各々前記分岐管路に配設され、前記複数の膨張器は、各々前記分岐管路に前記蒸発器と直列に配設されていることを特徴とする。 A refrigeration system according to a fifth aspect of the present invention is the refrigeration system according to the third or fourth aspect, further comprising a liquid receiver that temporarily stores the liquid refrigerant from the gas-liquid separator, and the liquid receiver is integrated with the gas-liquid separator. It is provided in.
The refrigeration system according to claim 6 is the refrigeration system according to claim 1 or 2, wherein the evaporator includes a plurality of the expanders and the expander includes a plurality of the internal heat exchange elements through the expander and the evaporator and the internal heat again. The pipelines toward the exchange element are branched and joined into a plurality of branch pipelines, and the plurality of evaporators are arranged in the branch pipelines so as to be parallel to each other, and the plurality of expanders are respectively The branch pipe is arranged in series with the evaporator.

請求項７の冷凍システムでは、請求項３乃至５のいずれかにおいて、前記蒸発器は複数からなるとともに前記第２膨張器は複数からなり、前記内部熱交換要素から前記第２膨張器及び前記蒸発器を経て再び前記内部熱交換要素に向かう管路は複数の分岐管路に分岐し合流しており、前記複数の蒸発器は、互いに並列となるよう各々前記分岐管路に配設され、前記複数の第２膨張器は、各々前記分岐管路に前記蒸発器と直列に配設されていることを特徴とする。   In the refrigeration system according to claim 7, in any one of claims 3 to 5, the evaporator includes a plurality and the second expander includes a plurality, and the second heat expander and the evaporation from the internal heat exchange element. The pipes that go to the internal heat exchanging element again through the condenser branch and merge into a plurality of branch pipes, and the plurality of evaporators are respectively arranged in the branch pipes so as to be parallel to each other, The plurality of second expanders are respectively disposed in the branch pipes in series with the evaporator.

請求項８の冷凍システムでは、請求項６または７において、前記分岐管路は３本以上であって該分岐管路の分岐部は２箇所以上あり、前記内部熱交換要素は、複数からなり、これら分岐部の手前にそれぞれ配設されていることを特徴とする。
請求項９の冷凍システムでは、請求項１乃至８のいずれかにおいて、前記内部熱交換要素は配管同士を接触させるよう構成されることを特徴とする。 The refrigeration system according to claim 8 is the refrigeration system according to claim 6 or 7, wherein the number of branch pipes is three or more, and there are two or more branch parts of the branch pipes, and the internal heat exchange element includes a plurality of parts. It is characterized by being arranged in front of these branch parts.
A refrigeration system according to a ninth aspect is characterized in that, in any one of the first to eighth aspects, the internal heat exchange element is configured to bring pipes into contact with each other.

請求項１０の冷凍システムでは、請求項１乃至７のいずれかにおいて、前記アキュムレータは、前記内部熱交換要素と一体に設けられていることを特徴とする。   A refrigeration system according to a tenth aspect is characterized in that, in any one of the first to seventh aspects, the accumulator is provided integrally with the internal heat exchange element.

請求項１の冷凍システムによれば、放熱器と膨張器との間の配管と蒸発器と圧縮機との間の配管とを跨いで内部熱交換要素を設けるようにしているので、放熱器から膨張器に向かう冷媒が蒸発器を経た冷媒によって冷却される。即ち、冷媒を例えば超臨界で使用するシステムでは、図２に示すように、膨張器に至る冷媒は飽和液線上の液冷媒であることから（破線で示す）、外気温が高いとフラッシュガスが発生して気体状の冷媒と液状の冷媒とが混在した状態になり易いのであるが、このような場合であっても膨張器に至る冷媒は過冷却状態とされ、良好に液状とされる（実線で示す）。   According to the refrigeration system of claim 1, since the internal heat exchange element is provided across the piping between the radiator and the expander and the piping between the evaporator and the compressor, The refrigerant going to the expander is cooled by the refrigerant that has passed through the evaporator. That is, in a system that uses a refrigerant in a supercritical state, for example, as shown in FIG. 2, the refrigerant reaching the expander is a liquid refrigerant on a saturated liquid line (shown by a broken line). Although it is easy to generate and it will be in the state where a gaseous refrigerant and a liquid refrigerant were mixed, even in such a case, the refrigerant which reaches an expander will be in a supercooled state, and will be in a good liquid state ( (Indicated by a solid line).

そして、この際、上述したように環境条件の変動等により現実には蒸発器からは気体状の冷媒のみならず液状の冷媒も流出するところ、本発明では液状の冷媒を貯留するアキュムレータを内部熱交換要素よりも圧縮機側に設けているので、放熱器から膨張器に向かう冷媒は蒸発器から流出する気体状の冷媒とともにかかる液状の冷媒によって顕熱利用のみならず潜熱利用によって十分に過冷却状態とされる。   At this time, as described above, not only the gaseous refrigerant but also the liquid refrigerant actually flows out of the evaporator due to fluctuations in the environmental conditions and the like. In the present invention, the accumulator storing the liquid refrigerant is internally heated. Since it is provided closer to the compressor than the replacement element, the refrigerant going from the radiator to the expander is sufficiently subcooled not only by sensible heat but also by latent heat by the liquid refrigerant together with the gaseous refrigerant flowing out of the evaporator. State.

従って、冷凍サイクルにおいて、放熱器から膨張器に向かう冷媒を良好に液状に維持でき、膨張器に至るまでに冷媒が気化して所謂フラッシュガスが発生してしまうことを防止することができる。
これにより、蒸発器の吸熱性能を高め、冷凍サイクルにおける成績係数（ＣＯＰ）ひいては冷凍能力の向上を図ることができる。 Therefore, in the refrigeration cycle, the refrigerant from the radiator to the expander can be maintained in a good liquid state, and it is possible to prevent so-called flash gas from being generated by the evaporation of the refrigerant before reaching the expander.
As a result, the endothermic performance of the evaporator can be improved, and the coefficient of performance (COP) in the refrigeration cycle and thus the refrigeration capacity can be improved.

また、蒸発器から流出する液状の冷媒は内部熱交換要素で潜熱利用されて気化することになるため、アキュムレータに貯留される液状の冷媒の量を少なく抑えるようにでき、アキュムレータの小型化を図ることもできる。
また、請求項２の冷凍システムによれば、冷媒が超臨界で使用するもの、例えば二酸化炭素であっても、放熱器から膨張器に向かう冷媒を良好に液状に維持でき、膨張器に至るまでにフラッシュガスが発生してしまうことを防止することができる。 Further, since the liquid refrigerant flowing out of the evaporator is vaporized by using latent heat in the internal heat exchange element, the amount of the liquid refrigerant stored in the accumulator can be reduced, and the accumulator can be downsized. You can also.
Moreover, according to the refrigeration system of claim 2, even if the refrigerant is supercritical, for example, carbon dioxide, the refrigerant from the radiator to the expander can be well maintained in a liquid state until the expander is reached. It is possible to prevent flash gas from being generated.

また、請求項３、４の冷凍システムによれば、ガスインジェクションサイクルを有した冷凍システムにおいて、気液分離器から第２膨張器に流れる液状の冷媒が蒸発器を経た冷媒によって冷却される。
従って、ガスインジェクションサイクルを有した冷凍システムにおいて超臨界で使用する二酸化炭素のような冷媒を用いる場合であっても、気液分離器から第２膨張器に向かう冷媒を確実に液状に維持でき、第２膨張器に至るまでにフラッシュガスが発生してしまうことを好適に防止することができる。 According to the refrigeration system of claims 3 and 4, in the refrigeration system having a gas injection cycle, the liquid refrigerant flowing from the gas-liquid separator to the second expander is cooled by the refrigerant passing through the evaporator.
Therefore, even when a refrigerant such as carbon dioxide used in a supercritical state in a refrigeration system having a gas injection cycle is used, the refrigerant directed from the gas-liquid separator to the second expander can be reliably maintained in a liquid state, It is possible to suitably prevent the flash gas from being generated before reaching the second expander.

これにより、ガスインジェクションサイクルの作用に加え、蒸発器の吸熱性能を高め、冷凍サイクルにおける冷凍能力のさらなる向上を図ることができる。
また、請求項５の冷凍システムによれば、受液器を気液分離器と一体に設けることで、冷凍システムの簡素化、低廉化を図りながら、放熱器から膨張器に向かう冷媒を確実に液状に維持でき、膨張器に至るまでにフラッシュガスが発生してしまうことを防止することができる。 Thereby, in addition to the effect | action of a gas injection cycle, the heat absorption performance of an evaporator can be improved and the further improvement of the refrigerating capacity in a refrigerating cycle can be aimed at.
Further, according to the refrigeration system of claim 5, by providing the liquid receiver integrally with the gas-liquid separator, the refrigerant from the radiator to the expander can be reliably supplied while simplifying and reducing the cost of the refrigeration system. It can be maintained in a liquid state, and flash gas can be prevented from being generated before reaching the expander.

また、請求項６、７の冷凍システムによれば、複数の蒸発器を互いに並列となるよう各々分岐管路に配設し、複数の膨張器または第２膨張器を各々分岐管路に蒸発器と直列に配設するようにしているので、放熱器から膨張器または第２膨張器に向かう冷媒が確実に液状に維持されることになり、当該液状に維持された冷媒を各膨張器または第２膨張器に向けてそれぞれ均等にバランスよく分流させることができる。   According to the refrigeration system of claims 6 and 7, a plurality of evaporators are arranged in the branch pipes so as to be parallel to each other, and the plurality of expanders or the second expanders are respectively connected to the branch pipes. Therefore, the refrigerant from the radiator to the expander or the second expander is surely maintained in the liquid state, and the refrigerant maintained in the liquid state is supplied to each expander or the second expander. Each of the two expanders can be divided equally and in a balanced manner.

これにより、各蒸発器の吸熱性能をばらつきなく高め、冷凍サイクルにおける冷凍能力のさらなる向上を図ることができる。
また、請求項８の冷凍システムによれば、分岐管路は３本以上であって該分岐管路の分岐部は２箇所以上あり、内部熱交換要素をこれら分岐部の手前にそれぞれ配設するようにしているので、各々分岐管路において冷媒を液状に維持でき、液状の冷媒をより一層確実に各膨張器または第２膨張器に向けて供給することができる。 Thereby, the endothermic performance of each evaporator can be improved without variation, and the refrigeration capacity in the refrigeration cycle can be further improved.
According to the refrigeration system of claim 8, there are three or more branch pipes, and there are two or more branch parts of the branch pipes, and the internal heat exchange elements are respectively arranged in front of these branch parts. Thus, the refrigerant can be maintained in a liquid state in each branch pipe, and the liquid refrigerant can be supplied to each expander or the second expander more reliably.

これにより、各蒸発器の吸熱性能をより一層高め、冷凍サイクルにおける冷凍能力のさらなる向上を図ることができる。
また、請求項９の冷凍システムによれば、内部熱交換要素は配管同士を抱き合わせて接触させるよう構成されているので、簡単な構成にして、放熱器から膨張器または第２膨張器に向かう冷媒を良好に液状に維持でき、膨張器または第２膨張器に至るまでにフラッシュガスが発生してしまうことを防止することができる。 Thereby, the heat absorption performance of each evaporator can be further enhanced, and the refrigeration capacity in the refrigeration cycle can be further improved.
According to the refrigeration system of the ninth aspect, since the internal heat exchange element is configured to tie the pipes in contact with each other, the refrigerant is directed from the radiator to the expander or the second expander with a simple configuration. Can be maintained in a liquid state, and flash gas can be prevented from being generated before reaching the expander or the second expander.

また、請求項１０の冷凍システムによれば、アキュムレータを内部熱交換要素と一体に設けることで、冷凍システムの簡素化、低廉化を図りながら、放熱器から膨張器に向かう冷媒を確実に液状に維持でき、膨張器に至るまでにフラッシュガスが発生してしまうことを防止することができる。   Further, according to the refrigeration system of claim 10, by providing the accumulator integrally with the internal heat exchange element, the refrigerant directed from the radiator to the expander is surely liquefied while simplifying and reducing the cost of the refrigeration system. It is possible to prevent the flash gas from being generated before reaching the expander.

以下、本発明の実施形態を図面を参照しながら説明する。
先ず、第１実施例について説明する。
図１には、本発明の第１実施例に係る冷凍システムの概略構成図が示されている。
なお、本発明に係る冷凍システムは、冷凍装置、空調装置、ヒートポンプ、給湯器、及び暖房器等の種々の冷凍・空調サイクルに適用されるものである。 Embodiments of the present invention will be described below with reference to the drawings.
First, the first embodiment will be described.
FIG. 1 shows a schematic configuration diagram of a refrigeration system according to a first embodiment of the present invention.
The refrigeration system according to the present invention is applied to various refrigeration / air conditioning cycles such as a refrigeration apparatus, an air conditioner, a heat pump, a water heater, and a heater.

同図に示すように、本発明の第１実施例に係る冷凍システムでは、二酸化炭素（ＣＯ２）を冷媒としており、当該冷媒を圧縮する第１圧縮機１０と、第１圧縮機１０で中間圧力まで昇圧された冷媒をさらに昇圧する第２圧縮機１２と、当該昇圧された冷媒を冷却するガス冷却器（放熱器）１３と、ガス冷却器１３よりも下流側に位置し、ガス冷却器１３で冷却された冷媒を減圧膨張する第１膨張弁（第１膨張器）１４とが順に配管接続されている。なお、第１圧縮機１０及び第２圧縮機１２は、例えばスクロール式、斜板式の圧縮機である。 As shown in the figure, in the refrigeration system according to the first embodiment of the present invention, carbon dioxide (CO 2 ) is used as a refrigerant, and the first compressor 10 that compresses the refrigerant and the first compressor 10 are intermediate. A second compressor 12 for further boosting the refrigerant whose pressure has been increased to a pressure; a gas cooler (heat radiator) 13 for cooling the boosted refrigerant; and a gas cooler positioned downstream of the gas cooler 13. A first expansion valve (first expander) 14 that decompresses and expands the refrigerant cooled in 13 is connected to the pipe in order. The first compressor 10 and the second compressor 12 are, for example, scroll-type and swash plate-type compressors.

また、第１膨張弁１４よりも下流側には、冷媒の気液分離を行う気液分離器１５が設けられており、該気液分離器１５のガス出口側と第２圧縮機１２の吸入側とが連結配管（ガスインジェクション管路）１６により接続されて所謂ガスインジェクションサイクルが構成されている。即ち、ガスインジェクションサイクルにより、気液分離器１５から第２圧縮機１２に向けてガス冷媒がインジェクションガスとして供給されるよう構成されている。なお、連結配管１６にはインジェクションガスの逆流を防止すべく逆止弁１６ａが介装されている。   Further, a gas-liquid separator 15 that performs gas-liquid separation of the refrigerant is provided downstream of the first expansion valve 14. The gas outlet side of the gas-liquid separator 15 and the suction of the second compressor 12 are provided. The so-called gas injection cycle is configured by connecting the sides to each other by a connecting pipe (gas injection pipe line) 16. That is, the gas refrigerant is supplied as the injection gas from the gas-liquid separator 15 to the second compressor 12 by the gas injection cycle. The connecting pipe 16 is provided with a check valve 16a to prevent the backflow of the injection gas.

一方、気液分離器１５の液出口側には一旦液冷媒を貯留する受液器１７が設けられ、受液器１７の下流側にはさらに第２膨張弁（第２膨張器）１８を介して蒸発器（吸熱器）２０が配管接続されており、蒸発器２０は上記第１圧縮機１０に配管接続されている。
そして、同図に示すように、気液分離器１５を経た受液器１７と第２膨張弁１８との間の配管と蒸発器２０と第１圧縮機１０との間の配管とに跨いで内部熱交換器（内部熱交換要素）３０が設けられている。この内部熱交換器３０は、ガス冷却器１３から気液分離器１５、受液器１７を経て第２膨張弁１８に向かう冷媒と蒸発器２０から第１圧縮機１０に向かう冷媒との間で熱交換を行う機能を有している。 On the other hand, a liquid receiver 17 that temporarily stores liquid refrigerant is provided on the liquid outlet side of the gas-liquid separator 15, and a second expansion valve (second expander) 18 is further provided downstream of the liquid receiver 17. The evaporator (heat absorber) 20 is connected by piping, and the evaporator 20 is connected by piping to the first compressor 10.
And as shown in the figure, straddling the pipe between the liquid receiver 17 and the second expansion valve 18 that have passed through the gas-liquid separator 15 and the pipe between the evaporator 20 and the first compressor 10. An internal heat exchanger (internal heat exchange element) 30 is provided. The internal heat exchanger 30 is connected between the refrigerant from the gas cooler 13 through the gas-liquid separator 15 and the liquid receiver 17 toward the second expansion valve 18 and the refrigerant from the evaporator 20 toward the first compressor 10. It has a function to perform heat exchange.

さらに、同図に示すように、蒸発器２０と第１圧縮機１０間のうち内部熱交換器３０と第１圧縮機１０との間にはアキュムレータ４０が介装されている。アキュムレータ４０は気液分離器と同様の気液分離機能と受液機能とを併せ有し、配管内の液冷媒を貯留してガス冷媒のみを第１圧縮機１０に供給するよう構成されている。
また、連結配管１６からは分岐合流してバイパス管路５２が設けられており、ガス冷却器１３と第１膨張弁１４との間の配管とバイパス管路５２とに跨いでガス熱交換器５０が設けられている。このガス熱交換器５０は、ガス冷却器１３から第１膨張弁１４に向かう冷媒とインジェクションガスとの間で熱交換を行う機能を有している。なお、バイパス管路５２の連結配管１６との分岐部には流量調整弁５４が設けられており、当該流量調整弁５４により連結配管１６から分かれてバイパス管路５２に流れるインジェクションガスの量が適宜調節される。 Furthermore, as shown in the figure, an accumulator 40 is interposed between the internal heat exchanger 30 and the first compressor 10 among the evaporator 20 and the first compressor 10. The accumulator 40 has a gas-liquid separation function and a liquid receiving function similar to those of the gas-liquid separator, and is configured to store the liquid refrigerant in the pipe and supply only the gas refrigerant to the first compressor 10. .
Further, a bypass pipe 52 is provided by branching and joining from the connecting pipe 16, and the gas heat exchanger 50 straddles the pipe between the gas cooler 13 and the first expansion valve 14 and the bypass pipe 52. Is provided. The gas heat exchanger 50 has a function of exchanging heat between the refrigerant from the gas cooler 13 toward the first expansion valve 14 and the injection gas. Note that a flow rate adjusting valve 54 is provided at a branching portion of the bypass pipe line 52 with the connecting pipe 16, and the amount of the injection gas that flows from the connecting pipe 16 and flows into the bypass pipe line 52 is appropriately determined by the flow rate adjusting valve 54. Adjusted.

以下、このように構成された本発明の第１実施例に係る冷凍システムの作用効果を説明する。ここで、図２を参照すると、当該冷凍サイクルのｐ−ｈ線図（モリエル線図）が示されており、同ｐ−ｈ線図をも参照しながら説明する。
第１圧縮機１０によって圧縮された冷媒は、気液分離器１５からのインジェクションガスとともに第２圧縮機１２で圧縮され、ＣＯ２からなる冷媒は高温高圧の超臨界状態の冷媒となってガス冷却器１３に流入し、当該ガス冷却器１３にて放熱して冷却される。 Hereinafter, the operation and effect of the refrigeration system according to the first embodiment of the present invention configured as described above will be described. Here, referring to FIG. 2, there is shown a ph diagram (Mollier diagram) of the refrigeration cycle, which will be described with reference to the ph diagram.
The refrigerant compressed by the first compressor 10 is compressed by the second compressor 12 together with the injection gas from the gas-liquid separator 15, and the refrigerant made of CO 2 becomes a high-temperature and high-pressure supercritical refrigerant and gas-cooled. It flows into the vessel 13 and is radiated by the gas cooler 13 to be cooled.

ガス冷却器１３を出た冷媒は、第１膨張弁１４により高圧から中間圧程度にまで膨張される。
第１膨張弁１４を出た冷媒は、気液二相状態であるため、気液分離器１５に流入してガス冷媒と液冷媒とに分離され、ガス冷媒についてはインジェクションガスとして上記の如く第２圧縮機１２に流入する一方、液冷媒については受液器１７及び内部熱交換器３０を経て第２膨張弁１８においてさらに低圧まで膨張された後、蒸発器２０に流入する。 The refrigerant leaving the gas cooler 13 is expanded from a high pressure to an intermediate pressure by the first expansion valve 14.
Since the refrigerant exiting the first expansion valve 14 is in a gas-liquid two-phase state, it flows into the gas-liquid separator 15 and is separated into a gas refrigerant and a liquid refrigerant. As described above, the gas refrigerant is injected as an injection gas. While flowing into the two compressors 12, the liquid refrigerant is further expanded to a low pressure in the second expansion valve 18 through the liquid receiver 17 and the internal heat exchanger 30, and then flows into the evaporator 20.

蒸発器２０では液冷媒が外気からの吸熱により気化してガス冷媒となる。実際には、蒸発器２０を出た冷媒は、完全には気化せずに液冷媒を含む気液二相状態であり、気液二相状態のまま内部熱交換器３０を経てアキュムレータ４０に至り、アキュムレータ４０において気液分離される。そして、ガス冷媒のみが第１圧縮機１０に向かいサイクル内を循環する。一方、液冷媒についてはアキュムレータ４０に貯留される。なお、アキュムレータ４０に貯留した冷媒は、サイクル内における冷媒のバッファ機能を有しており、これによりサイクル内において冷媒の相平衡が保持されている。   In the evaporator 20, the liquid refrigerant is vaporized by heat absorption from the outside air to become a gas refrigerant. Actually, the refrigerant exiting the evaporator 20 is in a gas-liquid two-phase state including liquid refrigerant without being completely vaporized, and reaches the accumulator 40 through the internal heat exchanger 30 while maintaining the gas-liquid two-phase state. The gas and liquid are separated in the accumulator 40. Then, only the gas refrigerant is circulated in the cycle toward the first compressor 10. On the other hand, the liquid refrigerant is stored in the accumulator 40. Note that the refrigerant stored in the accumulator 40 has a refrigerant buffer function in the cycle, whereby the refrigerant phase balance is maintained in the cycle.

ところで、上述した如く、受液器１７と第２膨張弁１８との間の配管と蒸発器２０とアキュムレータ４０との間の配管との間には内部熱交換器３０が設けられている。これより、受液器１７から第２膨張弁１８に向かう液冷媒は、蒸発器２０を出た気液二相状態の冷媒によって冷却される。
即ち、上述した如く、冷媒を超臨界で使用するシステムでは、第２膨張弁１８に至る冷媒は飽和液線上の液冷媒であることから（図２に破線で示す）、受液器１７から第２膨張弁１８までの間では、外気温が高いと冷媒は液化しても配管内で気化して所謂フラッシュガスを発生し、気体状の冷媒と液状の冷媒とが混在した状態になり易いのであるが、当該冷媒が蒸発器２０を出た気液二相状態の冷媒との熱交換によって過冷却状態とされてかかるフラッシュガスの発生が抑制され、良好に液状とされる（図２に実線で示す）。 As described above, the internal heat exchanger 30 is provided between the pipe between the liquid receiver 17 and the second expansion valve 18 and the pipe between the evaporator 20 and the accumulator 40. Thus, the liquid refrigerant from the liquid receiver 17 toward the second expansion valve 18 is cooled by the gas-liquid two-phase refrigerant that has exited the evaporator 20.
That is, as described above, in the system that uses the refrigerant in a supercritical state, the refrigerant reaching the second expansion valve 18 is a liquid refrigerant on the saturated liquid line (shown by a broken line in FIG. 2), so Between the two expansion valves 18, if the outside air temperature is high, even if the refrigerant is liquefied, it is vaporized in the pipe and so-called flash gas is generated, so that the gaseous refrigerant and the liquid refrigerant tend to be mixed. However, the refrigerant is brought into a supercooled state by heat exchange with the gas-liquid two-phase refrigerant that has left the evaporator 20 to suppress the generation of the flash gas, and the liquid is satisfactorily liquid (solid line in FIG. 2). ).

この際、特に、アキュムレータ４０に至る前の蒸発器２０を出た冷媒は気液二相状態であるため、ガス冷媒と液冷媒とが混在しており、受液器１７と第２膨張弁１８との間の配管を流れる冷媒は、蒸発器２０を出たガス冷媒のみならず液冷媒によって良好に過冷却状態にまで冷却される。つまり、受液器１７から第２膨張弁１８に向かう冷媒は、顕熱利用のみならず液冷媒の潜熱利用によって十分に冷却されて液状に保持され、ガス冷媒の顕熱利用による熱交換だけの場合に比べてフラッシュガスの発生がより一層良好に抑制される。   At this time, in particular, since the refrigerant exiting the evaporator 20 before reaching the accumulator 40 is in a gas-liquid two-phase state, gas refrigerant and liquid refrigerant are mixed, and the liquid receiver 17 and the second expansion valve 18 are mixed. The refrigerant flowing through the pipe between the two is cooled not only to the gas refrigerant exiting the evaporator 20 but also to the supercooled state well by the liquid refrigerant. That is, the refrigerant from the liquid receiver 17 toward the second expansion valve 18 is sufficiently cooled and held in a liquid state not only by using sensible heat but also by using latent heat of the liquid refrigerant, and only for heat exchange by using sensible heat of the gas refrigerant. Compared to the case, the generation of flash gas is suppressed even better.

これにより、蒸発器２０の吸熱性能を高めることが可能となり、ガスインジェクションサイクルの作用に加え、冷凍サイクルにおける成績係数（ＣＯＰ）ひいては冷凍能力の向上を図ることができる。
また、ここでは、ガス冷却器１３と第１膨張弁１４との間の配管とバイパス管路５２との間にはガス熱交換器５０が設けられており、流量調整弁５４の調節によりガス冷却器１３から第１膨張弁１４に向かう冷媒は、気液分離器１５から第２圧縮機１２に向かうインジェクションガスによっても冷却される。 Thereby, it becomes possible to improve the heat absorption performance of the evaporator 20, and in addition to the effect | action of a gas injection cycle, the coefficient of performance (COP) in a refrigerating cycle and a refrigerating capacity can be aimed at.
Further, here, a gas heat exchanger 50 is provided between the pipe between the gas cooler 13 and the first expansion valve 14 and the bypass line 52, and the gas cooling is performed by adjusting the flow rate adjusting valve 54. The refrigerant from the vessel 13 toward the first expansion valve 14 is also cooled by the injection gas from the gas-liquid separator 15 toward the second compressor 12.

これにより、ガス冷却器１３から第２膨張弁１８を経て蒸発器２０に向かう冷媒のエンタルピを増加させて、ＣＯＰひいては冷凍能力の向上を図ることができる。
また、蒸発器２０から流出する液冷媒は内部熱交換器３０で潜熱利用されて気化するので、内部熱交換器３０と第１圧縮機１０との間にアキュムレータ４０を介装することで、アキュムレータ４０に貯留される液冷媒を少なく抑えるようにでき、アキュムレータ４０の小型化を図ることも可能である。 Thereby, the enthalpy of the refrigerant | coolant which goes to the evaporator 20 through the 2nd expansion valve 18 from the gas cooler 13 can be increased, and improvement of COP and a refrigerating capacity can be aimed at.
Further, since the liquid refrigerant flowing out of the evaporator 20 is vaporized by using latent heat in the internal heat exchanger 30, the accumulator 40 is interposed between the internal heat exchanger 30 and the first compressor 10, thereby accumulating the accumulator. The liquid refrigerant stored in 40 can be reduced, and the accumulator 40 can be reduced in size.

次に、第２実施例について説明する。
図３には、本発明の第２実施例に係る冷凍システムの概略構成図が示されている。
当該第２実施例に係る冷凍システムでは、複数の蒸発器２０ａ、２０ｂを有している点が上記第１実施例と異なっており、以下、第１実施例と同一部分については説明を省略し、第１実施例と異なる部分を中心に説明する。 Next, a second embodiment will be described.
FIG. 3 shows a schematic configuration diagram of a refrigeration system according to a second embodiment of the present invention.
The refrigeration system according to the second embodiment is different from the first embodiment in that it has a plurality of evaporators 20a and 20b. Hereinafter, the description of the same parts as the first embodiment is omitted. The description will focus on the differences from the first embodiment.

同図に示すように、内部熱交換器３０から再び内部熱交換器３０に向かう配管は複数の分岐管路２１、２２に分岐し合流しており、各分岐管路２１、２２にはそれぞれ蒸発器２０ａ、２０ｂが互いに並列となるように配設されている。このような構成は、例えばコンビニエンスストア等において複数の冷凍装置を有する場合に多用される。
また、各分岐管路２１、２２には、蒸発器２０ａ、２０ｂの各上流に直列に位置して第２膨張弁１８ａ、１８ｂがそれぞれ設けられている。 As shown in the figure, the piping from the internal heat exchanger 30 to the internal heat exchanger 30 is branched into a plurality of branch pipes 21 and 22 and merged, and each branch pipe 21 and 22 is evaporated. The containers 20a and 20b are arranged in parallel with each other. Such a configuration is frequently used when a plurality of refrigeration apparatuses are provided in, for example, a convenience store.
The branch pipes 21 and 22 are provided with second expansion valves 18a and 18b, respectively, which are positioned in series upstream of the evaporators 20a and 20b.

このように複数の直列をなす第２膨張弁１８ａ、蒸発器２０ａと直列をなす第２膨張弁１８ｂ、２０ｂとが互いに並列となるように設けられていると、上述したように、例えば各分岐管路２１、２２の分岐部に至るまでにフラッシュガスが発生してしまうと冷媒を各蒸発器２０ａ、２０ｂに均等に分流させることが困難となり、蒸発器２０ａ、２０ｂ間で吸熱性能にばらつきが生じるおそれがある。   When the second expansion valves 18a in series and the second expansion valves 18b and 20b in series with the evaporator 20a are provided in parallel with each other, as described above, for example, each branch If flash gas is generated before reaching the branch portions of the pipelines 21 and 22, it becomes difficult to evenly distribute the refrigerant to each of the evaporators 20a and 20b, and the endothermic performance varies between the evaporators 20a and 20b. May occur.

しかしながら、このような構成であっても、受液器１７と各第２膨張弁１８ａ、１８ｂとの間の配管と蒸発器２０ａ、２０ｂとアキュムレータ４０との間の配管との間には内部熱交換器３０が設けられていることから、受液器１７から各分岐管路２１、２２の分岐部に向かう液冷媒は、蒸発器２０ａ、２０ｂを出た気液二相状態の冷媒によって良好に過冷却状態にまで冷却され、フラッシュガスの発生が抑制される。   However, even with such a configuration, internal heat is not generated between the pipe between the liquid receiver 17 and each of the second expansion valves 18a and 18b and the pipe between the evaporators 20a and 20b and the accumulator 40. Since the exchanger 30 is provided, the liquid refrigerant heading from the liquid receiver 17 toward the branch portions of the branch pipes 21 and 22 is favorably obtained by the refrigerant in the gas-liquid two-phase state exiting the evaporators 20a and 20b. It cools to a supercooled state and generation | occurrence | production of flash gas is suppressed.

従って、複数の蒸発器２０ａ、２０ｂを互いに並列に設けた場合であっても、冷媒を確実に液状に維持したまま各第２膨張弁１８ａ、１８ｂに均等にバランスよく分流させることが可能となる。
即ち、各分岐管路２１、２２にそれぞれ第２膨張弁１８ａ、１８ｂを設けることにより、冷媒を液状に維持したまま各分岐管路２１、２２に確実に均等に分流させることができ、各蒸発器２０ａ、２０ｂの吸熱性能をより一層ばらつきなく高め、冷凍サイクルにおける冷凍能力のさらなる向上を図ることが可能である。 Therefore, even when the plurality of evaporators 20a and 20b are provided in parallel with each other, it is possible to distribute the refrigerant equally and in a balanced manner to each of the second expansion valves 18a and 18b while maintaining the refrigerant in a liquid state. .
That is, by providing the second expansion valves 18a and 18b in the branch pipes 21 and 22, respectively, the refrigerant can be surely and equally divided into the branch pipes 21 and 22 while maintaining the liquid state. It is possible to improve the endothermic performance of the containers 20a and 20b more evenly and further improve the refrigeration capacity in the refrigeration cycle.

なお、ここでは各分岐管路２１、２２にそれぞれ第２膨張弁１８ａ、１８ｂを設けているが、各分岐管路２１、２２に蒸発器２０ａ、２０ｂ、分岐前の管路に上記第１実施例と同様の第２膨張弁１８を一つだけ配設することも可能である。このような構成であっても、内部熱交換器３０がない場合に比べて第２膨張弁１８に向かう冷媒が良好に液状に保持されるため、安定的に冷媒を供給することが可能である。   Here, the second expansion valves 18a and 18b are provided in the branch pipelines 21 and 22, respectively. However, the evaporators 20a and 20b are provided in the branch pipelines 21 and 22, respectively. It is also possible to dispose only one second expansion valve 18 similar to the example. Even with such a configuration, the refrigerant toward the second expansion valve 18 is better maintained in a liquid state than in the case where the internal heat exchanger 30 is not provided, so that the refrigerant can be supplied stably. .

これにより、第２膨張弁１８が一つであっても、複数の蒸発器２０ａ、２０ｂ間で吸熱性能にばらつきが生じることが低減され、各蒸発器２０ａ、２０ｂにおける吸熱性能を高めることができる。
次に、第３実施例について説明する。
図４には、本発明の第３実施例に係る冷凍システムの概略構成図が示されている。 Thereby, even if the number of the second expansion valve 18 is one, the occurrence of variation in the heat absorption performance among the plurality of evaporators 20a and 20b is reduced, and the heat absorption performance in each of the evaporators 20a and 20b can be enhanced. .
Next, a third embodiment will be described.
FIG. 4 shows a schematic configuration diagram of a refrigeration system according to a third embodiment of the present invention.

当該第３実施例に係る冷凍システムでは、内部熱交換器３０から再び内部熱交換器３０に向かう配管が３本以上の複数（ここでは３本）の分岐管路２１、２２、２３に分岐され、複数の蒸発器２０ａ、２０ｂ、２０ｃ及び第２膨張弁１８ａ、１８ｂ、１８ｃとともに複数の内部熱交換器（内部熱交換要素）３０ａ、３０ｂを有している点が上記第１、２実施例と異なっており、以下、第１、２実施例と同一部分については説明を省略し、第１、２実施例と異なる部分を中心に説明する。   In the refrigeration system according to the third embodiment, the pipe from the internal heat exchanger 30 to the internal heat exchanger 30 is branched into three or more (here, three) branch pipes 21, 22, and 23. The first and second embodiments described above have a plurality of internal heat exchangers (internal heat exchange elements) 30a, 30b together with a plurality of evaporators 20a, 20b, 20c and second expansion valves 18a, 18b, 18c. Hereinafter, the description of the same parts as those of the first and second embodiments will be omitted, and the description will focus on parts different from the first and second embodiments.

同図に示すように、当該第３実施例では、受液器１７の下流側で配管は複数の分岐管路２１、２２、２３に分岐し合流しており、各分岐管路２１、２２、２３には、それぞれ蒸発器２０ａ、２０ｂ、２０ｃが互いに並列となるように配設され、蒸発器２０ａ、２０ｂ、２０ｃの各上流に直列に位置して第２膨張弁１８ａ、１８ｂ、１８ｃが設けられている。そして、分岐管路２１、２２、２３の２箇所以上の分岐部（ここでは２箇所）の各上流に位置してそれぞれ内部熱交換器３０ａ、３０ｂが設けられている。   As shown in the figure, in the third embodiment, the pipe branches and merges into a plurality of branch pipes 21, 22, 23 on the downstream side of the liquid receiver 17, and the branch pipes 21, 22, 23, evaporators 20a, 20b, 20c are arranged in parallel with each other, and second expansion valves 18a, 18b, 18c are provided in series upstream of the evaporators 20a, 20b, 20c. It has been. And the internal heat exchangers 30a and 30b are each provided in the upstream of two or more branch parts (here two places) of the branch pipe lines 21, 22, and 23, respectively.

このように分岐管路２１、２２、２３の分岐部の手前にそれぞれ内部熱交換器３０ａ、３０ｂが設けられていると、各分岐管路２１、２２、２３において冷媒を良好に液状にでき、液状の冷媒を確実に各第２膨張弁１８ａ、１８ｂ、１８ｃに向けて供給することができる。
これにより、複数の蒸発器２０ａ、２０ｂ、２０ｃを設ける場合において、各蒸発器２０ａ、２０ｂ、２０ｃの吸熱性能を高め、冷凍サイクルにおける冷凍能力のさらなる向上を図ることが可能である。 When the internal heat exchangers 30a and 30b are respectively provided in front of the branch portions of the branch pipes 21, 22, and 23 as described above, the refrigerant can be favorably liquefied in the branch pipes 21, 22, and 23. A liquid refrigerant can be reliably supplied toward the second expansion valves 18a, 18b, and 18c.
Thereby, when providing several evaporator 20a, 20b, 20c, it is possible to improve the thermal absorption performance of each evaporator 20a, 20b, 20c, and to aim at the further improvement of the refrigerating capacity in a refrigerating cycle.

以上で本発明の一実施形態についての説明を終えるが、本発明は上記実施形態に限定されるものではない。
例えば、上記実施形態では、内部熱交換器３０或いは内部熱交換器３０ａ、３０ｂを用いて熱交換を行うようにしているが、第１乃至第３実施例において、内部熱交換要素は配管同士を抱き合わせて接触させるようなものであってもよい。即ち、図５を参照すると、本発明の他の実施例として上記第３実施例の内部熱交換器３０ａ、３０ｂに代えて配管同士を抱き合わせて接触させた構成が模式的に例示されているが、内部熱交換要素は、このように配管同士を単に接触させるだけの構成であってもよい。このようにすれば、簡単な構成にして、フラッシュガスの発生を好適に防止することができる。 This is the end of the description of the embodiment of the present invention, but the present invention is not limited to the above embodiment.
For example, in the above-described embodiment, heat exchange is performed using the internal heat exchanger 30 or the internal heat exchangers 30a and 30b. However, in the first to third examples, the internal heat exchange elements are pipes. It may be such that they are tangled and brought into contact. That is, referring to FIG. 5, as another embodiment of the present invention, a configuration in which pipes are tangled and contacted instead of the internal heat exchangers 30 a and 30 b of the third embodiment is schematically illustrated. In this way, the internal heat exchange element may be configured to simply bring the pipes into contact with each other. In this way, it is possible to suitably prevent the generation of flash gas with a simple configuration.

また、上記実施形態では、第１圧縮機１０及び第２圧縮機１２を設け、インジェクションガスを第２圧縮機１２に供給するようにガスインジェクションサイクルを構成したが、図６に一部分を示すように、本発明のさらに他の実施例として、ガスインジェクションサイクルを一つの圧縮機１０’を含んで構成し、気液分離器１５のガス出口側と圧縮機１０’の圧縮中間圧部とを連結配管１６により接続するようにしてもよい。この場合であっても、インジェクションガスが圧縮機１０’の圧縮中間圧部に供給され、ガスインジェクションサイクルに関し上記同様の作用効果を得ることができる。   Moreover, in the said embodiment, although the 1st compressor 10 and the 2nd compressor 12 were provided and the gas injection cycle was comprised so that injection gas might be supplied to the 2nd compressor 12, as shown in part in FIG. As still another embodiment of the present invention, the gas injection cycle includes a single compressor 10 ', and the gas outlet side of the gas-liquid separator 15 and the compression intermediate pressure portion of the compressor 10' are connected by piping. 16 may be connected. Even in this case, the injection gas is supplied to the compression intermediate pressure portion of the compressor 10 ′, and the same effect as described above can be obtained with respect to the gas injection cycle.

また、上記実施形態では、内部熱交換器３０或いは内部熱交換器３０ａ、３０ｂとアキュムレータ４０とをそれぞれ個別に設けるようにしているが、これらを一体にするようにしてもよい。このようにすれば、冷凍システムの簡素化、低廉化を図りながら、フラッシュガスの発生を好適に防止することができる。
また、上記実施形態では、気液分離器１５の液出口側に受液器１７を別途設けるようにしているが、これらを一体にするようにしてもよい。このようにすれば、やはり冷凍システムの簡素化、低廉化を図りながら、フラッシュガスの発生を好適に防止することができる。 Moreover, in the said embodiment, although the internal heat exchanger 30 or internal heat exchanger 30a, 30b and the accumulator 40 are each provided separately, you may make these integrate. In this manner, generation of flash gas can be suitably prevented while simplifying and reducing the cost of the refrigeration system.
Moreover, in the said embodiment, although the liquid receiver 17 is separately provided in the liquid outlet side of the gas-liquid separator 15, you may make these integrate. In this way, generation of flash gas can be suitably prevented while also simplifying and reducing the cost of the refrigeration system.

また、上記実施形態では、ガスインジェクションサイクルを有した冷凍システムについて説明したが、ガスインジェクションサイクルについては必ずしも設けなくてもよい。即ち、図示しないものの、第１圧縮機１０及び第２圧縮機１２を一つの圧縮機とし、第１膨張弁１４及び第２膨張弁１８を一つの膨張弁（膨張器）とし、気液分離器１５、連結配管１６、受液器１７を省略した通常の冷凍サイクルにおいて、ガス冷却器１３と膨張弁との間の配管に内部熱交換器３０或いは内部熱交換器３０ａ、３０ｂを設けるようにしてもよい。このようにガスインジェクションサイクルを有しない構成であっても、本発明の効果を得ることができる。   Moreover, although the said embodiment demonstrated the refrigerating system which has a gas injection cycle, it does not necessarily need to provide about a gas injection cycle. That is, although not shown, the first compressor 10 and the second compressor 12 are one compressor, the first expansion valve 14 and the second expansion valve 18 are one expansion valve (expander), and a gas-liquid separator. 15. In a normal refrigeration cycle in which the connecting pipe 16 and the liquid receiver 17 are omitted, the internal heat exchanger 30 or the internal heat exchangers 30a and 30b are provided in the pipe between the gas cooler 13 and the expansion valve. Also good. Thus, even if it is the structure which does not have a gas injection cycle, the effect of this invention can be acquired.

また、上記実施形態では、ガス熱交換器５０を設けるようにしているが、ガス熱交換器５０については必ずしも設けなくてもよい。即ち、図示しないものの、ガス熱交換器５０を設けることなく内部熱交換器３０或いは内部熱交換器３０ａ、３０ｂを設けるだけで、本発明の効果を得ることができる。
また、上記実施形態では、冷媒として二酸化炭素（ＣＯ２）を用いるようにしているが、冷媒は超臨界で使用する二酸化炭素に限られるものではなく、冷媒を超臨界で使用するか否かに拘わらず、冷媒の種類に拘わらず、本発明を好適に適用可能である。 In the above embodiment, the gas heat exchanger 50 is provided. However, the gas heat exchanger 50 is not necessarily provided. That is, although not shown, the effect of the present invention can be obtained only by providing the internal heat exchanger 30 or the internal heat exchangers 30a and 30b without providing the gas heat exchanger 50.
In the above embodiment, carbon dioxide (CO 2 ) is used as the refrigerant. However, the refrigerant is not limited to carbon dioxide used in a supercritical state, and whether or not the refrigerant is used in a supercritical state. Regardless of the type of refrigerant, the present invention can be preferably applied.

本発明の第１実施例に係る冷凍システムの概略構成図である。1 is a schematic configuration diagram of a refrigeration system according to a first embodiment of the present invention. 本発明に係る冷凍システムのｐ−ｈ線図である。It is a ph diagram of the refrigeration system concerning the present invention. 本発明の第２実施例に係る冷凍システムの概略構成図である。It is a schematic block diagram of the refrigeration system which concerns on 2nd Example of this invention. 本発明の第３実施例に係る冷凍システムの概略構成図である。It is a schematic block diagram of the refrigeration system which concerns on 3rd Example of this invention. 本発明の他の実施例に係る冷凍システムの概略構成図である。It is a schematic block diagram of the refrigeration system which concerns on the other Example of this invention. 本発明のさらに他の実施例に係る冷凍システムの概略構成図の一部である。It is a part of schematic structure figure of the refrigerating system concerning other examples of the present invention.

符号の説明Explanation of symbols

１０ 第１圧縮機
１０’ 圧縮機
１２ 第２圧縮機
１３ ガス冷却器（放熱器）
１４ 第１膨張弁（第１膨張器）
１５ 気液分離器
１６ 連結配管（ガスインジェクション管路）
１８、１８ａ、１８ｂ、１８ｃ 第２膨張弁（第２膨張器、膨張器）
２０、２０ａ、２０ｂ、２０ｃ 蒸発器
２１、２２、２３ 分岐管路
３０、３０ａ、３０ｂ内部熱交換器（内部熱交換要素）
４０ アキュムレータ
５０ ガス熱交換器 DESCRIPTION OF SYMBOLS 10 1st compressor 10 'compressor 12 2nd compressor 13 Gas cooler (heat radiator)
14 First expansion valve (first expander)
15 Gas-liquid separator 16 Connection piping (gas injection conduit)
18, 18a, 18b, 18c Second expansion valve (second expander, expander)
20, 20a, 20b, 20c Evaporator 21, 22, 23 Branch line 30, 30a, 30b Internal heat exchanger (internal heat exchange element)
40 Accumulator 50 Gas heat exchanger

Claims (10)

冷媒を圧縮する圧縮機と、該圧縮機で昇圧された冷媒を冷却する放熱器と、該放熱器で冷却された冷媒を減圧膨張させる膨張器と、該膨張器で減圧された冷媒を蒸発させる蒸発器とを順次配管接続してなる冷凍システムであって、
前記放熱器と前記膨張器との間の配管と前記蒸発器と前記圧縮機との間の配管とに跨いで設けられ、前記放熱器から前記膨張器に向かう冷媒と前記蒸発器から前記圧縮機に向かう冷媒との間で熱交換を行う内部熱交換要素と、
前記内部熱交換要素と前記圧縮機との間の配管に介装され、液状の冷媒を貯留するアキュムレータと、
を備えたことを特徴とする冷凍システム。 A compressor that compresses the refrigerant; a radiator that cools the refrigerant pressurized by the compressor; an expander that decompresses and expands the refrigerant cooled by the radiator; and evaporates the refrigerant decompressed by the expander A refrigeration system in which an evaporator and a pipe are sequentially connected,
The refrigerant between the radiator and the expander and the pipe between the evaporator and the compressor are provided to straddle, and the refrigerant from the radiator to the expander and the evaporator to the compressor An internal heat exchange element that exchanges heat with the refrigerant toward
An accumulator that is interposed in a pipe between the internal heat exchange element and the compressor and stores a liquid refrigerant;
A refrigeration system comprising: 前記冷媒は超臨界で使用するものであることを特徴とする、請求項１記載の冷凍システム。   The refrigeration system according to claim 1, wherein the refrigerant is used in a supercritical state. 前記圧縮機は第１圧縮機と該第１圧縮機の下流側に直列に接続された第２圧縮機とからなるとともに前記膨張器は第１膨張器と該第１膨張器の下流側に直列に接続された第２膨張器とからなり、
前記第１膨張器と前記第２膨張器との間に介装され、冷媒の気液分離を行って液状の冷媒を前記第２膨張器に供給する気液分離器と、
該気液分離器と前記第１圧縮機及び前記第２圧縮機間の管路とを連結して設けられ、前記気液分離器で分離された気体状の冷媒をインジェクションガスとして前記第２圧縮機に供給するガスインジェクション管路とを備え、
前記内部熱交換要素は、前記気液分離器と前記第２膨張器との間に介装されていることを特徴とする、請求項１または２記載の冷凍システム。 The compressor includes a first compressor and a second compressor connected in series downstream of the first compressor, and the expander is in series with the first expander and downstream of the first expander. A second inflator connected to
A gas-liquid separator that is interposed between the first expander and the second expander, performs gas-liquid separation of the refrigerant, and supplies liquid refrigerant to the second expander;
The gas-liquid separator is connected to a pipe line between the first compressor and the second compressor, and the second compression is performed using a gaseous refrigerant separated by the gas-liquid separator as an injection gas. A gas injection line for supplying to the machine,
The refrigeration system according to claim 1 or 2, wherein the internal heat exchange element is interposed between the gas-liquid separator and the second expander. 前記圧縮機は一つであり、
前記第１膨張器と前記第２膨張器との間に介装され、冷媒の気液分離を行って液状の冷媒を前記第２膨張器に供給する気液分離器と、
該気液分離器と前記圧縮機の圧縮中間圧部とを連通して設けられ、前記気液分離器で分離された気体状の冷媒をインジェクションガスとして前記圧縮機の圧縮中間圧部に供給するガスインジェクション管路とを備え、
前記内部熱交換要素は、前記気液分離器と前記第２膨張器との間に介装されていることを特徴とする、請求項１または２記載の冷凍システム。 The compressor is one;
A gas-liquid separator that is interposed between the first expander and the second expander, performs gas-liquid separation of the refrigerant, and supplies liquid refrigerant to the second expander;
The gas-liquid separator and a compression intermediate pressure part of the compressor are provided in communication with each other, and gaseous refrigerant separated by the gas-liquid separator is supplied to the compression intermediate pressure part of the compressor as an injection gas. A gas injection line,
The refrigeration system according to claim 1 or 2, wherein the internal heat exchange element is interposed between the gas-liquid separator and the second expander. 前記気液分離器からの液状の冷媒を一時的に貯留する受液器を備え、
該受液器は、前記気液分離器と一体に設けられていることを特徴とする、請求項３または４記載の冷凍システム。 A liquid receiver that temporarily stores liquid refrigerant from the gas-liquid separator;
The refrigeration system according to claim 3 or 4, wherein the liquid receiver is provided integrally with the gas-liquid separator. 前記蒸発器は複数からなるとともに前記膨張器は複数からなり、
前記内部熱交換要素から前記膨張器及び前記蒸発器を経て再び前記内部熱交換要素に向かう管路は複数の分岐管路に分岐し合流しており、
前記複数の蒸発器は、互いに並列となるよう各々前記分岐管路に配設され、前記複数の膨張器は、各々前記分岐管路に前記蒸発器と直列に配設されていることを特徴とする、請求項１または２記載の冷凍システム。 The evaporator comprises a plurality and the expander comprises a plurality,
The pipe from the internal heat exchange element to the internal heat exchange element again through the expander and the evaporator is branched into and merged with a plurality of branch pipes,
The plurality of evaporators are respectively disposed in the branch pipes so as to be parallel to each other, and the plurality of expanders are each disposed in series with the evaporator in the branch pipes. The refrigeration system according to claim 1 or 2. 前記蒸発器は複数からなるとともに前記第２膨張器は複数からなり、
前記内部熱交換要素から前記第２膨張器及び前記蒸発器を経て再び前記内部熱交換要素に向かう管路は複数の分岐管路に分岐し合流しており、
前記複数の蒸発器は、互いに並列となるよう各々前記分岐管路に配設され、前記複数の第２膨張器は、各々前記分岐管路に前記蒸発器と直列に配設されていることを特徴とする、請求項３乃至５のいずれか記載の冷凍システム。 The evaporator comprises a plurality and the second expander comprises a plurality,
The pipe from the internal heat exchange element to the internal heat exchange element through the second expander and the evaporator again branches into a plurality of branch pipes,
The plurality of evaporators are respectively disposed in the branch pipes so as to be parallel to each other, and the plurality of second expanders are respectively disposed in series with the evaporator in the branch pipes. The refrigeration system according to any one of claims 3 to 5, wherein the refrigeration system is characterized. 前記分岐管路は３本以上であって該分岐管路の分岐部は２箇所以上あり、
前記内部熱交換要素は、複数からなり、これら分岐部の手前にそれぞれ配設されていることを特徴とする、請求項６または７記載の冷凍システム。 There are three or more branch pipes, and there are two or more branch parts of the branch pipes.
The refrigeration system according to claim 6 or 7, wherein the internal heat exchange element includes a plurality of internal heat exchange elements and is disposed in front of the branch portions. 前記内部熱交換要素は配管同士を抱き合わせるよう構成されることを特徴とする、請求項１乃至８のいずれか記載の冷凍システム。   The refrigeration system according to any one of claims 1 to 8, wherein the internal heat exchange element is configured to tie pipes together. 前記アキュムレータは、前記内部熱交換要素と一体に設けられていることを特徴とする、請求項１乃至７のいずれか記載の冷凍システム。   The refrigeration system according to any one of claims 1 to 7, wherein the accumulator is provided integrally with the internal heat exchange element.
JP2008304079A 2008-11-28 2008-11-28 Refrigerating system Pending JP2010127563A (en)

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