JP2011133123A - Refrigerating cycle device - Google Patents

Refrigerating cycle device Download PDF

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JP2011133123A
JP2011133123A JP2009290492A JP2009290492A JP2011133123A JP 2011133123 A JP2011133123 A JP 2011133123A JP 2009290492 A JP2009290492 A JP 2009290492A JP 2009290492 A JP2009290492 A JP 2009290492A JP 2011133123 A JP2011133123 A JP 2011133123A
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refrigerant
ejector
refrigerant circuit
generator
circuit
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Inkan Ri
允煥 李
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Mitsubishi Electric Corp
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerant circuit of high efficiency, satisfying load condition by combining an ejector refrigerant circuit with a refrigerant circuit using a compressor, as the ejector refrigerant circuit applying solar heat as a heat source, has difficulty in supplying heat quantity to satisfy the load condition, and has low COP (coefficient of performance). <P>SOLUTION: In the vapor compression type refrigerant circuit 110, the compressor 9, a condenser 2a, a supercooler 11, an expanding mechanism 5a and an evaporator 1 are connected in this order, and a first refrigerant is circulated therein. In the ejector type refrigerant circuit 120, an ejector 6, a condenser 2b, and an expanding mechanism 5b are connected in this order, and a second refrigerant is circulated therein. The second refrigerant circulated in the ejector type refrigerant circuit 120 flows out from the expanding mechanism 5b in a liquid state, flows into the supercooler 11, absorbs heat from the first refrigerant in the vapor compression type refrigerant circuit 110 passing through the supercooler 11, to be evaporated, further flows in a suction opening 62 of the ejector in a gas state, flows out from an outlet 63 of the ejector, and successively circulates in the condenser 2b, the expanding mechanism 5b and the supercooler 11. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

本発明は、蒸気圧縮式冷媒回路とエジェクタ式冷媒回路とを組み合わせた複合冷媒回路に関する。   The present invention relates to a composite refrigerant circuit that combines a vapor compression refrigerant circuit and an ejector refrigerant circuit.

パネル面積当りのエネルギー利用率を高めて、太陽光発電システムの経済性を向上させることを目的に、従来利用されていなかった熱を回収する集熱パネルを一枚のパネルに複合化した太陽光電熱ハイブリッドパネルが開発されている。この太陽光電熱ハイブリッドパネルからの排熱を駆動熱源とすることで冷凍・空調システムを運転する冷媒回路として、デシカントサイクル、エジェクタ式冷媒回路、吸収式サイクル、吸着サイクル、ケミカルサイクルなどがある。その中でも吸収式サイクルは低温熱源を駆動源とする場合に有効である。しかし、吸収式サイクルを用いたシステムはその構成とメンテナンスが複雑であるため、初期コストや運転コストが高い。一方、エジェクタを使用したサイクルは設置コスト、運転コスト、信頼性などの面でメリットがあるため、従来から検討されてきた（例えば、特許文献１，２）。   In order to increase the energy utilization rate per panel area and improve the economic efficiency of the photovoltaic power generation system, a solar panel that combines a heat collection panel that collects heat that has not been used in the past into a single panel. Thermal hybrid panels have been developed. There are a desiccant cycle, an ejector-type refrigerant circuit, an absorption-type cycle, an adsorption cycle, a chemical cycle, and the like as a refrigerant circuit that operates the refrigeration / air-conditioning system by using the exhaust heat from the solar electric hybrid panel as a driving heat source. Among them, the absorption cycle is effective when a low-temperature heat source is used as a driving source. However, since the system using the absorption cycle is complicated in configuration and maintenance, the initial cost and the operation cost are high. On the other hand, since a cycle using an ejector has advantages in terms of installation cost, operation cost, reliability, and the like, it has been conventionally studied (for example, Patent Documents 1 and 2).

特開昭６０−１７５９８０号公報JP-A-60-175980 特開２００１−１９４０２５号公報JP 2001-194025 A

太陽熱からの収集熱を熱源とするエジェクタ式冷媒回路システムは、日射量が変動するため単独システムでは全負荷条件に対して成立するのは困難であるとともに、駆動熱源の温度が低いためＣＯＰ（Ｃｏｅｆｆｉｃｉｅｎｔ Ｏｆ Ｐｅｒｆｏｒｍａｎｃｅ）が比較的に低い。しかしながら、上記のエジェクタ式冷媒回路システムは、回路構成が簡単であるため設置コストが安価である点、電気駆動部が少ないため運転コストが安価である点、比較的低い熱源温度で作動可能である点、機械的稼動部分が少ないため信頼性が高い点など、多数の重要なメリットがある。   An ejector-type refrigerant circuit system that uses the collected heat from solar heat as a heat source is difficult to achieve for all load conditions in a single system because the amount of solar radiation fluctuates, and because the temperature of the drive heat source is low, COP (Coefficient Of Performance) is relatively low. However, the above-described ejector-type refrigerant circuit system has a simple circuit configuration, so that the installation cost is low, the operation cost is low because there are few electric drive units, and it can operate at a relatively low heat source temperature. There are many important merits such as high reliability because there are few mechanical working parts.

本発明は、エジェクタ式冷媒回路のメリットを有し、太陽熱を駆動熱源とするエジェクタ式冷媒回路を、通常の蒸気圧縮式冷媒回路と組み合せて複合冷媒回路化することで、冷凍・空調システム全体の年間性能を向上させることを目的とする。   The present invention has the advantage of an ejector-type refrigerant circuit, and an ejector-type refrigerant circuit that uses solar heat as a driving heat source is combined with an ordinary vapor compression refrigerant circuit to form a composite refrigerant circuit. The purpose is to improve the annual performance.

この発明の冷凍サイクル装置は、
圧縮機、第１の放熱器、過冷却器、第１の膨張機構、蒸発器が、これらの順に閉回路状に第１冷媒の循環流路で接続され、第１冷媒がこれらの順に循環する第１の冷媒回路と、
圧縮機を代替するエジェクタ、第２の放熱器、第２の膨張機構が、これらの順に閉回路状に第２冷媒の循環流路で接続され、第２冷媒がこれらの順に循環する第２の冷媒回路と
を備え、
前記第２の冷媒回路を循環する前記第２冷媒は、
前記第２の膨張機構から液状態で流出して前記第１の冷媒回路の前記過冷却器に流入し、前記過冷却器を通過する前記第１の冷媒回路の前記第１冷媒から吸熱して蒸発し、気体状態で前記エジェクタの吸引口に流入し、前記エジェクタの出口から流出して、前記第２の放熱器、前記第２の膨張機構、前記過冷却器の順に循環することを特徴とする。 The refrigeration cycle apparatus of the present invention is
The compressor, the first radiator, the supercooler, the first expansion mechanism, and the evaporator are connected in the order of these in a closed circuit shape with the circulation path of the first refrigerant, and the first refrigerant circulates in this order. A first refrigerant circuit;
An ejector that substitutes for the compressor, a second radiator, and a second expansion mechanism are connected in a closed circuit form in this order by a circulation path of the second refrigerant, and the second refrigerant circulates in this order. A refrigerant circuit,
The second refrigerant circulating in the second refrigerant circuit is
The liquid flows out from the second expansion mechanism, flows into the subcooler of the first refrigerant circuit, and absorbs heat from the first refrigerant of the first refrigerant circuit passing through the subcooler. It evaporates, flows into the suction port of the ejector in a gaseous state, flows out of the outlet of the ejector, and circulates in the order of the second radiator, the second expansion mechanism, and the subcooler. To do.

本発明により、エジェクタ式冷媒回路と、通常の蒸気圧縮式冷媒回路とを組み合わせることにより、日射量の変動と関係なく、システムが全条件に対して成立することが可能な、エジェクタ式冷媒回路を用いた冷凍サイクル装置を提供できる。   According to the present invention, there is provided an ejector-type refrigerant circuit that can be established for all conditions regardless of fluctuations in solar radiation by combining an ejector-type refrigerant circuit and a normal vapor compression refrigerant circuit. The used refrigeration cycle apparatus can be provided.

実施の形態１における、エジェクタを使用した通常の冷凍サイクルを示す図。The figure which shows the normal refrigerating cycle which uses the ejector in Embodiment 1. FIG. 実施の形態１における、エジェクタの原理を説明する図。FIG. 3 is a diagram for explaining the principle of an ejector in the first embodiment. 実施の形態１における、複合冷媒回路のＰ−ｈ線図。FIG. 2 is a Ph diagram of a composite refrigerant circuit in the first embodiment. 実施の形態１における、複合冷媒回路１００Ａの回路図。FIG. 3 is a circuit diagram of a composite refrigerant circuit 100A in the first embodiment. 実施の形態２の、複合冷媒回路１００Ｂの回路図。The circuit diagram of the composite refrigerant circuit 100B of Embodiment 2. FIG. 実施の形態３の、複合冷媒回路１００Ｃの回路図。The circuit diagram of 100 C of composite refrigerant circuits of Embodiment 3. FIG. 実施の形態４の、複合冷媒回路２００Ｃの回路図。The circuit diagram of the composite refrigerant circuit 200C of Embodiment 4. FIG.

図１は、太陽熱を熱源とするエジェクタ式冷媒回路を示す図である。図１に示すように、エジェクタ６が、通常の冷媒回路における圧縮機を代替する。エジェクタ６内の圧縮作用は、太陽熱集熱機構（太陽光電熱ハイブリッドパネル７）から提供される熱源により行われる。図１の冷媒回路は、エジェクタ６を、蒸発器１から出たガス冷媒の圧縮手段とする。この冷媒回路では、蒸発器１、エジェクタ６、凝縮器２が順次に接続され、凝縮器２で液となって出た冷媒は分岐部４０で分岐する。分岐後の冷媒の一方は、毛細管、電子弁のような膨張機構５に流入する。膨張機構５により低温低圧となった冷媒は、蒸発器１に戻り外部負荷により加熱されて蒸発する。蒸発したガス冷媒は、エジェクタ吸引口６２から吸引されて昇圧された後、エジェクタ出口６３から流出して再び凝縮器２に流入する。凝縮器２を出た液冷媒の他方は分岐部４０で分岐し、加圧機構であるポンプ４を介して発生器３に流入し、太陽熱を吸熱した作動媒体と発生器３において熱交換されることにより過熱ガス状態となってエジェクタ６の駆動流体の流入口６１に流入する。   FIG. 1 is a diagram showing an ejector refrigerant circuit that uses solar heat as a heat source. As shown in FIG. 1, an ejector 6 replaces a compressor in a normal refrigerant circuit. The compression action in the ejector 6 is performed by a heat source provided from a solar heat collecting mechanism (solar electric heat hybrid panel 7). In the refrigerant circuit of FIG. 1, the ejector 6 is used as a compression means for the gas refrigerant that has exited the evaporator 1. In this refrigerant circuit, the evaporator 1, the ejector 6, and the condenser 2 are connected in order, and the refrigerant that has come out as a liquid in the condenser 2 branches at the branching section 40. One of the branched refrigerant flows into the expansion mechanism 5 such as a capillary tube or an electronic valve. The refrigerant that has become low temperature and low pressure by the expansion mechanism 5 returns to the evaporator 1 and is heated by an external load to evaporate. The evaporated gas refrigerant is sucked from the ejector suction port 62 and pressurized, and then flows out from the ejector outlet 63 and flows into the condenser 2 again. The other of the liquid refrigerant exiting the condenser 2 branches at the branching section 40 and flows into the generator 3 through the pump 4 which is a pressurizing mechanism, and heat exchange is performed in the generator 3 with the working medium that has absorbed solar heat. As a result, an overheated gas state is obtained and flows into the driving fluid inlet 61 of the ejector 6.

（エジェクタ６）
図２は、エジェクタ冷媒回路に使用されるエジェクタの原理図である。図２（ａ）はエジェクタ断面を示し、図２（ｂ）は、各位置ｘ１〜ｘ３、ｘ５における各圧力Ｐ１〜Ｐ３、Ｐ５を示す。エジェクタは高圧の駆動流体を加速させることで吸引流体を加速させた後、駆動流体と吸引流体の混合流体を減速させることにより、高圧流体を低圧の吸引流体の圧縮に利用するデバイスである。エジェクタに流入したガス冷媒（駆動流体）は駆動ノズルで膨張加速し、蒸発器からのガス冷媒を吸引する。また、発生器で冷媒をガス化する熱源は、太陽熱パネル、太陽光電熱ハイブリッドパネルなどの集熱機構から供給する。そのため、太陽熱を吸熱した作動媒体が太陽熱パネルもしくは太陽光電熱ハイブリッドパネルと発生器間を循環するループ流路を設ける。 (Ejector 6)
FIG. 2 is a principle diagram of an ejector used in the ejector refrigerant circuit. FIG. 2A shows the ejector cross section, and FIG. 2B shows the pressures P1 to P3 and P5 at the positions x1 to x3 and x5. An ejector is a device that uses a high-pressure fluid to compress a low-pressure suction fluid by accelerating the suction fluid by accelerating a high-pressure drive fluid and then decelerating a mixed fluid of the drive fluid and the suction fluid. The gas refrigerant (driving fluid) flowing into the ejector is expanded and accelerated by the driving nozzle, and sucks the gas refrigerant from the evaporator. Moreover, the heat source which gasifies a refrigerant | coolant with a generator is supplied from heat collection mechanisms, such as a solar thermal panel and a solar electric hybrid panel. Therefore, a loop flow path is provided in which the working medium that has absorbed solar heat circulates between the solar panel or solar electric hybrid panel and the generator.

以下の実施の形態１〜４で説明する複合冷媒回路１００Ａ〜１００Ｃ，２００Ｃは、圧縮機９を圧縮手段とする通常の蒸気圧縮式冷媒回路１１０（第１の冷媒回路）と、エジェクタ６を圧縮手段とするエジェクタ式冷媒回路１２０（第２の冷媒回路）との、循環冷媒の流路が別々となる構成が特徴である。この構成により次の図３の説明で述べる効果がある。   The composite refrigerant circuits 100A to 100C and 200C described in the following first to fourth embodiments compress an ordinary vapor compression refrigerant circuit 110 (first refrigerant circuit) using the compressor 9 as a compression means and the ejector 6. The ejector-type refrigerant circuit 120 (second refrigerant circuit) as a means is characterized by a configuration in which the flow path of the circulating refrigerant is separate. This configuration has the effect described in the following description of FIG.

（冷媒について）
以下では、蒸気圧縮式冷媒回路１１０を循環する冷媒を第１冷媒といい、エジェクタ式冷媒回路１２０を循環する冷媒を第２冷媒といい、さらに、後述の図５などの太陽光電熱ハイブリッドパネル、発生器、ポンプからなる循環流路を流れる冷媒を第３冷媒という。 (About refrigerant)
Hereinafter, the refrigerant that circulates in the vapor compression refrigerant circuit 110 is referred to as a first refrigerant, the refrigerant that circulates in the ejector refrigerant circuit 120 is referred to as a second refrigerant, and further, a solar electric heat hybrid panel such as FIG. The refrigerant flowing through the circulation flow path including the generator and the pump is referred to as a third refrigerant.

図３は、実施の形態１〜４で説明する複合冷媒回路１００Ａ〜１００Ｃ，２００Ｃにおける冷媒回路のＰ−ｈ線図を示す。従来型の冷媒回路では、凝縮器出口の冷媒の過冷却度が殆んど取れていないサイクル（通常サイクル７１）である。これに対し、実施の形態１〜４で説明する複合冷媒回路では、複合サイクル７２として示すように過冷却度を多くとり、凝縮圧力を低く抑えることが特徴である。凝縮圧力を抑えることにより、蒸発器の出入り口エンタルピ差を増加させることができ、定格の能力を得るのに、冷媒循環量を減らすことができるので、最終的に圧縮機の動力を減らすことが可能となる。
実施の形態１〜４で説明する複合冷媒回路では、圧縮機吐出冷媒ガスの熱、太陽光電熱ハイブリッドパネルからの収集熱を駆動熱源とするエジェクタ式冷媒回路を用い、この過冷却度を得ることにより、冷房負荷の集中する日中に、その場で運転の高効率化を図ることができる。 FIG. 3 shows a Ph diagram of the refrigerant circuit in the composite refrigerant circuits 100A to 100C and 200C described in the first to fourth embodiments. The conventional refrigerant circuit is a cycle (normal cycle 71) in which the degree of supercooling of the refrigerant at the condenser outlet is hardly taken. In contrast, the composite refrigerant circuits described in the first to fourth embodiments are characterized in that the degree of supercooling is increased as shown in the composite cycle 72 and the condensation pressure is kept low. By suppressing the condensing pressure, it is possible to increase the enthalpy difference between the entrance and exit of the evaporator, and to obtain the rated capacity, it is possible to reduce the amount of refrigerant circulation, so it is possible to ultimately reduce the compressor power It becomes.
In the composite refrigerant circuit described in the first to fourth embodiments, the degree of supercooling is obtained by using an ejector type refrigerant circuit that uses the heat of the refrigerant gas discharged from the compressor and the heat collected from the solar electric hybrid panel as a driving heat source. Thus, it is possible to increase the efficiency of operation on the spot during the day when the cooling load is concentrated.

（エジェクタ６の駆動熱源のタイプ）
実施の形態１〜４で説明する複合冷媒回路は、以下のタイプのいずれかである。すなわち、エジェクタ式冷媒回路１２０のエジェクタ６は、駆動熱源として、
（Ａ）圧縮機吐出冷媒ガスの熱を利用するＡタイプ、
（Ｂ）太陽光電熱ハイブリッドパネルからの収集熱を利用するＢタイプ、
（Ｃ）両方を使用するＣタイプ、
の３つのタイプのうちのいずれかである。実施の形態１はＡタイプを説明し、実施の形態２はＢタイプを説明し、実施の形態３、４はＣタイプを説明する。 (Type of drive heat source for ejector 6)
The composite refrigerant circuit described in the first to fourth embodiments is one of the following types. That is, the ejector 6 of the ejector type refrigerant circuit 120 serves as a drive heat source.
(A) A type using the heat of the refrigerant gas discharged from the compressor,
(B) B type using the heat collected from the solar electric hybrid panel,
(C) C type using both,
One of the three types. The first embodiment describes the A type, the second embodiment describes the B type, and the third and fourth embodiments describe the C type.

（蒸気圧縮式冷媒回路１１０の構成）
実施の形態１〜４で説明する複合冷媒回路における主たる冷媒回路である通常の蒸気圧縮式冷媒回路１１０（第１の冷媒回路）は、後述する図４〜図７に示すように、構成要素として圧縮機９、凝縮器２ａ（第１の放熱器）、過冷却器１１、膨張機構５ａ（第１の膨張機構）、蒸発器１を備える冷媒回路である。蒸気圧縮式冷媒回路１１０は、圧縮機９、凝縮器２ａ、過冷却器１１、膨張機構５ａ、蒸発器１が、これらの順に閉回路状に第１冷媒の循環流路で接続され、第１冷媒がこれらの順に循環する。 (Configuration of vapor compression refrigerant circuit 110)
A normal vapor compression refrigerant circuit 110 (first refrigerant circuit), which is the main refrigerant circuit in the composite refrigerant circuit described in the first to fourth embodiments, is a component as shown in FIGS. The refrigerant circuit includes a compressor 9, a condenser 2 a (first radiator), a supercooler 11, an expansion mechanism 5 a (first expansion mechanism), and an evaporator 1. In the vapor compression refrigerant circuit 110, the compressor 9, the condenser 2a, the supercooler 11, the expansion mechanism 5a, and the evaporator 1 are connected in this order in a closed circuit shape through the circulation path of the first refrigerant. The refrigerant circulates in this order.

（エジェクタ式冷媒回路１２０の構成）
実施の形態１〜４で説明する複合冷媒回路における補助的な冷媒回路であるエジェクタ式冷媒回路１２０（第２の冷媒回路）は、後述する図４〜図７に示すように、圧縮機を代替するエジェクタ６、凝縮器２ｂ（第２の放熱器）、膨張機構５ｂ（第２の膨張機構）、冷媒ポンプ４、凝縮器２ｂを出た液冷媒からガス冷媒を発生させる発生器３、蒸気圧縮式冷媒回路１１０の過冷却器１１との一体型蒸発器等を備える。エジェクタ式冷媒回路１２０は、エジェクタ６、凝縮器２ｂ、膨張機構５ｂが、これらの順に閉回路状に第２冷媒の循環流路で接続され、第２冷媒がこれらの順に循環する。 (Configuration of ejector refrigerant circuit 120)
An ejector refrigerant circuit 120 (second refrigerant circuit), which is an auxiliary refrigerant circuit in the composite refrigerant circuit described in the first to fourth embodiments, replaces the compressor as shown in FIGS. Ejector 6, condenser 2b (second radiator), expansion mechanism 5b (second expansion mechanism), refrigerant pump 4, generator 3 for generating gas refrigerant from liquid refrigerant that has exited condenser 2b, vapor compression An evaporator integrated with the supercooler 11 of the refrigerant circuit 110 is provided. In the ejector refrigerant circuit 120, the ejector 6, the condenser 2b, and the expansion mechanism 5b are connected in a closed circuit shape in this order in the circulation path of the second refrigerant, and the second refrigerant circulates in that order.

実施の形態１．
図４は、実施の形態１の複合冷媒回路１００Ａ（Ａタイプ）の回路構成を示す図である。図４を参照して実施の形態１の複合冷媒回路１００Ａを説明する。複合冷媒回路１００Ａ（冷凍サイクル装置）は、圧縮機吐出冷媒ガスの熱を、エジェクタ式冷媒回路１２０（エジェクタ６）の駆動熱源とする回路（Ａタイプ）である。 Embodiment 1 FIG.
FIG. 4 is a diagram illustrating a circuit configuration of the composite refrigerant circuit 100A (A type) according to the first embodiment. The composite refrigerant circuit 100A of Embodiment 1 will be described with reference to FIG. The composite refrigerant circuit 100A (refrigeration cycle apparatus) is a circuit (A type) that uses the heat of the refrigerant gas discharged from the compressor as a driving heat source for the ejector refrigerant circuit 120 (ejector 6).

（蒸気圧縮式冷媒回路１１０の構成）
図４に示すように、蒸気圧縮式冷媒回路１１０では、冷媒が、圧縮機９、発生器３、凝縮器２ａ（第１の放熱器）、過冷却器１１、膨張機構５ａ（第１の膨張機構）、蒸発器１の順で流れる。圧縮機９から吐出された冷媒（第１冷媒）は、発生器３に流入して通過した後に、凝縮器２ａに向かう。 (Configuration of vapor compression refrigerant circuit 110)
As shown in FIG. 4, in the vapor compression refrigerant circuit 110, the refrigerant is the compressor 9, the generator 3, the condenser 2a (first radiator), the supercooler 11, and the expansion mechanism 5a (first expansion). Mechanism) and the evaporator 1 in this order. The refrigerant discharged from the compressor 9 (first refrigerant) flows into the generator 3 and passes therethrough, and then travels toward the condenser 2a.

（エジェクタ式冷媒回路１２０の構成）
エジェクタ式冷媒回路１２０では、図４に示すように、凝縮器２ｂと膨張機構５ｂとの間の分岐部４０から分岐してエジェクタ６の駆動流体の流入口６１に接続する分岐流路４１の途中に、発生器３が配置される。 (Configuration of ejector refrigerant circuit 120)
In the ejector-type refrigerant circuit 120, as shown in FIG. 4, a halfway of a branch flow path 41 branched from a branch portion 40 between the condenser 2b and the expansion mechanism 5b and connected to the driving fluid inlet 61 of the ejector 6 is provided. In addition, the generator 3 is arranged.

（液冷媒２１）
エジェクタ式冷媒回路１２０では、凝縮器２ｂで液化して流出した液冷媒（第２冷媒）の一方の液冷媒２１は、分岐部４０から分岐流路４１に分岐して加圧機構である冷媒ポンプＰ（４）を介し発生器３に流入し、圧縮機９を出た作動媒体（第１冷媒）から吸熱（熱交換）し、蒸発する。そして、この蒸発によりガス状に相変化した冷媒は、再びエジェクタ６の駆動流体の流入口６１に流入し、エジェクタ６の駆動流体となる。発生器３では、通常の蒸気圧縮式冷媒回路１１０の第１冷媒は、ガス状で冷却される。 (Liquid refrigerant 21)
In the ejector-type refrigerant circuit 120, one liquid refrigerant 21 of the liquid refrigerant (second refrigerant) liquefied and discharged by the condenser 2b branches from the branch portion 40 to the branch flow path 41, and is a refrigerant pump that is a pressurizing mechanism. It flows into the generator 3 via P (4), absorbs heat (heat exchange) from the working medium (first refrigerant) exiting the compressor 9, and evaporates. Then, the refrigerant that has undergone a gas phase change due to the evaporation again flows into the driving fluid inlet 61 of the ejector 6 and becomes the driving fluid of the ejector 6. In the generator 3, the first refrigerant in the normal vapor compression refrigerant circuit 110 is cooled in a gaseous state.

（液冷媒２２）
他方の液冷媒２２（第２冷媒）は、毛細管、電子弁のような膨張機構５ｂ（第２の膨張機構）に流入する。膨張機構５ｂにより低温低圧となった液冷媒２２は、エジェクタ式冷媒回路１２０の蒸発熱を用いて凝縮器２ａ出口の液冷媒の過冷却度を増加させるために設けられた蒸気圧縮式冷媒回路１１０の過冷却器１１に流入し、熱交換して蒸発した後、エジェクタ６に吸引される。すなわち、他方の液冷媒２２は、膨張機構５ｂから液状態で流出して過冷却器１１に流入し、過冷却器１１を通過する蒸気圧縮式冷媒回路１１０の第１冷媒から吸熱して蒸発し、気体状態でエジェクタ吸引口６２に流入し、エジェクタ出口６３から流出して、凝縮器２ｂ、膨張機構５ｂ、過冷却器１１の順に循環する。 (Liquid refrigerant 22)
The other liquid refrigerant 22 (second refrigerant) flows into an expansion mechanism 5b (second expansion mechanism) such as a capillary tube or an electronic valve. The liquid refrigerant 22 that has become low temperature and low pressure by the expansion mechanism 5b is used to increase the degree of supercooling of the liquid refrigerant at the outlet of the condenser 2a by using the evaporation heat of the ejector type refrigerant circuit 120. The vapor compression refrigerant circuit 110 is provided. Then, it is sucked into the ejector 6 after evaporating through heat exchange. That is, the other liquid refrigerant 22 flows out from the expansion mechanism 5b in a liquid state, flows into the subcooler 11, and absorbs heat from the first refrigerant of the vapor compression refrigerant circuit 110 passing through the subcooler 11 to evaporate. Then, the gas flows into the ejector suction port 62, flows out from the ejector outlet 63, and circulates in the order of the condenser 2b, the expansion mechanism 5b, and the supercooler 11.

以上のように、複合冷媒回路１００Ａは、圧縮機吐出冷媒ガスの熱をエジェクタ６の駆動熱源とするエジェクタ式冷媒回路１２０と、通常の蒸気圧縮式冷媒回路１１０とを組み合わせた。よって、日射量の変動と関係なく、システムが全条件に対して成立する冷凍サイクル装置を提供できる。また、エジェクタ式冷媒回路１２０を循環する第２冷媒と蒸気圧縮式冷媒回路１１０を循環する第１冷媒とを過冷却器１１で熱交換させ、第１冷媒を過冷却するので、図３の説明で述べた効果を得ることができる。   As described above, the composite refrigerant circuit 100A combines the ejector refrigerant circuit 120 that uses the heat of the refrigerant gas discharged from the compressor as a driving heat source for the ejector 6, and the normal vapor compression refrigerant circuit 110. Therefore, it is possible to provide a refrigeration cycle apparatus in which the system is established for all conditions regardless of variations in the amount of solar radiation. Further, since the second refrigerant circulating in the ejector refrigerant circuit 120 and the first refrigerant circulating in the vapor compression refrigerant circuit 110 are heat-exchanged by the supercooler 11, the first refrigerant is supercooled, so that FIG. The effect described in can be obtained.

実施の形態２．
次に実施の形態２の複合冷媒回路１００Ｂを説明する。図５は、複合冷媒回路１００Ｂの回路構成を示す図である。複合冷媒回路１００Ｂは、補助冷媒回路であるエジェクタ式冷媒回路１２０（エジェクタ６）の駆動熱源として、太陽光電熱ハイブリッドパネル７からの収集熱を使用するタイプ（Ｂタイプ）である。 Embodiment 2. FIG.
Next, the composite refrigerant circuit 100B of Embodiment 2 will be described. FIG. 5 is a diagram illustrating a circuit configuration of the composite refrigerant circuit 100B. The composite refrigerant circuit 100B is a type (B type) that uses the collected heat from the solar electric hybrid panel 7 as a driving heat source for an ejector refrigerant circuit 120 (ejector 6) that is an auxiliary refrigerant circuit.

（蒸気圧縮式冷媒回路１１０）
図５に示すように、通常の蒸気圧縮式冷媒回路１１０では、第１冷媒が、圧縮機９、凝縮器２ａ、過冷却器１１、膨張機構５ａ、蒸発器１の順で流れる。 (Vapor compression refrigerant circuit 110)
As shown in FIG. 5, in the normal vapor compression refrigerant circuit 110, the first refrigerant flows in the order of the compressor 9, the condenser 2 a, the subcooler 11, the expansion mechanism 5 a, and the evaporator 1.

（第３の冷媒回路）
複合冷媒回路１００Ｂでは、第３の冷媒回路として、太陽光電熱ハイブリッドパネル７と発生器３とが第３冷媒の循環流路で接続され、太陽光電熱ハイブリッドパネル７によって加熱された第３冷媒が発生器３を通過する。 (Third refrigerant circuit)
In the composite refrigerant circuit 100B, as the third refrigerant circuit, the solar electric hybrid panel 7 and the generator 3 are connected by a circulation path of the third refrigerant, and the third refrigerant heated by the solar electric hybrid panel 7 is the third refrigerant circuit. Pass through generator 3.

（エジェクタ式冷媒回路１２０）
エジェクタ式冷媒回路１２０では、発生器３が、凝縮器２ｂと膨張機構５ｂとの間の分岐部４０から分岐してエジェクタ６の駆動流体の流入口６１に接続する分岐流路４１の途中に配置されている。 (Ejector type refrigerant circuit 120)
In the ejector-type refrigerant circuit 120, the generator 3 is disposed in the middle of the branch flow path 41 that branches from the branch portion 40 between the condenser 2b and the expansion mechanism 5b and connects to the driving fluid inlet 61 of the ejector 6. Has been.

（液冷媒３１）
凝縮器２ｂで液化して流出した液冷媒（第２冷媒）の一方の液冷媒３１は、分岐部４０から分岐流路４１に分岐して加圧機構である冷媒ポンプＰ（４）を介し発生器３に流入し、太陽光電熱ハイブリッドパネル７から集熱した作動媒体（第３冷媒）と熱交換（吸熱）し、蒸発する。蒸発によりガス状に相変化した第２冷媒は、再びエジェクタ６の駆動流体の流入口６１に流入する。 (Liquid refrigerant 31)
One liquid refrigerant 31 of the liquid refrigerant (second refrigerant) liquefied and discharged by the condenser 2b is branched from the branch portion 40 to the branch flow path 41 and is generated via the refrigerant pump P (4) which is a pressurizing mechanism. The refrigerant flows into the vessel 3 and exchanges heat (absorbs heat) with the working medium (third refrigerant) collected from the solar electric hybrid panel 7 and evaporates. The second refrigerant whose phase has changed in a gaseous state due to evaporation again flows into the driving fluid inlet 61 of the ejector 6.

（液冷媒３２）
凝縮器２ｂで液化して流出した液冷媒のうち、分岐部４０で分岐した他方の液冷媒３２は、毛細管、電子弁のような膨張機構５ｂに流入する。膨張機構５ｂにより低温低圧となった液冷媒３２は、エジェクタ式冷媒回路１２０の蒸発熱を用いて凝縮器２ａ出口の液冷媒の過冷却度を増加させるために設けられた蒸気圧縮式冷媒回路１１０の過冷却器１１に流入し、熱交換して蒸発した後、エジェクタ６に吸引される。すなわち、実施の形態１と同様に、他方の液冷媒３２は、膨張機構５ｂから液状態で流出して過冷却器１１に流入し、過冷却器１１を通過する蒸気圧縮式冷媒回路１１０の第１冷媒から吸熱して蒸発し、気体状態でエジェクタ吸引口６２に流入し、エジェクタ出口６３から流出して、凝縮器２ｂ、膨張機構５ｂ、過冷却器１１の順に循環する。 (Liquid refrigerant 32)
Of the liquid refrigerant liquefied and discharged by the condenser 2b, the other liquid refrigerant 32 branched by the branching section 40 flows into the expansion mechanism 5b such as a capillary tube or an electronic valve. The liquid refrigerant 32 that has become low temperature and low pressure by the expansion mechanism 5b is used to increase the degree of supercooling of the liquid refrigerant at the outlet of the condenser 2a by using the evaporation heat of the ejector type refrigerant circuit 120. The vapor compression refrigerant circuit 110 is provided. Then, it is sucked into the ejector 6 after evaporating through heat exchange. That is, as in the first embodiment, the other liquid refrigerant 32 flows out of the expansion mechanism 5b in a liquid state, flows into the subcooler 11, and passes through the subcooler 11, and the second refrigerant refrigerant 110 of the vapor compression refrigerant circuit 110 passes through the subcooler 11. One refrigerant absorbs heat and evaporates, flows into the ejector suction port 62 in a gaseous state, flows out from the ejector outlet 63, and circulates in the order of the condenser 2b, the expansion mechanism 5b, and the subcooler 11.

以上のように、複合冷媒回路１００Ｂは、太陽光電熱ハイブリッドパネル７からの収集熱をエジェクタ６の駆動熱源とするエジェクタ式冷媒回路１２０と、通常の蒸気圧縮式冷媒回路１１０とを組み合わせた。よって、日射量の変動と関係なく、システムが全条件に対して成立する冷凍サイクル装置を提供できる。また、エジェクタ式冷媒回路１２０を循環する第２冷媒と蒸気圧縮式冷媒回路１１０を循環する第１冷媒とを過冷却器１１で熱交換させ、第１冷媒を過冷却するので、図３の説明で述べた効果を得ることができる。   As described above, the composite refrigerant circuit 100B combines the ejector refrigerant circuit 120 that uses the collected heat from the solar electric hybrid panel 7 as a driving heat source of the ejector 6, and the normal vapor compression refrigerant circuit 110. Therefore, it is possible to provide a refrigeration cycle apparatus in which the system is established for all conditions regardless of variations in the amount of solar radiation. Further, since the second refrigerant circulating in the ejector refrigerant circuit 120 and the first refrigerant circulating in the vapor compression refrigerant circuit 110 are heat-exchanged by the supercooler 11, the first refrigerant is supercooled, so that FIG. The effect described in can be obtained.

実施の形態３．
次に実施の形態３の複合冷媒回路１００Ｃを説明する。複合冷媒回路１００Ｃは、補助冷媒回路であるエジェクタ式冷媒回路１２０（エジェクタ６）の駆動熱源として、圧縮機吐出冷媒ガス（圧縮機９により圧縮されたガス状の第１冷媒）の熱と、太陽光電熱ハイブリッドパネル７からの収集熱との両方を使用するタイプ（Ｃタイプ）である。 Embodiment 3 FIG.
Next, the composite refrigerant circuit 100C of Embodiment 3 will be described. The composite refrigerant circuit 100C serves as a drive heat source for an ejector refrigerant circuit 120 (ejector 6), which is an auxiliary refrigerant circuit, and the heat of compressor discharge refrigerant gas (a gaseous first refrigerant compressed by the compressor 9) This is a type (C type) that uses both the heat collected from the photoelectric thermal hybrid panel 7.

（複合冷媒回路１００Ｃの構成）
図６は、複合冷媒回路１００Ｃの回路構成示す。複合冷媒回路１００Ｃは、実施の形態１の複合冷媒回路１００Ａに、実施の形態２で説明した「第３の冷媒回路」（太陽光電熱ハイブリッドパネル、第２発生器、ポンプからなる冷媒循環回路）を加えた構成である。 (Configuration of composite refrigerant circuit 100C)
FIG. 6 shows a circuit configuration of the composite refrigerant circuit 100C. The composite refrigerant circuit 100C is the same as the composite refrigerant circuit 100A of the first embodiment, but the “third refrigerant circuit” described in the second embodiment (a refrigerant circulation circuit including a solar electric hybrid panel, a second generator, and a pump). It is the structure which added.

図６に示すように、通常の蒸気圧縮式冷媒回路１１０では、複合冷媒回路１００Ａと同様に、第１冷媒が、圧縮機９、第１発生器３ａ、凝縮器２ａ、過冷却器１１、膨張機構５ａ、蒸発器１の順で循環する。   As shown in FIG. 6, in the normal vapor compression refrigerant circuit 110, the first refrigerant is the compressor 9, the first generator 3a, the condenser 2a, the subcooler 11, the expansion, as in the composite refrigerant circuit 100A. It circulates in order of the mechanism 5a and the evaporator 1.

（液冷媒２１）
一方、エジェクタ式冷媒回路１２０では、複合冷媒回路１００Ａと同様に、凝縮器２ｂで液化して出た液冷媒の一方の液冷媒２１は、分岐部４０で分岐して加圧機構である冷媒ポンプＰ（４）を介し第１発生器３ａに流入する。そして、液冷媒２１は、第１発生器３ａにおいて圧縮機９を出た作動媒体と熱交換し温度が上昇（この時点では液体である）する。熱交換により昇温して第１発生器３ａを出た液冷媒２１は、第２発生機器３ｂに流入し、太陽光電熱ハイブリッドパネル７から集熱した作動媒体（第３冷媒）と熱交換して加熱され、蒸発する。蒸発によりガス状に相変化した第２冷媒は、再びエジェクタ６の駆動流体の流入口６１に流入する。 (Liquid refrigerant 21)
On the other hand, in the ejector-type refrigerant circuit 120, like the composite refrigerant circuit 100A, one liquid refrigerant 21 of the liquid refrigerant liquefied by the condenser 2b is branched by the branching section 40 and is a refrigerant pump that is a pressurizing mechanism. It flows into the 1st generator 3a via P (4). And the liquid refrigerant 21 heat-exchanges with the working medium which left the compressor 9 in the 1st generator 3a, and temperature rises (it is a liquid at this time). The liquid refrigerant 21 that has been heated by heat exchange and has exited the first generator 3a flows into the second generator 3b and exchanges heat with the working medium (third refrigerant) collected from the solar electric hybrid panel 7. Heated and evaporated. The second refrigerant whose phase has changed in a gaseous state due to evaporation again flows into the driving fluid inlet 61 of the ejector 6.

（液冷媒２２）
分岐部４０で分岐した他方の液冷媒２２は、毛細管、電子弁のような膨張機構５ｂに流入する。膨張機構５ｂにより低温低圧となった液冷媒２２は、エジェクタ式冷媒回路の蒸発熱を用いて凝縮器出口の液冷媒の過冷却度を増加させるために設けられた蒸気圧縮式冷媒回路１１０の過冷却器１１に流入し、熱交換して蒸発した後、エジェクタ６のエジェクタ吸引口６２から吸引される。 (Liquid refrigerant 22)
The other liquid refrigerant 22 branched by the branch part 40 flows into the expansion mechanism 5b such as a capillary tube or an electronic valve. The liquid refrigerant 22 that has become low temperature and low pressure by the expansion mechanism 5b uses the heat of evaporation of the ejector type refrigerant circuit to increase the degree of supercooling of the liquid refrigerant at the outlet of the condenser. After flowing into the cooler 11 and evaporating through heat exchange, the air is sucked from the ejector suction port 62 of the ejector 6.

以上のように、複合冷媒回路１００Ｃは、圧縮機吐出冷媒ガスの熱及び太陽光電熱ハイブリッドパネルからの収集熱との両方の熱をエジェクタ６の駆動熱源とするエジェクタ式冷媒回路１２０と、通常の蒸気圧縮式冷媒回路１１０とを組み合わせた。よって、日射量の変動と関係なく、システムが全条件に対して成立する冷凍サイクル装置を提供できる。また、エジェクタ式冷媒回路１２０を循環する第２冷媒と蒸気圧縮式冷媒回路１１０を循環する第１冷媒とを過冷却器１１で熱交換させ、第１冷媒を過冷却するので、図３の説明で述べた効果を得ることができる。   As described above, the composite refrigerant circuit 100C includes an ejector-type refrigerant circuit 120 that uses both the heat of the refrigerant gas discharged from the compressor and the heat collected from the solar electric hybrid panel as a driving heat source for the ejector 6, A vapor compression refrigerant circuit 110 was combined. Therefore, it is possible to provide a refrigeration cycle apparatus in which the system is established for all conditions regardless of variations in the amount of solar radiation. Further, since the second refrigerant circulating in the ejector refrigerant circuit 120 and the first refrigerant circulating in the vapor compression refrigerant circuit 110 are heat-exchanged by the supercooler 11, the first refrigerant is supercooled, so that FIG. The effect described in can be obtained.

実施の形態４．
次に実施の形態４の複合冷媒回路２００Ｃを説明する。
図７は、複合冷媒回路２００Ｃの回路構成を示す図である。図７に示すように、複合冷媒回路２００Ｃは、実施の形態３の複合冷媒回路１００Ｃのエジェクタ６と過冷却器１１との間に、内部熱交換器１０を加えた構成である。 Embodiment 4 FIG.
Next, the composite refrigerant circuit 200C of Embodiment 4 will be described.
FIG. 7 is a diagram illustrating a circuit configuration of the composite refrigerant circuit 200C. As shown in FIG. 7, the composite refrigerant circuit 200 </ b> C has a configuration in which an internal heat exchanger 10 is added between the ejector 6 and the subcooler 11 of the composite refrigerant circuit 100 </ b> C of the third embodiment.

（蒸気圧縮式冷媒回路１１０）
通常の蒸気圧縮式冷媒回路１１０では、複合冷媒回路１００Ｃと同様に、第１冷媒が、圧縮機９、第１発生器３ａ、凝縮器２ａ、過冷却器１１、膨張機構５ａ、蒸発器１の順で流れる。 (Vapor compression refrigerant circuit 110)
In the normal vapor compression refrigerant circuit 110, the first refrigerant is the compressor 9, the first generator 3a, the condenser 2a, the subcooler 11, the expansion mechanism 5a, and the evaporator 1 as in the composite refrigerant circuit 100C. It flows in order.

（エジェクタ式冷媒回路１２０）
エジェクタ式冷媒回路１２０では、過冷却器１１とエジェクタ６との流路の間に内部熱交換器１０が配置されている。 (Ejector type refrigerant circuit 120)
In the ejector refrigerant circuit 120, the internal heat exchanger 10 is disposed between the flow path between the supercooler 11 and the ejector 6.

（液冷媒２１）
エジェクタ式冷媒回路１２０では、凝縮器２ｂで液化して流出した液冷媒の一方の液冷媒２１は、分岐部４０から分岐流路４１に分岐して加圧機構である冷媒ポンプＰ（４）を介し第１発生器３ａに流入し、圧縮機９を出た作動媒体（第１冷媒）と熱交換（この時点で液体である）し温度が上昇する。この熱交換により昇温して第１発生器３ａを出た液冷媒は、第２発生機器３ｂに流入し太陽光電熱ハイブリッドパネル７から集熱した作動媒体（第３冷媒）と熱交換（吸熱）し、蒸発する。蒸発によりガス状に相変化した冷媒は再びエジェクタ６の駆動流体の流入口６１（駆動ノズル）に流入する。 (Liquid refrigerant 21)
In the ejector-type refrigerant circuit 120, one liquid refrigerant 21 of the liquid refrigerant liquefied and discharged by the condenser 2b is branched from the branch portion 40 to the branch flow path 41, and the refrigerant pump P (4) which is a pressurizing mechanism is provided. Then, it flows into the first generator 3a, exchanges heat with the working medium (first refrigerant) exiting the compressor 9 (is liquid at this point), and the temperature rises. The liquid refrigerant heated up by this heat exchange and exiting the first generator 3a flows into the second generator 3b and exchanges heat with the working medium (third refrigerant) collected from the solar electric hybrid panel 7. ) And evaporate. The refrigerant whose phase has changed in a gaseous state due to evaporation again flows into the driving fluid inlet 61 (driving nozzle) of the ejector 6.

（液冷媒２２）
凝縮器２ｂで液化して流出し、分岐部４０で分岐した他方の液冷媒２２は、過冷却器１１とエジェクタ６の吸入配管との間に設けられた内部熱交換器１０において、過冷却器１１を出てエジェクタ吸引口６２から吸引されるガス冷媒と熱交換した後、膨張機構５ｂに流入する。この場合、分岐部４０で分岐した液冷媒２２は、内部熱交換器１０において、過冷却器１１から流出してエジェクタ６に向かうガス冷媒に熱を与え、その後、膨張機構５ｂに流入する。このように、内部熱交換器１０は凝縮器２ｂを出た液冷媒２２と、エジェクタ吸引口６２から吸引されるガス冷媒とを熱交換させることにより、サイクルの性能を向上させる。そして、膨張機構５ｂにより低温低圧となった液冷媒２２は、エジェクタ式冷媒回路１２０の蒸発熱を用いて凝縮器出口の液冷媒の過冷却度を増加させるために設けられた蒸気圧縮式冷媒回路１１０の過冷却器１１に流入し、熱交換して蒸発した後、上述の内部熱交換器１０を通過してエジェクタ吸引口６２から吸引される。 (Liquid refrigerant 22)
The other liquid refrigerant 22 liquefied and flowed out by the condenser 2 b and branched by the branching section 40 is supplied to the supercooler in the internal heat exchanger 10 provided between the supercooler 11 and the suction pipe of the ejector 6. After exiting 11 and exchanging heat with the gas refrigerant sucked from the ejector suction port 62, it flows into the expansion mechanism 5b. In this case, in the internal heat exchanger 10, the liquid refrigerant 22 branched at the branching section 40 flows out from the supercooler 11 and gives heat to the gas refrigerant directed toward the ejector 6, and then flows into the expansion mechanism 5b. Thus, the internal heat exchanger 10 improves the cycle performance by exchanging heat between the liquid refrigerant 22 exiting the condenser 2b and the gas refrigerant sucked from the ejector suction port 62. Then, the liquid refrigerant 22 that has become low temperature and low pressure by the expansion mechanism 5b is used to increase the degree of supercooling of the liquid refrigerant at the outlet of the condenser by using the evaporation heat of the ejector type refrigerant circuit 120. After flowing into the subcooler 11 of 110 and evaporating through heat exchange, it passes through the internal heat exchanger 10 and is sucked from the ejector suction port 62.

以上のように、複合冷媒回路２００Ｃは、圧縮機吐出冷媒ガスの熱及び太陽光電熱ハイブリッドパネルからの収集熱との両方の熱をエジェクタ６の駆動熱源とするエジェクタ式冷媒回路１２０と、通常の蒸気圧縮式冷媒回路１１０とを組み合わせた。よって、日射量の変動と関係なく、システムが全条件に対して成立する冷凍サイクル装置を提供できる。また、エジェクタ式冷媒回路１２０を循環する第２冷媒と蒸気圧縮式冷媒回路１１０を循環する第１冷媒とを過冷却器１１で熱交換させ、第１冷媒を過冷却するので、図３の説明で述べた効果を得ることができる。   As described above, the composite refrigerant circuit 200C includes the ejector-type refrigerant circuit 120 that uses both the heat of the refrigerant gas discharged from the compressor and the collected heat from the solar electric hybrid panel as the driving heat source of the ejector 6, A vapor compression refrigerant circuit 110 was combined. Therefore, it is possible to provide a refrigeration cycle apparatus in which the system is established for all conditions regardless of variations in the amount of solar radiation. Further, since the second refrigerant circulating in the ejector refrigerant circuit 120 and the first refrigerant circulating in the vapor compression refrigerant circuit 110 are heat-exchanged by the supercooler 11, the first refrigerant is supercooled, so that FIG. The effect described in can be obtained.

１ 蒸発器、２ａ，２ｂ 凝縮器、３，３ａ 発生器、４ 冷媒ポンプ、５ａ，５ｂ 膨張機構、６ エジェクタ、６１ 駆動流体の流入口、６２ エジェクタ吸引口、６３ エジェクタ出口、７ 太陽光電熱ハイブリッドパネル、８ 水ポンプ、９ 圧縮機、１０ 内部熱交換器、１１ 過冷却器、２１，２２ 冷媒、３１，３２ 冷媒、４０ 分岐部、４１ 分岐流路、１００Ａ，１００Ｂ，１００Ｃ，２００Ｃ 複合冷媒回路、１１０ 蒸気圧縮式冷媒回路、１２０ エジェクタ式冷媒回路。   DESCRIPTION OF SYMBOLS 1 Evaporator, 2a, 2b Condenser, 3, 3a generator, 4 Refrigerant pump, 5a, 5b Expansion mechanism, 6 Ejector, 61 Inlet of driving fluid, 62 Ejector suction port, 63 Ejector outlet, 7 Solar electric hybrid Panel, 8 Water pump, 9 Compressor, 10 Internal heat exchanger, 11 Subcooler, 21, 22 Refrigerant, 31, 32 Refrigerant, 40 Branch part, 41 Branch flow path, 100A, 100B, 100C, 200C Composite refrigerant circuit 110 Vapor compression refrigerant circuit, 120 Ejector refrigerant circuit.

Claims (6)

圧縮機、第１の放熱器、過冷却器、第１の膨張機構、蒸発器が、これらの順に閉回路状に第１冷媒の循環流路で接続され、第１冷媒がこれらの順に循環する第１の冷媒回路と、
圧縮機を代替するエジェクタ、第２の放熱器、第２の膨張機構が、これらの順に閉回路状に第２冷媒の循環流路で接続され、第２冷媒がこれらの順に循環する第２の冷媒回路と
を備え、
前記第２の冷媒回路を循環する前記第２冷媒は、
前記第２の膨張機構から液状態で流出して前記第１の冷媒回路の前記過冷却器に流入し、前記過冷却器を通過する前記第１の冷媒回路の前記第１冷媒から吸熱して蒸発し、気体状態で前記エジェクタの吸引口に流入し、前記エジェクタの出口から流出して、前記第２の放熱器、前記第２の膨張機構、前記過冷却器の順に循環することを特徴とする冷凍サイクル装置。 The compressor, the first radiator, the supercooler, the first expansion mechanism, and the evaporator are connected in the order of these in a closed circuit shape with the circulation path of the first refrigerant, and the first refrigerant circulates in this order. A first refrigerant circuit;
An ejector that substitutes for the compressor, a second radiator, and a second expansion mechanism are connected in a closed circuit form in this order by a circulation path of the second refrigerant, and the second refrigerant circulates in this order. A refrigerant circuit,
The second refrigerant circulating in the second refrigerant circuit is
The liquid flows out from the second expansion mechanism, flows into the subcooler of the first refrigerant circuit, and absorbs heat from the first refrigerant of the first refrigerant circuit passing through the subcooler. It evaporates, flows into the suction port of the ejector in a gaseous state, flows out of the outlet of the ejector, and circulates in the order of the second radiator, the second expansion mechanism, and the subcooler. Refrigeration cycle equipment. 前記第２の冷媒回路の前記エジェクタは、
前記第１の冷媒回路の前記圧縮機により吐出された気体状態の第１冷媒の保有する熱と、前記第１の冷媒回路及び前記第２の冷媒回路とは異なる第３の冷媒回路を循環する第３冷媒の保有する熱との、少なくともいずれかを駆動熱源とすることを特徴とする請求項１記載の冷凍サイクル装置。 The ejector of the second refrigerant circuit is
The heat of the first refrigerant in the gaseous state discharged by the compressor of the first refrigerant circuit circulates through a third refrigerant circuit different from the first refrigerant circuit and the second refrigerant circuit. The refrigeration cycle apparatus according to claim 1, wherein at least one of heat held by the third refrigerant is used as a driving heat source. 前記第２の冷媒回路は、さらに、
前記第２の放熱器と前記第２の膨張機構との間の分岐部から分岐して前記エジェクタの駆動流体の流入口に接続する分岐流路の途中に、発生器が配置され、
前記圧縮機から吐出された第１冷媒は、
前記発生器に流入して通過した後に前記第１の放熱器に向かい、
前記第２の冷媒回路を循環する第２冷媒は、
前記第２の放熱器から流出し、一部が前記分岐流路に分岐して前記発生器に流入し、前記発生器を通過する第１冷媒から吸熱し、前記分岐経路を介して前記エジェクタの駆動流体の流入口に流入し、前記エジェクタの駆動流体となることを特徴とする請求項２記載の冷凍サイクル装置。 The second refrigerant circuit further includes:
A generator is arranged in the middle of a branch flow path that branches from a branch portion between the second radiator and the second expansion mechanism and connects to an inlet of the drive fluid of the ejector,
The first refrigerant discharged from the compressor is
To the first radiator after flowing into and passing through the generator,
The second refrigerant circulating in the second refrigerant circuit is
Outflow from the second radiator, a part branches into the branch flow path, flows into the generator, absorbs heat from the first refrigerant passing through the generator, and passes through the branch path to the ejector. 3. The refrigeration cycle apparatus according to claim 2, wherein the refrigeration cycle apparatus flows into an inlet of a driving fluid and becomes a driving fluid of the ejector. 前記第３の冷媒回路は、
太陽光電熱ハイブリッドパネルと第２発生器とが第３冷媒の循環流路で接続され、前記太陽光電熱ハイブリッドパネルによって加熱された第３冷媒が前記第２発生器を通過する冷媒循環回路であり、
前記第２発生器は、
前記分岐経路において前記エジェクタと前記第１発生器との間に配置され、
前記第１発生器を流出した第２冷媒は、
前記第２発生器で前記第３冷媒から吸熱し、吸熱後に前記エジェクタの駆動流体の流入口に流入することを特徴とする請求項３記載の冷凍サイクル装置。 The third refrigerant circuit includes:
A solar electric hybrid panel and a second generator are connected by a circulation path of a third refrigerant, and the third refrigerant heated by the solar electric hybrid panel passes through the second generator. ,
The second generator includes:
Arranged in the branch path between the ejector and the first generator;
The second refrigerant flowing out of the first generator is
4. The refrigeration cycle apparatus according to claim 3, wherein the second generator absorbs heat from the third refrigerant and flows into the inlet of the drive fluid of the ejector after the heat absorption. 前記第２の冷媒回路は、
前記過冷却器と前記エジェクタとの流路の間に熱交換器が配置され、
前記分岐部から前記第２の膨張機構に向かう第２冷媒は、
前記第２の膨張機構に流入する前に前記熱交換器に流入し、前記熱交換器において前記過冷却器から流出して前記エジェクタに向かう第２冷媒に熱を与えた後、前記第２の膨張機構に流入することを特徴とする請求項３または４のいずれかに記載の冷凍サイクル装置。 The second refrigerant circuit is
A heat exchanger is disposed between the flow path between the subcooler and the ejector,
The second refrigerant heading from the branch portion to the second expansion mechanism is
Before flowing into the second expansion mechanism, it flows into the heat exchanger. In the heat exchanger, the second refrigerant flows out of the supercooler and heats the second refrigerant toward the ejector. The refrigeration cycle apparatus according to any one of claims 3 and 4, wherein the refrigeration cycle apparatus flows into an expansion mechanism. 前記第３の冷媒回路は、
太陽光電熱ハイブリッドパネルと発生器とが第３冷媒の循環流路で接続され、前記太陽光電熱ハイブリッドパネルによって加熱された第３冷媒が前記発生器を通過する冷媒循環回路であり、
前記発生器は、
前記第２の放熱器と前記第２の膨張機構との間の分岐部から分岐して前記エジェクタの駆動流体の流入口に接続する分岐流路の途中に配置され、
前記分岐経路から分岐した第２冷媒は、
前記発生器で前記第３冷媒から吸熱し、吸熱後に前記エジェクタの駆動流体の流入口に流入することを特徴とする請求項２記載の冷凍サイクル装置。 The third refrigerant circuit includes:
The solar electric hybrid panel and the generator are connected by a circulation path of a third refrigerant, and the third refrigerant heated by the solar electric hybrid panel is a refrigerant circulation circuit that passes through the generator.
The generator is
It is arranged in the middle of a branch flow path that branches from a branch portion between the second radiator and the second expansion mechanism and connects to an inflow port of the drive fluid of the ejector,
The second refrigerant branched from the branch path is
3. The refrigeration cycle apparatus according to claim 2, wherein the generator absorbs heat from the third refrigerant and, after absorbing heat, flows into an inlet of a drive fluid of the ejector.
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CN109869940A (en) * 2019-03-26 2019-06-11 天津商业大学 Injecting type critical-cross carbon dioxide double-stage compressive refrigerating system
CN109869940B (en) * 2019-03-26 2024-07-23 天津商业大学 Injection type transcritical carbon dioxide double-stage compression refrigeration system
CN113819678A (en) * 2021-10-22 2021-12-21 安徽普泛能源技术有限公司 Multi-heat-source generator unit with ejector and absorption type refrigerating system thereof

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