JP2016017718A - Refrigeration device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigeration device that suppresses evaporation of a refrigerant flowing into a heat absorber.SOLUTION: The refrigeration device where a refrigeration cycle 1 includes a compressor 2, a radiator 3 and the heat absorber 4 through which the refrigerant circulates includes: a first flow passage through which the refrigerant flows after passing through the radiator 3; a second flow passage branching from the first flow passage, through which the refrigerant flows; and a heat exchanger 6 exchanging heat between the refrigerant flowing through the first flow passage and the refrigerant flowing through the second flow passage. The refrigeration device causes the refrigerant that has flowed through the first flow passage and passing through the heat exchanger 6 to flow into the heat absorber 4.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a refrigeration apparatus.

  Patent Document 1 discloses a refrigeration apparatus in which a first expansion valve and a second expansion valve are provided between a radiator and a heat absorber, and a gas-liquid separator is further provided between the first expansion valve and the second expansion valve. It is disclosed.

JP 2001-56157 A

  However, in the above technique, when the refrigerant passes through a plurality of expansion valves and the refrigerant is decompressed, a part of the liquid phase refrigerant is vaporized in the pipe, and the gas phase refrigerant flows into the heat absorber. There is a possibility that the endothermic performance of the heat absorber may be reduced. In particular, in the above-described technology, a gas-liquid separator having a certain volume is provided, and when the refrigerant flows into the gas-liquid separator, the pressure of the refrigerant is further reduced, and the refrigerant is easily vaporized. Is likely to occur.

  The present invention has been invented to solve such problems, and it is an object of the present invention to prevent the refrigerant from evaporating before flowing into the heat absorber and to improve the heat absorption performance of the heat absorber.

  A refrigeration apparatus according to an aspect of the present invention is a refrigeration apparatus in which a refrigerant circulates in a refrigeration cycle having a compressor, a radiator, and a heat absorber, and the first flow path through which the refrigerant that has passed through the radiator flows. And a second flow path that branches from the first flow path and through which the refrigerant flows, a refrigerant that flows through the first flow path, and a heat exchanger that performs heat exchange between the refrigerant that flows through the second flow path, The refrigerant that has flowed through one flow path and passed through the heat exchanger is caused to flow into the heat absorber.

  According to this aspect, the refrigerant flowing into the heat absorber is cooled by the heat exchanger, whereby the refrigerant can be prevented from being vaporized, and the heat absorption performance of the heat absorber can be improved.

It is a schematic block diagram of the refrigerating cycle of 1st Embodiment. It is a figure which shows the relationship between the specific enthalpy of a refrigerating cycle, and the pressure of a refrigerant | coolant. It is a schematic block diagram of the refrigerating cycle of 2nd Embodiment.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  A refrigeration cycle 1 of a refrigeration apparatus according to a first embodiment of the present invention will be described with reference to FIG. FIG. 1 is a schematic configuration diagram of a refrigeration cycle 1.

  The refrigeration cycle 1 includes a compressor 2, a radiator 3, a heat absorber 4, a gas-liquid separator 5, a supercooler 6, a first expansion valve 7, a second expansion valve 8, and a third expansion. And a valve 9. In the refrigeration cycle 1, the outlet of the heat absorber 4 and the inlet of the radiator 3 are connected by a first refrigerant channel 20, and the compressor 2 is disposed in the first refrigerant channel 20. In the refrigeration cycle 1, the outlet of the radiator 3 and the inlet of the heat absorber 4 are connected by the second refrigerant channel 21, and the first expansion valve 7, the gas-liquid separator 5, The supercooler 6 and the third expansion valve 9 are arranged in order from the radiator 3 side. Further, in the refrigeration cycle 1, the third refrigerant flow path 22 is branched from the second refrigerant flow path 21 between the radiator 3 and the first expansion valve 7, and the second expansion is performed in the third refrigerant flow path 22. The valve 8 and the supercooler 6 are arranged in order from the radiator 3 side.

  The compressor 2 is configured by arranging a first compressor 2 a and a second compressor 2 b in series on the first refrigerant flow path 20. The first compressor 2a compresses the refrigerant, and the second compressor 2b further compresses the refrigerant compressed by the first compressor 2a.

  The radiator 3 cools the refrigerant whose temperature has been increased by being compressed by the first compressor 2a and the second compressor 2b by, for example, heat exchange with air, and liquefies the refrigerant.

  The first expansion valve 7 is liquefied by the radiator 3 and depressurizes the refrigerant flowing through the second refrigerant flow path 21. The second expansion valve 8 is liquefied by the radiator 3 and depressurizes the refrigerant flowing through the third refrigerant flow path 22.

  In the supercooler 6, the first expansion valve 7 and the second expansion valve 8 are configured so that the refrigerant flowing in the second refrigerant channel 21 can be supercooled by the refrigerant flowing in the third refrigerant channel 22. The refrigerant flowing through the refrigerant flow path 21 and the refrigerant flowing through the third refrigerant flow path 22 are decompressed. That is, in the subcooler 6, each decompression ratio is set so that the temperature of the refrigerant in the third refrigerant flow path 22 is lower than the temperature of the refrigerant in the second refrigerant flow path 21, and the second expansion valve The pressure reduction ratio of 8 is larger than the pressure reduction ratio of the first expansion valve 7.

  The gas-liquid separator 5 separates the refrigerant decompressed by the first expansion valve 7 into a liquid phase and a gas phase. In addition to the second refrigerant flow path 21, a fourth refrigerant flow path 23 is connected to the gas-liquid separator 5, and the separated refrigerant in the vapor phase state passes through the fourth refrigerant flow path 23. 2 flows into the compressor 2b.

  In the subcooler 6, the second refrigerant flow path 21 and the third refrigerant flow path 22 are arranged so as to be close to each other, separated by the gas-liquid separator 5, and in a liquid phase state flowing through the second refrigerant flow path 21. The refrigerant is supercooled by the refrigerant flowing through the third refrigerant flow path 22.

  The third refrigerant flow path 22 merges with the fourth refrigerant flow path 23 on the downstream side of the subcooler 6, and the refrigerant that has flowed through the third refrigerant flow path 22 is compressed by the second refrigerant flow path 23 through the second refrigerant flow path 23. Flows into the machine 2b.

  The third expansion valve 9 decompresses the refrigerant flowing through the second refrigerant flow path 21 so that the refrigerant supercooled by the supercooler 6 is vaporized in the heat absorber 4.

  The heat absorber 4 vaporizes the refrigerant decompressed by the third expansion valve 9 by, for example, heat exchange with air. When the refrigerant evaporates in the heat absorber 4, the air around the heat absorber 4 is cooled.

  Next, the effect | action of the refrigerating cycle 1 of this embodiment is demonstrated using FIG. FIG. 2 is a graph showing the relationship between the specific enthalpy of the refrigeration cycle 1 and the refrigerant pressure.

  By compressing the refrigerant by the first compressor 2a and the second compressor 2b, the pressure of the refrigerant increases (points a and b in FIG. 2). The refrigerant having increased pressure is cooled and liquefied by heat exchange by the radiator 3 (point c in FIG. 2). The liquefied refrigerant flows through the second refrigerant channel 21 and the third refrigerant channel 22 branched from the second refrigerant channel 21.

  The refrigerant flowing through the second refrigerant channel 21 is decompressed by the first expansion valve 7 (point d in FIG. 2), and separated into a liquid phase and a gas phase by the gas-liquid separator 5. The separated refrigerant in the liquid phase is supercooled by the refrigerant flowing through the third refrigerant flow path 22 in the supercooler 6 (point e in FIG. 2). The refrigerant flowing through the subcooled second refrigerant channel 21 is further decompressed by the third expansion valve 9 (point f in FIG. 2) and flows into the heat absorber 4. The refrigerant flowing through the second refrigerant flow path 21 is supercooled by the supercooler 6, so even when decompressed by the third expansion valve 9, it is difficult to vaporize and flows into the heat absorber 4 in a liquid phase state. On the other hand, the separated refrigerant in the gas phase state flows into the second compressor 2b via the fourth refrigerant flow path 23 (point g in FIG. 2).

  The refrigerant flowing through the third refrigerant flow path 22 is depressurized by the second expansion valve 8 and becomes lower in temperature than the refrigerant flowing through the second refrigerant flow path 21 (point h in FIG. 2). The refrigerant flowing through the two refrigerant channels 21 is vaporized by being supercooled, and flows into the second compressor 2b together with the refrigerant in the gas phase flowing through the fourth refrigerant channel 23 (point g in FIG. 2). In FIG. 2, the relationship between the specific enthalpy between the point c and the point h and the pressure is indicated by a broken line for explanation. Further, the specific enthalpy between the point c and the point d and the specific enthalpy between the point c and the point h are the same, but in FIG.

  The refrigerant that has flowed into the heat absorber 4 is vaporized by heat exchange in the heat absorber 4, and the gas-phase refrigerant flows into the first compressor 2a (point i in FIG. 2).

  The effect of 1st Embodiment of this invention is demonstrated.

  Heat exchange is performed between the refrigerant flowing through the second refrigerant flow path 21 and the refrigerant flowing through the third refrigerant flow path 22 branched from the second refrigerant flow path 21, and the refrigerant flowing through the second refrigerant flow path 21 is supercooled. A supercooler 6 is provided. By supercooling the refrigerant flowing into the heat absorber 4 by the subcooler 6, it is possible to suppress the vaporization of the refrigerant before flowing into the heat absorber 4, and to improve the heat absorption performance in the heat absorber 4. . In addition, by performing heat exchange between the refrigerant flowing through the second refrigerant flow path 21 and the refrigerant flowing through the third refrigerant flow path 22 branched from the second refrigerant flow path 21, a temperature adjustment device is provided for overcooling. Need not be separately provided, and the refrigeration cycle 1 can be prevented from being enlarged.

  The pressure reduction ratio in the second expansion valve 8 provided in the third refrigerant flow path 22 is made larger than the pressure reduction ratio in the first expansion valve 7 provided in the second refrigerant flow path 21. As a result, the refrigerant flowing through the second refrigerant flow path 21 in the supercooler 6 can be supercooled by the refrigerant flowing through the third refrigerant flow path 22, and the second refrigerant flow in the subcooler 6 can be achieved with a simple configuration. The refrigerant flowing through the passage 21 can be supercooled.

  If the refrigerant flows into the third expansion valve 9 in a gas-liquid mixed state, the discharge amount of the refrigerant discharged from the third expansion valve 9 is not stable, and hunting may occur. In the present embodiment, a supercooler 6 is provided between the first expansion valve 7 and the third expansion valve 9, and the refrigerant flowing into the third expansion valve 9 is supercooled by the supercooler 6. Thereby, it can suppress that a refrigerant | coolant vaporizes, it can suppress that the refrigerant | coolant of a gas-liquid mixed state flows into the 3rd expansion valve 9, and hunting arises in the refrigerant | coolant discharged from the 3rd expansion valve 9. Can be suppressed.

  A gas-liquid separator 5 is provided between the first expansion valve 7 and the supercooler 6 to separate the refrigerant flowing through the second refrigerant flow path 21 into a gas phase and a liquid phase, and only the refrigerant in the liquid phase state is separated. It flows into the subcooler 6. Thereby, it can suppress that the refrigerant | coolant of a gaseous-phase state flows into the heat absorber 4, and can supercool a refrigerant | coolant more in the supercooler 6, can suppress vaporization of a refrigerant | coolant, The endothermic performance in the heat absorber 4 can be improved.

  The refrigerant in the gas phase separated by the gas-liquid separator 5 is caused to flow into the second compressor 2b through the fourth refrigerant flow path 23. Further, the second refrigerant flow path 21 through which the refrigerant in the gas phase that has passed through the subcooler 6 flows is joined to the fourth refrigerant flow path 23, and the refrigerant in the gas phase that has passed through the subcooler 6 flows into the fourth refrigerant flow. It flows into the 2nd compressor 2b through the path | route 23. FIG. Thus, since the gas-phase state refrigerant is returned to the second compressor 2b, it is possible to suppress a decrease in the flow rate of the refrigerant circulating in the refrigeration cycle 1.

  Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 3 is a schematic configuration diagram of the refrigeration cycle 1 of the second embodiment. The second embodiment will be described with respect to differences from the first embodiment.

  In the refrigeration cycle 1 of the second embodiment, the gas-liquid separator 30 and the supercooler 31 are integrated. Specifically, a part of the third refrigerant flow path 22 is provided so as to pass through the inside of the gas-liquid separator 30, and the liquid-phase state of the gas-liquid separator 30 by the refrigerant flowing through the third refrigerant flow path 22. Overcool the refrigerant. That is, a part of the third refrigerant flow path 22 passing through the gas-liquid separator 30 functions as the supercooler 31. Note that a part of the third refrigerant flow path 22 that functions as the subcooler 31 is provided so as to be immersed in the liquid-phase refrigerant stored in the gas-liquid separator 30, and the liquid-phase refrigerant is Supercooled by the refrigerant flowing through the third refrigerant flow path 22.

  The effect of 2nd Embodiment of this invention is demonstrated.

  The supercooler 31 and the gas-liquid separator 30 are integrated. Thereby, the refrigeration cycle 1 can be made smaller than when the supercooler is provided separately from the gas-liquid separator, and the layout of the refrigeration cycle 1 can be improved.

  The embodiment of the present invention has been described above. However, the above embodiment only shows a part of application examples of the present invention, and the technical scope of the present invention is limited to the specific configuration of the above embodiment. Absent.

DESCRIPTION OF SYMBOLS 1 Refrigeration cycle 2 Compressor 2a 1st compressor 2b 2nd compressor 3 Radiator 4 Heat absorber 5 Gas-liquid separator 6 Supercooler (heat exchanger)
7 First expansion valve 8 Second expansion valve 9 Third expansion valve 21 Second refrigerant flow path (first flow path)
22 3rd refrigerant | coolant flow path (2nd flow path)
23 Fourth refrigerant channel (third channel)
30 Gas-liquid separator 31 Supercooler

Claims (6)

A refrigeration system in which a refrigerant circulates in a refrigeration cycle having a compressor, a radiator, and a heat absorber,
A first flow path through which the refrigerant that has passed through the radiator;
A second flow path branched from the first flow path and through which the refrigerant flows;
A heat exchanger for exchanging heat between the refrigerant flowing through the first flow path and the refrigerant flowing through the second flow path;
A refrigerating apparatus, wherein the refrigerant that flows through the first flow path and passes through the heat exchanger is caused to flow into the heat absorber. The refrigeration apparatus according to claim 1,
A first expansion valve that is provided upstream of the heat exchanger in the first flow path and depressurizes the refrigerant flowing through the first flow path;
A second expansion valve provided on the upstream side of the heat exchanger in the second flow path and depressurizing the refrigerant flowing in the second flow path;
The pressure reduction ratio of the second expansion valve is set larger than the pressure reduction ratio of the first expansion valve,
The heat exchanger is a subcooler that cools the refrigerant flowing through the first flow path by the refrigerant flowing through the second flow path.
A refrigeration apparatus characterized by that. The refrigeration apparatus according to claim 2,
A third expansion valve that is provided on the downstream side of the first expansion valve in the first flow path and depressurizes the refrigerant flowing in the first flow path;
The subcooler is provided between the first expansion valve and the third expansion valve.
A refrigeration apparatus characterized by that. The refrigeration apparatus according to claim 2 or 3,
A gas-liquid separator provided in the first flow path between the first expansion valve and the supercooler;
A refrigerant in a gas phase separated by the gas-liquid separator flows, and a third flow path for allowing the refrigerant in the gas phase to flow into the compressor,
The second flow path through which the refrigerant that has passed through the subcooler merges with the third flow path;
A refrigeration apparatus characterized by that. The refrigeration apparatus according to claim 3,
A gas-liquid separator provided in the first flow path between the first expansion valve and the third expansion valve and having the supercooler;
A refrigerant in a gas phase separated by the gas-liquid separator flows, and a third flow path for allowing the refrigerant in the gas phase to flow into the compressor,
The second flow path through which the refrigerant having exchanged heat with the liquid-phase refrigerant stored in the gas-liquid separator joins the third flow path;
A refrigeration apparatus characterized by that. The refrigeration apparatus according to claim 4 or 5, wherein
The compressor is configured by arranging a first compressor and a second compressor provided on the radiator side of the first compressor in series,
The third flow path causes the refrigerant that has flowed through the second flow path and the gas phase refrigerant of the gas-liquid separator to flow into the second compressor.
A refrigeration apparatus characterized by that.

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