JP2013036684A - Refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerating system striking a balance between the defrosting with respect to an evaporator at a low outside air temperature, and the maintenance and improvement of hot-water supply capacity.SOLUTION: This refrigeration cycle device using an ejector includes: a compressor 1; a first radiator 2; a second radiator 7; the evaporator 5; the ejector 3; a gas-liquid separator 4; a vortex tube 6; a first bypass passage A which is branched off from a second flow path 20 connecting the first radiator 2 and the inlet of the ejector 3 and which is connected to the introducing port of the vortex tube 6; a second bypass passage B for connecting the high temperature side outlet of the vortex tube 6 and the inlet of the ejector 3 through the second radiator 7; a third bypass passage C which is branched off from the second bypass passage B on the upstream side of the second radiator 7 and which is connected to the inlet of the ejector 3 through the evaporator 5; and a fourth bypass passage D for connecting the low temperature side outlet of the vortex tube 6 and the gas-liquid separator 4.

Description

  The present invention relates to a refrigeration cycle apparatus, and more particularly to a refrigeration cycle apparatus using an ejector.

  Conventionally, as a refrigeration cycle apparatus constituting a refrigerant circuit, one in which refrigerant circulates in the order of compressor → radiator → expansion valve → evaporator → compressor has been widely known. However, this refrigeration cycle apparatus using an expansion valve has a drawback that some kinetic energy is lost as a vortex when the refrigerant pressure is reduced by the expansion valve. On the other hand, a refrigeration cycle system has been developed that replaces the expansion valve with an injection device called an ejector to suppress the generation of vortices and convert part of the lost kinetic energy into pressure energy to help the compressor work. It was.

  However, in the refrigeration cycle apparatus using this ejector, a refrigerant circuit that circulates in the order of compressor → radiator → ejector → gas-liquid separator → compressor and gas-liquid separator → evaporator → ejector → gas-liquid separator Although there is a refrigerant circuit that circulates in order, the refrigeration efficiency can be increased, but the frost attached to the evaporator is removed by flowing a high-temperature refrigerant into the evaporator, which was possible in the expansion valve cycle. There was a problem that defrosting operation was not possible. This is because in the refrigeration cycle apparatus using the ejector, the high-temperature refrigerant flowing through the radiator and the refrigerant flowing through the evaporator are different flows, and the flow for driving cannot be supplied to the evaporator. .

  As a countermeasure, for example, there is “Ejector Cycle (registered trademark)” disclosed in Japanese Patent Application Laid-Open No. 2003-083622 (Patent Document 1). In the present invention, as shown in FIG. 6, a hot gas passage 700 (bypass passage) with a valve is provided immediately after the compressor 100, and when the evaporator 300 needs to be defrosted, Thus, the high-temperature and high-pressure refrigerant discharged from the compressor 100 is sent to the evaporator 300, and the evaporator 300 is defrosted.

  On the other hand, as a refrigeration cycle apparatus that does not use an expansion valve or an ejector, there is a “refrigeration cycle apparatus” disclosed in Japanese Patent Laid-Open No. 2005-127624 (Patent Document 2). As shown in FIG. 7, the present invention is a refrigeration cycle apparatus using a vortex tube 3 in an expansion valve portion of a normal vapor compression refrigeration cycle apparatus, and is separated into a high-temperature refrigerant and a low-temperature refrigerant by the vortex tube 3. It is an invention that effectively uses high-temperature refrigerants. The high-temperature refrigerant is returned to the vicinity of the inlet of the radiator 2 after separation, and effectively increases the efficiency of the refrigeration cycle apparatus and reduces the power of the compressor 1 by increasing the hot water supply capacity. In addition, since the code | symbol currently used by description of a prior art uses the code | symbol of the patent document shown below as it is, it differs from the code | symbol used by the component of this invention.

Japanese Patent Laid-Open No. 2003-083622 JP 2005-127624 A

  However, in the invention according to Patent Document 1, a part of the high-temperature and high-pressure refrigerant discharged from the compressor 100 via the hot gas passage 700 during defrosting is sent to the evaporator 300 side. However, there was a problem that it was difficult to maintain the hot water supply capacity during defrosting. Moreover, in the invention which concerns on patent document 2, since the function which defrosts at the time of low outside temperature is not provided, there existed a problem that the efficiency fall of the refrigerating-cycle apparatus at the time of low outside temperature was concerned.

  This invention is made | formed in view of said situation, Comprising: It aims at providing the refrigerating-cycle apparatus which makes compatible the defrosting of the evaporator at the time of low external temperature, and maintenance and improvement of hot-water supply capability.

(1) In order to solve the above problems, a refrigeration cycle apparatus using an ejector according to the present invention includes a compressor that sucks and compresses a refrigerant, a first radiator that radiates the refrigerant, and radiates the refrigerant. An ejector having a second radiator, an evaporator for evaporating the refrigerant, an inlet for sucking the refrigerant, an inlet for sucking the refrigerant, and an outlet for discharging the refrigerant, and the refrigerant as a gas phase refrigerant and a liquid phase refrigerant A vortex tube having an inlet for introducing refrigerant, a high-temperature side outlet for discharging high-temperature refrigerant, and a low-temperature side outlet for discharging low-temperature refrigerant, the compressor, and the first A first flow path for connecting the heat radiator, a second flow path for connecting the first heat radiator and the inlet of the ejector, and an outlet of the ejector and the gas-liquid separator. A third flow path, the gas-liquid separator, and the evaporator A fourth flow path for connecting the evaporator and the suction port of the ejector, a sixth flow path for connecting the gas-liquid separator and the compressor, A first bypass path branched from the second flow path and connected to the inlet of the vortex tube; a high temperature side outlet of the vortex tube; and an inlet of the ejector passing through the second radiator And a third bypass branching from the second bypass path upstream of the second radiator and passing through the evaporator and connected to the inlet of the ejector There is provided a refrigeration cycle apparatus comprising a passage, and a fourth bypass passage connected to the low temperature side outlet of the vortex tube and the gas-liquid separator.

(2) In addition to the above (1), a refrigeration cycle apparatus provided with a first valve provided on the ejector side above the branch point of the first bypass path on the second flow path is provided.

(3) In addition to the above (2), a second valve provided on the first bypass path, and a third valve provided on the third bypass path and upstream of the evaporator; A refrigeration cycle apparatus comprising: a fourth valve provided on the downstream side of the branch point with the third bypass path on the second bypass path and upstream of the second radiator. To do.

  According to the refrigeration cycle apparatus according to the present invention, it is possible to achieve both the defrosting of the evaporator at the time of low outside air temperature and the maintenance / improvement of hot water supply capacity. More specifically, the defrosting operation is performed while maintaining the hot water supply capacity, the hot water supply capacity is improved when it is desired to improve the hot water supply capacity, the energy recovery is performed using the ejector, and the hot water supply capacity using the vortex tube. Can be increased.

It is a figure which shows the refrigerating-cycle apparatus of embodiment which concerns on this invention. It is a figure which shows an example of the ejector used for embodiment which concerns on this invention. It is a figure which shows an example of the vortex tube used for embodiment which concerns on this invention. It is a Mollier diagram in an embodiment concerning the present invention. It is a figure which shows the pressure fluctuation in the vortex tube in embodiment which concerns on this invention. It is a figure which shows an example of a prior art. It is a figure which shows another example of a prior art.

  Hereinafter, embodiments according to the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a diagram showing a refrigeration cycle apparatus according to an embodiment of the present invention. In FIG. 1, a solid line connecting the elements indicates a refrigerant circuit. The thick solid line is the main refrigerant circuit of the ejector cycle, and the thin solid line is the bypass path in the present invention. Moreover, the dotted line has shown the circuit of the water through which water and hot water flow. In addition, the arrow attached | subjected to the solid line and the dotted line has each shown the direction through which a refrigerant | coolant flows. In the figure, the refrigeration cycle apparatus of the present embodiment connects a first flow path 10 that connects a compressor 1 and a first radiator 2, and a first radiator 2 and an inlet 3 a of an ejector 3. The second flow path 20 to be connected, the third flow path 30 for connecting the outlet 3c of the ejector 3 and the gas-liquid separator 4, and the fourth flow path for connecting the gas-liquid separator 4 and the evaporator 5 to each other. 40, a fifth flow path 50 connecting the evaporator 5 and the suction port 3b of the ejector 3, a sixth flow path 60 connecting the gas-liquid separator 4 and the compressor 1, and a second flow Branches from the path 20 (branch point A1), passes through the first bypass path A connected to the inlet 6a of the vortex tube 6, the high temperature side outlet 6b of the vortex tube 6, and the second radiator 7, The second bypass connecting the inlet 3a of the ejector 3 through the junction with the second flow path 20 (a junction B1). Branching from the second bypass path B to the upstream side of the second radiator 7 (branch point C1), passing through the evaporator 5 and passing through the junction with the second bypass path B (Conjunction point C2), a third bypass path C connected to the inlet 3a of the ejector 3, and a fourth bypass path D connecting the low temperature side outlet 6c of the vortex tube 6 and the gas-liquid separator 4 Has been. The configurations of the ejector 3 and the vortex tube 6 are as shown in FIGS. 2 and 3, respectively, and will be described in detail later.

  In the main refrigerant circuit including the first flow path 10, the second flow path 20, the third flow path 30, and the sixth flow path 60, the compressor 1 sucks and compresses the refrigerant, and the first heat release. Heat is exchanged between the water introduced from the hot water tank in the cooler 2 and the compressed refrigerant to generate hot water. The ejector 3 decompresses and expands the refrigerant and sucks the vapor-phase refrigerant evaporated in the evaporator 5. The pressure is increased, a part of the energy is recovered, the refrigerant introduced from the ejector 3 in the gas-liquid separator 4 is separated into a gas phase refrigerant and a liquid phase refrigerant, and the gas phase refrigerant is sucked into the compressor 1. As a result, the refrigerant makes a round.

  Next, the ejector 3 and the gas-liquid separator 4 will be described. As shown in FIG. 2, the ejector 3 includes a nozzle 31, a mixing unit 32 that mixes the high-speed refrigerant injected from the nozzle 31 and the gas-phase refrigerant sucked from the evaporator 5, and a diffuser 33. ing. The high-pressure refrigerant that has flowed from the inlet 3a of the nozzle 31 is injected into the mixing section 32 by the nozzle 31 and depressurized, and the gas evaporated by the evaporator 5 sucked from the suction port 3b using the negative pressure generated by the injection. Mixed with phase refrigerant. The flow rate of the mixed refrigerant decreases from the mixing section 32 to the diffuser 33, and the pressure increases. The outlet 3 c of the diffuser 33 is connected to the gas-liquid separator 4, and the refrigerant is separated into gas and liquid in the gas-liquid separator 4. The separated liquid phase refrigerant is guided to the evaporator 5, and the gas phase refrigerant is sucked into the compressor 1.

  In the above process, unlike the expansion valve, the ejector 3 can be expanded approximately isentropically. Specifically, in the expansion valve, a part of the energy lost due to the vortex generation is recovered as the kinetic energy of the refrigerant, and the recovered kinetic energy is converted into pressure energy by the mixing unit 32 and the diffuser 33 to change the pressure of the refrigerant. Is increased to increase the suction pressure of the compressor 1 and improve its efficiency. Moreover, since the state of the refrigerant at the inlet 5a of the evaporator 5 is liquid, the performance can be improved by effects such as pressure loss reduction in the evaporator 5 and increase in heat transfer coefficient.

  In the sub refrigerant circuit including the fourth flow path 40 and the fifth flow path 50, the liquid phase refrigerant separated in the gas-liquid separator 4 is evaporated by exchanging heat with the atmosphere in the evaporator 5, and in the ejector 3. The evaporated refrigerant is sucked, and the sucked refrigerant is mixed with the refrigerant decompressed and expanded by the nozzle 31 of the ejector 3 via the first radiator 2 of the main refrigerant circuit, and the pressure is increased by the diffuser 33. Then, the refrigerant goes around by returning to the gas-liquid separator 4.

  In the first bypass A, the refrigerant that has passed through the first radiator 2 is branched from the second flow path 20 (branch point A1) before flowing into the ejector 3, and is introduced into the vortex tube 6. The refrigerant introduced into the vortex tube 6 from the first bypass path A is separated into a high temperature refrigerant and a low temperature refrigerant, and the high temperature refrigerant is discharged from the high temperature side outlet 6b and enters the second bypass path B. The high-temperature refrigerant exchanges heat with water guided from the tank in the second radiator 7 to generate hot water, and the refrigerant that has passed through the second radiator 7 is transferred from the first radiator 2 to the second radiator. The refrigerant directly joined via the flow path 20 is joined (joining point B1) and sent to the ejector 3.

  In the third bypass C, the front surface of the evaporator 5 on the air suction side of the high-temperature refrigerant discharged from the high-temperature side outlet 6b of the vortex tube 6 and branched (branch point C1) before flowing into the second radiator 7 is obtained. The refrigerant that has been defrosted, defrosted, and defrosted by the evaporator 5 merges with the refrigerant led from the first radiator 2 and the second radiator 7 (confluence point C2) and is ejected. 3 is sent.

  In the fourth bypass D, the low-temperature refrigerant discharged from the low-temperature outlet 6 c of the vortex tube 6 is guided to the gas-liquid separator 4. In this embodiment, the gas-liquid separator 4 is directly joined, but the present invention is not limited to this, and it is sufficient that the low-temperature refrigerant discharged from the vortex tube 6 can flow into the gas-liquid separator 4. For example, the low-temperature refrigerant discharged from the vortex tube 6 may join the refrigerant jetted from the outlet 3c of the diffuser 33 of the ejector 3 and then flow into the gas-liquid separator 4.

  The vortex tube 6 positioned at the branch point of the first bypass path A, the second bypass path B, and the fourth bypass path D will be described with reference to FIGS. As shown in FIG. 3, the vortex tube 6 mainly includes a nozzle 61, a vortex chamber 62, a control valve 63, and a diffuser 64. The refrigerant flowing in the tangential direction from the inlet 6a of the nozzle 61 into the vortex chamber 62 becomes a high-speed vortex, flows from the right to the left in the figure while swirling the inner wall surface of the pipe, and the opening degree is adjusted by the control valve 63. A part of the high temperature side outlet 6b flows out of the high temperature side outlet 6b. On the other hand, the remaining refrigerant whose flow direction is reversed by the control valve 63 flows from the left to the right in the figure as a vortex in the center of the vortex chamber 62, and then flows out from the low temperature side outlet 6c of the diffuser 64 at a low temperature. . This is because the vortex of the refrigerant flowing on the inner wall surface of the pipe is a free vortex, whereas the vortex of the refrigerant flowing in the center of the vortex chamber 62 is a forced vortex generated by the free vortex. This is because a decrease in energy occurs, and the difference is transferred as heat from the latter to the former, thereby realizing temperature separation.

  FIG. 4 shows an embodiment according to the present invention, that is, when a vortex tube is incorporated in the ejector cycle, the first valve 81 and the third valve 83 are closed, and the second valve 82 and the fourth valve 84 are opened. It is a Mollier diagram. Here, FIG. 4 shows the first bypass where the high-temperature and high-pressure refrigerant discharged from the compressor does not pass through the second flow path 20 in the main refrigerant circuit and flows directly from the first radiator 2 into the ejector 3. Shows the case of flowing from the path A to the second bypass path B through the vortex tube 6 and the second radiator 7 into the ejector 3 (corresponding to the operation for increasing the hot water supply capacity among the operations described later). ing. The high-temperature and high-pressure refrigerant R1a discharged from the compressor 1 exchanges heat with a fluid (for example, water) by the first radiator 2 to become a low-temperature and high-pressure refrigerant R2a. Thereafter, the low-temperature high-pressure refrigerant R2a flows into the nozzle inlet 6a of the vortex tube 6 and the high-temperature high-pressure refrigerant R1b discharged from the high-temperature side outlet 6b of the vortex tube 6 exchanges heat with a fluid (for example, water) in the second radiator 7. By doing so, a low-temperature and high-pressure refrigerant R2b is obtained. The low-temperature and high-pressure refrigerant R2b is decompressed by the nozzle 31 of the ejector 3 to become a gas-liquid two-phase refrigerant R3, and the gas-liquid two-phase refrigerant flows from the inlet 3a of the nozzle 31 and is ejected to the mixing unit 32. Then, the jetted refrigerant and the vapor phase refrigerant R7 evaporated by the evaporator 5 sucked from the suction port 3b are mixed to become the refrigerant R4. The refrigerant R4 is pressurized by the diffuser 33, and the refrigerant flowing out from the outlet 3c of the diffuser 33 is separated into the gas-liquid separator 4, that is, the refrigerant R5 into the gas-phase refrigerant R8 and the liquid-phase refrigerant R6. Moreover, the low-temperature refrigerant | coolant discharged from the low temperature side exit 6c of the vortex tube 6 merges with the refrigerant | coolant ejected from the exit 3c of the diffuser 33, and in the embodiment of FIG. 1, it merges with the gas-liquid separator 4 and becomes state R5. Yes. The separated liquid-phase refrigerant R6 is supplied to the evaporator 5, and the vapor-phase refrigerant R7 evaporated by, for example, exchanging heat with the atmosphere in the evaporator 5 is again sucked into the suction port 3b of the ejector 3 (state of R4) ) Further, the gas-phase refrigerant separated by the gas-liquid separator 4 is again sucked into the compressor 1 in the state R8.

  FIG. 5 shows pressure fluctuations of the high-temperature refrigerant and the low-temperature refrigerant for each part in the vortex tube 6 in the embodiment according to the present invention, that is, the nozzle 61 part, the vortex chamber 62 part, and the diffuser 64 part. The high-pressure refrigerant flowing in from the inlet 6a of the nozzle 61 reduces the pressure and passes through the nozzle 61 portion, and then the high-temperature refrigerant swirling as a vortex on the wall surface of the vortex chamber 62 is the inlet of the vortex chamber 62 located on the nozzle 61 side. The pressure rises toward the high temperature side outlet 6b, and almost recovers to the level when flowing into the inlet 6a of the nozzle 61. On the other hand, for the low-temperature refrigerant in which a part of the refrigerant is reversed by the control valve 63 positioned at the left end of the vortex chamber 62 and flows back in the central portion of the vortex chamber 62, the pressure is increased from the control valve 63 toward the nozzle 61 side. It is lowered and part of the diffuser 64 is recovered.

  Each bypass path or flow path described above is provided with several valves for controlling the flow of the refrigerant so that the refrigeration cycle apparatus can perform a desired operation. That is, the first valve 81 provided on the ejector 3 side from the branch point A1 of the first bypass path A on the second flow path 20 and the first valve provided on the first bypass path A. The second valve 82, the third valve 83 provided on the third bypass path C and upstream of the evaporator 5, and the second heat sink 7 on the second bypass path B There is a fourth valve 84 provided on the downstream side. These valves are not particularly limited as long as the valves can be opened and closed and the opening thereof can be adjusted. For example, proportional solenoid valves are preferably used. In the present embodiment, the fourth valve 84 is provided on the downstream side of the radiator 7, but the present invention is not limited to this, and may be provided between the radiator 7 and the branch point C1. It is sufficient that the second bypass passage B is provided so that the refrigerant does not flow.

  The evaporator 5 is provided with a pressure sensor 51 and a temperature sensor 52 on the outlet side of the evaporated refrigerant on the sub refrigerant circuit. This is for detecting data as a judgment material when selecting the defrosting operation of the evaporator 5.

  In FIG. 1, a hot water supply circuit that generates hot water by receiving heat supplied from the refrigeration cycle apparatus described above is indicated by a broken line. That is, a fluid (for example, water) is supplied from the hot water supply tank to at least one of the first radiator 2 and the second radiator 7, and the fluid (hot water) heated by heat exchange with the refrigerant is supplied to the hot water tank. Return circuit. The fluid (water) guided from the hot water tank is controlled to flow into the first radiator 2 and / or the second radiator 7 by the fifth valve 85 and the sixth valve 86.

  Furthermore, the refrigeration cycle apparatus of the present embodiment detects pressure and temperature from a pressure sensor 51 and a temperature sensor 52 provided in the evaporator 5, and a plurality of temperature sensors for each water level provided in the hot water tank, Controls the opening and closing and opening of the first to fourth valves 81, 82, 83, 84 for controlling the flow of the fluid, and the fifth and sixth valves 85, 86 for controlling the flow of the fluid (for example, water). Control means (not shown) are provided. This control means is incorporated in a control device that performs capacity control or the like based on the rotational speed of the compressor 1, and controls the flow of refrigerant and fluid to operate the refrigeration cycle apparatus in a normal operation and a normal operation as will be described later. And the defrosting operation, the operation for increasing the hot water supply capability, and the operation for increasing the hot water supply capability and the combined operation of the defrosting operation are provided.

  Next, the basic operation of the refrigeration cycle apparatus having the above configuration will be described with reference to FIG. Table 1 shows the opening / closing and opening of each valve for each operation (operation).

  First, the operation when performing normal operation will be described. As shown in Table 1, in normal operation, only the first valve 81 provided on the second flow path 20 of the main refrigerant circuit is opened and provided on the first bypass path A. The second valve 82, the third valve 83 provided on the third bypass passage C, and the fourth valve 84 provided on the second bypass passage B are closed. Thereby, the refrigerant such as carbon dioxide in a supercritical state discharged from the first compressor 1 exchanges heat with water in the first radiator 2 and supplies heat to the water, and then the total amount of the refrigerant is the first. 1 passes through the first valve 81 and is sent to the ejector 3, where the decompressed and expanded refrigerant is sent to the gas-liquid separator 4 for gas-liquid separation. Thereafter, the gas-phase refrigerant is sent to the suction port of the compressor 1, but the liquid-phase refrigerant is evaporated by exchanging heat with the atmosphere in the evaporator 5, and then sucked into the ejector 3 by the suction effect to again separate the gas and liquid. Will be sent to the container 4. In addition, since the heat radiator to function at this time is only the first heat radiator 2, the water circuit opens the valve 85 and closes the valve 86.

  Next, the operation at the time of performing the normal operation and the defrosting operation will be described. As shown in Table 1, when the normal operation and the defrosting operation are performed at the same time, the first valve 81 provided on the second flow path 20 of the main refrigerant circuit and the first bypass path A are used. The second valve 82 provided on the third valve 83 and the third valve 83 provided on the third bypass C are opened. Then, the fourth valve 84 on the second bypass path B is closed. As a result, the refrigerant such as carbon dioxide in a supercritical state discharged from the compressor 1 exchanges heat with water by the first radiator 2 and supplies heat to the water, and then a part of the refrigerant is second. After passing through the valve 82 and sent to the vortex tube 6 and separated into a high-temperature refrigerant and a low-temperature refrigerant, the high-temperature refrigerant passes through the third valve 83 and is sent to the evaporator 5 to remove frost adhering to the evaporator 5. Remove. Thereafter, the remaining refrigerant that has passed through the first valve 81 merges and is sent to the ejector 3. Since the rest is the same as the normal operation, the description is omitted. The low-temperature refrigerant separated by the vortex tube 6 is sent to the gas-liquid separator 4 through the third bypass C without passing through the ejector 3. Note that the distribution ratio of the refrigerant in the main refrigerant circuit and the bypass passage A is adjusted by controlling the first valve 81 and the second valve 82. Since the rest is the same as the normal operation, the description is omitted. Here, the defrosting operation is performed when the state of the evaporator 5 is grasped from the temperature sensor 52 and the pressure sensor 51 installed on the outlet side of the evaporator 5 and defrosting is necessary. Again, since the heat radiator to function at this time is only the first heat radiator 2, the water circuit opens the valve 85 and closes the valve 86.

  Next, an operation for increasing the hot water supply capacity will be described. As shown in Table 1, when the hot water supply capacity is increased, the first valve 81 provided on the second flow path 20 of the main refrigerant circuit is closed and provided on the first bypass path A. Then, the second valve 82 and the fourth valve 84 provided on the second bypass B are opened. Then, the third valve 83 provided on the third bypass C is closed. Here, since the first radiator 2 and the second radiator 7 are functioned, the valves 85 and 86 are open. Thus, after the refrigerant such as carbon dioxide in a supercritical state discharged from the compressor 1 exchanges heat with water by the first radiator 2 and supplies heat to the water, the entire amount increases the hot water supply capacity. After passing through the second valve 82 and being sent to the vortex tube 6 and separated into a high-temperature refrigerant and a low-temperature refrigerant, the high-temperature refrigerant exchanges heat with water in the second radiator 7 to heat the water. Then, it passes through the fourth valve 84 and is sent to the ejector 3. As shown in FIG. 4, the temperature and pressure can be adjusted using the control valve 63 of the vortex tube 6 until the high-temperature refrigerant separated by the vortex tube 6 and brought into the state R1b is as close to the state R1a as possible. Since the rest is the same as the normal operation, the description is omitted. Further, the low-temperature refrigerant separated by the vortex tube 6 is sent to the gas-liquid separator 4 through the fourth bypass D without passing through the ejector 3. Since the rest is the same as the normal operation, the description is omitted. The operation for increasing the hot water supply capacity is executed as necessary depending on the temperature state of the temperature sensor for each water level installed in the hot water supply tank outside the refrigeration cycle apparatus.

  Finally, the operation in the case of simultaneously performing the operation for increasing the hot water supply capacity and the defrosting operation will be described. As shown in Table 1, when the hot water supply capacity is increased and the defrosting operation is performed, the first valve 81 on the second flow path 20 of the main refrigerant circuit is closed, and the first bypass path A is The second valve 82 provided on the second bypass passage C, the third valve 83 provided on the third bypass passage C, and the fourth valve 84 provided on the second bypass passage B are opened. As a result, the refrigerant such as carbon dioxide in a supercritical state discharged from the compressor 1 exchanges heat with water by the first radiator 2 and supplies heat to the water, and then the entire amount is supplied to the vortex tube 6. The refrigerant sent to be separated into a high-temperature refrigerant and a low-temperature refrigerant is further separated into a refrigerant for increasing the hot water supply capacity and a refrigerant for performing a defrosting operation at the branch point C1, and then You will be driving for each purpose. The distribution control of the high-temperature refrigerant sent to the front side of the air intake side of the second radiator 7 and the evaporator 5 is performed by the valve 83 and the valve 84. The rest is the same as the operation for increasing the hot water supply capacity and the defrosting operation, and thus the description thereof is omitted. On the other hand, the low-temperature refrigerant separated by the vortex tube 6 is sent to the gas-liquid separator 4 without passing through the ejector 3. Since the rest is the same as the normal operation, the description is omitted. Note that the operation for increasing the hot water supply capacity and the defrosting operation are performed according to necessity as described above.

  The embodiment according to the present invention has been described in detail above, but the refrigeration cycle apparatus according to the present invention is not limited to the above-described embodiment, and is within the scope of the gist of the present invention described in the claims. Various modifications and changes are possible. For example, the compressor 1 can be applied to a heat pump apparatus having various compressors such as a rotary type, a scroll type, or a reciprocating type. The compressor 1 may be a multistage compression mechanism having two or more stages.

DESCRIPTION OF SYMBOLS 1 Compressor 2 1st heat radiator 3 Ejector 4 Gas-liquid separator 5 Evaporator 6 Vortex tube 7 2nd heat radiator 81-84 1st thru | or 4th valve 85, 86 5th, 6th valve 10 1st 1 channel 20 second channel 30 third channel 40 fourth channel 50 fifth channel 60 sixth channel A first bypass channel B second bypass channel C third channel Bypass path D Fourth bypass path

Claims (3)

A compressor that sucks and compresses the refrigerant;
A first radiator that dissipates the refrigerant;
A second radiator that dissipates the refrigerant;
An evaporator for evaporating the refrigerant;
An ejector having an inlet for sucking refrigerant, an inlet for sucking refrigerant, and an outlet for discharging refrigerant;
A gas-liquid separator that separates the refrigerant into a gas-phase refrigerant and a liquid-phase refrigerant;
A vortex tube having an inlet for introducing the refrigerant, a high temperature side outlet for discharging the high temperature refrigerant, and a low temperature side outlet for discharging the low temperature refrigerant;
A first flow path connecting the compressor and the first radiator;
A second flow path connecting the first radiator and the inlet of the ejector;
A third flow path connecting the outlet of the ejector and the gas-liquid separator;
A fourth flow path connecting the gas-liquid separator and the evaporator;
A fifth flow path connecting the evaporator and the suction port of the ejector;
A sixth flow path connecting the gas-liquid separator and the compressor;
A first bypass path branched from the second flow path and connected to the inlet of the vortex tube;
A second bypass path that connects the high temperature side outlet of the vortex tube and the inlet of the ejector through the second radiator;
A third bypass path that branches from the second bypass path upstream of the second radiator, passes through the evaporator and is connected to the inlet of the ejector;
A fourth bypass path connecting the low temperature side outlet of the vortex tube and the gas-liquid separator;
A refrigeration cycle apparatus comprising:   2. The refrigeration cycle apparatus according to claim 1, further comprising a first valve provided on the ejector side with respect to the branch point of the first bypass path on the second flow path.   A second valve provided on the first bypass path; a third valve provided on the third bypass path upstream of the evaporator; and on the second bypass path. The refrigeration cycle apparatus according to claim 2, further comprising a fourth valve provided on the downstream side of a branch point with the third bypass path on the upstream side of the second radiator.

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