JP2017142027A - Air conditioning device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve performance of a refrigeration circuit by exerting original feature of a vortex tube in a refrigeration circuit using a vortex tube.SOLUTION: The refrigeration circuit 1 in an air conditioning device 100 includes a first supercooling heat exchanger 7 for exchanging heat between a low-temperature gas refrigerant introduced into a compressor 2 from a low-temperature refrigerant discharge port 4c of the vortex tube 4 and a high-pressure refrigerant introduced into a second heat exchanger 10 from a high-temperature refrigerant discharge port 4b of the vortex tube 4 via a first heat exchanger 6, during air-conditioning operation.SELECTED DRAWING: Figure 1

Description

  The present invention relates to an air conditioner having a refrigeration circuit using a vortex tube.

  Some air conditioners use vortex tubes in the refrigeration circuit. For example, Patent Literature 1 discloses an air conditioner in which a compressor, a condenser, an expansion mechanism, and an evaporator are sequentially connected to constitute a refrigeration circuit that circulates a refrigerant, and a vortex tube is provided between the compressor and the condenser. Is disclosed. The vortex tube has a refrigerant supply port, a high temperature refrigerant discharge port, and a low temperature refrigerant discharge port. The refrigerant supply port of this vortex tube is connected to the refrigerant discharge side refrigerant piping of the compressor, the high temperature refrigerant discharge port of the vortex tube is connected to the condenser, and the low temperature refrigerant discharge port of the vortex tube is connected to the suction port of the compressor. It is connected. Further, an electromagnetic on-off valve that is controlled to open only at the time of heating activation is provided between the refrigerant supply port of the vortex tube and the discharge port of the compressor. The high-temperature and high-pressure gas refrigerant discharged from the compressor that has not reached the high-temperature and high-pressure state at the start of heating is first supplied to the vortex tube and separated into a high-temperature gas refrigerant and a low-temperature gas refrigerant. And since only a high temperature gas refrigerant | coolant flows in into a condenser among the isolate | separated refrigerant | coolants, even if it turns the indoor unit side fan at the time of this heating start-up, a warm air can be ventilated. That is, in the refrigeration circuit described in Patent Document 1, the vortex tube is used for the purpose of extracting the high-temperature gas refrigerant from the refrigerant discharged from the compressor when heating is started.

JP-A-8-313096

  However, in Patent Document 1, since the low-temperature gas refrigerant discharged from the low-temperature refrigerant discharge port of the vortex tube circulates as it is to the compressor, this low-temperature gas refrigerant has not been effectively used in the refrigeration circuit. Therefore, there is room for improving the capacity of the refrigeration circuit.

  In view of the above circumstances, an object of the present invention is to provide an air conditioner that can improve the performance of a refrigeration circuit by utilizing a refrigerant circulating between the vortex tube and a compressor in a refrigeration circuit using a vortex tube. Is to provide.

  In order to achieve the above object, in the air conditioning apparatus of the present invention, during cooling operation, the refrigerant is a compressor, from the refrigerant supply port of the vortex tube to the high-temperature refrigerant discharge port, the first heat exchanger, and the first subcooling heat exchanger. A refrigeration circuit that sequentially circulates through the expansion valve and the second heat exchanger, and in which the refrigerant circulates in order from the refrigerant supply port of the compressor and the vortex tube to the low-temperature refrigerant discharge port and the first subcooling heat exchanger. And the first supercooling heat exchanger exchanges heat between the high-pressure refrigerant that has flowed out of the first heat exchanger and the low-temperature gas refrigerant that has flowed out of the low-temperature refrigerant discharge port of the vortex tube.

  In the air conditioning apparatus of the present invention, during the heating operation, the refrigerant flows from the compressor, the refrigerant supply port of the vortex tube to the high-temperature refrigerant discharge port, the second heat exchanger, the second subcooling heat exchanger, and the expansion. A refrigeration circuit that sequentially circulates the valve, the first heat exchanger, and the refrigerant circulates sequentially from the compressor, a refrigerant supply port of the vortex tube to a low-temperature refrigerant discharge port, and the second subcooling heat exchanger. The second supercooling heat exchanger exchanges heat between the high-pressure refrigerant that has flowed out of the second heat exchanger and the low-temperature gas refrigerant that has flowed out of the low-temperature refrigerant discharge port of the vortex tube.

  In the air conditioner of the present invention, the air conditioner further includes a first pressure sensor that measures the pressure at the outlet of the nozzle of the vortex tube, and a second pressure that measures the pressure on the high-temperature refrigerant outlet side of the vortex tube. A sensor, a third pressure sensor for measuring the pressure on the low-temperature refrigerant outlet side of the vortex tube, a first temperature sensor for measuring the temperature on the high-temperature refrigerant outlet side of the vortex tube, and a low-temperature refrigerant discharge of the vortex tube The temperature, pressure, and flow rate of the refrigerant discharged from the vortex tube based on the measurement results of the second temperature sensor that measures the temperature on the outlet side, the first to third pressure sensors, and the first and second temperature sensors. A control unit that controls the pressure at the outlet of the nozzle and the opening of the flow rate adjustment valve so that the ratio becomes a predetermined value Comprising a.

  According to the present invention, the performance of the refrigeration circuit can be improved.

The refrigerating circuit at the time of air_conditionaing | cooling operation of the air conditioning apparatus of one Embodiment. The refrigerating circuit at the time of the heating operation of the air conditioning apparatus of one Embodiment. The block diagram of the control part of the air conditioning apparatus of one Embodiment. The control flow of the control part of the air conditioning apparatus of one Embodiment.

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

  The refrigeration circuit 1 of the air conditioner 100 shown in FIGS. 1 and 2 includes a compressor 2, an oil separator 3, a vortex tube 4, a four-way valve 5, a first heat exchanger 6, and a first subcooling heat exchanger 7. , Expansion valve 8, second subcooling heat exchanger 9, second heat exchanger 10, accumulator 11, first check valve 12, second check valve 13, three-way valve 14 and pipe P connecting them Composed.

  As shown in FIG. 1, the refrigeration circuit 1 includes a compressor 2, an oil separator 3, a vortex tube 4, a four-way valve 5, a first heat exchanger 6, and a first subcooling heat exchanger, as shown in FIG. 7, an expansion valve 8, a second subcooling heat exchanger 9, a second heat exchanger 10, a four-way valve 5, an accumulator 11, and a main refrigeration circuit (main refrigeration circuit during cooling operation) sequentially connected to the compressor 2. , Compressor 2, oil separator 3, vortex tube 4, three-way valve 14, first supercooling heat exchanger 7, first check valve 12, accumulator 11, sub-refrigeration circuit sequentially connected to compressor 2 ( A secondary refrigeration circuit is formed during cooling operation.

  On the other hand, during the heating operation, the refrigeration circuit 1 includes a compressor 2, an oil separator 3, a vortex tube 4, a four-way valve 5, a second heat exchanger 10, and a second subcooling heat exchange, as shown in FIG. Main refrigeration circuit (main refrigeration circuit during heating operation) sequentially connected to the chamber 9, the expansion valve 8, the first supercooling heat exchanger 7, the first heat exchanger 6, the four-way valve 5, the accumulator 11, and the compressor 2 And a secondary refrigeration circuit sequentially connected to the compressor 2, the oil separator 3, the vortex tube 4, the three-way valve 14, the second supercooling heat exchanger 9, the second check valve 13, the accumulator 11, and the compressor 2. (Sub-refrigeration circuit during heating operation) is formed.

  The vortex tube 4 includes a refrigerant supply port 4a, a high-temperature refrigerant discharge port 4b, and a low-temperature refrigerant discharge port 4c. The refrigerant supply port 4 a of the vortex tube 4 is connected to the discharge port 2 a of the compressor 2 via the oil separator 3. The high temperature refrigerant discharge port 4 b of the vortex tube 4 is connected to the four-way valve 5. The low-temperature refrigerant discharge port 4 c of the vortex tube 4 is connected to the inlet of the three-way valve 14. The vortex tube 4 is supplied with the high-temperature and high-pressure gas refrigerant discharged from the discharge port 2a of the compressor 2 from the refrigerant supply port 4a, and separates energy into high-temperature gas refrigerant and low-temperature gas refrigerant by the Ranque-Hilsch effect. To do. At that time, when the refrigerant passes through the nozzle 4d on the side of the refrigerant supply port 4a of the vortex tube 4, the energy reaches the refrigerant discharge port 4e of the nozzle 4d while performing decompression expansion close to isentropic expansion (adiabatic expansion). Separation occurs. The vortex tube 4 constitutes a high-temperature refrigerant discharge path between the refrigerant supply port 4a and the high-temperature refrigerant discharge port 4b, and constitutes a low-temperature refrigerant discharge path between the refrigerant supply port 4a and the low-temperature refrigerant discharge port 4c. The vortex tube 4 has a needle valve (not shown) in the nozzle 4d of the vortex tube on the refrigerant supply port 4a side, and a flow rate adjustment valve (not shown) on the high temperature refrigerant discharge port 4b side of the vortex tube 4. ).

  The four-way valve 5 includes four ports, the first port 5a is connected to the high temperature refrigerant outlet 4b of the vortex tube 4 as described above, the second port 5b is connected to the first heat exchanger 6, and the third The port 5c is connected to the second heat exchanger 10, and the fourth port 5d is connected to the accumulator 11 as described above.

  In the first supercooling heat exchanger 7, a main flow path 7a that is a part of the main refrigeration circuit and a sub flow path 7b that is a part of the sub refrigeration circuit are formed. One refrigerant inlet / outlet 7 c of the main channel 7 a is connected to the first heat exchanger 6, and the other refrigerant inlet / outlet 7 d is connected to the expansion valve 8. One refrigerant inlet / outlet 7e of the secondary flow path 7b is connected to the three-way valve 14, and the other refrigerant inlet / outlet 7f is connected to the first check valve 12. The first supercooling heat exchanger 7 is used for supercooling during cooling operation, and exchanges heat between the high-pressure refrigerant flowing from the first heat exchanger 6 and the low-temperature gas refrigerant flowing from the vortex tube 4. ing. During the heating operation, the low-temperature gas refrigerant that has flowed out of the vortex tube 4 by a three-way valve 14 described later flows into a second subcooling heat exchanger 9 described later, and is a follower of the first subcooling heat exchanger 7. Since it does not flow into the path 7b, the first subcooling heat exchanger 7 does not function as a heat exchanger.

  Similarly to the first subcooling heat exchanger 7, the second subcooling heat exchanger 9 includes a main flow path 9a that is a part of the main refrigeration circuit and a sub flow path 9b that is a part of the sub refrigeration circuit. Is done. One refrigerant inlet / outlet 9c of the main channel 9a is connected to the expansion valve 8, and the other refrigerant inlet / outlet 9d is connected to the second heat exchanger 10. One refrigerant inlet / outlet 9 f of the secondary flow path 9 b is connected to the three-way valve 14, and the other refrigerant inlet / outlet 9 e is connected to the second check valve 13. The second subcooling heat exchanger 9 is used for supercooling during heating operation, and exchanges heat between the high-pressure refrigerant flowing from the second heat exchanger 10 and the low-temperature gas refrigerant flowing from the vortex tube 4. ing. During the cooling operation, the low-temperature gas refrigerant that has flowed out of the vortex tube 4 by the three-way valve 14 described later flows into the first subcooling heat exchanger 7, and the secondary flow path 9 b of the second subcooling heat exchanger 9. Therefore, the second subcooling heat exchanger 9 does not function as a heat exchanger.

  The three-way valve 14 includes three ports, the first port 14a is connected to the low-temperature refrigerant discharge port 4c of the vortex tube 4 as described above, and the second port 14b is the first supercooling heat exchanger as described above. 7 and the third port 14c is connected to the secondary flow path 9b of the second subcooling heat exchanger 9 as described above. The three-way valve 14 switches the connection destination to the secondary flow path 7b of the first supercooling heat exchanger 7 during the cooling operation, and connects the connection destination to the secondary flow path 9b of the second supercooling heat exchanger 9 during the heating operation. Switch.

  Each of the first check valve 12 and the second check valve 13 is connected to a pipe P that connects the fourth port 5 d of the four-way valve 5 and the accumulator 11.

  The oil separator 3 separates and collects refrigeration oil dissolved in the high-pressure gas refrigerant discharged from the compressor 2 and returns it to the suction side of the compressor 2. Thereby, while baking of the compressor 2 is prevented, the performance deterioration of the vortex tube 4 and the heat transfer performance of various heat exchangers are also prevented.

  The first heat exchanger 6 is an outdoor heat exchanger that functions as a condenser or a radiator during cooling operation and functions as an evaporator during heating operation.

  The second heat exchanger 10 is an indoor heat exchanger and functions as an evaporator during cooling operation and functions as a condenser or radiator during heating operation.

  The first check valve 12 is connected to the secondary flow path 7 b of the first supercooling heat exchanger 7. The first check valve 12 is for preventing the refrigerant from flowing backward during the heating operation and flowing into the follower flow path 7b and the three-way valve 14 of the first supercooling heat exchanger 7.

  The second check valve 13 is connected to the secondary flow path 9 b of the second subcooling heat exchanger 9. The second check valve 13 serves to prevent the refrigerant from flowing backward during the cooling operation and flowing into the secondary flow path 9b and the three-way valve 14 of the second supercooling heat exchanger 9.

  In the refrigeration circuit 1 having this configuration, during the cooling operation, as shown in FIG. 1, the refrigerant is supplied to the vortex tube 4 via the compressor 2 and the oil separator 3, and is converted into a high-temperature gas refrigerant and a low-temperature gas refrigerant. To be separated. The low-temperature gas refrigerant separated by the vortex tube 4 flows from the fourth port 5d of the four-way valve 5 via the three-way valve 14, the secondary flow path 7b of the first supercooling heat exchanger 7, and the first check valve 12. After joining with the low-temperature refrigerant, it returns to the compressor 2 through the accumulator 11. On the other hand, the high-temperature gas refrigerant separated by the vortex tube 4 is expanded from the first port 5a to the twenty-second port 5b of the four-way valve 5, the first heat exchanger 6, the main flow path 7a of the first subcooling heat exchanger 7, and the expansion. After merging with the low-temperature refrigerant of the secondary refrigeration circuit via the valve 8, the main flow path 9a of the second subcooling heat exchanger 9, the second heat exchanger 10, and the third port 5c of the four-way valve 5 through the fourth port 5d. Return to the compressor 2 via the accumulator 11.

  Therefore, in the refrigeration circuit 1 during the cooling operation, the low-temperature gas refrigerant separated by the vortex tube 4 does not return to the compressor 2 as it is, but is discharged from the first heat exchanger 6 by the first supercooling heat exchanger 7. Since the high-pressure refrigerant thus supercooled, the heat exchange capacity of the refrigeration circuit can be improved.

  On the other hand, during the heating operation, as shown in FIG. 2, the refrigerant is supplied to the vortex tube 4 via the compressor 2 and the oil separator 3, and is separated into a high temperature gas refrigerant and a low temperature gas refrigerant. The separated low-temperature gas refrigerant is separated from the low-temperature gas refrigerant from the fourth port 5d of the four-way valve 5 via the three-way valve 14, the secondary flow path 9b of the second supercooling heat exchanger 9, and the second check valve 13. After joining, it returns to the compressor 2 through the accumulator 11. On the other hand, the separated high-temperature gas refrigerant flows from the first port 5a to the third port 5c of the four-way valve 5, the second heat exchanger 10, the main flow path 9a of the second subcooling heat exchanger 9, the expansion valve 8, 1 After merging with the low-temperature refrigerant of the secondary refrigeration circuit from the main flow path 7a of the supercooling heat exchanger 7, the first heat exchanger 6 and the second port 5b of the four-way valve 5 through the fourth port 5d, the accumulator 11 is To return to the compressor 2.

  Accordingly, even in the refrigeration circuit 1 during heating operation, the low-temperature gas refrigerant separated by the vortex tube 4 does not return to the compressor 2 as it is, but is discharged from the second heat exchanger 10 by the second subcooling heat exchanger 9. Since the high-pressure refrigerant thus supercooled, the heat exchange capacity of the refrigeration circuit can be improved.

  As shown in FIGS. 1 to 3, the air conditioner 100 of this embodiment includes a first pressure sensor 16 and a high-temperature refrigerant discharge of the vortex tube 4 at the discharge port 4 e of the nozzle 4 d on the refrigerant supply port 4 a side of the vortex tube 4. The second pressure sensor 17 is at the outlet 4b, the first temperature sensor 18 is at the high temperature refrigerant discharge port 4b of the vortex tube 4, the third pressure sensor 19 is at the low temperature refrigerant discharge port 4c of the vortex tube 4, and the low temperature refrigerant discharge port 4c is at the vortex tube 4. A second temperature sensor 20, a pressure sensor 21 at the suction port 11 a of the accumulator 11, a pressure sensor 22 at the discharge port 2 a of the compressor 2, an indoor temperature sensor 24 near the first heat exchanger 6, and a second heat exchanger. 10 has an outdoor temperature sensor 23 in the vicinity.

  A second pressure sensor 17 and a first temperature sensor 18 are provided at the high temperature refrigerant discharge port 4b of the vortex tube 4, and a third pressure sensor 19 and a second temperature sensor 20 are provided at the low temperature refrigerant discharge port 4c of the vortex tube 4, for example, in the vicinity of the pipe P. Placed in. A pressure sensor 21 is disposed at the suction port 11a of the accumulator 11, and a pressure sensor 22 is disposed near the pipe P, for example, at the discharge port 2a of the compressor 2. The indoor temperature sensor 24 is disposed, for example, on the windward side of the second heat exchanger 10 and is disposed at a position in contact with the sucked indoor air. Similarly, the outdoor temperature sensor 24 is disposed, for example, on the windward side of the first heat exchanger 6 and is disposed at a position in contact with the sucked outdoor air.

  As shown in FIG. 3, the control unit 25 of the air conditioner 100 inputs measurement values from these various sensors 16 to 24, and the rotational speed of the compressor 2, the opening degree of the expansion valve 8, and the four-way valve 5. Switching, switching of the three-way valve 14, adjusting mechanism 4 a of the needle valve opening degree of the nozzle 4 d of the vortex tube 4, the rotational speed of the indoor fan 26, the rotational speed of the outdoor fan 27, and the high-temperature refrigerant of the vortex tube 4 The degree of opening of the flow rate adjustment valve on the discharge port 4b side is controlled.

Typically, the control unit 25 controls the direction switching of the four-way valve 5 and the direction switching of the three-way valve 14 to configure the refrigeration circuit 1 shown in FIG. 1 during the cooling operation and shown in FIG. 2 during the heating operation. A refrigeration circuit 1 is configured.
Further, the control unit 25 controls the opening degree of the needle valve of the nozzle 4 d of the vortex tube 4 and the opening degree of the flow rate adjustment valve on the high temperature refrigerant discharge port 4 b side of the vortex tube 4.

  Conventionally, the vortex tube 4 has a mechanism for performing decompression expansion in the nozzle 4d and the vortex chamber, and the amount of decompression cannot be freely adjusted. Therefore, since most of the pressure reduction amount is determined by the specifications of the nozzle structure, it is difficult to adopt this as the main pressure reduction expansion mechanism. Furthermore, when liquid or gas-liquid two-phase refrigerant is introduced into the refrigerant supply port 4a of the vortex tube 4, energy separation does not occur. Therefore, in the present invention, the refrigerant supply port 4a of the vortex tube 4 is connected to the discharge port 2a side of the compressor 2 via the oil separator 3, and high-temperature superheated gas refrigerant is introduced. At that time, the oil separator 3 separates the refrigerating machine oil from the high-temperature gas refrigerant and puts it into the refrigerant supply port 4a of the vortex tube 4 as a high-temperature gas refrigerant without oil mist. Further, the nozzle 4d of the vortex tube 4 is a variable nozzle (not shown), and the structure thereof is such that, for example, a needle valve is installed inside the nozzle, and the amount of restriction is adjusted (for example, the amount of vertical movement), thereby adjusting the nozzle amount. Adjustment of the pressure at the 4d discharge port 4e and reliable energy separation are performed. At that time, the opening degree of the flow rate adjustment valve on the high temperature refrigerant discharge port 4b side of the vortex tube 4 is linked. More specifically, the pressure is measured by the first pressure sensor 16 at the outlet of the nozzle 4d on the refrigerant supply port 4a side of the vortex tube 4, and the control unit 25 determines the flow rate on the high temperature refrigerant discharge port 4b side based on the measured value. Controls the opening of the regulating valve. Here, the opening degree of the flow rate adjusting valve is linked with the opening degree adjustment of the needle valve because the high temperature gas refrigerant temperature and pressure and the flow rate ratio (flow rate ratio: low temperature gas refrigerant discharge amount / total mass flow rate) are close to a predetermined value Alternatively, the main purpose is to converge to a predetermined range. Basically, the flow rate adjusting valve acts on the adjustment of the flow rate ratio and the temperature of each separated refrigerant, and the needle valve of the nozzle 4d adjusts the pressure of the discharge port 4e of the nozzle 4d. By linking these two valves, the discharge temperature and pressure of the high-temperature gas refrigerant and the low-temperature gas refrigerant can be converged to a predetermined (target) range, and good system efficiency can be realized.

For example, in order to lower the pressure at the discharge port 4e of the nozzle 4d with respect to the target value of the operating pressure of the refrigerant, the needle valve inside the nozzle of the vortex tube 4 is actuated in the closing direction, and the pressure at the discharge port 4e of the nozzle 4d. Adjust. When it is necessary to increase the high temperature refrigerant discharge temperature of the vortex tube 4 with respect to the target values of the operating temperature and pressure of the refrigerant, the flow rate regulating valve on the high temperature refrigerant discharge port 4b side of the vortex tube 4 is increased so that the flow rate ratio is increased. Actuate in the closing direction. By decreasing the pressure at the discharge port 4e of the nozzle 4d, the high-temperature refrigerant discharge temperature of the vortex tube 4 tends to increase, and the low-temperature refrigerant discharge temperature of the vortex tube 4 also tends to decrease. Further, when it is desired to lower the low-temperature refrigerant discharge temperature of the vortex tube 4 with respect to the target values of the operating temperature and pressure of the refrigerant, the flow rate adjustment in the direction of decreasing the flow rate ratio, that is, the high-temperature refrigerant discharge port 4b side of the vortex tube 4. Operate in the direction to open the valve.
Such operation control is performed by the control unit 25. FIG. 4 is an example of the control flow.

  The control unit 25 adjusts the opening degree of the needle valve inside the nozzle of the vortex tube 4 so that the refrigerant pressure becomes a predetermined value corresponding to the target value (step 401), and sets the pressure at the discharge port 4e of the nozzle 4d to the first value. 1 Measurement is performed by the pressure sensor 16 (step 402). Next, the control unit 25 adjusts the opening degree of the flow rate adjustment valve on the high temperature refrigerant discharge port 4b side of the vortex tube 4 so as to have a predetermined value corresponding to the target temperature and pressure of the refrigerant on the high temperature refrigerant discharge port 4b side. (Step 403) The temperature and pressure of the high-temperature gas refrigerant discharged from the high-temperature refrigerant discharge port 4b of the vortex tube 4 are measured by the first temperature sensor 18 and the second pressure sensor 17 (step 404). The control unit 25 repeats Steps 403 and 404 until the target temperature and pressure of the refrigerant on the high-temperature refrigerant discharge port 4b side are reached, and when the target temperature and pressure are reached (Step 405), the flow rate ratio is measured (Step S405). 406). Then, the control unit 25 repeats steps 401 to 406 N times until the target flow rate ratio is reached (steps 407 and 408).

The high-temperature gas refrigerant discharged from the high-temperature refrigerant discharge port 4b side of the vortex tube 4 is supplied to the first port 5a of the four-way valve 5, and the low-temperature gas refrigerant discharged from the low-temperature refrigerant discharge port 4c side of the vortex tube 4 is supplied to the three-way valve. 14 is supplied to the secondary flow path of either the first or second subcooling heat exchanger 7 or 9 through the cooling unit 14 according to the cooling operation or the heating operation, but the adjustment ratio realizes a good system efficiency. For this reason, the above-mentioned target value is determined and is different between the cooling operation and the heating operation.
The present invention is not limited to the above embodiment.

  For example, the nozzle 4d of the vortex tube 4 is not a variable nozzle as in the above embodiment, and a plurality of nozzles are installed and the number of used nozzles is controlled so as to function substantially equivalent to the above variable nozzle. Can do.

DESCRIPTION OF SYMBOLS 1 Refrigeration circuit 2 Compressor 3 Oil separator 4 Vortex tube 5 Four-way valve 6 1st heat exchanger 7 1st supercooling heat exchanger 8 Expansion valve 9 2nd supercooling heat exchanger 10 2nd heat exchanger 11 Accumulator 12 First check valve 13 Second check valve 14 Three-way valve 16 First pressure sensor 17 Second pressure sensor 18 First temperature sensor 19 Third pressure sensor 20 Second temperature sensor 21, 22 Pressure sensor 23, 24 Temperature Sensor 25 control unit

Claims (3)

During the cooling operation, the refrigerant circulates in order from the compressor, the refrigerant supply port of the vortex tube to the high temperature refrigerant discharge port, the first heat exchanger, the first subcooling heat exchanger, the expansion valve, and the second heat exchanger, and And a refrigerant circuit that sequentially circulates the refrigerant, the refrigerant supply port of the vortex tube, the low-temperature refrigerant discharge port, and the first supercooling heat exchanger,
An air conditioner for exchanging heat between the high pressure refrigerant flowing out from the first heat exchanger and the low temperature gas refrigerant flowing out from the low temperature refrigerant discharge port of the vortex tube in the first subcooling heat exchanger. . The air conditioner according to claim 1,
During the heating operation, the refrigerant passes through the compressor, the refrigerant supply port of the vortex tube to the high-temperature refrigerant discharge port, the second heat exchanger, the second subcooling heat exchanger, the expansion valve, and the first heat exchanger. Comprising a refrigeration circuit that sequentially circulates and sequentially circulates the refrigerant from the compressor, a refrigerant supply port of the vortex tube to a low-temperature refrigerant discharge port, and the second subcooling heat exchanger;
An air conditioner for exchanging heat between the high pressure refrigerant flowing out of the second heat exchanger and the low temperature gas refrigerant flowing out of the low temperature refrigerant discharge port of the vortex tube in the second subcooling heat exchanger. . The air conditioner according to claim 1 or 2,
The air conditioner further includes a first pressure sensor that measures a pressure of a refrigerant passing through an outlet of a nozzle of the vortex tube;
A second pressure sensor for measuring the pressure of the refrigerant passing through the high temperature refrigerant outlet side of the vortex tube;
A third pressure sensor for measuring the pressure on the low-temperature refrigerant outlet side of the vortex tube;
A first temperature sensor for measuring the temperature of the refrigerant passing through the high temperature refrigerant outlet side of the vortex tube;
A second temperature sensor that measures the temperature of the vortex tube on the low-temperature refrigerant outlet side;
Based on the measurement results of the first to third pressure sensors and the first and second temperature sensors, the temperature, pressure, and flow rate ratio of the refrigerant discharged from the vortex tube are set to predetermined values. An air conditioner comprising: a control unit that controls a pressure and an opening degree of the flow regulating valve.

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