Air conditioning device

Abstract

To provide an air conditioning device in which heat exchanger effectiveness in indoor heat exchangers is improved, the indoor heat exchangers can be downsized, and energy can be saved.SOLUTION: An air conditioning device comprises a first indoor heat exchanger, a second indoor heat exchanger, a connection pipe, an outdoor heat exchanger, a first pipe, a second pipe, a compressor, a four-way valve, an expansion valve, an ejector, a gas-liquid separator, and a first flow rate control valve. The connection pipe connects the first indoor heat exchanger and the second indoor heat exchanger. The ejector is provided in the second pipe between the expansion valve and the second indoor heat exchanger, and comprises a first inflow / outflow port and a second inflow / outflow port into / out of which a refrigerant flows, and an inflow port into which the refrigerant to be mixed is made to flow when the refrigerant is made to flow in from the first inflow / outflow port and flow out of the second inflow / outflow port. The gas-liquid separator is provided in the connection pipe, and provided with a first opening connected to the second indoor heat exchanger, a second opening connected to the first indoor heat exchanger, and a third opening connected to the inflow port of the ejector.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] An embodiment of the present invention relates to an air conditioning apparatus. [Background technology]

[0002] Air conditioning devices such as air conditioners regulate indoor temperatures by absorbing and releasing heat through the condensation and evaporation of refrigerant in a refrigeration cycle. During heating operation, the refrigerant evaporates in the outdoor heat exchanger (evaporator) and condenses in the indoor heat exchanger (condenser). During cooling operation, the refrigerant condenses in the outdoor heat exchanger (condenser) and evaporates in the indoor heat exchanger (evaporator). [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Japanese Patent Application Laid-Open No. 2010-32106 Summary of the Invention [Problem to be solved by the invention]

[0004] The state of the refrigerant changes within the heat exchanger. For example, in an indoor heat exchanger that functions as an evaporator during cooling operation, liquid refrigerant changes to gaseous refrigerant. In this case, as the amount of gaseous refrigerant increases inside the indoor heat exchanger, pressure loss increases. In other words, the increase in gaseous refrigerant can cause a decrease in the heat exchange rate. On the other hand, in an indoor heat exchanger that functions as a condenser during heating operation, gaseous refrigerant changes to liquid refrigerant. In this case, the liquid refrigerant inside the indoor heat exchanger does not contribute to heat exchange, so the heat exchange rate can decrease in areas where the liquid refrigerant increases. As a result, the indoor heat exchanger needs to be larger to discharge air at the desired temperature from the indoor unit, which can hinder energy conservation.

[0005] One example of a problem to be solved by the present invention is to provide an air conditioner that improves the heat exchange rate in an indoor heat exchanger, thereby enabling the indoor heat exchanger to be made smaller and more energy-efficient. [Means for solving the problem]

[0006] An air conditioning apparatus according to one embodiment of the present invention includes a first indoor heat exchanger, a second indoor heat exchanger, a connecting pipe, an outdoor heat exchanger, a first pipe, a second pipe, a compressor, a four-way valve, an expansion valve, an ejector, a gas-liquid separator, and a first flow control valve. The first indoor heat exchanger and the second indoor heat exchanger are provided in an indoor unit. A connecting pipe connects the first indoor heat exchanger and the second indoor heat exchanger. The outdoor heat exchanger is provided in an outdoor unit. The first pipe connects the first indoor heat exchanger and the outdoor heat exchanger, and a refrigerant flows through it. The second pipe connects the outdoor heat exchanger and the second indoor heat exchanger, and the refrigerant flows through it. The compressor is provided in the first pipe and has an inlet for drawing in the refrigerant and an outlet for discharging the refrigerant. A four-way valve is provided in the first pipe and is capable of changing the direction of refrigerant flow. An expansion valve is provided in the second pipe. An ejector is provided in the second pipe between the expansion valve and the second indoor heat exchanger and includes a first inlet / outlet and a second inlet / outlet through which the refrigerant flows, and an inlet through which the refrigerant flows to be mixed when the refrigerant flows in from the first inlet / outlet and flows out from the second inlet / outlet. A gas-liquid separator is provided in the connecting pipe and includes a first opening connected to the second indoor heat exchanger, a second opening connected to the first indoor heat exchanger, and a third opening connected to the inlet of the ejector. A first flow control valve is provided between the third opening and the inlet.

[0007] The air conditioning apparatus may also include, for example, a third pipe connecting the first pipe between the first indoor heat exchanger and the four-way valve and a position between the gas-liquid separator and the first indoor heat exchanger, and a second flow control valve provided on the third pipe.

[0008] According to the air conditioner described above, for example, it is possible to provide an air conditioner that improves the heat exchange rate in the indoor heat exchanger, thereby enabling the indoor heat exchanger to be made smaller and more energy-efficient. [Brief explanation of the drawings]

[0009] [Figure 1] FIG. 1 is a refrigerant system diagram of an air conditioner according to an embodiment, and is also an exemplary and schematic diagram showing the flow of refrigerant during cooling operation. [Figure 2] FIG. 2 is an exemplary schematic cross-sectional view illustrating the configuration of an ejector mounted in an indoor heat exchanger of an air conditioner according to an embodiment. [Figure 3] FIG. 3 is an exemplary schematic block diagram showing a control device for an air conditioner according to an embodiment and a configuration controlled by the control device. [Figure 4] FIG. 4 is a refrigerant system diagram of the air conditioner according to the embodiment, and is also an exemplary schematic diagram showing the flow of refrigerant during heating operation. DETAILED DESCRIPTION OF THE INVENTION

[0010] Several embodiments will be described below with reference to FIGS. 1 to 4. In this specification, components according to the embodiments and descriptions of the components may be described using multiple expressions. The components and their descriptions are merely examples and are not limited by the expressions in this specification. The components may also be identified by names different from those in this specification. Furthermore, the components may also be described using expressions different from those in this specification.

[0011] FIG. 1 is a refrigerant system diagram of an air conditioning apparatus 10 according to an embodiment, and is also an exemplary and schematic diagram showing the flow of refrigerant during cooling operation. FIG. 4 is a refrigerant system diagram of an air conditioning apparatus 10 according to an embodiment, and is also an exemplary and schematic diagram showing the flow of refrigerant during heating operation. The air conditioning apparatus 10 is, for example, a home air conditioner. However, the air conditioning apparatus 10 is not limited to this example and may be another air conditioning apparatus, such as a commercial air conditioner.

[0012] 1 and 4, an air conditioner 10 has an outdoor unit 11, an indoor unit 12, refrigerant piping 13, and a control device 14. The outdoor unit 11 is disposed outdoors, for example. The indoor unit 12 is disposed indoors, for example.

[0013] The air conditioner 10 includes a refrigeration cycle in which an outdoor unit 11 and an indoor unit 12 are connected by refrigerant piping 13. A refrigerant flows between the outdoor unit 11 and the indoor unit 12 through the refrigerant piping 13. The outdoor unit 11 and the indoor unit 12 are also electrically connected to each other by, for example, electrical wiring.

[0014] The outdoor unit 11 includes an outdoor heat exchanger 21, an outdoor blower fan 22, a compressor 23, an accumulator 24, a four-way valve 25, an expansion valve 26, and the like.

[0015] The indoor unit 12 has a first indoor heat exchanger 41A, a second indoor heat exchanger 41B, an indoor blower fan 42, an ejector 27, a gas-liquid separator 28, a first flow control valve 29, and a second flow control valve 30. Note that in Fig. 1, for the convenience of illustrating that the gas-liquid separator 28 is disposed between the first indoor heat exchanger 41A and the second indoor heat exchanger 41B, the first indoor heat exchanger 41A and the second indoor heat exchanger 41B are shown in separate positions in a separated state. In this case, the capacity (size) of the first indoor heat exchanger 41A and the capacity (size) of the second indoor heat exchanger 41B can be, for example, 1:1, and the gas-liquid separator 28 is disposed between the first indoor heat exchanger 41A and the second indoor heat exchanger 41B. Also shown is a state in which an indoor blower fan 42 is disposed for each of the first indoor heat exchanger 41A and the second indoor heat exchanger 41B. The first indoor heat exchanger 41A, the second indoor heat exchanger 41B, and the indoor blower fan 42 may be disposed as shown in Fig. 1, but as long as there is an area between the first indoor heat exchanger 41A and the second indoor heat exchanger 41B that allows connection to a first opening 28a and a second opening 28b (described below) of the gas-liquid separator 28, the first indoor heat exchanger 41A and the second indoor heat exchanger 41B may be configured to be continuous. In this case, a single indoor blower fan 42 may be configured to blow air to both the first indoor heat exchanger 41A and the second indoor heat exchanger 41B.

[0016] The refrigerant pipes 13 are pipes made of metal such as copper or aluminum, and include a first pipe 51, a second pipe 52, a third pipe 53, and so on.

[0017] The first piping 51 connects the first indoor heat exchanger 41A and the outdoor heat exchanger 21. The compressor 23, the accumulator 24, and the four-way valve 25 are provided in the first piping 51. The first piping 51 has a first region 51a, a second region 51b, a third region 51c, and a fourth region 51d. The first region 51a is a piping region that connects the four-way valve 25 and the first indoor heat exchanger 41A. The second region 51b is a piping region that connects the four-way valve 25 and the accumulator 24. The third region 51c is a piping region that connects the four-way valve 25 and the outdoor heat exchanger 21. The fourth region 51d is a piping region that connects the four-way valve 25 and the discharge port 23b of the compressor 23.

[0018] The second piping 52 connects the outdoor heat exchanger 21 and the second indoor heat exchanger 41B. The expansion valve 26 and the ejector 27 are provided in the second piping 52. The second piping 52 has a fifth region 52a, a sixth region 52b, and a seventh region 52c. The fifth region 52a is a piping region that connects the outdoor heat exchanger 21 and the expansion valve 26. The sixth region 52b is a piping region that connects the expansion valve 26 and the first inlet / outlet 71 of the ejector 27. The seventh region 52c is a piping region that connects the second inlet / outlet 72 of the ejector 27 and the second indoor heat exchanger 41B.

[0019] The third piping 53 connects the first piping 51 (first region 51a) between the first indoor heat exchanger 41A and the four-way valve 25 with a position between the gas-liquid separator 28 and the first indoor heat exchanger 41A (a position on the first indoor heat exchanger 41 side of a first connecting pipe 54 described later). In other words, the third piping 53 is a bypass piping arranged in parallel with the first indoor heat exchanger 41A. The second flow control valve 30 is provided in the third piping 53. The third piping 53 has an eighth region 53a and a ninth region 53b. The eighth region 53a is a piping region that connects the first piping 51 (first region 51a) and the second flow control valve 30. The ninth region 53b is a piping region that connects the second flow control valve 30, the gas-liquid separator 28, and the first indoor heat exchanger 41A to the first connection region 54a of the first connection pipe 54 described below.

[0020] As described above, the gas-liquid separator 28 is disposed between the first indoor heat exchanger 41A and the second indoor heat exchanger 41B. That is, the first indoor heat exchanger 41A and the second indoor heat exchanger 41B are connected by, for example, a connecting pipe, and the gas-liquid separator 28 is disposed (connected) to the connecting pipe. Specifically, the first indoor heat exchanger 41A and the second indoor heat exchanger 41B are connected by a first connecting pipe 54. The first connecting pipe 54 has a first connecting region 54a and a second connecting region 54b. The first connecting region 54a is a region that connects the second indoor heat exchanger 41B and the first opening 28a of the gas-liquid separator 28. The second connecting region 54b is a region that connects the second opening 28b of the gas-liquid separator 28 and the first indoor heat exchanger 41A.

[0021] The third opening 28c of the gas-liquid separator 28 and the inlet 73 of the ejector 27 are connected by a second connecting pipe 55. The first flow control valve 29 is provided on the second connecting pipe 55. The second connecting pipe 55 has a third connecting region 55a and a fourth connecting region 55b. The third connecting region 55a is a region that connects the third opening 28c of the gas-liquid separator 28 and the first flow control valve 29. The fourth connecting region 55b is a region that connects the first flow control valve 29 and the inlet 73 of the ejector 27.

[0022] As described above, the first connecting pipe 54 and the second connecting pipe 55 are shown in a long state for the convenience of illustrating the first indoor heat exchanger 41A and the second indoor heat exchanger 41B, but in reality, it is sufficient that there is an area between the first indoor heat exchanger 41A and the second indoor heat exchanger 41B where the first opening 28a and the second opening 28b of the gas-liquid separator 28 can be connected, and the first connecting pipe 54 may be a pipe that connects a short area (small space). Similarly, it is sufficient that the second connecting pipe 55 can connect the first flow control valve 29 and the ejector 27 to the gas-liquid separator 28, and the second connecting pipe 55 may be a pipe that connects a short area (small space).

[0023] As shown in Fig. 1, in cooling operation, the refrigerant flows from the first indoor heat exchanger 41A to the outdoor heat exchanger 21 through the first pipe 51, and flows from the outdoor heat exchanger 21 to the second indoor heat exchanger 41B through the second pipe 52. Also, as shown in Fig. 4, in heating operation, the refrigerant flows from the outdoor heat exchanger 21 to the first indoor heat exchanger 41A through the first pipe 51, further flows through the second indoor heat exchanger 41B, and flows to the outdoor heat exchanger 21 through the second pipe 52.

[0024] The outdoor heat exchanger 21 of the outdoor unit 11 acts as an evaporator to absorb heat from the refrigerant or as a condenser to release heat from the refrigerant depending on the direction of refrigerant flow. The outdoor blower fan 22 blows air to the outdoor heat exchanger 21 to promote heat exchange between the refrigerant and air in the outdoor heat exchanger 21. In other words, the outdoor blower fan 22 generates an airflow that exchanges heat with the outdoor heat exchanger 21.

[0025] Compressor 23 has suction port 23a and discharge port 23b. Compressor 23 draws in refrigerant through suction port 23a and discharges the compressed refrigerant through discharge port 23b. In this way, compressor 23 compresses the refrigerant in a refrigeration cycle and causes the refrigerant to circulate.

[0026] The accumulator 24 is connected to the suction port 23a of the compressor 23. The accumulator 24 separates the gaseous refrigerant from the liquid refrigerant. This allows the compressor 23 to draw the gaseous refrigerant that has passed through the accumulator 24 from the suction port 23a. The accumulator 24 can also function as the suction port of the compressor 23 by being configured integrally with the compressor 23.

[0027] The four-way valve 25 is connected to the outdoor heat exchanger 21, the accumulator 24 (on the side of the suction port 23a of the compressor 23), the first indoor heat exchanger 41A, and the discharge port 23b of the compressor 23. The four-way valve 25 switches the flow paths connected to the outdoor heat exchanger 21, the accumulator 24, the first indoor heat exchanger 41A, and the discharge port 23b of the compressor 23 between cooling operation and heating operation, thereby changing the direction in which the refrigerant flows.

[0028] During cooling operation, the four-way valve 25 connects the discharge port 23b of the compressor 23 to the outdoor heat exchanger 21 and supplies high-temperature, high-pressure gaseous refrigerant to the outdoor heat exchanger 21. Furthermore, during cooling operation, the four-way valve 25 connects the first indoor heat exchanger 41A to the accumulator 24 and returns the low-temperature, low-pressure gaseous refrigerant to the accumulator 24. As a result, the refrigerant compressed by the compressor 23 flows to the outdoor heat exchanger 21, and the refrigerant that has undergone heat exchange (evaporated) in the first indoor heat exchanger 41A and the second indoor heat exchanger 41B flows to the accumulator 24. During cooling operation, the second flow control valve 30 is fully closed and the refrigerant does not flow into the third pipe 53.

[0029] 4, during heating operation, the four-way valve 25 connects the discharge port 23b of the compressor 23 to the first indoor heat exchanger 41A and the second flow control valve 30, and supplies high-temperature, high-pressure gaseous refrigerant to the second indoor heat exchanger 41B via the first indoor heat exchanger 41A and the gas-liquid separator 28. During heating operation, the four-way valve 25 connects the outdoor heat exchanger 21 to the accumulator 24, and supplies low-temperature, low-pressure gaseous refrigerant to the accumulator 24. As a result, the refrigerant compressed by the compressor 23 flows to the first indoor heat exchanger 41A and the second indoor heat exchanger 41B, and the refrigerant that has undergone heat exchange (evaporated) in the outdoor heat exchanger 21 flows to the accumulator 24. As will be described later, during heating operation, the distribution ratio of the high-temperature, high-pressure gaseous refrigerant flowing to the first indoor heat exchanger 41A and the gas-liquid separator 28 (second indoor heat exchanger 41B) is determined by flow control using the second flow control valve 30.

[0030] The expansion valve 26 is, for example, an electromagnetic expansion valve. However, other types of expansion valves may be used as the expansion valve 26. The opening of the expansion valve 26 is controlled to adjust the amount of refrigerant passing through, thereby determining the amount of expansion of the refrigerant and adjusting the decrease in the refrigerant temperature.

[0031] The ejector 27 is provided in the second pipe 52. More specifically, the ejector 27 includes a first inlet / outlet 71, a second inlet / outlet 72, and an inlet 73.

[0032] During cooling operation, the refrigerant that flows out of the outdoor heat exchanger 21 and expands in the expansion valve 26 flows into the first inlet / outlet 71 as a driving flow. The gaseous refrigerant separated in the gas-liquid separator 28 flows into the inlet 73 as a suction flow via the first flow control valve 29. The second inlet / outlet 72 mixes the refrigerant supplied to the first inlet / outlet 71 (driving flow) with the refrigerant supplied to the inlet 73 (suction flow), and discharges the pressurized refrigerant toward the second indoor heat exchanger 41B.

[0033] On the other hand, during heating operation, the ejector 27 is used by flowing the refrigerant in the direction opposite to the normal use mode. In this case, the ejector 27 is used without generating the ejector effect. In this case, when the almost liquid refrigerant after heat exchange is supplied from the second indoor heat exchanger 41B to the second inlet / outlet 72, the almost liquid refrigerant is supplied directly from the first inlet / outlet 71 toward the expansion valve 26 (exterior heat exchanger 21 side).

[0034] Fig. 2 is an exemplary and schematic cross-sectional view showing the structure of the ejector 27 of this embodiment. As shown in Fig. 2, the ejector 27 has a simple structure, which makes it easy to maintain and incorporate into the air conditioning apparatus 10. The structure of the ejector 27 is not limited to the example shown in Fig. 2. The ejector 27 is provided with a first inlet / outlet 71, a second inlet / outlet 72, an inlet 73, a nozzle portion 74, a suction portion 75, a mixing portion 76, and a diffuser portion 77.

[0035] 1, the first inlet / outlet 71 is connected to the expansion valve 26 via the sixth region 52b of the second pipe 52. For example, during cooling operation, the refrigerant flows into the first inlet / outlet 71 from the outdoor heat exchanger 21 side. During heating operation, the refrigerant flows out from the first inlet / outlet 71 toward the expansion valve 26.

[0036] The second inlet / outlet 72 is connected to the second indoor heat exchanger 41B via the seventh region 52c of the second pipe 52. For example, during cooling operation, the second inlet / outlet 72 discharges pressurized gas-liquid two-phase refrigerant to the second indoor heat exchanger 41B via the sixth region 52b of the second pipe 52. During heating operation, the second inlet / outlet 72 receives the gas-liquid two-phase refrigerant from the second indoor heat exchanger 41B.

[0037] The inlet 73 is connected to the first flow control valve 29 via the fourth connection region 55b of the second connecting pipe 55. For example, during cooling operation, the gaseous refrigerant separated in the gas-liquid separator 28 flows into the inlet 73 via the first flow control valve 29. During heating operation, the first flow control valve 29 is fully closed, and therefore no refrigerant flows into the inlet 73.

[0038] As described above, during cooling operation, the ejector 27 mixes the refrigerant (driving refrigerant) supplied to the first inlet / outlet 71 with the refrigerant (suction refrigerant) supplied to the inlet / outlet 73, increases the pressure of the refrigerant, and discharges it from the second inlet / outlet 72. On the other hand, during heating operation, the ejector 27 is used in a manner opposite to the normal use in which the ejector effect is obtained. In this case, the refrigerant that flows in from the second inlet / outlet 72 is discharged from the first inlet / outlet 71 without providing the ejector effect, and is supplied to the outdoor heat exchanger 21 side via the expansion valve 26.

[0039] As shown in FIG. 2, the nozzle portion 74 is provided between the first inlet / outlet 71 and the mixing portion 76. The nozzle portion 74 is a flow path having a portion that tapers toward the mixing portion 76 and a portion that gradually widens toward the mixing portion 76. The shape of the nozzle portion 74 is not limited to this, and any structure may be used as long as it can reduce the pressure of the refrigerant that has flowed in and spray it at high speed. The nozzle portion 74 reduces the pressure of the refrigerant that has flowed into the first inlet / outlet 71, expands it, and sprays it into the mixing portion 76. Because the pressure near the outlet of the nozzle portion 74 is low, the first inlet / outlet 71 connected to the nozzle portion 74 can suck in the refrigerant.

[0040] The suction section 75 is provided between the inlet 73 and the mixing section 76. The suction section 75 is provided around the nozzle section 74 and is a substantially cylindrical flow path having a portion tapering toward the mixing section 76. The suction section 75 reduces the pressure of the refrigerant that has flowed into the inlet 73, expands it, and sprays it into the mixing section 76. Because the pressure near the outlet of the suction section 75 is low, the inlet 73 connected to the suction section 75 can draw in the refrigerant.

[0041] The mixing section 76 is provided between the nozzle section 74 and the suction section 75 and the diffuser section 77. In the mixing section 76, the ejector 27 mixes the refrigerant ejected from the suction section 75 with the refrigerant ejected from the nozzle section 74.

[0042] The diffuser section 77 is provided between the mixing section 76 and the second inlet / outlet 72. The diffuser section 77 is a flow path having a portion that expands toward the second inlet / outlet 72. The refrigerant mixed in the mixing section 76 is decelerated and pressurized in the diffuser section 77 and is released from the second inlet / outlet 72.

[0043] The ejector 27 has an ejector solenoid valve 78. The ejector solenoid valve 78 can open and close the first inlet / outlet 71. Note that FIG. 2 shows an example in which the ejector solenoid valve 78 is located outside the nozzle portion 74, but the ejector solenoid valve 78 may be provided inside the nozzle portion 74 or in another location. For example, the ejector solenoid valve 78 may be a needle-shaped valve inserted into the nozzle portion 74 to adjust its opening. By controlling the opening of the ejector solenoid valve 78, the amount of refrigerant supplied to the first inlet / outlet 71 can be adjusted, thereby controlling the ejector effect (adjusting the flow rate, pressure increase, temperature, etc.). Note that in the ejector 27, the amount of refrigerant supplied to the inlet 73 can be adjusted by the first flow control valve 29. However, the ejector solenoid valve may be provided at or inside the inlet 73, similar to the first inlet / outlet 71. In this case, the first flow control valve 29 may be omitted.

[0044] When the ejector 27 is used in reverse during heating operation, the refrigerant flowing in from the second inlet / outlet 72 is discharged from the first inlet / outlet 71 without being given the ejector effect. In other words, the ejector 27 is in an unused state.

[0045] Returning to FIG. 1, gas-liquid separator 28 is provided in first connecting pipe 54. Gas-liquid separator 28 is, for example, a surface tension gas-liquid separator. Note that gas-liquid separator 28 may be another gas-liquid separator such as a receiver tank, as long as it can separate refrigerant into gaseous and liquid states. Gas-liquid separator 28 is provided with first opening 28a (refrigerant inlet / outlet), second opening 28b (refrigerant inlet / outlet), and third opening 28c (gaseous refrigerant outlet).

[0046] During cooling operation, the first opening 28a is supplied with the gas-liquid two-phase refrigerant after heat exchange in the second indoor heat exchanger 41B via the first connection area 54a of the first connecting pipe 54. The second opening 28b supplies the liquid refrigerant separated in the gas-liquid separator 28 to the first indoor heat exchanger 41A via the second connection area 54b of the first connecting pipe 54. The third opening 28c supplies the gaseous refrigerant separated in the gas-liquid separator 28 to the first flow control valve 29 via the third connection area 55a of the second connecting pipe 55. The gaseous refrigerant whose flow rate is controlled by the first flow control valve 29 is supplied to the inlet 73 of the ejector 27 as a suction flow.

[0047] During heating operation, the first opening 28a supplies the gaseous refrigerant separated in the gas-liquid separator 28 to the second indoor heat exchanger 41B via the first connection region 54a of the first connecting pipe 54. Furthermore, the second opening 28b receives the two-phase gas-liquid refrigerant from the first indoor heat exchanger 41A and the high-temperature, high-pressure gaseous refrigerant from the compressor 23 side, which is supplied via the third piping 53, via the second connection region 54b of the first connecting pipe 54. During heating operation, the first flow control valve 29 is fully closed, and therefore no gaseous refrigerant flows out from the third opening 28c.

[0048] The first flow control valve 29 is provided on the second connecting pipe 55. During cooling operation, the first flow control valve 29 is basically controlled to be fully open, and supplies gaseous refrigerant to the inlet 27c of the ejector 27 as a suction flow. The first flow control valve 29 may also control the flow rate in order to control the ejector effect of the ejector 27. During heating operation, the first flow control valve 29 is controlled to be fully closed, and cuts off the supply of refrigerant to the inlet 27c of the ejector 27. The first flow control valve 29 may be any other type of solenoid valve or the like as long as it can adjust the flow rate.

[0049] The second flow control valve 30 is provided on the third pipe 53. During cooling operation, the second flow control valve 30 is controlled to be fully closed, blocking the flow of refrigerant to the third pipe 53. During heating operation, the second flow control valve 30 is controlled to be open, and distributes the high-temperature, high-pressure gaseous refrigerant supplied from the compressor 23 via the four-way valve 25 between the first indoor heat exchanger 41A and the second indoor heat exchanger 41B, bypassing the first indoor heat exchanger 41A via the gas-liquid separator 28. The second flow control valve 30 controls the amount of refrigerant supplied to the second indoor heat exchanger 41B, for example, so that the amount of refrigerant supplied to the first indoor heat exchanger 41A is greater than the amount supplied to the second indoor heat exchanger 41B. The second flow control valve 30 may be any other type of solenoid valve or the like as long as it can adjust the flow rate.

[0050] The control device 14 controls the outdoor blower fan 22, the indoor blower fan 42, the compressor 23, the valves, and other components provided in the outdoor unit 11 and the indoor unit 12, and performs cooling, heating, dehumidifying, and defrosting operations, as well as other operational controls. The control device 14 may be configured, for example, as an outdoor control device 14a provided in the outdoor unit 11 and an indoor control device 14b provided in the indoor unit 12. The outdoor control device 14a and the indoor control device 14b are electrically connected to each other and transmit and receive control signals to cooperate to control the outdoor unit 11 and the indoor unit 12. The indoor control device 14b provided in the indoor unit 12 may be controlled by receiving signals from a remote controller operated by the user, or by receiving signals from an information terminal such as a smartphone via a communication device. The outdoor control device 14a and the indoor control device 14b may be combined into a single control device 14. In this case, the control device 14 may be provided in either the outdoor unit 11 or the indoor unit 12, but can be provided in the indoor unit 12, for example.

[0051] The control device 14 is, for example, a computer having a control device such as a CPU (Central Processing Unit) or a microcontroller, and a storage device such as a ROM (Read Only Memory), a RAM (Random Access Memory), and a flash memory. However, the control device 14 is not limited to this example.

[0052] Fig. 3 is an exemplary schematic block diagram showing the control device 14 of the air conditioner 10 of this embodiment and the configuration controlled by the control device 14. As shown in Fig. 3, the air conditioner 10 of this embodiment has an outdoor fan drive circuit 81, an indoor fan drive circuit 82, an inverter circuit 83, a four-way valve drive circuit 84, an expansion valve drive circuit 85, a first flow control valve drive circuit 86, a second flow control valve drive circuit 87, an ejector solenoid valve drive circuit 88, and the like.

[0053] The outdoor fan drive circuit 81 is a drive circuit for the outdoor blower fan 22. The indoor fan drive circuit 82 is a drive circuit for the indoor blower fan 42. The inverter circuit 83 inverter-controls the compressor 23 to change the frequency of the compressor 23. The inverter circuit 83 is, for example, a PAM (Pulse Amplitude Modulation) type inverter circuit. However, the inverter circuit 83 is not limited to this example.

[0054] The four-way valve drive circuit 84 is a drive circuit for the four-way valve 25. The expansion valve drive circuit 85 is a drive circuit for the expansion valve 26. The first flow control valve drive circuit 86 is a drive circuit for the first flow control valve 29. The second flow control valve drive circuit 87 is a drive circuit for the second flow control valve 30. The ejector solenoid valve drive circuit 88 is a drive circuit for the ejector solenoid valve 78.

[0055] The control device 14 is connected to the temperature sensors T1 to T4, the temperature sensor Su, the outdoor fan drive circuit 81, the indoor fan drive circuit 82, the inverter circuit 83, the four-way valve drive circuit 84, the expansion valve drive circuit 85, the first flow control valve drive circuit 86, the second flow control valve drive circuit 87, and the ejector solenoid valve drive circuit 88. The control device 14 includes a temperature acquisition unit 91, an operation switching unit 92, an outdoor fan control unit 93, an indoor fan control unit 94, a compressor control unit 95, and a valve control unit 96.

[0056] The temperature acquisition unit 91 measures the temperatures of various parts in the refrigeration cycle using temperature sensors T1 to T4 and temperature sensor Su. For example, temperature sensor T1 detects the temperature (T1 value) of the refrigerant near the first indoor heat exchanger 41A between the first indoor heat exchanger 41A and the four-way valve 25. Temperature sensor T2 detects the temperature (T2 value) of the refrigerant near the first indoor heat exchanger 41A between the first indoor heat exchanger 41A and the gas-liquid separator 28. Temperature sensor T3 detects the temperature (T3 value) of the refrigerant near the second indoor heat exchanger 41B between the second indoor heat exchanger 41B and the gas-liquid separator 28. Temperature sensor T4 detects the temperature (T4 value) of the refrigerant near the second indoor heat exchanger 41B between the second indoor heat exchanger 41B and the ejector 27. Temperature sensor Su detects the temperature (Su value) of the refrigerant at the refrigerant inlet of the accumulator. The temperature sensors are not limited to the above-mentioned temperature sensors T1 to T4 and temperature sensor Su, but may be provided in various locations in the outdoor unit 11 and the indoor unit 12, and the detection results may be used to control the air conditioner .

[0057] The operation switching unit 92 switches the air conditioner 10 between cooling operation, heating operation, dehumidifying operation, defrosting operation, and other operations.

[0058] The outdoor fan control unit 93 controls the outdoor blower fan 22. For example, the outdoor fan control unit 93 controls the outdoor fan drive circuit 81 to control the rotation speed of the motor of the outdoor blower fan 22.

[0059] The indoor fan control unit 94 controls the indoor blower fan 42. For example, the indoor fan control unit 94 controls the indoor fan drive circuit 82 to control the rotation speed of the motor of the indoor blower fan 42.

[0060] The compressor control unit 95 controls the compressor 23. For example, the compressor control unit 95 controls the inverter circuit 83 to control the frequency (operating frequency) of the compressor 23 through inverter control.

[0061] The valve control unit 96 controls the four-way valve 25, the expansion valve 26, the first flow control valve 29, the second flow control valve 30, and the ejector solenoid valve 78. The valve control unit 96 controls the four-way valve drive circuit 84 to drive the actuator of the four-way valve 25 and change the direction of refrigerant flow in the four-way valve 25. The valve control unit 96 controls the expansion valve drive circuit 85 to drive the actuator of the expansion valve 26 and control the amount of refrigerant flowing (expansion amount) in the expansion valve 26. The valve control unit 96 controls the first flow control valve drive circuit 86, the second flow control valve drive circuit 87, and the ejector solenoid valve drive circuit 88 to change the opening degrees of the first flow control valve 29, the second flow control valve 30, and the ejector solenoid valve 78, and adjust the flow rate of the medium.

[0062] The cooling operation and heating operation of the air conditioner 10 of this embodiment configured as described above will be described. Note that the air conditioner 10 is not limited to the cooling operation and heating operation, and can also perform other operations such as a dehumidifying operation, a defrosting operation, and a sterilizing operation.

[0063] First, the cooling operation will be described based on the medium flow pattern shown in Fig. 1. For example, when the air conditioning apparatus 10 starts up and the cooling operation starts simultaneously, the outdoor blower fan 22, the compressor 23, and the indoor blower fan 42 are stopped. In this case, the outdoor fan control unit 93, the indoor fan control unit 94, and the compressor control unit 95 start the outdoor blower fan 22, the compressor 23, and the indoor blower fan 42 when the cooling operation starts.

[0064] During cooling operation, the outdoor fan control unit 93 adjusts the rotation speed of the outdoor blower fan 22. The indoor fan control unit 94 adjusts the rotation speed of the indoor blower fan 42. For example, the indoor fan control unit 94 controls the indoor blower fan 42 between weak wind (low speed) operation and strong wind (high speed) operation in accordance with the temperature of the room where the indoor unit 12 is installed or a signal input from a remote controller. The compressor control unit 95 adjusts the frequency of the compressor 23.

[0065] When the cooling operation is started, the valve control unit 96 controls the four-way valve drive circuit 84 to change the direction of refrigerant flow in the four-way valve 25 for cooling. The valve control unit 96 also controls the expansion valve drive circuit 85, the first flow control valve drive circuit 86, and the second flow control valve drive circuit 87 to change the open / close valve states of the expansion valve 26, the first flow control valve 29, and the second flow control valve 30 for cooling.

[0066] Specifically, the four-way valve 25 connects the fourth region 51d and the third region 51c of the first pipe 51, and connects the discharge port 23b of the compressor 23 and the outdoor heat exchanger 21. As a result, the high-pressure, high-temperature gaseous refrigerant discharged from the compressor 23 is supplied to the outdoor heat exchanger 21. The outdoor heat exchanger 21 functions as a condenser and performs heat exchange of the refrigerant. As a result of the heat exchange in the outdoor heat exchanger 21, the refrigerant changes to a medium-temperature, high-pressure liquid state and flows to the expansion valve 26.

[0067] The expansion valve 26 reduces the temperature of the medium-temperature, high-pressure liquid refrigerant by controlling the throttle of the valve, thereby expanding the refrigerant. The refrigerant that has changed into a low-temperature, low-pressure liquid state is then supplied to the first inlet / outlet 71 of the ejector 27.

[0068] The liquid refrigerant supplied to the ejector 27 is mixed with the gaseous refrigerant supplied to the inlet 27c, and is supplied to the second indoor heat exchanger 41B from the second inlet / outlet 72 in a gas-liquid two-phase state pressurized by the ejector effect.

[0069] The two-phase gas-liquid refrigerant pressurized by the ejector 27 is supplied to the second indoor heat exchanger 41B and exchanges heat with the indoor air, and the cooled air is released into the room. Note that while the second indoor heat exchanger 41B is supplied with two-phase gas-liquid refrigerant and the proportion of gaseous refrigerant increases due to heat exchange, the refrigerant is pressurized by the ejector 27 and its flow rate is increased, so that a decrease in heat exchange efficiency due to the presence of gaseous refrigerant can be alleviated. In other words, during cooling operation, the efficiency of the first half of the heat exchange performed in the second indoor heat exchanger 41B can be improved.

[0070] As a result of heat exchange in the second indoor heat exchanger 41B, the gas-liquid two-phase refrigerant, with the proportion of gas increased as a result, is supplied from the first opening 28a to the gas-liquid separator 28, where it is separated into gaseous refrigerant and liquid refrigerant. The separated gaseous refrigerant is then supplied from the third opening 28c to the first flow control valve 29 as a suction flow of the ejector 27.

[0071] Meanwhile, the separated liquid refrigerant is supplied to the first indoor heat exchanger 41A from the second opening 28b via the second connection region 54b of the first connecting pipe 54. In the case of a conventional indoor heat exchanger that does not include the ejector 27 and the gas-liquid separator 28, the proportion of gas in the refrigerant increases from the moment it flows into the indoor heat exchanger and heat exchange begins, resulting in increased pressure loss. As a result, this can cause a gradual decrease in heat exchange efficiency in the indoor heat exchanger, starting from the refrigerant inlet side of the indoor heat exchanger. On the other hand, the air conditioning apparatus 10 of this embodiment is equipped with the ejector 27 and the gas-liquid separator 28, and the gas-liquid separator 28 is disposed between the first indoor heat exchanger 41A and the second indoor heat exchanger 41B. As a result, only liquid refrigerant can be supplied to the first indoor heat exchanger 41A, which is responsible for the latter half of the heat exchange during cooling operation. That is, during cooling operation, the gaseous refrigerant generated by heat exchange in the second indoor heat exchanger 41B and the gaseous refrigerant supplied to the ejector 27 as a suction flow can be prevented from being supplied to the first indoor heat exchanger 41A. As a result, the amount of gaseous refrigerant in the first indoor heat exchanger 41A can be reduced, the occurrence of pressure loss can be alleviated, and heat exchange efficiency can be improved. Furthermore, the ejector 27 uses the gaseous refrigerant separated in the gas-liquid separator 28 as a suction flow to pressurize the refrigerant supplied to the second indoor heat exchanger 41B and the first indoor heat exchanger 41A. As a result, the flow velocity of the refrigerant flowing through the second indoor heat exchanger 41B and the first indoor heat exchanger 41A increases. Furthermore, the gaseous refrigerant generated as a result of the second indoor heat exchanger 41B and the first indoor heat exchanger 41A functioning as evaporators can be smoothly discharged downstream. In this respect as well, it is possible to reduce pressure losses in the second indoor heat exchanger 41B and the first indoor heat exchanger 41A and improve heat exchange efficiency.

[0072] The refrigerant that has been gasified through heat exchange in the first indoor heat exchanger 41A returns to the compressor 23 via the four-way valve 25 and the accumulator 24. As described above, the refrigerant supplied to the second indoor heat exchanger 41B and the first indoor heat exchanger 41A is pressurized by the ejector 27. That is, the pressure of the refrigerant returned to the compressor 23 is higher than in a configuration without the ejector 27. As a result, the air conditioner 10 of this embodiment can reduce the workload in the compressor 23 to bring the refrigerant into a high-pressure, high-temperature state to be supplied to the outdoor heat exchanger 21, compared to an air conditioner configuration without the ejector 27. That is, this can contribute to energy savings during cooling operation.

[0073] As described above, the air conditioner 10 of this embodiment, which controls the circulation of refrigerant during cooling operation, is equipped with an ejector 27 and a gas-liquid separator 28 in the indoor unit 12. The indoor heat exchanger is divided into a first indoor heat exchanger 41A and a second indoor heat exchanger 41B, and the gas-liquid separator 28 is disposed between the first indoor heat exchanger 41A and the second indoor heat exchanger 41B. This configuration reduces pressure loss in the first indoor heat exchanger 41A and the second indoor heat exchanger 41B during cooling operation, improves the heat exchange efficiency of the refrigerant, and contributes to improving the cooling capacity while preventing the indoor unit 12 from becoming larger. In addition, because the pressure of the refrigerant returned to the compressor 23 can be increased by the ejector 27, the workload of the compressor 23 can be reduced, contributing to energy savings during cooling operation of the air conditioner 10.

[0074] Next, heating operation will be described based on the medium flow pattern shown in Fig. 4. In the case of heating operation, for example, if the air conditioner 10 starts up and the heating operation begins simultaneously, the outdoor blower fan 22, the compressor 23, and the indoor blower fan 42 are stopped. In this case, the outdoor fan control unit 93, the indoor fan control unit 94, and the compressor control unit 95 start the outdoor blower fan 22, the compressor 23, and the indoor blower fan 42 when the heating operation begins.

[0075] During heating operation, the outdoor fan control unit 93 adjusts the rotation speed of the outdoor blower fan 22. The indoor fan control unit 94 adjusts the rotation speed of the indoor blower fan 42. For example, the indoor fan control unit 94 controls the indoor blower fan 42 between weak wind (low speed) operation and strong wind (high speed) operation in accordance with the air temperature in the room where the indoor unit 12 is installed or a signal input from a remote controller. The compressor control unit 95 adjusts the frequency of the compressor 23.

[0076] When the heating operation is started, the valve control unit 96 controls the four-way valve drive circuit 84 to change the direction of refrigerant flow in the four-way valve 25 for heating. The valve control unit 96 also controls the expansion valve drive circuit 85, the first flow control valve drive circuit 86, and the second flow control valve drive circuit 87 to change the open / close valve states of the expansion valve 26, the first flow control valve 29, and the second flow control valve 30 for heating.

[0077] Specifically, the four-way valve 25 connects the fourth region 51d of the first pipe 51 to the first region 51a, and connects the discharge port 23b of the compressor 23 to the first indoor heat exchanger 41A and the eighth region 53a of the third pipe 53. At this time, the second flow control valve drive circuit 87 controls the opening of the second flow control valve 30 and determines the distribution amount of high-pressure, high-temperature gaseous refrigerant to be flowed to the first indoor heat exchanger 41A side and the third pipe 53 side. In this case, the second flow control valve drive circuit 87 controls the second flow control valve 30 based on the detection values (T1 value to T4 value) of the temperature sensors T1 to T4. Specifically, the control is based on the subcooling SC1 (= T1 value - T2 value) in the first indoor heat exchanger 41A and the subcooling SC2 (= T3 value - T4 value) in the second indoor heat exchanger 41B. In this case, for example, more refrigerant is made to flow to the first indoor heat exchanger 41A side to which high-temperature, high-pressure gaseous refrigerant is supplied directly from the compressor 23. As a result, heat exchange in the first indoor heat exchanger 41A is more efficient than in the second indoor heat exchanger 41B to which the refrigerant after heat exchange in the first indoor heat exchanger 41A is mixed and supplied, enabling an efficient supply of hot air to the room.

[0078] Meanwhile, a portion of the high-temperature, high-pressure gaseous refrigerant discharged from the compressor 23 passes through the third pipe 53 and is supplied to the first connecting pipe 54, where it is mixed with the liquid refrigerant that has undergone heat exchange in the first indoor heat exchanger 41A, and is supplied to the gas-liquid separator 28 from the second opening 28b.

[0079] The gaseous refrigerant separated by the gas-liquid separator 28 is then supplied through the first opening 28a to the second indoor heat exchanger 41B, which functions as a second condenser during heating operation. In this case, a refrigerant mixed with high-temperature, high-pressure gaseous refrigerant from the compressor 23 is supplied to the second indoor heat exchanger 41B. In other words, a refrigerant with a higher temperature and flow rate is supplied to the second indoor heat exchanger 41B than in a case where the third piping 53 is not present and high-temperature, high-pressure gaseous refrigerant is not bypassed through the third piping 53. As a result, pressure loss is reduced and heat exchange efficiency is improved compared to a structure in which the first indoor heat exchanger 41A and the second indoor heat exchanger 41B are not separated and high-temperature, high-pressure refrigerant is not bypassed. In other words, efficient heat exchange is also possible in the second indoor heat exchanger 41B, which is responsible for the second half of heat exchange, allowing for efficient supply of warm air to the room. In this way, by supplying high-temperature, high-pressure gaseous refrigerant to the second indoor heat exchanger 41B via a bypass using the third pipe 53, it is no longer necessary to improve the flow rate by, for example, reducing the diameter of the pipes inside the indoor heat exchanger, as was done in the past. As a result, it is possible to simplify the structure of the indoor heat exchanger as a whole, reduce manufacturing costs, and reduce the occurrence of problems such as clogging of the paths (pipes) inside the heat exchanger.

[0080] The refrigerant that has undergone heat exchange in the second indoor heat exchanger 41B is supplied to the ejector 27 from the second inlet / outlet 72. In this case, the ejector 27 is used in a manner opposite to its normal use. Furthermore, because the first flow control valve 29 is controlled to a fully closed state, the gaseous refrigerant separated in the gas-liquid separator 28 is not supplied to the inlet 27c of the ejector 27. The ejector 27 discharges the refrigerant from the first inlet / outlet 71 toward the expansion valve 26 without exerting an ejector effect on the passing refrigerant. The liquid refrigerant that has been converted to a low-temperature, low-pressure state by the expansion valve 26 is supplied to the outdoor heat exchanger 21, where it is converted to a gaseous state through heat exchange and then discharged. The refrigerant discharged from the outdoor heat exchanger 21 is returned to the compressor 23 via the four-way valve 25 and the accumulator 24. There, it is converted back to a high-temperature, high-pressure state.

[0081] In this manner, the air conditioner 10 of this embodiment, which controls refrigerant circulation during heating operation, uses the third piping 53 to supply high-temperature, high-pressure gaseous refrigerant from the compressor 23 to the first indoor heat exchanger 41A, which handles the first half of heat exchange, and the second indoor heat exchanger 41B, which handles the second half of heat exchange. This configuration increases the refrigerant flow rate in the second indoor heat exchanger 41B, reducing the accumulation of liquid refrigerant in the second indoor heat exchanger 41B, which functions as a condenser downstream of the first indoor heat exchanger 41A during heating operation, thereby contributing to improved heat exchange efficiency. As a result, warm air can be supplied to the room more efficiently than in a configuration in which high-pressure, high-temperature refrigerant is not supplied from the compressor 23 between the first indoor heat exchanger 41A and the second indoor heat exchanger 41B via the third piping 53. Furthermore, efficient warm air supply contributes to energy savings during heating operation of the air conditioner 10.

[0082] The air conditioning apparatus 10 according to the embodiment described above includes a first indoor heat exchanger 41A, a second indoor heat exchanger 41B, an outdoor heat exchanger 21, a first pipe 51, a second pipe 52, a compressor 23, a four-way valve 25, an expansion valve 26, an ejector 27, a gas-liquid separator 28, and a first flow control valve 29. The first indoor heat exchanger 41A and the second indoor heat exchanger 41B are provided in the indoor unit 12. The outdoor heat exchanger 21 is provided in the outdoor unit 11. The first pipe 51 connects the first indoor heat exchanger 41A and the outdoor heat exchanger 21, and a refrigerant flows through it. The second pipe 52 connects the outdoor heat exchanger 21 and the second indoor heat exchanger 41B, and a refrigerant flows through it. The compressor 23 is provided in the first pipe 51 and has an inlet 23a that draws in a refrigerant and an outlet 23b that discharges the refrigerant. The four-way valve 25 is provided in the first pipe 51 and is capable of changing the direction in which the refrigerant flows. The expansion valve 26 is provided in the second pipe 52. The ejector 27 is provided between the expansion valve 26 of the second pipe 52 and the second indoor heat exchanger 41B and has a first inlet / outlet 71 and a second inlet / outlet 72 through which the refrigerant flows in and out, and an inlet 73 through which a refrigerant to be mixed flows in when the refrigerant flows in from the first inlet / outlet 71 and flows out from the second inlet / outlet 72. The gas-liquid separator 28 is provided between the first indoor heat exchanger 41A and the second indoor heat exchanger 41B, and is provided with a first opening 28a connected to the second indoor heat exchanger 41B, a second opening 28b connected to the first indoor heat exchanger 41A, and a third opening 28c connected to the inlet 73 of the ejector 27. The first flow control valve 29 is provided between the third opening 28c and the inlet 73. This configuration provides an air conditioner that can, for example, increase the flow rate of the refrigerant in the first indoor heat exchanger 41A and the second indoor heat exchanger 41B, improve the heat exchange rate, and enable the indoor unit 12 (the first indoor heat exchanger 41A and the second indoor heat exchanger 41B) to be made smaller and more energy-efficient. Furthermore, the first indoor heat exchanger 41A and the second indoor heat exchanger 41B can be made smaller, which can contribute to reducing (cutting) the total amount of circulating refrigerant.

[0083] The air conditioner 10 may also include, for example, a first pipe 51 between the first indoor heat exchanger 41A and the four-way valve 25, a third pipe 53 connecting a position between the gas-liquid separator 28 and the first indoor heat exchanger 41A, and a second flow control valve 30 provided on the third pipe 53. This configuration, for example, can increase the flow rate of the refrigerant in the second indoor heat exchanger 41B during heating operation, contributing to improving the heat exchange efficiency of the second indoor heat exchanger 41B, which functions as a condenser downstream of the first indoor heat exchanger 41A. As a result, the efficiency of supplying warm air to the room can be improved, contributing to energy savings during heating operation of the air conditioner 10.

[0084] Although several embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be embodied in various other forms, and various omissions, substitutions, and modifications can be made without departing from the spirit of the invention. These embodiments and their modifications are included within the scope and spirit of the invention, and are also included in the scope of the invention and its equivalents as defined in the claims. [Explanation of symbols]

[0085] 10...air conditioning device, 11...outdoor unit, 12...indoor unit, 13...refrigerant piping, 14...control device, 21...outdoor heat exchanger, 22...outdoor blower fan, 23...compressor, 24...accumulator, 25...four-way valve, 26...expansion valve, 27...ejector, 28...gas-liquid separator, 29...first flow control valve, 30...second flow control valve, 41A...first indoor heat exchanger, 41B...second indoor heat exchanger, 42...indoor blower fan, 51...first piping, 52...second piping, 53...third piping.

Claims

1. a first indoor heat exchanger provided in the indoor unit; a second indoor heat exchanger provided in the indoor unit; a connecting pipe connecting the first indoor heat exchanger and the second indoor heat exchanger; an outdoor heat exchanger provided in the outdoor unit; a first pipe connecting the first indoor heat exchanger and the outdoor heat exchanger and through which a refrigerant flows; a second pipe connecting the outdoor heat exchanger and the second indoor heat exchanger and through which the refrigerant flows; a compressor provided in the first pipe, the compressor having a suction port for drawing in the refrigerant and a discharge port for discharging the refrigerant; a four-way valve provided in the first pipe and capable of changing the direction in which the refrigerant flows; an expansion valve provided in the second pipe; an ejector provided on the second pipe between the expansion valve and the second indoor heat exchanger, the ejector including a first inlet / outlet and a second inlet / outlet through which the refrigerant flows, and an inlet through which the refrigerant flows to be mixed when the refrigerant flows in from the first inlet / outlet and flows out from the second inlet / outlet; a gas-liquid separator that is provided in the connecting pipe and has a first opening connected to the second indoor heat exchanger, a second opening connected to the first indoor heat exchanger, and a third opening connected to the inlet of the ejector; a first flow control valve provided between the third opening and the inlet; An air conditioning device comprising:

2. a third pipe connecting the first pipe between the first indoor heat exchanger and the four-way valve and a position between the gas-liquid separator and the first indoor heat exchanger; a second flow control valve provided in the third pipe; The air conditioning apparatus according to claim 1 .

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