JP6620824B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner, in particular, an outdoor unit having a compressor and an outdoor heat exchanger, a plurality of indoor units having an indoor heat exchanger, and a liquid refrigerant communication pipe connecting the outdoor unit and the plurality of indoor units. And an outdoor liquid refrigerant pipe connecting the liquid side end of the outdoor heat exchanger and the liquid refrigerant communication pipe so that the refrigerant flowing through the liquid refrigerant communication pipe is in a gas-liquid two-phase state. The present invention relates to an air conditioner provided with a hydraulic pressure adjusting expansion valve for reducing pressure.

  Conventionally, it has an outdoor unit having a compressor and an outdoor heat exchanger, a plurality of indoor units having an indoor heat exchanger, and a liquid refrigerant communication pipe connecting the outdoor unit and the plurality of indoor units. There is an air conditioner that performs an operation in which the refrigerant discharged from the compressor flows in the order of the outdoor heat exchanger, the liquid refrigerant communication tube, and the indoor heat exchanger. As such an air conditioner, as shown in Patent Document 1 (International Publication No. 2015/029160), a liquid refrigerant communication pipe is connected to an outdoor liquid refrigerant pipe connecting an outdoor heat exchanger and a liquid refrigerant communication pipe. Some have a hydraulic pressure adjusting expansion valve that depressurizes the refrigerant so that the refrigerant flowing in the gas-liquid two-phase state. That is, in this air conditioner, when performing an operation of flowing the refrigerant discharged from the compressor in the order of the outdoor heat exchanger, the liquid refrigerant communication tube, and the indoor heat exchanger, the gas-liquid is reduced by the pressure reduction in the hydraulic pressure adjusting expansion valve. The two-phase refrigerant is sent from the outdoor unit side to the indoor unit side by flowing the two-phase refrigerant through the liquid refrigerant communication tube, so that two-phase conveyance is performed.

  In the air conditioner of Patent Document 1, when the discharge temperature of the compressor is excessively increased, for example, the opening degree of the indoor expansion valve provided in each indoor unit is set for protection control to decrease the discharge temperature. It is conceivable to perform control to increase temporarily.

  However, in such control, the state of the refrigerant flowing through the liquid refrigerant communication tube fluctuates, and a desired gas-liquid two-phase state cannot be obtained, which hinders the two-phase conveyance of the refrigerant by the hydraulic pressure adjusting expansion valve. There is a fear.

  An object of the present invention is to include an outdoor unit having a compressor and an outdoor heat exchanger, a plurality of indoor units having an indoor heat exchanger, and a liquid refrigerant communication pipe connecting the two units. The outdoor liquid refrigerant pipe connecting the liquid side end of the heat exchanger and the liquid refrigerant communication pipe is provided with a liquid pressure adjusting expansion valve that depressurizes the refrigerant so that the refrigerant flowing through the liquid refrigerant communication pipe is in a gas-liquid two-phase state. Another object of the present invention is to satisfactorily carry out the two-phase refrigerant transport while suppressing an increase in the discharge temperature of the compressor.

An air conditioner according to a first aspect includes an outdoor unit having a compressor and an outdoor heat exchanger, a plurality of indoor units having an indoor heat exchanger, and a liquid refrigerant communication connecting the outdoor unit and the plurality of indoor units. And an air conditioner that performs an operation of flowing the refrigerant discharged from the compressor in the order of the outdoor heat exchanger, the liquid refrigerant communication tube, and the indoor heat exchanger. And here, the liquid pressure adjustment for reducing the pressure of the refrigerant flowing through the liquid refrigerant communication tube to the gas-liquid two-phase state to the outdoor liquid refrigerant tube connecting the liquid side end of the outdoor heat exchanger and the liquid refrigerant communication tube An expansion valve is provided. In addition, here, an indoor expansion valve that further depressurizes the refrigerant in the gas-liquid two-phase state flowing through the liquid refrigerant communication tube is provided corresponding to each of the plurality of indoor units, and the liquid pressure adjusting expansion valve of the outdoor liquid refrigerant tube is provided. In addition, a liquid injection pipe that branches a part of the refrigerant flowing through the outdoor liquid refrigerant pipe and sends it to the compressor without passing through the heat exchanger is connected to the part closer to the outdoor heat exchanger.

Here, in the configuration for performing the two-phase conveyance of the refrigerant that flows the refrigerant in the gas-liquid two-phase state through the liquid refrigerant communication tube by the above-described hydraulic pressure adjusting expansion valve and sends the refrigerant from the outdoor unit side to the indoor unit side, as described above, A liquid injection pipe that branches a part of the refrigerant flowing through the outdoor liquid refrigerant pipe to the part closer to the outdoor heat exchanger than the liquid pressure adjusting expansion valve in the outdoor liquid refrigerant pipe and sends it to the compressor without passing through the heat exchanger. Furthermore, it is provided. By providing such a liquid injection pipe, it is possible to send the refrigerant to the compressor while suppressing fluctuations in the temperature of the refrigerant flowing through the outdoor liquid refrigerant pipe, so that after the pressure is reduced by the liquid pressure adjusting expansion valve, While preventing the state of the refrigerant flowing through the liquid refrigerant communication tube from fluctuating, an increase in the discharge temperature of the compressor can be suppressed. As described above, the refrigerant flowing through the liquid refrigerant communication tube can be reliably maintained in a desired gas-liquid two-phase state while suppressing an increase in the discharge temperature of the compressor.

  That is, here, in the configuration having the hydraulic pressure adjusting expansion valve, the two-phase conveyance of the refrigerant can be performed satisfactorily while suppressing the rise in the discharge temperature of the compressor by providing the liquid injection pipe.

  An air conditioner according to a second aspect is the air conditioner according to the first aspect, wherein a liquid injection pipe is connected to a suction refrigerant pipe through which a refrigerant sucked into the compressor flows.

  Here, as described above, since the refrigerant branched from the outdoor liquid refrigerant pipe can be sent to the suction side of the compressor, the temperature of the refrigerant sucked into the compressor can be lowered.

  An air conditioner according to a third aspect is the air conditioner according to the second aspect, wherein the suction refrigerant pipe is provided with an accumulator for temporarily storing the refrigerant, and the suction refrigerant pipe has a portion on the outlet side of the accumulator. A liquid injection tube is connected.

  Here, as described above, since the liquid injection pipe is connected to the outlet side of the accumulator, the refrigerant flowing through the liquid injection pipe can be merged with the refrigerant sucked into the compressor without passing through the accumulator. Compared to the case where the liquid injection pipe is connected to the inlet side of the accumulator, the effect of lowering the temperature of the refrigerant sucked into the compressor can be improved.

An air conditioner according to a fourth aspect is the air conditioner according to the second aspect, wherein the suction refrigerant pipe is provided with an accumulator for temporarily storing the refrigerant, the liquid injection pipe is branched into two, and the suction refrigerant pipe Among these, a liquid injection pipe is connected to both the inlet side portion of the accumulator and the outlet side portion of the accumulator.

  Here, as described above, since the liquid injection pipe is connected to both the inlet side and the outlet side of the accumulator, when it is desired to improve the effect of reducing the temperature of the refrigerant sucked into the compressor, When the refrigerant flowing through the injection pipe is sent to the outlet side of the accumulator and the liquid is discharged so that the pressure of the refrigerant discharged from the compressor does not exceed the predetermined discharge pressure threshold, the refrigerant flowing through the liquid injection pipe is discharged from the accumulator. Can be sent to the entrance side.

  An air conditioner according to a fifth aspect is the air conditioner according to the first aspect, wherein a liquid injection pipe is connected to an intermediate part of the compression stroke of the compressor.

  Here, as described above, since the refrigerant branched from the outdoor liquid refrigerant pipe can be sent to the middle part of the compression stroke of the compressor, the temperature of the refrigerant compressed to the intermediate pressure in the compressor can be lowered. .

  An air conditioner according to a sixth aspect is the air conditioner according to the fifth aspect, wherein an accumulator for temporarily storing the refrigerant is provided in an intake refrigerant pipe through which the refrigerant sucked into the compressor flows, and a liquid injection pipe is provided. The liquid injection pipe is connected to both the inlet side portion of the accumulator and the middle portion of the compression stroke of the compressor.

  Here, as described above, since the liquid injection pipe is connected to both the inlet side of the accumulator and the middle part of the compression stroke of the compressor, it is desired to lower the temperature of the refrigerant compressed to the intermediate pressure in the compressor. In this case, when the refrigerant flowing through the liquid injection pipe is sent to the middle part of the compression stroke of the compressor and the pressure of the refrigerant discharged from the compressor is to be discharged so as not to exceed a predetermined discharge pressure threshold, The refrigerant flowing through the liquid injection tube can be sent to the inlet side of the accumulator.

  An air conditioner according to a seventh aspect is the air conditioner according to the first aspect, wherein a refrigerant return pipe for branching a part of the refrigerant flowing through the outdoor liquid refrigerant pipe and sending it to the compressor is branched to the outdoor liquid refrigerant pipe. A refrigerant cooler is provided that connects and cools the refrigerant that flows through the portion of the outdoor liquid refrigerant pipe that is closer to the outdoor heat exchanger than the liquid pressure adjusting expansion valve, by the refrigerant that flows through the refrigerant return pipe.

  Here, in the configuration for performing the two-phase conveyance of the refrigerant that flows the refrigerant in the gas-liquid two-phase state through the liquid refrigerant communication tube by the above-described hydraulic pressure adjusting expansion valve and sends the refrigerant from the outdoor unit side to the indoor unit side, as described above, The refrigerant return pipe and the refrigerant cooler that cools the refrigerant flowing in the outdoor heat exchanger side of the outdoor liquid refrigerant pipe with respect to the liquid pressure adjusting expansion valve by the refrigerant flowing through the refrigerant return pipe are further provided.

  Here, assuming that such a refrigerant return pipe and a refrigerant cooler are provided without providing the liquid injection pipe, the refrigerant flowing through the refrigerant return pipe is cooled after the refrigerant flowing through the refrigerant cooler is cooled. Therefore, an increase in the discharge temperature of the compressor can be suppressed. However, since the refrigerant flowing through the refrigerant return pipe is sent to the compressor after cooling the refrigerant flowing through the outdoor liquid refrigerant pipe in the refrigerant cooler, the temperature of the refrigerant flowing through the outdoor liquid refrigerant pipe after passing through the refrigerant cooler is As a result, the state of the refrigerant flowing through the liquid refrigerant communication pipe after being depressurized by the liquid pressure adjusting expansion valve also fluctuates. For example, if the flow rate of the refrigerant flowing through the refrigerant return pipe increases too much, the rise in the discharge temperature of the compressor can be suppressed to some extent, but the temperature of the refrigerant flowing through the outdoor liquid refrigerant pipe after passing through the refrigerant cooler decreases. As a result, the refrigerant flowing through the liquid refrigerant communication tube after being depressurized by the liquid pressure adjusting expansion valve becomes a gas-liquid two-phase state with a large amount of liquid components.

  That is, in a configuration having a hydraulic pressure adjusting expansion valve, it may not be possible to maintain a desired gas-liquid two-phase state simply by providing a refrigerant return pipe and a refrigerant cooler. It is difficult to satisfactorily carry out the two-phase conveyance of the refrigerant while suppressing the above.

  Therefore, here, not only the refrigerant return pipe and the refrigerant cooler, but also the liquid injection pipe is provided. Providing such a liquid injection pipe allows the refrigerant to be sent to the compressor while suppressing fluctuations in the temperature of the refrigerant flowing through the outdoor liquid refrigerant pipe, so that it is not necessary to increase the flow rate of the refrigerant flowing through the refrigerant return pipe. The rise in the discharge temperature of the compressor can be suppressed. If the flow rate of the refrigerant flowing through the refrigerant return pipe is not large, the temperature of the refrigerant flowing through the outdoor liquid refrigerant pipe after passing through the refrigerant cooler will not be excessively lowered. The refrigerant flowing through the liquid refrigerant communication tube after being decompressed does not enter a gas-liquid two-phase state with a large amount of liquid components. As described above, the refrigerant flowing through the liquid refrigerant communication tube can be maintained in a desired gas-liquid two-phase state while suppressing an increase in the discharge temperature of the compressor.

  That is, in this case, in the configuration having the hydraulic pressure adjusting expansion valve, by providing the liquid injection pipe together with the refrigerant return pipe and the refrigerant cooler, it is possible to suppress the increase of the discharge temperature of the compressor while suppressing the increase of the refrigerant discharge temperature. Phase conveyance can be performed satisfactorily.

  An air conditioner according to an eighth aspect is the air conditioner according to the seventh aspect, wherein a liquid injection pipe and / or a refrigerant return pipe are connected to a suction refrigerant pipe through which a refrigerant sucked into the compressor flows. .

  Here, as described above, since the refrigerant branched from the outdoor liquid refrigerant pipe can be sent to the suction side of the compressor, the temperature of the refrigerant sucked into the compressor can be lowered.

  An air conditioner according to a ninth aspect is the air conditioner according to the eighth aspect, wherein the suction refrigerant pipe is provided with an accumulator that temporarily stores the refrigerant, and the suction refrigerant pipe has a portion on the outlet side of the accumulator, A liquid injection pipe and / or a refrigerant return pipe are connected.

  Here, as described above, the liquid injection pipe and / or the refrigerant return pipe are connected to the outlet side of the accumulator, so that the refrigerant flowing through the liquid injection pipe and / or the refrigerant return pipe without passing through the accumulator is supplied to the compressor. Since it can be merged with the sucked refrigerant, the effect of lowering the temperature of the refrigerant sucked into the compressor is improved as compared with the case where the liquid injection pipe and / or the refrigerant return pipe are connected to the inlet side of the accumulator. Can be made.

An air conditioner according to a tenth aspect is the air conditioner according to the eighth aspect, wherein the suction refrigerant pipe is provided with an accumulator for temporarily storing the refrigerant , and the suction refrigerant pipe has a portion on the inlet side of the accumulator, A liquid injection pipe and / or a refrigerant return pipe are connected.

  Here, as described above, by connecting the liquid injection pipe and / or the refrigerant return pipe to the inlet side of the accumulator, the refrigerant flowing through the refrigerant return pipe is joined to the refrigerant sucked into the compressor via the accumulator. Therefore, compared with the case where the liquid injection pipe and / or the refrigerant return pipe are connected to the outlet side of the accumulator, for example, liquid compression in the compressor can be prevented.

An air conditioner according to an eleventh aspect is the air conditioner according to the eighth aspect, wherein the suction refrigerant pipe is provided with an accumulator for temporarily storing the refrigerant , and the liquid injection pipe or the refrigerant return pipe is branched into two. The liquid injection pipe or the refrigerant return pipe is connected to both the inlet side portion of the accumulator and the outlet side portion of the accumulator of the suction refrigerant pipe.

  Here, as described above, since the liquid injection pipe or the refrigerant return pipe is connected to both the inlet side and the outlet side of the accumulator, it is desired to improve the effect of reducing the temperature of the refrigerant sucked into the compressor If the refrigerant flowing through the liquid injection pipe or the refrigerant return pipe is sent to the outlet side of the accumulator, and the liquid is discharged so that the pressure of the refrigerant discharged from the compressor does not exceed the predetermined discharge pressure threshold, The refrigerant flowing through the injection pipe or the refrigerant return pipe can be sent to the inlet side of the accumulator.

  An air conditioner according to a twelfth aspect is the air conditioner according to the seventh aspect, wherein a liquid injection pipe and / or a refrigerant return pipe are connected to an intermediate part of the compression stroke of the compressor.

  Here, as described above, since the refrigerant branched from the outdoor liquid refrigerant pipe can be sent to the middle part of the compression stroke of the compressor, the temperature of the refrigerant compressed to the intermediate pressure in the compressor can be lowered. .

  An air conditioner according to a thirteenth aspect is the air conditioner according to the twelfth aspect, wherein an accumulator for temporarily accumulating the refrigerant is provided in an intake refrigerant pipe through which the refrigerant sucked into the compressor flows, and a liquid injection pipe or The refrigerant return pipe is branched into two, and a liquid injection pipe or a refrigerant return pipe is connected to both the inlet side portion of the accumulator and the middle portion of the compressor compression stroke of the suction refrigerant tube.

  Here, as described above, since the liquid injection pipe or the refrigerant return pipe is connected to both the inlet side of the accumulator and the middle part of the compression stroke of the compressor, the temperature of the refrigerant compressed to the intermediate pressure in the compressor. In order to reduce the pressure, the refrigerant flowing through the liquid injection pipe or the refrigerant return pipe is sent to the middle part of the compression stroke of the compressor so that the pressure of the refrigerant discharged from the compressor does not exceed a predetermined discharge pressure threshold. When it is desired to drain the liquid, the refrigerant flowing through the liquid injection pipe or the refrigerant return pipe can be sent to the inlet side of the accumulator.

  An air conditioner according to a fourteenth aspect is the air conditioner according to any one of the first to sixth aspects, wherein a liquid injection expansion valve that depressurizes the refrigerant branched from the outdoor liquid refrigerant pipe is provided in the liquid injection pipe. Provided. And the control part which controls the component apparatus of an outdoor unit and an indoor unit controls the opening degree of a liquid injection expansion valve so that the temperature of the refrigerant | coolant discharged from the compressor may not exceed a predetermined discharge temperature threshold value.

  Here, as described above, the flow rate of the refrigerant sent from the outdoor liquid refrigerant pipe to the compressor through the liquid injection pipe can be adjusted by controlling the opening of the liquid injection expansion valve provided in the liquid injection pipe. Therefore, an increase in the temperature of the refrigerant discharged from the compressor (discharge temperature of the compressor) can be reliably suppressed.

  As described in the above description, according to the present invention, in the air conditioner having a hydraulic pressure adjusting expansion valve, by providing the liquid injection pipe, the increase in the discharge temperature of the compressor is suppressed, and the two-phase refrigerant The conveyance can be performed satisfactorily.

It is a schematic structure figure of the air harmony device concerning a 1st embodiment of the present invention. It is the pressure-enthalpy diagram in which the refrigerating cycle at the time of cooling operation in the air harmony device concerning a 1st embodiment of the present invention was illustrated. It is a schematic block diagram of the air conditioning apparatus concerning the modification 1 of 1st Embodiment of this invention. It is a schematic block diagram of the air conditioning apparatus concerning the modification 2 of 1st Embodiment of this invention. It is a schematic block diagram of the air conditioning apparatus concerning the modification 3 of 1st Embodiment of this invention. It is the pressure-enthalpy diagram in which the refrigerating cycle at the time of the cooling operation in the air conditioning apparatus concerning the modification 3 of 1st Embodiment of this invention was illustrated. It is a schematic block diagram of the air conditioning apparatus concerning the modification 4 of 1st Embodiment of this invention. It is a schematic block diagram of the air conditioning apparatus concerning 2nd Embodiment of this invention. It is the pressure-enthalpy diagram in which the refrigerating cycle at the time of air_conditionaing | cooling operation in the air conditioning apparatus concerning 2nd Embodiment of this invention was illustrated. It is a schematic block diagram of the air conditioning apparatus concerning the modification 1 of 2nd Embodiment of this invention. It is a schematic block diagram of the air conditioning apparatus concerning the modification 2 of 2nd Embodiment of this invention. It is a schematic block diagram of the air conditioning apparatus concerning the modification 2 of 2nd Embodiment of this invention. It is a schematic block diagram of the air conditioning apparatus concerning the modification 3 of 2nd Embodiment of this invention. It is the pressure-enthalpy diagram in which the refrigerating cycle at the time of the cooling operation in the air conditioning apparatus concerning the modification 3 of 2nd Embodiment of this invention was illustrated. It is a schematic block diagram of the air conditioning apparatus concerning the modification 3 of 2nd Embodiment of this invention. It is the pressure-enthalpy diagram in which the refrigerating cycle at the time of the cooling operation in the air conditioning apparatus concerning the modification 3 of 2nd Embodiment of this invention was illustrated. It is a schematic block diagram of the air conditioning apparatus concerning the modification 4 of 2nd Embodiment of this invention. It is a schematic block diagram of the air conditioning apparatus concerning the modification 4 of 2nd Embodiment of this invention. It is a schematic block diagram of the air conditioning apparatus concerning 3rd Embodiment of this invention. It is a schematic block diagram (only outdoor liquid refrigerant pipe periphery) of the air conditioning apparatus concerning other embodiment of this invention. It is a schematic block diagram (only outdoor liquid refrigerant pipe periphery) of the air conditioning apparatus concerning other embodiment of this invention. It is a schematic block diagram (only outdoor liquid refrigerant pipe periphery) of the air conditioning apparatus concerning other embodiment of this invention. It is a schematic block diagram (only outdoor liquid refrigerant pipe periphery) of the air conditioning apparatus concerning other embodiment of this invention. It is a schematic block diagram (only outdoor liquid refrigerant pipe periphery) of the air conditioning apparatus concerning other embodiment of this invention.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of an air conditioner according to the present invention will be described with reference to the drawings. In addition, the specific structure of embodiment of the air conditioning apparatus concerning this invention is not restricted to the following embodiment and its modification, It can change in the range which does not deviate from the summary of invention.

(1) First Embodiment <Configuration>
FIG. 1 is a schematic configuration diagram of an air-conditioning apparatus 1 according to the first embodiment of the present invention. The air conditioner 1 is an apparatus that cools or heats a room such as a building by a vapor compression refrigeration cycle. The air conditioner 1 mainly includes an outdoor unit 2, a plurality (here, two) of indoor units 3a and 3b that are connected in parallel, and a liquid that connects the outdoor unit 2 and the indoor units 3a and 3b. The refrigerant communication pipe 5 and the gas refrigerant communication pipe 6 and a control unit 19 that controls the components of the outdoor unit 2 and the indoor units 3a and 3b are provided. The vapor compression refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2 and the plurality of indoor units 3a and 3b via the liquid refrigerant communication tube 5 and the gas refrigerant communication tube 6. ing. The refrigerant circuit 10 is filled with a refrigerant such as R32.

-Refrigerant communication pipe-
The liquid refrigerant communication pipe 5 mainly has a merging pipe portion extending from the outdoor unit 2 and branch pipe portions 5a and 5b branched into a plurality (here, two) in front of the indoor units 3a and 3b. Yes. The gas refrigerant communication pipe 6 mainly includes a merging pipe portion extending from the outdoor unit 2 and branch pipe portions 6a and 6b branched into a plurality (here, two) in front of the indoor units 3a and 3b. are doing.

-Indoor unit-
The indoor units 3a and 3b are installed in a room such as a building. The indoor units 3a and 3b are connected to the outdoor unit 2 via the liquid refrigerant communication pipe 5 and the gas refrigerant communication pipe 6 as described above, and constitute a part of the refrigerant circuit 10.

  Next, the configuration of the indoor units 3a and 3b will be described. Since the indoor unit 3a and the indoor unit 3b have the same configuration, only the configuration of the indoor unit 3a will be described here. The configuration of the indoor unit 3b is a subscript “ Subscript “b” is attached instead of “a”, and description of each part is omitted.

  The indoor unit 3a mainly includes an indoor expansion valve 51a and an indoor heat exchanger 52a. The indoor unit 3a includes an indoor liquid refrigerant pipe 53a that connects the liquid side end of the indoor heat exchanger 52a and the liquid refrigerant communication pipe 5, and a gas side end of the indoor heat exchanger 52a and the gas refrigerant communication pipe 6. And an indoor gas refrigerant pipe 54a to be connected.

  The indoor expansion valve 51a is an electric expansion valve that adjusts the flow rate of the refrigerant flowing through the indoor heat exchanger 52a while reducing the pressure of the refrigerant, and is provided in the indoor liquid refrigerant pipe 53a.

  The indoor heat exchanger 52a is a heat exchanger that functions as a refrigerant evaporator and cools indoor air, or functions as a refrigerant radiator and heats indoor air. Here, the indoor unit 3a has an indoor fan 55a for sucking indoor air into the indoor unit 3a, exchanging heat with the refrigerant in the indoor heat exchanger 52a, and supplying the indoor air as supply air. Yes. That is, the indoor unit 3a has an indoor fan 55a as a fan that supplies indoor air as a cooling source or heating source of the refrigerant flowing through the indoor heat exchanger 52a to the indoor heat exchanger 52a. The indoor fan 55a is driven by an indoor fan motor 56a.

  Various sensors are provided in the indoor unit 3a. Specifically, the indoor unit 3a includes an indoor heat exchange liquid side sensor 57a that detects a refrigerant temperature Trl at the liquid side end of the indoor heat exchanger 52a, and a refrigerant temperature at the gas side end of the indoor heat exchanger 52a. An indoor heat exchange gas side sensor 58a for detecting Trg and an indoor air sensor 59a for detecting the temperature Tra of indoor air sucked into the indoor unit 3a are provided.

-Outdoor unit-
The outdoor unit 2 is installed outside a building or the like. As described above, the outdoor unit 2 is connected to the indoor units 3a and 3b via the liquid refrigerant communication pipe 5 and the gas refrigerant communication pipe 6 and constitutes a part of the refrigerant circuit 10.

  Next, the configuration of the outdoor unit 2 will be described.

  The outdoor unit 2 mainly has a compressor 21 and an outdoor heat exchanger 23. The outdoor unit 2 also has a switching mechanism 22 for switching between a heat radiation operation state in which the outdoor heat exchanger 23 functions as a refrigerant radiator and an evaporation operation state in which the outdoor heat exchanger 23 functions as a refrigerant evaporator. have. The switching mechanism 22 and the suction side of the compressor 21 are connected by a suction refrigerant pipe 31. The suction refrigerant pipe 31 is provided with an accumulator 29 for temporarily storing the refrigerant sucked into the compressor 21. The discharge side of the compressor 21 and the switching mechanism 22 are connected by a discharge refrigerant pipe 32. The switching mechanism 22 and the gas side end of the outdoor heat exchanger 23 are connected by a first outdoor gas refrigerant pipe 33. The liquid side end of the outdoor heat exchanger 23 and the liquid refrigerant communication pipe 5 are connected by an outdoor liquid refrigerant pipe 34. A liquid side shut-off valve 27 is provided at a connection portion between the outdoor liquid refrigerant pipe 34 and the liquid refrigerant communication pipe 5. The switching mechanism 22 and the gas refrigerant communication pipe 6 are connected by a second outdoor gas refrigerant pipe 35. A gas side shut-off valve 28 is provided at a connection portion between the second outdoor gas refrigerant pipe 35 and the gas refrigerant communication pipe 6. The liquid side closing valve 27 and the gas side closing valve 28 are manually opened and closed valves.

  The compressor 21 is a device for compressing a refrigerant. For example, the compressor 21 has a hermetic structure in which a rotary type or scroll type positive displacement compression element (not shown) is rotationally driven by a compressor motor 21a. Machine is used.

  The switching mechanism 22 connects the discharge side of the compressor 21 and the gas side of the outdoor heat exchanger 23 when the outdoor heat exchanger 23 functions as a refrigerant radiator (hereinafter referred to as “outdoor heat dissipation state”). 1 (see the solid line of the switching mechanism 22 in FIG. 1), when the outdoor heat exchanger 23 functions as a refrigerant evaporator (hereinafter referred to as “outdoor evaporation state”), the suction side of the compressor 21 and the outdoor heat 1 is a device capable of switching the flow of refrigerant in the refrigerant circuit 10 so as to be connected to the gas side of the exchanger 23 (see the broken line of the switching mechanism 22 in FIG. 1). Become.

  The outdoor heat exchanger 23 is a heat exchanger that functions as a refrigerant radiator or functions as a refrigerant evaporator. Here, the outdoor unit 2 has an outdoor fan 24 for sucking outdoor air into the outdoor unit 2 and exchanging heat with the refrigerant in the outdoor heat exchanger 23 and then discharging the air to the outside. That is, the outdoor unit 2 has an outdoor fan 24 as a fan that supplies outdoor air as a cooling source or a heating source of the refrigerant flowing through the outdoor heat exchanger 23 to the outdoor heat exchanger 23. Here, the outdoor fan 24 is driven by an outdoor fan motor 24a.

  And in the air conditioning apparatus 1, when paying attention only to the compressor 21, the outdoor heat exchanger 23, the liquid refrigerant communication pipe 5, and the indoor heat exchangers 52a and 52b, the refrigerant discharged from the compressor 21 is subjected to outdoor heat exchange. The operation (cooling operation) is performed in the order of the cooler 23, the liquid refrigerant communication tube 5, and the indoor heat exchangers 52a and 52b. Further, in the air conditioner 1, when attention is paid only to the compressor 21, the gas refrigerant communication pipe 6, the indoor heat exchangers 52a and 52b, the liquid refrigerant communication pipe 5 and the outdoor heat exchanger 23, the air is discharged from the compressor 21. An operation (heating operation) is performed in which the refrigerant flows in the order of the gas refrigerant communication tube 6, the indoor heat exchangers 52 a and 52 b, the liquid refrigerant communication tube 5, and the outdoor heat exchanger 23. Here, the switching mechanism 22 is switched to the outdoor heat dissipation state during the cooling operation, and the switching mechanism 22 is switched to the outdoor evaporation state during the heating operation.

  Here, the outdoor liquid refrigerant pipe 34 is provided with an outdoor expansion valve 25 and a fluid pressure adjusting expansion valve 26. The outdoor expansion valve 25 is an electric expansion valve that depressurizes the refrigerant during the heating operation, and is provided in a portion of the outdoor liquid refrigerant pipe 34 near the liquid side end of the outdoor heat exchanger 23. The liquid pressure adjusting expansion valve 26 is an electric expansion valve that reduces the pressure of the refrigerant so that the refrigerant flowing through the liquid refrigerant communication tube 5 is in a gas-liquid two-phase state during the cooling operation, and the liquid refrigerant communication tube of the outdoor liquid refrigerant tube 34. It is provided in the part near 5. That is, the hydraulic pressure adjusting expansion valve 26 is provided in a portion of the outdoor liquid refrigerant pipe 34 closer to the liquid refrigerant communication pipe 5 than the outdoor expansion valve 25.

  In the air conditioner 1, during the cooling operation, the refrigerant in the gas-liquid two-phase state is caused to flow through the liquid refrigerant communication tube 5 by the hydraulic pressure adjusting expansion valve 26 and is sent from the outdoor unit 2 side to the indoor units 3a, 3b side. Two-phase conveyance is performed.

In addition, here, a liquid injection pipe 46 is connected to the outdoor liquid refrigerant pipe 34 and a part of the refrigerant flowing in the outdoor liquid refrigerant pipe 34 is branched and sent to the compressor 21 without passing through the heat exchanger . The liquid injection pipe 46 is connected to a part of the outdoor liquid refrigerant pipe 34 that is closer to the outdoor heat exchanger 23 than the liquid pressure adjusting expansion valve 26. More specifically, the liquid injection pipe 46 is connected to a part of the outdoor liquid refrigerant pipe 34 between the outdoor expansion valve 25 and the hydraulic pressure adjusting expansion valve 26. The liquid injection pipe 46 is connected to a suction refrigerant pipe 31 through which a refrigerant sucked into the compressor 21 flows. Moreover, the injection pipe 46 is connected to a portion of the suction refrigerant pipe 31 on the outlet side of the accumulator 29. The liquid injection pipe 46 is provided with a liquid injection expansion valve 47 that decompresses the refrigerant branched from the outdoor liquid refrigerant pipe 34. The liquid injection expansion valve 47 is an electric expansion valve.

  Various types of sensors are provided in the outdoor unit 2. Specifically, the outdoor unit 2 includes a discharge pressure sensor 36 for detecting the pressure of the refrigerant discharged from the compressor 21 (discharge pressure Pd), and the temperature of the refrigerant discharged from the compressor 21 (discharge temperature Td). A discharge temperature sensor 37 for detecting the pressure, a suction pressure sensor 39 for detecting the pressure of the refrigerant sucked into the compressor 21 (suction pressure Ps), and a temperature of the refrigerant sucked into the compressor 21 (suction temperature Ts). An inhalation temperature sensor 40 is provided. The outdoor unit 2 includes an outdoor heat exchange liquid side sensor 38 that detects the refrigerant temperature Tol (outdoor heat exchange outlet temperature Tol) at the liquid side end of the outdoor heat exchanger 24, and the outdoor liquid refrigerant pipe 25. A liquid pipe temperature sensor 49 for detecting the refrigerant temperature (liquid pipe temperature Tlp) in the portion between the expansion valve 25 and the liquid pressure adjusting expansion valve 26 is provided.

-Control unit-
The control unit 19 is configured by communication connection of control boards (not shown) provided in the outdoor unit 2 and the indoor units 3a and 3b. In FIG. 1, for the sake of convenience, the outdoor unit 2 and the indoor units 3a and 3b are illustrated at positions away from each other. Based on the detection signals of the various sensors 36, 37, 38, 39, 40, 49, 57a, 57b, 58a, 58b, 59a, 59b as described above, the control unit 19 (in this case, the outdoor unit) Control of various components 21, 22, 24, 25, 26, 47, 51a, 51b, 55a, 55b of the unit 2 and the indoor units 3a, 3b), that is, operation control of the entire air conditioner 1 is performed. ing.

<Operation and features of air conditioner>
Next, operation | movement and the characteristic of the air conditioning apparatus 1 are demonstrated using FIG.1 and FIG.2. Here, FIG. 2 is a pressure-enthalpy diagram illustrating the refrigeration cycle during the cooling operation in the air-conditioning apparatus 1 according to the first embodiment of the present invention.

In the air conditioner 1, the cooling operation and the heating operation are performed as described above. In the cooling operation, the liquid-pressure adjusting expansion valve 26 provided in the outdoor liquid refrigerant pipe 34 causes the gas-liquid two-phase refrigerant to flow through the liquid refrigerant communication pipe 5 and from the outdoor unit 2 side to the indoor units 3a, 3b. Two-phase conveyance of the refrigerant sent to the side is performed. Further, in cooling operation, the heat exchanger branches a portion of the refrigerant flowing through the outdoor liquid refrigerant pipe 34 to the portion of the outdoor heat exchanger 23 side of the inner fluid pressure adjusting expansion valve 26 of the outdoor liquid refrigerant tube 34 The operation of sending the refrigerant to the compressor 21 is performed while suppressing the fluctuation of the temperature of the refrigerant flowing in the outdoor liquid refrigerant pipe 34 (liquid pipe temperature Tlp) by the liquid injection pipe 46 that is sent to the compressor 21 without intervention . In addition, operation | movement of the air conditioning apparatus 1 demonstrated below is performed by the control part 19 which controls the component apparatus of the air conditioning apparatus 1. FIG.

-Cooling operation-
During the cooling operation, for example, all of the indoor units 3a and 3b are in the cooling operation (that is, all of the indoor heat exchangers 52a and 52b function as a refrigerant evaporator, and the outdoor heat exchanger 23 is a refrigerant radiator. 1), the switching mechanism 22 is switched to the outdoor heat radiation state (the state indicated by the solid line of the switching mechanism 22 in FIG. 1), and the compressor 21, the outdoor fan 24, the indoor fan 55a, 55b is driven.

  Then, the high-pressure refrigerant discharged from the compressor 21 is sent to the outdoor heat exchanger 23 through the switching mechanism 22 (see point B in FIGS. 1 and 2). The refrigerant sent to the outdoor heat exchanger 23 is condensed by being cooled by exchanging heat with outdoor air supplied by the outdoor fan 24 in the outdoor heat exchanger 23 functioning as a radiator of the refrigerant (see FIG. 1 and 2 (see point C). This refrigerant flows out of the outdoor unit 2 through the outdoor expansion valve 25, the hydraulic pressure adjusting expansion valve 26, and the liquid side closing valve 27 (see point D in FIGS. 1 and 2).

  The refrigerant flowing out of the outdoor unit 2 is branched and sent to the indoor units 3a and 3b through the liquid refrigerant communication pipe 5 (see point E in FIGS. 1 and 2). The refrigerant sent to the indoor units 3a and 3b is depressurized to a low pressure by the indoor expansion valves 51a and 51b, and then sent to the indoor heat exchangers 52a and 52b (see point F in FIGS. 1 and 2). The refrigerant sent to the indoor heat exchangers 52a and 52b is heated by exchanging heat with indoor air supplied from the indoors by the indoor fans 55a and 55b in the indoor heat exchangers 52a and 52b functioning as an evaporator of the refrigerant. As a result, it evaporates (see point G in FIGS. 1 and 2). This refrigerant flows out of the indoor units 3a and 3b. On the other hand, the room air cooled in the indoor heat exchangers 52a and 52b is sent into the room, thereby cooling the room.

  The refrigerant that has flowed out of the indoor units 3a and 3b joins and is sent to the outdoor unit 2 through the gas refrigerant communication pipe 6 (see point H in FIGS. 1 and 2). The refrigerant sent to the outdoor unit 2 is sucked into the compressor 21 through the gas side closing valve 28, the switching mechanism 22 and the accumulator 29 (see point A in FIGS. 1 and 2).

  Here, at the time of the above cooling operation, the refrigerant of the gas-liquid two-phase state is caused to flow through the liquid refrigerant communication pipe 5 by the hydraulic pressure adjusting expansion valve 26 and sent from the outdoor unit 2 side to the indoor units 3a, 3b side. Two-phase conveyance is performed. In addition, as will be described below, in carrying out the two-phase conveyance of the refrigerant, the two-phase conveyance of the refrigerant can be performed satisfactorily while suppressing an increase in the discharge temperature Td of the compressor 21 by the liquid injection pipe 46.

  First, the control unit 19 causes the liquid pressure adjusting expansion valve 26 to reduce pressure so that the refrigerant flowing through the liquid refrigerant communication tube 5 is in a gas-liquid two-phase state (points C and D in FIGS. reference). The refrigerant after being depressurized by the hydraulic pressure adjusting expansion valve 26 becomes an intermediate pressure refrigerant whose pressure is lower than that of the high pressure refrigerant and higher than that of the low pressure refrigerant (see point D in FIGS. 1 and 2). . Here, the control unit 19 controls the opening degree of the hydraulic pressure adjusting expansion valve 26 so that the supercooling degree SCo of the refrigerant at the liquid side end of the outdoor heat exchanger 23 becomes the target supercooling degree SCot. Specifically, the control unit 19 obtains the supercooling degree SCo of the refrigerant at the liquid side end of the outdoor heat exchanger 23 from the outdoor heat exchange outlet temperature Tol. The controller 19 subtracts the outdoor heat exchange outlet temperature Tol from the refrigerant temperature Toc obtained by converting the discharge pressure Pd into the saturation temperature, thereby setting the refrigerant subcooling degree SCo at the liquid side end of the outdoor heat exchanger 23. obtain. Then, when the degree of supercooling SCo is greater than the target supercooling degree Scot, the control unit 19 performs control to increase the opening of the hydraulic pressure adjusting expansion valve 26, and the degree of supercooling SCo is greater than the target supercooling degree Scot Is also small, control is performed to reduce the opening degree of the hydraulic pressure adjusting expansion valve 26. At this time, the control unit 19 performs control to fix the opening of the outdoor expansion valve 25 in a fully opened state.

  By this control, the refrigerant flowing through the liquid refrigerant communication tube 5 is in a gas-liquid two-phase state, so that the refrigerant communication pipe 5 is a liquid state refrigerant as compared with the case where the refrigerant flowing through the liquid refrigerant communication tube 5 is in the liquid state. The amount of refrigerant existing in the liquid refrigerant communication tube 5 can be reduced by that amount.

Further, the control unit 19 branches a part of the refrigerant flowing through the outdoor liquid refrigerant pipe 34 so as to suppress an increase in the discharge temperature Td of the compressor 21, and the compressor 21 (here, the compression) The suction refrigerant pipe 31) connected to the suction side of the machine 21 is sent. Here, the control unit 19 controls the opening degree of the liquid injection expansion valve 47 so that the discharge temperature Td of the compressor 21 does not exceed a predetermined discharge temperature threshold Tdx (for example, the upper limit discharge temperature). Specifically, when the discharge temperature Td rises to the discharge temperature threshold Tdx, the control unit 19 performs control to increase the opening of the liquid injection expansion valve 47 until the discharge temperature Td becomes equal to or lower than the discharge temperature threshold Tdx. Is going.

  With this control, the refrigerant (point H in FIGS. 1 and 2) sent from the indoor units 3a and 3b to the outdoor unit 2 is cooled by the refrigerant sent to the compressor 21 through the liquid injection pipe 46 (see FIG. 1). In accordance with the amount of cooling, an increase in the discharge temperature Td of the compressor 21 can be suppressed (see point B in FIGS. 1 and 2).

-Heating operation-
During the heating operation, for example, all of the indoor units 3a and 3b are in the heating operation (that is, all of the indoor heat exchangers 52a and 52b function as a refrigerant radiator, and the outdoor heat exchanger 23 is a refrigerant evaporator. 1), the switching mechanism 22 is switched to the outdoor evaporation state (the state indicated by the broken line of the switching mechanism 22 in FIG. 1), and the compressor 21, the outdoor fan 24, the indoor fan 55a, 55b is driven.

  Then, the high-pressure refrigerant discharged from the compressor 21 flows out of the outdoor unit 2 through the switching mechanism 22 and the gas side shut-off valve 28.

  The refrigerant that has flowed out of the outdoor unit 2 is branched and sent to the indoor units 3 a and 3 b through the gas refrigerant communication pipe 6. The refrigerant sent to the indoor units 3a and 3b is sent to the indoor heat exchangers 52a and 52b. The high-pressure refrigerant sent to the indoor heat exchangers 52a and 52b exchanges heat with indoor air supplied from the indoors by the indoor fans 55a and 55b in the indoor heat exchangers 52a and 52b that function as refrigerant radiators. It is condensed by being cooled. This refrigerant flows out of the indoor units 3a and 3b through the indoor expansion valves 51a and 51b. On the other hand, the indoor air heated in the indoor heat exchangers 52a and 52b is sent into the room, thereby heating the room.

  The refrigerant that has flowed out of the indoor units 3 a and 3 b joins through the liquid refrigerant communication pipe 5 and is sent to the outdoor unit 2. The refrigerant sent to the outdoor unit 2 is sent to the outdoor expansion valve 25 through the liquid side closing valve 27 and the liquid pressure adjusting expansion valve 26. The refrigerant sent to the outdoor expansion valve 25 is reduced to a low pressure by the outdoor expansion valve 25 and then sent to the outdoor heat exchanger 23. The refrigerant sent to the outdoor heat exchanger 23 evaporates when heated by exchanging heat with the outdoor air supplied by the outdoor fan 24. This refrigerant is sucked into the compressor 21 through the switching mechanism 22 and the accumulator 29.

  At this time, the control unit 19 performs control to fix the opening degree of the hydraulic pressure adjusting expansion valve 26 in a fully opened state, and opens the liquid injection expansion valve 47 in a fully closed state so that the refrigerant is supplied to the liquid injection pipe 46. I try not to let it flow.

-Features-
Here, in the configuration in which a refrigerant in a gas-liquid two-phase state is caused to flow through the liquid refrigerant communication tube 5 by the above-described hydraulic pressure adjusting expansion valve 26 and the refrigerant is sent from the outdoor unit 2 side to the indoor units 3a and 3b side. As described above, a part of the refrigerant flowing in the outdoor liquid refrigerant pipe 34 is branched to the part on the outdoor heat exchanger 23 side of the liquid pressure adjusting expansion valve 26 in the outdoor liquid refrigerant pipe 34 via the heat exchanger. A liquid injection pipe 46 that is sent to the compressor 21 without being provided is further provided. Providing such a liquid injection pipe 46 allows the refrigerant to be sent to the compressor 21 while suppressing fluctuations in the temperature of the refrigerant flowing through the outdoor liquid refrigerant pipe 34 (liquid pipe temperature Tlp) (point C in FIG. 2). Thus, the discharge temperature Td of the compressor 21 is prevented while changing the state of the refrigerant flowing through the liquid refrigerant communication pipe 5 after being depressurized by the liquid pressure adjusting expansion valve 26 (see point D in FIG. 2). Can be suppressed (see point B in FIG. 2). Thus, here, the refrigerant flowing through the liquid refrigerant communication tube 5 can be reliably maintained in a desired gas-liquid two-phase state while suppressing an increase in the discharge temperature Td of the compressor 21.

  That is, here, in the configuration having the hydraulic pressure adjusting expansion valve 26, by providing the above-described liquid injection pipe 46, the two-phase conveyance of the refrigerant is favorably performed while suppressing the increase in the discharge temperature Td of the compressor 21. Can do.

  Here, as described above, the control unit 19 opens the hydraulic pressure adjusting expansion valve 26 so that the supercooling degree SCo of the refrigerant at the liquid side end of the outdoor heat exchanger 23 becomes the target supercooling degree Scot. By controlling the degree, the fluid pressure adjusting expansion valve 26 is decompressed so that the refrigerant flowing through the liquid refrigerant communication tube 5 is in a gas-liquid two-phase state. For this reason, it becomes easy to maintain the refrigerant | coolant amount of the outdoor heat exchanger 23 in a desired state here (refer the point C of FIG. 2), As a result, the liquid refrigerant after being pressure-reduced with the hydraulic pressure adjustment expansion valve 26 The refrigerant flowing through the communication pipe 5 can be easily maintained in a desired gas-liquid two-phase state (see point D in FIG. 2).

  In addition, here, the liquid injection pipe 46 is provided with a liquid injection expansion valve 47 for reducing the pressure of the refrigerant branched from the outdoor liquid refrigerant pipe 34. The control unit 19 controls the opening degree of the liquid injection expansion valve 47 so that the discharge temperature Td of the compressor 21 does not exceed a predetermined discharge temperature threshold value Tdx (for example, an upper limit discharge temperature). As described above, since the flow rate of the refrigerant sent from the outdoor liquid refrigerant pipe 34 to the compressor 21 through the liquid injection pipe 46 can be adjusted here, it is possible to reliably suppress an increase in the discharge temperature Td of the compressor 21. Yes (see point B in FIG. 2).

  Here, a liquid injection pipe 46 is connected to the suction refrigerant pipe 31 through which the refrigerant sucked into the compressor 21 flows. For this reason, since the refrigerant branched from the outdoor liquid refrigerant pipe 34 can be sent to the suction side of the compressor 21 here, the temperature of the refrigerant sucked into the compressor 21 can be lowered (point of FIG. 2). H, A). In particular, here, a liquid injection pipe 46 is connected to a portion of the suction refrigerant pipe 31 on the outlet side of the accumulator 29, and the refrigerant flowing through the liquid injection pipe 46 without being passed through the accumulator 29 is sucked into the compressor 21. It can be made to merge with the refrigerant. For this reason, here, compared with the case where the liquid injection pipe 46 is connected to the inlet side of the accumulator 29, the effect of lowering the temperature of the refrigerant sucked into the compressor 21 can be improved.

<Modification 1>
In the air conditioner 1 of the first embodiment (see FIG. 1), the liquid injection pipe 46 is connected to the portion of the suction refrigerant pipe 31 on the outlet side of the accumulator 29, so that the suction to the compressor 21 is achieved. The effect of lowering the temperature of the refrigerant to be improved is improved. However, the connection position of the liquid injection pipe 46 to the suction refrigerant pipe 31 is not limited to this.

  Here, as shown in FIG. 3, a liquid injection pipe 46 is connected to a portion of the suction refrigerant pipe 34 on the inlet side of the accumulator 29, and the refrigerant flowing through the liquid injection pipe 46 via the accumulator 29 is supplied to the compressor. The refrigerant can be merged with the refrigerant sucked into 21. For this reason, compared with the case where the liquid injection pipe | tube 46 is connected to the exit side of the accumulator 29 here, the liquid compression in the compressor 21 can be prevented, for example. In this configuration, a return pipe 31a for sending the refrigerant from the bottom of the accumulator 29 to a portion of the suction refrigerant pipe 31 on the outlet side of the accumulator 29 is provided, and the control unit 19 is provided with a return pipe provided in the return pipe 31a. The liquid refrigerant accumulated in the accumulator 29 may be returned to the compressor 21 by controlling the liquid valve 31b.

<Modification 2>
In the air conditioner 1 according to the first embodiment and the first modification (see FIGS. 1 and 3), the liquid injection pipe 46 is provided at the inlet side portion of the accumulator 29 or the outlet side portion of the accumulator 29 in the suction refrigerant pipe 31. Is connected. However, the connection position of the liquid injection pipe 46 to the suction refrigerant pipe 31 is not limited to these.

  Here, as shown in FIG. 4, the liquid injection pipe 46 is branched into two, and the liquid injection pipe 46 is provided in both the inlet side portion of the accumulator 29 and the outlet side portion of the accumulator 29 in the suction refrigerant pipe 31. Is connected. Here, the liquid injection pipe 46 that is connected to the outlet side portion of the accumulator 29 is referred to as a first liquid injection pipe 46a, and the liquid injection pipe 46 that is connected to the inlet side portion of the accumulator 29 is a second liquid. The injection tube 46b is used. Thus, here, when the liquid injection pipe 46 is connected to both the inlet side and the outlet side of the accumulator 29, when it is desired to improve the effect of reducing the temperature of the refrigerant sucked into the compressor 21, The refrigerant flowing through the liquid injection pipe 46 is sent to the outlet side of the accumulator 29. For example, when it is desired to prevent liquid compression in the compressor 21, the refrigerant flowing through the liquid injection pipe 46 may be sent to the inlet side of the accumulator 29. Good.

  Also, the liquid injection pipe 46 of FIG. 4 is branched into two, and the liquid injection pipe 46 is connected to both the inlet side portion of the accumulator 29 and the outlet side portion of the accumulator 29 in the suction refrigerant pipe 31. Utilization can suppress an increase in the discharge pressure Pd of the compressor 21. Specifically, a liquid drain valve 46d is provided in the second liquid injection pipe 46b connected to the inlet side portion of the accumulator 29 in the liquid injection pipe 46, and the discharge pressure Pd of the compressor 21 is set at a predetermined discharge level. The drain valve 46d is controlled so as not to exceed the pressure threshold Pdx (for example, the upper limit discharge pressure). Specifically, when the discharge pressure Pd rises to the discharge pressure threshold value Pdx, the control unit 19 performs control to open the drain valve 46d until the discharge pressure Pd becomes equal to or lower than the discharge pressure threshold value pdx. As a result, the liquid refrigerant existing in the outdoor heat exchanger 23 can be sent to the accumulator 29 through the liquid injection pipe 46, and as a result, an increase in the discharge pressure Pd can be suppressed. Thus, here, by controlling the drain valve 46d provided in the second liquid injection pipe 46b connected to the inlet side of the accumulator 29 in the liquid injection pipe 46, the outdoor liquid refrigerant is passed through the liquid injection pipe 46. Since the refrigerant can be sent from the pipe 34 to the accumulator 29, an increase in the discharge pressure Pd of the compressor 21 can be suppressed. In this configuration, a capillary tube 46c that provides flow resistance is provided in the first liquid injection pipe 46a so that a large amount of refrigerant can flow through the second liquid injection pipe 46b during the liquid drain control.

<Modification 3>
In the air conditioner 1 of the first embodiment (see FIG. 1), the refrigerant branched from the outdoor liquid refrigerant pipe 34 is sent to the suction side of the compressor 21 by connecting the liquid injection pipe 46 to the suction refrigerant pipe 31. Thus, the temperature of the refrigerant sucked into the compressor 21 is lowered (see points H and A in FIG. 2), and as a result, an increase in the discharge temperature Td of the compressor 21 is suppressed. However, the destination of the refrigerant flowing through the liquid injection pipe 46 to the compressor 21 is not limited to this.

  Here, as shown in FIG. 5, a liquid injection pipe 46 may be connected to an intermediate part of the compression stroke of the compressor 21.

  In this configuration, unlike the first embodiment (see points H and A in FIG. 2), as shown in FIGS. 5 and 6, the refrigerant branched from the outdoor liquid refrigerant pipe 34 to the liquid injection pipe 46 is compressed. The temperature of the refrigerant sent to the middle part of the compression stroke 21 and reduced to the intermediate pressure in the compressor 21 is reduced (see point I in FIG. 6), thereby suppressing an increase in the discharge temperature Td of the compressor 21. it can. In this case as well, the control of the hydraulic pressure adjusting expansion valve 26 for carrying out the two-phase conveyance of the refrigerant is the same as that in the first embodiment, and the description thereof is omitted here.

<Modification 4>
Also in the air conditioner 1 of Modification 3 (see FIG. 5) of the first embodiment, as shown in FIG. 7, the liquid injection pipe 46 is divided into two as in Modification 2 (see FIG. 4). The liquid injection pipe 46 may be connected to both the portion of the intake refrigerant pipe 31 on the inlet side of the accumulator 29 and the middle part of the compression stroke of the compressor 21. Here, one of the liquid injection pipes 46 connected to the middle part of the compression stroke of the compressor 21 is referred to as a first liquid injection pipe 46a, and one of the liquid injection pipes 46 connected to the inlet side portion of the accumulator 29 is first. A two-liquid injection tube 46b is used. Thus, here, by connecting the liquid injection pipe 46 to both the inlet side portion of the accumulator 29 and the middle portion of the compression stroke of the compressor 21 in the suction refrigerant pipe 31, the compressor 21 reaches the intermediate pressure. When it is desired to lower the temperature of the compressed refrigerant, the refrigerant flowing through the liquid injection pipe 46 is sent to the middle part of the compression stroke of the compressor 21. For example, when liquid compression in the compressor 21 is to be prevented, The refrigerant flowing through the injection pipe 46 can be sent to the inlet side of the accumulator.

  Further, the liquid injection pipe 46 of FIG. 7 is branched into two, and the liquid injection pipe 46 is connected to both the inlet side portion of the accumulator 29 and the middle portion of the compression stroke of the compressor 21 in the suction refrigerant pipe 31. By using the configuration, it is possible to suppress an increase in the discharge pressure Pd of the compressor 21. Specifically, a liquid drain valve 46d is provided in the second liquid injection pipe 46b connected to the inlet side portion of the accumulator 29 in the liquid injection pipe 46, and the discharge pressure Pd of the compressor 21 is set at a predetermined discharge level. The drain valve 46d is controlled so as not to exceed the pressure threshold Pdx (for example, the upper limit discharge pressure). Specifically, when the discharge pressure Pd rises to the discharge pressure threshold value Pdx, the control unit 19 performs control to open the drain valve 46d until the discharge pressure Pd becomes equal to or lower than the discharge pressure threshold value pdx. As a result, the liquid refrigerant existing in the outdoor heat exchanger 23 can be sent to the accumulator 29 through the liquid injection pipe 46, and as a result, an increase in the discharge pressure Pd can be suppressed. Thus, here, by controlling the drain valve 46d provided in the second liquid injection pipe 46b connected to the inlet side of the accumulator 29 in the liquid injection pipe 46, the outdoor liquid refrigerant is passed through the liquid injection pipe 46. Since the refrigerant can be sent from the pipe 34 to the accumulator 29, an increase in the discharge pressure Pd of the compressor 21 can be suppressed.

(2) Second Embodiment <Configuration>
FIG. 8 is a schematic configuration diagram of an air-conditioning apparatus 1 according to the second embodiment of the present invention. The air conditioner 1 is an apparatus that cools or heats a room such as a building by a vapor compression refrigeration cycle. The air conditioner 1 mainly includes an outdoor unit 2, a plurality (here, two) of indoor units 3a and 3b that are connected in parallel, and a liquid that connects the outdoor unit 2 and the indoor units 3a and 3b. The refrigerant communication pipe 5 and the gas refrigerant communication pipe 6 and a control unit 19 that controls the components of the outdoor unit 2 and the indoor units 3a and 3b are provided. The vapor compression refrigerant circuit 10 of the air conditioner 1 is configured by connecting the outdoor unit 2 and the plurality of indoor units 3a and 3b via the liquid refrigerant communication tube 5 and the gas refrigerant communication tube 6. ing. The refrigerant circuit 10 is filled with a refrigerant such as R32.

-Refrigerant communication pipe-
The liquid refrigerant communication pipe 5 mainly has a merging pipe portion extending from the outdoor unit 2 and branch pipe portions 5a and 5b branched into a plurality (here, two) in front of the indoor units 3a and 3b. Yes. The gas refrigerant communication pipe 6 mainly includes a merging pipe portion extending from the outdoor unit 2 and branch pipe portions 6a and 6b branched into a plurality (here, two) in front of the indoor units 3a and 3b. are doing.

-Indoor unit-
The indoor units 3a and 3b are installed in a room such as a building. The indoor units 3a and 3b are connected to the outdoor unit 2 via the liquid refrigerant communication pipe 5 and the gas refrigerant communication pipe 6 as described above, and constitute a part of the refrigerant circuit 10.

  In addition, since the structure of the indoor units 3a and 3b is the same structure as the indoor units 3a and 3b of 1st Embodiment, description is abbreviate | omitted here.

-Outdoor unit-
The outdoor unit 2 is installed outside a building or the like. As described above, the outdoor unit 2 is connected to the indoor units 3a and 3b via the liquid refrigerant communication pipe 5 and the gas refrigerant communication pipe 6 and constitutes a part of the refrigerant circuit 10.

  The configuration of the outdoor unit 2 is different from the configuration of the outdoor unit 2 of the first embodiment only in that a refrigerant return pipe 41 and a refrigerant cooler 45 are provided. For this reason, the structure of the refrigerant | coolant return pipe | tube 41 and the refrigerant | coolant cooler 45 is mainly demonstrated here.

  Here, a refrigerant return pipe 41 is connected to the outdoor liquid refrigerant pipe 34, and a refrigerant cooler 45 is provided. The refrigerant return pipe 41 is a refrigerant pipe that branches a part of the refrigerant flowing through the outdoor liquid refrigerant pipe 34 and sends it to the compressor 21. The refrigerant cooler 45 is a heat exchanger that cools the refrigerant flowing in the outdoor heat exchanger 23 side of the outdoor liquid refrigerant pipe 34 with respect to the outdoor heat exchanger 23 by the refrigerant flowing through the refrigerant return pipe 41. Here, the outdoor expansion valve 25 is provided in a portion of the outdoor liquid refrigerant pipe 34 that is closer to the outdoor heat exchanger 23 than the refrigerant cooler 45. Further, the liquid pressure adjusting expansion valve 26 is a portion of the outdoor liquid refrigerant pipe 34 closer to the liquid refrigerant communication pipe 5 than the part to which the refrigerant cooler 45 is connected (here, the refrigerant cooler 45 and the liquid side closing valve 27). Between the two). Further, here, the liquid injection pipe 46 is connected to a portion of the outdoor liquid refrigerant pipe 34 between the refrigerant cooler 45 and the liquid pressure adjusting expansion valve 26.

  The refrigerant return pipe 41 is a refrigerant pipe that sends the refrigerant branched from the outdoor liquid refrigerant pipe 34 to the suction side of the compressor 21. The refrigerant return pipe 41 mainly has a refrigerant return inlet pipe 42 and a refrigerant return outlet pipe 43. The refrigerant return inlet pipe 42, a part of the refrigerant flowing through the outdoor liquid refrigerant pipe 34, is a portion between the liquid side end of the outdoor heat exchanger 23 and the hydraulic pressure adjusting expansion valve 26 (here, the outdoor expansion valve 25 and the refrigerant). The refrigerant pipe is branched from the portion between the refrigerant cooler 45 and sent to the inlet of the refrigerant cooler 45 on the refrigerant return pipe 41 side. The refrigerant return inlet pipe 42 is provided with a refrigerant return expansion valve 44 that adjusts the flow rate of the refrigerant flowing through the refrigerant cooler 45 while decompressing the refrigerant flowing through the refrigerant return pipe 41. Here, the refrigerant return expansion valve 44 is an electric expansion valve. The refrigerant return outlet pipe 43 is a refrigerant pipe sent from the outlet on the refrigerant return pipe 41 side of the refrigerant cooler 45 to the suction refrigerant pipe 31. Moreover, the refrigerant return outlet pipe 43 of the refrigerant return pipe 41 is connected to a portion of the suction refrigerant pipe 31 on the outlet side of the accumulator 29. The refrigerant cooler 45 cools the refrigerant flowing through the outdoor liquid refrigerant pipe 34 with the refrigerant flowing through the refrigerant return pipe 41. Here, the refrigerant cooler 45 is a heat exchanger of a type in which the refrigerant flowing through the refrigerant return pipe 41 and the refrigerant flowing through the outdoor liquid refrigerant pipe 34 are opposed to each other during the cooling operation.

  Also, here, the outlet of the refrigerant cooler 45 and the liquid injection pipe of the outdoor liquid refrigerant pipe 34 so that the liquid pipe temperature sensor 49 detects the temperature of the refrigerant at the outlet of the refrigerant cooler 45 as the liquid pipe temperature Tlp. 46 is provided in the part between the connected parts.

-Control unit-
The control unit 19 is configured by communication connection of control boards (not shown) provided in the outdoor unit 2 and the indoor units 3a and 3b. In FIG. 8, for the sake of convenience, the outdoor unit 2 and the indoor units 3a and 3b are illustrated at positions away from each other. Based on the detection signals of the various sensors 36, 37, 38, 39, 40, 49, 57a, 57b, 58a, 58b, 59a, 59b as described above, the control unit 19 (in this case, the outdoor unit) Control of the various components 21, 22, 24, 25, 26, 41, 47, 51 a, 51 b, 55 a, 55 b of the unit 2 and indoor units 3 a, 3 b), that is, operation control of the entire air conditioner 1 is performed. It has become.

<Operation and features of air conditioner>
Next, operation | movement and the characteristic of the air conditioning apparatus 1 are demonstrated using FIG.8 and FIG.9. Here, FIG. 9 is a pressure-enthalpy diagram illustrating the refrigeration cycle during the cooling operation in the air-conditioning apparatus 1 according to the second embodiment of the present invention.

In the air conditioner 1, the cooling operation and the heating operation are performed as described above. In the cooling operation, the liquid-pressure adjusting expansion valve 26 provided in the outdoor liquid refrigerant pipe 34 causes the gas-liquid two-phase refrigerant to flow through the liquid refrigerant communication pipe 5 and from the outdoor unit 2 side to the indoor units 3a, 3b. Two-phase conveyance of the refrigerant sent to the side is performed. Further, in the cooling operation, a part of the refrigerant flowing in the outdoor liquid refrigerant pipe 34 is branched and sent to the compressor 21, and the liquid in the outdoor liquid refrigerant pipe 34 is cooled by the refrigerant flowing in the refrigerant return pipe 41. A portion of the outdoor liquid refrigerant pipe 34 between the refrigerant cooler 45 and the liquid pressure adjusting expansion valve 26 is cooled by the refrigerant cooler 45 that cools the refrigerant flowing in the portion closer to the outdoor heat exchanger 23 than the pressure adjusting expansion valve 26. The operation of cooling the refrigerant in is performed. Further, in cooling operation, the heat exchanger branches a portion of the refrigerant flowing through the outdoor liquid refrigerant pipe 34 to the portion of the outdoor heat exchanger 23 side of the inner fluid pressure adjusting expansion valve 26 of the outdoor liquid refrigerant tube 34 The operation of sending the refrigerant to the compressor 21 is performed while suppressing the fluctuation of the temperature of the refrigerant flowing in the outdoor liquid refrigerant pipe 34 (liquid pipe temperature Tlp) by the liquid injection pipe 46 that is sent to the compressor 21 without intervention . In addition, operation | movement of the air conditioning apparatus 1 demonstrated below is performed by the control part 19 which controls the component apparatus of the air conditioning apparatus 1. FIG.

-Cooling operation-
During the cooling operation, for example, all of the indoor units 3a and 3b are in the cooling operation (that is, all of the indoor heat exchangers 52a and 52b function as a refrigerant evaporator, and the outdoor heat exchanger 23 is a refrigerant radiator. When switching is performed, the switching mechanism 22 is switched to the outdoor heat dissipation state (the state indicated by the solid line of the switching mechanism 22 in FIG. 8), and the compressor 21, the outdoor fan 24, the indoor fan 55a, 55b is driven.

  Then, the high-pressure refrigerant discharged from the compressor 21 is sent to the outdoor heat exchanger 23 through the switching mechanism 22 (see point B in FIGS. 8 and 9). The refrigerant sent to the outdoor heat exchanger 23 is condensed by being cooled by exchanging heat with outdoor air supplied by the outdoor fan 24 in the outdoor heat exchanger 23 functioning as a radiator of the refrigerant (see FIG. (Refer to point C in 8 and 9). This refrigerant flows out of the outdoor unit 2 through the outdoor expansion valve 25, the refrigerant cooler 45, the liquid pressure adjusting expansion valve 26, and the liquid side closing valve 27 (see point D in FIGS. 8 and 9).

  The refrigerant flowing out of the outdoor unit 2 is branched and sent to the indoor units 3a and 3b through the liquid refrigerant communication tube 5 (see point E in FIGS. 8 and 9). The refrigerant sent to the indoor units 3a and 3b is reduced to a low pressure by the indoor expansion valves 51a and 51b, and then sent to the indoor heat exchangers 52a and 52b (see point F in FIGS. 8 and 9). The refrigerant sent to the indoor heat exchangers 52a and 52b is heated by exchanging heat with indoor air supplied from the indoors by the indoor fans 55a and 55b in the indoor heat exchangers 52a and 52b functioning as an evaporator of the refrigerant. This evaporates (see point G in FIGS. 8 and 9). This refrigerant flows out of the indoor units 3a and 3b. On the other hand, the room air cooled in the indoor heat exchangers 52a and 52b is sent into the room, thereby cooling the room.

  The refrigerant that has flowed out of the indoor units 3a and 3b joins and is sent to the outdoor unit 2 through the gas refrigerant communication pipe 6 (see point H in FIGS. 8 and 9). The refrigerant sent to the outdoor unit 2 is sucked into the compressor 21 through the gas side closing valve 28, the switching mechanism 22 and the accumulator 29 (see point A in FIGS. 8 and 9).

  Here, at the time of the above cooling operation, the refrigerant of the gas-liquid two-phase state is caused to flow through the liquid refrigerant communication pipe 5 by the hydraulic pressure adjusting expansion valve 26 and sent from the outdoor unit 2 side to the indoor units 3a, 3b side. Two-phase conveyance is performed. Moreover, as will be described below, the refrigerant flowing through the outdoor liquid refrigerant pipe 34 is cooled by the refrigerant return pipe 41 and the refrigerant cooler 45 in carrying out the two-phase conveyance of the refrigerant, and the compressor 21 is made by the liquid injection pipe 46. Thus, the refrigerant can be favorably transported in two phases while suppressing an increase in the discharge temperature Td.

  First, the control unit 19 causes the liquid pressure adjusting expansion valve 26 to reduce pressure so that the refrigerant flowing through the liquid refrigerant communication tube 5 is in a gas-liquid two-phase state (points J and D in FIGS. 8 and 9). reference). The refrigerant after being depressurized by the hydraulic pressure adjusting expansion valve 26 becomes an intermediate pressure refrigerant whose pressure is lower than that of the high pressure refrigerant and higher than that of the low pressure refrigerant (see point D in FIGS. 8 and 9). . Here, the control unit 19 controls the opening degree of the hydraulic pressure adjusting expansion valve 26 so that the supercooling degree SCo of the refrigerant at the liquid side end of the outdoor heat exchanger 23 becomes the target supercooling degree SCot. Specifically, the control unit 19 obtains the supercooling degree SCo of the refrigerant at the liquid side end of the outdoor heat exchanger 23 from the outdoor heat exchange outlet temperature Tol. The controller 19 subtracts the outdoor heat exchange outlet temperature Tol from the refrigerant temperature Toc obtained by converting the discharge pressure Pd into the saturation temperature, thereby setting the refrigerant subcooling degree SCo at the liquid side end of the outdoor heat exchanger 23. obtain. Then, when the degree of supercooling SCo is greater than the target supercooling degree Scot, the control unit 19 performs control to increase the opening of the hydraulic pressure adjusting expansion valve 26, and the degree of supercooling SCo is greater than the target supercooling degree Scot Is also small, control is performed to reduce the opening degree of the hydraulic pressure adjusting expansion valve 26. At this time, the control unit 19 performs control to fix the opening of the outdoor expansion valve 25 in a fully opened state.

  By this control, the refrigerant flowing through the liquid refrigerant communication tube 5 is in a gas-liquid two-phase state, so that the refrigerant communication pipe 5 is a liquid state refrigerant as compared with the case where the refrigerant flowing through the liquid refrigerant communication tube 5 is in the liquid state. The amount of refrigerant existing in the liquid refrigerant communication tube 5 can be reduced by that amount.

  Further, the control unit 19 cools the refrigerant flowing in the outdoor heat exchanger 23 side of the outdoor liquid refrigerant pipe 34 with respect to the outdoor heat exchanger 23 in the refrigerant cooler 45 by the refrigerant flowing in the refrigerant return pipe 41. Thus, the refrigerant temperature (liquid pipe temperature Tlp) in the portion of the outdoor liquid refrigerant pipe 34 between the refrigerant cooler 45 and the hydraulic pressure adjusting expansion valve 26 is made constant. Here, the controller 19 causes the refrigerant temperature (liquid pipe temperature Tlp) in the portion between the refrigerant cooler 45 and the hydraulic pressure adjusting expansion valve 26 in the outdoor liquid refrigerant pipe 34 to become the target liquid pipe temperature Tlpt. In addition, the opening degree of the refrigerant return expansion valve 44 is controlled. Specifically, when the liquid pipe temperature Tlp is higher than the target liquid pipe temperature Tlpt, the control unit 19 performs control to increase the opening degree of the refrigerant return expansion valve 44, and the liquid pipe temperature Tlp is set to the target liquid pipe temperature. When it is lower than Tlpt, control is performed to reduce the opening degree of the refrigerant return expansion valve 44.

  By this control, the temperature of the refrigerant (liquid pipe temperature Tlp) in the portion of the outdoor liquid refrigerant pipe 34 between the refrigerant cooler 45 and the hydraulic pressure adjusting expansion valve 26 can be kept constant at the target liquid pipe temperature Tlpt. (See point J in FIGS. 8 and 9).

Further, the control unit 19 branches a part of the refrigerant flowing through the outdoor liquid refrigerant pipe 34 so as to suppress an increase in the discharge temperature Td of the compressor 21, and the compressor 21 (here, the compression) The suction refrigerant pipe 31) connected to the suction side of the machine 21 is sent. Here, the control unit 19 controls the opening degree of the liquid injection expansion valve 47 so that the discharge temperature Td of the compressor 21 does not exceed a predetermined discharge temperature threshold Tdx (for example, the upper limit discharge temperature). Specifically, when the discharge temperature Td rises to the discharge temperature threshold Tdx, the control unit 19 performs control to increase the opening of the liquid injection expansion valve 47 until the discharge temperature Td becomes equal to or lower than the discharge temperature threshold Tdx. Is going.

  By this control, the refrigerant (point H in FIGS. 8 and 9) sent from the indoor units 3a and 3b to the outdoor unit 2 is cooled by the refrigerant sent to the compressor 21 through the liquid injection pipe 46 (see FIG. 8). According to the cooling amount, an increase in the discharge temperature Td of the compressor 21 can be suppressed (see point B in FIGS. 8 and 9).

-Heating operation-
During the heating operation, for example, all of the indoor units 3a and 3b are in the heating operation (that is, all of the indoor heat exchangers 52a and 52b function as a refrigerant radiator, and the outdoor heat exchanger 23 is a refrigerant evaporator. When the switching mechanism 22 is switched to the outdoor evaporation state (the state indicated by the broken line of the switching mechanism 22 in FIG. 8), the compressor 21, the outdoor fan 24, the indoor fan 55a, 55b is driven.

  Then, the high-pressure refrigerant discharged from the compressor 21 flows out of the outdoor unit 2 through the switching mechanism 22 and the gas side shut-off valve 28.

  The refrigerant that has flowed out of the outdoor unit 2 is branched and sent to the indoor units 3 a and 3 b through the gas refrigerant communication pipe 6. The refrigerant sent to the indoor units 3a and 3b is sent to the indoor heat exchangers 52a and 52b. The high-pressure refrigerant sent to the indoor heat exchangers 52a and 52b exchanges heat with indoor air supplied from the indoors by the indoor fans 55a and 55b in the indoor heat exchangers 52a and 52b that function as refrigerant radiators. It is condensed by being cooled. This refrigerant flows out of the indoor units 3a and 3b through the indoor expansion valves 51a and 51b. On the other hand, the indoor air heated in the indoor heat exchangers 52a and 52b is sent into the room, thereby heating the room.

  The refrigerant that has flowed out of the indoor units 3 a and 3 b joins through the liquid refrigerant communication pipe 5 and is sent to the outdoor unit 2. The refrigerant sent to the outdoor unit 2 is sent to the outdoor expansion valve 25 through the liquid side closing valve 27, the liquid pressure adjusting expansion valve 26 and the refrigerant cooler 45. The refrigerant sent to the outdoor expansion valve 25 is reduced to a low pressure by the outdoor expansion valve 25 and then sent to the outdoor heat exchanger 23. The refrigerant sent to the outdoor heat exchanger 23 evaporates when heated by exchanging heat with the outdoor air supplied by the outdoor fan 24. This refrigerant is sucked into the compressor 21 through the switching mechanism 22 and the accumulator 29.

  At this time, the control unit 19 performs control to fix the opening of the hydraulic pressure adjusting expansion valve 26 in a fully opened state, and sets the opening of the refrigerant return expansion valve 44 and the liquid injection expansion valve 47 to a fully closed state. The refrigerant is prevented from flowing through the return pipe 41 and the liquid injection pipe 46.

-Features-
Here, in the configuration in which a refrigerant in a gas-liquid two-phase state is caused to flow through the liquid refrigerant communication tube 5 by the above-described hydraulic pressure adjusting expansion valve 26 and the refrigerant is sent from the outdoor unit 2 side to the indoor units 3a and 3b side. As described above, the refrigerant return pipe 41 and the refrigerant flowing through the refrigerant return pipe 41 cool the refrigerant flowing in the outdoor liquid refrigerant pipe 34 through the portion closer to the outdoor heat exchanger 23 than the liquid pressure adjusting expansion valve 26. A vessel 45 is further provided.

  Here, assuming that such a refrigerant return pipe 41 and a refrigerant cooler 45 are provided without providing the liquid injection pipe 46, the refrigerant flowing through the refrigerant return pipe 41 is the refrigerant flowing through the refrigerant cooler 45. Since it is sent to the compressor 21 after cooling, it is possible to suppress an increase in the discharge temperature Td of the compressor 21. However, since the refrigerant flowing through the refrigerant return pipe 41 is sent to the compressor 21 after cooling the refrigerant flowing through the outdoor liquid refrigerant pipe 34 in the refrigerant cooler 45, the outdoor liquid refrigerant pipe 34 after passing through the refrigerant cooler 45. The temperature of the refrigerant flowing through the refrigerant (liquid pipe temperature Tlp) varies according to the flow rate of the refrigerant flowing through the refrigerant return pipe 41, and as a result, flows through the liquid refrigerant communication pipe 5 after being depressurized by the liquid pressure adjusting expansion valve 26. The state of the refrigerant also varies. For example, if the flow rate of the refrigerant flowing through the refrigerant return pipe 41 increases too much, the rise in the discharge temperature Td of the compressor 21 can be suppressed to some extent, but the liquid pipe temperature Tlp is too low. The refrigerant flowing through the liquid refrigerant communication tube 5 after being depressurized by the pressure adjusting expansion valve 26 becomes a gas-liquid two-phase state with a large amount of liquid components.

  That is, in the configuration having the hydraulic pressure adjusting expansion valve 26, it may not be possible to maintain a desired gas-liquid two-phase state simply by providing the refrigerant return pipe 41 and the refrigerant cooler 45. It is difficult to satisfactorily carry out the two-phase conveyance of the refrigerant while suppressing an increase in the discharge temperature Td.

  Therefore, here, not only the refrigerant return pipe 41 and the refrigerant cooler 45 but also the liquid injection pipe 46 is provided. Providing such a liquid injection pipe 46 allows the refrigerant to be sent to the compressor 21 while suppressing fluctuations in the liquid pipe temperature Tlp (see point J in FIG. 9), so the flow rate of the refrigerant flowing through the refrigerant return pipe 41 Even if the amount is not increased, an increase in the discharge temperature Td of the compressor 21 can be suppressed. If the flow rate of the refrigerant flowing through the refrigerant return pipe 41 is not large, the liquid pipe temperature Tlp will not decrease too much. As a result, the liquid refrigerant communication pipe 5 after being depressurized by the liquid pressure adjusting expansion valve 26 is connected. The flowing refrigerant does not become a gas-liquid two-phase state with many liquid components. As described above, the refrigerant flowing through the liquid refrigerant communication pipe 5 can be maintained in a desired gas-liquid two-phase state while suppressing an increase in the discharge temperature Td of the compressor 21 (see point B in FIG. 9). (See point D in FIG. 9).

  That is, here, in the configuration having the hydraulic pressure adjusting expansion valve 26, the discharge temperature td of the compressor 21 is increased by providing the liquid injection pipe 46 together with the refrigerant return pipe 41 and the refrigerant cooler 45. While suppressing, the two-phase conveyance of the refrigerant can be performed satisfactorily.

  Here, as described above, the control unit 19 opens the hydraulic pressure adjusting expansion valve 26 so that the supercooling degree SCo of the refrigerant at the liquid side end of the outdoor heat exchanger 23 becomes the target supercooling degree Scot. By controlling the degree, the fluid pressure adjusting expansion valve 26 is decompressed so that the refrigerant flowing through the liquid refrigerant communication tube 5 is in a gas-liquid two-phase state. For this reason, it becomes easy to maintain the refrigerant | coolant amount of the outdoor heat exchanger 23 in a desired state here (refer FIG. 9 point C), As a result, the state of the refrigerant | coolant sent to the refrigerant cooler 45 can be stabilized. it can.

  In addition, here, the liquid injection pipe 46 is provided with a liquid injection expansion valve 47 for decompressing the refrigerant branched from the outdoor liquid refrigerant pipe 34, and the refrigerant branched from the outdoor liquid refrigerant pipe 34 is decompressed in the refrigerant return pipe 41. A refrigerant return expansion valve 44 is provided. The control unit 19 controls the opening degree of the liquid injection expansion valve 47 so that the discharge temperature Td of the compressor 21 does not exceed a predetermined discharge temperature threshold Tdx (for example, the upper limit discharge temperature), and the outdoor liquid refrigerant. The opening degree of the refrigerant return expansion valve 44 is set so that the refrigerant temperature (liquid pipe temperature Tlp) in the portion of the pipe 34 between the refrigerant cooler 45 and the hydraulic pressure adjusting expansion valve 26 becomes the target liquid pipe temperature Tlpt. I have control. Thus, here, the flow rate of the refrigerant sent from the outdoor liquid refrigerant pipe 34 to the compressor 21 through the liquid injection pipe 46 is controlled by controlling the opening degree of the liquid injection expansion valve 47 provided in the liquid injection pipe 46. Since it can be adjusted, an increase in the discharge temperature Td of the compressor 21 can be reliably suppressed (see point B in FIG. 9). In addition, here, the flow rate of the refrigerant that exchanges heat with the refrigerant flowing in the outdoor liquid refrigerant pipe 34 in the refrigerant cooler 45 is adjusted by controlling the opening degree of the refrigerant return expansion valve 44 provided in the refrigerant return pipe 41. Therefore, the liquid pipe temperature Tlp can be kept constant at the target liquid pipe temperature Tlpt (see point J in FIG. 9). Then, by making the liquid pipe temperature Tlp constant, the refrigerant flowing through the liquid refrigerant communication pipe 5 after being decompressed by the liquid pressure adjusting expansion valve 26 can be reliably maintained in a desired gas-liquid two-phase state ( (See point D in FIG. 9). As described above, in the two-phase conveyance of the refrigerant by the hydraulic pressure adjusting expansion valve 26, the refrigerant return pipe 41 and the refrigerant cooler 45 are used in order to maintain the liquid pipe temperature Tlp constant, and the compression is performed. The liquid injection pipe 46 is used to suppress the rise in the discharge temperature Td of the machine 21.

  Further, here, a liquid injection pipe 46 and a refrigerant return pipe 41 are connected to a suction refrigerant pipe 31 through which a refrigerant sucked into the compressor 21 flows. For this reason, here, since the refrigerant branched from the outdoor liquid refrigerant pipe 34 can be sent to the suction side of the compressor 21, the temperature of the refrigerant sucked into the compressor 21 can be lowered (point of FIG. 9). H, A). In particular, here, a liquid injection pipe 46 and a refrigerant return pipe 41 are connected to a portion of the suction refrigerant pipe 31 on the outlet side of the accumulator 29, and the refrigerant flowing through the liquid injection pipe 46 is compressed without going through the accumulator 29. The refrigerant can be merged with the refrigerant sucked into the machine 21. For this reason, here, compared with the case where the liquid injection pipe 46 and / or the refrigerant return pipe 41 are connected to the inlet side of the accumulator 29, the effect of reducing the temperature of the refrigerant sucked into the compressor 21 is improved. Can do.

<Modification 1>
In the air conditioner 1 of the second embodiment (see FIG. 8), the liquid injection pipe 46 and the refrigerant return pipe 41 are connected to the portion of the suction refrigerant pipe 31 on the outlet side of the accumulator 29. The effect of lowering the temperature of the refrigerant sucked into the compressor 21 is improved. However, the connection positions of the liquid injection pipe 46 and the refrigerant return pipe 41 to the suction refrigerant pipe 31 are not limited to this.

  Here, as shown in FIG. 10, a liquid injection pipe 46 and a refrigerant return pipe 41 are connected to a portion of the suction refrigerant pipe 34 on the inlet side of the accumulator 29, and the liquid injection pipe 46 is connected via the accumulator 29. The flowing refrigerant can be merged with the refrigerant sucked into the compressor 21. For this reason, compared with the case where the liquid injection pipe | tube 47 and the refrigerant | coolant return pipe | tube 41 are connected to the exit side of the accumulator 29 here, the liquid compression in the compressor 21 can be prevented, for example. In this configuration, a return pipe 31a for sending the refrigerant from the bottom of the accumulator 29 to a portion of the suction refrigerant pipe 31 on the outlet side of the accumulator 29 is provided, and the control unit 19 is provided with a return pipe provided in the return pipe 31a. The liquid refrigerant accumulated in the accumulator 29 may be returned to the compressor 21 by controlling the liquid valve 31b.

  Although not shown here, a liquid injection pipe 46 is connected to a portion of the suction refrigerant pipe 31 on the outlet side of the accumulator 29, and a refrigerant return pipe 41 is connected to a part of the suction refrigerant pipe 31 on the inlet side of the accumulator 29. May be connected. Further, the liquid injection pipe 46 may be connected to a portion of the suction refrigerant pipe 31 on the inlet side of the accumulator 29, and the refrigerant return pipe 41 may be connected to a part of the suction refrigerant pipe 31 on the outlet side of the accumulator 29. .

<Modification 2>
In the air conditioner 1 according to the second embodiment and the first modification (see FIGS. 8 and 10), the liquid injection pipe 46 is provided at the inlet side portion of the accumulator 29 or the outlet side portion of the accumulator 29 in the suction refrigerant pipe 31. And / or the refrigerant | coolant return pipe | tube 41 is connected. However, the connection position of the liquid injection pipe 46 and / or the refrigerant return pipe 41 to the suction refrigerant pipe 31 is not limited to these.

  Here, as shown in FIG. 11, the liquid injection pipe 46 is branched into two, and the liquid injection pipe 46 is provided in both the inlet side portion of the accumulator 29 and the outlet side portion of the accumulator 29 in the suction refrigerant pipe 31. Is connected. Here, the liquid injection pipe 46 connected to the outlet side portion of the accumulator 29 is referred to as a first liquid injection pipe 46a, and the liquid injection pipe 46 connected to the inlet side portion of the accumulator 29 is referred to as a second liquid. The injection tube 46b is used. Thus, here, when the liquid injection pipe 46 is connected to both the inlet side and the outlet side of the accumulator 29, when it is desired to improve the effect of reducing the temperature of the refrigerant sucked into the compressor 21, The refrigerant flowing through the liquid injection pipe 46 is sent to the outlet side of the accumulator 29. For example, when it is desired to prevent liquid compression in the compressor 21, the refrigerant flowing through the liquid injection pipe 46 may be sent to the inlet side of the accumulator 29. Good. Further, here, as shown in FIG. 12, the refrigerant return pipe 41 is branched into two, and the refrigerant return pipe 41 is supplied to both the inlet side portion of the accumulator 29 and the outlet side portion of the accumulator 29 in the intake refrigerant pipe 31. A tube 41 may be connected. Here, the refrigerant return pipe 41 connected to the outlet side portion of the accumulator 29 is the first refrigerant return pipe 41a, and the refrigerant return pipe 41 connected to the inlet side portion of the accumulator 29 is the second one. This is a refrigerant return pipe 41b.

  Further, the liquid injection pipe 46 of FIG. 11 is branched into two, and the liquid injection pipe 46 is connected to both the inlet side portion of the accumulator 29 and the outlet side portion of the accumulator 29 in the suction refrigerant pipe 31. By utilizing this, it is possible to suppress an increase in the discharge pressure Pd of the compressor 21. Specifically, a liquid drain valve 46d is provided in the second liquid injection pipe 46b connected to the inlet side portion of the accumulator 29 in the liquid injection pipe 46, and the discharge pressure Pd of the compressor 21 is set at a predetermined discharge level. The drain valve 46d is controlled so as not to exceed the pressure threshold Pdx (for example, the upper limit discharge pressure). Specifically, when the discharge pressure Pd rises to the discharge pressure threshold value Pdx, the control unit 19 performs control to open the drain valve 46d until the discharge pressure Pd becomes equal to or lower than the discharge pressure threshold value pdx. As a result, the liquid refrigerant existing in the outdoor heat exchanger 23 can be sent to the accumulator 29 through the liquid injection pipe 46, and as a result, an increase in the discharge pressure Pd can be suppressed. Thus, here, by controlling the drain valve 46d provided in the second liquid injection pipe 46b connected to the inlet side of the accumulator 29 in the liquid injection pipe 46, the outdoor liquid refrigerant is passed through the liquid injection pipe 46. Since the refrigerant can be sent from the pipe 34 to the accumulator 29, an increase in the discharge pressure Pd of the compressor 21 can be suppressed. In this configuration, a capillary tube 46c that provides flow resistance is provided in the first liquid injection pipe 46a so that a large amount of refrigerant can flow through the second liquid injection pipe 46b during the liquid drain control. Further, the refrigerant return pipe 41 of FIG. 12 is branched into two, and the refrigerant return pipe 41 is connected to both the inlet side portion of the accumulator 29 and the outlet side portion of the accumulator 29 in the suction refrigerant pipe 31. It may be used to suppress an increase in the discharge pressure Pd of the compressor 21. Specifically, as in the case of the liquid injection pipe 46, a liquid discharge valve 41d is provided in the second refrigerant return pipe 41b connected to the inlet side portion of the accumulator 29 in the refrigerant return pipe 41, and compression is performed. The drain valve 41d is controlled so that the discharge pressure Pd of the machine 21 does not exceed the discharge pressure threshold value Pdx. In this configuration as well, a capillary tube 41c serving as a flow resistance can be provided in the first refrigerant return pipe 41a so that a large amount of refrigerant can flow through the second refrigerant return pipe 41b during the liquid drain control. Good.

<Modification 3>
In the air conditioner 1 of the second embodiment (see FIG. 8), the refrigerant branched from the outdoor liquid refrigerant pipe 34 is supplied to the compressor 21 by connecting the liquid injection pipe 46 and the refrigerant return pipe 41 to the suction refrigerant pipe 31. So that the temperature of the refrigerant sucked into the compressor 21 is lowered (see points H and A in FIG. 2), and as a result, an increase in the discharge temperature Td of the compressor 21 is suppressed. I have to. However, the destination of the refrigerant flowing through the liquid injection pipe 46 and the refrigerant return pipe 41 to the compressor 21 is not limited to this.

  Here, as shown in FIG. 13, a refrigerant return pipe 41 may be connected to the middle part of the compression stroke of the compressor 21.

  In this configuration, as shown in FIGS. 13 and 14, the refrigerant branched from the outdoor liquid refrigerant pipe 34 to the refrigerant return pipe 41 is sent to an intermediate part of the compression stroke of the compressor 21, and is compressed to an intermediate pressure in the compressor 21. This is different from the second embodiment in that the temperature of the refrigerant is also lowered (see point K in FIG. 14). In this case as well, the control and the like of the hydraulic pressure adjusting expansion valve 26 for carrying out the two-phase conveyance of the refrigerant are the same as in the second embodiment, and the description thereof is omitted here.

  Further, as shown in FIG. 15, a liquid injection pipe 46 may be connected to an intermediate part of the compression stroke of the compressor 21.

  In this configuration, as shown in FIGS. 15 and 16, unlike the second embodiment (see points H and A in FIG. 9), the refrigerant branched from the outdoor liquid refrigerant pipe 34 to the liquid injection pipe 46 is compressed. 21. By suppressing the temperature of the refrigerant sent to the middle part of the compression stroke 21 and reduced to the intermediate pressure in the compressor 21 (see point L in FIG. 16), the increase in the discharge temperature Td of the compressor 21 can be suppressed. it can. In this case as well, the control and the like of the hydraulic pressure adjusting expansion valve 26 for carrying out the two-phase conveyance of the refrigerant are the same as in the second embodiment, and the description thereof is omitted here.

  Further, although not shown here, both of the refrigerant branched from the outdoor liquid refrigerant pipe 34 to the liquid injection pipe 46 and the refrigerant return pipe 41 are sent to the middle part of the compression stroke of the compressor 21 as in FIG. The temperature of the refrigerant compressed to the intermediate pressure in the compressor 21 may be lowered.

<Modification 4>
Also in the air conditioner 1 of Modification 3 (see FIG. 13) of the second embodiment, as in Modification 2 (see FIG. 11), as shown in FIG. The liquid injection pipe 46 may be connected to both the portion of the intake refrigerant pipe 31 on the inlet side of the accumulator 29 and the middle part of the compression stroke of the compressor 21. Here, one of the liquid injection pipes 46 connected to the middle part of the compression stroke of the compressor 21 is referred to as a first liquid injection pipe 46a, and one of the liquid injection pipes 46 connected to the inlet side portion of the accumulator 29 is first. A two-liquid injection tube 46b is used. Thus, here, by connecting the liquid injection pipe 46 to both the inlet side portion of the accumulator 29 and the middle portion of the compression stroke of the compressor 21 in the suction refrigerant pipe 31, the compressor 21 reaches the intermediate pressure. When it is desired to lower the temperature of the compressed refrigerant, the refrigerant flowing through the liquid injection pipe 46 is sent to the middle part of the compression stroke of the compressor 21. For example, when liquid compression in the compressor 21 is to be prevented, The refrigerant flowing through the injection pipe 46 can be sent to the inlet side of the accumulator. Further, here, as shown in FIG. 18, the refrigerant return pipe 41 is branched into two, both of the inlet refrigerant pipe 31 on the inlet side of the accumulator 29 and the middle part of the compression stroke of the compressor 21. A refrigerant return pipe 41 may be connected. Here, the refrigerant return pipe 41 connected to the outlet side portion of the accumulator 29 is the first refrigerant return pipe 41a, and the refrigerant return pipe 41 connected to the inlet side portion of the accumulator 29 is the second one. This is a refrigerant return pipe 41b.

  Further, the liquid injection pipe 46 of FIG. 17 is branched into two, and the liquid injection pipe 46 is connected to both the inlet side portion of the accumulator 29 and the midway portion of the compression stroke of the compressor 21 in the suction refrigerant pipe 31. By using the configuration, it is possible to suppress an increase in the discharge pressure Pd of the compressor 21. Specifically, a liquid drain valve 46d is provided in the second liquid injection pipe 46b connected to the inlet side portion of the accumulator 29 in the liquid injection pipe 46, and the discharge pressure Pd of the compressor 21 is set at a predetermined discharge level. The drain valve 46d is controlled so as not to exceed the pressure threshold Pdx (for example, the upper limit discharge pressure). Specifically, when the discharge pressure Pd rises to the discharge pressure threshold value Pdx, the control unit 19 performs control to open the drain valve 46d until the discharge pressure Pd becomes equal to or lower than the discharge pressure threshold value pdx. As a result, the liquid refrigerant existing in the outdoor heat exchanger 23 can be sent to the accumulator 29 through the liquid injection pipe 46, and as a result, an increase in the discharge pressure Pd can be suppressed. Thus, here, by controlling the drain valve 46d provided in the second liquid injection pipe 46b connected to the inlet side of the accumulator 29 in the liquid injection pipe 46, the outdoor liquid refrigerant is passed through the liquid injection pipe 46. Since the refrigerant can be sent from the pipe 34 to the accumulator 29, an increase in the discharge pressure Pd of the compressor 21 can be suppressed. Further, the refrigerant return pipe 41 of FIG. 18 is branched into two, and the refrigerant return pipe 41 is connected to both the inlet side portion of the accumulator 29 and the middle portion of the compression stroke of the compressor 21 in the intake refrigerant tube 31. You may make it suppress the raise of the discharge pressure Pd of the compressor 21 using a structure. Specifically, as in the case of the liquid injection pipe 46, a liquid discharge valve 41d is provided in the second refrigerant return pipe 41b connected to the inlet side portion of the accumulator 29 in the refrigerant return pipe 41, and compression is performed. The drain valve 41d is controlled so that the discharge pressure Pd of the machine 21 does not exceed the discharge pressure threshold value Pdx.

(3) Third Embodiment <Configuration>
FIG. 19 is a schematic configuration diagram of an air-conditioning apparatus 1 according to the third embodiment of the present invention. The air conditioner 1 is an apparatus that cools or heats a room such as a building by a vapor compression refrigeration cycle. The air conditioner 1 mainly includes an outdoor unit 2, a plurality of (in this case, four) indoor units 3a, 3b, 3c, and 3d that are connected in parallel to each other, and the indoor units 3a, 3b, 3c, and 3d. And the refrigerant communication pipes 5, 6 that connect the outdoor unit 2 and the indoor units 3a, 3b, 3c, 3d via the relay units 4a, 4b, 4c, 4d. And a control unit 19 that controls the components of the outdoor unit 2, the indoor units 3a, 3b, 3c, and 3d and the relay units 4a, 4b, 4c, and 4d. The vapor compression refrigerant circuit 10 of the air conditioner 1 includes an outdoor unit 2, indoor units 3a, 3b, 3c, and 3d, relay units 4a, 4b, 4c, and 4d, and refrigerant communication tubes 5 and 6. Is configured by being connected. The refrigerant circuit 10 is filled with a refrigerant such as R32. In the air conditioner 1, the indoor units 3a, 3b, 3c, and 3d can individually perform the cooling operation or the heating operation by the relay units 4a, 4b, 4c, and 4d, and perform the heating operation. Heat can be recovered between the indoor units by sending a refrigerant from the indoor unit to the indoor unit that performs the cooling operation (here, simultaneous cooling and heating operation in which the cooling operation and the heating operation are performed simultaneously) is possible. It is configured.

-Refrigerant communication pipe-
The liquid refrigerant communication pipe 5 mainly includes a merging pipe portion extending from the outdoor unit 2 and first branch pipe portions 5a and 5b branched into a plurality (four in this case) before the relay units 4a, 4b, 4c and 4d. 5c, 5d, and second branch pipe portions 5aa, 5bb, 5cc, 5dd that connect the relay units 4a, 4b, 4c, 4d and the indoor units 3a, 3b, 3c, 3d.
The gas refrigerant communication pipe 6 mainly connects the high and low pressure gas refrigerant communication pipe 7, the low pressure gas refrigerant communication pipe 8, the relay units 4a, 4b, 4c and 4d and the indoor units 3a, 3b, 3c and 3d. Branch pipe parts 6a, 6b, 6c, 6d. The high and low pressure gas refrigerant communication pipe 7 includes a merging pipe portion extending from the outdoor unit 2 and branch pipe portions 7a, 7b, 7c branched into a plurality (four in this case) before the relay units 4a, 4b, 4c, 4d. , 7d. The low-pressure gas refrigerant communication pipe 8 includes a merging pipe portion extending from the outdoor unit 2 and branch pipe portions 8a, 8b, 8c branched into a plurality (here, four) before the relay units 4a, 4b, 4c, and 4d. 8d.

-Indoor unit-
The indoor units 3a, 3b, 3c, and 3d are installed in a room such as a building. As described above, the indoor units 3a, 3b, 3c, and 3d include the liquid refrigerant communication pipe 5, the gas refrigerant communication pipe 6 (the high and low pressure gas refrigerant communication pipe 7, the low pressure gas refrigerant communication pipe 8, and the branch pipe portions 6a, 6b, 6c, 6d) and the relay unit 4a, 4b, 4c, 4d are connected to the outdoor unit 2 and constitute a part of the refrigerant circuit 10.

  In addition, since the structure of indoor unit 3a, 3b, 3c, 3d is the same structure as the indoor unit 3a, 3b of 1st and 2nd embodiment, description is abbreviate | omitted here.

-Relay unit-
The relay units 4a, 4b, 4c, and 4d are installed together with the indoor units 3a, 3b, 3c, and 3d in a room such as a building. The relay units 4a, 4b, 4c, and 4d have the liquid refrigerant communication pipe 5 and the gas refrigerant communication pipe 6 (the high and low pressure gas refrigerant communication pipe 7, the low pressure gas refrigerant communication pipe 8, and the branch pipe portions 6a, 6b, 6c, and 6d). These are interposed between the indoor units 3a, 3b, 3c, 3d and the outdoor unit 2, and constitute a part of the refrigerant circuit 10.

  Next, the configuration of the relay units 4a, 4b, 4c, and 4d will be described. Since the relay unit 4a and the relay units 4b, 4c, and 4d have the same configuration, only the configuration of the relay unit 4a will be described here, and the configurations of the relay units 4b, 4c, and 4d will be described respectively. In place of the subscript “a” indicating the respective parts of 4a, the subscript “b”, “c” or “d” is attached, and the description of each part is omitted.

  The relay unit 4a mainly has a liquid connection pipe 61a and a gas connection pipe 62a.

  One end of the liquid connection pipe 61 a is connected to the first branch pipe part 5 a of the liquid refrigerant communication pipe 5, and the other end is connected to the second branch pipe part 5 aa of the liquid refrigerant communication pipe 5.

  The gas connection pipe 62a includes a high pressure gas connection pipe 63a connected to the branch pipe section 7a of the high and low pressure gas refrigerant communication pipe 7, and a low pressure gas connection pipe 64a connected to the branch pipe section 8a of the low pressure gas refrigerant communication pipe 8. The high-pressure gas connection pipe 63a and the low-pressure gas connection pipe 64a are joined together. The merged gas connection pipe 65 a is connected to the branch pipe part 6 a of the gas refrigerant communication pipe 6. The high pressure gas connection pipe 63a is provided with a high pressure gas valve 66a, and the low pressure gas connection pipe 64a is provided with a low pressure gas valve 67a. Here, the high-pressure gas valve 66a and the low-pressure gas valve 67a are electric expansion valves.

  The relay unit 4a flows into the liquid connection pipe 61a through the first branch pipe portion 5a of the liquid refrigerant communication pipe 5 with the low pressure gas valve 67a opened when the indoor unit 3a performs the cooling operation. The refrigerant is sent to the indoor unit 3a through the second branch pipe portion 5aa of the liquid refrigerant communication pipe 5, and then the refrigerant evaporated by heat exchange with the indoor air in the indoor heat exchanger 52a is supplied to the branch pipe of the gas refrigerant communication pipe 6. It can function to return to the branch pipe part 8a of the low-pressure gas refrigerant communication pipe 8 through the part 6a, the merged gas connection pipe 65a and the low-pressure gas connection pipe 64a. In addition, the relay unit 4a closes the low-pressure gas valve 67a and opens the high-pressure gas valve 66a when the indoor unit 3a performs the heating operation, and opens the branch pipe of the high-low pressure gas refrigerant communication pipe 7. The refrigerant flowing into the high-pressure gas connection pipe 63a and the merged gas connection pipe 65a through the section 7a is sent to the indoor unit 3a through the branch pipe section 6a of the gas refrigerant communication pipe 6, and then heated with the indoor air in the indoor heat exchanger 52a. The refrigerant radiated by the exchange can function to return to the first branch pipe part 5a of the liquid refrigerant communication pipe 5 through the second branch pipe part 5aa and the liquid connection pipe 61a of the liquid refrigerant communication pipe 5. Since this function has not only the relay unit 4a but also the relay units 4b, 4c, and 4d, the indoor heat exchangers 52a, 52b, 52c, and 52d are connected by the relay units 4a, 4b, 4c, and 4d. It is possible to switch individually to function as a refrigerant evaporator or radiator.

-Outdoor unit-
The outdoor unit 2 is installed outside a building or the like. As described above, the outdoor unit 2 includes the liquid refrigerant communication pipe 5, the gas refrigerant communication pipe 6 (the high and low pressure gas refrigerant communication pipe 7, the low pressure gas refrigerant communication pipe 8, and the branch pipe portions 6a, 6b, 6c, and 6d) and the relay. It is connected to the indoor units 3a, 3b, 3c, and 3d via the units 4a, 4b, 4c, and 4d, and constitutes a part of the refrigerant circuit 10.

  The outdoor unit 2 mainly includes a compressor 21 and a plurality (here, two) of outdoor heat exchangers 23a and 23b. The outdoor unit 2 has a heat radiation operation state in which each outdoor heat exchanger 23a, 23b functions as a refrigerant radiator, and an evaporation operation state in which each outdoor heat exchanger 23a, 23b functions as a refrigerant evaporator. Switching mechanisms 22a and 22b for switching are provided. The switching mechanisms 22 a and 22 b and the suction side of the compressor 21 are connected by a suction refrigerant pipe 31. The suction refrigerant pipe 31 is provided with an accumulator 29 for temporarily storing the refrigerant sucked into the compressor 21. The discharge side of the compressor 21 and the switching mechanisms 22 a and 2 b are connected by a discharge refrigerant pipe 32. The switching mechanism 22a and the gas side ends of the outdoor heat exchangers 23a and 23b are connected by first outdoor gas refrigerant tubes 33a and 33b. The liquid side ends of the outdoor heat exchangers 23 a and 23 b and the liquid refrigerant communication tube 5 are connected by an outdoor liquid refrigerant tube 34. A liquid side shut-off valve 27 is provided at a connection portion between the outdoor liquid refrigerant pipe 34 and the liquid refrigerant communication pipe 5. Further, the outdoor unit 2 is in a refrigerant derivation state in which the refrigerant discharged from the compressor 21 is sent to the high / low pressure gas refrigerant communication pipe 7 and a refrigerant introduction state in which the refrigerant flowing through the high / low pressure gas refrigerant communication pipe 7 is sent to the suction refrigerant pipe 31. And a third switching mechanism 22c for switching between. The third switching mechanism 22c and the high / low pressure gas refrigerant communication pipe 7 are connected by a second outdoor gas refrigerant pipe 35. The third switching mechanism 22c and the suction side of the compressor 21 are connected by a suction refrigerant pipe 31. The discharge side of the compressor 21 and the third switching mechanism 22 c are connected by a discharge refrigerant pipe 32. A high / low pressure gas side shut-off valve 28a is provided at a connection portion between the second outdoor gas refrigerant pipe 35 and the high / low pressure gas refrigerant communication pipe 7. The suction refrigerant pipe 31 is connected to the low-pressure gas refrigerant communication pipe 8. A low-pressure gas side shut-off valve 28b is provided at a connection portion between the suction refrigerant pipe 31 and the low-pressure gas refrigerant communication pipe 8. The liquid side closing valve 27 and the gas side closing valves 28a, 28b are valves that are manually opened and closed.

  The compressor 21 is a device for compressing a refrigerant. For example, the compressor 21 has a hermetic structure in which a rotary type or scroll type positive displacement compression element (not shown) is rotationally driven by a compressor motor 21a. Machine is used.

  When the first switching mechanism 22a causes the first outdoor heat exchanger 23a to function as a refrigerant radiator (hereinafter referred to as "outdoor heat dissipation state"), the first switching mechanism 22a and the first outdoor heat exchanger 23a (Refer to the solid line of the first switching mechanism 22a in FIG. 19) and the first outdoor heat exchanger 23a functions as a refrigerant evaporator (hereinafter referred to as "outdoor evaporation state"). Switches the refrigerant flow in the refrigerant circuit 10 so as to connect the suction side of the compressor 21 and the gas side of the first outdoor heat exchanger 23a (see the broken line of the first switching mechanism 22a in FIG. 19). For example, a four-way switching valve. In addition, the second switching mechanism 22b allows the second outdoor heat exchanger 23b to function as a refrigerant radiator (hereinafter referred to as “outdoor heat dissipation state”) and the second outdoor heat exchange with the discharge side of the compressor 21. When connecting the gas side of the cooler 23b (see the solid line of the second switching mechanism 22b in FIG. 19) and causing the second outdoor heat exchanger 23b to function as a refrigerant evaporator (hereinafter referred to as “outdoor evaporation state”). ), The refrigerant flow in the refrigerant circuit 10 is changed so that the suction side of the compressor 21 and the gas side of the second outdoor heat exchanger 23b are connected (see the broken line of the second switching mechanism 22b in FIG. 19). This is a device that can be switched, and is composed of, for example, a four-way switching valve. By changing the switching state of the switching mechanisms 22a and 22b, the outdoor heat exchangers 23a and 23b can be switched to function individually as refrigerant evaporators or radiators.

  The first outdoor heat exchanger 23a is a heat exchanger that functions as a refrigerant radiator or a refrigerant evaporator. The second outdoor heat exchanger 23b is a heat exchanger that functions as a refrigerant radiator or a refrigerant evaporator. Here, the outdoor unit 2 has an outdoor fan 24 for sucking outdoor air into the outdoor unit 2 and exchanging heat with the refrigerant in the outdoor heat exchangers 23a and 23b, and then discharging the air to the outside. . That is, the outdoor unit 2 has the outdoor fan 24 as a fan which supplies the outdoor air as a cooling source or heating source of the refrigerant | coolant which flows through the outdoor heat exchangers 23a and 23b to the outdoor heat exchangers 23a and 23b. Here, the outdoor fan 24 is driven by an outdoor fan motor 24a.

  When the refrigerant discharged from the compressor 21 is sent to the high / low pressure gas refrigerant communication pipe 7 (hereinafter referred to as “refrigerant derivation state”), the third switching mechanism 23c is connected to the discharge side of the compressor 21 and the high / low pressure gas refrigerant. When connecting the connecting pipe 7 (see the broken line of the third switching mechanism 22c in FIG. 19) and sending the refrigerant flowing through the high and low pressure gas refrigerant connecting pipe 7 to the suction refrigerant pipe 31 (hereinafter referred to as “refrigerant introduction state”). ), The refrigerant flow in the refrigerant circuit 10 can be switched so that the suction side of the compressor 21 and the high / low pressure gas refrigerant communication pipe 7 are connected (see the solid line of the third switching mechanism 22c in FIG. 19). For example, a four-way switching valve.

  And in the air conditioning apparatus 1, when paying attention only to the compressor 21, the outdoor heat exchangers 23a and 23b, the liquid refrigerant communication pipe 5, and the indoor heat exchangers 52a, 52b, 52c, and 52d, the air is discharged from the compressor 21. The refrigerant is supplied in the order of the outdoor heat exchanger 23, the liquid refrigerant communication tube 5, the indoor heat exchangers 52a, 52b, 52c, and 52d (all cooling operation and cooling main operation). Here, the cooling only operation means an operation state in which only the indoor heat exchanger functioning as the refrigerant evaporator exists, and the cooling main operation means the indoor heat exchange functioning as the refrigerant evaporator. Both the heat exchanger and the indoor heat exchanger functioning as a refrigerant radiator are mixed, but as a whole, it means that the load on the evaporation side is large. Further, in the air conditioner 1, when focusing only on the compressor 21, the gas refrigerant communication pipe 6, the indoor heat exchangers 52a, 52b, 52c, 52d, the liquid refrigerant communication pipe 5, and the outdoor heat exchangers 23a, 23b, Operation for flowing the refrigerant discharged from the compressor 21 in the order of the gas refrigerant communication tube 6, the indoor heat exchangers 52a, 52b, 52c, 52d, the liquid refrigerant communication tube 5, and the outdoor heat exchangers 23a, 23b (all heating operation and heating) (Main driving). Here, the all-heating operation means an operation state in which only an indoor heat exchanger functioning as a refrigerant radiator exists, and the heating-main operation means an indoor heat exchange functioning as a refrigerant evaporator. Both the heat exchanger and the indoor heat exchanger functioning as a refrigerant radiator are mixed, which means that the load on the heat radiation side is large as a whole. Here, at the time of the cooling only operation or the cooling main operation, at least one of the switching mechanisms 22a and 22b is switched to the outdoor heat dissipation state, and the outdoor heat exchangers 23a and 23b as a whole function as a refrigerant radiator. The refrigerant flows through the refrigerant communication pipe 5 from the outdoor unit 2 side to the indoor units 3a, 3b, 3c, and 3d side. Further, at the time of the all heating operation and the heating main operation, at least one of the switching mechanisms 22a and 22b is switched to the outdoor evaporation state, and the third switching mechanism 22c is switched to the refrigerant discharge state, and the outdoor heat exchangers 23a and 23b. As a whole, it functions as a refrigerant evaporator, and the refrigerant flows from the indoor unit 3a, 3b, 3c, 3d side to the outdoor unit 2 side through the liquid refrigerant communication tube 5.

  Here, as in the outdoor unit 2 of the second embodiment, the outdoor liquid refrigerant pipe 34 is provided with a liquid pressure adjusting expansion valve 26, a liquid injection pipe 46, a refrigerant return pipe 41, and a refrigerant cooler 45. . The configurations of the hydraulic pressure adjusting expansion valve 26, the liquid injection pipe 46, the refrigerant return pipe 41, and the refrigerant cooler 45 are the same as those in the second embodiment, and thus the description thereof is omitted here.

-Control unit-
The control unit 19 is configured by communication connection of a control board or the like (not shown) provided in the outdoor unit 2, the indoor units 3a, 3b, 3c, and 3d, and the relay units 4a, 4b, 4c, and 4d. Yes. In FIG. 19, for convenience, the outdoor unit 2, the indoor units 3a and 3b, and the relay units 4a, 4b, 4c, and 4d are illustrated at positions away from each other. Based on the detection signals of the various sensors 36, 37, 38, 39, 40, 49, 57a to 57d, 58a to 58d, and 59a to 59d as described above, the control unit 19 (here, the outdoor unit) Unit 2, indoor units 3 a, 3 b, 3 c, 3 d and relay units 4 a, 4 b, 4 c, 4 d), 21, 22 a to 22 c, 24, 25 a, 25 b, 26, 41, 47, 51 a to 51 d, 55 a Control of -55d, 66a-66d, 67a-67d, ie, operation control of the air conditioning apparatus 1 whole is performed.

<Operation and features of air conditioner>
Next, operation | movement and the characteristic of the air conditioning apparatus 1 are demonstrated using FIG.19 and FIG.9.

In the air conditioner 1, as described above, the cooling only operation, the cooling main operation, the heating only operation, and the heating main operation are performed. In the cooling only operation and the cooling main operation, the gas-liquid two-phase refrigerant is converted into the liquid refrigerant by the liquid pressure adjusting expansion valve 26 provided in the outdoor liquid refrigerant pipe 34 as in the first and second embodiments. Two-phase conveyance of the refrigerant that flows through the communication pipe 5 and is sent from the outdoor unit 2 side to the indoor units 3a, 3b, 3c, and 3d side is performed. Further, in the cooling only operation and the cooling main operation, a part of the refrigerant flowing through the outdoor liquid refrigerant pipe 34 is branched and sent to the compressor 21, and the outdoor liquid refrigerant is supplied by the refrigerant flowing through the refrigerant return pipe 41. The refrigerant cooler 45 and the liquid pressure adjusting expansion valve 26 in the outdoor liquid refrigerant pipe 34 are cooled by the refrigerant cooler 45 that cools the refrigerant flowing in the portion closer to the outdoor heat exchanger 23 than the liquid pressure adjusting expansion valve 26. The operation of cooling the refrigerant in the portion between is performed. Further, in the cooling only operation and the cooling main operation, a part of the refrigerant flowing through the outdoor liquid refrigerant pipe 34 is branched to a part of the outdoor liquid refrigerant pipe 34 closer to the outdoor heat exchanger 23 than the liquid pressure adjusting expansion valve 26. The operation of sending the refrigerant to the compressor 21 while suppressing the fluctuation of the temperature of the refrigerant flowing in the outdoor liquid refrigerant pipe 34 (liquid pipe temperature Tlp) by the liquid injection pipe 46 sent to the compressor 21 without passing through the heat exchanger. Done. In addition, operation | movement of the air conditioning apparatus 1 is performed by the control part 19 which controls the component apparatus of the air conditioning apparatus 1. FIG. In the following description, the cooling only operation will be described on behalf of the operation involving the control of the hydraulic pressure adjusting expansion valve 26 and the like, and the description of the cooling main operation will be omitted.

  In the cooling only operation, for example, all of the indoor units 3a, 3b, 3c, and 3d are in the cooling operation (that is, all of the indoor heat exchangers 52a, 52b, 52c, and 52d function as a refrigerant evaporator, and the outdoor unit When performing the operation in which the heat exchangers 23a and 23b function as a refrigerant radiator), the switching mechanisms 22a and 22b are switched to the outdoor heat radiation state (the state indicated by the solid lines of the switching mechanisms 22a and 22b in FIG. 19). Thus, the compressor 21, the outdoor fan 24, and the indoor fans 55a and 55b are driven. Further, the third switching mechanism 22c is switched to the refrigerant introduction state (the state indicated by the solid line of the switching mechanism 22c in FIG. 19), and the high pressure gas valves 66a, 66b, 66c, 66d of the relay units 4a, 4b, 4c, 4d. And the low pressure gas valves 67a, 67b, 67c, 67d are opened.

  Then, the high-pressure refrigerant discharged from the compressor 21 is sent to the outdoor heat exchangers 23a and 23b through the switching mechanisms 22a and 22b (see point B in FIGS. 19 and 9). The refrigerant sent to the outdoor heat exchangers 23a and 23b is cooled by exchanging heat with outdoor air supplied by the outdoor fan 24 in the outdoor heat exchangers 23a and 23b functioning as a refrigerant radiator. Condensation (see point C in FIGS. 19 and 9). This refrigerant flows out of the outdoor unit 2 through the outdoor expansion valves 25a and 25b, the refrigerant cooler 45, the liquid pressure adjusting expansion valve 26, and the liquid side closing valve 27 (see point D in FIGS. 19 and 9).

  The refrigerant flowing out of the outdoor unit 2 is branched and sent to the indoor units 3a, 3b, 3c, and 3d through the liquid refrigerant communication tube 5 and the relay units 4a, 4b, 4c, and 4d (see point E in FIGS. 19 and 9). . The refrigerant sent to the indoor units 3a, 3b, 3c, and 3d is depressurized to a low pressure by the indoor expansion valves 51a, 51b, 51c, and 51d, and then sent to the indoor heat exchangers 52a, 52b, 52c, and 52d (see FIG. 19 and 9 (see point F). The refrigerant sent to the indoor heat exchangers 52a, 52b, 52c, and 52d is supplied indoors by indoor fans 55a and 55b in the indoor heat exchangers 52a, 52b, 52c, and 52d that function as refrigerant evaporators. It evaporates when heated by exchanging heat with air (see point G in FIGS. 19 and 9). This refrigerant flows out of the indoor units 3a, 3b, 3c, and 3d. On the other hand, the indoor air cooled in the indoor heat exchangers 52a, 52b, 52c, and 52d is sent into the room, thereby cooling the room.

  The refrigerant that has flowed out of the indoor units 3a, 3b, 3c, and 3d joins and is sent to the outdoor unit 2 through the gas refrigerant communication pipe 6 and the relay units 4a, 4b, 4c, and 4d (see point H in FIGS. 19 and 9). . The refrigerant sent to the outdoor unit 2 is sucked into the compressor 21 through the gas side closing valve 28 and the accumulator 29 (see point A in FIGS. 19 and 9).

  Here, at the time of the above-described cooling only operation, the gas-liquid two-phase refrigerant is transferred to the liquid refrigerant communication tube 5 by the hydraulic pressure adjusting expansion valve 26 as in the cooling operation of the first and second embodiments. The two-phase conveyance of the refrigerant that is sent to the indoor units 3a, 3b, 3c, and 3d from the outdoor unit 2 side is performed. In addition, when carrying out the two-phase conveyance of the refrigerant, the refrigerant flowing through the outdoor liquid refrigerant pipe 34 is cooled by the refrigerant return pipe 41 and the refrigerant cooler 45 as in the cooling operation of the second embodiment, and liquid injection is performed. The pipe 46 makes it possible to satisfactorily carry out the two-phase conveyance of the refrigerant while suppressing an increase in the discharge temperature Td of the compressor 21. The details of this operation are the same as the operation and control related to the two-phase refrigerant transport in the cooling operation of the second embodiment, and thus the description thereof is omitted here. In the cooling main operation, the operation and control related to the two-phase refrigerant transport are the same as in the cooling only operation.

<Modification>
In the air conditioner 1 of the third embodiment (see FIG. 19), the liquid injection pipe 46 and the refrigerant return pipe 41 are connected to the portion of the suction refrigerant pipe 31 on the outlet side of the accumulator 29. However, the connection positions of the liquid injection pipe 46 and the refrigerant return pipe 41 may be devised similarly to the second embodiment and the first to fourth modifications.

  Moreover, in the air conditioning apparatus 1 of the said 3rd Embodiment (refer FIG. 19), although it has the refrigerant | coolant return pipe 41 and the refrigerant | coolant cooler 45, it is not limited to this, 1st Embodiment and Similarly to the first to fourth modifications, a configuration without the refrigerant return pipe 41 and the refrigerant cooler 45 may be adopted.

(4) Other embodiments <A>
In the air conditioner 1 of the second and third embodiments and the modified example, the liquid injection pipe 46 is connected to a part of the outdoor liquid refrigerant pipe 34 between the refrigerant cooler 45 and the liquid pressure adjusting expansion valve 26. However, it is not limited to this.

  For example, as shown in FIG. 20, the liquid injection pipe 46 may be connected to a position closer to the outdoor heat exchanger 23 than the branch position of the refrigerant return pipe 41 in the outdoor liquid refrigerant pipe 34. Further, as shown in FIG. 21, the liquid injection pipe 46 may be connected to a position between the branch position of the refrigerant return pipe 41 and the refrigerant cooler 45 in the outdoor liquid refrigerant pipe 34.

<B>
In the air conditioning apparatus 1 according to the second and third embodiments and the modified example, the refrigerant cooler 45 is a refrigerant that flows through the refrigerant return pipe 41 during the cooling operation (the same as the cooling only operation or the cooling main operation). The heat exchanger is of a type in which the refrigerant flowing through the outdoor liquid refrigerant pipe 34 is opposed to the refrigerant, and the refrigerant return pipe 41 is branched from a position upstream of the refrigerant cooler 45 in the outdoor liquid refrigerant pipe 34. However, the present invention is not limited to this.

  For example, as shown in FIG. 22, when the refrigerant cooler 45 is in a cooling operation (same as all cooling operation and cooling main operation), the refrigerant flowing through the refrigerant return pipe 41 and the refrigerant flowing through the outdoor liquid refrigerant pipe 34 are separated. The heat exchanger may be of a parallel flow type, and the refrigerant return pipe 41 may be branched from a position upstream of the refrigerant cooler 45 in the outdoor liquid refrigerant pipe 34. Further, as shown in FIG. 23, when the refrigerant cooler 45 is in the cooling operation (the same is the case with all cooling operation and cooling main operation), the refrigerant flowing through the refrigerant return pipe 41 and the refrigerant flowing through the outdoor liquid refrigerant pipe 34 are separated. The refrigerant return pipe 41 may be branched from a position downstream of the refrigerant cooler 45 in the outdoor liquid refrigerant pipe 34. Also. As shown in FIG. 24, when the refrigerant cooler 45 is in a cooling operation (same as all cooling operation and cooling main operation), the refrigerant flowing through the refrigerant return pipe 41 and the refrigerant flowing through the outdoor liquid refrigerant pipe 34 are in parallel flow. The refrigerant return pipe 41 may be branched from a position downstream of the refrigerant cooler 45 in the outdoor liquid refrigerant pipe 34.

<C>
The air conditioner 1 according to the first and second embodiments and the modified example has a configuration capable of switching between the cooling operation and the heating operation, but is not limited thereto, and only the cooling operation can be performed. It may be an air conditioning apparatus dedicated to cooling that is possible.

  The present invention includes an outdoor unit having a compressor and an outdoor heat exchanger, a plurality of indoor units having an indoor heat exchanger, and a liquid refrigerant communication tube connecting the outdoor unit and the plurality of indoor units. A liquid pressure adjusting expansion that decompresses the refrigerant so that the refrigerant flowing through the liquid refrigerant communication tube is in a gas-liquid two-phase state to the outdoor liquid refrigerant tube connecting the liquid side end of the outdoor heat exchanger and the liquid refrigerant communication tube. The present invention can be widely applied to an air conditioner provided with a valve.

DESCRIPTION OF SYMBOLS 1 Air conditioning apparatus 2 Outdoor unit 3a, 3b, 3c, 3d Indoor unit 5 Liquid refrigerant communication pipe 19 Control part 21 Compressor 23, 23a, 23b Outdoor heat exchanger 26 Hydraulic pressure adjustment expansion valve 29 Accumulator 31 Intake refrigerant pipe 34 Outdoor Liquid refrigerant pipe 41 Refrigerant return pipe 41d Liquid discharge valve 44 Refrigerant return expansion valve 45 Refrigerant cooler 46 Liquid injection pipe 46d Liquid discharge valve 47 Liquid injection expansion valve 52a, 52b, 52c, 52d Indoor heat exchanger

International Publication No. 2015/029160

Claims (9)

An outdoor unit (2) having a compressor (21) and outdoor heat exchangers (23, 23a, 23b) and a plurality of indoor units (3a, 3b, having an indoor heat exchanger (52a, 52b, 52c, 52d) 3c, 3d), and a liquid refrigerant communication pipe (5) connecting the outdoor unit and the plurality of indoor units, and the refrigerant discharged from the compressor is used as the outdoor heat exchanger, In the air conditioner that performs the operation of flowing the liquid refrigerant communication tube and the indoor heat exchanger in this order,
Liquid that reduces the pressure of the refrigerant flowing through the liquid refrigerant communication tube to a gas-liquid two-phase state in an outdoor liquid refrigerant tube (34) that connects the liquid side end of the outdoor heat exchanger and the liquid refrigerant communication tube. A pressure regulating expansion valve (26) is provided;
In correspondence with each of the plurality of indoor units, provided are indoor expansion valves (51a, 51b) for further decompressing the refrigerant in a gas-liquid two-phase state flowing through the liquid refrigerant communication pipe,
A part of the refrigerant flowing through the outdoor liquid refrigerant pipe is branched to the portion of the outdoor liquid refrigerant pipe that is closer to the outdoor heat exchanger than the liquid pressure adjusting expansion valve, and the compression is performed without passing through the heat exchanger. Connect the liquid injection pipe (46) to the machine ,
The liquid injection pipe is connected to a suction refrigerant pipe (31) through which the refrigerant sucked into the compressor flows,
An accumulator (29) for temporarily storing the refrigerant is provided in the suction refrigerant pipe,
Branching the liquid injection pipe into two,
The liquid injection pipe is connected to both the inlet side portion of the accumulator and the outlet side portion of the accumulator of the suction refrigerant pipe .
Air conditioner (1). An outdoor unit (2) having a compressor (21) and outdoor heat exchangers (23, 23a, 23b) and a plurality of indoor units (3a, 3b, having an indoor heat exchanger (52a, 52b, 52c, 52d) 3c, 3d), and a liquid refrigerant communication pipe (5) connecting the outdoor unit and the plurality of indoor units, and the refrigerant discharged from the compressor is used as the outdoor heat exchanger, In the air conditioner that performs the operation of flowing the liquid refrigerant communication tube and the indoor heat exchanger in this order,
Liquid that reduces the pressure of the refrigerant flowing through the liquid refrigerant communication tube to a gas-liquid two-phase state in an outdoor liquid refrigerant tube (34) that connects the liquid side end of the outdoor heat exchanger and the liquid refrigerant communication tube. A pressure regulating expansion valve (26) is provided;
In correspondence with each of the plurality of indoor units, provided are indoor expansion valves (51a, 51b) for further decompressing the refrigerant in a gas-liquid two-phase state flowing through the liquid refrigerant communication pipe,
A part of the refrigerant flowing through the outdoor liquid refrigerant pipe is branched to the portion of the outdoor liquid refrigerant pipe that is closer to the outdoor heat exchanger than the liquid pressure adjusting expansion valve, and the compression is performed without passing through the heat exchanger. Connect the liquid injection pipe (46) to the machine ,
A refrigerant return pipe (41) for branching a part of the refrigerant flowing through the outdoor liquid refrigerant pipe and sending it to the compressor is connected to the outdoor liquid refrigerant pipe, and the outdoor liquid refrigerant pipe is connected to the outdoor liquid refrigerant pipe by the refrigerant flowing through the refrigerant return pipe. A refrigerant cooler (45) is provided for cooling the refrigerant flowing in the portion closer to the outdoor heat exchanger than the liquid pressure adjusting expansion valve in the liquid refrigerant pipe .
Air conditioner. The liquid injection pipe and / or the refrigerant return pipe are connected to a suction refrigerant pipe (31) through which the refrigerant sucked into the compressor flows.
The air conditioning apparatus according to claim 2 . An accumulator (29) for temporarily storing the refrigerant is provided in the suction refrigerant pipe,
The liquid injection pipe and / or the refrigerant return pipe are connected to a part of the suction refrigerant pipe on the outlet side of the accumulator,
The air conditioning apparatus according to claim 3 . An accumulator (29) for temporarily storing the refrigerant is provided in the suction refrigerant pipe,
The liquid injection pipe and / or the refrigerant return pipe are connected to the inlet side portion of the accumulator of the suction refrigerant pipe.
The air conditioning apparatus according to claim 3 . An accumulator (29) for temporarily storing the refrigerant is provided in the suction refrigerant pipe,
Branching the liquid injection pipe or the refrigerant return pipe into two;
The liquid injection pipe or the refrigerant return pipe is connected to both the inlet side portion of the accumulator and the outlet side portion of the accumulator of the suction refrigerant pipe.
The air conditioning apparatus according to claim 3 . The liquid injection pipe and / or the refrigerant return pipe are connected to the middle part of the compression stroke of the compressor,
The air conditioning apparatus according to claim 2 . An accumulator (29) for temporarily storing the refrigerant is provided in an intake refrigerant pipe (31) through which the refrigerant sucked into the compressor flows,
Branching the liquid injection pipe or the refrigerant return pipe into two;
The liquid injection pipe or the refrigerant return pipe is connected to both the inlet side portion of the accumulator and the middle portion of the compressor in the compression stroke of the suction refrigerant pipe.
The air conditioning apparatus according to claim 7 . The liquid injection pipe is provided with a liquid injection expansion valve (47) for depressurizing the refrigerant branched from the outdoor liquid refrigerant pipe,
The control unit (19) that controls the outdoor unit and the constituent devices of the indoor unit opens the liquid injection expansion valve so that the temperature of the refrigerant discharged from the compressor does not exceed a predetermined discharge temperature threshold. Control the degree,
The air conditioning apparatus according to claim 1 .

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