WO2023238181A1 - Dispositif de climatisation - Google Patents

Dispositif de climatisation Download PDF

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Publication number
WO2023238181A1
WO2023238181A1 PCT/JP2022/022755 JP2022022755W WO2023238181A1 WO 2023238181 A1 WO2023238181 A1 WO 2023238181A1 JP 2022022755 W JP2022022755 W JP 2022022755W WO 2023238181 A1 WO2023238181 A1 WO 2023238181A1
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WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
flow path
pressure
side flow
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PCT/JP2022/022755
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English (en)
Japanese (ja)
Inventor
皓亮 宮脇
洋志 守安
宏亮 浅沼
宗史 池田
傑 鳩村
淳 西尾
勇輝 水野
啓人 緒方
卓 羽入田
Original Assignee
三菱電機株式会社
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Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2022/022755 priority Critical patent/WO2023238181A1/fr
Publication of WO2023238181A1 publication Critical patent/WO2023238181A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/02—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the heat-exchange media travelling at an angle to one another

Definitions

  • the present disclosure relates to an air conditioner capable of defrost operation.
  • defrost is performed by stopping the air blowing from the indoor unit.
  • the evaporation capacity of the indoor heat exchanger installed in the indoor unit decreases significantly, and the refrigerant that condenses by exchanging heat with the frost in the outdoor unit cannot evaporate, causing an excess amount to flow into the compressor. Liquid refrigerant is supplied, causing a malfunction.
  • the present disclosure has been made in view of the above circumstances, and aims to provide an air conditioner that can improve both defrost performance and space availability of an outdoor unit.
  • a compressor, an outdoor heat exchanger, a first expansion device, an indoor heat exchanger, and a refrigerant tank are connected, and during a defrost operation, the refrigerant is supplied to the compressor, the outdoor heat exchanger, the first expansion device, and the refrigerant tank.
  • an inter-refrigerant heat exchanger for exchanging heat between the high-pressure refrigerant and a reduced-pressure low-pressure refrigerant; and a branch from a first branch provided in the refrigerant pipe between the first expansion device and the refrigerant heat exchanger.
  • a second throttling device that is installed in the refrigerant pipe and reduces the pressure of the high-pressure refrigerant flowing through the branched refrigerant pipe to the low-pressure refrigerant; a high-temperature-side flow path inlet into which the high-pressure refrigerant flows, and a high-temperature-side flow path outlet connected to the first throttle device and the second throttle device, through which the high-pressure refrigerant that has flowed into the high-pressure refrigerant flows out.
  • a low-temperature side flow path inlet connected to the second throttle device and into which the low-pressure refrigerant flowing out from the second throttle device flows; and a refrigerant connecting the indoor heat exchanger and the refrigerant tank during the defrost operation.
  • a low-temperature side flow path outlet connected to a second branch provided in the piping, through which the low-pressure refrigerant that has flowed into the low-temperature side flow path inlet flows out, the high-temperature side flow path outlet and the first throttle device; a first temperature measurement section that is provided in a first refrigerant pipe between the refrigerant pipe and measures the temperature of the refrigerant flowing through the first refrigerant pipe; A first pressure measurement unit that measures the pressure of the refrigerant, and is provided in a second refrigerant pipe between the low temperature side flow path outlet and the second branch, and measures the temperature of the refrigerant flowing through the second refrigerant pipe.
  • a control device that controls opening degrees of the first throttle device and the second throttle device is provided.
  • the refrigerant in a gas-liquid two-phase or liquid phase is retained in the path from the high-temperature side outlet through the first expansion device and the indoor heat exchanger to the second branch, and Gas refrigerant can flow from the outlet to the second branch. Therefore, the amount of liquid refrigerant flowing into the compressor is reduced, and the air conditioner can perform defrost operation while suppressing excessive flow of liquid refrigerant into the compressor, thereby improving defrost performance. Furthermore, since the amount of liquid refrigerant flowing into the refrigerant tank is reduced, space efficiency of the outdoor unit in which the refrigerant tank is provided is improved without increasing the size of the refrigerant tank.
  • FIG. 3 is a diagram showing the dependence of the refrigerant dryness at the compressor inlet of the compressor on the tank size ratio of the refrigerant tank of the air conditioner according to the first embodiment.
  • FIG. 2 is a schematic diagram showing a gas-liquid refrigerant distribution during defrost operation of the air conditioner according to the first embodiment.
  • FIG. 3 is a configuration diagram of a first modification of the air conditioner according to the first embodiment.
  • FIG. 3 is a configuration diagram of a second modification example of the air conditioner according to the first embodiment.
  • FIG. 7 is an isoliquid refrigerant inflow diagram for SC and SH of liquid refrigerant flowing into the compressor of the air conditioner according to Embodiment 2.
  • the discharge side of the compressor 14 is connected to the flow path switching device 15 through the refrigerant pipe 3, and the suction side is connected to the refrigerant tank 6 through the refrigerant pipe 3.
  • the compressor 14 takes in refrigerant, compresses the refrigerant, and discharges the refrigerant in a high temperature and high pressure state.
  • the refrigerant compressed by the compressor 14 is discharged and sent to the flow path switching device 15.
  • the compressor 14 is configured with, for example, a rotary compressor, a scroll compressor, a screw compressor, a reciprocating compressor, or the like.
  • the outdoor heat exchanger 11 functions as an evaporator during heating operation, exchanging heat between the refrigerant that has flowed into the interior and outdoor air, and evaporating the refrigerant.
  • the outdoor heat exchanger 11 functions as a condenser during cooling operation and defrosting operation, exchanges heat between the refrigerant that has flowed into the interior, and outdoor air, and condenses and liquefies the refrigerant.
  • the high temperature side flow path inlet 51 is connected to the high temperature side flow path outlet 52 by high temperature side flow path piping.
  • the refrigerant flow path between the high temperature side flow path inlet 51 and the high temperature side flow path outlet 52 that the refrigerant heat exchanger 2 has will be referred to as a high temperature side flow path or a high pressure flow path.
  • the high temperature side flow path inlet 51 is connected to the third throttle device 23 provided on the upstream side of the refrigerant during cooling operation and defrosting operation.
  • the high-temperature high-pressure refrigerant flowing out from the outdoor heat exchanger 11 flows into the high-temperature side flow path inlet 51 via the third throttle device 23 during cooling operation and defrosting operation.
  • the second branch 32 connects the refrigerant pipe 3 connected to the low temperature side flow path outlet 54 to the refrigerant pipe 3 that connects the flow path switching device 15 and the refrigerant tank 6.
  • the first pressure measurement unit 81 is provided in the first refrigerant pipe and measures the pressure of the refrigerant flowing through the first refrigerant pipe.
  • the second temperature measurement unit 72 is provided in the refrigerant pipe 3, which is a second refrigerant pipe between the low temperature side flow path outlet 54 of the refrigerant heat exchanger 2 and the second branch 32, and is configured to flow through the second refrigerant pipe. Measure the temperature of the refrigerant.
  • the control device 210 controls the operating state of the entire air conditioner 200, such as cooling operation or heating operation.
  • the control device 210 may control the flow path switching device 15 and switches the direction in which the refrigerant flows in the refrigerant pipe 3 .
  • the control device 210 may control the compressor 14, for example, may control the discharge amount of compressed refrigerant.
  • the control device 210 may control the amount of rotation of the outdoor fan 13.
  • the control device 210 may adjust the opening degrees of the first diaphragm device 21, the second diaphragm device 22, and the third diaphragm device 23. Further, the control device 210 performs control processing according to an embodiment described later.
  • the control device 210 controls the first expansion device so that the degree of supercooling based on the temperature measured by the first temperature measurement section 71 and the pressure measured by the first pressure measurement section 81 during the defrost operation is 0° C. or higher. 21 is controlled. When the degree of supercooling is less than 0, the control device 210 reduces the opening degree of the first expansion device 21.
  • the control device 210 controls the second expansion device 22 so that the degree of superheat based on the temperature measured by the second temperature measurement section 72 and the pressure measured by the second pressure measurement section 82 during the defrost operation is 0° C. or higher. Controls the opening degree. When the degree of superheat is less than 0, the control device 210 reduces the opening degree of the second expansion device 22.
  • control device 210 controls the opening degree of the first expansion device 21 so that the temperature measured by the first temperature measurement section 71 is lower than the saturation temperature of the pressure measured by the first pressure measurement section 81. .
  • the control device 210 controls the opening degree of the second expansion device 22 so that the temperature measured by the second temperature measurement section 72 is higher than the saturation temperature of the pressure measured by the second pressure measurement section 82.
  • the processing circuit of the control device 210 When the processing circuit of the control device 210 is dedicated hardware, the processing circuit may be, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), or an FPGA (Field Programmable Gate Array). ), or a combination of these is applicable. Each of the functional units realized by the processing circuit may be realized by separate hardware, or each functional unit may be realized by one piece of hardware.
  • the processing circuit of the control device 210 is a CPU
  • each function executed by the processing circuit is realized by software, firmware, or a combination of software and firmware.
  • Software and firmware are written as programs and stored in a storage unit. The CPU implements each function of the processing circuit by reading and executing programs stored in the storage unit. Note that some of the functions of the processing circuit may be realized by dedicated hardware, and some of them may be realized by software or firmware.
  • the indoor unit 202 includes a first expansion device 21 and an indoor heat exchanger 16.
  • the first expansion device 21 is provided in the refrigerant pipe 3 and connected to the first branch 31.
  • the first expansion device 21 has a function as a pressure reducing valve or an expansion valve, and expands and reduces the pressure of the refrigerant.
  • the first expansion device 21 controls the pressure of the refrigerant flowing into the indoor heat exchanger 16 during defrost operation.
  • the first expansion device 21 is composed of, for example, an electric expansion valve that can adjust the flow rate of the refrigerant. Note that the first expansion device 21 is not limited to an electric expansion valve, and may be configured with a mechanical expansion valve using a diaphragm as a pressure receiving part, a capillary tube, or the like.
  • the downstream side of the refrigerant flow during the cooling operation and defrosting operation of the indoor heat exchanger 16 is connected to the low temperature side flow path outlet 54 and the refrigerant tank 6 by the refrigerant pipe 3 via the flow path switching device 15 and the second branch 32.
  • the first branch 31 is connected to the second branch 32 via the second expansion device 22 and the refrigerant heat exchanger 2.
  • An indoor fan (not shown) is placed adjacent to the indoor heat exchanger 16 in order to increase the efficiency of heat exchange between the refrigerant in the indoor heat exchanger 16 and outdoor air.
  • the outdoor heat exchanger 11 and the indoor heat exchanger 16 function as heat exchangers that exchange heat between the refrigerant flowing in the refrigerant pipe 3 and a heat transport medium such as air flowing outside the pipe.
  • the outdoor heat exchanger 11 and the indoor heat exchanger 16 are, for example, a fin-and-tube heat exchanger, a microchannel heat exchanger, a shell-and-tube heat exchanger, a heat pipe heat exchanger, or a double-tube heat exchanger. It consists of a heat exchanger or a plate heat exchanger.
  • the high-temperature, high-pressure gas refrigerant compressed by the compressor 14 passes through the flow path switching device 15 and flows into the indoor heat exchanger 16 that functions as a condenser.
  • the high-temperature, high-pressure gas refrigerant that has flowed into the indoor heat exchanger 16 is cooled while supplying heat to the indoor air, and flows out of the indoor heat exchanger 16 as a low-temperature liquid refrigerant.
  • the liquid refrigerant flowing out from the indoor heat exchanger 16 is depressurized by the first expansion device 21 to become a low temperature, low pressure, gas-liquid two-phase refrigerant, and flows into the outdoor heat exchanger 11, which functions as an evaporator.
  • the refrigerant flows through the interrefrigerant heat exchanger 2, but at this time, the second expansion device 22 may be closed and all the refrigerant flows into the outdoor heat exchanger 11. Further, the opening ratio of the second throttle device 22 and the third throttle device 23 is adjusted to flow a part of the refrigerant from the first branch 31 to the second branch 32 via the low-pressure flow path of the refrigerant heat exchanger 2. By doing so, the degree of dryness of the refrigerant flowing to the outdoor heat exchanger 11 may be controlled.
  • the high-temperature, high-pressure gas refrigerant compressed by the compressor 14 passes through the flow path switching device 15 and flows into the outdoor heat exchanger 11.
  • the high-temperature, high-pressure gas refrigerant that has flowed into the outdoor heat exchanger 11 is cooled and condensed by heat radiation to the frost, and flows out as a low-temperature gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant flowing out from the outdoor heat exchanger 11 exchanges heat with the low-pressure refrigerant in the inter-refrigerant heat exchanger 2 to become a single-phase liquid refrigerant, and flows out from the inter-refrigerant heat exchanger 2.
  • the refrigerant in a two-phase state of low-pressure gas refrigerant and liquid refrigerant whose pressure has been reduced through the first expansion device 21 flows into the indoor heat exchanger 16.
  • an indoor fan (not shown) is stopped in order to suppress the temperature drop in the indoor space.
  • some of the liquid refrigerant in the two-phase refrigerant that has flowed into the indoor heat exchanger 16 evaporates due to heat radiation due to natural convection, it flows out as a gas-liquid two-phase refrigerant, and the flow path switching device 15 to the second branch 32 via.
  • the intermediate-pressure liquid-based gas-liquid two-phase refrigerant whose pressure has been reduced through the second throttle device 22 flows into the low temperature side flow passage inlet 53 of the refrigerant heat exchanger 2 , and flows into the refrigerant heat exchanger 2 .
  • the refrigerant flowing through the low-temperature side flow path of the refrigerant heat exchanger 2 exchanges heat with the refrigerant flowing through the high-temperature side flow path of the refrigerant heat exchanger 2 and becomes a low-pressure gas refrigerant. It flows out from the side channel outlet 54.
  • FIG. 3 is a flowchart for explaining control of the opening degree of the first diaphragm device 21 and the opening degree of the second diaphragm device 22 of the control device 210 according to the first embodiment.
  • the control device 210 calculates the degree of supercooling based on the temperature measured by the first temperature measurement unit 71 and the pressure measured by the first pressure measurement unit 81 during the defrost operation (step S1).
  • step S2 determines whether the degree of supercooling calculated in step S1 is ⁇ 0 (step S2). In step S2, if it is determined that the degree of supercooling is not 0 (NO in step S2), the opening degree of the first throttle device 21 is controlled to be smaller than the current opening degree (step S3).
  • step S2 If it is determined in step S2 that the degree of supercooling is ⁇ 0 (YES in step S2) or after the process in step S3, the control device 210 determines the temperature measured by the second temperature measurement unit 72 during the defrost operation, The degree of superheat is calculated based on the pressure measured by the second pressure measuring section 82 (step S4).
  • control device 210 determines whether the superheat degree calculated in step S4 ⁇ 0 (step S5). If it is determined in step S5 that the degree of superheat is not 0 (NO in step S5), the opening degree of the second throttle device 22 is controlled to be smaller than the current opening degree (step S6).
  • control device 210 determines that the degree of superheat ⁇ 0 in step S5 (YES in step S5) or after the process in step S6, the control device 210 returns to the process in step S1.
  • FIG. 4 is a refrigerant circuit diagram showing a refrigerant flow path of a conventional air conditioner 200.
  • FIG. 5 is a schematic diagram showing the gas-liquid refrigerant distribution during defrost operation of the conventional air conditioner 200.
  • the refrigerant 63 becomes a phase or liquid phase state.
  • an air conditioner 200 including a refrigerant heat exchanger 2 is conventionally known, in the defrost operation, the second throttle device 22 is fully closed to direct the refrigerant indoors as in the conventional configuration shown in FIG. machine unit 202.
  • the second throttle device 22 is controlled to be fully opened. Therefore, the effect of retaining the liquid refrigerant in the refrigerant pipe 3 from the refrigerant heat exchanger 2 to the first expansion device 21 is small.
  • the refrigerant from the high-temperature side flow path outlet 52 of the inter-refrigerant heat exchanger 2 to the first expansion device 21 may temporarily cool depending on the amount of heat held by the indoor heat exchanger 16 and the refrigerant piping 3 during heating operation. Becomes liquid phase.
  • the gas becomes a two-phase gas-liquid phase that requires a small amount of heat to reach the gas phase. As a result, the amount of liquid refrigerant flowing into the compressor 14 increases.
  • FIG. 6 is a diagram showing the dependence of the refrigerant dryness at the compressor inlet of the compressor 14 on the tank size ratio of the refrigerant tank 6 of the air conditioner 200 according to the first embodiment.
  • black squares indicate the refrigerant dryness at the compressor inlet of the air conditioner 200 in Embodiment 1
  • white circles indicate the refrigerant dryness in the conventional air conditioner 200 shown in FIG. .
  • the conventional tank size is taken as 100%.
  • the refrigerant dryness at the compressor inlet in Embodiment 1 exceeds the refrigerant dryness in the conventional air conditioner 200. Therefore, it can be seen that there is an effect of suppressing the inflow of liquid refrigerant into the refrigerant tank 6. Furthermore, it can be seen that when the tank size ratio is 20%, the refrigerant dryness at the compressor inlet becomes 1, which is effective in reducing the size of the refrigerant tank 6.
  • FIG. 7 is a schematic diagram showing the gas-liquid refrigerant distribution during defrost operation of the air conditioner 200 according to the first embodiment.
  • the absolute value of the difference between the temperature measured by the first temperature measurement section 71 and the saturation temperature of the pressure measured by the first pressure measurement section 81 is defined as SC.
  • the absolute value of the difference between the temperature measured by the second temperature measuring section 72 and the pressure saturation temperature measured by the second pressure measuring section 82 is defined as SH.
  • a pressure measuring means may be provided separately, and the saturation temperature may be measured by this pressure measuring means.
  • the control device 210 makes the opening degree of the second throttle device 22 smaller than the current opening degree when (SC) is smaller than (SH). .
  • the control device 210 makes the opening degree of the second throttle device 22 smaller than the current opening degree. .
  • the control device 210 controls the opening degree of the first throttle device 21 to be small when (SC) is smaller than (SH). In this case, the amount of liquid refrigerant held in the refrigerant piping 3 between the refrigerant heat exchanger 2 and the indoor heat exchanger 16 is improved, so that the effect of suppressing the amount of liquid flowing into the compressor 14 is large.
  • FIG. 12 is a perspective view showing a first example of the refrigerant heat exchanger 2 and the refrigerant piping 3 around the refrigerant heat exchanger 2 in the air conditioner 200 according to the third embodiment.
  • the refrigerant heat exchanger 2 is a plate-type heat exchanger having a plurality of plates 1 in which high-pressure refrigerant flow paths and low-pressure refrigerant flow paths are alternately arranged in the horizontal direction.
  • the high temperature side flow path outlet 52 is provided at the lower part of the side surface of the plate 1 on the first temperature measuring section 71 side among the plurality of plates 1 parallel to the direction of gravity 100.
  • the high temperature side flow path outlet 52 is provided at the same height as the low temperature side flow path inlet 53.
  • the high-pressure refrigerant that flows in from the high-temperature side flow path inlet 51 exchanges heat with the low-temperature refrigerant that flows in from the low-temperature side flow path inlet 53 to become a low-temperature refrigerant.
  • the heat-exchanged low-temperature refrigerant flows out from the high-temperature side flow path outlet 52.
  • the plate type refrigerant heat exchanger 2 shown in the first example of the third embodiment has the high temperature side flow path inlet 51 on the upper side of gravity and the high temperature side flow path outlet 52 on the lower side of gravity in the defrost operation. Defrost performance is improved by suppressing gas refrigerant from flowing out from the high-pressure refrigerant outlet without heat exchange.
  • the high temperature side flow path inlet 51 is provided at the upper part of the side surface of the plate 1 on the first temperature measuring section 71 side among the plurality of plates 1 parallel to the direction of gravity 100.
  • the high temperature side flow path inlet 51 is provided at the same height as the low temperature side flow path inlet 53. During defrost operation or cooling operation, high-pressure refrigerant flows from the outdoor heat exchanger 11 into the high temperature side flow path inlet 51.
  • the component of the second unit vector 92 in the direction of gravity 100 (negative direction) is smaller than the component of the third unit vector 93 in the direction of gravity 100 (positive direction).
  • the gas refrigerant flowing out from the high temperature side flow path outlet 52 is transferred to the low temperature side flow path inlet 53 in the first branch 31 due to the buoyancy caused by the density difference between gas and liquid.
  • Improve gas refrigerant inflow This increases the refrigerant density in the refrigerant pipe 3 from the refrigerant heat exchanger 2 to the first expansion device 21 where the liquid refrigerant inflow increases, thereby improving the amount of refrigerant held and reducing the liquid inflow into the compressor 14. control and reduce quality deterioration.
  • the gas refrigerant flowing out from the high temperature side flow path outlet 52 is transferred to the first branch 31 by the inertial force of the gas refrigerant having a higher flow rate than the liquid refrigerant.
  • This improves the flow of gas refrigerant into the low temperature side flow path inlet 53.
  • This increases the refrigerant density in the refrigerant pipe 3 from the interrefrigerant heat exchanger 2 to the first expansion device 21, where the amount of liquid refrigerant inflow increases, and thereby improves the amount of refrigerant held. Therefore, the amount of liquid flowing into the compressor 14 is suppressed, and quality deterioration is suppressed.
  • the high temperature side flow path inlet 51 is provided at the lower part of the side surface of the plate 1 on the first temperature measuring section 71 side among the plurality of plates 1 parallel to the direction of gravity 100.
  • the high temperature side flow path inlet 51 is provided at the same height as the low temperature side flow path inlet 53. During defrost operation or cooling operation, high-pressure refrigerant flows from the outdoor heat exchanger 11 into the high temperature side flow path inlet 51.
  • the refrigerant pipe 3 connecting the high temperature side flow path outlet 52 and the low temperature side flow path inlet 53 extends horizontally from the high temperature side flow path outlet 52, curves downward, and then extends horizontally in a folded manner to connect the low temperature side flow path. It has a U-shape that reaches the flow path entrance 53.
  • a first branch 31 is provided in the lower straight part of the two horizontally extending straight parts of this U-shape.
  • the other refrigerant pipe 3 branched at the first branch 31 is connected to the first expansion device 21 as shown in FIG.
  • the other branched refrigerant pipe 3 is provided with a first pressure measuring section 81 and a first temperature measuring section 71.
  • the refrigerant pipe 3 provided with the first pressure measurement section 81 and the first temperature measurement section 71 intersects with the horizontally extending lower straight portion of the U-shape.
  • the gas-liquid two-phase refrigerant that exits from the high-temperature side flow path outlet 52, most of the gas refrigerant travels straight through the first branch 31 and is transferred from the low-temperature side flow path inlet 53 provided downward to a plate-type heat exchanger. It flows into a certain refrigerant heat exchanger 2.
  • the liquid refrigerant branches at the first branch 31 and heads toward the first expansion device 21. Thereby, the refrigerant density in the refrigerant pipe 3 from the refrigerant heat exchanger 2 to the first expansion device 21 increases.
  • the gas refrigerant flowing out from the high temperature side flow path outlet 52 is transferred to the low temperature side by the inertial force of the gas refrigerant having a higher flow rate than the liquid refrigerant in the first branch 31.
  • the inflow of gas refrigerant into the flow path inlet 53 is improved. This increases the refrigerant density in the refrigerant pipe 3 from the refrigerant heat exchanger 2 to the first expansion device 21 where the liquid refrigerant inflow increases, thereby improving the amount of refrigerant held and reducing the liquid inflow into the compressor 14. control and reduce quality deterioration.
  • the refrigerant heat exchanger 2 of the fourth example includes a high temperature side flow path outlet 52 on the upper side in the direction of gravity 100 and a high temperature side flow path inlet 51 on the lower side in the gravity direction 100 in the defrost operation.
  • the first outlet 31b which is connected to the low temperature side flow path inlet 53 of the refrigerant heat exchanger 2 via the second expansion device 22, is It is provided above the second outlet 31c in the direction of gravity 100 with respect to the second outlet 31c connected to the first throttle device 21.
  • the driving source for the gas-liquid branch in the first branch 31 is the gas flow velocity of the refrigerant, and the inertia from the high temperature side flow path outlet 52 to the low temperature side flow path inlet 53
  • the main driving source is force difference.
  • the gas refrigerant flowing out from the high temperature side flow path outlet 52 is transferred to the low temperature side flow path inlet 53 by the buoyancy due to the density difference between gas and liquid and the inertial force from the refrigerant heat exchanger 2 to the first branch 31 at the first branch 31. Refrigerant inflow is improved.
  • the amount of refrigerant retained is improved by increasing the refrigerant density in the refrigerant pipe 3 from the refrigerant heat exchanger 2 to the first expansion device 21, where the amount of liquid refrigerant inflow increases. Therefore, the amount of liquid flowing into the compressor 14 is suppressed, the defrost performance is improved, and the comfort is improved.
  • FIG. 16 is a perspective view for explaining the size of the refrigerant heat exchanger 2 in the air conditioner 200 according to the third embodiment.
  • the flow rate of refrigerant flowing from the low temperature side flow path inlet 53 to the low temperature side flow path outlet 54 is larger than that in the conventional refrigerant heat exchanger 2.
  • the refrigerant heat exchanger 2 includes a plurality of plates 1 in which high-pressure refrigerant flow paths and low-pressure refrigerant flow paths are alternately arranged in a direction horizontal to the direction of gravity 100. It is an exchanger.
  • the refrigerant heat exchanger 2 of Embodiment 3 has a length of X in the flow path stacking direction in the direction perpendicular to gravity, a length of Y in the direction perpendicular to gravity and perpendicular to the flow path stacking direction, and a length in the direction perpendicular to gravity and perpendicular to the flow path stacking direction.
  • Z/(XY) is 0.01 or more and 0.1 or less, where Z is the height direction.
  • the high temperature side flow path inlet 51, the high temperature side flow path outlet 52, the low temperature side flow path inlet 53, and the low temperature side flow path outlet 54 the high temperature side and low temperature side flow are shown as seen through in the stacking direction of the plate 1. Although the paths are shown arranged so that they intersect, they may be arranged parallel to each other.
  • FIG. 17 is a diagram showing the sensitivity of the dryness of the refrigerant flowing into the compressor 14 to the size of the refrigerant heat exchanger 2 in the air conditioner 200 according to the third embodiment.
  • FIG. 17 shows the improvement rate in suction dryness with respect to the configuration of a conventional air conditioner that does not include the refrigerant heat exchanger 2.
  • the air conditioner 200 according to the third embodiment it is possible to achieve both defrost performance and space efficiency.
  • FIG. 18 is a diagram showing a refrigerant circuit of an air conditioner 200 according to the fourth embodiment. Note that the same parts as in FIG. 1 will be described with the same reference numerals unless otherwise specified.
  • the first indoor unit 202_1 includes a first expansion device 21 and an indoor heat exchanger 16.
  • the second indoor unit 202_2 includes a first expansion device 21 and an indoor heat exchanger 16.
  • the diversion unit 203 divides the refrigerant from the outdoor unit 201 into the first indoor unit 202_1 and the second indoor unit 202_2.
  • the flow dividing unit 203 includes a fourth throttle device 24, a first on-off valve 40_1, and a second on-off valve 40_2.
  • the fourth expansion device 24 is provided in the third refrigerant pipe between the first refrigerant pipe and the second refrigerant pipe.
  • the first refrigerant pipe is the refrigerant pipe 3 between the first expansion device 21 of the first indoor unit 202_1 and the first expansion device 21 of the second indoor unit 202_2 and the first branch 31.
  • the second refrigerant pipe is the refrigerant pipe 3 between the indoor heat exchanger 16 of the first indoor unit 202_1 and the second branch 32 and the indoor heat exchanger 16 of the second indoor unit 202_2.
  • the first on-off valve 40_1 is connected to the indoor heat exchanger 16 of the first indoor unit 202_1 and the third branch 33_1.
  • the third branch 33_1 is provided in the refrigerant pipe 3 between the fourth expansion device 24 and the second branch 32.
  • the second on-off valve 40_2 is connected to the indoor heat exchanger 16 of the second indoor unit 202_2 and the third branch 33_2.
  • the third branch 33_2 is provided in the refrigerant pipe 3 between the fourth expansion device 24 and the second branch 32.
  • the control device 210 By performing such control by the control device 210, during the defrost operation, the refrigerant coming out of the refrigerant heat exchanger 2 does not flow through the refrigerant channels of the first indoor unit 202_1 and the second indoor unit 202_2. , returns to the refrigerant tank 6 and circulates.
  • the indoor heat exchangers 16 of the first indoor unit 202_1 and the second indoor unit 202_2 can hold the refrigerant as refrigerant containers. Thereby, the inflow of liquid refrigerant into the compressor 14 can be suppressed and quality can be improved.
  • the effect of suppressing refrigerant outflow from the first indoor unit 202_1 and the second indoor unit 202_2 to the outdoor unit 201 is further increased.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
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  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

Ce dispositif de climatisation est pourvu d'un dispositif de commande qui commande les degrés d'ouverture d'un premier dispositif d'étranglement et d'un second dispositif d'étranglement sur la base d'une température mesurée par une première unité de mesure de température pendant une opération de dégivrage, d'une pression mesurée par une première unité de mesure de pression, d'une température mesurée par une seconde unité de mesure de température, et d'une pression mesurée par une seconde unité de mesure de pression.
PCT/JP2022/022755 2022-06-06 2022-06-06 Dispositif de climatisation WO2023238181A1 (fr)

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JPH1123036A (ja) * 1997-07-04 1999-01-26 Fujitsu General Ltd 空気調和機
JP2009228979A (ja) * 2008-03-24 2009-10-08 Mitsubishi Electric Corp 空気調和装置
JP2010101570A (ja) * 2008-10-24 2010-05-06 Panasonic Corp 空気調和機
JP2010190537A (ja) * 2009-02-20 2010-09-02 Fujitsu General Ltd 空気調和機
JP2011085025A (ja) * 2009-10-13 2011-04-28 Toyota Industries Corp 廃熱回生システム
WO2014080612A1 (fr) * 2012-11-26 2014-05-30 パナソニック株式会社 Dispositif à cycle de réfrigération et dispositif de production d'eau chaude équipé de celui-ci
JP2016176649A (ja) * 2015-03-20 2016-10-06 ダイキン工業株式会社 冷凍装置
WO2017037891A1 (fr) * 2015-09-02 2017-03-09 三菱電機株式会社 Dispositif à cycle de réfrigération
JP2018087675A (ja) * 2016-11-30 2018-06-07 ダイキン工業株式会社 冷凍装置
JP2019158189A (ja) * 2018-03-09 2019-09-19 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置およびそれを備えた温水生成装置
JP2019530843A (ja) * 2016-09-26 2019-10-24 グリー エレクトリック アプライアンシーズ インク オブ ズーハイＧｒｅｅ Ｅｌｅｃｔｒｉｃ Ａｐｐｌｉａｎｃｅｓ， Ｉｎｃ． Ｏｆ Ｚｈｕｈａｉ 空調器及びその除霜システム
WO2020174685A1 (fr) * 2019-02-28 2020-09-03 三菱電機株式会社 Dispositif à cycle frigorifique

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH1123036A (ja) * 1997-07-04 1999-01-26 Fujitsu General Ltd 空気調和機
JP2009228979A (ja) * 2008-03-24 2009-10-08 Mitsubishi Electric Corp 空気調和装置
JP2010101570A (ja) * 2008-10-24 2010-05-06 Panasonic Corp 空気調和機
JP2010190537A (ja) * 2009-02-20 2010-09-02 Fujitsu General Ltd 空気調和機
JP2011085025A (ja) * 2009-10-13 2011-04-28 Toyota Industries Corp 廃熱回生システム
WO2014080612A1 (fr) * 2012-11-26 2014-05-30 パナソニック株式会社 Dispositif à cycle de réfrigération et dispositif de production d'eau chaude équipé de celui-ci
JP2016176649A (ja) * 2015-03-20 2016-10-06 ダイキン工業株式会社 冷凍装置
WO2017037891A1 (fr) * 2015-09-02 2017-03-09 三菱電機株式会社 Dispositif à cycle de réfrigération
JP2019530843A (ja) * 2016-09-26 2019-10-24 グリー エレクトリック アプライアンシーズ インク オブ ズーハイＧｒｅｅ Ｅｌｅｃｔｒｉｃ Ａｐｐｌｉａｎｃｅｓ， Ｉｎｃ． Ｏｆ Ｚｈｕｈａｉ 空調器及びその除霜システム
JP2018087675A (ja) * 2016-11-30 2018-06-07 ダイキン工業株式会社 冷凍装置
JP2019158189A (ja) * 2018-03-09 2019-09-19 パナソニックＩｐマネジメント株式会社 冷凍サイクル装置およびそれを備えた温水生成装置
WO2020174685A1 (fr) * 2019-02-28 2020-09-03 三菱電機株式会社 Dispositif à cycle frigorifique

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