WO2016016999A1 - Dispositif à cycle de réfrigération - Google Patents

Dispositif à cycle de réfrigération Download PDF

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Publication number
WO2016016999A1
WO2016016999A1 PCT/JP2014/070221 JP2014070221W WO2016016999A1 WO 2016016999 A1 WO2016016999 A1 WO 2016016999A1 JP 2014070221 W JP2014070221 W JP 2014070221W WO 2016016999 A1 WO2016016999 A1 WO 2016016999A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchanger
heat
header
refrigeration cycle
Prior art date
Application number
PCT/JP2014/070221
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English (en)
Japanese (ja)
Inventor
山下　浩司
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
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 JP2016537680A priority Critical patent/JPWO2016016999A1/ja
Priority to PCT/JP2014/070221 priority patent/WO2016016999A1/fr
Priority to GB1700157.9A priority patent/GB2543206A/en
Publication of WO2016016999A1 publication Critical patent/WO2016016999A1/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
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0243—Header boxes having a circular cross-section
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/031—Sensor arrangements
    • F25B2313/0314—Temperature sensors near the indoor heat exchanger
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1933—Suction pressures
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/02—Heat exchange conduits with particular branching, e.g. fractal conduit arrangements

Definitions

  • the present invention relates to a refrigeration cycle apparatus such as an air conditioner applied to, for example, a building multi-air conditioner.
  • a refrigeration cycle apparatus that forms a refrigerant circuit that circulates refrigerant and performs air conditioning, such as a multi air conditioner for buildings, generally, R410A that is nonflammable, hydrogen and carbon such as propane that exhibits flammability
  • R410A that is nonflammable, hydrogen and carbon such as propane that exhibits flammability
  • a substance containing is used as a refrigerant. When these substances are released into the atmosphere, they have different lifetimes until they are decomposed in the atmosphere and changed to other substances. However, they are highly stable in the refrigeration cycle apparatus and have been used for a long period of several decades. It can be used as a refrigerant.
  • Disproportionation is the property that substances of the same type react to change to another substance. For example, when some strong energy is applied to the refrigerant in a state where the distance between adjacent substances such as a liquid state is very close, this energy causes a disproportionation reaction, and the adjacent substances react with each other, It changes to another substance. When a disproportionation reaction occurs, heat is generated and a rapid temperature rise occurs. As a result, the pressure may increase rapidly.
  • a substance that causes a disproportionation reaction is used as a refrigerant in a refrigeration cycle device and is enclosed in a pipe such as copper, the pipe cannot withstand the pressure rise of the internal refrigerant, and the pipe will burst. Accidents may occur.
  • substances having such a disproportionation reaction for example, 1,1,2-trifluoroethylene (HFO-1123), acetylene and the like are known.
  • thermal cycle system refrigeration cycle apparatus
  • HFO-1123 1,1,2-trifluoroethylene
  • Patent Document 1 describes that 1,1,2-trifluoroethylene (HFO-1123) is used as a working medium for a heat cycle in a refrigeration cycle apparatus such as a heat cycle system.
  • 1,1,2-trifluoroethylene (HFO-1123) is a substance having a disproportionation reaction. Therefore, when used as a refrigerant as it is, a disproportionation reaction may occur due to some energy at a place in the refrigerant circuit where a liquid substance such as a liquid or a two-phase adjacent substance flows very close. When adjacent substances disproportionate, they change to another substance and do not function as a refrigerant. In addition, in the refrigerant circuit, an accident such as a pipe rupture may occur due to a sudden pressure increase.
  • Patent Document 1 do not describe any method for realizing an apparatus that does not cause the disproportionation reaction.
  • the present invention has been made to solve the above-described problem, and a refrigeration cycle that can safely use a substance having a property of causing a disproportionation reaction by reducing energy received from the outside of the refrigerant as a refrigerant. Get the device.
  • a refrigeration cycle apparatus is composed of a substance having a property of causing a disproportionation reaction by connecting a compressor, a first heat exchanger, a throttling device, and a second heat exchanger with a refrigerant pipe.
  • a refrigerant circuit is formed by charging a single refrigerant or a mixed refrigerant containing a substance having a property of causing a disproportionation reaction and a refrigerating machine oil having compatibility with the refrigerant to form a first heat exchanger and a second heat exchanger.
  • At least one of the heat exchangers has a plurality of heat transfer tubes through which the refrigerant flows, and a header through which the refrigerant outlet side end of the heat transfer tubes is inserted, and the inner diameter of the header is that of the heat transfer tubes.
  • the end of the heat transfer tube on the side of the refrigerant outlet that is larger than the inner diameter is disposed so as to face the inner wall surface of the header, and from the center of the end of the heat transfer tube on the side of the refrigerant outlet, the end of the header corresponding to the center L is the distance to the wall surface, the inner diameter at the end of the heat transfer tube on the refrigerant outlet side, or The equivalent diameter corresponding to the diameter when the inner diameter d, the value of L / d is, at a position of 20 and less than 0, greater than one in which the ends of the refrigerant outlet side of the heat transfer tube is located.
  • a refrigerant circuit is formed using a substance having a property of causing a disproportionation reaction such as 1,1,2-trifluoroethylene (HFO-1123) as a refrigerant
  • a disproportionation reaction such as 1,1,2-trifluoroethylene (HFO-1123)
  • HFO-1123 1,1,2-trifluoroethylene
  • FIG. 1 Schematic which shows the example of installation of the refrigerating-cycle apparatus which concerns on Embodiment 1 of this invention.
  • the circuit block diagram which shows an example of the circuit structure of the refrigerating-cycle apparatus which concerns on Embodiment 1 of this invention.
  • the refrigerant circuit figure which shows the flow of the refrigerant
  • the refrigerant circuit figure which shows the flow of the refrigerant
  • FIG. Schematic of the structure of the heat exchanger used for the heat source side heat exchanger 12, the load side heat exchanger 15, etc. in Embodiment 1 of this invention.
  • Sectional drawing which shows the relationship between the header 47 used for the heat exchanger of the refrigerating-cycle apparatus which concerns on Embodiment 1 of this invention, and the heat exchanger tube 43.
  • FIG. Schematic of another structure of the heat exchanger of the refrigeration cycle apparatus which concerns on Embodiment 1 of this invention.
  • the schematic diagram of the heat exchanger tube used for the heat exchanger of the refrigerating cycle device concerning Embodiment 1 of the present invention.
  • the circuit block diagram of the refrigerating-cycle apparatus which concerns on Embodiment 2 of this invention.
  • FIG. 1 and the following drawings the same reference numerals denote the same or corresponding parts, and are common to the whole text of the embodiments described below.
  • the form of the component represented to the whole text of specification is an illustration to the last, Comprising: It does not limit to the form described in the specification.
  • the combination of the components is not limited to the combination in each embodiment, and the components described in the other embodiments can be applied to another embodiment.
  • the subscripts may be omitted.
  • the size relationship of each component may be different from the actual one.
  • the level of temperature, pressure, etc. is not particularly determined in relation to absolute values, but is relatively determined in the state, operation, etc. of the system, apparatus, and the like.
  • FIG. Embodiment 1 of the present invention will be described with reference to the drawings.
  • FIG. 1 is a schematic diagram illustrating an installation example of a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • the refrigeration cycle apparatus shown in FIG. 1 can select either a cooling mode or a heating mode as an operation mode by configuring a refrigerant circuit that circulates refrigerant and using the refrigerant refrigeration cycle.
  • the refrigeration cycle apparatus of the present embodiment will be described by taking an air conditioning apparatus that performs air conditioning of the air-conditioning target space (indoor space 7) as an example.
  • the refrigeration cycle apparatus has one outdoor unit 1 that is a heat source unit and a plurality of indoor units 2.
  • the outdoor unit 1 and the indoor unit 2 are connected by an extension pipe (refrigerant pipe) 4 that conducts the refrigerant, and the cold or warm heat generated in the outdoor unit 1 is delivered to the indoor unit 2 via the extension pipe 4. It is like that.
  • the outdoor unit 1 is usually arranged in an outdoor space 6 that is a space outside a building 9 such as a building (for example, a rooftop), and supplies cold or hot heat to the indoor unit 2.
  • the indoor unit 2 is disposed at a position where the temperature-adjusted air can be supplied to the indoor space 7 which is a space inside the building 9 (for example, a living room). Air is supplied.
  • an outdoor unit 1 and each indoor unit 2 are connected to each other using two extension pipes 4.
  • FIG. 1 shows an example in which the indoor unit 2 is a ceiling cassette type, but the present invention is not limited to this. Any type may be used as long as heating air or cooling air can be blown directly into the indoor space 7 by a duct or the like, such as a ceiling-embedded type or a ceiling-suspended type.
  • the outdoor unit 1 is installed in the outdoor space 6 as an example, but the present invention is not limited to this.
  • the outdoor unit 1 may be installed in an enclosed space such as a machine room with a ventilation opening. Further, if the waste heat can be exhausted outside the building 9 by the exhaust duct, it may be installed inside the building 9. Furthermore, you may make it install in the inside of the building 9 using the water-cooled outdoor unit 1. FIG. No matter what place the outdoor unit 1 is installed, no particular problem occurs.
  • the number of connected outdoor units 1 and indoor units 2 is not limited to the number shown in FIG. 1, and the number of units can be determined according to the building 9 in which the refrigeration cycle apparatus according to the present embodiment is installed. That's fine.
  • FIG. 2 is a circuit configuration diagram showing an example of a refrigerant circuit configuration of the refrigeration cycle apparatus (hereinafter referred to as the refrigeration cycle apparatus 100) according to the first embodiment. Based on FIG. 2, the detailed structure of the refrigerating-cycle apparatus 100 is demonstrated. As shown in FIG. 2, the outdoor unit 1 and the indoor unit 2 are connected by an extension pipe (refrigerant pipe) 4 through which a refrigerant flows.
  • extension pipe refrigerant pipe
  • Outdoor unit 1 The outdoor unit 1 is mounted with a compressor 10, a first refrigerant flow switching device 11 such as a four-way valve, a heat source side heat exchanger 12, and an accumulator 19 connected in series by a refrigerant pipe.
  • the compressor 10 sucks in the refrigerant, compresses the refrigerant, discharges it in a high temperature and high pressure state.
  • the compressor 10 has, for example, a low-pressure shell structure that has a compression chamber in a sealed container, the inside of the sealed container has a low-pressure refrigerant pressure atmosphere, and sucks and compresses the low-pressure refrigerant in the sealed container.
  • a high-pressure shell structure is used in which the inside of the sealed container becomes a high-pressure refrigerant pressure atmosphere and the high-pressure refrigerant compressed in the compression chamber is discharged into the sealed container.
  • the compressor 10 of this Embodiment it is good to comprise by the inverter compressor etc.
  • the first refrigerant flow switching device 11 switches the refrigerant flow during the heating operation and the refrigerant flow during the cooling operation.
  • the heat source side heat exchanger 12 serving as the first heat exchanger functions as an evaporator during heating operation and functions as a condenser (or radiator) during cooling operation.
  • the heat source side heat exchanger 12 exchanges heat between air supplied from a blower (not shown) and the refrigerant, and evaporates or condenses the refrigerant.
  • the heat source side heat exchanger 12 functions as a condenser in the operation of cooling the indoor space 7.
  • operation which heats the indoor space 7, it functions as an evaporator.
  • the accumulator 19 is provided on the suction side of the compressor 10 and stores excess refrigerant in the refrigerant circuit due to an operation mode change or the like.
  • the outdoor unit 1 is provided with a high pressure detection device 37, a low pressure detection device 38, and a control device 60.
  • the control device 60 controls devices based on detection information from various detection devices, instructions from a remote controller, and the like. For example, the driving frequency of the compressor 10, the rotation speed of the blower (including ON / OFF), the switching of the first refrigerant flow switching device 11 and the like are controlled, and each operation mode described later is executed.
  • the control device 60 of the present embodiment is constituted by a microcomputer having a control arithmetic processing means such as a CPU (Central Processing Unit). Moreover, it has a memory
  • the control arithmetic processing means executes processing based on the program data to realize control.
  • the high-pressure detection device 37 is installed in the discharge side piping of the compressor 10 that has a high pressure in the refrigerant circuit.
  • the low-pressure detection device 38 is installed in a pipe on the refrigerant inflow side of the accumulator 19 that has a low pressure in the refrigerant circuit.
  • the high pressure detection device 37 and the low pressure detection device 38 transmit a signal based on the detected pressure to the control device 60.
  • the control device 60 controls each device of the outdoor unit 1 based on the pressure detected by processing the transmitted signal.
  • the indoor unit 2 is equipped with a load-side heat exchanger 15 serving as a second heat exchanger.
  • the load side heat exchanger 15 is connected to the outdoor unit 1 by the extension pipe 4.
  • the load-side heat exchanger 15 performs heat exchange between air supplied from a blower (not shown) and the refrigerant, and generates heating air or cooling air to be supplied to the indoor space 7.
  • the load side heat exchanger 15 acts as a condenser in the case of an operation for heating the indoor space 7.
  • each indoor unit 2 has a control device that controls the devices in the indoor unit 2.
  • FIG. 2 shows an example in which four indoor units 2 are connected, and are illustrated as an indoor unit 2a, an indoor unit 2b, an indoor unit 2c, and an indoor unit 2d from the bottom of the page.
  • the load side heat exchanger 15 is also loaded from the lower side of the page with the load side heat exchanger 15a, the load side heat exchanger 15b, the load side heat exchanger 15c, and the load side heat exchange. It is shown as a container 15d.
  • the number of indoor units 2 connected is not limited to the four shown in FIG.
  • the refrigeration cycle apparatus 100 determines the operation mode of the outdoor unit 1 to be either the cooling operation mode or the heating operation mode based on an instruction from each indoor unit 2. That is, the refrigeration cycle apparatus 100 can perform the same operation (cooling operation or heating operation) for all of the indoor units 2 and adjusts the indoor temperature.
  • each indoor unit 2 can be operated / stopped freely.
  • the operation mode executed by the refrigeration cycle apparatus 100 includes a cooling operation mode in which all the driven indoor units 2 perform a cooling operation (including a stop), and all of the driven indoor units 2 are in a heating operation. There is a heating operation mode for executing (including stopping). Below, each operation mode is demonstrated with the flow of a refrigerant
  • FIG. 3 is a refrigerant circuit diagram illustrating a refrigerant flow when the refrigeration cycle apparatus 100 is in the cooling operation mode.
  • the cooling operation mode will be described by taking as an example a case where a cooling load is generated in all the load-side heat exchangers 15.
  • a pipe indicated by a thick line indicates a pipe through which the refrigerant flows, and a flow direction of the refrigerant is indicated by a solid line arrow.
  • the control device 60 switches the first refrigerant flow path so that the refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12. Switch the device 11.
  • the low-temperature and low-pressure refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12 via the first refrigerant flow switching device 11.
  • the refrigerant that has flowed in is condensed and liquefied while dissipating heat to the outdoor air in the heat source side heat exchanger 12, becomes a high-pressure liquid refrigerant, and flows out of the outdoor unit 1.
  • the high-pressure liquid refrigerant that has flowed out of the outdoor unit 1 passes through the extension pipe 4 and flows into each of the indoor units 2 (2a to 2d).
  • the high-pressure liquid refrigerant that has flowed into the indoor unit 2 (2a to 2d) flows into the expansion device 16 (16a to 16d), and is throttled and decompressed by the expansion device 16 (16a to 16d). It flows out as a phase refrigerant.
  • the refrigerant that has passed through the expansion device 16 (16a to 16d) flows into each of the load side heat exchangers 15 (15a to 15d) acting as an evaporator, and absorbs heat from the air circulating around the load side heat exchanger 15. Thus, it becomes a low-temperature and low-pressure gas refrigerant.
  • the low-temperature and low-pressure gas refrigerant flows out of the indoor unit 2 (2a to 2d), flows into the outdoor unit 1 again through the extension pipe 4, passes through the first refrigerant flow switching device 11, and passes through the accumulator 19. Then, it is sucked into the compressor 10 again.
  • the opening degree (opening area) of the expansion devices 16a to 16d is determined based on the detected temperature of the load-side heat exchanger gas refrigerant temperature detection device 28 and the control device 60 of each outdoor unit 2 from the control device 60 of the outdoor unit 1 (FIG. It is controlled so that the temperature difference (superheat degree) between the evaporation temperature transmitted by communication to the target value (not shown) approaches the target value.
  • the indoor units 2 perform the cooling operation. However, when the cooling operation mode is executed, it is not necessary to flow the refrigerant to the load-side heat exchanger 15 (including the thermo-off) having no heat load. For this reason, the indoor unit 2 stops operation. At this time, the expansion device 16 corresponding to the stopped indoor unit 2 is fully closed or set to a small opening at which the refrigerant does not flow.
  • FIG. 4 is a refrigerant circuit diagram illustrating a refrigerant flow when the refrigeration cycle apparatus 100 is in the heating operation mode.
  • the heating operation mode will be described by taking as an example a case where a thermal load is generated in all the load-side heat exchangers 15.
  • a pipe indicated by a thick line indicates a pipe through which the refrigerant flows, and a flow direction of the refrigerant is indicated by a solid line arrow.
  • the control device 60 uses the first refrigerant flow switching device 11, the refrigerant discharged from the compressor 10, and the heat source side heat exchanger 12. It switches so that it may flow into indoor unit 2 without going through.
  • the low-temperature and low-pressure refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure gas refrigerant, passes through the first refrigerant flow switching device 11, and flows out of the outdoor unit 1.
  • the high-temperature and high-pressure gas refrigerant that has flowed out of the outdoor unit 1 flows into each of the indoor units 2 (2a to 2d) through the extension pipe 4.
  • the high-temperature and high-pressure liquid refrigerant that has flowed out of the load-side heat exchanger 15 (15a to 15d) flows into the expansion device 16 (16a to 16d), is throttled and decompressed by the expansion device 16 (16a to 16d), It becomes a low-pressure two-phase refrigerant and flows out of the indoor unit 2 (2a to 2d).
  • the low-temperature and low-pressure two-phase refrigerant that has flowed out of the indoor unit 2 flows into the outdoor unit 1 again through the extension pipe 4.
  • the opening degree (opening area) of the expansion devices 16a to 16d is determined based on the condensation temperature transmitted from the control device 60 of the outdoor unit 1 to the control device (not shown) of each indoor unit 2 through communication, Control is performed such that the temperature difference (degree of supercooling) from the detected temperature of the heat exchanger liquid refrigerant temperature detecting device 27 approaches the target value.
  • the low-temperature and low-pressure two-phase refrigerant that has flowed into the outdoor unit 1 flows into the heat source side heat exchanger 12, absorbs heat from the air flowing around the heat source side heat exchanger 12, and evaporates to form a low-temperature and low-pressure gas refrigerant or low-temperature and low-pressure. It becomes a two-phase refrigerant with a large dryness.
  • the low-temperature and low-pressure gas refrigerant or the two-phase refrigerant is again sucked into the compressor 10 via the first refrigerant flow switching device 11 and the accumulator 19.
  • the heating operation mode When the heating operation mode is executed, it is not necessary to flow the refrigerant to the load-side heat exchanger 15 (including the thermo-off) that has no heat load.
  • the heating operation mode if the expansion device 16 corresponding to the load-side heat exchanger 15 having no heating load is fully closed or has a small opening at which the refrigerant does not flow, the load-side heat exchanger of the indoor unit 2 that is not operating. In 15, the refrigerant is cooled and condensed by the ambient air, the refrigerant accumulates, and the refrigerant circuit as a whole may fall short of the refrigerant. Therefore, during heating operation, the opening degree (opening area) of the expansion device 16 corresponding to the load-side heat exchanger 15 having no heat load is set to a large opening degree such as full opening to prevent accumulation of refrigerant.
  • the heat source side heat exchanger 12 acts as a condenser, and the heat source side heat exchanger 12 has a high-temperature and high-pressure gas.
  • the refrigerant flows in and condenses, liquefies through a two-phase region, and flows out as a high-temperature and high-pressure liquid refrigerant.
  • the load side heat exchanger 15 acts as a condenser, and the load side heat exchanger 15 (15a to 15d)
  • the refrigerant flows in and condenses, liquefies through a two-phase region, and flows out as a high-temperature and high-pressure liquid refrigerant.
  • the refrigerant used in the refrigeration cycle apparatus 100 is a substance that is generally used as a refrigerant, such as R32, R410A, etc., a device for improving the stability of the refrigerant in the refrigerant circuit. It can be used as it is, without applying.
  • a disproportionation reaction such as 1,1,2-trifluoroethylene (HFO-1123) represented by C 2 H 1 F 3 and having one double bond in the molecular structure is performed.
  • the substance mixed with the substance having a disproportionation reaction is not limited to these.
  • HC-290 (propane) or the like may be mixed.
  • Any material having thermal performance that can be used as a refrigerant of the refrigeration cycle apparatus 100 may be used.
  • the mixing ratio may be any mixing ratio.
  • a substance that causes a disproportionation reaction is used as a refrigerant as it is, the following problems occur. For example, in a place where there is a substance in a liquid state where the distance between adjacent substances is very close, such as a liquid phase, two phases, etc., if some strong energy is applied, the adjacent substances react to each other and become It will change and will not function as a refrigerant. In addition, there is a possibility that an accident such as a pipe rupture may occur due to a rapid pressure rise due to heat generation.
  • the refrigerating machine oil filled in the refrigerant circuit is mainly composed of either polyol ester or polyvinyl ether, and a part of the refrigerating machine oil filled in the compressor 10 circulates in the refrigerant circuit together with the refrigerant.
  • Both the polyol ester and the polyvinyl ether are refrigerating machine oils that are easily soluble in a refrigerant having one double bond in the molecular structure.
  • HFO-1123 is dissolved to some extent in the refrigerating machine oil.
  • the refrigerating machine oil is not limited to this as long as it is compatible with the refrigerant, and another type of oil may be used.
  • FIG. 5 is a solubility diagram of the refrigerating machine oil of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • High solubility means that many refrigerants are dissolved in the refrigeration oil
  • low solubility means that only a small amount of refrigerant is dissolved in the refrigeration oil.
  • FIG. 5 shows the relationship between the solubility and the pressure for each of the refrigerant temperatures T1, T2, and T3.
  • T1, T2, and T3 are different temperatures, and the formula (1) is established.
  • the refrigerant temperature As shown in FIG. 5, under the same pressure condition, the lower the refrigerant temperature, the higher the solubility, and under the same temperature condition, the higher the refrigerant pressure, the higher the solubility.
  • the refrigerant When the refrigerant is dissolved in the refrigerating machine oil, the refrigerating machine oil molecules are present between the refrigerant molecules. Therefore, if the solubility of the refrigerant in the refrigerating machine oil is large, the refrigerating machine oil exists between many refrigerant molecules.
  • the refrigerant disproportionation reaction is a phenomenon in which adjacent refrigerant molecules react with each other. For this reason, if the refrigerating machine oil having compatibility with the refrigerant is used, the refrigerant oil molecules are present between the refrigerant molecules, so that the disproportionation reaction of the refrigerant hardly occurs.
  • solubility of the refrigerant in the refrigeration oil the greater the effect of suppressing the disproportionation reaction of the refrigerant. Practically, if the solubility is 50 wt% (weight%) or more, many refrigerants are dissolved in the refrigerating machine oil, so that the disproportionation reaction can be suppressed.
  • FIG. 6 is a diagram showing an outline of the configuration of a plate fin tube type heat exchanger used in the heat source side heat exchanger 12, the load side heat exchanger 15 (15a to 15d) and the like in the first embodiment of the present invention. is there.
  • a plate fin tube type heat source side heat exchanger 12 or load side heat exchanger 15 (here, referred to as heat exchanger 12 or 15) includes a first connection pipe 41, a second connection pipe 42, and a surrounding area. It has a heat transfer tube 43, fins 44, a first header 47, and a second header 48 for exchanging heat between air or the like as a heat medium and an internal refrigerant.
  • the configuration of the heat exchanger 12 or 15 will be described in more detail.
  • the heat exchanger 12 or 15 has a configuration in which a plurality of fins 44 are arranged at intervals, and a plurality of heat transfer tubes 43 are arranged through the plurality of fins 44.
  • One end of both ends of the plurality of heat transfer tubes 43 is connected to the first header 47, and the other end of the heat transfer tubes 43 is connected to the second header 48.
  • a first connection pipe 41 and a second connection pipe 42 that serve as refrigerant inlets and outlets from other devices in the refrigerant circuit are connected to the first header 47 and the second header 48, respectively.
  • the first header 47 or the second header 48 distributes the refrigerant flowing from the first connection pipe 41 or the second connection pipe 42 to each heat transfer pipe 43.
  • the refrigerant that flows in from the heat transfer tubes 43 is joined.
  • FIG. 6 shows a case where there is one first header 47 and one second header 48, and the same number of heat transfer tubes 43 are connected to each of the first header 47 and the second header 48.
  • the solid line arrow indicates the direction of refrigerant flow when the heat exchanger 12 or 15 acts as a condenser, and the broken line arrow indicates the case where the heat exchanger 12 or 15 acts as an evaporator.
  • the direction in which the refrigerant flows is shown. This also applies to FIGS. 8 and 9 described later.
  • a high-temperature and high-pressure gas refrigerant flows into the heat exchanger 12 or 15.
  • the high-temperature and high-pressure gas refrigerant that has flowed into the heat exchanger 12 or 15 from the first connection pipe 41 is distributed by the first header 47 and flows into the heat transfer pipes 43.
  • the heat transfer tube 43 and the fins 44 are condensed by exchanging heat with surrounding air and the like, and liquefied through a two-phase region in which gas and liquid are mixed to become a high-temperature and high-pressure liquid refrigerant. From the second header 48, and flows into the second connection pipe 42.
  • a low-temperature and low-pressure two-phase refrigerant flows into the heat exchanger 12 or 15.
  • the low-temperature and low-pressure two-phase refrigerant that has flowed into the heat exchanger 12 or 15 from the second connection pipe 42 is distributed by the second header 48 and flows into the heat transfer pipes 43.
  • the heat transfer tubes 43 and fins 44 evaporate by exchanging heat with the surrounding air and the like, and the dryness of the two-phase refrigerant increases, resulting in a two-phase refrigerant or gas refrigerant with a low temperature and low pressure and high dryness. It flows out from the heat pipe 43, merges at the first header 47, and flows out to the first connection pipe 41.
  • the heat exchanger 12 or 15 when the flow rate of the refrigerant flowing inside the heat transfer tube 43 becomes too large, the pressure loss of the refrigerant in the heat transfer tube 43 becomes too large. For this reason, there is a limit to the flow rate of the refrigerant that can flow with respect to the inner diameter of one heat transfer tube 43. Therefore, when the heat transfer tube 43 is thin, it is necessary to increase the number of the heat transfer tubes 43 in order to flow the refrigerant at the same flow rate as when the heat transfer tube 43 is thick. In addition, the heat transfer tube 43 has a larger heat transfer area of the heat transfer tube 43 with respect to the flow rate of the refrigerant flowing inside, and the performance of the heat exchanger 12 or 15 is improved.
  • the heat transfer tube 43 having a thin outer diameter such as 7 mm or 5 mm is usually used.
  • the heat exchanger 12 or 15 is configured using the plurality of heat transfer tubes 43, and the first connection tube 41 or the second connection tube 42 (here, the connection tube 41 or 42) is required to be distributed or merged with the plurality of heat transfer tubes 43.
  • the first header 47 or the second header 48 (here, referred to as the header 47 or 48) is used. It is general because it can.
  • the header 47 or 48 is connected to a plurality of heat transfer tubes 43 and is distributed or merged.
  • the header 47 or 48 is often composed of a circular tube thicker than the heat transfer tubes 43.
  • the header 47 or 48 may have any structure as long as it can distribute or merge the refrigerant of the plurality of heat transfer tubes 43.
  • the cross section may be rectangular, elliptical, or the like.
  • the material may also be copper, aluminum or the like. What is necessary is just to have the intensity
  • FIG. 7 is a cross-sectional view showing the relationship between the header 47 or 48 and the heat transfer tube 43 used in the heat exchanger of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • a plurality of heat transfer tubes 43 are inserted into the header 47 or 48. Since FIG. 7 shows a cross section, the heat transfer tube 43 appears to be one, but the heat transfer tube 43 overlaps in a direction perpendicular to the paper surface. Actually, a plurality of heat transfer tubes 43 are connected to one header 47 or 48.
  • the heat exchanger 12 or 15 acts as a condenser, a high-pressure liquid refrigerant flows into the second header 48. Moreover, when the heat exchanger 12 or 15 acts as an evaporator, it may flow into the first header 47 of the low-pressure two-phase refrigerant.
  • the inner diameter of the header 47 or 48 is larger than the outer diameter of the heat transfer tube 43.
  • a hole is made in the side surface of the header 47 or 48 to insert the heat transfer tube 43, and the header 47 or 48 and the heat transfer tube 43 are fixed by brazing or the like.
  • the refrigerant flowing into the header 47 or 48 Since the refrigerant flowing into the header 47 or 48 has an inertial force, it collides with the pipe inner wall surface (inner surface) 50 of the header 47 or 48 facing the center 45 or 46 of the outlet 45 (refrigerant outlet) of the heat transfer tube 43. The direction of flow in a substantially perpendicular direction can be changed. If the refrigerant flowing into the header 47 or 48 collides with the inner surface 50 of the header 47 or 48 when the collision energy is large, the collision energy causes a disproportionation reaction for a substance that causes a disproportionation reaction. May be a factor. Therefore, in the present embodiment, conditions (use of compatible refrigerating machine oil) are provided for the refrigerant to be used so as to suppress the disproportionation reaction.
  • the collision energy between the inner surface 50 of the header 47 or 48 and the refrigerant is obtained by the equation (2).
  • the disproportionation reaction is a property in which the same type of substances react with each other and change into different substances. This disproportionation reaction is likely to occur when some strong energy is applied from the outside in a state where the distance between adjacent substances such as liquid components and two-phase liquid components is very close. On the other hand, in the gas state, the distance between the refrigerant molecules is considerably longer than in the liquid state. For this reason, in the gas state, even if a large amount of HFO-1123, which is a substance that causes a disproportionation reaction, is included, the disproportionation reaction is unlikely to occur.
  • the behavior of the jet of refrigerant flowing into the header 47 or 48 from the pipe will be examined.
  • the length of the inner diameter of the pipe is d (mm) and the distance from the outlet of the pipe to the collision surface of the jet flowing out from the outlet is L (mm)
  • the following points are generally known in fluid mechanics: Yes.
  • the turbulence component of the jet is large, and when the value of (L / d) is greater than or equal to the predetermined value, the turbulence of the jet The components disappear and the flow is completely stabilized.
  • the predetermined value is 20-30.
  • the inner diameter d and the distance L are applied to the heat transfer tube 43 and the inner surface 50 of the header 47 or 48 facing the heat transfer tube 43, the inner diameter d becomes the inner diameter of the heat transfer tube 43 as shown in FIG. Further, the distance L is the distance from the center 45 or 46 of the outlet of the heat transfer tube 43 to the inner surface 50 of the header 47 or 48 and the portion facing the center 45 or 46 of the outlet of the heat transfer tube 43.
  • the heat exchanger 12 or 15 acts as an evaporator and the two-phase refrigerant flowing out of the heat transfer tube 43 collides with the inner surface 50 of the first header 47. Therefore, if the refrigerant circuit is filled with compatible refrigerating machine oil, the turbulence of the jet remains, such as a position where the value of (L / d) is less than 20 and greater than 0 from the inner surface 50 of the header 47 or 48. Even if the center 45 or 46 of the outlet of the heat transfer tube 43 is installed at a certain position, the disproportionation reaction of the liquid refrigerant or the two-phase refrigerant due to the collision with the inner surface 50 hardly occurs.
  • the inner diameter of the header 47 or 48 is 17.05 mm
  • the inner diameter of the heat transfer tube 43 is 7.44 mm
  • the center 45 or 46 of the outlet of the heat transfer tube 43 is in contact with the inner surface of the header 47 or 48.
  • the distance L that is the inner diameter of the header 47 or 48 is d is the inner diameter of the heat transfer tube 43
  • the value of (L / d) is 2.3. Therefore, a turbulence component that is considerably smaller than 20 to 30 and considerably larger remains.
  • the condensation temperature which is the temperature of the refrigerant in the condenser
  • the expansion device 16 is controlled so that the degree of supercooling of the refrigerant at the outlet of the condenser is about 10 ° C. Therefore, if the condensation temperature is about 50 ° C., about 40 ° C. refrigerant flows out at the outlet of the condenser. Therefore, the refrigerant flowing into the second header 48 is in a saturated pressure state where the temperature is about 40 ° C. and the pressure is 50 ° C.
  • the refrigerant flowing into the second header 48 is in a state of a temperature between about 40-50 ° C. and a saturation pressure where the pressure is 50 ° C. . Therefore, if the solubility of the refrigerant in the refrigerating machine oil is high at these temperatures and pressures, the refrigerant disproportionation reaction hardly occurs. Practically, in the state where the refrigerant is at these temperatures and pressures, if the solubility of the refrigerant in the refrigerating machine oil is 50 wt% (weight percent) or more, many refrigerants are dissolved in the refrigerating machine oil, so disproportionation The reaction can be suppressed.
  • the value of (L / d) is less than 10 if the refrigerant flowing into the second header 48 has a solubility of 50 wt% (weight%) or more in the refrigeration oil and is dissolved in the refrigeration oil. Even when the refrigerant is ejected from such a relatively close position and collides with the inner surface 50 of the second header 48, the disproportionation reaction hardly occurs.
  • the refrigerant flowing into the second header 48 is a liquid refrigerant
  • the amount of refrigerant filled in the refrigerant circuit is small, for example, a two-phase refrigerant having a dryness greater than 0 and less than or equal to 0.2 may flow into the second header 48. Even in this case, the same effect is obtained.
  • the refrigerant disproportionation reaction is likely to occur when the distance between adjacent substances such as liquid refrigerant and two-phase refrigerant is very close.
  • the heat exchanger 12 or 15 acts as a condenser and the liquid refrigerant or the two-phase refrigerant flows into the second header 48 installed on the outlet side thereof has been described.
  • the heat source side heat exchanger 12 acts as an evaporator
  • the two-phase refrigerant flows out from the heat transfer tube 43 and the two-phase refrigerant flows into the first header 47. Even in such a case, the disproportionation reaction of the refrigerant is likely to occur.
  • the disproportionation reaction can be made difficult to occur. Even when the load side heat exchanger 15 acts as an evaporator during the cooling operation, the two-phase refrigerant may flow out from the load side heat exchanger 15 to the first header 47. In this case as well, the same structure as the heat source side heat exchanger 12 may be used.
  • the driving frequency of the compressor 10 and the rotational speed of a blower (not shown) attached to the heat source side heat exchanger 12 are controlled to adjust the refrigerant in the evaporator.
  • the evaporation temperature which is the temperature
  • the expansion device 16 is controlled so that the degree of superheat of the refrigerant at the outlet of the evaporator is about 0 to 5 ° C. Therefore, the refrigerant flowing into the first header 47 from the heat transfer tube 43 is in a saturated pressure state where the temperature is about 0 ° C. and the pressure is about 0 ° C.
  • the solubility of the refrigerant in the refrigerating machine oil is 50 wt% (weight%) or more, a large amount of refrigerant dissolves in the refrigerating machine oil, so that the disproportionation reaction can be made difficult to occur. Therefore, if the refrigerant flowing into the first header 47 has a solubility of 50 wt% (weight%) or more in the refrigeration oil and is dissolved in the refrigeration oil, the value of (L / d) is less than 10. Even when the refrigerant is ejected from such a relatively close position and collides with the inner surface 50 of the first header 47, the disproportionation reaction hardly occurs.
  • a two-phase refrigerant having a dryness of 0.8 or more and 0.99 or less flows into the first header 47, for example.
  • the center 45 or 46 of the outlet of the heat transfer tube 43 is illustrated as if it is oriented in the normal direction of the inner surface 50 of the header 47 or 48, but the direction is not limited thereto.
  • the outlet of the heat transfer tube 43 may be connected to the inner surface 50 of the header 47 or 48 in an inclined manner, and has the same effect.
  • the shape of the outlet of the heat transfer tube 43 is not particularly limited, and may be any shape. Although shown here as a circular tube, the outlet of the heat transfer tube 43 may have a long hole shape formed by cutting obliquely with respect to the tube axis of the heat transfer tube 43, or other shapes may be used. Have the same effect.
  • the equivalent diameter of the heat transfer tube 43 at this time is the inner diameter d.
  • a hole is formed in the side surface of the header 47 or 48 and the heat transfer tube 43 is inserted, and the header 47 or 48 and the heat transfer tube 43 are fixed by brazing or the like.
  • the center 45 or 46 of the outlet of the heat transfer tube 43 is often installed so as to protrude to the inner side of the position in contact with the inner surface of the header 47 or 48, and the amount of protrusion is 1 of the inner diameter of the header 47 or 48 / 3 or less in many cases. That is, the distance L is often smaller than the inner diameter of the header 47 or 48 and larger than 2/3 of the inner diameter of the header 47 or 48.
  • the path is divided into four, and the four heat transfer tubes 43 are connected to the header 47 or 48, but the number of the heat transfer tubes 43 is four. It is not limited to books.
  • FIG. 8 is a schematic diagram of another configuration of the heat exchanger of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • the heat exchanger 12 or 15 shown in FIG. 8 is configured to include a plurality of headers on the refrigerant inflow side and the refrigerant outflow side, respectively.
  • one end of the heat exchanger 12 or 15 has two first headers 47a and a first header 47b.
  • the first connection pipe 41 is the same number (two in this case) of branch pipes as the number of headers.
  • One of the branched pipes is connected to the first header 47a, and the other pipe is connected to the first header 47b.
  • the first header 47a and the first header 47b are connected to the two heat transfer tubes 43, respectively.
  • the other end of the heat exchanger 12 or 15 also has two second headers 48a and second headers 48b.
  • the second connection pipe 42 is branched into two as many as the number of headers, one pipe is connected to the second header 48a, and the other pipe is connected to the second header 48b.
  • the second header 48 a and the second header 48 b are connected to the two heat transfer tubes 43, respectively.
  • connection pipe 41 or 42 is a branch pipe, and a heat exchanger structure connected to a plurality of (here, two) headers 47 or 48 has the same effect.
  • FIG. 9 is a schematic diagram of another configuration of the heat exchanger of the refrigeration cycle apparatus according to Embodiment 1 of the present invention.
  • the heat exchanger 12 or 15 in FIG. 9 is a so-called 1-2-pass heat exchanger in which the number of passes (number of channels) changes in the middle of the channel.
  • the first connection pipe 41 is connected to the first header 47.
  • the first header 47 is branched into six paths, and the number of paths is halved by joining two paths along the way.
  • the second connection pipe 42 is connected to the second header 48, and the second header 48 is connected to the three heat transfer pipes 43. For this reason, the number of heat transfer tubes 43 connected to the first connection pipe 41 via the first header 47 is six, and the number of heat transfer tubes 43 connected to the second connection pipe 42 via the second header 48 is It becomes three.
  • the same effect can be obtained even in a heat exchanger structure in which the number of heat transfer tubes 43 connected to the first header 47 and the number of heat transfer tubes 43 connected to the second header 48 are different.
  • the configuration of the 1-2 path, the number of pipes, and the like are not limited thereto.
  • FIG. 10 is a schematic diagram of another heat transfer tube used in the heat exchanger of the refrigeration cycle apparatus according to Embodiment 1 of the present invention. So far, the description has been made on the assumption that the heat transfer tube 43 is a circular tube. However, the shape of the heat transfer tube 43 is not limited to a circular tube.
  • FIG. 10 shows a flat tube having a flat channel structure in which the inside is divided into a plurality of (here, four) channels (microchannels) 49.
  • the cross-sectional areas of the respective flow paths 49 inside one heat transfer tube 43 are summed up in considering the above-described configuration in which disproportionation reaction hardly occurs.
  • the total sectional area is treated as the inner sectional area of one heat transfer tube 43. A specific example will be described below.
  • the heat exchanger 12 or 15 of FIG. 6 is configured by a heat transfer tube 43 that is internally divided into four flow paths 49.
  • the four heat transfer tubes 43 are connected to the first connection pipe 41 via the first header 47, and the four heat transfer tubes 43 are connected to the first header pipe 48 via the second header 48. 2 connected to the connecting pipe 42. Therefore, when the inner cross-sectional areas of all the flow paths 49 in the heat transfer tube 43 are the same, the number of the flow paths 49 in one heat transfer pipe 43 (here, four), the inner cross-sectional area of the flow paths 49, and The value multiplied by is taken as the total inner cross-sectional area.
  • the value converted into an equivalent diameter based on the total inner cross-sectional area is treated as the inner diameter d.
  • the heat exchanger 12 or 15 with which disproportionation reaction hardly occurs can be comprised by making the relationship between the distance L and the internal diameter d into the same thing as the description mentioned above.
  • the case where the inner cross-sectional areas of all the flow paths 49 in the heat transfer tube 43 are the same has been described as an example, but the present invention is not limited to this, and the cross-sectional areas of the inner cross-sectional areas of some of the flow paths 49 are May be different.
  • the inner cross-sectional areas of the two flow paths 49 at both ends may be different from the inner cross-sectional areas of the other flow paths 49.
  • the number of the flow paths 49 of the heat transfer tubes 43 is not limited to four.
  • the heat transfer tube 43 has a flat tube shape, and when the heat transfer tube 43 is connected to the header 47 or 48, a flat tube shape hole is formed in the header 47 or 48 and the heat transfer tube 43 is formed in the header 47 or 48. You may connect directly. Further, a circular hole may be formed in the header 47 or 48, and the header 47 or 48 may be connected to the header 47 or 48 via a joint that is deformed from a flat tube shape to a circular tube shape.
  • the refrigeration cycle apparatus 100 has several operation modes. In these operation modes, the refrigerant flows through the extension pipe 4 that connects the outdoor unit 1 and the indoor unit 2.
  • the high pressure detection device 37 and the low pressure detection device 38 are installed to control the refrigeration cycle high pressure and low pressure to target values, but may be a temperature detection device that detects a saturation temperature.
  • coolant flow path switching device 11 was shown as if it were a four-way valve, it is not restricted to this, It uses the two-way flow path switching valve and the three-way flow path switching valve similarly, You may comprise so that a refrigerant
  • a heat blower is attached to the heat source side heat exchanger 12 and the load side heat exchangers 15a to 15d, and in many cases, condensation or evaporation is promoted by air blowing, but it is not limited to this.
  • the load side heat exchangers 15a to 15d a panel heater using radiation can be used, and as the heat source side heat exchanger 12, a water-cooled type that moves heat by water or antifreeze. Things can also be used. Any heat exchanger that can dissipate or absorb heat can be used.
  • the heat source side heat exchanger 12 or the load side heat exchangers 15a to 15d have fins 44 in order to improve the heat transfer performance, but sufficient heat transfer performance can be obtained by using only the heat transfer tube 43. May not have the fins 44.
  • the cooling / heating switching type refrigeration cycle apparatus 100 in which the indoor unit 2 performs only the cooling operation or the heating operation has been described as an example.
  • the present invention is not limited to this. Absent.
  • the indoor unit 2 can arbitrarily select one of a cooling operation and a heating operation, and the entire system can perform a mixed operation of the indoor unit 2 that performs the cooling operation and the indoor unit 2 that performs the heating operation.
  • the present invention can also be applied to a refrigeration cycle apparatus and has the same effect.
  • air conditioners such as room air conditioners, to which only one indoor unit 2 can be connected, refrigeration equipment to connect a showcase and a unit cooler, etc., constituting a refrigerant circuit and using a refrigeration cycle If it is a refrigeration cycle device that supplies heat, the same effect is obtained.
  • first header 47 and the second header 48 are connected to both ends of the heat source side heat exchanger 12 or the load side heat exchangers 15a to 15d
  • the present invention is not limited to this.
  • a refrigerant distributor and a capillary tube are connected to one end of the heat source side heat exchanger 12 or the load side heat exchangers 15a to 15d, and the other end of the heat source side heat exchanger 12 or the load side heat exchangers 15a to 15d. You may comprise so that a header may be connected to.
  • any other configuration may be used.
  • FIG. A second embodiment of the present invention will be described with reference to the drawings. In the following, the second embodiment will be described focusing on the differences from the first embodiment. Note that the modification applied in the configuration part of the first embodiment is also applied to the same configuration part of the second embodiment.
  • FIG. 11 is a circuit configuration diagram of the refrigeration cycle apparatus according to Embodiment 2 of the present invention.
  • a refrigeration cycle apparatus 100 shown in FIG. 11 includes a refrigerant circulation circuit A in which an outdoor unit 1 and a heat medium relay unit 3 that is a relay unit are connected by an extension pipe 4 to circulate refrigerant.
  • the refrigeration cycle apparatus 100 includes a heat medium circulation circuit B in which the heat medium converter 3 and the indoor unit 2 are connected by a pipe (heat medium pipe) 5 and a heat medium such as water or brine circulates.
  • the heat medium relay unit 3 includes a load side heat exchanger 15a and a load side heat exchanger 15b that perform heat exchange between the refrigerant circulating in the refrigerant circuit A and the heat medium circulating in the heat medium circuit B.
  • the heat medium relay unit 3 is located separately from the outdoor unit 1 and the indoor unit 2, for example, a ceiling that is inside the building 9 but separate from the indoor space 7 as shown in FIG. 1. It is installed in a space such as the back (hereinafter simply referred to as space 8).
  • the heat medium relay 3 can also be installed in a common space where there is an elevator or the like.
  • the operation mode executed by the refrigeration cycle apparatus 100 includes a cooling only operation mode in which all of the driven indoor units 2 execute a cooling operation and a heating operation in which all of the driven indoor units 2 execute a heating operation. There is an operation mode. Further, there are a cooling main operation mode executed when the cooling load is larger, and a heating main operation mode executed when the heating load is larger.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12 via the first refrigerant flow switching device 11 and dissipates heat to the surrounding air. It condenses and becomes high-pressure liquid refrigerant and flows out of the outdoor unit 1 through the check valve 13a. Then, it flows into the heat medium relay unit 3 through the extension pipe 4. The refrigerant flowing into the heat medium relay unit 3 passes through the opening / closing device 17a, expands in the expansion device 16a and the expansion device 16b, and becomes a low-temperature and low-pressure two-phase refrigerant.
  • the two-phase refrigerant flows into each of the load side heat exchanger 15a and the load side heat exchanger 15b acting as an evaporator, absorbs heat from the heat medium circulating in the heat medium circuit B, and becomes a low-temperature and low-pressure gas refrigerant. .
  • the gas refrigerant flows out of the heat medium relay unit 3 through the second refrigerant flow switching device 18a and the second refrigerant flow switching device 18b. Then, it flows into the outdoor unit 1 again through the extension pipe 4.
  • the refrigerant that has flowed into the outdoor unit 1 passes through the check valve 13d, and is sucked into the compressor 10 again via the first refrigerant flow switching device 11 and the accumulator 19.
  • the heat medium is cooled by the refrigerant in both the load side heat exchanger 15a and the load side heat exchanger 15b.
  • the cooled heat medium flows through the pipe 5 by the pump 21a and the pump 21b.
  • the heat medium flowing into the use side heat exchangers 26a to 26d through the second heat medium flow switching devices 23a to 23d absorbs heat from the indoor air.
  • the indoor air is cooled to cool the indoor space 7.
  • the refrigerant that has flowed out of the use side heat exchangers 26a to 26d flows into the heat medium flow control devices 25a to 25d, passes through the first heat medium flow switching devices 22a to 22d, and passes through the load side heat exchanger 15a and the load side.
  • the heat medium flow control devices 25a to 25d corresponding to the use side heat exchangers 26a to 26d without heat load are fully closed. Further, the heat medium flow control devices 25a to 25d corresponding to the use side heat exchangers 26a to 26d having the heat load adjust the opening degree to adjust the heat load in the use side heat exchangers 26a to 26d.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows out of the outdoor unit 1 through the first refrigerant flow switching device 11 and the first connection pipe 4a and the check valve 13b. To do. Then, it flows into the heat medium relay unit 3 through the extension pipe 4. The refrigerant flowing into the heat medium relay unit 3 flows into the load side heat exchanger 15a and the load side heat exchanger 15b through the second refrigerant flow switching device 18a and the second refrigerant flow switching device 18b, respectively. The heat is radiated to the heat medium circulating in the heat medium circuit B, and becomes a high-pressure liquid refrigerant.
  • the high-pressure liquid refrigerant expands in the expansion device 16a and the expansion device 16b to become a low-temperature and low-pressure two-phase refrigerant, and flows out of the heat medium relay unit 3 through the opening / closing device 17b. Then, it flows into the outdoor unit 1 again through the extension pipe 4.
  • the refrigerant flowing into the outdoor unit 1 passes through the second connection pipe 4b and the check valve 13c, flows into the heat source side heat exchanger 12 acting as an evaporator, absorbs heat from the surrounding air, and is a low-temperature and low-pressure gas refrigerant. It becomes.
  • the gas refrigerant is again sucked into the compressor 10 via the first refrigerant flow switching device 11 and the accumulator 19.
  • the operation of the heat medium in the heat medium circuit B is the same as in the cooling only operation mode.
  • the heat medium is heated by the refrigerant, and is radiated to the indoor air in the use-side heat exchanger 26a and the use-side heat exchanger 26b.
  • the indoor space 7 is heated.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12 via the first refrigerant flow switching device 11 and radiates and condenses to the surrounding air. Then, it becomes a two-phase refrigerant and flows out of the outdoor unit 1 through the check valve 13a. Then, it flows into the heat medium relay unit 3 through the extension pipe 4. The refrigerant flowing into the heat medium relay unit 3 flows into the load-side heat exchanger 15b acting as a condenser through the second refrigerant flow switching device 18b, and dissipates heat to the heat medium circulating in the heat medium circuit B. And high pressure liquid refrigerant.
  • the high-pressure liquid refrigerant expands in the expansion device 16b and becomes a low-temperature and low-pressure two-phase refrigerant.
  • the two-phase refrigerant flows into the load-side heat exchanger 15a acting as an evaporator through the expansion device 16a, absorbs heat from the heat medium circulating in the heat medium circuit B, and becomes a low-pressure gas refrigerant. It flows out of the heat medium relay unit 3 through the path switching device 18a. Then, it flows into the outdoor unit 1 again through the extension pipe 4.
  • the refrigerant that has flowed into the outdoor unit 1 passes through the check valve 13d, and is sucked into the compressor 10 again via the first refrigerant flow switching device 11 and the accumulator 19.
  • the heat of the refrigerant is transmitted to the heat medium by the load side heat exchanger 15b.
  • the heated heat medium flows in the pipe 5 by the pump 21b.
  • the heat medium that has flowed into the use side heat exchangers 26a to 26d for which heating is requested by operating the first heat medium flow switching devices 22a to 22d and the second heat medium flow switching devices 23a to 23d radiates heat to the indoor air.
  • the indoor air is heated to heat the indoor space 7.
  • the cold heat of the refrigerant is transmitted to the heat medium in the load side heat exchanger 15a.
  • the cooled heat medium flows through the pipe 5 by the pump 21a.
  • the heat medium that has flowed into the use side heat exchangers 26a to 26d for which cooling is requested by operating the first heat medium flow switching devices 22a to 22d and the second heat medium flow switching devices 23a to 23d absorbs heat from the indoor air. To do.
  • the indoor air is cooled to cool the indoor space 7.
  • the heat medium flow control devices 25a to 25d corresponding to the use side heat exchangers 26a to 26d without heat load are fully closed.
  • the heat medium flow control devices 25a to 25d corresponding to the use side heat exchangers 26a to 26d having the heat load adjust the opening degree to adjust the heat load in the use side heat exchangers 26a to 26d.
  • Heating main operation mode In the heating main operation mode, the high-temperature and high-pressure gas refrigerant discharged from the compressor 10 passes through the first refrigerant flow switching device 11, passes through the first connection pipe 4 a and the check valve 13 b, and then the outdoor unit 1. Spill from. Then, it flows into the heat medium relay unit 3 through the extension pipe 4. The refrigerant flowing into the heat medium relay unit 3 flows into the load-side heat exchanger 15b acting as a condenser through the second refrigerant flow switching device 18b, and dissipates heat to the heat medium circulating in the heat medium circuit B. And high pressure liquid refrigerant.
  • the high-pressure liquid refrigerant expands in the expansion device 16b and becomes a low-temperature and low-pressure two-phase refrigerant.
  • the two-phase refrigerant flows into the load-side heat exchanger 15a acting as an evaporator via the expansion device 16a, absorbs heat from the heat medium circulating in the heat medium circuit B, and passes through the second refrigerant flow switching device 18a. And flows out of the heat medium relay unit 3. Then, it flows into the outdoor unit 1 again through the extension pipe 4.
  • the refrigerant flowing into the outdoor unit 1 passes through the second connection pipe 4b and the check valve 13c, flows into the heat source side heat exchanger 12 acting as an evaporator, absorbs heat from the surrounding air, and is a low-temperature and low-pressure gas. Becomes a refrigerant.
  • the gas refrigerant is again sucked into the compressor 10 via the first refrigerant flow switching device 11 and the accumulator 19.
  • the operations of the heat exchangers 26a to 26d are the same as those in the cooling main operation mode.
  • the first heat medium flow switching device 22 corresponding to the use side heat exchanger 26 performing the heating operation and The second heat medium flow switching device 23 is switched to a flow path connected to the load side heat exchanger 15b for heating. Further, the first heat medium flow switching device 22 and the second heat medium flow switching device 23 corresponding to the use side heat exchanger 26 performing the cooling operation are connected to the cooling load side heat exchanger 15a. Switch to the flow path. For this reason, in each indoor unit 2, heating operation and cooling operation can be performed freely.
  • the first heat medium flow switching device 22 and the second heat medium flow switching device 23 can switch a three-way flow path such as a three-way valve, and can open and close a two-way flow path such as an on-off valve. What is necessary is just to be able to switch a flow path, such as combining two.
  • the first heat medium can be obtained by combining two things such as a stepping motor drive type mixing valve that can change the flow rate of the three-way flow path and two things that can change the flow rate of the two-way flow path such as an electronic expansion valve.
  • the flow path switching device 22 and the second heat medium flow path switching device 23 may be used.
  • the heat medium flow control device 25 may be installed as a control valve having a three-way flow path with a bypass pipe that bypasses the use-side heat exchanger 26 other than the two-way valve. Further, the heat medium flow control device 25 may be a stepping motor drive type that can control the flow rate flowing through the flow path, and may be a two-way valve or a device in which one end of the three-way valve is closed. Further, as the heat medium flow control device 25, a device that opens and closes a two-way flow path such as an open / close valve may be used, and the average flow rate may be controlled by repeating ON / OFF.
  • first refrigerant flow switching device 11 and the second refrigerant flow switching device 18 are shown as if they were four-way valves. However, the present invention is not limited to this, and a two-way flow switching valve or a three-way flow switching is possible. A plurality of valves may be used so that the refrigerant flows in the same manner.
  • the same is true even when only one use-side heat exchanger 26 and one heat medium flow control device 25 are connected, and the load-side heat exchanger 15 and the expansion device 16 are the same.
  • the heat medium flow control device 25 is not limited thereto, and may be built in the indoor unit 2. 3 and the indoor unit 2 may be configured separately.
  • the heat medium flow control device 25 may not be provided. Also good.
  • the heat medium for example, brine (antifreeze), water, a mixture of brine and water, a mixture of water and an additive having a high anticorrosive effect, or the like can be used. Therefore, in the refrigeration cycle apparatus 100, even if the heat medium leaks into the indoor space 7 through the indoor unit 2, a highly safe heat medium is used, which contributes to an improvement in safety. Become.
  • the heat source side heat exchanger 12 and the use side heat exchangers 26a to 26d are provided with a blower, and in many cases, condensation or evaporation is promoted by blowing, but this is not restrictive.
  • a blower for example, as the use side heat exchangers 26a to 26d, a panel heater using radiation can be used.
  • a water-cooled type that moves heat by water or antifreeze can also be used. Any structure that can dissipate or absorb heat can be used.
  • a plate-type heat exchanger is generally used as the load-side heat exchanger 15.
  • the load-side heat exchanger 15 is not limited to a plate type, but can be any type that can exchange heat between the refrigerant and the heat medium. It may be a thing.
  • the number of pumps 21a and 21b is not limited to one, and a plurality of small capacity pumps may be arranged in parallel.
  • the refrigeration cycle apparatus of the present embodiment accommodates the compressor 10, the four-way valve (first refrigerant flow switching device) 11, and the heat source side heat exchanger 12 in the outdoor unit 1, and air and refrigerant in the air-conditioning target space Are used in the indoor unit 2, and the load-side heat exchanger 15 and the expansion device 16 are accommodated in the heat medium converter 3.
  • the outdoor unit 1 and the heat medium converter 3 are connected by an extension pipe 4 to circulate the refrigerant
  • the indoor unit 2 and the heat medium converter 3 are connected by a set of two pipes 5 each.
  • the load-side heat exchanger 15 exchanges heat between the refrigerant and the heat medium.
  • the explanation has been given by taking as an example a system capable of mixed operation of the indoor unit 2 that performs the cooling operation and the indoor unit 2 that performs the heating operation.
  • the present invention is not limited to this.
  • the outdoor unit 1 and the heat medium relay unit 3 described in the first embodiment can be combined and applied to a system that performs only a cooling operation or a heating operation in the indoor unit 2 and has the same effect.
  • Embodiment 3 As shown in the first embodiment and the second embodiment, it is common to use a four-way valve as the first refrigerant flow switching device 11, but this is not a limitation. For example, a plurality of two-way flow switching valves and three-way flow switching valves may be used so that the refrigerant flows in the same manner as when a four-way valve is used.
  • the present invention is not limited to this.
  • the number of indoor units 2 is one, etc., there is no problem even if the accumulator 19 is not provided because the surplus refrigerant is small in the refrigerant circuit.
  • Heat source unit (outdoor unit), 2, 2a, 2b, 2c, 2d indoor unit, 3 heat medium converter (relay unit), 4 extension pipe (refrigerant pipe), 4a first connection pipe, 4b second connection pipe, 5 piping (heat medium piping), 6 outdoor space, 7 indoor space, 8 outdoor space such as the back of the ceiling and indoor space, 9 building, 10 compressor, 11 1st refrigerant flow switching device (Four-way valve), 12 heat source side heat exchanger (first heat exchanger), 13a, 13b, 13c, 13d check valve, 15, 15a, 15b, 15c, 15d load side heat exchanger (second heat Exchanger, 16, 16a, 16b, 16c, 16d throttle device, 17a, 17b switchgear, 18, 18a, 18b second refrigerant flow switching device, 19 accumulator, 21a, 21b pump, 22, 22a, 22b, 2 c, 22d First heat medium flow switching device, 23, 23a, 23b, 23c, 23d Second heat medium flow switching device, 25, 25a

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention porte sur un dispositif à cycle de réfrigération (100) qui forme un circuit d'agent de refroidissement grâce à un agent de refroidissement qui le remplit et qui comprend une substance ayant la propriété de provoquer une réaction disproportionnée, et à une huile de réfrigérateur qui est compatible avec l'agent de refroidissement. Au moins un premier échangeur de chaleur ou un second échangeur de chaleur comprend une pluralité de tuyaux de transfert de chaleur (43) et un collecteur (47 ou 48). Le diamètre interne du collecteur (47 ou 48) est supérieur au diamètre interne du tuyau de transfert de chaleur (43), et la section d'extrémité, sur le côté de sortie d'agent de refroidissement du tuyau de transfert de chaleur (43), est disposée de façon à faire face à une surface de paroi interne de tuyau (50) du collecteur. La section d'extrémité, sur le côté de sortie d'agent de refroidissement du tuyau de transfert de chaleur (43), est disposée en une position telle que la valeur de L/d est inférieure à 20 et supérieure à 0, si la distance du centre (45 ou 46) de la section d'extrémité, sur le côté de sortie d'agent de refroidissement du tuyau de transfert de chaleur (43), à la surface de paroi interne de tuyau (50) du collecteur correspondant au centre (45 ou 46) est la distance L et que le diamètre interne ou le diamètre équivalent au niveau de la section d'extrémité, sur le côté de sortie d'agent de refroidissement du tuyau de transfert de chaleur (43), est le diamètre interne d.
PCT/JP2014/070221 2014-07-31 2014-07-31 Dispositif à cycle de réfrigération WO2016016999A1 (fr)

Priority Applications (3)

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JP2016537680A JPWO2016016999A1 (ja) 2014-07-31 2014-07-31 冷凍サイクル装置
PCT/JP2014/070221 WO2016016999A1 (fr) 2014-07-31 2014-07-31 Dispositif à cycle de réfrigération
GB1700157.9A GB2543206A (en) 2014-07-31 2014-07-31 Refrigeration cycle device

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WO2018047511A1 (fr) * 2016-09-12 2018-03-15 三菱電機株式会社 Échangeur de chaleur et climatiseur

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JP2009191212A (ja) * 2008-02-15 2009-08-27 Idemitsu Kosan Co Ltd 冷凍機用潤滑油組成物
JP2013210184A (ja) * 2008-04-01 2013-10-10 Honeywell Internatl Inc 熱伝達回路への油戻り率を改善する方法
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WO2018047511A1 (fr) * 2016-09-12 2018-03-15 三菱電機株式会社 Échangeur de chaleur et climatiseur
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