WO2015063853A1 - Cycle de réfrigération et climatiseur - Google Patents

Cycle de réfrigération et climatiseur Download PDF

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Publication number
WO2015063853A1
WO2015063853A1 PCT/JP2013/079224 JP2013079224W WO2015063853A1 WO 2015063853 A1 WO2015063853 A1 WO 2015063853A1 JP 2013079224 W JP2013079224 W JP 2013079224W WO 2015063853 A1 WO2015063853 A1 WO 2015063853A1
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Prior art keywords
refrigerant
heat exchanger
refrigeration cycle
low
heat
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PCT/JP2013/079224
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English (en)
Japanese (ja)
Inventor
佐々木　重幸
禎夫 関谷
小谷　正直
久保田　淳
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株式会社日立製作所
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Priority to PCT/JP2013/079224 priority Critical patent/WO2015063853A1/fr
Publication of WO2015063853A1 publication Critical patent/WO2015063853A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F24F1/16—Arrangement or mounting thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
    • 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
    • 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
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0234—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in series arrangements
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element

Definitions

  • the present invention relates to the configuration of a refrigerant path of a refrigeration cycle of an air conditioner.
  • a copper heat transfer tube is inserted into a hole provided in a strip-like aluminum fin arranged in parallel with a predetermined gap, and then the heat transfer tube is expanded. It is connected with aluminum fins.
  • the heat transfer coefficient between the heat transfer pipe on the refrigerant side and the refrigerant with phase change is high, but the heat transfer coefficient between the air outside the heat transfer pipe and the aluminum fin is low in physical property value . Therefore, the surface area of the aluminum fins is set larger (the enlarged heat transfer surface) than the inner surface area of the heat transfer tube, thereby reducing the magnitude of the heat passing loss (heat resistance).
  • a heat phenomenon occurs in which a refrigerant changes in phase in a heat transfer tube.
  • the refrigerant evaporates when the air temperature is higher than the refrigerant temperature, and conversely condenses when the refrigerant temperature is higher than the air temperature. Therefore, when switching between cooling and heating with a fixed-type heat exchanger, the refrigerant flows in the opposite direction according to the cooling and heating operations, and the evaporation and condensation of the heat exchanger are performed. Is configured to switch.
  • the refrigeration cycle 1 includes a refrigerant compressor 2, a heat exchanger 3 acting as a condenser or an evaporator, a heat exchanger 4, and a refrigerant flow control mechanism 5.
  • the iso-enthalpy change by the throttle passage of the refrigerant flow control mechanism 5 such as an electronic expansion valve changes to a low temperature low pressure (gas-liquid two-phase flow) refrigerant.
  • the (gas-liquid two-phase flow) refrigerant flows in the heat exchanger 4 to be an indoor heat exchanger.
  • the refrigerant absorbs heat of evaporation from the surrounding air and is vaporized. Thereby, the temperature of the air flowing between the aluminum fins can be lowered.
  • the low-temperature low-pressure (gaseous) refrigerant returns from the four-way valve 6 back to the compressor 2 again. Cooling operation is possible by repeating this series of cycles.
  • the (gas) refrigerant that has become high temperature and high pressure in the compressor 2 is guided by the four-way valve 6 to flow into the heat exchanger 4.
  • the flowing direction of the refrigerant is indicated by an arrow whose outline is described by a broken line.
  • the heat exchanger 4 by blowing the surrounding air, the heat-transferred heat is transferred from the high-temperature and high-pressure (gas) refrigerant, and the air that has absorbed heat is discharged, and the heating (heat release) operation is performed.
  • the refrigerant releases heat of condensation and is liquefied to be a high pressure (liquid) refrigerant.
  • refrigerant flows in different directions for cooling and heating, and in the heat exchanger 3 and the heat exchanger 4, respectively.
  • the evaporation and condensation of the refrigerant are carried out.
  • the pressure loss being larger on the evaporator side than on the condenser side, and the increase in pressure loss on the evaporator side tend to lead to work for the compressor. Therefore, the number of appropriate flow paths of the refrigerant flow path formed of the heat transfer pipe in each heat exchanger in the case of using as an evaporator and the case of using as a condenser is different.
  • the refrigerant flow path of the indoor heat exchanger is divided, and a plurality of valve bodies for opening and closing the flow of the refrigerant are provided, and heat exchangers divided by opening and closing each valve body are used in parallel, or in series
  • the technology which changes the number of flow paths of a refrigerant, and improves performance by using as is indicated for example, refer to patent documents 1).
  • FIG. 9 shows an example of the cross-sectional structure of the outdoor unit.
  • the outdoor unit in FIG. 9 includes a relatively large heat exchanger 4 and a fan 8.
  • the air flows 910, 920 on the right side of FIG. 9 show the air flow of the heat exchanger 4 flowed by the fan 8, the air flow 910 on the left side shows the air flow of the heat exchanger 41, and the air flow 920 on the left
  • the air flow of the exchanger 42 is shown.
  • the wind velocity 910 passing through the heat exchanger is high near the fan 8, and conversely, the wind velocity 920 is small in the heat exchanger away from the fan 8.
  • the heat exchanger functions as an evaporator, it is necessary to secure the refrigerant at the outlet of the evaporator at a predetermined degree of superheat, but as shown in FIG. 9, the bias of the wind speed of the air passing through the heat exchanger Also, since the refrigerant flow rate adjustment of the refrigerant is not taken into consideration in the refrigeration cycle, the heat exchanger is configured to be partially overheated.
  • the object of the present invention is to determine the wind speed distribution of the air passing through the heat exchanger while setting the optimum number of refrigerant flow paths at the time of operation, specifically at the time of evaporation and condensation of the refrigerant flowing in the heat exchanger. Accordingly, it is an object of the present invention to provide a refrigeration cycle capable of improving heat exchange performance and an air conditioner having the refrigeration cycle.
  • the refrigeration cycle of the present invention includes a compressor that compresses a low-temperature low-pressure gaseous refrigerant to generate a high-temperature high-pressure gaseous refrigerant, and a four-way valve that switches the circulation direction of the refrigerant.
  • a condenser comprising a heat exchanger for cooling the high temperature / high pressure gas refrigerant into a low temperature / high pressure liquid refrigerant, and the low temperature / high pressure liquid refrigerant flowing in and reducing pressure
  • a parallel connection is made between a refrigerant flow control valve that produces a low-pressure liquid or gas-liquid two-phase refrigerant and a heat exchanger that heats the low-temperature low-pressure liquid or gas-liquid two-phase refrigerant into a low-temperature low-pressure gas refrigerant
  • the refrigerant was allowed to circulate through the pressure reducing / evaporating device.
  • a plurality of heat exchangers are connected in series to cool the high-temperature and high-pressure gaseous refrigerant to form a low-temperature and high-pressure liquid refrigerant, which is depressurized to produce a low-temperature low-pressure liquid or
  • the refrigerant circulates through a pressure reduction / condenser that converts it into a gas-liquid two-phase flow refrigerant and an evaporator that heats the low-temperature low-pressure liquid or the gas-liquid two-phase flow refrigerant into a low-temperature low-pressure gas refrigerant did.
  • the medium flow rate according to the wind speed distribution of the air passing through the heat exchanger while maintaining the optimum number of refrigerant flow paths at the time of evaporation and condensation of the refrigerant flowing in the heat exchanger of the refrigeration cycle Since it is possible to adjust the heat exchange performance of the refrigeration cycle, it is possible to improve the energy saving performance of the refrigeration cycle.
  • FIG. 1 is a view for explaining the flow of refrigerant at the time of evaporation in the first embodiment.
  • FIG. 2 is a view for explaining the flow of the refrigerant at the time of condensation in the first embodiment.
  • FIG. 3 is a view for explaining the flow of the refrigerant at the time of condensation in the second embodiment.
  • FIG. 4 is a view for explaining the flow of the refrigerant at the time of condensation in the third embodiment.
  • FIG. 5 is a view for explaining the flow of the refrigerant at the time of condensation in the fourth embodiment.
  • FIG. 6 is a view for explaining the flow of the refrigerant at the time of condensation in the fifth embodiment.
  • FIG. 7 is a view for explaining the flow of the refrigerant at the time of condensation in the sixth embodiment.
  • FIG. 8 is a view for explaining the flow of the refrigerant in the conventional heat exchanger.
  • FIG. 9 is a view for explaining the wind speed distribution of air passing through the heat exchanger of the
  • Example 1 1 and 2 are diagrams showing the configuration of a typical refrigeration system.
  • the refrigeration cycle 1 includes a compressor 2, a first heat exchanger 3, an upper heat exchanger 41, a lower heat exchanger 42, and refrigerant flow control valves 5a and 5b.
  • a different point from the refrigeration system of FIG. 8 shown above is that the second heat exchanger 4 is divided into an upper heat exchanger 41 and a lower heat exchanger 42.
  • the refrigeration cycle 1 is provided with a compressor 2 for compressing the gaseous refrigerant to a high temperature and high pressure, and a four-way valve 6.
  • the flow path of the refrigerant compressed by the compressor 2 is switched by the four-way valve 6, and it is selected whether the first heat exchanger 3 is used as a condenser or an evaporator of the refrigerant.
  • the upper heat exchanger 41 and the lower heat exchanger 42 function as an evaporator when the first heat exchanger 3 is a condenser, and function as a condenser when the first heat exchanger 3 is an evaporator. .
  • the first heat exchanger 3 is a fin-tube type heat exchanger, and both ends of the plurality of heat transfer pipes are joined to the refrigerant branching / merging portions 301 and 302 and connected to the refrigerant circulation path of the refrigeration cycle 1.
  • the upper heat exchanger 41 and the lower heat exchanger 42 are connected to the refrigerant circulation path of the refrigeration cycle 1 by the refrigerant branching / merging portions 401 a and 402 a and the refrigerant branching / merging portions 401 b and 402 b.
  • the refrigerant branching / merging parts 301, 402a, 402b have a header type refrigerant distribution structure
  • the refrigerant branching / merging parts 302, 401a, 401b have an orifice branch type refrigerant distribution structure.
  • the header type a small diameter branch pipe is provided on the side surface of a thick, pipe-like header in the vertical direction.
  • the header type refrigerant distributor has less throttling structure than the orifice branch type, so the pressure loss at the time of refrigerant flow is small.
  • the present embodiment is not limited to the combination of the orifice branch type and the header type shown in FIG.
  • refrigerant control valves 403, 404 and 405 are connected to the upper heat exchanger 41 and the lower heat exchanger 42, and a connecting pipe for connecting the upper heat exchanger 41 and the lower heat exchanger 42 in series is further provided.
  • 406 and a refrigerant control valve 407 are provided. Although details will be described later, whether the upper heat exchanger 41 and the lower heat exchanger 42 are connected in parallel or in series can be selected by opening and closing the refrigerant control valves 403, 404, 405, 407.
  • a refrigerant flow control valve 5a is provided in the middle of the refrigerant flow path of the first heat exchanger 3 and the upper heat exchanger 41, and the refrigerant flow paths of the first heat exchanger 3 and the lower heat exchanger 42 are provided.
  • a refrigerant flow control valve 5b is provided midway.
  • the refrigerant flow control valves 5a and 5b are also referred to as expansion valves, and perform pressure reduction and flow control of the refrigerant.
  • an electronic expansion valve is suitable for controlling the flow rate according to the operating conditions of cooling and heating.
  • the second heat exchanger 4 is illustrated as being completely divided into the upper heat exchanger 41 and the lower heat exchanger 42, but the refrigerant flow path is divided. It should be done.
  • Aluminum fins (not shown) are made to communicate in the direction of gravity by the upper heat exchanger 41 and the lower heat exchanger 42. As a result, condensed water condensed on the surface of the fins can be quickly led downward, which facilitates the treatment of drain water.
  • FIG. 1 shows the case where the second heat exchanger (upper heat exchanger 41 and lower heat exchanger 42) is an evaporator.
  • FIG. 2 shows the case where the second heat exchanger (upper heat exchanger 41 and lower heat exchanger 42) is a condenser. If the second heat exchanger is an indoor heat exchanger of an air conditioner, FIG. 1 shows the cooling operation, and FIG. 2 shows the heating operation.
  • each refrigerant control valve 407 is “closed”, and the refrigerant control valves 403, 404, and 405 are “opened”. Note that, in FIG. 1, the refrigerant control valve is described as “open” in the case where it is white and as “closed” in the case where it is white so that it is easy to understand.
  • the upper heat exchanger 41 and the lower heat exchanger 42 are connected in parallel.
  • the gaseous refrigerant that has become high temperature and high pressure in the compressor 2 flows into the first heat exchanger 3 according to the setting of the four-way valve 6.
  • the first heat exchanger 3 acts as a condenser, and the heat of condensation of the refrigerant is transferred to the air from the fan which ventilates the first heat exchanger 3 to condense the refrigerant into a liquid.
  • the refrigerant is a low temperature and high pressure liquid refrigerant.
  • the low-temperature high-pressure refrigerant at the outlet of the first heat exchanger 3 passes through the refrigerant flow control valves 5a and 5b provided on the inflow side of the upper heat exchanger 41 and the lower heat exchanger 42 to form the upper heat exchanger 41. And the lower heat exchanger 42.
  • the refrigerant flow control valves 5a and 5b When the low temperature and high pressure refrigerant flows through the refrigerant flow control valves 5a and 5b, the refrigerant is decompressed to be a low temperature and low pressure gas-liquid two-phase flow refrigerant.
  • the upper heat exchanger 41 and the lower heat exchanger 42 function as an evaporator, heat of vaporization is transferred from the air by the ventilating fan to the refrigerant flowing in the heat transfer pipe, the refrigerant is vaporized, and the low temperature low pressure gas It becomes a refrigerant.
  • the heat transfer of the heat of vaporization lowers the temperature of the air and cooling is performed.
  • the low-temperature low-pressure gaseous refrigerant flowing out of the upper heat exchanger 41 and the lower heat exchanger 42 merges, returns to the four-way valve 6, and flows to the compressor 2.
  • the compressor 2 is a high temperature / high pressure gas refrigerant
  • the first heat exchanger 3 acts as a condenser and is a low temperature / high pressure liquid refrigerant
  • a refrigerant system is connected to form a refrigeration system by circulating a refrigerant 5b, and an upper heat exchanger 41 and a lower heat exchanger 42 which function as an evaporator and change the medium to a low-temperature low-pressure gaseous medium.
  • the pressure reduction amount and the flow rate are controlled in accordance with the opening degree of each valve.
  • the opening degree of the valve is set so that the refrigerant completely evaporates at the outlets of the upper heat exchanger 41 and the lower heat exchanger 42.
  • the opening degree of the valve is changed. Details will be described later.
  • the embodiment shown in FIG. 2 is an example in which the second heat exchanger 4 (upper heat exchanger 41 and lower heat exchanger 42) is a condenser.
  • the gaseous refrigerant that has become high temperature and high pressure in the compressor 2 flows into the second heat exchanger 4 according to the setting of the four-way valve 6.
  • the refrigerant control valves 404 and 407 are “opened” and the refrigerant control valves 403 and 405 are “closed”, and the upper heat exchanger 41 and the lower heat exchanger 42 are connected in series, and the high temperature / high pressure gaseous refrigerant is The upper heat exchanger 41 and the lower heat exchanger 42 flow in this order.
  • the refrigerant flow rate is reduced due to the increase in pressure loss, and the heat transfer rate is reduced.
  • the influence of the pressure loss of the refrigerant is small, so that the flow velocity decrease is small. Therefore, the heat transfer coefficient in the pipe between the refrigerant and the inner surface of the heat transfer pipe is improved, and an increase in the amount of heat transfer can be expected.
  • the second heat exchanger 4 is made to act as a condenser, the refrigerant is made to flow in series in the order of the upper heat exchanger 41 and the lower heat exchanger 42 as described above. , Increase the flow rate of the refrigerant to increase the heat transfer amount of the second heat exchanger 4.
  • the gas refrigerant that has become high temperature and high pressure by the compressor 2 flows in the heat transfer pipe of the above-mentioned heat exchanger 4 (the upper heat exchanger 41 and the lower heat exchanger 42 are connected in series), and the heat exchanger Heats condensation heat to the fan air which ventilates 4. Due to the heat transfer of the condensation heat, the refrigerant is liquefied to change from a high temperature / high pressure refrigerant to a low temperature / high pressure liquid refrigerant and flows out from the refrigerant branching / merging portion 401 b of the lower heat exchanger 42. The heat transfer of the condensation heat raises the temperature of the air and heating is performed.
  • the refrigerant flowing out of the heat exchanger 4 is depressurized by the refrigerant flow control valve 5 b to become a low-temperature low-pressure gas-liquid two-phase refrigerant, and flows into the heat exchanger 3.
  • the heat of vaporization is transferred from the fan air which ventilates the heat exchanger 3 to the low-temperature low-pressure liquid or the gas-liquid two-phase refrigerant flowing in the heat transfer pipe.
  • the refrigerant is vaporized by the heat of vaporization, and the refrigerant becomes a low temperature and low pressure gas at the outlet of the heat exchanger 3.
  • the refrigerant at the outlet of the heat exchanger 3 returns to the four-way valve 6 and flows to the compressor 2.
  • the circulation direction of the refrigerant is achieved by switching the four-way valve 6 of the refrigeration cycle in FIGS. 1 and 2 and setting the opening and closing of the refrigerant control valves 403, 404, 405, and 407.
  • segmented into several heat exchanger is made into a series connection from parallel connection.
  • the compressor may be compressed by the liquid to cause an excessive load and damage it, or the reliability may be deteriorated.
  • the refrigerant is set at the outlet of the heat exchanger so as to be in a superheated state (vapor) of several degrees which is a superheated state (vapor) in which the liquid is completely evaporated.
  • the opening degree of the refrigerant flow control valve small, the evaporation pressure can be lowered and the refrigerant can be brought into the superheated state.
  • the power input to the compressor is increased, and the energy saving property of the air conditioner is reduced.
  • the air which ventilates the heat exchanger has a wind speed distribution
  • the amount of heat transfer in each heat transfer tube changes. For this reason, at the heat transfer tube outlet where the wind speed is low, the refrigerant does not completely evaporate and some liquid remains.
  • the refrigerant evaporates and becomes superheated (vapor). Therefore, at the outlet of the heat exchanger, the liquid becomes a liquid refrigerant that is not completely evaporated.
  • the evaporation pressure can be lowered by setting the opening degree of the refrigerant flow control valve small and the liquid can be completely evaporated in all the heat transfer tubes, but the refrigerant is compressed to a predetermined pressure as described above. As a result, the power input to the compressor is increased, and the energy saving performance of the air conditioner is reduced.
  • the superheat state of the refrigerant is controlled uniformly at the divided heat exchanger outlets. Is possible. Therefore, the evaporation pressure of the refrigerant can be set high, the compressor input can be suppressed, and the energy saving performance can be improved.
  • the refrigerant flow control valve may control the overheat state of the refrigerant at the outlet of the heat exchanger constant as described above. It is possible.
  • the appropriate flow rate of the refrigerant can be supplied to each of the divided heat exchangers.
  • Example 2 Next, another configuration example of the heat exchanger 4 of FIG. 2 will be described. While the upper stage heat exchanger 41 and the lower heat exchanger 42 have the same size in FIG. 2, in the example shown in FIG. 3, they are located upstream of the size of the lower heat exchanger 42 located downstream of the refrigerant. The difference is that the size of the upper stage heat exchanger 41 is increased.
  • the refrigerant in the lower heat exchanger 42 can be accelerated more than in the case of FIG. 2 than in the upper heat exchanger 41, and the heat transfer coefficient in the pipe is further improved. Exchange performance can be enhanced.
  • Example 3 As described above, when the flow velocity of the refrigerant increases, the heat transfer coefficient in the pipe increases.
  • the heat transfer tubes are joined together inside the heat exchanger, and the number of heat transfer tubes on the outlet side of the heat exchanger is smaller than that on the inlet side. More specifically, as shown in FIG. 4, the heat transfer tubes are joined as shown by two flow paths and one flow path in the drawing for the refrigerant flow paths shown by dotted lines in the lower heat exchanger 42. The number of outlets is smaller than the number of inlets.
  • the refrigerant can be accelerated at the time of condensation of the refrigerant, and furthermore, the heat exchange performance can be enhanced.
  • the structure of the inlet / outlet of the liquid refrigerant of the heat exchanger in which a plurality of heat transfer pipes are arranged in parallel includes a header type and an orifice branched type refrigerant distribution structure.
  • a header type a small diameter branch pipe is provided on the side surface of a thick, pipe-like header in the vertical direction.
  • the header type refrigerant distributor has less throttling structure than the orifice branch type, and therefore the pressure loss at the time of refrigerant flow is small.
  • coolant branch / junction part 302 of FIG. 5 is an orifice branch type, and the refrigerant
  • Example 4 shown in FIG. 5 the structure of the heat exchanger 4 which divides
  • the refrigerant branching / merging portions 401 a, 402 a, 401 b and 402 b of the upper heat exchanger 41 and the lower heat exchanger 42 are header-type refrigerant distributors. With this configuration, the pressure loss of the refrigerant flowing through the refrigerant branch portion when flowing in series under the condensing condition can be reduced, and the influence of the performance deterioration in the refrigerant branch can be reduced.
  • the heat exchanger 4 is configured by connecting the two heat exchangers of the upper heat exchanger 41 and the lower heat exchanger 42 in series, the flow velocity of the refrigerant increases and the heat transfer coefficient in the pipe increases.
  • the heat exchanger 4 is configured by three heat exchangers of an upper heat exchanger 41, a middle heat exchanger 42, and a lower heat exchanger 43.
  • refrigerant flow control valves 5a, 5b, 5c and refrigerant control valves 403a, 403b, 404a, 404b, 404c, 407a, 407b are provided corresponding to the divided heat exchangers and performing connection switching in series and parallel.
  • the flow velocity of the refrigerant is increased and the heat transfer coefficient in the pipe is increased as compared to the case of dividing into two heat exchangers.
  • the heat exchanger 4 when the heat exchanger 4 is made to act as an evaporator, the upper heat exchanger 41, the middle heat exchanger 42, and the lower heat exchanger 43 are connected in parallel.
  • the refrigerant flow control valves 5a, 5b and 5c are respectively provided, the opening degree of the refrigerant flow control valves 5a, 5b and 5c is adjusted according to the wind velocity distribution of the heat exchanger 4 Since the refrigerant flow rate can be set to a small value, energy efficiency can be improved.
  • Example 6 A sixth embodiment will now be described with reference to FIG.
  • the heat exchanger is divided in the vertical direction, the effects of the present invention can be obtained even with the configuration of the heat exchanger divided in right and left as shown in FIG. Is achieved.
  • the heat exchanger can be applied to a radiator-type heat exchanger for an automobile provided with a refrigerant header in the left-right direction. In this case, it can respond to the wind speed distribution of the horizontal direction of the air which passes a heat exchanger.
  • the refrigerant flow control valve upstream of the divided heat exchangers, it is possible to supply appropriate refrigerant flow rates to the individual heat exchangers even when wind speed distribution occurs due to the housing structure etc. Since heat exchange performance can be enhanced, there is also an effect of improving the degree of freedom in structural design.
  • one of the two heat exchangers has a plurality of configurations, and an example of connecting in parallel when forming an evaporator and connecting in series when forming an condenser has been disclosed.
  • the present invention is not limited to this configuration, and two heat exchangers may be configured in plural, respectively, connected in parallel when forming an evaporator, and connected in series when forming a condenser.
  • the present invention is not limited to the embodiments described above, but includes various modifications.
  • the above-described embodiments are described in detail for easy understanding in the present invention, and the present invention is not necessarily limited to those having all the configurations described.
  • part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment.

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  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

La présente invention concerne un climatiseur qui est en mesure de présenter, pour l'évaporation et la condensation, le nombre optimal de passages de fluide frigorigène à travers lesquels un fluide frigorigène s'écoule dans un échangeur de chaleur, et qui est configuré de telle sorte que les performances d'échange de chaleur peuvent être améliorées en fonction de la répartition de la vitesse du vent de l'air passant à travers l'échangeur de chaleur. Le climatiseur équipé d'un cycle de réfrigération est pourvu de mécanismes de régulation du flux de fluide frigorigène au niveau des entrées d'évaporation de chaque section d'un échangeur de chaleur divisé, lesdits mécanismes de régulation du flux de fluide frigorigène étant prévus de façon à commuter les passages de fluide frigorigène en fonction des états de fonctionnement de l'échangeur de chaleur, c'est-à-dire selon que l'échangeur de chaleur est en mode évaporation ou en mode condensation, et à réguler le débit de fluide frigorigène en fonction de la répartition de la vitesse du vent de l'air passant à travers l'échangeur de chaleur.
PCT/JP2013/079224 2013-10-29 2013-10-29 Cycle de réfrigération et climatiseur WO2015063853A1 (fr)

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JP2023148248A (ja) * 2022-03-30 2023-10-13 株式会社富士通ゼネラル 空気調和機の室内機
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JPWO2016208042A1 (ja) * 2015-06-25 2017-12-21 三菱電機株式会社 空気調和装置
CN110494701B (zh) * 2017-04-18 2023-01-17 三菱电机株式会社 空调机
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JPWO2018193518A1 (ja) * 2017-04-18 2019-11-21 三菱電機株式会社 空気調和機
CN110494701A (zh) * 2017-04-18 2019-11-22 三菱电机株式会社 空调机
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WO2020017036A1 (fr) * 2018-07-20 2020-01-23 三菱電機株式会社 Dispositif à cycle de réfrigération
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JPWO2020017036A1 (ja) * 2018-07-20 2021-06-24 三菱電機株式会社 冷凍サイクル装置
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WO2020148826A1 (fr) * 2019-01-16 2020-07-23 三菱電機株式会社 Climatiseur
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CN114508797B (zh) * 2022-01-28 2024-05-10 青岛海尔空调电子有限公司 热交换装置
CN114593466B (zh) * 2022-02-21 2023-09-12 青岛海信日立空调系统有限公司 空调器
CN114593466A (zh) * 2022-02-21 2022-06-07 青岛海信日立空调系统有限公司 空调器
JP2023148248A (ja) * 2022-03-30 2023-10-13 株式会社富士通ゼネラル 空気調和機の室内機
JP7392757B2 (ja) 2022-03-30 2023-12-06 株式会社富士通ゼネラル 空気調和機の室内機
WO2023206885A1 (fr) * 2022-04-29 2023-11-02 广东美的制冷设备有限公司 Échangeur de chaleur, procédé de commande de trajet d'écoulement pour échangeur de chaleur, support de stockage lisible et climatiseur
WO2024024393A1 (fr) * 2022-07-26 2024-02-01 ハイリマレリジャパン株式会社 Échangeur de chaleur

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