EP2578966B1 - Dispositif de réfrigération et dispositif de refroidissement et de chauffage - Google Patents

Dispositif de réfrigération et dispositif de refroidissement et de chauffage Download PDF

Info

Publication number
EP2578966B1
EP2578966B1 EP11786271.4A EP11786271A EP2578966B1 EP 2578966 B1 EP2578966 B1 EP 2578966B1 EP 11786271 A EP11786271 A EP 11786271A EP 2578966 B1 EP2578966 B1 EP 2578966B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
region
equal
heat exchanger
less
Prior art date
Legal status (The legal status 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 status listed.)
Active
Application number
EP11786271.4A
Other languages
German (de)
English (en)
Other versions
EP2578966A1 (fr
EP2578966A4 (fr
Inventor
Kazuhiko Marumoto
Akira Fujitaka
Yoshikazu Kawabe
Shoichi Yokoyama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Corp
Original Assignee
Panasonic Corp
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 Panasonic Corp filed Critical Panasonic Corp
Publication of EP2578966A1 publication Critical patent/EP2578966A1/fr
Publication of EP2578966A4 publication Critical patent/EP2578966A4/fr
Application granted granted Critical
Publication of EP2578966B1 publication Critical patent/EP2578966B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F25B39/00—Evaporators; Condensers
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
    • 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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • F25B2600/00—Control issues
    • F25B2600/21—Refrigerant outlet evaporator temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements

Definitions

  • the present invention relates to a refrigerating appliance and an air conditioner both employing a refrigerant therein.
  • Chlorofluorocarbons have been used as a refrigerant in a refrigerating appliance, but have posed a problem of ozone layer depletion. Accordingly, HCFCs are recently used as a substitute refrigerant and, in particular, an HFC (R410A) is mostly used now, as shown in Fig. 11 .
  • Patent Document 2 discloses a heat exchanger comprising a plurality of plate fins, arranged with a prescript spacing there-between in the thickness direction and a plurality of heat transfer tubes which pass through plate fins in thickness direction.
  • the width of plate fins tapers in a continuous or stepwise manner from a larger fin width to a smaller fin width.
  • Each plate fin includes through-holes though which heat transfer tubes are passed.
  • the through-holes are arranged in three groups provided with different diameter sizes.
  • Heat transfer tubes are provided in at least two different diameter sizes, wherein each individual heat transfer tube has only one of said diameter sizes. Heat transfer tubes having the larger diameter are arranged on the upper part of heat exchanger and the smaller diameter heat transfer tubes are arranged in the lower part of heat exchanger.
  • Patent Document 2 further discloses that a known heat exchanger may be installed in an outdoor unit of an air conditioner, which can function as a condenser with respect to the refrigerant, or which may be functioning as an evaporator with respect to the refrigerant.
  • the R410A refrigerant has a high global warming potential (GWP) of 2088 and is problematic in terms of prevention of global warming.
  • GWP global warming potential
  • a refrigerant such as an HFO1234yf of GWP4 has been proposed as a refrigerant having a low GWP, but this refrigerant is smaller than the R410A refrigerant in refrigerating capacity per unit volume.
  • this refrigerant is employed in a conventional apparatus to obtain the same capacity as the R410A refrigerant, it is necessary to increase a refrigerant circulation volume by increasing a speed of a compressor.
  • the present invention has been developed to overcome the above-described problem inherent in the conventional technology. It is accordingly an objective of the present invention to provide a highly efficient refrigerating appliance and air conditioner capable of securing a predetermined cooling capacity by reducing the pressure loss in the heat exchanger even using a refrigerant that is smaller than the R410A refrigerant in refrigerating capacity per unit volume.
  • the present invention is directed to a refrigerating appliance as defined in claim 1.
  • the refrigerating appliance includes at least a compressor, an outdoor heat exchanger, a throttling device and an indoor heat exchanger, all connected to one another via connecting pipes to form an annular refrigerant circuit.
  • the refrigerant circuit is designed to be filled with a refrigerant that has a small refrigerating capacity per unit volume compared with an R410A refrigerant.
  • the indoor heat exchanger includes a plurality of fins arrayed at regular intervals and a plurality of heat-transfer tubes extending through the fins in a direction generally perpendicular thereto with the refrigerant flowing through the heat-transfer tubes.
  • the indoor heat exchanger also includes at least three regions, in which the refrigerant flows through the heat-transfer tubes at different mass speeds.
  • the three regions are an inlet region, an intermediate region and an outlet region.
  • the indoor heat exchanger serves as an evaporator, the refrigerant flows through the inlet region, the intermediate region and the outlet region in this order, and the three regions are arranged such that an airflow successively passes the inlet region and the intermediate region in parallel to the outlet region, or such that an airflow successively passes the outlet region, the intermediate region and the inlet region.
  • the refrigerant flows through the outlet region, the intermediate region and the inlet region in this order, and the three regions are arranged such that an airflow successively passes the intermediate region and the inlet region in parallel to the outlet region, or such that an airflow successively passes the inlet region, the intermediate region and the outlet region.
  • the pressure loss in the heat exchanger can be reduced even if a refrigerant that has a smaller refrigerating capacity per unit volume than the R410A refrigerant is used, not only can a cooling capacity of a refrigerating appliance be ensured, but an efficiency thereof can be also enhanced.
  • a refrigerating appliance uses, as a refrigerant filled in a refrigerant circuit, a refrigerant having a small refrigerating capacity per unit volume compared with an R410A refrigerant and is provided with an indoor heat exchanger that includes a plurality of fins arrayed at regular intervals and a plurality of heat-transfer tubes extending through the fins in a direction generally perpendicular thereto with the refrigerant flowing through the heat-transfer tubes.
  • the indoor heat exchanger also includes at least three regions, in which the refrigerant flows through the heat-transfer tubes at different mass speeds, thereby optimizing an area of passage. The three regions are an inlet region, an intermediate region and an outlet region.
  • the refrigerant flows through the inlet region, the intermediate region and the outlet region in this order, and the three regions are arranged such that an airflow successively passes the inlet region and the intermediate region in parallel to the outlet region, or such that an airflow successively passes the outlet region, the intermediate region and the inlet region.
  • the indoor heat exchanger serves as a condenser
  • the refrigerant flows through the outlet region, the intermediate region and the inlet region in this order, and the three regions are arranged such that an airflow successively passes the intermediate region and the inlet region in parallel to the outlet region, or such that an airflow successively passes the inlet region, the intermediate region and the outlet region.
  • This aspect of the present invention optimizes the mass speed to reduce a pressure loss during cooling, thereby making it possible to obtain an appropriate temperature difference between air and the refrigerant.
  • a second aspect of the present invention is such that in the refrigerating appliance according to the first aspect, when the indoor heat exchanger serves as an evaporator, the at least three regions include an inlet region, an intermediate region and an outlet region along a flow of the refrigerant, wherein a mass speed per unit capacity of the refrigerant in the heat-transfer tubes in the inlet region is greater than or equal to 0.44 g/mm 2 hW and less than 0.50 g/mm 2 hW, that of the refrigerant in the heat-transfer tubes in the intermediate region is greater than or equal to 0.14 g/mm 2 hW and less than 0.16 g/mm 2 hW, and that of the refrigerant in the heat-transfer tubes in the outlet region is greater than or equal to 0.13 g/mm 2 hW and less than 0.15 g/mm 2 hW.
  • This aspect of the present invention optimizes the mass speed to reduce a pressure loss during cooling, thereby making it possible to obtain an appropriate temperature difference between
  • a third aspect of the present invention is such that in the refrigerating appliance according to the first or second aspect, a quality of wet vapor of the refrigerant in the inlet region, the intermediate region and the outlet region in a standard cooling capacity is greater than or equal to 0.215 and less than 0.437, greater than or equal to 0.437 and less than 0.8, and greater than or equal to 0.8 and less than or equal to 1.0, respectively.
  • This aspect of the present invention optimizes the mass speed to reduce a pressure loss during cooling, thereby making it possible to obtain an appropriate temperature difference between air and the refrigerant.
  • a fourth aspect of the present invention is such that in the refrigerating appliance according to any one of the first to third aspects, a quality of wet vapor of the refrigerant in the inlet region, the intermediate region and the outlet region in an intermediate cooling capacity is greater than or equal to 0.23 and less than 0.408, greater than or equal to 0.408 and less than 0.645, and greater than or equal to 0.645 and less than or equal to 1.0, respectively.
  • This aspect of the present invention optimizes the mass speed to reduce a pressure loss during cooling, thereby making it possible to obtain an appropriate temperature difference between air and the refrigerant.
  • a fifth aspect of the present invention is such that in the refrigerating appliance according to any one of the first to fourth aspects, when the indoor heat exchanger serves as a condenser, a mass speed per unit capacity of the refrigerant in the outlet region, the intermediate region and the inlet region is greater than or equal to 0.120 g/mm 2 hW and less than 0.121 g/mm 2 hW, greater than or equal to 0.127 g/mm 2 hW and less than 0.129 g/mm 2 hW, and greater than or equal to 0.446 g/mm 2 hW and less than 0.451 g/mm 2 hW, respectively.
  • This aspect of the present invention can restrain a reduction in performance even in a heating operation and achieve a good balance between a heating performance and a cooling performance, thus making it possible to obtain an optimized annual efficiency.
  • a sixth aspect of the present invention is such that in the refrigerating appliance according to any one of the first to fifth aspects, a quality of wet vapor of the refrigerant in the outlet region, the intermediate region and the inlet region in a standard heating capacity is greater than or equal to 0.408 and less than 1.00, greater than or equal to zero and less than 0.408, and 0.00, respectively.
  • This aspect of the present invention can restrain a reduction in performance even in a heating operation and achieve a good balance between a heating performance and a cooling performance, thus making it possible to obtain an optimized annual efficiency.
  • a seventh aspect of the present invention is such that in the refrigerating appliance according to any one of the first to sixth aspects, a quality of wet vapor of the refrigerant in the outlet region, the intermediate region and the inlet region in an intermediate heating capacity is greater than or equal to 0.681 and less than 1.00, greater than or equal to 0.163 and less than 0.681, and greater than or equal to 0.00 and less than or equal to 0.681, respectively.
  • an air conditioner includes the refrigerating appliance according to any one of the first to seventh aspects and a four-way valve provided in the refrigerating appliance, wherein a direction of flow of the refrigerant flowing through the outdoor heat exchanger and the indoor heat exchanger can be changed for cooling and heating.
  • This aspect of the present invention can switch between a cooling operation and a heating operation.
  • a ninth aspect of the present invention is such that in the refrigerating appliance or the air conditioner according to any one of the first to eighth aspects, a fan is further provided to supply the indoor heat exchanger with air, wherein when the indoor heat exchanger serves as a condenser, a downstream side of a flow of the refrigerant in the indoor heat exchanger is an upstream side of a flow of air created by the fan.
  • This aspect of the present invention can enhance an efficiency during heating.
  • a tenth aspect of the present invention is such that in the refrigerating appliance or the air conditioner according to any one of the first to ninth aspects, a refrigerant whose main component is hydrofluoroolefin having a carbon-carbon double bond or a mixture refrigerant including this refrigerant is filled in the refrigerant circuit.
  • This aspect of the present invention makes use of a refrigerant having a small global warming potential and can accordingly minimize, even if part of the refrigerant that cannot be collected is vented to atmosphere, the influence of the refrigerant on global warming.
  • Embodiments of the present invention are described hereinafter taking the case of an air conditioner, but the present invention is not limited to the embodiments.
  • Fig. 1 is a piping diagram of an air conditioner according to this embodiment.
  • the air conditioner according to the first embodiment includes a compressor 1 for compressing a refrigerant, a four-way valve 2 for switching a refrigerant circuit between a heating operation and a cooling operation, an outdoor heat exchanger 3 for exchanging heat between the refrigerant and outdoor air, a throttling device 4 for reducing a pressure of the refrigerant, and an indoor heat exchanger for exchanging heat between the refrigerant and indoor air.
  • the compressor 1, the four-way valve 2, the outdoor heat exchanger 3, the throttling device 4 and the indoor heat exchanger 5 are circularly connected to one another via connecting pipes.
  • An outdoor unit 10 includes the compressor 1, the four-way valve 2, the outdoor heat exchanger 3 and the throttling device 4, while an indoor unit 11 includes the indoor heat exchanger 5.
  • the outdoor unit 10 and the indoor unit 11 are connected to each other via a connecting pipe A12 and a connecting pipe B13.
  • a refrigerant compressed by the compressor 1 turns into a high-temperature and high-pressure refrigerant, which passes through the four-way valve 2 and is introduced into the outdoor heat exchanger 3.
  • the refrigerant exchanges heat with outdoor air in the outdoor heat exchanger 3 for radiation of heat and turns into a high-pressure liquid refrigerant, which is sent to the throttling device 4.
  • the refrigerant is then reduced in pressure by the throttling device 4 and turns into a low-temperature and low-pressure two-phase refrigerant, which enters the indoor heat exchanger 5 via the connecting pipe B13.
  • the refrigerant exchanges heat with indoor air to absorb heat in the indoor heat exchanger 5.
  • the refrigerant then evaporates and turns into a low-temperature gas refrigerant. In this event, indoor air is cooled to cool an interior of a room and the refrigerant returns to the compressor 1 via the connecting pipe A12 and the four-way valve 2.
  • the refrigerant compressed by the compressor 1 turns into a high-temperature and high-pressure refrigerant, which passes through the four-way valve 2 and is introduced into the indoor heat exchanger 5 via the connecting pipe A12.
  • the indoor heat exchanger 3 the refrigerant exchanges heat with indoor air and is cooled upon radiation of heat.
  • the cooled refrigerant turns into a high-pressure liquid refrigerant.
  • indoor air is heated to heat the interior of the room.
  • the refrigerant is sent to the throttling device 4 via the connecting pipe B13.
  • the refrigerant is then reduced in pressure by the throttling device 4 and turns into a low-temperature and low-pressure two-phase refrigerant, which is introduced into the outdoor heat exchanger 3.
  • the refrigerant exchanges heat with outdoor air and evaporates in the outdoor heat exchanger 3 before it returns to the compressor 1 via the four-way valve 2.
  • the cooling operation and the heating operation are conducted in the above-described manner.
  • the refrigerant circuit constituting the air conditioner according to this embodiment is filled with a refrigerant that has a refrigerating capacity per unit volume smaller than that of the R410A refrigerant.
  • This refrigerant is a refrigerant whose main component is tetrafluoropropene in hydrofluoroolefin having a carbon-carbon double bond.
  • an HFO1234yf is employed as such a refrigerant.
  • Fig. 2 is a table in which the refrigerating capacity per unit volume of the R410A refrigerant and that of the HFO1234yf refrigerant are compared.
  • Fig. 2 indicates, when an evaporative temperature of the evaporator is 5°C and 10°C, a saturated gas density, evaporative latent heat and the refrigerating capacity per unit volume of the evaporator (saturated gas density x evaporative latent heat) of the R410A refrigerant and those of the HFO1234yf refrigerant.
  • the refrigerating capacity per unit volume of the R410A and that of the HFO1234yf in the cooling operation are 7715.1 kJ/m 3 and 3310.5 kJ/m 3 , respectively, and when the evaporative temperature is 10°C, the refrigerating capacity per unit volume of the R410A and that of the HFO1234yf in the cooling operation are 8742.6 kJ/m 3 and 3791.7 kJ/m 3 , respectively. That is, the HFO1234yf is about 1/2.3 times greater than the R410A in the refrigerating capacity per unit volume.
  • the HFO1234yf in order for the HFO1234yf to have the same refrigerating capacity as the R410A, it is necessary to make a volumetric flow rate per unit time (hereinafter referred to as "refrigerant circulation volume") of the HFO1234yf about 2.3 times greater than that of the R410A.
  • refrigerant circulation volume a volumetric flow rate per unit time
  • Fig. 3 depicts an example of the indoor heat exchanger 5 for the R410A refrigerant.
  • This indoor heat exchanger 5 includes a plurality of fins 19 arrayed at regular intervals and a plurality of heat-transfer tubes extending through the fins 19 in a direction generally perpendicular thereto with the refrigerant flowing through the heat-transfer tubes.
  • the indoor heat exchanger 5 also includes a fan 18 to convey air for heat exchange with the refrigerant.
  • the indoor heat exchange 5 has an inlet region 80, an intermediate region 81 and an outlet region 82 along a flow of refrigerant, in which regions the refrigerant flows at different mass speeds.
  • a refrigerant sent from the throttling device 4 enters a heat-transfer tube 50, then passes through a heat-transfer tube 51 and a heat-transfer tube 52, and reaches a heat-transfer tube 53.
  • the heat-transfer tube 53 is branched into four heat-transfer tubes 60, 61, 62, 63, through which respective refrigerants pass before they reach heat-transfer tubes 60', 61', 62', 63'.
  • the refrigerants passing through the heat-transfer tubes 60', 61', 62', 63' reach, for example, a header (not shown), from which two heat-transfer tubes 70, 71 are branched so that almost the same amount of refrigerant may flow through each of the two heat-transfer tubes 70, 71.
  • a header not shown
  • the refrigerants Having passed through the heat-transfer tubes 70, 71, the refrigerants reach heat-transfer tubes 70', 71', pass through the connecting pipe B13 and returns to the compressor 1 via the four-way valve 2.
  • Fig. 4 indicates a mass speed, a quality of wet vapor (dryness), a saturated temperature difference and a refrigerating capacity of a refrigerant in each region when the indoor heat exchanger 5 for the R410A refrigerant shown in Fig. 3 was used and the R410A and the HFO1234yf were used as refrigerants.
  • the saturated temperature difference was used as an indicator of a pressure loss.
  • the saturated temperature difference is a difference between a saturated temperature of a refrigerant obtained from a refrigerant pressure at an inlet of the indoor heat exchanger 5 and that of a refrigerant obtained from a refrigerant pressure at an outlet of the indoor heat exchanger 5.
  • the reason for this is that a relationship between the pressure and the temperature differs depending on the kind of refrigerants and, hence, the pressure losses pertaining to the performance cannot be simply compared as pressure differences.
  • the saturated temperature differences corresponding thereto are generally utilized. It is considered that the pressure loss increases with an increase in saturated temperature difference.
  • Fig. 4 indicates data obtained under the condition that the cooling capacity was maximized by increasing the refrigerant circulation volume with the use of the HFO1234yf.
  • Fig. 5 depicts a PH diagram under the condition of Fig. 4 when the indoor heat exchanger 5 for the R410A refrigerant as shown in Fig. 3 and the HFO1234yf refrigerant were used.
  • a point A indicates an inlet portion of a compressor
  • a point B indicates a discharge portion of the compressor
  • a point C indicates an inlet portion of a condenser
  • a point D indicates an outlet portion of the condenser
  • a point E indicates an inlet portion of an evaporator
  • a point F indicates an outlet portion of the evaporator.
  • a gradient of a line extending from the point E at the inlet portion of the evaporator to the point F at the outlet portion of the evaporator is large. This means that an increase in refrigerant circulation volume results in a large pressure loss. Also, because the refrigerant temperature increases from the point F toward the point E, a temperature difference between the refrigerant and air, i.e., a heat exchange fluid gradually becomes small and is minimal at the point E, i.e., at the inlet of the indoor heat exchanger 5. A reduction in temperature difference between the refrigerant and air is followed by a reduction in the amount of heat exchange and, hence, a predetermined cooling capacity cannot be ensured.
  • Fig. 6 depicts an example of an indoor heat exchanger 5 according to the present invention.
  • the indoor heat exchanger 5 includes a plurality of fins 19 arrayed at regular intervals and a plurality of heat-transfer tubes extending through the fins 19 in a direction generally perpendicular thereto with the refrigerant flowing through the heat-transfer tubes.
  • the indoor heat exchanger 5 also includes a fan 18 to convey air for heat exchange with the refrigerant.
  • a direction of flow of the refrigerant is the same as that of air.
  • the indoor heat exchange 5 has an inlet region 15, an intermediate region 16 and an outlet region 17 along a flow of refrigerant, all of which regions have different mass speeds per unit capacity.
  • a refrigerant sent from the throttling device 4 enters two heat-transfer tubes 20, 21, through which respective refrigerants pass before they reach heat-transfer tubes 20', 21'.
  • the refrigerants passing through the heat-transfer tubes 20', 21' reach, for example, a header (not shown), from which heat-transfer tubes 30, 31, 32, 33, 34, 35, 36 are branched so that almost the same amount of refrigerant may flow through each of the heat-transfer tubes 30, 31, 32, 33, 34, 35, 36.
  • the refrigerants Having passed through the heat-transfer tubes 30, 31, 32, 33, 34, 35, 36, the refrigerants reach heat-transfer tubes 30', 31', 32', 33', 34', 35', 36' and then reach heat-transfer tubes 40', 41', 42', 43', 44', 45' via, for example, a header (not shown) and via heat-transfer tubes 40, 41, 42, 43, 44, 45.
  • the refrigerants then pass through the connecting pipe B13 via, for example, a header (not shown) and return to the compressor 1 via the four-way valve 2.
  • the heat-transfer tubes in the inlet region 15 and those in the intermediate region 16 have a diameter of, for example, 6.35 mm and those in the outlet region 17 have a diameter of, for example, 7 mm.
  • the inlet region 15, the intermediate region 16 and the outlet region 17 may have two, seven and six passes, respectively.
  • Fig. 7 indicates a mass speed, a quality of wet vapor, a saturated temperature difference and a refrigerating capacity of a refrigerant in each region calculated from a simulation in a standard cooling capacity when the indoor heat exchanger 5 according to the present invention as shown in Fig. 3 was used and the HFO1234yf was used as a refrigerant.
  • the mass speed per unit capacity of the refrigerant in the heat-transfer tubes in the inlet region 15 is greater than or equal to 0.44 g/mm 2 hW and less than 0.50 g/mm 2 hW
  • that of the refrigerant in the heat-transfer tubes in the intermediate region 16 is greater than or equal to 0.14 g/mm 2 hW and less than 0.16 g/mm 2 hW
  • that of the refrigerant in the heat-transfer tubes in the outlet region 17 is greater than or equal to 0.13 g/mm 2 hW and less than 0.15 g/mm 2 hW.
  • the quality of wet vapor of the refrigerant in the inlet region 15, the intermediate region 16 and the outlet region 17 in the standard cooling capacity is greater than or equal to 0.215 and less than 0.437, greater than or equal to 0.437 and less than 0.8, and greater than or equal to 0.8 and less than or equal to 1.0, respectively.
  • the quality of wet vapor of the refrigerant in the inlet region 15, the intermediate region 16 and the outlet region 17 in an intermediate cooling capacity is greater than or equal to 0.23 and less than 0.408, greater than or equal to 0.408 and less than 0.645, and greater than or equal to 0.645 and less than or equal to 1.0, respectively.
  • the saturated temperature difference is about 9.5K and the cooling capacity is 3912W, which is about the same as in the case where the R410A refrigerant was used, as shown in Fig. 4 , thus making it possible to ensure the cooling capacity.
  • Fig. 8 depicts a PH diagram under the condition of Fig. 7 when the indoor heat exchanger 5 according to the present invention shown in Fig. 6 and the HFO1234yf refrigerant were used.
  • a point A indicates an inlet portion of a compressor
  • a point B indicates a discharge portion of the compressor
  • a point C indicates an inlet portion of a condenser
  • a point D indicates an outlet portion of the condenser
  • a point E' indicates an inlet portion of an evaporator
  • a point F indicates an outlet portion of the evaporator.
  • a point E indicates an inlet portion of an indoor heat exchanger when the indoor heat exchanger 5 for the R410A was used.
  • the indoor heat exchanger 5 according to the present invention as shown in Fig. 6 was used.
  • the flow of refrigerant in the heating operation is the reverse of that in the cooling operation.
  • a gas refrigerant reaches heat-transfer tubes 40', 41', 42', 43', 44', 45', through which respective refrigerants pass and reach, for example, a header (not shown) via heat-transfer tubes 40, 41, 42, 43, 44, 45.
  • the header is branched into heat-transfer tubes 30', 31', 32', 33', 34', 35', 36' so that almost the same amount of refrigerant may flow through each of them.
  • the refrigerants Having passed through the heat-transfer tubes 30', 31', 32', 33', 34', 35', 36', the refrigerants reach heat-transfer tubes 30, 31, 32, 33, 34, 35, 36, through which the refrigerants pass and reach, for example, a header (not shown).
  • the refrigerant in the header is almost equally divided into two to enter heat-transfer tubes 20', 21'.
  • the refrigerants reach heat-transfer tubes 20, 21, respectively, and are sent to the connecting pipe A13.
  • the refrigerant flows through the outlet region 17, the intermediate region 16 and the inlet region 15 in this order, in which regions the refrigerant has different mass speeds per unit capacity.
  • the mass speed per unit capacity calculated from a simulation is greater than or equal to 0.120 g/mm 2 hW and less than 0.121 g/mm 2 hW in the outlet region 17, greater than or equal to 0.127 g/mm 2 hW and less than 0.129 g/mm 2 hW in the intermediate region 16, and greater than or equal to 0.446 g/mm 2 hW and less than 0.451 g/mm 2 hW in the inlet region 15.
  • the simulation also reveals that the quality of wet vapor in a standard heating capacity is greater than or equal to 0.408 and less than 1.00, greater than or equal to zero and less than 0.408, and 0.00, respectively, and that the quality of wet vapor in an intermediate heating capacity is greater than or equal to 0.681 and less than 1.00, greater than or equal to 0.163 and less than 0.681, and greater than or equal to 0.00 and less than or equal to 0.681, respectively.
  • a direction of flow of the refrigerant is the same direction of air conveyed by the fan 18.
  • a downstream side of the flow of refrigerant in the indoor heat exchanger 5 is an upstream side of the flow of air created by the fan 18, i.e., the refrigerant flows in a direction counter to a direction in which air conveyed by the fan 18 flows. Accordingly, a larger average temperature difference can be obtained compared with a case where the refrigerant and airflow in the same direction, thus resulting in an increase in efficiency.
  • Fig. 9A or 9B depicts an arrangement of the inlet, intermediate and outlet regions.
  • the indoor heat exchanger 5 includes the inlet region 15, the intermediate region 16 and the outlet region 17 arranged in a manner as shown in Fig. 9A or 9B .
  • the three regions may be arranged separately, as shown in Fig. 9A or assembled in a row, as shown in Fig. 9B .
  • the arrangement of the inlet, intermediate and outlet regions is not limited to these figures.
  • Fig. 10 indicates calculation results where the indoor heat exchanger 5 according to the present invention was used and where the mass speed per unit capacity was changed in each of the inlet region 15, the intermediate region 16 and the outlet region 17.
  • the case where the indoor heat exchanger 5 according to the present invention was used is indicated by boldface in the center of each table, in which the capacity during standard cooling, intermediate cooling, standard heating or intermediate heating was set to 100% and the term-efficiency, i.e., the efficiency during each operation was similarly set to 100%.
  • the heating capacity is higher when the mass speed per unit capacity is 0.117 g/mm 2 hW, but Fig. 10 reveals that in terms of the characteristic features of the refrigerant in this invention, it is important to increase the cooling capacity even if the heating capacity is slightly reduced.
  • the tube diameter is standardized, it cannot be arbitrarily selected. Accordingly, the tube diameter or the number of passes is appropriately selected so that the mass speed and the quality of wet vapor as indicated in the above-described embodiment or those close to them can be obtained in any way possible.
  • HFO1234yf a refrigerant whose main component is hydrofluoroolefin having a carbon-carbon double bond may be used.
  • Hydrofluoroolefin may be, for example, HFO1234ze if it is tetrafluoropropene to which HFO1234yf belongs.
  • such a refrigerant may be used alone or in combination with another refrigerant such as, for example, hydrofluorocarbon having no double bond.
  • a mixture refrigerant having tetrafluoropropene (HFO1234yf or HFO1234ze) as an alternative for hydrofluoroolefin and also having difluoromethane (HFC32) as an alternative for hydrofluorocarbon may be used as a refrigerant.
  • a mixture refrigerant having tetrafluoropropene (HFO1234yf) as an alternative for hydrofluoroolefin and also having pentafluoroethane (HFC125) as an alternative for hydrofluorocarbon may be used as a refrigerant.
  • a three-component mixture refrigerant having tetrafluoropropene (HFO1234yf) as an alternative for hydrofluoroolefin and also having pentafluoroethane (HFC125) and difluoromethane (HFC32) as an alternative for hydrofluorocarbon may be used as a refrigerant.
  • the present invention is applicable to a refrigerating appliance having no four-way valve such as, for example, a water heater exclusively for heating or a cooler, a freezer and the like exclusively for cooling.
  • a refrigerating appliance having no four-way valve
  • an indoor heat exchanger and an outdoor heat exchanger serve as a condenser and an evaporator, respectively.
  • the present invention can make use of a refrigerant having a small GWP such as, for example, an HFO1234yf of GWP4.

Landscapes

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

Claims (10)

  1. Appareil de réfrigération comprenant au moins un compresseur (1), une soupape à quatre voies (2), un échangeur de chaleur extérieur (3), un dispositif d'étranglement (4) et un échangeur de chaleur intérieur (5), tous reliés les uns aux autres par l'intermédiaire de tuyaux de raccordement pour former un circuit de fluide frigorigène annulaire, le circuit de fluide frigorigène étant conçu pour être rempli d'un fluide frigorigène qui présente une faible capacité de réfrigération par volume unitaire (6) par rapport à un fluide frigorigène de type R410A ;
    l'échangeur de chaleur intérieur (5) comprenant une pluralité d'ailettes (19) disposées en réseau à intervalles réguliers et une pluralité de tubes de transfert de chaleur (20, 21, 20', 21', 30, 31, 32, 33, 34, 35, 36, 30', 31', 32', 33', 34', 35', 36', 40, 41, 42, 43, 44, 45, 40', 41', 42', 43', 44', 45'), s'étendant à travers les ailettes (19) dans une direction généralement perpendiculaire à celles-ci, le fluide frigorigène s'écoulant à travers les tubes de transfert de chaleur (20, 21, 20', 21', 30, 31, 32, 33, 34, 35, 36, 30', 31', 32', 33', 34', 35', 36', 40, 41, 42, 43, 44, 45, 40', 41', 42', 43', 44', 45') ; et
    l'échangeur de chaleur intérieur (5) comprenant au moins trois zones (15, 16, 17), dans lesquelles le fluide frigorigène s'écoule à travers les tubes de transfert de chaleur (20, 21, 20', 21', 30, 31, 32, 33, 34, 35, 36, 30', 31', 32', 33', 34', 35', 36', 40, 41, 42, 43, 44, 45, 40', 41', 42', 43', 44', 45') à différentes vitesses massiques,
    caractérisé en ce que les trois zones (15, 16, 17) sont une zone d'entrée (15), une zone intermédiaire (16) et une zone de sortie (17) et
    lorsque l'échangeur de chaleur intérieur (5) sert d'évaporateur,
    le fluide frigorigène s'écoule à travers la zone d'entrée (15), la zone intermédiaire (16) et la zone de sortie (17) dans cet ordre et
    les trois zones (15, 16 17) sont disposées de telle sorte qu'un flux d'air traverse successivement la zone d'entrée (15) et la zone intermédiaire (16) parallèlement à la zone de sortie (17) ou de telle sorte qu'un flux d'air traverse successivement la zone de sortie (17), la zone intermédiaire (16) et la zone d'entrée (15) et
    lorsque l'échangeur de chaleur intérieur (5) sert de condenseur,
    le fluide frigorigène s'écoule à travers la zone de sortie (17), la zone intermédiaire (16) et la zone d'entrée (15) dans cet ordre et
    les trois zones (15, 16 17) sont disposées de telle sorte qu'un flux d'air traverse successivement la zone intermédiaire (16) et la zone d'entrée (15) parallèlement à la zone de sortie (17) ou de telle sorte qu'un flux d'air traverse successivement la zone d'entrée (15), la zone intermédiaire (16) et la zone de sortie (17).
  2. Appareil de réfrigération selon la revendication 1, où, lorsque l'échangeur de chaleur intérieur (5) sert d'évaporateur, lesdites au moins trois zones comprennent une zone d'entrée (15), une zone intermédiaire (16) et une zone de sortie (17) le long d'un flux du fluide frigorigène et une vitesse massique par capacité unitaire du fluide frigorigène dans les tubes de transfert de chaleur (20, 21, 20', 21', 30, 31, 32, 33, 34, 35, 36, 30', 31', 32', 33', 34', 35', 36', 40, 41, 42, 43, 44, 45, 40', 41', 42', 43', 44', 45') dans la zone d'entrée (15) est supérieure ou égale à 0,44 g/mm2hW et inférieure à 0,50 g/mm2hW, celle du fluide frigorigène dans les tubes de transfert de chaleur (20, 21, 20', 21', 30, 31, 32, 33, 34, 35, 36, 30', 31', 32', 33', 34', 35', 36', 40, 41, 42, 43, 44, 45, 40', 41', 42', 43', 44', 45') dans la zone intermédiaire (16) est supérieure ou égale à 0,14 g/mm2hW et inférieure à 0,16 g/mm2hW et celle du fluide frigorigène dans les tubes de transfert de chaleur (20, 21, 20', 21', 30, 31, 32, 33, 34, 35, 36, 30', 31', 32', 33', 34', 35', 36', 40, 41, 42, 43, 44, 45, 40', 41', 42', 43', 44', 45') dans la zone de sortie (17) est supérieure ou égale à 0,13 g/mm2hW et inférieure à 0,15 g/mm2hW.
  3. Appareil de réfrigération selon la revendication 1 ou 2, une qualité de vapeur humide du fluide frigorigène dans la zone d'entrée (15), dans la zone intermédiaire (16) et dans la zone de sortie (17) dans une capacité de refroidissement standard étant respectivement supérieure ou égale à 0,215 et inférieure à 0,437, supérieure ou égale à 0,437 et inférieure à 0,8 et supérieure ou égale à 0,8 et inférieure ou égale à 1,0.
  4. Appareil de réfrigération selon l'une quelconque des revendications 1 à 3, une qualité de vapeur humide du fluide frigorigène dans la zone d'entrée (15), dans la zone intermédiaire (16) et dans la zone de sortie (17) dans une capacité de refroidissement intermédiaire étant respectivement supérieure ou égale à 0,23 et inférieure à 0,408, supérieure ou égale à 0,408 et inférieure à 0,645 et supérieure ou égale à 0,645 et inférieure ou égale à 1,0.
  5. Appareil de réfrigération selon l'une quelconque des revendications 1 à 4, où, lorsque l'échangeur de chaleur intérieur (5) sert de condenseur, une vitesse massique par capacité unitaire du fluide frigorigène dans la zone de sortie (17), dans la zone intermédiaire (16) et dans la zone d'entrée (15) est respectivement supérieure ou égale à 0,120 g/mm2hW et inférieure à 0,121 g/mm2hW, supérieure ou égale à 0,127 g/mm2hW et inférieure à 0,129 g/mm2hW et supérieure ou égale à 0,446 g/mm2hW et inférieure à 0,451 g/mm2hW.
  6. Appareil de réfrigération selon l'une quelconque des revendications 1 à 5, une qualité de vapeur humide du fluide frigorigène dans la zone de sortie (17), dans la zone intermédiaire (16) et dans la zone d'entrée (15) dans une capacité de chauffage standard étant respectivement supérieure ou égale à 0,408 et inférieure à 1,00, supérieure ou égale à zéro et inférieure à 0,408 et de 0,00.
  7. Appareil de réfrigération selon l'une quelconque des revendications 1 à 6, une qualité de vapeur humide du fluide frigorigène dans la zone de sortie (17), dans la zone intermédiaire (16) et dans la zone d'entrée (15) dans une capacité de chauffage intermédiaire étant respectivement supérieure ou égale à 0,681 et inférieure à 1,00, supérieure ou égale à 0,163 et inférieure à 0,681 et supérieure ou égale à 0,00 et inférieure ou égale à 0,681.
  8. Climatiseur comprenant un appareil de réfrigération selon l'une quelconque des revendications 1 à 7 et une soupape à quatre voies (2) disposée dans l'appareil de réfrigération, une direction du flux du fluide frigorigène s'écoulant à travers l'échangeur de chaleur extérieur (3) et l'échangeur de chaleur intérieur (5) pouvant être changée pour un refroidissement et un chauffage.
  9. Appareil de réfrigération ou climatiseur selon l'une quelconque des revendications 1 à 8, comprenant en outre un ventilateur (18) utilisable pour alimenter l'échangeur de chaleur intérieur (5) en air, où, lorsque l'échangeur de chaleur intérieur (5) sert de condenseur, un côté en aval d'un flux du fluide frigorigène dans l'échangeur de chaleur intérieur (5) est un côté en amont d'un flux d'air créé par le ventilateur (18).
  10. Appareil de réfrigération ou climatiseur selon l'une quelconque des revendications 1 à 9, un fluide frigorigène dont le constituant principal est une hydrofluorooléfine présentant une double liaison carbone-carbone ou un fluide frigorigène de mélange comprenant ce fluide frigorigène étant rempli dans le circuit de fluide frigorigène.
EP11786271.4A 2010-05-27 2011-04-22 Dispositif de réfrigération et dispositif de refroidissement et de chauffage Active EP2578966B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2010121096A JP2011247482A (ja) 2010-05-27 2010-05-27 冷凍装置および冷暖房装置
PCT/JP2011/002369 WO2011148567A1 (fr) 2010-05-27 2011-04-22 Dispositif de réfrigération et dispositif de refroidissement et de chauffage

Publications (3)

Publication Number Publication Date
EP2578966A1 EP2578966A1 (fr) 2013-04-10
EP2578966A4 EP2578966A4 (fr) 2015-12-09
EP2578966B1 true EP2578966B1 (fr) 2020-08-26

Family

ID=45003568

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11786271.4A Active EP2578966B1 (fr) 2010-05-27 2011-04-22 Dispositif de réfrigération et dispositif de refroidissement et de chauffage

Country Status (6)

Country Link
EP (1) EP2578966B1 (fr)
JP (1) JP2011247482A (fr)
KR (1) KR20130088020A (fr)
CN (1) CN102918338A (fr)
BR (1) BR112012029878A2 (fr)
WO (1) WO2011148567A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2013084455A1 (ja) * 2011-12-08 2015-04-27 パナソニックＩｐマネジメント株式会社 熱交換器及びそれを備える空気調和機
JP6180338B2 (ja) 2014-01-29 2017-08-16 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド 空気調和機
JP6494916B2 (ja) * 2014-03-07 2019-04-03 三菱重工サーマルシステムズ株式会社 熱交換器およびそれを用いた空気調和機
FR3019637A1 (fr) * 2014-04-02 2015-10-09 Bosch Gmbh Robert Evaporateur air/fluide compose d'un echangeur de chaleur a ailettes
FR3028930B1 (fr) 2014-11-20 2016-12-02 Air Liquide Echangeur compact pour le transport cryogenique en injection indirecte
CN106091486A (zh) * 2016-07-15 2016-11-09 珠海格力电器股份有限公司 换热器及具有其的空调器

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3918455A1 (de) * 1989-06-06 1990-12-20 Thermal Waerme Kaelte Klima Verfluessiger fuer ein kaeltemittel einer fahrzeugklimaanlage
JPH04186079A (ja) * 1990-11-16 1992-07-02 Hitachi Ltd 冷蔵庫
JP3979118B2 (ja) * 2002-02-20 2007-09-19 ダイキン工業株式会社 熱交換器、熱交換器の製造方法及び空気調和機
JP2009257745A (ja) * 2008-03-25 2009-11-05 Daikin Ind Ltd 冷凍装置
JP2009270775A (ja) * 2008-05-08 2009-11-19 Sanden Corp 冷凍サイクル
JP5180680B2 (ja) * 2008-05-20 2013-04-10 サンデン株式会社 冷凍サイクル

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
CN102918338A (zh) 2013-02-06
EP2578966A1 (fr) 2013-04-10
KR20130088020A (ko) 2013-08-07
JP2011247482A (ja) 2011-12-08
WO2011148567A1 (fr) 2011-12-01
EP2578966A4 (fr) 2015-12-09
BR112012029878A2 (pt) 2016-08-16

Similar Documents

Publication Publication Date Title
CN107003048B (zh) 空调机
EP2578966B1 (fr) Dispositif de réfrigération et dispositif de refroidissement et de chauffage
EP3343129B1 (fr) Appareil de cycle de réfrigération
JPWO2015111175A1 (ja) ヒートポンプ装置
JPWO2018029784A1 (ja) 熱交換器及びこの熱交換器を備えた冷凍サイクル装置
WO2018131309A1 (fr) Climatiseur
EP3062037B1 (fr) Échangeur thermique et dispositif à cycle de réfrigération utilisant ledit échangeur thermique
JP5627635B2 (ja) 空気調和機
JP5646257B2 (ja) 冷凍サイクル装置
CN103765131A (zh) 热交换器和具备该热交换器的空气调节机
JP2012237518A (ja) 空気調和機
JP2011052850A (ja) ヒートポンプ式温水暖房装置
KR101624622B1 (ko) 공기열 히트펌프를 이용한 온수공급장치
JP4983878B2 (ja) 熱交換器及びこの熱交換器を備えた冷蔵庫、空気調和機
US20220214081A1 (en) Air conditioning apparatus and outdoor unit
JP2015087038A (ja) 熱交換器及び冷凍サイクル装置
KR20050043089A (ko) 히트 펌프
JP2013174407A (ja) 加熱器及び冷凍サイクル装置
JP6956866B2 (ja) 冷凍サイクル装置
CN211823250U (zh) 一种空调器
JP2020173056A (ja) 冷凍サイクル装置
CN116438413A (zh) 制冷循环装置
JP2011252638A (ja) 空気調和機
KR20120077170A (ko) 공기조화기의 실외기

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20130102

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
RA4 Supplementary search report drawn up and despatched (corrected)

Effective date: 20151111

RIC1 Information provided on ipc code assigned before grant

Ipc: F28F 1/32 20060101ALI20151105BHEP

Ipc: F25B 39/00 20060101AFI20151105BHEP

Ipc: F25B 1/00 20060101ALI20151105BHEP

Ipc: F28D 1/04 20060101ALI20151105BHEP

Ipc: F28D 1/047 20060101ALI20151105BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20190902

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20200310

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1306774

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200915

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602011068360

Country of ref document: DE

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201228

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201126

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201127

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201126

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20200826

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1306774

Country of ref document: AT

Kind code of ref document: T

Effective date: 20200826

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201226

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602011068360

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

26N No opposition filed

Effective date: 20210527

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20210422

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210422

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20210430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210430

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210430

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210430

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210422

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210422

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20201226

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20110422

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20230420

Year of fee payment: 13

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20200826