EP3477227B1 - Refrigerating cycle device and outdoor heat exchanger used in same - Google Patents
Refrigerating cycle device and outdoor heat exchanger used in same Download PDFInfo
- Publication number
- EP3477227B1 EP3477227B1 EP16906317.9A EP16906317A EP3477227B1 EP 3477227 B1 EP3477227 B1 EP 3477227B1 EP 16906317 A EP16906317 A EP 16906317A EP 3477227 B1 EP3477227 B1 EP 3477227B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- exchange unit
- heat exchange
- refrigerant
- temperature
- heat transfer
- 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.)
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Links
- 239000003507 refrigerant Substances 0.000 claims description 232
- 238000005057 refrigeration Methods 0.000 claims description 34
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 17
- 230000008014 freezing Effects 0.000 claims description 13
- 238000007710 freezing Methods 0.000 claims description 13
- 230000007246 mechanism Effects 0.000 claims description 8
- 238000004378 air conditioning Methods 0.000 description 34
- 239000012071 phase Substances 0.000 description 19
- 230000007704 transition Effects 0.000 description 15
- 239000000203 mixture Substances 0.000 description 14
- 239000007788 liquid Substances 0.000 description 13
- 230000000052 comparative effect Effects 0.000 description 11
- 239000003921 oil Substances 0.000 description 11
- 238000010257 thawing Methods 0.000 description 11
- 238000010586 diagram Methods 0.000 description 8
- 230000008859 change Effects 0.000 description 5
- 238000001704 evaporation Methods 0.000 description 5
- 230000008018 melting Effects 0.000 description 5
- 238000002844 melting Methods 0.000 description 5
- 239000003657 drainage water Substances 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 4
- 238000009833 condensation Methods 0.000 description 3
- 230000005494 condensation Effects 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- RTZKZFJDLAIYFH-UHFFFAOYSA-N Diethyl ether Chemical compound CCOCC RTZKZFJDLAIYFH-UHFFFAOYSA-N 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 239000007791 liquid phase Substances 0.000 description 2
- 239000012808 vapor phase Substances 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- YCKRFDGAMUMZLT-UHFFFAOYSA-N Fluorine atom Chemical compound [F] YCKRFDGAMUMZLT-UHFFFAOYSA-N 0.000 description 1
- 150000004996 alkyl benzenes Chemical class 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000010696 ester oil Substances 0.000 description 1
- 239000011737 fluorine Substances 0.000 description 1
- 229910052731 fluorine Inorganic materials 0.000 description 1
- NBVXSUQYWXRMNV-UHFFFAOYSA-N fluoromethane Chemical compound FC NBVXSUQYWXRMNV-UHFFFAOYSA-N 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 239000002480 mineral oil Substances 0.000 description 1
- 235000010446 mineral oil Nutrition 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/028—Evaporators having distributing means
-
- 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
- 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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
- F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
- F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
Definitions
- the present invention relates to a refrigeration cycle apparatus and an outdoor heat exchanger used for the refrigeration cycle apparatus, and particularly to: a refrigeration cycle apparatus including an outdoor heat exchanger equipped with a main heat exchange unit and an auxiliary heat exchange unit; and such an outdoor heat exchanger.
- an outdoor heat exchanger used in an air conditioning apparatus as an example of a refrigeration cycle apparatus
- an outdoor heat exchanger configured such that a heat transfer tube through which refrigerant flows is disposed so as to penetrate a plurality of plate-shaped fins.
- Such an outdoor heat exchanger is referred to as a fin-and-tube type heat exchanger.
- a flat tube having a cross section formed in a flat shape is used as a heat transfer tube such that heat exchange is efficiently conducted.
- PTD 1 is listed herein as an example of a patent literature disclosing a refrigeration cycle apparatus including an outdoor heat exchanger of the above-described type. Further prior art useful for understanding the current invention is described in PTD 2 and PTD 3.
- PTD2 discloses a refrigeration apparatus according to the preamble of claim 1.
- the air conditioning apparatus including the outdoor heat exchanger as described above poses the following problem.
- the outdoor heat exchanger is operated as an evaporator.
- the surface temperature of the outdoor heat exchanger falls below the freezing point in order to maintain the heat exchange performance. Consequently, frost may adhere to the outdoor heat exchanger.
- frost may adhere also to this auxiliary heat exchange unit.
- frost adheres to the outdoor heat exchanger the ventilation resistance increases, so that the heat exchange performance deteriorates.
- a defrosting operation is performed in the air conditioning apparatus.
- the present invention has been made to solve the above-described problems.
- One object of the present invention is to provide a refrigeration cycle apparatus including an outdoor heat exchanger configured to prevent adhesion of frost to an auxiliary heat exchange unit.
- Another object of the present invention is to provide an outdoor heat exchanger including such an auxiliary heat exchange unit.
- the refrigeration cycle apparatus in particular comprises an outdoor heat exchanger.
- the outdoor heat exchanger includes a first heat exchange unit and a second heat exchange unit that is disposed adjacent to the first heat exchange unit.
- the first heat exchange unit includes a plurality of fins each formed in a plate shape, a first heat transfer tube, a second heat transfer tube, and a pressure loss mechanism.
- the first heat transfer tube is disposed to penetrate the plurality of fins.
- the second heat transfer tube is disposed to penetrate the plurality of fins and located at a distance from the first heat transfer tube in a direction crossing a direction in which the first heat transfer tube extends.
- the pressure loss mechanism is configured to lower pressure of refrigerant flowing through the first heat exchange unit.
- the refrigeration cycle apparatus operates such that a temperature of refrigerant flowing into the first heat exchange unit is higher than an outdoor air temperature and that the temperature of the refrigerant flowing out of the first heat exchange unit is lower than the outdoor air temperature.
- An outdoor heat exchanger is an outdoor heat exchanger comprising a first heat exchange unit and a second heat exchange unit that is disposed adjacent to the first heat exchange unit.
- the first heat exchange unit includes a plurality of fins each formed in a plate shape, a first heat transfer tube, a second heat transfer tube, and a pressure loss unit.
- the first heat transfer tube is disposed to penetrate the plurality of fins.
- the second heat transfer tube is disposed to penetrate the plurality of fins and located at a distance from the first heat transfer tube in a direction crossing a direction in which the first heat transfer tube extends.
- the pressure loss unit is disposed between the first heat transfer tube and the second heat transfer tube.
- the refrigeration cycle apparatus during the operation of the outdoor heat exchanger functioning as an evaporator, when the temperature of the refrigerant flowing out of the first heat exchange unit is lower than the freezing point of water, the refrigeration cycle apparatus operates such that the temperature of the refrigerant flowing into the first heat exchange unit is higher than the outdoor air temperature and that the temperature of the refrigerant flowing out of the first heat exchange unit is lower than the outdoor air temperature. Thereby, adhesion of frost to the first heat exchange unit of the outdoor heat exchanger can be prevented.
- a pressure loss unit configured to lower the pressure of the refrigerant is provided between the first heat transfer tube and the second heat transfer tube, each of which is disposed so as to penetrate a plurality of fins.
- an air conditioning apparatus 1 includes a compressor 3, an indoor heat exchanger 5, an indoor fan 7, a throttle device 9, an outdoor heat exchanger 11, an outdoor fan 21, a four-way valve 23, and a control unit 51.
- Compressor 3, indoor heat exchanger 5, throttle device 9, outdoor heat exchanger 11, and four-way valve 23 are connected through a refrigerant pipe.
- air conditioning apparatus 1 is provided with: two temperature sensors 53 and 55 each configured to detect the temperature of refrigerant in outdoor heat exchanger 11; and a temperature sensor 57 configured to sense the outdoor air temperature. Temperature sensors 53, 55, and 57 are electrically connected to control unit 51. As will be described later, in air conditioning apparatus 1, control unit 51 controls the temperature of the refrigerant according to the relation with the temperature of the outdoor air (air) in order to prevent adhesion of frost to outdoor heat exchanger 11 when outdoor heat exchanger 11 is operated to function as an evaporator.
- outdoor heat exchanger 11 includes a main heat exchange unit 13 and an auxiliary heat exchange unit 15.
- Main heat exchange unit 13 is disposed on auxiliary heat exchange unit 15.
- auxiliary heat exchange unit 15 a plurality of first heat transfer tubes 33a and a plurality of second heat transfer tubes 33b are disposed so as to penetrate a plurality of plate-shaped fins 31 that are disposed at a distance from one another.
- first heat transfer tubes 33a and second heat transfer tubes 33b a flat tube is used, which has a flat cross-sectional shape having a major axis and a minor axis.
- Fig. 3 shows a flat tube having one refrigerant path 35 formed therein.
- Fig. 4 shows a flat tube having a plurality of refrigerant paths 35 formed therein.
- each of the first heat transfer tube and the second heat transfer tube is not limited to a flat tube, but may be a heat transfer tube having a cross section, for example, formed in a circular shape, an elliptical shape, and the like.
- the plurality of first heat transfer tubes 33a are disposed to be spaced apart from each other in the direction in which the minor axis extends.
- the plurality of first heat transfer tubes 33a are disposed in the first column.
- the first column serves as an auxiliary heat exchange unit 15a.
- the plurality of second heat transfer tubes 33b are disposed to be spaced apart from each other in the direction in which the minor axis extends.
- the plurality of second heat transfer tubes 33b are disposed in the second column.
- the second column serves as an auxiliary heat exchange unit 15b.
- auxiliary heat exchange unit 15a (a windward column) is located on the windward side while auxiliary heat exchange unit 15b (a leeward column) is located on the leeward side.
- the plurality of first heat transfer tubes 33a each have one end (the first end) connected to a distributor 25.
- Distributor 25 of auxiliary heat exchange unit 15 is connected to throttle device 9 (see Fig. 5 ).
- temperature sensor 53 configured to sense the temperature of the refrigerant is provided.
- the other ends (the second ends) of the plurality of first heat transfer tubes 33a and the other ends (the third ends) of the plurality of second heat transfer tubes 33b are connected through a pressure loss unit 17 (a pressure loss mechanism) configured to lose pressure of the refrigerant.
- a specific structure of pressure loss unit 17 will be described later.
- the plurality of second heat transfer tubes 33b each have one end (the fourth end) connected to main heat exchange unit 13.
- temperature sensor 55 configured to sense the temperature of the refrigerant is provided.
- Fig. 2 representatively shows the case where temperature sensor 55 is provided in the refrigerant pipe that is connected to one end of second heat transfer tube 33b disposed at the lowermost position, but temperature sensors may be provided at portions of the refrigerant pipes that are connected to their respective one ends of the plurality of second heat transfer tubes 33b.
- main heat exchange unit 13 a plurality of third heat transfer tubes 33c and a plurality of fourth heat transfer tubes 33d are disposed to penetrate the plurality of plate-shaped fins 31 that are disposed to be spaced apart from one another.
- a flat tube is used as in the case of first heat transfer tubes 33a and second heat transfer tubes 33b.
- Fig. 2 shows a series of third heat transfer tube 33c and fourth heat transfer tube 33d for simplification of illustration.
- the plurality of third heat transfer tubes 33c are disposed to be spaced apart from each other in the direction in which the minor axis extends.
- the plurality of third heat transfer tubes 33c are disposed in the first column (a windward column).
- the first column serves as main heat exchange unit 13a.
- the plurality of fourth heat transfer tubes 33d are disposed to be spaced apart from each other in the direction in which the minor axis extends.
- the plurality of fourth heat transfer tubes 33d are disposed in the second column (a leeward column).
- the second column serves as a main heat exchange unit 13b.
- the plurality of fourth heat transfer tubes 33d each have one end connected to a corresponding one of one ends of the plurality of second heat transfer tubes 33b through distributor 29.
- the plurality of fourth heat transfer tubes 33d each have the other end connected to a corresponding one of the other ends of the plurality of third heat transfer tubes 33c.
- the plurality of third heat transfer tubes 33c each have one end connected to a header 27. Header 27 is connected to four-way valve 23 (see Fig. 5 ).
- Outdoor heat exchanger 11 of air conditioning apparatus 1 is configured as described above.
- high-temperature and high-pressure gaseous refrigerant is discharged from compressor 3.
- the refrigerant flows thereafter as indicated by a dotted line arrow.
- the discharged high-temperature and high-pressure gas refrigerant (a single phase) flows through four-way valve 23 into outdoor heat exchanger 11.
- outdoor heat exchanger 11 heat exchange is conducted between the refrigerant flown therethrough and the air supplied by outdoor fan 21, so that the high-temperature and high-pressure gas refrigerant is condensed into high-pressure liquid refrigerant (a single phase).
- the high-pressure liquid refrigerant delivered out of outdoor heat exchanger 11 is turned into refrigerant in a two-phase state including low-pressure gas refrigerant and low-pressure liquid refrigerant.
- the refrigerant in a two-phase state flows into indoor heat exchanger 5.
- indoor heat exchanger 5 heat exchange is conducted between the incoming refrigerant in a two-phase state and the air supplied by indoor fan 7. Then, as a result of evaporation of the liquid refrigerant, the refrigerant in a two-phase state is turned into low-pressure gas refrigerant (a single phase). Through this heat exchange, the indoor area is cooled.
- the low-pressure gas refrigerant delivered out of indoor heat exchanger 5 flows through four-way valve 23 into compressor 3, and then compressed into high-temperature and high-pressure gas refrigerant, which is again discharged from compressor 3. This cycle is repeated thereafter.
- the refrigerant delivered from compressor 3 flows into header 27 and passes through header 27. Then, the refrigerant flows through third heat transfer tube 33c of main heat exchange unit 13a in the direction as indicated by an arrow. The refrigerant having flown through third heat transfer tube 33c then flows through fourth heat transfer tube 33d of main heat exchange unit 13b in the direction as indicated by an arrow, and thereafter flows into distributor 29.
- the refrigerant having flown into distributor 29 then flows through second heat transfer tube 33b of auxiliary heat exchange unit 15b in the direction as indicated by an arrow.
- the refrigerant having flown through second heat transfer tube 33b then flows through first heat transfer tube 33a of auxiliary heat exchange unit 15a in the direction as indicated by an arrow.
- the refrigerant having flown through first heat transfer tube 33a is discharged to the outside of outdoor heat exchanger 11.
- outdoor heat exchanger 11 functioning as an evaporator (a heating operation).
- a heating operation As shown in Fig. 5 , by driving compressor 3, high-temperature and high-pressure gaseous refrigerant is discharged from compressor 3. The refrigerant flows thereafter as indicated by a solid line arrow.
- the discharged high-temperature and high-pressure gas refrigerant flows through four-way valve 23 into indoor heat exchanger 5.
- indoor heat exchanger 5 heat exchange is conducted between the gas refrigerant having flown thereinto and the air supplied by indoor fan 7. Then, the high-temperature and high-pressure gas refrigerant is condensed into high-pressure liquid refrigerant (a single phase). Through this heat exchange, the indoor area is heated.
- throttle device 9 the high-pressure liquid refrigerant delivered out of indoor heat exchanger 5 is turned into refrigerant in a two-phase state including low-pressure gas refrigerant and low-pressure liquid refrigerant.
- the refrigerant in a two-phase state flows into outdoor heat exchanger 11.
- outdoor heat exchanger 11 heat exchange is conducted between the incoming refrigerant in a two-phase state and the air supplied by outdoor fan 21.
- the refrigerant in a two-phase state is turned into low-pressure gas refrigerant (a single phase).
- the low-pressure gas refrigerant delivered out of outdoor heat exchanger 11 flows through four-way valve 23 into compressor 3 and then compressed into high-temperature and high-pressure gas refrigerant, which is again discharged from compressor 3. This cycle is repeated thereafter.
- the refrigerant delivered from throttle device 9 flows into distributor 25 of auxiliary heat exchange unit 15 and passes through distributor 25. Then, the refrigerant flows through first heat transfer tube 33a of auxiliary heat exchange unit 15a in the direction as indicated by an arrow. The refrigerant having flown through first heat transfer tube 33a then flows through second heat transfer tube 33b of auxiliary heat exchange unit 15b in the direction as indicated by an arrow.
- the refrigerant having flown through second heat transfer tube 33b then flows into distributor 29 of main heat exchange unit 13.
- the refrigerant having flown into distributor 29 then flows through fourth heat transfer tube 33d of main heat exchange unit 13b in the direction as indicated by an arrow.
- the refrigerant having flown through fourth heat transfer tube 33d then flows through third heat transfer tube 33c of main heat exchange unit 13a in the direction as indicated by an arrow.
- the refrigerant having flown through third heat transfer tube 33c then flows into header 27 and passes through header 27. Then, the refrigerant is delivered to the outside of outdoor heat exchanger 11.
- the outdoor air temperature is higher than the above-described condition
- the air dry-bulb temperature is 5 °C
- the air wet-bulb temperature is 4 °C.
- the dew point temperature of air is about 2.8 °C.
- both the air dry-bulb temperature and the dew point temperature may reach the temperature close to the refrigerant temperature.
- frost may adhere to the outdoor heat exchanger.
- the air dry-bulb temperature is 2 °C
- the air wet-bulb temperature is 1 °C
- the dew point temperature is -0.4 °C.
- Fig. 8 shows: a graph showing transition of the temperature of the refrigerant that flows through auxiliary heat exchange unit 15 with respect to the refrigerant flow direction (a dashed line); a graph showing transition of the air dry-bulb temperature with respect to the air flow direction (a solid line); and a graph showing transition of the dew point temperature with respect to the air flow direction (a dotted line).
- the refrigerant inlet temperature (Tref-in) of the refrigerant flowing into auxiliary heat exchange unit 15 is lower than the outdoor air temperature (air inlet temperature (Tair-in)).
- the air dry-bulb temperature immediately reaches approximately the same temperature as the dew point temperature. Since the dew point temperature is lower than the freezing point of water (for example, 0 °C), frost is to adhere to the most part of outdoor heat exchanger 11 including auxiliary heat exchange unit 15.
- the defrosting operation is generally performed in the same operation mode as that in the operation of the outdoor heat exchanger functioning as a condenser.
- the direction in which the refrigerant flows is opposite to the direction in which the refrigerant flows during the operation of outdoor heat exchanger 11 functioning as an evaporator.
- the refrigerant flows through auxiliary heat exchange unit 15 after it flows through main heat exchange unit 13 (see Fig. 6 ).
- Auxiliary heat exchange unit 15 is disposed below main heat exchange unit 13. Accordingly, the quantity of heat of the refrigerant is removed in main heat exchange unit 13 on the upstream side of the refrigerant flow.
- auxiliary heat exchange unit 15 on the downstream side the performance of defrosting adhering frost deteriorates, which may lengthen the defrosting time.
- the indoor temperature gradually lowers, so that a comfortable state may not be able to be maintained.
- frost may further grow to thereby damage auxiliary heat exchange unit 15 and the like.
- a significant problem may occur, for example, that a heat transfer tube is damaged to thereby cause leakage of refrigerant, and the like.
- Fig. 9 shows: a graph showing transition of the temperature of the refrigerant that flows through auxiliary heat exchange unit 15 with respect to the refrigerant flow direction (a dashed line); a graph showing transition of the air dry-bulb temperature with respect to the air flow direction (a solid line); and a graph showing transition of the dew point temperature with respect to the air flow direction (a dotted line).
- the refrigerant outlet temperature (Tref-out) of the refrigerant delivered out of auxiliary heat exchange unit 15 is higher than the outdoor air temperature (air inlet temperature (Tair-in)).
- air inlet temperature (Tair-in) the outdoor air temperature
- frost does not adhere to auxiliary heat exchange unit 15, so that auxiliary heat exchange unit 15 is not damaged.
- the reliability as auxiliary heat exchange unit 15 is ensured.
- auxiliary heat exchange unit 15 used as a condenser the refrigerant changes so as to be liquefied. Accordingly, in main heat exchange unit 13 used as an evaporator, for evaporating the liquefied refrigerant, the load for heat exchange in main heat exchange unit 13 is increased. Therefore, the heat exchange performance significantly deteriorates.
- Fig. 10 shows: a graph showing transition of the temperature of the refrigerant that flows through auxiliary heat exchange unit 15 with respect to the refrigerant flow direction (a dashed line); a graph showing transition of the air dry-bulb temperature with respect to the air flow direction (a solid line); and a graph showing transition of the dew point temperature with respect to the air flow direction (a dotted line).
- This operation of outdoor heat exchanger 11 functioning as an evaporator is performed on the conditions that, in the case where the refrigerant outlet temperature (Tref-out) is lower than the freezing point of water (for example, 0 °C), the refrigerant inlet temperature (Tref-in) of the refrigerant flowing into auxiliary heat exchange unit 15 is higher than the outdoor air temperature (air inlet temperature (Tair-in)), and the refrigerant outlet temperature of the refrigerant delivered out of auxiliary heat exchange unit 15 (Tref-out) is lower than the outdoor air temperature (air inlet temperature (Tair-in)).
- auxiliary heat exchange unit 15 The refrigerant flowing through auxiliary heat exchange unit 15 is in a two-phase state including liquid refrigerant and gas refrigerant.
- adjusting the pressure loss of the refrigerant in auxiliary heat exchange unit 15 means the same as adjusting the refrigerant temperature.
- pressure loss unit 17 is provided between auxiliary heat exchange unit 15a located in the first column and auxiliary heat exchange unit 15b located in the second column, so that auxiliary heat exchange unit 15a is caused to function as a condenser and auxiliary heat exchange unit 15b is caused to function as an evaporator.
- auxiliary heat exchange unit 15a located in the windward column When auxiliary heat exchange unit 15a located in the windward column is caused to function as a condenser, the air temperature rises. Thus, even when auxiliary heat exchange unit 15b located in the leeward column is caused to function as an evaporator, the air temperature is less likely to fall below the dew point temperature. Thereby, auxiliary heat exchange unit 15 can be caused to entirely function as an evaporator in the state where the temperature of the refrigerant lowers, and also, adhesion of frost to auxiliary heat exchange unit 15 can be prevented.
- the refrigerant flows through auxiliary heat exchange unit 15a located on the windward side, and thereafter, flows through auxiliary heat exchange unit 15b located on the leeward side.
- the refrigerant flows from the windward side toward the leeward side in the same manner as with the flow of air.
- Such the refrigerant flow is referred to as a parallel flow.
- the flow of the refrigerant from the leeward side toward the windward side is referred to as a counterflow.
- auxiliary heat exchange unit 15 in outdoor heat exchanger 11, the refrigerant first flows through auxiliary heat exchange unit 15, and then flows through main heat exchange unit 13.
- the refrigerant having flown through second heat transfer tube 33b then flows through first heat transfer tube 33a of auxiliary heat exchange unit 15a in the direction as indicated by an arrow.
- the refrigerant having flown through auxiliary heat exchange unit 15a is caused to flow through main heat exchange unit 13 and thereafter delivered out of outdoor heat exchanger 11, in the same manner as shown in Fig. 7 .
- Fig. 12 represents the case where the refrigerant flows as a counterflow, and shows: a graph showing transition of the temperature of the refrigerant that flows through auxiliary heat exchange unit 15 with respect to the refrigerant flow direction (a dashed line); a graph showing transition of the air dry-bulb temperature with respect to the air flow direction (a solid line); and a graph showing transition of the dew point temperature with respect to the air flow direction (a dotted line).
- auxiliary heat exchange unit 15 when the temperature of the refrigerant flowing through auxiliary heat exchange unit 15a located on the windward side is set to be higher than the outdoor air temperature (air inlet temperature (Tair-in)), the temperature of the refrigerant flowing through auxiliary heat exchange unit 15b located on the leeward side is also higher than the outdoor air temperature (air inlet temperature (Tair-in)).
- auxiliary heat exchange unit 15 entirely functions as a condenser, so that the heat exchange performance deteriorates, as having been described with reference to Fig. 9 . Therefore, in order that outdoor heat exchanger 11 is operated to function as an evaporator so as to prevent adhesion of frost to auxiliary heat exchange unit 15, it is desirable to perform the operation such that the refrigerant flows as a parallel flow along the flow of air.
- pressure loss unit 17 is disposed between auxiliary heat exchange unit 15a and auxiliary heat exchange unit 15b.
- the friction loss inside the heat transfer tube such as first heat transfer tube 33a and second heat transfer tube 33b may be employed.
- Fig. 13 represents the case where outdoor heat exchanger 11 is operated to function as an evaporator, and shows: a graph showing transition of the temperature of the refrigerant flowing through auxiliary heat exchange unit 15 with respect to the refrigerant flow direction (a dashed line); a graph showing transition of the air dry-bulb temperature with respect to the air flow direction (a solid line); and a graph showing transition of the dew point temperature with respect to the air flow direction (a dotted line).
- the temperature of the refrigerant lowers gradually by the friction loss inside the heat transfer tube.
- the friction loss inside the heat transfer tube is defined by the flow velocity of the refrigerant, the inside shape of the heat transfer tube, and the length of the heat transfer tube. Accordingly, the amount of the refrigerant circulating in the air conditioning apparatus, the dimensions of the heat transfer tube inside the outdoor heat exchanger, the number of paths in the heat transfer tube, and the like are set at their respective prescribed values based on the design. Then, on the condition that the refrigerant temperature establishes a prescribed temperature relation, outdoor heat exchanger 11 is operated to function as an evaporator, with the result that adhesion of frost to auxiliary heat exchange unit 15 can be prevented.
- the operation is performed such that the refrigerant inlet temperature (Tref-in) is higher than the outdoor air temperature (air inlet temperature (Tair-in)), and that the refrigerant outlet temperature (Tref-out) is lower than the outdoor air temperature (air inlet temperature (Tair-in)), so that adhesion of frost to auxiliary heat exchange unit 15 can be prevented.
- auxiliary heat exchange unit 15 Furthermore, by performing the operation such that the refrigerant outlet temperature (Tref-out) of the refrigerant delivered out of auxiliary heat exchange unit 15 is higher than the dew point temperature, adhesion of frost to auxiliary heat exchange unit 15 can be reliably prevented.
- a throttle device disposed between auxiliary heat exchange unit 15a and auxiliary heat exchange unit 15b, a throttle device may be used, for example.
- Fig. 14 shows throttle devices 39 each of which is provided for a corresponding one of a plurality of first heat transfer tubes 33a disposed in auxiliary heat exchange unit 15a and a corresponding one of a plurality of second heat transfer tubes 33b disposed in auxiliary heat exchange unit 15b, such that each of throttle devices 39 is disposed for a route (path) extending from a corresponding one of first heat transfer tubes 33a to a corresponding one of second heat transfer tubes 33b.
- Fig. 15 shows throttle device 39 provided such that the refrigerants having flown through first heat transfer tubes 33a are joined on the upstream side of the throttle device, and then branched (divided) again on the downstream side of the throttle device so as to be delivered to their respective second heat transfer tubes 33b.
- auxiliary heat exchange unit 15 the opening degree of throttle device 39 is adjusted with respect to the temperature of the refrigerant on the upstream side of throttle device 39, so that the temperature of the refrigerant on the downstream side of throttle device 39 can be adjusted.
- throttle device 39 when throttle device 39 is placed between auxiliary heat exchange unit 15a and auxiliary heat exchange unit 15b (between the columns), the temperature of the refrigerant flowing through auxiliary heat exchange unit 15a located on the windward side and the temperature of the refrigerant flowing through auxiliary heat exchange unit 15b located on the leeward side can be separately adjusted.
- auxiliary heat exchange unit 15a located on the windward side can be entirely functioned as a condenser while auxiliary heat exchange unit 15b located on the leeward side can be entirely functioned as an evaporator. Consequently, as having been described in the first embodiment, adhesion of frost to auxiliary heat exchange unit 15 of outdoor heat exchanger 11 can be prevented during the operation of outdoor heat exchanger 11 functioning as an evaporator.
- a header (an inter-columnar header) may be used, for example.
- Fig. 16 shows an inter-columnar header 41 disposed between auxiliary heat exchange unit 15a and auxiliary heat exchange unit 15b.
- a flow path through which refrigerant flows is provided inside inter-columnar header 41 for each route (path) extending from first heat transfer tube 33a to second heat transfer tube 33b.
- a throttle portion 43 is provided at some midpoint of the flow path in such a manner that the cross-sectional area of this midpoint in the flow path is narrower than the cross-sectional area of another portion in the flow path.
- auxiliary heat exchange unit 15a can be functioned as a condenser while auxiliary heat exchange unit 15b can be functioned as an evaporator. Consequently, during the operation of outdoor heat exchanger 11 functioning as an evaporator, adhesion of frost to auxiliary heat exchange unit 15 of outdoor heat exchanger 11 can be prevented.
- auxiliary heat exchange unit 15a disposed between auxiliary heat exchange unit 15a and auxiliary heat exchange unit 15b, for example, two headers may be used, including a header connected to auxiliary heat exchange unit 15a and a header connected to auxiliary heat exchange unit 15b.
- Fig. 20 shows a header including a header 45a, a header 45b, and a header connection tube 47.
- Header 45a is connected to first heat transfer tube 33a of auxiliary heat exchange unit 15a.
- Header 45b is connected to second heat transfer tube 33b of auxiliary heat exchange unit 15b.
- Header connection tube 47 provides connection between header 45a and header 45b.
- auxiliary heat exchange unit 15a and the temperature of the refrigerant flowing through auxiliary heat exchange unit 15b can be separately adjusted.
- adhesion of frost to auxiliary heat exchange unit 15 of outdoor heat exchanger 11 can be prevented during the operation of outdoor heat exchanger 11 functioning as an evaporator.
- flow paths causing friction loss may be separately provided inside the flow paths of headers 45a and 45b. Then, also by adjusting the shapes of these flow paths to thereby adjust the pressure loss, adhesion of frost can be prevented
- a U-shaped tube may be used other than a header.
- a U-shaped tube 49 is connected for each route (path) extending from first heat transfer tube 33a to second heat transfer tube 33b.
- the temperature of the refrigerant flowing through auxiliary heat exchange unit 15a and the temperature of the refrigerant flowing through auxiliary heat exchange unit 15b can be separately adjusted.
- adhesion of frost to auxiliary heat exchange unit 15 of outdoor heat exchanger 11 can be prevented during the operation of outdoor heat exchanger 11 functioning as an evaporator.
- refrigerant used in air conditioning apparatus 1 having been described in the above embodiment, by using any kind of refrigerant such as refrigerant R410A, refrigerant R407C, refrigerant R32, refrigerant R507A, refrigerant HFO1234yf, and the like, adhesion of frost to auxiliary heat exchange unit 15 of outdoor heat exchanger 11 can be prevented.
- refrigerant R410A refrigerant R407C
- refrigerant R32 refrigerant R507A
- refrigerant HFO1234yf refrigerant HFO1234yf
- Each of refrigerant R410A and refrigerant R407C is a refrigerant mixture and particularly referred to as a non-azeotropic refrigerant mixture.
- a non-azeotropic refrigerant mixture has different compositions in a vapor phase and in a liquid phase in a moist vapor state, and also has a characteristic that it undergoes a phase change of evaporation or condensation while it undergoes a temperature change and a composition conversion between two phases of gas refrigerant and liquid refrigerant under fixed pressure.
- refrigerant R407C and the like undergo extremely small temperature change during a phase change, and particularly, is referred to as a pseudo-azeotropic refrigerant mixture.
- Refrigerant R32 and refrigerant HFO1234yf each are refrigerant formed of a single component.
- Refrigerant R507A is a refrigerant mixture and referred to as an azeotropic refrigerant mixture.
- the azeotropic refrigerant mixture has a composition that is identical in a vapor phase and a liquid phase in moist vapor in a certain component ratio, and also has a characteristic that it undergoes a phase change of evaporation or condensation at a fixed temperature under fixed pressure, as in the case of the refrigerant formed of a single component.
- a non-azeotropic refrigerant mixture a pseudo-azeotropic refrigerant mixture, refrigerant formed of a single component, or an azeotropic refrigerant mixture
- the refrigerant outlet temperature is lower than the freezing point of water (for example, 0 °C)
- the operation is performed such that the refrigerant inlet temperature is higher than the outdoor air temperature and that the refrigerant outlet temperature is lower than the outdoor air temperature, with the result that adhesion of frost to auxiliary heat exchange unit 15 of outdoor heat exchanger 11 can be prevented.
- adhesion of frost to auxiliary heat exchange unit 15 can be reliably prevented.
- refrigeration oil used in the air conditioning apparatus refrigeration oil having compatibility is employed in consideration of the mutual solubility to the refrigerant to be applied.
- fluorocarbon-based refrigerant such as refrigerant R410A
- alkylbenzene oil-based refrigeration oil for example, alkylbenzene oil-based refrigeration oil, ester oil-based refrigeration oil or ether oil-based refrigeration oil is used.
- mineral oil-based refrigeration oil or fluorine oil-based refrigeration oil may be used.
- the operation is performed such that the refrigerant inlet temperature is higher than the outdoor air temperature and that the refrigerant outlet temperature is lower than the outdoor air temperature, with the result that adhesion of frost to auxiliary heat exchange unit 15 of outdoor heat exchanger 11 can be prevented.
- the refrigeration cycle apparatus is not limited to an air conditioning apparatus, but may be applicable, for example, also to an apparatus including an outdoor heat exchanger such as a heat pump water heater configured to perform heat exchange with air. Furthermore, various combinations can be made as appropriate for the refrigeration cycle apparatus including an outdoor heat exchanger, which has been described in the embodiments.
- the present invention is effectively utilized in a refrigeration cycle apparatus such as an air conditioning apparatus including an outdoor heat exchanger equipped with a main heat exchange unit and an auxiliary heat exchange unit.
- 1 air conditioning apparatus 3 compressor, 5 indoor heat exchanger, 7 indoor fan, 9 throttle device, 11 outdoor heat exchanger, 13 main heat exchange unit, 13a, 13b main heat exchange unit, 15 auxiliary heat exchange unit, 15a, 15b auxiliary heat exchange unit, 17 pressure loss unit, 21 outdoor fan, 23 four-way valve, 25 distributor, 27 header, 29 distributor, 31 fin, 33a first heat transfer tube, 33b second heat transfer tube, 33c third heat transfer tube, 33d fourth heat transfer tube, 35 refrigerant path, 37 refrigerant pipe, 39 throttle device, 41 inter-columnar header, 43 throttle portion, 45a, 45b header, 47 header connection tube, 49 U-shaped tube, 51 control unit, 53, 55, 57 temperature sensor.
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Description
- The present invention relates to a refrigeration cycle apparatus and an outdoor heat exchanger used for the refrigeration cycle apparatus, and particularly to: a refrigeration cycle apparatus including an outdoor heat exchanger equipped with a main heat exchange unit and an auxiliary heat exchange unit; and such an outdoor heat exchanger.
- As an outdoor heat exchanger used in an air conditioning apparatus as an example of a refrigeration cycle apparatus, there is an outdoor heat exchanger configured such that a heat transfer tube through which refrigerant flows is disposed so as to penetrate a plurality of plate-shaped fins. Such an outdoor heat exchanger is referred to as a fin-and-tube type heat exchanger. In this type of outdoor heat exchanger, a flat tube having a cross section formed in a flat shape is used as a heat transfer tube such that heat exchange is efficiently conducted.
- There is one type of outdoor heat exchanger including a main heat exchange unit for condensation and an auxiliary heat exchange unit for supercooling. In general, the main heat exchange unit is disposed on the auxiliary heat exchange unit. When a cooling operation of the refrigeration cycle apparatus is performed, the refrigerant having flown into the outdoor heat exchanger is heat-exchanged with air while the refrigerant flows through the main heat exchange unit, and then, condensed into liquid refrigerant. Then, the liquid refrigerant flows through the auxiliary heat exchange unit, so that the liquid refrigerant is further cooled. PTD 1 is listed herein as an example of a patent literature disclosing a refrigeration cycle apparatus including an outdoor heat exchanger of the above-described type. Further prior art useful for understanding the current invention is described in PTD 2 and
PTD 3. PTD2 discloses a refrigeration apparatus according to the preamble ofclaim 1. -
- PTL 1: Japanese Patent Laying-Open No.
2013-83419 - PTL 2: European Patent Application No.
3 032 182 A1 - PTL 3: European Patent Application No.
2 865 967 A1 - However, the air conditioning apparatus including the outdoor heat exchanger as described above poses the following problem. When a heating operation of the air conditioning apparatus is performed, the outdoor heat exchanger is operated as an evaporator. When the air temperature on the outside where the outdoor heat exchanger is installed becomes closer to a temperature below the freezing point, the surface temperature of the outdoor heat exchanger falls below the freezing point in order to maintain the heat exchange performance. Consequently, frost may adhere to the outdoor heat exchanger.
- Particularly when the air conditioning apparatus is operated while the auxiliary heat exchange unit is also used as an evaporator, frost may adhere also to this auxiliary heat exchange unit. When frost adheres to the outdoor heat exchanger, the ventilation resistance increases, so that the heat exchange performance deteriorates. In order to prevent adhesion of frost, a defrosting operation is performed in the air conditioning apparatus.
- When the defrosting operation is performed in the state where frost adheres to the outdoor heat exchanger, water resulting from melting of frost flows through the outdoor heat exchanger from its upper portion to its lower portion, so that it falls as drainage water downward through the outdoor heat exchanger. In this case, in the heat exchanger using a flat tube as a heat transfer tube, water resulting from melting of frost is less likely to fall downward but is more likely to accumulate in the auxiliary heat exchange unit located on the lower side.
- Consequently, it takes longer time to perform the defrosting operation for melting the adhering frost, with the result that power consumption is increased. On the other hand, when the heating operation is resumed in the state where frost or water still remains, the remaining water is cooled and frozen by the refrigerant, with the result that the outdoor heat exchanger may become damaged.
- The present invention has been made to solve the above-described problems. One object of the present invention is to provide a refrigeration cycle apparatus including an outdoor heat exchanger configured to prevent adhesion of frost to an auxiliary heat exchange unit. Another object of the present invention is to provide an outdoor heat exchanger including such an auxiliary heat exchange unit.
- A refrigeration cycle apparatus according to the present invention is specified in the independent claim. The refrigeration cycle apparatus in particular comprises an outdoor heat exchanger. The outdoor heat exchanger includes a first heat exchange unit and a second heat exchange unit that is disposed adjacent to the first heat exchange unit. The first heat exchange unit includes a plurality of fins each formed in a plate shape, a first heat transfer tube, a second heat transfer tube, and a pressure loss mechanism. The first heat transfer tube is disposed to penetrate the plurality of fins. The second heat transfer tube is disposed to penetrate the plurality of fins and located at a distance from the first heat transfer tube in a direction crossing a direction in which the first heat transfer tube extends. The pressure loss mechanism is configured to lower pressure of refrigerant flowing through the first heat exchange unit. During an operation of the outdoor heat exchanger functioning as an evaporator, when a temperature of refrigerant flowing out of the first heat exchange unit is lower than a freezing point of water, the refrigeration cycle apparatus operates such that a temperature of refrigerant flowing into the first heat exchange unit is higher than an outdoor air temperature and that the temperature of the refrigerant flowing out of the first heat exchange unit is lower than the outdoor air temperature.
- An outdoor heat exchanger according to the present invention is an outdoor heat exchanger comprising a first heat exchange unit and a second heat exchange unit that is disposed adjacent to the first heat exchange unit. The first heat exchange unit includes a plurality of fins each formed in a plate shape, a first heat transfer tube, a second heat transfer tube, and a pressure loss unit. The first heat transfer tube is disposed to penetrate the plurality of fins. The second heat transfer tube is disposed to penetrate the plurality of fins and located at a distance from the first heat transfer tube in a direction crossing a direction in which the first heat transfer tube extends. The pressure loss unit is disposed between the first heat transfer tube and the second heat transfer tube.
- According to the refrigeration cycle apparatus of the present invention, during the operation of the outdoor heat exchanger functioning as an evaporator, when the temperature of the refrigerant flowing out of the first heat exchange unit is lower than the freezing point of water, the refrigeration cycle apparatus operates such that the temperature of the refrigerant flowing into the first heat exchange unit is higher than the outdoor air temperature and that the temperature of the refrigerant flowing out of the first heat exchange unit is lower than the outdoor air temperature. Thereby, adhesion of frost to the first heat exchange unit of the outdoor heat exchanger can be prevented.
- According to the outdoor heat exchanger of the present invention, a pressure loss unit configured to lower the pressure of the refrigerant is provided between the first heat transfer tube and the second heat transfer tube, each of which is disposed so as to penetrate a plurality of fins. Thereby, when the outdoor heat exchanger is operated to function as an evaporator, the temperature of the refrigerant is controlled according to the relation with the temperature of air, so that adhesion of frost to the first heat exchange unit of the outdoor heat exchanger can be prevented.
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Fig. 1 is a diagram showing an example of a refrigerant circuit in an air conditioning apparatus according to an embodiment of the current invention. -
Fig. 2 is a perspective view showing an outdoor heat exchanger in the embodiment. -
Fig. 3 is a cross-sectional view showing an example of a refrigerant path of a heat transfer tube in the embodiment. -
Fig. 4 is a cross-sectional view showing another example of the refrigerant path of the heat transfer tube in the embodiment. -
Fig. 5 is a diagram showing each flow of refrigerant in the outdoor heat exchanger at the time when the outdoor heat exchanger is operated to function as a condenser or at the time when the outdoor heat exchanger is operated to function as an evaporator, in the embodiment. -
Fig. 6 is a perspective view showing the flow of the refrigerant in the outdoor heat exchanger in the case where the outdoor heat exchanger is operated to function as a condenser in the embodiment. -
Fig. 7 is a perspective view showing the flow of the refrigerant in the outdoor heat exchanger in the case where the outdoor heat exchanger is operated to function as an evaporator in the embodiment. -
Fig. 8 is a diagram for illustrating the relation between the temperature of the refrigerant flowing through an auxiliary heat exchange unit in the outdoor heat exchanger and the temperature of air in the case where the outdoor heat exchanger is operated to function as an evaporator in an air conditioning apparatus according to the first comparative example. -
Fig. 9 is a diagram for illustrating the relation between the temperature of the refrigerant flowing through an auxiliary heat exchange unit in the outdoor heat exchanger and the temperature of air in the case where the outdoor heat exchanger is operated to function as an evaporator in an air conditioning apparatus according to the second comparative example. -
Fig. 10 is a diagram for illustrating the relation between the temperature of the refrigerant flowing through the auxiliary heat exchange unit in the outdoor heat exchanger and the temperature of air in the case where the outdoor heat exchanger is operated to function as an evaporator, in the embodiment. -
Fig. 11 is a diagram showing the flow of refrigerant in an outdoor heat exchanger in the case where the outdoor heat exchanger is operated to function as an evaporator in an air conditioning apparatus according to the third comparative example. -
Fig. 12 is a diagram for illustrating the relation between the temperature of the refrigerant flowing through an auxiliary heat exchange unit in the outdoor heat exchanger and the temperature of air in the case where the outdoor heat exchanger is operated to function as an evaporator in the air conditioning apparatus according to the third comparative example. -
Fig. 13 is a diagram for illustrating the relation between the temperature of the refrigerant flowing through the auxiliary heat exchange unit in the outdoor heat exchanger and the temperature of air in the case where the outdoor heat exchanger is operated to function as an evaporator in the air conditioning apparatus including a heat transfer tube applied as a pressure loss unit, not according to the invention. -
Fig. 14 is a side view schematically showing the auxiliary heat exchange unit equipped with a throttle device as the first example of the pressure loss unit, according to an embodiment of the current invention. -
Fig. 15 is a side view schematically showing the auxiliary heat exchange unit equipped with a throttle device as the second example of the pressure loss unit, according to an embodiment of the current invention. -
Fig. 16 is a perspective view schematically showing the auxiliary heat exchange unit equipped with an inter-columnar header as the third example of a pressure loss unit, not according to an embodiment of the current invention. -
Fig. 17 is a cross-sectional view taken along a cross-sectional line XVII-XVII shown inFig. 16 . -
Fig. 18 is a cross-sectional view taken along a cross-sectional line XVIII-XVIII shown inFig. 16 . -
Fig. 19 is a cross-sectional view taken along a cross-sectional line XIX-XIX shown inFig. 16 . -
Fig. 20 is a perspective view schematically showing the auxiliary heat exchange unit equipped with a header as the fourth example of the pressure loss unit, not according to an embodiment of the current invention. -
Fig. 21 is a perspective view schematically showing the auxiliary heat exchange unit equipped with a U-shaped tube as the fifth example of the pressure loss unit, not according to an embodiment of the current invention. - First, the entire configuration (a refrigerant circuit) of an air conditioning apparatus as an example of a refrigeration cycle apparatus will be hereinafter described. As shown in
Fig. 1 , anair conditioning apparatus 1 includes acompressor 3, anindoor heat exchanger 5, anindoor fan 7, athrottle device 9, anoutdoor heat exchanger 11, anoutdoor fan 21, a four-way valve 23, and acontrol unit 51.Compressor 3,indoor heat exchanger 5,throttle device 9,outdoor heat exchanger 11, and four-way valve 23 are connected through a refrigerant pipe. - Furthermore,
air conditioning apparatus 1 is provided with: twotemperature sensors outdoor heat exchanger 11; and atemperature sensor 57 configured to sense the outdoor air temperature.Temperature sensors unit 51. As will be described later, inair conditioning apparatus 1,control unit 51 controls the temperature of the refrigerant according to the relation with the temperature of the outdoor air (air) in order to prevent adhesion of frost tooutdoor heat exchanger 11 whenoutdoor heat exchanger 11 is operated to function as an evaporator. - Then,
outdoor heat exchanger 11 will be hereinafter described. As shown inFig. 2 ,outdoor heat exchanger 11 includes a mainheat exchange unit 13 and an auxiliaryheat exchange unit 15. Mainheat exchange unit 13 is disposed on auxiliaryheat exchange unit 15. In auxiliaryheat exchange unit 15, a plurality of firstheat transfer tubes 33a and a plurality of secondheat transfer tubes 33b are disposed so as to penetrate a plurality of plate-shapedfins 31 that are disposed at a distance from one another. - As each of first
heat transfer tubes 33a and secondheat transfer tubes 33b, a flat tube is used, which has a flat cross-sectional shape having a major axis and a minor axis. As an example of the flat tube,Fig. 3 shows a flat tube having onerefrigerant path 35 formed therein. As another example of the flat tube,Fig. 4 shows a flat tube having a plurality ofrefrigerant paths 35 formed therein. In addition, each of the first heat transfer tube and the second heat transfer tube is not limited to a flat tube, but may be a heat transfer tube having a cross section, for example, formed in a circular shape, an elliptical shape, and the like. - The plurality of first
heat transfer tubes 33a are disposed to be spaced apart from each other in the direction in which the minor axis extends. The plurality of firstheat transfer tubes 33a are disposed in the first column. The first column serves as an auxiliaryheat exchange unit 15a. The plurality of secondheat transfer tubes 33b are disposed to be spaced apart from each other in the direction in which the minor axis extends. The plurality of secondheat transfer tubes 33b are disposed in the second column. The second column serves as an auxiliaryheat exchange unit 15b. As will be described later, when the air conditioning apparatus operates, auxiliaryheat exchange unit 15a (a windward column) is located on the windward side while auxiliaryheat exchange unit 15b (a leeward column) is located on the leeward side. - The plurality of first
heat transfer tubes 33a each have one end (the first end) connected to adistributor 25.Distributor 25 of auxiliaryheat exchange unit 15 is connected to throttle device 9 (seeFig. 5 ). At a portion of the refrigerant pipe in the vicinity ofdistributor 25,temperature sensor 53 configured to sense the temperature of the refrigerant is provided. The other ends (the second ends) of the plurality of firstheat transfer tubes 33a and the other ends (the third ends) of the plurality of secondheat transfer tubes 33b are connected through a pressure loss unit 17 (a pressure loss mechanism) configured to lose pressure of the refrigerant. A specific structure ofpressure loss unit 17 will be described later. - The plurality of second
heat transfer tubes 33b each have one end (the fourth end) connected to mainheat exchange unit 13. At a portion ofrefrigerant pipe 37 that is connected to one end of secondheat transfer tube 33b,temperature sensor 55 configured to sense the temperature of the refrigerant is provided.Fig. 2 representatively shows the case wheretemperature sensor 55 is provided in the refrigerant pipe that is connected to one end of secondheat transfer tube 33b disposed at the lowermost position, but temperature sensors may be provided at portions of the refrigerant pipes that are connected to their respective one ends of the plurality of secondheat transfer tubes 33b. - In main
heat exchange unit 13, a plurality of thirdheat transfer tubes 33c and a plurality of fourthheat transfer tubes 33d are disposed to penetrate the plurality of plate-shapedfins 31 that are disposed to be spaced apart from one another. As each of thirdheat transfer tubes 33c and fourthheat transfer tubes 33d, a flat tube is used as in the case of firstheat transfer tubes 33a and secondheat transfer tubes 33b.Fig. 2 shows a series of thirdheat transfer tube 33c and fourthheat transfer tube 33d for simplification of illustration. - The plurality of third
heat transfer tubes 33c are disposed to be spaced apart from each other in the direction in which the minor axis extends. The plurality of thirdheat transfer tubes 33c are disposed in the first column (a windward column). The first column serves as mainheat exchange unit 13a. The plurality of fourthheat transfer tubes 33d are disposed to be spaced apart from each other in the direction in which the minor axis extends. The plurality of fourthheat transfer tubes 33d are disposed in the second column (a leeward column). The second column serves as a mainheat exchange unit 13b. - The plurality of fourth
heat transfer tubes 33d each have one end connected to a corresponding one of one ends of the plurality of secondheat transfer tubes 33b throughdistributor 29. The plurality of fourthheat transfer tubes 33d each have the other end connected to a corresponding one of the other ends of the plurality of thirdheat transfer tubes 33c. The plurality of thirdheat transfer tubes 33c each have one end connected to aheader 27.Header 27 is connected to four-way valve 23 (seeFig. 5 ).Outdoor heat exchanger 11 ofair conditioning apparatus 1 is configured as described above. - Then, as an operation (the flow of the refrigerant) of
air conditioning apparatus 1 described above, the operation ofoutdoor heat exchanger 11 functioning as a condenser (a cooling operation) will be first described. - As shown in
Fig. 5 , by drivingcompressor 3, high-temperature and high-pressure gaseous refrigerant is discharged fromcompressor 3. The refrigerant flows thereafter as indicated by a dotted line arrow. The discharged high-temperature and high-pressure gas refrigerant (a single phase) flows through four-way valve 23 intooutdoor heat exchanger 11. Inoutdoor heat exchanger 11, heat exchange is conducted between the refrigerant flown therethrough and the air supplied byoutdoor fan 21, so that the high-temperature and high-pressure gas refrigerant is condensed into high-pressure liquid refrigerant (a single phase). - By
throttle device 9, the high-pressure liquid refrigerant delivered out ofoutdoor heat exchanger 11 is turned into refrigerant in a two-phase state including low-pressure gas refrigerant and low-pressure liquid refrigerant. The refrigerant in a two-phase state flows intoindoor heat exchanger 5. Inindoor heat exchanger 5, heat exchange is conducted between the incoming refrigerant in a two-phase state and the air supplied byindoor fan 7. Then, as a result of evaporation of the liquid refrigerant, the refrigerant in a two-phase state is turned into low-pressure gas refrigerant (a single phase). Through this heat exchange, the indoor area is cooled. The low-pressure gas refrigerant delivered out ofindoor heat exchanger 5 flows through four-way valve 23 intocompressor 3, and then compressed into high-temperature and high-pressure gas refrigerant, which is again discharged fromcompressor 3. This cycle is repeated thereafter. - In the following, an explanation will be given with regard to the flow of the refrigerant in
outdoor heat exchanger 11 in the case whereoutdoor heat exchanger 11 is operated to function as a condenser. As shown inFig. 6 , inoutdoor heat exchanger 11, the refrigerant first flows through mainheat exchange unit 13, and then flows through auxiliaryheat exchange unit 15. Also, by outdoor fan 21 (seeFig. 1 ), air flows from auxiliaryheat exchange unit 15a and mainheat exchange unit 13a in the first column (a windward column) toward auxiliaryheat exchange unit 15b and mainheat exchange unit 13b in the second column (a leeward column), as indicated by an arrow. - The refrigerant delivered from
compressor 3 flows intoheader 27 and passes throughheader 27. Then, the refrigerant flows through thirdheat transfer tube 33c of mainheat exchange unit 13a in the direction as indicated by an arrow. The refrigerant having flown through thirdheat transfer tube 33c then flows through fourthheat transfer tube 33d of mainheat exchange unit 13b in the direction as indicated by an arrow, and thereafter flows intodistributor 29. - The refrigerant having flown into
distributor 29 then flows through secondheat transfer tube 33b of auxiliaryheat exchange unit 15b in the direction as indicated by an arrow. The refrigerant having flown through secondheat transfer tube 33b then flows through firstheat transfer tube 33a of auxiliaryheat exchange unit 15a in the direction as indicated by an arrow. The refrigerant having flown through firstheat transfer tube 33a is discharged to the outside ofoutdoor heat exchanger 11. - Then, an explanation will be hereinafter given with regard to the operation of
outdoor heat exchanger 11 functioning as an evaporator (a heating operation). As shown inFig. 5 , by drivingcompressor 3, high-temperature and high-pressure gaseous refrigerant is discharged fromcompressor 3. The refrigerant flows thereafter as indicated by a solid line arrow. - The discharged high-temperature and high-pressure gas refrigerant (single phase) flows through four-
way valve 23 intoindoor heat exchanger 5. Inindoor heat exchanger 5, heat exchange is conducted between the gas refrigerant having flown thereinto and the air supplied byindoor fan 7. Then, the high-temperature and high-pressure gas refrigerant is condensed into high-pressure liquid refrigerant (a single phase). Through this heat exchange, the indoor area is heated. Bythrottle device 9, the high-pressure liquid refrigerant delivered out ofindoor heat exchanger 5 is turned into refrigerant in a two-phase state including low-pressure gas refrigerant and low-pressure liquid refrigerant. - The refrigerant in a two-phase state flows into
outdoor heat exchanger 11. Inoutdoor heat exchanger 11, heat exchange is conducted between the incoming refrigerant in a two-phase state and the air supplied byoutdoor fan 21. Then, as a result of evaporation of the liquid refrigerant, the refrigerant in a two-phase state is turned into low-pressure gas refrigerant (a single phase). The low-pressure gas refrigerant delivered out ofoutdoor heat exchanger 11 flows through four-way valve 23 intocompressor 3 and then compressed into high-temperature and high-pressure gas refrigerant, which is again discharged fromcompressor 3. This cycle is repeated thereafter. - In the following, an explanation will be described with regard to the flow of the refrigerant in
outdoor heat exchanger 11 in the case whereoutdoor heat exchanger 11 is operated to function as an evaporator. As shown inFig. 7 , inoutdoor heat exchanger 11, the refrigerant first flows through auxiliaryheat exchange unit 15, and then flows through mainheat exchange unit 13. Also, by outdoor fan 21 (seeFig. 1 ), air flows from auxiliaryheat exchange unit 15a and mainheat exchange unit 13a in the first column (a windward column) toward auxiliaryheat exchange unit 15b and mainheat exchange unit 13b in the second column (a leeward column), as indicated by an arrow. - The refrigerant delivered from
throttle device 9 flows intodistributor 25 of auxiliaryheat exchange unit 15 and passes throughdistributor 25. Then, the refrigerant flows through firstheat transfer tube 33a of auxiliaryheat exchange unit 15a in the direction as indicated by an arrow. The refrigerant having flown through firstheat transfer tube 33a then flows through secondheat transfer tube 33b of auxiliaryheat exchange unit 15b in the direction as indicated by an arrow. - The refrigerant having flown through second
heat transfer tube 33b then flows intodistributor 29 of mainheat exchange unit 13. The refrigerant having flown intodistributor 29 then flows through fourthheat transfer tube 33d of mainheat exchange unit 13b in the direction as indicated by an arrow. The refrigerant having flown through fourthheat transfer tube 33d then flows through thirdheat transfer tube 33c of mainheat exchange unit 13a in the direction as indicated by an arrow. The refrigerant having flown through thirdheat transfer tube 33c then flows intoheader 27 and passes throughheader 27. Then, the refrigerant is delivered to the outside ofoutdoor heat exchanger 11. - In
outdoor heat exchanger 11 ofair conditioning apparatus 1 as described above, the temperature of the refrigerant flowing into auxiliary heat exchange unit 15 (a refrigerant inlet temperature), the temperature of the refrigerant delivered out of auxiliary heat exchange unit 15 (a refrigerant outlet temperature), and the outdoor air temperature are sensed. Then,air conditioning apparatus 1 is operated such that the refrigerant temperature establishes a prescribed temperature relation with the outdoor air temperature. Thereby, adhesion of frost to auxiliaryheat exchange unit 15 can be prevented. This will be described below. - First, a general idea about adhesion of frost to an outdoor heat exchanger will be hereinafter described. As an example of the condition that frost adheres to an outdoor heat exchanger, an explanation will be given with regard to the case where the air dry-bulb temperature is 2 °C and the air wet-bulb temperature is 1 °C. On the above-mentioned condition, since the dew point temperature of air is about -0.4 °C, the outdoor heat exchanger functions as an evaporator. When the air dry-bulb temperature falls below the dew point temperature, moisture condenses in the outdoor heat exchanger. Since the air dry-bulb temperature is lower than the freezing point at this time, the condensed moisture is to adhere as frost. Thus, in the outdoor heat exchanger, the ventilation resistance increases to thereby reduce the volume of air that passes through the outdoor heat exchanger, with the result that the heat exchange performance deteriorates.
- In this case, for ensuring the air conditioning performance of the indoor heat exchanger, it is necessary to increase the temperature difference between the temperature of the refrigerant flowing through the outdoor heat exchanger and the temperature of air. Thus, the temperature of the refrigerant flowing through the outdoor heat exchanger lowers, thereby causing further adhesion of frost to the outdoor heat exchanger. When frost adheres to the outdoor heat exchanger, the defrosting operation for melting the adhering frost is performed to thereby ensure the air conditioning performance, after which the normal operation is performed. It is a common practice to repeat the above-described operation when the outdoor air is at a low temperature.
- Then, as an example of the case where the outdoor air temperature is higher than the above-described condition, an explanation will be given with regard to the case where the air dry-bulb temperature is 5 °C and the air wet-bulb temperature is 4 °C. On the above-described condition, the dew point temperature of air is about 2.8 °C. Thus, when the air dry-bulb temperature falls below the dew point temperature due to heat exchange with the refrigerant, the moisture in air condenses and then adheres as water droplets to the outdoor heat exchanger. In this case, air that passes through the outdoor heat exchanger flows toward the leeward side of the outdoor heat exchanger at a temperature lower than the dew point temperature. Accordingly, when the refrigerant temperature is lower than the freezing point of water (for example, 0 °C), both the air dry-bulb temperature and the dew point temperature may reach the temperature close to the refrigerant temperature. Thus, when the dew point temperature is lower than the freezing point of water (for example, 0 °C), there is a possibility that frost may adhere to the outdoor heat exchanger.
- Then, adhesion of frost to the auxiliary heat exchange unit of the outdoor heat exchanger will be hereinafter specifically described. In this case, as an example of the operating condition, the air dry-bulb temperature is 2 °C, the air wet-bulb temperature is 1 °C, and the dew point temperature is -0.4 °C.
- First, as to an
outdoor heat exchanger 11 of an air conditioning apparatus in a comparative example, an explanation will be hereinafter given with regard to the case where when thisoutdoor heat exchanger 11 is operated to function as an evaporator, both mainheat exchange unit 13 and auxiliaryheat exchange unit 15 are used as evaporators (the first comparative example).Fig. 8 shows: a graph showing transition of the temperature of the refrigerant that flows through auxiliaryheat exchange unit 15 with respect to the refrigerant flow direction (a dashed line); a graph showing transition of the air dry-bulb temperature with respect to the air flow direction (a solid line); and a graph showing transition of the dew point temperature with respect to the air flow direction (a dotted line). - On this operating condition, the refrigerant inlet temperature (Tref-in) of the refrigerant flowing into auxiliary
heat exchange unit 15 is lower than the outdoor air temperature (air inlet temperature (Tair-in)). In this case, the air dry-bulb temperature immediately reaches approximately the same temperature as the dew point temperature. Since the dew point temperature is lower than the freezing point of water (for example, 0 °C), frost is to adhere to the most part ofoutdoor heat exchanger 11 including auxiliaryheat exchange unit 15. - When the defrosting operation for removing the frost adhering to
outdoor heat exchanger 11 is performed, water (drainage water) resulting from melting of frost is caused to flow by gravity toward the lower portion ofoutdoor heat exchanger 11 so as to be discharged fromoutdoor heat exchanger 11. However, inoutdoor heat exchanger 11 employing a flat tube as a heat transfer tube, the rate at which drainage water flows down is decreased, with the result that drainage water keeps flowing down from above toward auxiliaryheat exchange unit 15 disposed below mainheat exchange unit 13. This may consequently require an extra quantity of heat for defrosting auxiliaryheat exchange unit 15. Furthermore, the defrosting operation may require extra time. - Furthermore, the defrosting operation is generally performed in the same operation mode as that in the operation of the outdoor heat exchanger functioning as a condenser. Also, the direction in which the refrigerant flows is opposite to the direction in which the refrigerant flows during the operation of
outdoor heat exchanger 11 functioning as an evaporator. Thus, the refrigerant flows through auxiliaryheat exchange unit 15 after it flows through main heat exchange unit 13 (seeFig. 6 ). Auxiliaryheat exchange unit 15 is disposed below mainheat exchange unit 13. Accordingly, the quantity of heat of the refrigerant is removed in mainheat exchange unit 13 on the upstream side of the refrigerant flow. Thus, in auxiliaryheat exchange unit 15 on the downstream side, the performance of defrosting adhering frost deteriorates, which may lengthen the defrosting time. In this case, for example, the indoor temperature gradually lowers, so that a comfortable state may not be able to be maintained. - Furthermore, after the defrosting operation is ended in the state where frost still remains, and when the operation of
outdoor heat exchanger 11 functioning as an evaporator is resumed, frost may further grow to thereby damage auxiliaryheat exchange unit 15 and the like. Thus, it is conceivable that a significant problem may occur, for example, that a heat transfer tube is damaged to thereby cause leakage of refrigerant, and the like. - Then, as to an
outdoor heat exchanger 11 of another air conditioning apparatus in a comparative example, an explanation will be hereinafter given with regard to the case where, when thisoutdoor heat exchanger 11 is operated to function as an evaporator, mainheat exchange unit 13 is used as an evaporator and auxiliaryheat exchange unit 15 is used as a condenser (the second comparative example).Fig. 9 shows: a graph showing transition of the temperature of the refrigerant that flows through auxiliaryheat exchange unit 15 with respect to the refrigerant flow direction (a dashed line); a graph showing transition of the air dry-bulb temperature with respect to the air flow direction (a solid line); and a graph showing transition of the dew point temperature with respect to the air flow direction (a dotted line). - On this operating condition, the refrigerant outlet temperature (Tref-out) of the refrigerant delivered out of auxiliary
heat exchange unit 15 is higher than the outdoor air temperature (air inlet temperature (Tair-in)). In this case, frost does not adhere to auxiliaryheat exchange unit 15, so that auxiliaryheat exchange unit 15 is not damaged. Thus, the reliability as auxiliaryheat exchange unit 15 is ensured. - However, on the above-described operating condition, in auxiliary
heat exchange unit 15 used as a condenser, the refrigerant changes so as to be liquefied. Accordingly, in mainheat exchange unit 13 used as an evaporator, for evaporating the liquefied refrigerant, the load for heat exchange in mainheat exchange unit 13 is increased. Therefore, the heat exchange performance significantly deteriorates. - In contrast to the first comparative example and the second comparative example, in
outdoor heat exchanger 11 ofair conditioning apparatus 1 according to the embodiment, whenoutdoor heat exchanger 11 is operated to function as an evaporator, mainheat exchange unit 13 is used as an evaporator while auxiliaryheat exchange unit 15 is used as a condenser and an evaporator.Fig. 10 shows: a graph showing transition of the temperature of the refrigerant that flows through auxiliaryheat exchange unit 15 with respect to the refrigerant flow direction (a dashed line); a graph showing transition of the air dry-bulb temperature with respect to the air flow direction (a solid line); and a graph showing transition of the dew point temperature with respect to the air flow direction (a dotted line). - This operation of
outdoor heat exchanger 11 functioning as an evaporator is performed on the conditions that, in the case where the refrigerant outlet temperature (Tref-out) is lower than the freezing point of water (for example, 0 °C), the refrigerant inlet temperature (Tref-in) of the refrigerant flowing into auxiliaryheat exchange unit 15 is higher than the outdoor air temperature (air inlet temperature (Tair-in)), and the refrigerant outlet temperature of the refrigerant delivered out of auxiliary heat exchange unit 15 (Tref-out) is lower than the outdoor air temperature (air inlet temperature (Tair-in)). - The refrigerant flowing through auxiliary
heat exchange unit 15 is in a two-phase state including liquid refrigerant and gas refrigerant. Thus, adjusting the pressure loss of the refrigerant in auxiliaryheat exchange unit 15 means the same as adjusting the refrigerant temperature. In this auxiliaryheat exchange unit 15,pressure loss unit 17 is provided between auxiliaryheat exchange unit 15a located in the first column and auxiliaryheat exchange unit 15b located in the second column, so that auxiliaryheat exchange unit 15a is caused to function as a condenser and auxiliaryheat exchange unit 15b is caused to function as an evaporator. - When auxiliary
heat exchange unit 15a located in the windward column is caused to function as a condenser, the air temperature rises. Thus, even when auxiliaryheat exchange unit 15b located in the leeward column is caused to function as an evaporator, the air temperature is less likely to fall below the dew point temperature. Thereby, auxiliaryheat exchange unit 15 can be caused to entirely function as an evaporator in the state where the temperature of the refrigerant lowers, and also, adhesion of frost to auxiliaryheat exchange unit 15 can be prevented. In order to reliably prevent adhesion of frost to auxiliaryheat exchange unit 15, it is only necessary to perform the operation in such a manner such that the refrigerant outlet temperature (Tref-out) of the refrigerant delivered out of auxiliaryheat exchange unit 15 is higher than the dew point temperature. - In addition, in
outdoor heat exchanger 11 ofair conditioning apparatus 1 according to the embodiment as described above, the refrigerant flows through auxiliaryheat exchange unit 15a located on the windward side, and thereafter, flows through auxiliaryheat exchange unit 15b located on the leeward side. In other words, the refrigerant flows from the windward side toward the leeward side in the same manner as with the flow of air. Such the refrigerant flow is referred to as a parallel flow. In contrast to the parallel flow, the flow of the refrigerant from the leeward side toward the windward side is referred to as a counterflow. - In the following, an explanation will be given with regard to the case where the refrigerant is caused to flow as a counterflow through auxiliary
heat exchange unit 15 ofoutdoor heat exchanger 11 whenoutdoor heat exchanger 11 is operated to function as an evaporator (the third comparative example). As shown inFig. 11 , inoutdoor heat exchanger 11, the refrigerant first flows through auxiliaryheat exchange unit 15, and then flows through mainheat exchange unit 13. In this case, in auxiliaryheat exchange unit 15, the refrigerant first flows through secondheat transfer tube 33b of auxiliaryheat exchange unit 15b in the direction as indicated by an arrow. The refrigerant having flown through secondheat transfer tube 33b then flows through firstheat transfer tube 33a of auxiliaryheat exchange unit 15a in the direction as indicated by an arrow. The refrigerant having flown through auxiliaryheat exchange unit 15a is caused to flow through mainheat exchange unit 13 and thereafter delivered out ofoutdoor heat exchanger 11, in the same manner as shown inFig. 7 . -
Fig. 12 represents the case where the refrigerant flows as a counterflow, and shows: a graph showing transition of the temperature of the refrigerant that flows through auxiliaryheat exchange unit 15 with respect to the refrigerant flow direction (a dashed line); a graph showing transition of the air dry-bulb temperature with respect to the air flow direction (a solid line); and a graph showing transition of the dew point temperature with respect to the air flow direction (a dotted line). - In this case, even when
pressure loss unit 17 for lowering the pressure of the refrigerant is disposed, the temperature of the refrigerant flowing through auxiliaryheat exchange unit 15a located on the windward side falls below the temperature of the refrigerant flowing through auxiliaryheat exchange unit 15b located on the leeward side. At this time, when the temperature of air falls below the dew point temperature, there is a possibility that frost may adhere to auxiliaryheat exchange unit 15a. - In this case, when the temperature of the refrigerant flowing through auxiliary
heat exchange unit 15a located on the windward side is set to be higher than the outdoor air temperature (air inlet temperature (Tair-in)), the temperature of the refrigerant flowing through auxiliaryheat exchange unit 15b located on the leeward side is also higher than the outdoor air temperature (air inlet temperature (Tair-in)). Thereby, auxiliaryheat exchange unit 15 entirely functions as a condenser, so that the heat exchange performance deteriorates, as having been described with reference toFig. 9 . Therefore, in order thatoutdoor heat exchanger 11 is operated to function as an evaporator so as to prevent adhesion of frost to auxiliaryheat exchange unit 15, it is desirable to perform the operation such that the refrigerant flows as a parallel flow along the flow of air. - As to
outdoor heat exchanger 11 ofair conditioning apparatus 1 as described above, an explanation has been given with regard to the case wherepressure loss unit 17 is disposed between auxiliaryheat exchange unit 15a and auxiliaryheat exchange unit 15b. As a pressure loss unit not according to the invention, for example, the friction loss inside the heat transfer tube such as firstheat transfer tube 33a and secondheat transfer tube 33b may be employed. -
Fig. 13 represents the case whereoutdoor heat exchanger 11 is operated to function as an evaporator, and shows: a graph showing transition of the temperature of the refrigerant flowing through auxiliaryheat exchange unit 15 with respect to the refrigerant flow direction (a dashed line); a graph showing transition of the air dry-bulb temperature with respect to the air flow direction (a solid line); and a graph showing transition of the dew point temperature with respect to the air flow direction (a dotted line). - As shown in
Fig. 13 , as the refrigerant flows through a heat transfer tube (firstheat transfer tube 33a and secondheat transfer tube 33b), the temperature of the refrigerant lowers gradually by the friction loss inside the heat transfer tube. The friction loss inside the heat transfer tube is defined by the flow velocity of the refrigerant, the inside shape of the heat transfer tube, and the length of the heat transfer tube. Accordingly, the amount of the refrigerant circulating in the air conditioning apparatus, the dimensions of the heat transfer tube inside the outdoor heat exchanger, the number of paths in the heat transfer tube, and the like are set at their respective prescribed values based on the design. Then, on the condition that the refrigerant temperature establishes a prescribed temperature relation,outdoor heat exchanger 11 is operated to function as an evaporator, with the result that adhesion of frost to auxiliaryheat exchange unit 15 can be prevented. - In other words, in the case where the refrigerant outlet temperature (Tref-out) is lower than the freezing point of water (for example, 0 °C), the operation is performed such that the refrigerant inlet temperature (Tref-in) is higher than the outdoor air temperature (air inlet temperature (Tair-in)), and that the refrigerant outlet temperature (Tref-out) is lower than the outdoor air temperature (air inlet temperature (Tair-in)), so that adhesion of frost to auxiliary
heat exchange unit 15 can be prevented. Furthermore, by performing the operation such that the refrigerant outlet temperature (Tref-out) of the refrigerant delivered out of auxiliaryheat exchange unit 15 is higher than the dew point temperature, adhesion of frost to auxiliaryheat exchange unit 15 can be reliably prevented. - As
pressure loss unit 17 according to the present invention, disposed between auxiliaryheat exchange unit 15a and auxiliaryheat exchange unit 15b, a throttle device may be used, for example. -
Fig. 14 shows throttledevices 39 each of which is provided for a corresponding one of a plurality of firstheat transfer tubes 33a disposed in auxiliaryheat exchange unit 15a and a corresponding one of a plurality of secondheat transfer tubes 33b disposed in auxiliaryheat exchange unit 15b, such that each ofthrottle devices 39 is disposed for a route (path) extending from a corresponding one of firstheat transfer tubes 33a to a corresponding one of secondheat transfer tubes 33b.Fig. 15 showsthrottle device 39 provided such that the refrigerants having flown through firstheat transfer tubes 33a are joined on the upstream side of the throttle device, and then branched (divided) again on the downstream side of the throttle device so as to be delivered to their respective secondheat transfer tubes 33b. - In auxiliary
heat exchange unit 15, the opening degree ofthrottle device 39 is adjusted with respect to the temperature of the refrigerant on the upstream side ofthrottle device 39, so that the temperature of the refrigerant on the downstream side ofthrottle device 39 can be adjusted. In other words, whenthrottle device 39 is placed between auxiliaryheat exchange unit 15a and auxiliaryheat exchange unit 15b (between the columns), the temperature of the refrigerant flowing through auxiliaryheat exchange unit 15a located on the windward side and the temperature of the refrigerant flowing through auxiliaryheat exchange unit 15b located on the leeward side can be separately adjusted. - Thereby, auxiliary
heat exchange unit 15a located on the windward side can be entirely functioned as a condenser while auxiliaryheat exchange unit 15b located on the leeward side can be entirely functioned as an evaporator. Consequently, as having been described in the first embodiment, adhesion of frost to auxiliaryheat exchange unit 15 ofoutdoor heat exchanger 11 can be prevented during the operation ofoutdoor heat exchanger 11 functioning as an evaporator. - As
pressure loss unit 17 not according to the present invention, disposed between auxiliaryheat exchange unit 15a and auxiliaryheat exchange unit 15b, a header (an inter-columnar header) may be used, for example. -
Fig. 16 shows aninter-columnar header 41 disposed between auxiliaryheat exchange unit 15a and auxiliaryheat exchange unit 15b. As shown inFigs. 17, 18 and19 , a flow path through which refrigerant flows is provided insideinter-columnar header 41 for each route (path) extending from firstheat transfer tube 33a to secondheat transfer tube 33b. At some midpoint of the flow path, athrottle portion 43 is provided in such a manner that the cross-sectional area of this midpoint in the flow path is narrower than the cross-sectional area of another portion in the flow path. - By adjusting the width of
throttle portion 43 and the length of the flow path inthrottle portion 43, the pressure loss can be adjusted before and afterinter-columnar header 41. Also, the temperature of the refrigerant flowing through auxiliaryheat exchange unit 15a and the temperature of the refrigerant flowing through auxiliaryheat exchange unit 15b can be separately adjusted. Thereby, auxiliaryheat exchange unit 15a can be functioned as a condenser while auxiliaryheat exchange unit 15b can be functioned as an evaporator. Consequently, during the operation ofoutdoor heat exchanger 11 functioning as an evaporator, adhesion of frost to auxiliaryheat exchange unit 15 ofoutdoor heat exchanger 11 can be prevented. - As
pressure loss unit 17 not according to the present invention, disposed between auxiliaryheat exchange unit 15a and auxiliaryheat exchange unit 15b, for example, two headers may be used, including a header connected to auxiliaryheat exchange unit 15a and a header connected to auxiliaryheat exchange unit 15b. -
Fig. 20 shows a header including aheader 45a, aheader 45b, and a header connection tube 47.Header 45a is connected to firstheat transfer tube 33a of auxiliaryheat exchange unit 15a.Header 45b is connected to secondheat transfer tube 33b of auxiliaryheat exchange unit 15b. Header connection tube 47 provides connection betweenheader 45a andheader 45b. - In this case, for example, by adjusting the inner diameter and the like of header connection tube 47 so as to provide
throttle portion 43, the temperature of the refrigerant flowing through auxiliaryheat exchange unit 15a and the temperature of the refrigerant flowing through auxiliaryheat exchange unit 15b can be separately adjusted. Thus, adhesion of frost to auxiliaryheat exchange unit 15 ofoutdoor heat exchanger 11 can be prevented during the operation ofoutdoor heat exchanger 11 functioning as an evaporator. Furthermore, flow paths causing friction loss may be separately provided inside the flow paths ofheaders - As
pressure loss unit 17 not according to the present invention, disposed between auxiliaryheat exchange unit 15a and auxiliaryheat exchange unit 15b, for example, a U-shaped tube may be used other than a header. - As shown in
Fig. 21 , a U-shaped tube 49 is connected for each route (path) extending from firstheat transfer tube 33a to secondheat transfer tube 33b. In this case, by adjusting the inner diameter of U-shaped tube 49, the temperature of the refrigerant flowing through auxiliaryheat exchange unit 15a and the temperature of the refrigerant flowing through auxiliaryheat exchange unit 15b can be separately adjusted. Thus, adhesion of frost to auxiliaryheat exchange unit 15 ofoutdoor heat exchanger 11 can be prevented during the operation ofoutdoor heat exchanger 11 functioning as an evaporator. - As refrigerant used in
air conditioning apparatus 1 having been described in the above embodiment, by using any kind of refrigerant such as refrigerant R410A, refrigerant R407C, refrigerant R32, refrigerant R507A, refrigerant HFO1234yf, and the like, adhesion of frost to auxiliaryheat exchange unit 15 ofoutdoor heat exchanger 11 can be prevented. - Each of refrigerant R410A and refrigerant R407C is a refrigerant mixture and particularly referred to as a non-azeotropic refrigerant mixture. A non-azeotropic refrigerant mixture has different compositions in a vapor phase and in a liquid phase in a moist vapor state, and also has a characteristic that it undergoes a phase change of evaporation or condensation while it undergoes a temperature change and a composition conversion between two phases of gas refrigerant and liquid refrigerant under fixed pressure. Among such non-azeotropic refrigerant mixtures, refrigerant R407C and the like undergo extremely small temperature change during a phase change, and particularly, is referred to as a pseudo-azeotropic refrigerant mixture.
- Refrigerant R32 and refrigerant HFO1234yf each are refrigerant formed of a single component. Refrigerant R507A is a refrigerant mixture and referred to as an azeotropic refrigerant mixture. The azeotropic refrigerant mixture has a composition that is identical in a vapor phase and a liquid phase in moist vapor in a certain component ratio, and also has a characteristic that it undergoes a phase change of evaporation or condensation at a fixed temperature under fixed pressure, as in the case of the refrigerant formed of a single component.
- Also in the case where such a non-azeotropic refrigerant mixture, a pseudo-azeotropic refrigerant mixture, refrigerant formed of a single component, or an azeotropic refrigerant mixture is used, when the refrigerant outlet temperature is lower than the freezing point of water (for example, 0 °C), the operation is performed such that the refrigerant inlet temperature is higher than the outdoor air temperature and that the refrigerant outlet temperature is lower than the outdoor air temperature, with the result that adhesion of frost to auxiliary
heat exchange unit 15 ofoutdoor heat exchanger 11 can be prevented. Furthermore, when the operation is performed such that the refrigerant outlet temperature of the refrigerant delivered out of auxiliaryheat exchange unit 15 is higher than the dew point temperature, adhesion of frost to auxiliaryheat exchange unit 15 can be reliably prevented. - Furthermore, as refrigeration oil used in the air conditioning apparatus, refrigeration oil having compatibility is employed in consideration of the mutual solubility to the refrigerant to be applied. For fluorocarbon-based refrigerant such as refrigerant R410A, for example, alkylbenzene oil-based refrigeration oil, ester oil-based refrigeration oil or ether oil-based refrigeration oil is used. Other than the above, mineral oil-based refrigeration oil or fluorine oil-based refrigeration oil may be used.
- Also in the case where the refrigeration oil as described above is used, when the refrigerant outlet temperature is lower than the freezing point of water (for example, 0 °C), the operation is performed such that the refrigerant inlet temperature is higher than the outdoor air temperature and that the refrigerant outlet temperature is lower than the outdoor air temperature, with the result that adhesion of frost to auxiliary
heat exchange unit 15 ofoutdoor heat exchanger 11 can be prevented. - In the above-described embodiment, an explanation has been given with regard to the air conditioning apparatus as an example of a refrigeration cycle apparatus. The refrigeration cycle apparatus is not limited to an air conditioning apparatus, but may be applicable, for example, also to an apparatus including an outdoor heat exchanger such as a heat pump water heater configured to perform heat exchange with air. Furthermore, various combinations can be made as appropriate for the refrigeration cycle apparatus including an outdoor heat exchanger, which has been described in the embodiments.
- The embodiments disclosed herein are merely by way of example and not limited thereto. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope of the claims.
- The present invention is effectively utilized in a refrigeration cycle apparatus such as an air conditioning apparatus including an outdoor heat exchanger equipped with a main heat exchange unit and an auxiliary heat exchange unit.
- 1 air conditioning apparatus, 3 compressor, 5 indoor heat exchanger, 7 indoor fan, 9 throttle device, 11 outdoor heat exchanger, 13 main heat exchange unit, 13a, 13b main heat exchange unit, 15 auxiliary heat exchange unit, 15a, 15b auxiliary heat exchange unit, 17 pressure loss unit, 21 outdoor fan, 23 four-way valve, 25 distributor, 27 header, 29 distributor, 31 fin, 33a first heat transfer tube, 33b second heat transfer tube, 33c third heat transfer tube, 33d fourth heat transfer tube, 35 refrigerant path, 37 refrigerant pipe, 39 throttle device, 41 inter-columnar header, 43 throttle portion, 45a, 45b header, 47 header connection tube, 49 U-shaped tube, 51 control unit, 53, 55, 57 temperature sensor.
Claims (8)
- A refrigeration cycle apparatus (1) comprising refrigerant pipes, a compressor (3), an indoor heat exchanger (5), a four-way valve (23), three temperature sensors (53, 55, 57), a control unit (51), and an outdoor heat exchanger (11) configured to be operated functioning as a condenser or as an evaporator, wherein the refrigerant pipes connect:the compressor (3) with the indoor heat exchanger (5) via the four-way valve (23),the indoor heat exchanger (5) with the outdoor heat exchanger (11), andthe outdoor heat exchanger (11) with the compressor (3) via the four-way valve (23),the outdoor heat exchanger (11) includinga first heat exchange unit (15), anda second heat exchange unit (13) that is disposed adjacent to the first heat exchange unit (15),the first heat exchange unit (15) includinga plurality of fins (31) each formed in a plate shape,a first heat transfer tube (33a) disposed to penetrate the plurality of fins (31) in a first direction,a second heat transfer tube (33b) disposed to penetrate the plurality of fins (31) in the first direction and located at a distance from the first heat transfer tube (33a) in a direction perpendicular to the first direction, anda pressure loss mechanism (17) configured to lower pressure of refrigerant flowing through the first heat exchange unit (15),wherein the three temperature sensors (53) are configured to sense a temperature of refrigerant flowing into the first heat exchange unit (15), a temperature of refrigerant flowing out of the first heat exchange unit (15), and an outdoor air temperature, andthe control unit (51) is configured to operate, during an operation of the outdoor heat exchanger (11) functioning as an evaporator:the four way valve (23) such that single-phase, high-temperature, high-pressure gaseous refrigerant discharged from the compressor (3) is delivered to the indoor heat exchanger (5) and such that single-phase, low-pressure gas refrigerant discharged from the outdoor heat exchanger (11) is delivered to the compressor (3), and,when the temperature of refrigerant flowing out of the first heat exchange unit (15) is lower than a freezing point of water, the pressure loss mechanism (17) to adjust the pressure loss of the refrigerant in the first heat exchange unit (15) such that the temperature of refrigerant flowing into the first heat exchange unit (15) is higher than the outdoor air temperature and that the temperature of the refrigerant flowing out of the first heat exchange unit (15) is lower than the outdoor air temperature.
- The refrigeration cycle apparatus (1) according to claim 1, wherein the operation is performed such that the temperature of the refrigerant flowing out of the first heat exchange unit (15) is higher than a dew point temperature.
- The refrigeration cycle apparatus according to claim 1, wherein
the first heat transfer tube (33a) has a first end and a second end,
the second heat transfer tube (33b) has a third end and a fourth end,
the third end of the second heat transfer tube (33b) is connected to the second end of the first heat transfer tube (33a), and
the fourth end of the second heat transfer tube (33b) is connected to the second heat exchange unit (13). - The refrigeration cycle apparatus (1) according to claim 3, wherein
the pressure loss mechanism (17) includes a throttle portion (39, 41) disposed between the second end of the first heat transfer tube (33a) and the third end of the second heat transfer tube (33b), and
the throttle portion (41) includesa first flow path having a first cross-sectional area, anda second flow path (43) having a second cross-sectional area that is smaller than the first cross-sectional area. - The refrigeration cycle apparatus (1) according to claim 4, wherein the throttle portion includes (39) a throttle adjustment unit configured to adjust the second cross-sectional area of the second flow path.
- The refrigeration cycle apparatus (1) according to claim 1, wherein the pressure loss mechanism (17) includes the first heat transfer tube (33a) and the second heat transfer tube (33b).
- The refrigeration cycle apparatus (1) according to claim 1, wherein
the first heat transfer tube (33a) is formed as a first flat tube having a flat cross-sectional shape that has a major axis and a minor axis, and
the second heat transfer tube (33b) is formed as a second flat tube having the flat cross-sectional shape, the second flat tube being located at a distance from the first flat tube in a direction in which the major axis extends. - The refrigeration cycle apparatus (1) according to claim 1, further comprising an air blower unit (21) configured to blow air from a side on which the first heat transfer tube (33a) is disposed toward a side on which the second heat transfer tube (33b) is disposed, wherein
refrigerant flows from the first heat transfer tube (33a) into the second heat transfer tube (33b).
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PCT/JP2016/068810 WO2017221400A1 (en) | 2016-06-24 | 2016-06-24 | Refrigerating cycle device and outdoor heat exchanger used in same |
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US (1) | US20190128574A1 (en) |
EP (1) | EP3477227B1 (en) |
JP (1) | JPWO2017221400A1 (en) |
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JP7406297B2 (en) * | 2018-03-01 | 2023-12-27 | ダイキン工業株式会社 | Heat exchanger |
WO2020194517A1 (en) * | 2019-03-26 | 2020-10-01 | 三菱電機株式会社 | Heat exchanger and refrigeration cycle device |
JP7425282B2 (en) * | 2019-09-30 | 2024-01-31 | ダイキン工業株式会社 | Evaporator and refrigeration cycle equipment equipped with it |
CN111238090B (en) * | 2020-01-09 | 2021-02-02 | 西安交通大学 | Micro-channel evaporator and control method thereof |
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WO2023234121A1 (en) * | 2022-05-31 | 2023-12-07 | 株式会社デンソーエアクール | Vehicle-mounted heat exchanger |
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- 2016-06-24 CN CN201680085743.0A patent/CN109312971B/en active Active
- 2016-06-24 EP EP16906317.9A patent/EP3477227B1/en active Active
- 2016-06-24 US US16/089,634 patent/US20190128574A1/en not_active Abandoned
- 2016-06-24 ES ES16906317T patent/ES2844591T3/en active Active
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Title |
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None * |
Also Published As
Publication number | Publication date |
---|---|
JPWO2017221400A1 (en) | 2019-02-28 |
US20190128574A1 (en) | 2019-05-02 |
EP3477227A4 (en) | 2019-08-07 |
CN109312971A (en) | 2019-02-05 |
ES2844591T3 (en) | 2021-07-22 |
CN109312971B (en) | 2020-11-06 |
EP3477227A1 (en) | 2019-05-01 |
WO2017221400A1 (en) | 2017-12-28 |
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