EP1944562B1 - Air conditioner - Google Patents
Air conditioner Download PDFInfo
- Publication number
- EP1944562B1 EP1944562B1 EP06798039.1A EP06798039A EP1944562B1 EP 1944562 B1 EP1944562 B1 EP 1944562B1 EP 06798039 A EP06798039 A EP 06798039A EP 1944562 B1 EP1944562 B1 EP 1944562B1
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- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- refrigerant
- pressure
- low
- pressure refrigerant
- 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.)
- Not-in-force
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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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
- F28D7/0016—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being bent
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
- F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
Definitions
- the present invention relates to an air conditioning apparatus that uses a supercooling heat exchanger.
- FIG. 4 shows a configuration of an air conditioning apparatus that uses a conventional supercooling heat exchanger.
- a compressor 1 a four-way switching valve 2, an outdoor-side heat exchanger 3 that functions as a condenser during the cooling operation and as an evaporator during the heating operation, a heating expansion valve 4, a receiver 5, a cooling expansion valve 6, an indoor-side heat exchanger 8 that functions as an evaporator during the cooling operation and as a condenser during the heating operation, and other components are connected sequentially via the four-way switching valve 2, thereby constituting a refrigerating cycle for air conditioning as is shown in the drawing.
- the switching operation of the four-way switching valve 2 allows a refrigerant to be reversibly circulated in the direction shown by solid arrows in the drawing during the cooling operation, and in the direction shown by dashed arrows in the drawing during the heating operation, thereby resulting in cooling and heating, respectively.
- the outdoor-side heat exchanger 3 and the indoor-side heat exchanger 8 are both configured to include numerous refrigerant paths. Therefore, even if the capacity of the flow divider portion to distribute the refrigerant is improved to a maximum, it is difficult to distribute the refrigerant evenly throughout the refrigerant paths.
- the amount of pressure reduction in the heating expansion valve 4 or cooling expansion valve 6 is appropriately set so that the refrigerant of the exit side of the outdoor-side heat exchanger 3 or the indoor-side heat exchanger 8 is in appropriately humidified condition.
- maximum performance as the evaporator can be guaranteed even if, for example, the refrigerant drifts into the outdoor-side heat exchanger 3 or the indoor-side heat exchanger 8, and therefore the evaporator can be made as compact as possible.
- the performance of the evaporator can be further improved by removing the refrigerant supercooling of the exit side of the condenser, increasing the difference in enthalpy of the evaporator side to reduce circulating volume, and reducing the pressure loss on the evaporator side.
- This is accomplished by providing a liquid-gas heat exchanger 13 having a double pipe structure, composed of a low-pressure refrigerant suction pipe 14 as an inner pipe and a high-pressure liquid refrigerant pipe 15 as an outer pipe, as a supercooling heat exchanger.
- liquid-gas heat exchanger 13 e.g., the flow rate of the refrigerant, the length of the double pipes, the inside diameter of the outer pipe, and the outside diameter of the inner pipe are set in a predetermined manner appropriately.
- the liquid-gas heat exchanger 13 As the liquid-gas heat exchanger 13 is provided in this manner, the refrigerant of the exit side of the evaporator is superheated, backflow into the compressor 1 can be prevented, the refrigerant of the exit side of the condenser is supercooled, and the difference in enthalpy of the evaporator side can be increased to reduce circulating volume. Therefore, the pressure loss can also be reduced, and the evaporator 8 (or the evaporator 3) can be made even more compact (see JP-A-5-332641 (Specification pg. 1-5, FIGS. 1-5 ) as an example).
- JP-A-06-213518 An air conditioner having the features defined in the preamble of claim 1 is known from JP-A-06-213518 .
- JP-A-06-213518 further suggests to use a control and corresponding valve to achieve that the flow of liquid refrigerant through the high-pressure liquid refrigerant pipe is either directed concurrently with the flow of the low-pressure refrigerant and the low-pressure refrigerant suction pipe during cooling operation and countercurrently during heating operation.
- a supercooling heat exchanger in which heat is exchanged between a high-pressure refrigerant and a low-pressure refrigerant as described above has problems in that since the refrigerant flows in opposite directions during cooling and heating, the flows are parallel in either of the operating modes, and heat exchange is less efficient. For example, in the case shown in FIG. 4 , the flows are countercurrent to each other during cooling and are parallel to each other during heating, causing heat exchange to be less efficient.
- the present invention was designed in order to resolve such problems, and an object thereof is to provide an air conditioning apparatus comprising a supercooling heat exchanger for exchanging heat between a low-pressure refrigerant and a high-pressure refrigerant, wherein the supercooling heat exchanger is divided into a first heat exchanger and a second heat exchanger, either one of these heat exchangers is disposed so that the high-pressure refrigerant and the low-pressure refrigerant flow countercurrent to each other, and the other heat exchanger is disposed so that the high-pressure refrigerant and the low-pressure refrigerant flow parallel to each other, whereby the above-described problems with conventional practice are appropriately resolved.
- the present invention suggests an air conditioning apparatus having the features of claim 1. Embodiments are named in the dependent claims.
- the supercooling heat exchanger 13 for exchanging heat between a high-pressure refrigerant and a low-pressure refrigerant as previously described has problems in that since the refrigerants flow in opposite directions during cooling and heating, the flows are parallel in either of the operating modes, and heat exchange is less efficient.
- the supercooling heat exchanger 13 is divided into two heat exchangers, i.e., the first heat exchanger 13A and the second heat exchanger 13B, either the first heat exchanger 13A or the second heat exchanger 13B is disposed so that the high-pressure refrigerant and the low-pressure refrigerant flow countercurrent to each other, and the other heat exchanger, i.e., either the second heat exchanger 13B or the first heat exchanger 13A, is disposed so that the high-pressure refrigerant and the low-pressure refrigerant flow parallel to each other, whereby the supercooling heat exchanger 13 can maintain its heat exchange performance without variation even if the direction of refrigerant flow changes during cooling or heating.
- the capacity of the heat exchanger itself does not need to be increased, and the supercooling heat exchangers 13A, 13B can be made as small as possible.
- first and second supercooling heat exchangers 13A, 13B both have a double-pipe structure in which the high-pressure liquid refrigerant pipe 15 is fitted coaxially over the low-pressure refrigerant suction pipe 14, the structures of the supercooling heat exchangers 13A, 13B themselves are simplified.
- the supercooling heat exchanger can maintain high heat exchange performance even when the flows of the refrigerants change direction during cooling and heating.
- the evaporator can be made more compact.
- the supercooling heat exchanger itself can be made as small as possible.
- Compressor 2 Four-way switching valve 3 Outdoor-side heat exchanger 4, 6 Expansion valves 5 Receiver 8 Indoor-side heat exchanger 13A First heat exchanger 13B Second heat exchanger 14 Low-pressure refrigerant suction pipe 15 High-pressure liquid refrigerant pipe 16 Muffler
- FIGS. 1 and 2 of the attached drawings show the configuration of the entirety and relevant parts of the refrigerant circuits in an air conditioning apparatus according to a preferred embodiment of the present invention.
- a compressor 1, a four-way switching valve 2, an outdoor-side heat exchanger 3 that functions as a condenser during the cooling operation and as an evaporator during the heating operation, a heating expansion valve 4, a receiver 5, a cooling expansion valve 6, an indoor-side heat exchanger 8 that functions as an evaporator during the cooling operation and as a condenser during the heating operation, and other components are connected sequentially via the four-way switching valve 2, thereby constituting a refrigerating cycle for air conditioning as shown in the drawing.
- the switching operation of the four-way switching valve 2 allows refrigerant to be reversibly circulated in the direction shown by solid arrows in the diagram during the cooling operation, and in the direction shown by dashed arrows in the diagram during the heating operation, thereby resulting in cooling and heating, respectively.
- a liquid-gas heat exchanger 13 is provided in this embodiment as well as the case in FIG. 4 described previously.
- This liquid-gas heat exchanger 13 comprises a low-pressure refrigerant suction pipe 14 and a high-pressure liquid refrigerant pipe 15, and is used as a supercooling heat exchanger for exchanging heat between low-pressure refrigerant and high-pressure refrigerant.
- liquid-gas heat exchanger 13 As the liquid-gas heat exchanger 13 is provided in this manner, refrigerant of the exit side of the evaporator is superheated, backflow into the compressor 1 can be prevented, the refrigerant of the exit side of the condenser is supercooled, and the difference in enthalpy of the evaporator side can be increased to reduce refrigerant circulating volume, as was described previously. Therefore, pressure loss can also be reduced, and the evaporator (the indoor-side heat exchanger 8 during cooling or the outdoor-side heat exchanger 3 during heating) can be made as compact as possible.
- the liquid-gas heat exchanger 13 is divided into two liquid-gas heat exchangers, i.e., a first liquid-gas heat exchanger 13A and a second liquid-gas heat exchanger 13B in which refrigerants flow in mutually opposite directions.
- the first heat exchanger 13A may, for example, be disposed so that the high-pressure refrigerant and low-pressure refrigerant flow countercurrent to each other, and the second heat exchanger 13B may be disposed so that the high-pressure refrigerant and low-pressure refrigerant flow parallel to each other.
- the liquid-gas heat exchanger 13 can maintain its performance without variation as shown in the diagrams, even when the refrigerant flow changes direction during cooling and heating.
- the refrigerant of the exit side of the condenser is supercooled without variation during heating, and the difference in enthalpy of the evaporator side can be increased to reduce the circulating volume.
- first and second liquid-gas heat exchangers 13A, 13B are both configured so that the high-pressure liquid refrigerant pipe 15 from the exit side of the condenser that is smaller in diameter than the low-pressure refrigerant suction pipe 14 is wound in a helical structure in mutually opposite directions, for example, as shown in detail in FIG. 2 , around the external periphery of the low-pressure refrigerant suction pipe 14.
- the existing low-pressure refrigerant suction pipe 14 leads from the indoor-side heat exchanger (evaporator) 8 during cooling or from the outdoor-side heat exchanger (evaporator) 3 during heating back to the refrigerant suction inlet in the compressor 1 via the four-way switching valve 2. Therefore, the supercooling heat exchanger 13 itself can have a small capacity and can be made as small in size as possible.
- the improvement in supercooling heat exchange efficiency is effective in contributing to making the evaporators themselves smaller and more compact.
- winding the high-pressure liquid refrigerant pipe 15 around the existing low-pressure refrigerant suction pipe 14 as shown in FIG. 2 makes it possible to inhibit increases in suctioned gas pressure loss, and to prevent the COP from decreasing.
- the reference numeral 16 in FIG. 2 denotes a muffler for gas refrigerant in the low-pressure refrigerant suction pipe 14.
- the divided first and second heat exchangers 13A, 13B have a structure in which a high-pressure liquid refrigerant pipe 15 having a small diameter is helically wound around an existing low-pressure refrigerant suction pipe 14 that goes from the four-way switching valve 2 to the refrigerant suction inlet of the compressor 1, as shown in FIG. 2 .
- a high-pressure liquid refrigerant pipe 15 having a small diameter is helically wound around an existing low-pressure refrigerant suction pipe 14 that goes from the four-way switching valve 2 to the refrigerant suction inlet of the compressor 1, as shown in FIG. 2 .
- FIG. 1 In another possible configuration, as shown in FIG.
- the first and second heat exchangers 13A, 13B have a double-pipe structure in which a high-pressure liquid refrigerant pipe 15 larger in diameter than the low-pressure refrigerant suction pipe 14 is fitted as a coaxial structure around the external periphery of the low-pressure refrigerant suction pipe 14, and these pipes are disposed so that the refrigerant flows in mutually opposite directions.
- first and second heat exchangers 13A, 13B for supercooling have a double-pipe structure in which the high-pressure liquid refrigerant pipe 15 is fitted as a coaxial structure around the low-pressure refrigerant suction pipe 14, the structure of the supercooling heat exchanger itself is simplified.
- the present invention can be widely utilized within the field of air conditioning apparatuses that use supercooling heat exchangers.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
- The present invention relates to an air conditioning apparatus that uses a supercooling heat exchanger.
-
FIG. 4 shows a configuration of an air conditioning apparatus that uses a conventional supercooling heat exchanger. - In this air conditioning apparatus, a
compressor 1, a four-way switching valve 2, an outdoor-side heat exchanger 3 that functions as a condenser during the cooling operation and as an evaporator during the heating operation, aheating expansion valve 4, areceiver 5, acooling expansion valve 6, an indoor-side heat exchanger 8 that functions as an evaporator during the cooling operation and as a condenser during the heating operation, and other components are connected sequentially via the four-way switching valve 2, thereby constituting a refrigerating cycle for air conditioning as is shown in the drawing. - The switching operation of the four-
way switching valve 2 allows a refrigerant to be reversibly circulated in the direction shown by solid arrows in the drawing during the cooling operation, and in the direction shown by dashed arrows in the drawing during the heating operation, thereby resulting in cooling and heating, respectively. - The outdoor-
side heat exchanger 3 and the indoor-side heat exchanger 8 are both configured to include numerous refrigerant paths. Therefore, even if the capacity of the flow divider portion to distribute the refrigerant is improved to a maximum, it is difficult to distribute the refrigerant evenly throughout the refrigerant paths. - In view of this, when the outdoor-
side heat exchanger 3 or the indoor-side heat exchanger 8 functions as the evaporator, the amount of pressure reduction in theheating expansion valve 4 orcooling expansion valve 6 is appropriately set so that the refrigerant of the exit side of the outdoor-side heat exchanger 3 or the indoor-side heat exchanger 8 is in appropriately humidified condition. Thus, maximum performance as the evaporator can be guaranteed even if, for example, the refrigerant drifts into the outdoor-side heat exchanger 3 or the indoor-side heat exchanger 8, and therefore the evaporator can be made as compact as possible. - The performance of the evaporator can be further improved by removing the refrigerant supercooling of the exit side of the condenser, increasing the difference in enthalpy of the evaporator side to reduce circulating volume, and reducing the pressure loss on the evaporator side. This is accomplished by providing a liquid-
gas heat exchanger 13 having a double pipe structure, composed of a low-pressurerefrigerant suction pipe 14 as an inner pipe and a high-pressureliquid refrigerant pipe 15 as an outer pipe, as a supercooling heat exchanger. - In this liquid-
gas heat exchanger 13, e.g., the flow rate of the refrigerant, the length of the double pipes, the inside diameter of the outer pipe, and the outside diameter of the inner pipe are set in a predetermined manner appropriately. - As the liquid-
gas heat exchanger 13 is provided in this manner, the refrigerant of the exit side of the evaporator is superheated, backflow into thecompressor 1 can be prevented, the refrigerant of the exit side of the condenser is supercooled, and the difference in enthalpy of the evaporator side can be increased to reduce circulating volume. Therefore, the pressure loss can also be reduced, and the evaporator 8 (or the evaporator 3) can be made even more compact (seeJP-A-5-332641 FIGS. 1-5 ) as an example). - An air conditioner having the features defined in the preamble of
claim 1 is known fromJP-A-06-213518 JP-A-06-213518 - However, a supercooling heat exchanger in which heat is exchanged between a high-pressure refrigerant and a low-pressure refrigerant as described above has problems in that since the refrigerant flows in opposite directions during cooling and heating, the flows are parallel in either of the operating modes, and heat exchange is less efficient. For example, in the case shown in
FIG. 4 , the flows are countercurrent to each other during cooling and are parallel to each other during heating, causing heat exchange to be less efficient. - The present invention was designed in order to resolve such problems, and an object thereof is to provide an air conditioning apparatus comprising a supercooling heat exchanger for exchanging heat between a low-pressure refrigerant and a high-pressure refrigerant, wherein the supercooling heat exchanger is divided into a first heat exchanger and a second heat exchanger, either one of these heat exchangers is disposed so that the high-pressure refrigerant and the low-pressure refrigerant flow countercurrent to each other, and the other heat exchanger is disposed so that the high-pressure refrigerant and the low-pressure refrigerant flow parallel to each other, whereby the above-described problems with conventional practice are appropriately resolved.
- To achieve these objects, the present invention suggests an air conditioning apparatus having the features of
claim 1. Embodiments are named in the dependent claims. - The
supercooling heat exchanger 13 for exchanging heat between a high-pressure refrigerant and a low-pressure refrigerant as previously described has problems in that since the refrigerants flow in opposite directions during cooling and heating, the flows are parallel in either of the operating modes, and heat exchange is less efficient. - However, as the
supercooling heat exchanger 13 is divided into two heat exchangers, i.e., thefirst heat exchanger 13A and thesecond heat exchanger 13B, either thefirst heat exchanger 13A or thesecond heat exchanger 13B is disposed so that the high-pressure refrigerant and the low-pressure refrigerant flow countercurrent to each other, and the other heat exchanger, i.e., either thesecond heat exchanger 13B or thefirst heat exchanger 13A, is disposed so that the high-pressure refrigerant and the low-pressure refrigerant flow parallel to each other, whereby thesupercooling heat exchanger 13 can maintain its heat exchange performance without variation even if the direction of refrigerant flow changes during cooling or heating. - When the first and
second heat exchangers liquid refrigerant pipe 15 around the low-pressurerefrigerant suction pipe 14, the capacity of the heat exchanger itself does not need to be increased, and thesupercooling heat exchangers - When the first and second
supercooling heat exchangers liquid refrigerant pipe 15 is fitted coaxially over the low-pressurerefrigerant suction pipe 14, the structures of thesupercooling heat exchangers - According to the present invention, the supercooling heat exchanger can maintain high heat exchange performance even when the flows of the refrigerants change direction during cooling and heating. As a result, the evaporator can be made more compact.
- In this case, when the each heat exchanger is configured by winding a high-pressure liquid refrigerant pipe around a low-pressure refrigerant suction pipe, the supercooling heat exchanger itself can be made as small as possible.
-
-
FIG. 1 is a refrigeration circuit diagram showing the configuration of an air conditioning apparatus according to Preferred Embodiment of the present invention; -
FIG. 2 is an enlarged view showing the portion of the first and second liquid-gas heat exchangers as relevant parts of the same apparatus; -
FIG. 3 is an enlarged view showing a portion of the first and second liquid-gas heat exchangers according to another embodiment of the present invention; and -
FIG. 4 is a refrigerant circuit diagram showing the configuration of a conventional example of air conditioning apparatus. -
1 Compressor 2 Four- way switching valve 3 Outdoor- side heat exchanger 4, 6 Expansion valves 5 Receiver 8 Indoor- side heat exchanger 13A First heat exchanger 13B Second heat exchanger 14 Low-pressure refrigerant suction pipe 15 High-pressure liquid refrigerant pipe 16 Muffler -
FIGS. 1 and2 of the attached drawings show the configuration of the entirety and relevant parts of the refrigerant circuits in an air conditioning apparatus according to a preferred embodiment of the present invention. - First, as shown in
FIG. 1 , in the air conditioning apparatus of this embodiment, acompressor 1, a four-way switching valve 2, an outdoor-side heat exchanger 3 that functions as a condenser during the cooling operation and as an evaporator during the heating operation, aheating expansion valve 4, areceiver 5, acooling expansion valve 6, an indoor-side heat exchanger 8 that functions as an evaporator during the cooling operation and as a condenser during the heating operation, and other components are connected sequentially via the four-way switching valve 2, thereby constituting a refrigerating cycle for air conditioning as shown in the drawing. - The switching operation of the four-
way switching valve 2 allows refrigerant to be reversibly circulated in the direction shown by solid arrows in the diagram during the cooling operation, and in the direction shown by dashed arrows in the diagram during the heating operation, thereby resulting in cooling and heating, respectively. - A liquid-
gas heat exchanger 13 is provided in this embodiment as well as the case inFIG. 4 described previously. This liquid-gas heat exchanger 13 comprises a low-pressurerefrigerant suction pipe 14 and a high-pressureliquid refrigerant pipe 15, and is used as a supercooling heat exchanger for exchanging heat between low-pressure refrigerant and high-pressure refrigerant. - As the liquid-
gas heat exchanger 13 is provided in this manner, refrigerant of the exit side of the evaporator is superheated, backflow into thecompressor 1 can be prevented, the refrigerant of the exit side of the condenser is supercooled, and the difference in enthalpy of the evaporator side can be increased to reduce refrigerant circulating volume, as was described previously. Therefore, pressure loss can also be reduced, and the evaporator (the indoor-side heat exchanger 8 during cooling or the outdoor-side heat exchanger 3 during heating) can be made as compact as possible. - However, in this embodiment, unlike in the case in
FIG. 4 described previously, the liquid-gas heat exchanger 13 is divided into two liquid-gas heat exchangers, i.e., a first liquid-gas heat exchanger 13A and a second liquid-gas heat exchanger 13B in which refrigerants flow in mutually opposite directions. Thefirst heat exchanger 13A may, for example, be disposed so that the high-pressure refrigerant and low-pressure refrigerant flow countercurrent to each other, and thesecond heat exchanger 13B may be disposed so that the high-pressure refrigerant and low-pressure refrigerant flow parallel to each other. - Therefore, with this configuration, the liquid-
gas heat exchanger 13 can maintain its performance without variation as shown in the diagrams, even when the refrigerant flow changes direction during cooling and heating. As a result, the refrigerant of the exit side of the condenser is supercooled without variation during heating, and the difference in enthalpy of the evaporator side can be increased to reduce the circulating volume. - Moreover, the first and second liquid-
gas heat exchangers liquid refrigerant pipe 15 from the exit side of the condenser that is smaller in diameter than the low-pressurerefrigerant suction pipe 14 is wound in a helical structure in mutually opposite directions, for example, as shown in detail inFIG. 2 , around the external periphery of the low-pressurerefrigerant suction pipe 14. The existing low-pressurerefrigerant suction pipe 14 leads from the indoor-side heat exchanger (evaporator) 8 during cooling or from the outdoor-side heat exchanger (evaporator) 3 during heating back to the refrigerant suction inlet in thecompressor 1 via the four-way switching valve 2. Therefore, thesupercooling heat exchanger 13 itself can have a small capacity and can be made as small in size as possible. - The improvement in supercooling heat exchange efficiency is effective in contributing to making the evaporators themselves smaller and more compact.
- Furthermore, winding the high-pressure
liquid refrigerant pipe 15 around the existing low-pressurerefrigerant suction pipe 14 as shown inFIG. 2 makes it possible to inhibit increases in suctioned gas pressure loss, and to prevent the COP from decreasing. - The
reference numeral 16 inFIG. 2 denotes a muffler for gas refrigerant in the low-pressurerefrigerant suction pipe 14. - In the above embodiment, the divided first and
second heat exchangers liquid refrigerant pipe 15 having a small diameter is helically wound around an existing low-pressurerefrigerant suction pipe 14 that goes from the four-way switching valve 2 to the refrigerant suction inlet of thecompressor 1, as shown inFIG. 2 . In another possible configuration, as shown inFIG. 3 , for example, the first andsecond heat exchangers liquid refrigerant pipe 15 larger in diameter than the low-pressurerefrigerant suction pipe 14 is fitted as a coaxial structure around the external periphery of the low-pressurerefrigerant suction pipe 14, and these pipes are disposed so that the refrigerant flows in mutually opposite directions. - Thus, as the first and
second heat exchangers liquid refrigerant pipe 15 is fitted as a coaxial structure around the low-pressurerefrigerant suction pipe 14, the structure of the supercooling heat exchanger itself is simplified. - The present invention can be widely utilized within the field of air conditioning apparatuses that use supercooling heat exchangers.
Claims (3)
- An air conditioning apparatus comprising
a supercooling heat exchanger (13) having a low-pressure refrigerant suction pipe (14) and a high-pressure liquid refrigerant pipe (15) for exchanging heat between a low-pressure refrigerant and a high-pressure refrigerant;
the supercooling heat exchanger (13) is divided into a first and a second heat exchanger (13A), (13B); characterized in that
in one of the first heat exchanger (13A) and the second heat exchanger (13B) the high-pressure liquid refrigerant pipe (15) and the low-pressure refrigerant suction pipe (14) are disposed so that the high-pressure refrigerant and the low-pressure refrigerant flow countercurrently to each other; and
in the other of the second heat exchanger (13B) and the first heat exchanger (13A) the high-pressure liquid refrigerant pipe (15) and the low-pressure refrigerant suction pipe (14) are disposed so that the high-pressure refrigerant and the low-pressure refrigerant flow concurrently to each other. - The air conditioning apparatus according to claim 1, characterized in that the high-pressure liquid refrigerant pipe (15) is wound around the external periphery of the low-pressure refrigerant suction pipe (14).
- The air conditioning apparatus according to claim 1, characterized in that the high-pressure liquid refrigerant pipe (15) is fitted around the external periphery of the low-pressure refrigerant suction pipe (14) in a coaxial structure, wherein the high-pressure liquid refrigerant pipe (15) is larger in diameter than the low-pressure refrigerant suction pipe (14).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005275493A JP3982545B2 (en) | 2005-09-22 | 2005-09-22 | Air conditioner |
PCT/JP2006/318376 WO2007034745A1 (en) | 2005-09-22 | 2006-09-15 | Air conditioner |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1944562A1 EP1944562A1 (en) | 2008-07-16 |
EP1944562A4 EP1944562A4 (en) | 2011-03-23 |
EP1944562B1 true EP1944562B1 (en) | 2013-04-17 |
Family
ID=37888790
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06798039.1A Not-in-force EP1944562B1 (en) | 2005-09-22 | 2006-09-15 | Air conditioner |
Country Status (7)
Country | Link |
---|---|
US (1) | US20090282861A1 (en) |
EP (1) | EP1944562B1 (en) |
JP (1) | JP3982545B2 (en) |
KR (1) | KR100905995B1 (en) |
CN (1) | CN101268312B (en) |
AU (1) | AU2006293191B2 (en) |
WO (1) | WO2007034745A1 (en) |
Families Citing this family (32)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008304078A (en) * | 2007-06-05 | 2008-12-18 | Denso Corp | Refrigerating cycle device |
US8291719B2 (en) * | 2007-10-09 | 2012-10-23 | Be Aerospace, Inc. | Thermal control system and method |
JP2009115415A (en) * | 2007-11-08 | 2009-05-28 | Calsonic Kansei Corp | Supercritical refrigerating cycle |
JP4947043B2 (en) * | 2008-07-14 | 2012-06-06 | ダイキン工業株式会社 | Outdoor unit for air conditioner and method for manufacturing the same |
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-
2005
- 2005-09-22 JP JP2005275493A patent/JP3982545B2/en not_active Expired - Fee Related
-
2006
- 2006-09-15 CN CN2006800342799A patent/CN101268312B/en not_active Expired - Fee Related
- 2006-09-15 US US12/067,087 patent/US20090282861A1/en not_active Abandoned
- 2006-09-15 AU AU2006293191A patent/AU2006293191B2/en not_active Ceased
- 2006-09-15 EP EP06798039.1A patent/EP1944562B1/en not_active Not-in-force
- 2006-09-15 WO PCT/JP2006/318376 patent/WO2007034745A1/en active Application Filing
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2008
- 2008-04-04 KR KR1020087008289A patent/KR100905995B1/en not_active IP Right Cessation
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JP2007085647A (en) | 2007-04-05 |
KR20080042178A (en) | 2008-05-14 |
AU2006293191A1 (en) | 2007-03-29 |
KR100905995B1 (en) | 2009-07-06 |
JP3982545B2 (en) | 2007-09-26 |
US20090282861A1 (en) | 2009-11-19 |
EP1944562A1 (en) | 2008-07-16 |
EP1944562A4 (en) | 2011-03-23 |
CN101268312B (en) | 2010-05-19 |
CN101268312A (en) | 2008-09-17 |
WO2007034745A1 (en) | 2007-03-29 |
AU2006293191B2 (en) | 2009-11-19 |
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