WO2010038403A1 - Dispositif de climatisation - Google Patents

Dispositif de climatisation Download PDF

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Publication number
WO2010038403A1
WO2010038403A1 PCT/JP2009/004910 JP2009004910W WO2010038403A1 WO 2010038403 A1 WO2010038403 A1 WO 2010038403A1 JP 2009004910 W JP2009004910 W JP 2009004910W WO 2010038403 A1 WO2010038403 A1 WO 2010038403A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
tube
refrigerant
air conditioner
carbon dioxide
Prior art date
Application number
PCT/JP2009/004910
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English (en)
Japanese (ja)
Inventor
吉岡俊
織谷好男
金鉉永
笠井一成
Original Assignee
ダイキン工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ダイキン工業株式会社 filed Critical ダイキン工業株式会社
Publication of WO2010038403A1 publication Critical patent/WO2010038403A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
    • F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements

Definitions

  • the present invention relates to an air conditioner including a refrigerant circuit that performs a supercritical refrigeration cycle by circulating carbon dioxide.
  • an air conditioner including a refrigerant circuit for performing a vapor compression refrigeration cycle is known.
  • an internally grooved tube is used in the heat source side heat exchanger and the use side heat exchanger of the refrigerant circuit.
  • the inner grooved tube of Patent Document 1 is used in an air conditioner, and a large number of continuous spiral grooves are formed on the inner peripheral surface thereof. It is said that the refrigerant flowing in the pipe is well stirred by this spiral groove, and high heat transfer performance can be obtained.
  • one of the causes that the cooling capacity of the air conditioner is significantly lower than the conventional one is that a refrigerating machine oil (for example, PAG (polyalkylene) sealed in a refrigerant circuit in order to lubricate each sliding portion of the compressor. Glycol))).
  • a refrigerating machine oil for example, PAG (polyalkylene) sealed in a refrigerant circuit in order to lubricate each sliding portion of the compressor. Glycol
  • the refrigerating machine oil that could not be returned from the discharge side of the compressor to the suction side by the oil return circuit provided in the refrigerant circuit is combined with the carbon dioxide. Flows to the side heat exchanger.
  • the above refrigerating machine oil shows good lubricity with respect to each sliding portion of the compressor, the compatibility with carbon dioxide is low. From this, among the carbon dioxide and the refrigeration oil that flowed to the heat source side heat exchanger, the refrigeration oil that could not be dissolved in the carbon dioxide seems to travel along the inner peripheral surface of the inner grooved tube in the heat source side heat exchanger. Flowing into. As a result, the refrigerating machine oil is likely to be captured by a large number of grooves formed on the inner peripheral surface of the inner grooved tube, and the oil film formed on the inner peripheral surface is likely to be thick. When this oil film becomes thick, the thermal resistance between the carbon dioxide and the inner peripheral surface of the inner grooved tube increases, and it becomes difficult for the carbon dioxide to dissipate heat.
  • the present invention has been made in view of such a point, and in an air conditioner using carbon dioxide as a refrigerant, the cooling capacity is significantly lower than that of a conventional air conditioner using an HFC refrigerant as a refrigerant. There is to suppress.
  • the compression mechanism (11), the heat source side heat exchanger (15), the expansion mechanism (14), and the use side heat exchanger (13) having refrigerating machine oil are sequentially arranged. It is premised on an air conditioner that includes a refrigerant circuit (10) that is connected to perform a supercritical refrigeration cycle and that performs at least a cooling operation.
  • a smooth tube (1) is used for the heat source side heat exchanger (15) of the air conditioner, and an inner grooved tube (6) is used for the use side heat exchanger (13). It is characterized by.
  • the usage side heat exchanger (13) is used instead of using the inner grooved pipe (6) for both the heat source side heat exchanger (15) and the usage side heat exchanger (13).
  • the usage side heat exchanger (13) is used only the inner grooved tube (6) is used, and the heat source side heat exchanger (15) uses a smooth tube (1) instead of the inner grooved tube (6).
  • the refrigerating machine oil is less likely to be captured than when the inner grooved tube (6) is used.
  • the refrigerating machine oil flows smoothly in the pipe. Since the refrigeration oil flows smoothly through the pipe of the smooth pipe (1), the oil film in the pipe can be made thinner than when the inner grooved pipe (6) is used for the heat source side heat exchanger (15). . As the oil film becomes thinner, the thermal resistance between the carbon dioxide and the inner peripheral surface of the smooth tube (1) becomes smaller, and the carbon dioxide tends to dissipate heat. Thereby, the thermal radiation amount of the said heat source side heat exchanger (15) can be increased.
  • the ratio of the mass flow rate of the refrigerating machine oil to the total mass flow rate of the carbon dioxide and the refrigerating machine oil of the carbon dioxide and the refrigerating machine oil flowing through the smooth pipe (1) is 0.3. It is characterized by being at least mass%.
  • the mass of the refrigerating machine oil relative to the total mass flow rate of the carbon dioxide plus the refrigerating machine oil is regulated to 0.3% by mass or more.
  • FIG. 3 is a graph comparing the effect of the amount of oil circulation of the refrigerating machine oil on the evaporative heat exchange capacity ratio between the smooth tube (1) and the internally grooved tube (6).
  • FIG. 4 is a graph comparing the effect of the amount of oil circulation of the refrigerating machine oil on the heat dissipation capacity ratio between the smooth tube (1) and the internally grooved tube (6).
  • 3 and 4 both show the capacity ratio based on the heat exchange capacity of the internally grooved pipe (6) when the oil circulation amount of the refrigerating machine oil is zero, that is, when only carbon dioxide is flowing. .
  • ⁇ marks are measured values of the smooth tube, and ⁇ marks indicate measured values of the internally grooved tube.
  • the inner grooved tube (6) always has a larger evaporative heat exchange capacity ratio than the smooth tube (1), regardless of the amount of refrigeration oil circulating.
  • the heat source side heat exchanger (15) using the smooth tube (1) when the oil circulation amount of the refrigerating machine oil is regulated to 0.3% by mass or more, the heat source using the inner grooved tube (6) Compared with the side heat exchanger (15), the heat radiation heat exchange capability of the heat source side heat exchanger (15) during the cooling operation can be effectively increased.
  • the refrigerant circuit (10) is provided with a switching valve (12) for reversing the circulation direction of carbon dioxide flowing through the refrigerant circuit (10). It is characterized by having.
  • an air conditioner capable of air conditioning operation can be configured by providing the switching valve (12) in the refrigerant circuit (10). And about the air conditioner which can perform such an air conditioning operation, even if it uses a smooth pipe (1) for the said heat source side heat exchanger (15), like this invention, this heat source side heat exchanger ( 15) Compared with the use of an internally grooved tube (6), the oil film in the heat transfer tube can be made thinner, and the deterioration of the heat transfer performance of the heat source side heat exchanger (15) can be suppressed. it can.
  • a smooth tube (1) is used for the heat source side heat exchanger (15), and an internally grooved tube is used for the use side heat exchanger (13). (6) is used.
  • the oil film in the smooth tube (1) in the heat source side heat exchanger (15) can be made thinner than in the case where there is a groove on the inner peripheral surface. Thereby, it becomes easy to radiate carbon dioxide, and the heat radiation amount of the heat source side heat exchanger (15) can be increased.
  • the use of the smooth tube (1) for the heat source side heat exchanger (15) significantly increases the conventional air conditioner using the HFC refrigerant as the refrigerant. It can suppress that the cooling capacity falls.
  • the heat source side heat exchanger (15) using the smooth tube (1) when the amount of oil circulation is specified to be 0.3% by mass or more, an internally grooved tube ( Compared with the heat source side heat exchanger (15) using 6), the heat radiation heat exchange capacity of the heat source side heat exchanger (15) during cooling operation can be effectively increased.
  • an air conditioner using carbon dioxide as a refrigerant it is possible to effectively suppress the cooling capacity from being significantly reduced as compared with an air conditioner using an HFC refrigerant as a refrigerant.
  • an air conditioner capable of air-conditioning operation can be configured by providing a switching valve (12) in the refrigerant circuit (10). And also in the air conditioning apparatus in which this air conditioning operation is possible, the effect similar to the 1st and 2nd invention can be acquired at the time of air_conditionaing
  • FIG. 1 is a refrigerant circuit diagram of an air conditioner according to an embodiment of the present invention.
  • FIG. 2 is a schematic view of a heat exchanger of the air-conditioning apparatus according to the embodiment of the present invention.
  • FIG. 3 is a graph showing the influence of the oil circulation amount on the evaporative heat exchange capacity ratio.
  • FIG. 4 is a graph showing the effect of the amount of oil circulation on the ratio of heat radiation heat exchange capacity.
  • FIG. 5 is a cross-sectional view of an internally grooved tube according to an embodiment of the present invention. 6 is an enlarged view of a portion A in FIG.
  • FIG. 7 is a longitudinal sectional view of the internally grooved tube according to the embodiment of the present invention.
  • FIG. 1 shows a refrigerant circuit diagram of the air conditioner of this embodiment.
  • the air conditioner performs indoor air conditioning, and includes an outdoor unit (3) disposed outdoors and the indoor unit (2) disposed indoors.
  • the outdoor unit (3) is provided with an outdoor circuit (8).
  • the indoor unit (2) is provided with an indoor circuit (7).
  • This connecting pipe (4,5) consists of a gas side connecting pipe (4) and a liquid side connecting pipe (5).
  • the gas side connecting pipe (4) is the gas end of both circuits (7,8).
  • the liquid side connecting pipe (5) connects the liquid ends of both the circuits (7, 8).
  • the refrigerant circuit (10) is configured to perform a supercritical refrigeration cycle by enclosing carbon dioxide (hereinafter referred to as refrigerant) and circulating the refrigerant.
  • the outdoor circuit (8) of the outdoor unit (3) includes a compressor (compression mechanism) (11), a four-way switching valve (switching valve) (12), an expansion valve (expansion mechanism) (14), and an outdoor heat exchanger. (Heat source side heat exchanger) (15).
  • the compressor (11) is composed of, for example, a scroll type compressor.
  • An inverter (not shown) is connected to the compressor (11).
  • the inverter is configured to supply a current to the compressor (11) and to change the frequency of the current. That is, the capacity of the compressor (11) can be freely changed within a certain range by the inverter.
  • the compressor (11) accommodates polyalkylene glycol (PAG) (hereinafter referred to as refrigeration oil) for lubricating the sliding portion of the compressor (11).
  • PAG polyalkylene glycol
  • the four-way switching valve (12) has four ports (12a, 12b, 12c, 12d) from the first to the fourth.
  • a pipe extending from the first port (12a) is connected to the discharge side of the compressor (11).
  • a pipe extending from the second port (12b) is connected to the suction side of the compressor (11).
  • the pipe extending from the third port (12c) is connected to the gas end of the outdoor circuit (8).
  • a pipe extending from the fourth port (12d) is connected to one end of the outdoor heat exchanger (15).
  • the four-way selector valve (12) is in a first state in which the first port (12a) and the fourth port (12d) communicate with each other and the second port (12b) and the third port (12c) communicate with each other. (A state shown by a solid line in FIG. 1) and a second state in which the first port (12a) and the third port (12c) communicate with each other and the second port (12b) and the fourth port (12d) communicate with each other ( The state can be switched to the state shown by the broken line in FIG.
  • the expansion valve (14) is an electronic expansion valve whose opening degree can be adjusted. One end of the expansion valve (14) is connected to the liquid end of the outdoor circuit (8), and the other end is connected to the other end of the outdoor heat exchanger (15).
  • the outdoor heat exchanger (15) is a cross fin type fin-and-tube heat exchanger.
  • FIG. 2 shows a part of the outdoor heat exchanger (15).
  • the outdoor heat exchanger (15) includes a heat transfer fin group (22) including a plurality of heat transfer fins (21), a plurality of heat transfer tubes (1), and a U-shaped tube (23). And a heat transfer tube group (28).
  • Each heat transfer fin (21) is formed in a rectangular flat plate shape.
  • Each heat transfer tube (1) passes through each heat transfer fin (21), and ends of the heat transfer tubes (1) are connected to each other by a U-shaped tube (23). Thereby, one refrigerant flow path is formed from the inlet side end (27) to the outlet side end (28).
  • the outdoor heat exchanger (15) is a so-called multi-pass heat exchanger having a plurality of refrigerant flow paths as a whole. A plurality of refrigerant inlet side ends (27) and outlet side ends (28) are provided.
  • an outdoor fan (not shown) is provided in the vicinity of the outdoor heat exchanger (15). Then, the refrigerant flows through the refrigerant flow paths, and the air from the outdoor fan flows between the heat transfer fins (21) so as to be orthogonal to the flow of the refrigerant, whereby heat exchange between the refrigerant and the air is performed. Done.
  • a smooth tube (1) is used as the heat transfer tube (1) of the outdoor heat exchanger (15).
  • the smooth tube (1) has an outer diameter of 7.0 mm and a wall thickness of 0.9 mm.
  • the indoor circuit (7) of the indoor unit (2) has an indoor heat exchanger (use side heat exchanger) (13). One end of the indoor heat exchanger (13) is connected to the gas end of the indoor circuit (7), and the other end is connected to the liquid end of the indoor circuit (7).
  • the indoor heat exchanger (13) is composed of a cross-fin type fin-and-tube heat exchanger, like the outdoor heat exchanger (15) described above.
  • an internally grooved tube (6) having an outer diameter of 7.0 mm and a bottom wall thickness of 0.6 mm is used for the heat transfer tube of the indoor heat exchanger (13). Since the other configuration is the same as that of the outdoor heat exchanger (15), description thereof is omitted.
  • a plurality of grooves (16) and adjacent fins (17) are provided between the grooves (16) on the inner peripheral surface of the inner grooved tube (6).
  • the groove (16) and the fin (17) are formed in an inverted trapezoidal cross section, and the fin (17) is formed in a tapered mountain shape.
  • the number (strip number) of the grooves (16) is 60.
  • a bottom flat portion (16a) is formed at the bottom of the groove (16), and bottom corners (16b) are formed at both ends of the bottom flat portion (16a).
  • the tip (17a) of the fin (17) is formed in an arc shape, and linear inclined portions (17b) continuous to the tip (17a) are formed on both sides thereof.
  • the bottom corner (16b) and the inclined portion (17b) are continuous such that the fin (17) is disposed adjacent to the groove (16) and the groove (16).
  • the angle (fin apex angle) formed by the inclined portion (17b) and the inclined portion (17b) on both sides of the fin (17) is 60 degrees.
  • the bottom width ⁇ between the groove (16) and the groove (16) is indicated by the distance connecting the intersection of the extended line of the inclined part (17b) and the extended line of the bottom flat part (16a).
  • the fin height h is a length between the bottom flat portion (16a) and the taper of the fin (17), and this length is 0.15 mm.
  • the extending direction of the grooves (16) and the fins (17) has a predetermined angle with respect to the tube axis direction. This angle is 12 deg.
  • the air conditioner can perform indoor air conditioning by reversing the circulation direction of the refrigerant flowing through the refrigerant circuit (10) by the switching operation of the four-way switching valve (12). .
  • the four-way selector valve (12) is set to the first state as described above. In this state, the refrigerant compressed to the critical pressure or higher by the compressor (11) is discharged from the compressor (11).
  • the compressor (11) discharges refrigeration oil used for lubricating each sliding portion of the compressor (11) together with the supercritical pressure refrigerant.
  • the discharged refrigerant and refrigerating machine oil flow into the outdoor heat exchanger (15) after passing through the four-way switching valve (12).
  • the refrigerant that has flowed into the outdoor heat exchanger (15) passes through the smooth tube (1), which is a heat transfer tube, while radiating heat to the air blown from the outdoor fan. During this passage, the refrigerant and the blown air exchange heat through the smooth tube (1).
  • the refrigerating machine oil that has flown into the smooth pipe (1) is separated from the refrigerant and smoothed. It flows along the inner peripheral surface of the pipe (1).
  • the heat transfer tube of the outdoor heat exchanger (15) is composed of an internally grooved tube (6)
  • the refrigerating machine oil is easily captured in the spiral groove formed on the inner surface of the internally grooved tube (6). Become.
  • the oil film formed on the inner side of the pipe becomes thick, and the heat transfer performance of the outdoor heat exchanger (15) is reduced.
  • the smooth tube (1) is used as the heat transfer tube of the outdoor heat exchanger (15), the refrigerating machine oil is not captured unlike the internally grooved tube (6). Flows smoothly. As a result, compared to the inner grooved tube (6), the oil film in the heat transfer tube can be made thinner, and the deterioration of the heat transfer performance of the outdoor heat exchanger (15) can be suppressed. In addition, the oil circulation amount of this refrigerating machine oil is set to 0.3 mass% or more.
  • the refrigerant that has flowed out of the outdoor heat exchanger (15) flows into the expansion valve (14) while radiating heat to the blown air from the outdoor fan in the outdoor heat exchanger (15).
  • the refrigerant flowing into the expansion valve (14) is depressurized to a predetermined pressure and becomes a low-pressure refrigerant.
  • the low-pressure refrigerant flows into the indoor heat exchanger (13), evaporates by absorbing heat from indoor air sent from an indoor fan (not shown). As a result, the room air is cooled.
  • the indoor heat exchanger (13) uses the internally grooved tube (6) as described above. As shown in FIG. 3, the heat exchange amount of the indoor heat exchanger (13) is as follows. Larger than when using a smooth tube (1).
  • the refrigerant evaporated in the indoor heat exchanger (13) is sucked into the compressor (11) and compressed to a critical pressure or higher. Then, the supercritical pressure refrigerant is discharged again. In this way, the refrigerant circulates through the refrigerant circuit (10), thereby cooling the room.
  • the smooth tube (1) is used for the outdoor heat exchanger (15), and the internally grooved tube (6) is used for the indoor heat exchanger (13).
  • the oil film in the smooth tube (1) in the outdoor heat exchanger (15) can be made thinner than in the case where there is a groove on the inner peripheral surface. Thereby, it becomes easy to radiate carbon dioxide, and the heat radiation amount of the outdoor heat exchanger (15) can be increased.
  • the use of the smooth tube (1) for the outdoor heat exchanger (15) significantly cools the air conditioner compared to the conventional air conditioner using the HFC refrigerant as the refrigerant. It is possible to suppress a decrease in ability.
  • the amount of oil circulation is regulated to 0.3% by mass or more.
  • FIG. 3 shows the effect of the amount of circulating oil in the refrigerating machine oil on the evaporative heat exchange capacity ratio in the smooth pipe (1) used in the outdoor heat exchanger (15) and the indoor heat exchanger (13). It is the graph compared with the inner surface grooved pipe (6).
  • FIG. 4 is a graph comparing the influence of the amount of oil circulation of the refrigerating machine oil on the heat dissipation capacity ratio between the smooth tube (1) and the inner grooved tube (6).
  • 3 and 4 both show the capacity ratio based on the heat exchange capacity of the internally grooved pipe (6) when the oil circulation amount of the refrigerating machine oil is zero, that is, when only carbon dioxide is flowing. .
  • ⁇ marks are measured values of the smooth tube, and ⁇ marks indicate measured values of the internally grooved tube.
  • the inner grooved tube (6) always has a larger evaporative heat exchange capacity ratio than the smooth tube (1), regardless of the amount of refrigeration oil circulating.
  • the internally grooved pipe (6) has a larger heat dissipation heat exchange capacity ratio than the smooth pipe (1). This is because there is no oil film of refrigerating machine oil and the effect of promoting heat transfer by the spiral groove is sufficiently exhibited.
  • the heat radiating heat exchange capacity ratio of the inner grooved pipe (6) decreases.
  • the air conditioner is configured as an air conditioner capable of cooling and heating operation, but may be an air conditioner dedicated to cooling, and is not limited to an air conditioner, and is applied to various air conditioners such as a refrigerator. can do.
  • the present invention is useful for an air conditioner including a refrigerant circuit that performs a supercritical refrigeration cycle by circulating carbon dioxide.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

L'invention porte sur un tuyau lisse (1) utilisé pour un échangeur de chaleur extérieur (15) d'un dispositif de climatisation, et sur un tuyau (6) avec une surface interne rainurée utilisé pour un échangeur de chaleur intérieur (13) du dispositif de climatisation.
PCT/JP2009/004910 2008-09-30 2009-09-28 Dispositif de climatisation WO2010038403A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008-255057 2008-09-30
JP2008255057A JP4813534B2 (ja) 2008-09-30 2008-09-30 空気調和装置

Publications (1)

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WO2010038403A1 true WO2010038403A1 (fr) 2010-04-08

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105605821A (zh) * 2016-01-25 2016-05-25 铁道第三勘察设计院集团有限公司 一种二氧化碳直膨空调装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017044431A (ja) * 2015-08-28 2017-03-02 日立アプライアンス株式会社 ヒートポンプ式給湯機

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0336496A (ja) * 1989-06-30 1991-02-18 Toshiba Corp ヒートポンプ式空気調和機用熱交換器の冷媒管
JP2006064311A (ja) * 2004-08-27 2006-03-09 Kobelco & Materials Copper Tube Inc 蒸発器用内面溝付伝熱管
JP2007322069A (ja) * 2006-06-01 2007-12-13 Hitachi Cable Ltd ヒートポンプ式熱交換機器の冷媒用伝熱管およびそれを用いたガスクーラ

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3811116B2 (ja) * 2001-10-19 2006-08-16 松下電器産業株式会社 冷凍サイクル装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0336496A (ja) * 1989-06-30 1991-02-18 Toshiba Corp ヒートポンプ式空気調和機用熱交換器の冷媒管
JP2006064311A (ja) * 2004-08-27 2006-03-09 Kobelco & Materials Copper Tube Inc 蒸発器用内面溝付伝熱管
JP2007322069A (ja) * 2006-06-01 2007-12-13 Hitachi Cable Ltd ヒートポンプ式熱交換機器の冷媒用伝熱管およびそれを用いたガスクーラ

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105605821A (zh) * 2016-01-25 2016-05-25 铁道第三勘察设计院集团有限公司 一种二氧化碳直膨空调装置

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JP4813534B2 (ja) 2011-11-09

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