EP1031801A2 - Wärmetauscher - Google Patents

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Publication number
EP1031801A2
EP1031801A2 EP00103971A EP00103971A EP1031801A2 EP 1031801 A2 EP1031801 A2 EP 1031801A2 EP 00103971 A EP00103971 A EP 00103971A EP 00103971 A EP00103971 A EP 00103971A EP 1031801 A2 EP1031801 A2 EP 1031801A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
pass
tube
side row
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.)
Withdrawn
Application number
EP00103971A
Other languages
English (en)
French (fr)
Other versions
EP1031801A3 (de
Inventor
Yasushi Watanabe
Toru Yasuda
Ming Leu
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Matsushita Electric Industrial Co Ltd
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 Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Publication of EP1031801A2 publication Critical patent/EP1031801A2/de
Publication of EP1031801A3 publication Critical patent/EP1031801A3/de
Withdrawn legal-status Critical Current

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    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component

Definitions

  • the present invention relates to a heat exchanger for use in an air conditioner.
  • a general cross-fin tube type heat exchanger is, as shown in FIG. 9, constructed of a fin group 1 comprising a plurality of flat plate-shaped fins arranged at predetermined intervals in parallel with each other, and heat exchanger tubes 2 (2i, 2j, 2k) inserted substantially orthogonally to this fin group 1, that is, along a stacking direction of the fins. Also, the heat exchanger tubes 2 in this type of heat exchangers are arranged in a plurality of rows (two rows in FIG. 9) in an air current direction (lateral direction in FIG. 9) for passing air.
  • a heat exchanger of this type is constructed by piping 2-pass heat exchanger tubes 2i and 2j in parallel on a refrigerant inlet-side of the heat exchanger where there are contained gas and a high proportion of gaseous phase component, and by piping an 1-pass heat exchanger tube 2k in a piping portion, where there will be contained liquid and a high proportion of liquid phase component.
  • Refrigerant within the piping of each pass described above flows in a predetermined direction (downward from above in FIG.
  • a reference numeral 3c designates a coupling member for causing the 2-pass heat exchanger tubes 2i and 2j and the 1-pass heat exchanger tube 2k to communicate to each other.
  • an arrow in FIG. 9 indicates a refrigerant flowing direction when the condenser is operating.
  • FIG. 10 schematically shows relationship between temperatures of refrigerant flowing through a heat exchanger shown in FIG. 9, air temperatures at an inlet and an outlet of the heat exchanger, and a state of the refrigerant within the heat exchanger.
  • this heat exchanger of the 2-pass rectangular flow to 1-pass rectangular flow system is used as a condenser, heat exchange is performed between superheated gas and air on the inlet side, and the refrigerant temperature changes from a superheating temperature T1 to a saturation temperature T2. At this saturation temperature T2, heat exchange is performed and the refrigerant which was gaseous condenses into liquid. Further, when the refrigerant has an increased proportion of liquid component and its liquid content reaches 100%, the temperature decreases from the temperature T2 to a temperature T3.
  • c air specific heat
  • Q an air flow rate
  • ⁇ Tm an average temperature difference between an air outlet and an air inlet in the heat exchanger.
  • the present invention has been achieved to solve the above-described problems, and is aimed to provide a heat exchanger capable of improving heat exchange efficiency.
  • a heat exchanger in which a plurality of flat plate-shaped fins are stacked at predetermined intervals, heat exchanger tubes for passing refrigerant therethrough are inserted along a stacking direction, air is caused to pass through between each fin group, and the heat exchanger tubes are disposed in a plurality of rows in an air passage direction, wherein the heat exchanger tube is partitioned into a portion for containing gas and a high proportion of gaseous phase of a gas-liquid two-layer flow of the refrigerant flowing in the tube, and a portion for containing liquid and a high proportion of liquid phase of the gas-liquid two-layer flow of the refrigerant, wherein there are disposed first heat exchanger tubes of a 2-pass structure as the former portion, and a second heat exchanger tube of a 1-pass structure as the latter portion, wherein these first and second heat exchanger tubes are communicated to each other through a coupling member, wherein each pass of these first and second heat exchanger tubes has, when
  • the portion containing gas and a high proportion of gaseous phase of the gas-liquid two-layer flow of the refrigerant is comprised of a counterflow type first heat exchanger tube of the 2-pass structure, and the portion containing a high proportion of liquid and liquid phase of a gas-liquid two-layer flow, is comprised of a counterflow type second heat exchanger tube of the 1-pass structure.
  • the counterflow here means that when the heat exchanger is used as a condenser, the refrigerant containing a high proportion of gas first goes through the heat exchanger tube in the leeward-side row, and next goes through the heat exchanger tube in the windward-side row which substantially overlap with the heat exchanger tube in the leeward-side row in the air current direction, and that when the heat exchanger is used as an evaporator, the refrigerant first goes through the heat exchanger tube in the windward-side row, and next goes through the heat exchanger tube in the leeward-side row.
  • this refrigeran8 ⁇ t containing a high proportion of liquid phase component flows through the leeward-side row in the second heat exchanger tube of the 1-pass structure, the refrigerant which has further decreased in temperature due to heat exchange with air, flows through the windward-side row in the second heat exchanger tube to exchange heat with air, so that the refrigerant is further cooled.
  • the refrigerant temperature within the first and second heat exchanger tubes in the leeward-side row is higher substantially in the whole area than the refrigerant temperature within the respectively corresponding first and second heat exchanger tubes in the windward-side row, and therefore, a temperature difference between the refrigerant and air can be taken large, and the heat exchange efficiency can be enhanced.
  • the heat exchanger when used as an evaporator, the above-described refrigerant flow is reversed, and in a similar manner, the refrigerant temperature within the first and second heat exchanger tubes in the leeward-side row is higher substantially in the whole area than the refrigerant temperature within the respectively corresponding first and second heat exchanger tubes in the windward-side row, and therefore, a temperature difference between the refrigerant and air can be taken large, and the heat exchange efficiency can be enhanced.
  • the outlet portion of the second heat exchanger tube, at which the liquid refrigerant is at the lowest temperature, can be arranged at the lower end of the heat exchanger, and therefore, the windward and leeward second heat exchanger tube can be of a more complete counterflow type, the condensation performance can be further enhanced, and liquid seal can be prevented in an inverter type air conditioner.
  • a heat exchanger defined in claim 1 or 2, wherein the coupling member is a Y-branch type (Y-shaped branch type) flow divider.
  • the heat exchanger when the heat exchanger is used as a heat source-side heat exchanger in a heat pump type air conditioner, the first heat exchanger tube at a higher temperature than the second heat exchanger tube is located below the heat exchanger, and therefore, if this heat exchanger is positioned in the vicinity of the substrate of an outdoor unit, it becomes possible to improve the defrosting performance during the heating and defrosting operation, and to prevent the substrate of the outdoor unit from being frozen.
  • FIG. 1 is a perspective view of the essential portion showing a first embodiment in which a heat exchanger according to the present invention has been applied to a condenser
  • FIG. 2 is a side view (an arrow indicating a refrigerant flowing direction shows when the condenser is operating) showing this heat exchanger.
  • FIGS. 1 and 2 Even in this heat exchanger, as shown in FIGS. 1 and 2, a plurality of flat plate-shaped fins 1a are stacked at predetermined intervals, a heat exchanger tube 2 for a refrigerant is inserted substantially orthogonally to this fin group 1, that is, along a stacking direction of the fins so as to cause air to pass through between each fin group 1.
  • the heat exchanger tube 2 is partitioned into a portion for containing gas and a high proportion of gaseous phase of a gas-liquid two-layer flow of the refrigerant flowing in the tube, and a portion for containing liquid and a high proportion of liquid phase of the gas-liquid two-layer flow of the refrigerant, wherein there are disposed first heat exchanger tubes 2a and 2b of a 2-pass structure as the former portion, and a second heat exchanger tube 2c of a 1-pass structure as the latter portion, and wherein these first heat exchanger tubes 2a and 2b and a second heat exchanger tube 2c are communicated to each other through a coupling member 3.
  • each pass of the first heat exchanger tubes 2a and 2b and the second heat exchanger tube 2c has, when the heat exchanger is operated as a condenser, an inlet in a leeward-side row, and an outlet in a windward-side row, and at least part of the passes are of a counterflow type, being overlapped between a plurality of rows in the air passage direction.
  • FIG. 3 is a view schematically showing temperature changes of the refrigerant between the inlet and the outlet, air temperatures in heat exchange and a state of refrigerant within the heat exchanger when the heat exchanger is used as a condenser.
  • the above-described embodiment is a case where the heat exchanger is used as a condenser, and in the case of an evaporator, the action can be applied in quite the same manner although the flow of refrigerant is reversed. More specifically, in the case of the evaporator, a refrigerant containing liquid and a high proportion of liquid phase component, adiabatically expanded by a throttle, first flows in the second heat exchanger tube 2c of the 1-pass structure, and a refrigerant containing gas and a high proportion of gaseous phase component flows into the first heat exchanger tubes 2a and 2b of the 2-pass structure through the coupling member 3 while heat exchange.
  • each pass for the first heat exchanger tubes 2a and 2b and the second heat exchanger tube 2c has, when the heat exchanger is operated as an evaporator, the inlet in the windward-side row and the outlet in the leeward-side row, and at least part of the passes are made to be a counterflow type, being overlapped between a plurality of rows in the air passage direction. Therefore, the temperature difference between the refrigerant and air can be taken large, and the heat exchange efficiency can be improved.
  • FIG. 4 is a side view (an arrow indicating a refrigerant flowing direction shows when a condenser is operating) showing the second embodiment in which a heat exchanger according to the present invention is applied to the condenser.
  • a different point from the first embodiment is that the outlet of the windward-side row in the pass of the second heat exchanger tube 2c is constructed to be located at the lowest end of the windward-side row.
  • a wind velocity is low.
  • An outlet portion 2f of the windward-side heat exchanger tube in the second heat exchanger tube 2c which is a feature of a heat exchanger according to the second embodiment, becomes, when the heat exchanger is operated as a condenser, the lowest in temperature, and therefore, by locating the outlet portion 2f at the lowest end, the heat exchanger ability of the second heat exchanger tube 2c constructed to be a 1-pass counterflow type becomes larger than that of the first embodiment, and it can be seen that the heat exchanger performance can be improved.
  • the second heat exchanger tube 2c does not have such a concave type pass structure as the heat exchanger has in the first embodiment, but since the pass in the vicinity of the outlet portion 2f does not rise upward from below, it is possible to prevent liquid seal which occurs particularly in an inverter type air conditioner at a low speed, that is, when the refrigerant flow rate is slow.
  • FIG. 5 is a side view (an arrow indicating a refrigerant flowing direction shows when an evaporator is operating) showing the third embodiment in which the heat exchanger according to the present invention is applied to the evaporator.
  • a different point from the heat exchanger according to the above-described second embodiment is that as a coupling member 3 for coupling the first and second heat exchanger tubes 2a, 2b and 2c, a Y-branch type flow divider 3a is used as a coupling member 3 for coupling the first and second heat exchanger tubes 2a, 2b and 2c.
  • the Y-branch type flow divider 3a is employed as the coupling member 3 and is provided horizontally or vertically, whereby it becomes possible to substantially uniformly distribute refrigerants 5a and 5b which flow into the first heat exchanger tubes 2a and 2b respectively, so that the evaporator performance can be improved by a large amount. Further, since the Y-branch type flow divider 3a having multipurpose properties is used, it is possible to reduce the cost as compared with the case where any component having no multipurpose properties is used.
  • FIG. 6 is a side view (an arrow indicating a refrigerant flowing direction shows when a condenser is operating) showing the fourth embodiment in which the heat exchanger according to the present invention is applied to the condenser.
  • a different point from the above-described third embodiment is that one heat exchanger tube 2b in the first heat exchanger tubes 2a and 2b of the 2-pass structure is arranged below the other first heat exchanger tube 2a and the second heat exchanger tube 2c.
  • FIG. 7 shows a general refrigerating cycle for a heat pump type air conditioner, and this refrigerating cycle is constructed by piping and connecting, in an annular shape, a compressor 11, a four-way type valve 12, an application-side heat exchanger 13, a heat source-side heat exchanger (outdoor unit) 14, and a throttle 15, respectively.
  • the heat exchanger 14 operates as a condenser during a cooling operation, and as an evaporator during a heating operation.
  • the heat source-side heat exchanger 14 When heating at a low temperature (for example, outdoor temperature of 2°C/wet-bulb temperature of 1°C), the heat source-side heat exchanger 14 operates as the evaporator, and therefore, frost forms on the fins, and when a continuous operation is performed, defrosting becomes necessary to recover the heating ability. During defrosting, the operation is made in the refrigerating cycle, and the heat source-side heat exchanger 14 operates as the condenser, and the frost is caused to break to flow down from the upper portion of the heat exchanger 14 to the lower portion.
  • a low temperature for example, outdoor temperature of 2°C/wet-bulb temperature of 1°C
  • the lower portion of the heat exchanger has the heat exchanger tube corresponding to the outlet portion of the condenser, which is the lowest in temperature, and therefore, water which has collected on a substrate provided in the outdoor unit, grows into ice, possibly resulting in deterioration of the heating ability or causing growth of ice formed on the substrate by continuous operation.
  • one first heat exchanger tube 2b of the 2-pass structure is arranged below the other first heat exchanger tube 2a and the second heat exchanger tube 2c as shown in FIG. 6, whereby refrigerant at comparatively high temperature, which flows through the first heat exchanger tube 2b, can be located in a position nearest to the substrate 6 of the heat source-side heat exchanger (outdoor unit) 14 during the defrosting operation. Therefore, the temperature at the substrate 6 can be increased as compared with the heat exchanger according to the third embodiment, and it is possible to prevent ice from being formed and growing on the substrate 5 after the defrosting operation.
  • first heat exchanger tubes 2a and 2b and the second heat exchanger tube 2c maintain to be in the 2-pass counterflow to 1-pass counterflow form, respectively, it is possible to secure the performance equivalent to the heat exchanger efficiencies obtained in the first to third embodiments.
  • FIG. 8 is a side view (an arrow indicating a refrigerant flowing direction shows when a condenser is operating) showing the fifth embodiment in which a heat exchanger according to the present invention is applied to the condenser.
  • a different point from the above-described fourth embodiment is that an inlet heat exchanger tube portion 2h of the first heat exchanger tube 2b located in the lower portion of the second heat exchanger tube 2c is caused to be located between the lower stage of the heat exchanger and the second tube, and be positioned in the vicinity of the substrate 6 of the outdoor unit in which the heat source-side heat exchanger 14 is disposed.
  • an inlet heat exchanger tube portion 2h leading to the condenser which is at the highest temperature, can be disposed in a position nearest to the substrate 6 of the outdoor unit during a defrosting operation, and therefore, the temperature at the substrate x6 can be further increased as compared with the heat exchanger according to the fourth embodiment, and it becomes possible to prevent ice formed on the substrate 6 from growing after the defrosting operation.
  • This structure is particularly useful for a heat pump type air conditioner using a constant-speed compressor having low defrosting performance. Further, since the first heat exchanger tubes 2a and 2b and the second heat exchanger tube 2c maintain the 2-pass counterflow to 1-pass counterflow form, respectively, it is possible to secure the performance equivalent to the heat exchanger efficiencies obtained in the first to fourth embodiments.
  • HCFC-22 which is one type of flon
  • HFC-32 which is one of flon substitutes
  • hydrocarbon refrigerant in place of the HCFC-22.
  • HFC-407C and HFC-410A in the Table 1 are combined refrigerants respectively containing HFC-32 which is one of the flon substitutes, and HC-290 is a hydrocarbon refrigerant. It can be seen that HFC-32 or a part of the combined refrigerant containing HFC-32 (HFC-410A), or the hydrocarbon refrigerant (HC-290) is about 20 to 30% less in pressure loss than HCFC-22 which is one type flon refrigerant.
  • HFC-32 or the combined refrigerant containing HFC-32, or the hydrocarbon refrigerant as described above in the heat exchangers in each embodiment described above it is possible to reduce the pressure loss in the evaporator by a large amount, and it becomes also possible to enhance the heat exchanger efficiencies in both evaporator and condenser as compared with the case where the conventional HCFC-22 is used.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP00103971A 1999-02-26 2000-02-25 Wärmetauscher Withdrawn EP1031801A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP4923399A JP2000249479A (ja) 1999-02-26 1999-02-26 熱交換器
JP4923399 1999-02-26

Publications (2)

Publication Number Publication Date
EP1031801A2 true EP1031801A2 (de) 2000-08-30
EP1031801A3 EP1031801A3 (de) 2001-12-05

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EP00103971A Withdrawn EP1031801A3 (de) 1999-02-26 2000-02-25 Wärmetauscher

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EP (1) EP1031801A3 (de)
JP (1) JP2000249479A (de)
CN (1) CN1265463A (de)

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EP1798490A1 (de) * 2005-08-08 2007-06-20 Mitsubishi Electric Corporation Klimaanlage und verfahren zur herstellung einer klimaanlage
DE102012014825A1 (de) * 2012-07-27 2014-01-30 Schmöle GmbH Flächenwärmetauscherelement
EP2672205A3 (de) * 2012-06-06 2014-03-12 Mitsubishi Heavy Industries, Ltd. Wärmetauschersystem
CN106595131A (zh) * 2016-12-27 2017-04-26 天津商业大学 立式直接接触凝结过冷换热器
CN107003048A (zh) * 2014-12-12 2017-08-01 江森自控日立空调技术（香港）有限公司 空调机
EP3128263A4 (de) * 2014-03-07 2018-01-10 Mitsubishi Electric Corporation Wärmetauscher und klimaanlage
US10422566B2 (en) 2013-06-13 2019-09-24 Mitsubishi Electric Corporation Air-Conditioning apparatus
US10605502B2 (en) 2014-10-07 2020-03-31 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus
US10845099B2 (en) 2016-02-22 2020-11-24 Mitsubishi Electric Corporation Refrigeration cycle apparatus with path switching circuit
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JP4495090B2 (ja) * 2006-02-03 2010-06-30 ダイキン工業株式会社 空気調和装置
JP4922669B2 (ja) * 2006-06-09 2012-04-25 日立アプライアンス株式会社 空気調和機及び空気調和機の熱交換器
JP4814823B2 (ja) * 2007-03-28 2011-11-16 日立アプライアンス株式会社 冷凍装置
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WO2012017681A1 (ja) * 2010-08-05 2012-02-09 三菱電機株式会社 熱交換器及び冷凍空調装置
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JP6180845B2 (ja) * 2013-08-09 2017-08-16 日立アプライアンス株式会社 熱交換器およびそれを用いたヒートポンプ式給湯機
US10082322B2 (en) * 2014-10-07 2018-09-25 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus
CN105928394A (zh) * 2016-05-11 2016-09-07 南京工业大学 一种层叠式翅片管换热器
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Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4344482A (en) * 1979-12-29 1982-08-17 Suddeutsche Kuhlerfabrik Julius Fr. Behr Gmbh & Co. Kg Multiple flow condenser for air conditioning units of motor vehicles
US4831844A (en) * 1988-05-26 1989-05-23 General Motors Corporation Condenser with improved flow path
JPH02290493A (ja) * 1989-04-28 1990-11-30 Toshiba Corp ヒートポンプ式ルームエアコン室内ユニットの熱交換器
US5219023A (en) * 1992-03-09 1993-06-15 General Motors Corporation Three row condenser with high efficiency flow path
US5542271A (en) * 1993-10-18 1996-08-06 Hitachi, Ltd. Air-conditioner employing non-azeotrope refrigerant
US5660056A (en) * 1994-01-17 1997-08-26 Kabushiki Kaisha Toshiba Air conditioner
US5685163A (en) * 1994-09-20 1997-11-11 Hitachi, Ltd. Refrigerating apparatus
US5810074A (en) * 1996-09-13 1998-09-22 American Standard Inc. Serial heat exchanger and cascade circuitry

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4344482A (en) * 1979-12-29 1982-08-17 Suddeutsche Kuhlerfabrik Julius Fr. Behr Gmbh & Co. Kg Multiple flow condenser for air conditioning units of motor vehicles
US4831844A (en) * 1988-05-26 1989-05-23 General Motors Corporation Condenser with improved flow path
JPH02290493A (ja) * 1989-04-28 1990-11-30 Toshiba Corp ヒートポンプ式ルームエアコン室内ユニットの熱交換器
US5219023A (en) * 1992-03-09 1993-06-15 General Motors Corporation Three row condenser with high efficiency flow path
US5542271A (en) * 1993-10-18 1996-08-06 Hitachi, Ltd. Air-conditioner employing non-azeotrope refrigerant
US5660056A (en) * 1994-01-17 1997-08-26 Kabushiki Kaisha Toshiba Air conditioner
US5685163A (en) * 1994-09-20 1997-11-11 Hitachi, Ltd. Refrigerating apparatus
US5810074A (en) * 1996-09-13 1998-09-22 American Standard Inc. Serial heat exchanger and cascade circuitry

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 015, no. 061 (M-1081), 13 February 1991 (1991-02-13) & JP 02 290493 A (TOSHIBA CORP), 30 November 1990 (1990-11-30) *

Cited By (15)

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Publication number Priority date Publication date Assignee Title
EP1798490A4 (de) * 2005-08-08 2008-09-10 Mitsubishi Electric Corp Klimaanlage und verfahren zur herstellung einer klimaanlage
US7703504B2 (en) 2005-08-08 2010-04-27 Mitsubishi Electric Corporation Air conditioner and manufacturing method therefor
EP1798490A1 (de) * 2005-08-08 2007-06-20 Mitsubishi Electric Corporation Klimaanlage und verfahren zur herstellung einer klimaanlage
EP2672205A3 (de) * 2012-06-06 2014-03-12 Mitsubishi Heavy Industries, Ltd. Wärmetauschersystem
DE102012014825A1 (de) * 2012-07-27 2014-01-30 Schmöle GmbH Flächenwärmetauscherelement
US10422566B2 (en) 2013-06-13 2019-09-24 Mitsubishi Electric Corporation Air-Conditioning apparatus
EP3128263A4 (de) * 2014-03-07 2018-01-10 Mitsubishi Electric Corporation Wärmetauscher und klimaanlage
US10605502B2 (en) 2014-10-07 2020-03-31 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus
CN107003048A (zh) * 2014-12-12 2017-08-01 江森自控日立空调技术（香港）有限公司 空调机
CN107003048B (zh) * 2014-12-12 2019-07-16 日立江森自控空调有限公司 空调机
US10386081B2 (en) 2014-12-12 2019-08-20 Hitachi-Johnson Controls Air Conditioning, Inc. Air-conditioning device
EP3232139A4 (de) * 2014-12-12 2018-08-15 Hitachi-Johnson Controls Air Conditioning, Inc. Klimatisierungsvorrichtung
US10845099B2 (en) 2016-02-22 2020-11-24 Mitsubishi Electric Corporation Refrigeration cycle apparatus with path switching circuit
CN106595131A (zh) * 2016-12-27 2017-04-26 天津商业大学 立式直接接触凝结过冷换热器
US11226149B2 (en) 2017-11-29 2022-01-18 Mitsubishi Electric Corporation Air-conditioning apparatus

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JP2000249479A (ja) 2000-09-14
EP1031801A3 (de) 2001-12-05

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