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WO2007063978A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2007063978A1
WO2007063978A1 PCT/JP2006/324055 JP2006324055W WO2007063978A1 WO 2007063978 A1 WO2007063978 A1 WO 2007063978A1 JP 2006324055 W JP2006324055 W JP 2006324055W WO 2007063978 A1 WO2007063978 A1 WO 2007063978A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
heat exchange
heat exchanger
flow direction
header
Prior art date
Application number
PCT/JP2006/324055
Other languages
English (en)
Japanese (ja)
Inventor
Etsuo Shinmura
Koichiro Take
Original Assignee
Showa Denko K.K.
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 Showa Denko K.K. filed Critical Showa Denko K.K.
Priority to DE112006003241T priority Critical patent/DE112006003241T5/de
Publication of WO2007063978A1 publication Critical patent/WO2007063978A1/fr

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Classifications

    • 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
    • F28D1/053—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 straight
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05341—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28D1/053—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 straight
    • F28D1/0535—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 straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • 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
    • F28F1/14—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 longitudinally
    • F28F1/22—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 longitudinally the means having portions engaging further tubular elements
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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 using a non-azeotropic mixed refrigerant containing carbon dioxide and carbon dioxide as a refrigerant, and a related technique.
  • FIG. 18 is a view showing a cross-flow type heat exchanger for a car air conditioner in which the refrigerant flow direction is orthogonal to the air flow direction.
  • a pair of headers (1) (1) along the vertical direction, multiple heat exchange tubes (2) with both ends communicating with both headers (1) (1) are arranged in parallel.
  • fins (3) are arranged between the tubes (2).
  • a refrigerant inlet nozzle (4) is provided at the lower end of the right header (1), and a refrigerant outlet nozzle (5) is provided at the upper end.
  • a partition plate (6) is provided in the header (1) (1), and the heat exchange tube (2) is divided into a plurality of paths. Then, the refrigerant force flowing from the refrigerant inlet nozzle (4) flows in each path in order to meander, and the refrigerant outlet nozzle (5) force flows out.
  • Patent Document 1 JP 2001-99522
  • FIG. 17 shows a Mollier diagram of a refrigeration cycle using a non-azeotropic mixed refrigerant in which the ratio of carbon dioxide and dimethyl ether (DME) is 90:10.
  • DME dimethyl ether
  • the non-azeotropic mixed refrigerant having a temperature gradient in the cooling process or the like is applied to the cross-flow type heat exchanger as shown in Fig. 18 as it is, for example, the core portion on the refrigerant inlet side (heat exchange) In the lower area of the vessel, the refrigerant temperature is lower in the core part (upper area of the heat exchanger) on the refrigerant outlet side where the refrigerant temperature is higher. For this reason, although the temperature of the refrigerant is high and a large temperature difference with the air can be secured in the vicinity of the refrigerant inlet, the temperature differential force with the air becomes small near the refrigerant outlet with a low refrigerant temperature. Since the exchange capacity has been significantly reduced, there is a concern that the heat exchange cannot be performed efficiently over the entire heat exchange area.
  • Preferred embodiments of the present invention have been made in view of the foregoing and Z or other issues in the related art. Preferred embodiments of the present invention are those that can significantly improve existing methods and Z or equipment.
  • the present invention has been made in view of the above circumstances, and provides a heat exchange and related technology capable of efficiently performing heat exchange while using a non-azeotropic mixed refrigerant containing carbon dioxide.
  • the purpose is to provide.
  • the heat exchange is characterized in that the flow direction of the refrigerant flowing through the heat exchange path is opposed to the air flow direction.
  • a heat exchanger characterized in that the flow direction of the refrigerant flowing through the heat exchange tube is opposed to the flow direction of air.
  • An inflow side main header is disposed on the leeward side with respect to the air flow direction, and an outflow side main header is disposed on the leeward side.
  • An end portion of the inflow side subheader is connected in communication with the inflow side main header, an end portion of the outflow side subheader is connected in communication with the outflow side main header, and the plurality of heat exchange tube forces have their inflow side ends 3.
  • the apparatus according to item 2 wherein the inflow side subheader is arranged in parallel between the inflow side subheader and the outflow side subheader with the outflow side end connected in communication with the outflow side subheader. Heat exchanger.
  • a pair of inflow side main headers are arranged in parallel on the leeward side with respect to the air flow direction, and a pair of outflow side main headers are arranged in parallel on the upwind side corresponding to the inflow side main header. Arranged,
  • Both end portions of the inflow side subheader are connected to the pair of inflow side main headers, respectively.
  • Both end portions of the outflow side subheader are respectively connected to the pair of outflow side main headers,
  • the plurality of heat exchange tube forces The inflow side and the outflow side in a state where the inflow side end portion is connected to the inflow side subheader and the outflow side end portion is connected to the outflow side subheader.
  • the previous item 2 or 3 placed in parallel between subheaders The described heat exchanger.
  • a plurality of the inflow side subheaders are provided in parallel along the length direction of the inflow side main header,
  • a plurality of the outflow side subheaders are provided in parallel along the length direction of the outflow side main header,
  • Non-azeotropic mixed refrigerant containing carbon dioxide and carbon dioxide is circulated through a plurality of heat exchange tubes and heat exchange is performed between the refrigerant and air.
  • the plurality of heat exchange tubes are arranged in parallel to form a path,
  • a plurality of the paths are arranged in parallel along the air flow direction in a state where the heat exchange tubes are orthogonal to the air flow direction,
  • the downstream path in the refrigerant flow direction is disposed on the windward side in the air flow direction with respect to the upstream path.
  • a path disposed at the downstream end is connected to the inflow side header of the inflow side end of the heat exchange tube in the path disposed at the upstream end.
  • the outflow side end of the heat exchange tube is connected in communication with the outflow side header, and the outflow side end of the heat exchange tube in the nose arranged upstream of the two adjacent paths is arranged downstream. 7.
  • the heat exchanger according to item 6 above wherein the inflow side end portion of the heat exchange tube in the path to be communicated via the coolant turn header.
  • a communication hole that connects adjacent refrigerant passage holes is formed in a partition wall between adjacent refrigerant passage holes, and the refrigerant flowing through the refrigerant passage holes is communicated with the communication tube.
  • a refrigerant cooler comprising the heat exchanger described in any one of items 1 to 10 above.
  • the refrigerant compressed by the compressor is cooled by the cooler, and the cooled refrigerant is decompressed by the decompression means and evaporated by the evaporator, and then returns to the compressor.
  • a refrigeration cycle wherein at least one of the cooler and the evaporator is configured by the heat exchange described in any one of 1 to 10 above.
  • a heat exchange method characterized in that the flow direction of the refrigerant flowing through the heat exchange path is opposed to the air flow direction.
  • the refrigerant when heat is exchanged between the refrigerant and the air in using the diacid-carbon-carbon mixed refrigerant having a temperature gradient in the cooling process and the evaporation process, the refrigerant
  • the counter flow method is adopted in which the flow direction of the air is opposed to the flow direction of the air.Therefore, a constant temperature difference between the refrigerant and the air is maintained until the heat exchange is started and the force is finished. Can be ensured, and heat can be exchanged efficiently.
  • the flow direction of the refrigerant can be reliably opposed to the flow direction of the air, and the above-described effects can be reliably obtained.
  • the refrigerant can be distributed in a well-balanced and evenly distributed manner in the heat exchange, and the heat exchange performance can be further improved. .
  • the flow direction of the refrigerant is changed according to how the air flows.
  • the direction can be made to face the direction in a pseudo manner, and the same effect can be obtained as described above.
  • FIG. 1 is a perspective view showing a heat exchanger according to a first embodiment of the present invention.
  • FIG. 2 is an exploded perspective view showing the heat exchanger according to the first embodiment.
  • FIG. 3 is a plan view showing the heat exchanger of the first embodiment.
  • FIG. 4 is a perspective view showing a refrigerant flow in the heat exchanger of the first embodiment.
  • FIG. 5 is a cross-sectional view showing a heat exchange tube applied to the heat exchanger of the first embodiment.
  • FIG. 6 is an exploded perspective view showing an inter-passage heat exchange tube applicable to the heat exchanger of the present invention.
  • FIG. 7 shows an inter-passage heat exchange tube applicable to the heat exchanger of the present invention.
  • FIG. FIG. 4A is a side sectional view
  • FIG. 4B is a front sectional view.
  • FIG. 8 is a circuit diagram of a refrigeration cycle in which the heat exchanger of the present invention can be employed.
  • FIG. 9 is a perspective view showing a heat exchanger according to a second embodiment of the present invention.
  • FIG. 10 is an exploded perspective view showing the heat exchanger according to the second embodiment.
  • FIG. 11 is a plan view showing a heat exchanger according to the second embodiment.
  • FIG. 12 is a perspective view showing a refrigerant flow in the heat exchanger according to the second embodiment.
  • FIG. 13 is a perspective view showing heat exchange according to a third embodiment of the present invention.
  • FIG. 14 is a plan view showing a heat exchanger according to a third embodiment.
  • FIG. 15 is a perspective view showing heat exchange according to a fourth embodiment of the present invention.
  • FIG. 16 is a plan view showing a heat exchanger according to a fourth embodiment.
  • FIG. 17 is a Mollier diagram of a refrigeration cycle using a mixed refrigerant of carbon dioxide and dimethyl ether.
  • FIG. 18 is a front view showing a conventional heat exchanger.
  • A Air (outside air)
  • CP Compressor
  • FIG. 1 is a perspective view showing a heat exchanger according to a first embodiment of the present invention
  • FIG. 2 is an exploded perspective view showing the heat exchanger
  • FIG. 3 is a plan view showing the heat exchanger.
  • the heat exchanger (10) of the first embodiment includes a pair of inflow side main headers (15a) (15a) and a large number of headers (15a) (15a) arranged between the headers (15a) (15a).
  • the inflow-side and outflow-side main headers (15a) and (15b) are formed of a round pipe member made of aluminum or aluminum alloy, and are configured to allow refrigerant to flow therethrough.
  • the pair of inflow side main headers (15a) (15a) are positioned on both sides of the rear side with respect to the core (11) when the direction of force is on the windward side with respect to the flow direction of the air (A). Further, they are arranged in parallel to each other along the vertical direction.
  • the pair of outflow side main headers (15b) and (15b) correspond to the pair of inflow side main headers (15a) and (15a) in parallel with each other at the front both sides of the core (11). It is arranged along the vertical direction.
  • the inflow side and outflow side subheaders (16a) and (16b) are formed by round pipe members made of aluminum or aluminum alloy having a diameter slightly smaller than that of the main headers (15a) and (15b).
  • the refrigerant is configured to be able to circulate.
  • the inflow side subheader (16a) and the outflow side subheader (16b) are arranged at the same pitch in the vertical direction.
  • the core (11) has a number of heat exchange tubes (12). As shown in FIG. 5, the heat exchange tube (12) has an extruded tube made of aluminum or aluminum alloy, and has a flat cross-sectional shape in which the height (thickness) dimension is smaller than the width dimension. Yes.
  • the heat exchange tube (12) is provided with refrigerant passage holes (12a) extending continuously in the length direction and arranged in parallel in the width direction.
  • the refrigerant passage hole (12a) is configured as a heat exchange passage.
  • This heat exchange tube (12) force In the state where the length direction is directed forward and backward and the width direction is directed to the left and right direction, the adjacent tubes are joined to each other with no gap therebetween, while Direction).
  • a plurality of heat exchange tubes (12) arranged side by side in the lateral direction and corrugated fins (13) made of aluminum or an aluminum alloy are alternately stacked in the up-down direction, and are stacked. ) Is formed.
  • the heat exchange tube (12) is connected to the sub header (16a) (16b). Are arranged at predetermined intervals in the vertical direction.
  • each heat exchange tube (12) of the core (11) is connected to the corresponding upstream subheader (16a) and connected to the front end portion (outflow side). End portions) are connected in communication with the corresponding downstream sub-headers (16b).
  • the heat exchanger (10) of the first embodiment is formed.
  • this heat exchanger (10) for example, as a fin (13) or a header (15a) (15b) (16a) (16b), an aluminum brazing brazed at least on one side of the core material It is made up of things made of a sheet. Then, after the heat exchange tubes (12), fins (13), and headers (15a) (15b) (16a) (16b) are temporarily assembled into a heat exchanger shape, the temporary assembly products are batched in the furnace. By brazing, the whole is joined and integrated, and the heat exchange (10) is manufactured.
  • the heat exchanger (10) of the first embodiment uses carbon dioxide (CO
  • a non-azeotropic mixed refrigerant whose main component is the main component is used.
  • a non-azeotropic mixed refrigerant in which 99 to 60% by weight of carbon dioxide and 1 to 40% by weight of dimethyl ether (DME) are mixed is used.
  • the heat exchanger (10) of the present embodiment is suitably used as a condenser (refrigerant cooler), an evaporator, or the like in a refrigeration cycle for a car air conditioner.
  • the refrigerant circuit constituting the refrigeration cycle includes a compressor other than the refrigerant cooler (RC) having the heat exchange (10) force of the present embodiment.
  • CP compressor other than the refrigerant cooler
  • EX expansion valves
  • EV decompressors and evaporators
  • the refrigerant outlet of the compressor (CP) is connected to the refrigerant inlet (14a) (14a) of the heat exchanger (10) as the refrigerant cooler (RC), and the refrigerant outlet (14b) of the heat exchanger (10) (14b) is connected to the refrigerant inlet of the evaporator (EV) via the expansion valve (EX). Further, the refrigerant outlet of the evaporator (EV) is connected to the refrigerant inlet of the compressor (CP).
  • the outflow side header (15b) (16b) side is arranged on the windward side with respect to the flow direction of the air (A), and the inflow side header (15a) (16a) side is arranged on the leeward side. It is installed as follows.
  • the refrigerant compressed by the compressor (CP) is converted into a pair of inflow side main headers (15a) (15a) in the heat exchanger (10) as a cooler (RC). To that It is introduced from the refrigerant inlet (14a) (14a).
  • the refrigerant (R) introduced into the main header (15a) (15a) is evenly distributed from both sides into each inflow side subheader (16a) and flows into each sub-header (16a). It flows into the refrigerant passage hole (12a) of the exchange tube (12).
  • the refrigerant (R) flowing into the heat exchange tube (12) is cooled by exchanging heat with the outside air (A) while passing through the refrigerant passage hole (12a).
  • the refrigerant (R) employed in the present embodiment is composed of a mixed refrigerant with dimethyl ether containing carbon dioxide as a main component, and this mixed refrigerant (R) is used in the condensation process (cooling process). Has a temperature gradient with a constant pressure and a gradual drop in temperature. On the other hand, the temperature of air (A) gradually increases by exchanging heat with refrigerant (R).
  • the refrigerant (R) that decreases in temperature and the air (A) that increases in temperature are opposed to each other.
  • a certain temperature difference can be ensured between the two, the heat exchange capacity can be improved, and heat can be exchanged efficiently.
  • the refrigerant (R) cooled through the heat exchange tube (12) is introduced into the outflow side subheader (16b), and a pair of outflow side main headers (15b) (15b ). Furthermore, the refrigerant (R) that has flowed into the main header (15b) (15b) flows out from the refrigerant outlet (14b) (14b), is decompressed by the expansion valve (EX), and then flows into the evaporator (EV). Is done. The refrigerant then evaporates through the evaporator (EX) to absorb heat from the outside air and cool the outside air. In addition, the refrigerant flowing out of the evaporator (EV) returns to the compressor (CP).
  • the heat exchanger (10) of the present embodiment is used as an evaporator (EV) in a refrigeration cycle as shown in Fig. 8, heat can be exchanged efficiently. That is, after the refrigerant (R) cooled through the refrigerant cooler (RC) is depressurized by the expansion valve (EX), the inflow header (15a) of the heat exchanger (10) as the evaporator (EV) (15a) ( It is introduced into the heat exchange tube (12) through 16a). Heat is exchanged between the refrigerant (R) passing through the heat exchange tube (12) and the air (A).
  • the refrigerant (R) is While air (A) gradually decreases the temperature while increasing the temperature gradually, in this embodiment, the flow direction of the refrigerant (R) is opposed to the flow direction of the air (A). Therefore, throughout the evaporation process, a certain temperature difference between the refrigerant (R) and the air (A) can be reliably ensured, and the heat exchange capacity and thus the heat exchange efficiency can be improved. That's right.
  • the refrigerant that has evaporated through the heat exchange tube (12) flows out through the outflow side sub-header (16b) and the pair of outflow side main headers (15b) (15b), and is compressed in the compressor. Return to (CP).
  • a mixed refrigerant of carbon dioxide and dimethyl ether that decreases in temperature in the cooling process and increases in temperature in the evaporation process is used. Therefore, when heat exchange is performed between the refrigerant (R) and the air (A), a counter flow method is adopted in which the flow direction of the refrigerant (R) is opposed to the flow direction of the air (A). Therefore, for example, in the cooling process, heat is exchanged between the refrigerant (R) whose temperature drops and the air (A) whose temperature rises, so that the refrigerant (R) and air (A) are exchanged throughout the cooling process. A certain temperature difference can be secured and heat can be exchanged efficiently.
  • the inflow side main header (15a) is provided on both sides.
  • the refrigerant (R) can be introduced into the core (11) through the subheader (16a) in a balanced manner with both side forces. For this reason, it is possible to disperse the entire core (11) without deviation, and the heat exchange efficiency can be further improved.
  • the refrigerant (R) that has passed through the core (11) is used as the subheader. Via (16b), it can be evenly distributed on both sides and led to the outflow main header (15b) (15b). Therefore, the refrigerant (R) can smoothly flow out to the core (11) force outflow side main header (15b) (15b), and the heat exchange efficiency can be further improved.
  • the heat exchange tube (12) is a passage as shown in Figs.
  • An intercommunicating heat exchange tube can also be used. This inter-passage heat exchange tube (
  • FIGS. 9 to 12 are views showing a heat exchanger (20) according to the second embodiment of the present invention.
  • the heat exchanger (20) of the second embodiment only one inflow side main header (15a) is arranged on one side and the outflow side main header (15b) is on one side. Only one is placed in each.
  • one end of each of the inflow side subheaders (16a) is connected to the one inflow side main header (15a) on one side, and the other end side is closed.
  • one end of each of the large number of outflow side subheaders (16b) is connected to the single outflow side main header (15b) on one side, and the other end side is closed.
  • the refrigerant (R) and air (A) are counterflowed. For example, during the cooling process, heat is exchanged between the refrigerant (R) that drops in temperature and the air (A) that rises in temperature during the cooling process! As a result, a certain temperature difference can be secured between the refrigerant (R) and the air (A), and heat can be exchanged efficiently.
  • the inflow side and outflow side main headers (15a) (15b) are added. Since it is configured by only one on one side, the number of components can be reduced, the structure can be simplified, the apparatus can be reduced in size and weight, and the cost can be reduced.
  • FIG. 13 is a perspective view showing a heat exchanger (30) according to a third embodiment of the present invention
  • FIG. 14 is a plan view showing the heat exchanger (30).
  • the heat exchanger (30) of the third embodiment includes an inflow header (35a), an outflow header (35b), a refrigerant turn header (36), and two paths (PI).
  • the inflow side and outflow side headers (35a) and (35b) are arranged on one side with respect to the core (31) when the direction facing the windward is forward based on the flow direction of the air (A) ( They are arranged along the vertical direction in the front-to-back direction (left side of Fig. 13). At this time, the inflow header (35a)
  • Each header (35a) (35b) is constituted by a round pipe member made of aluminum or aluminum alloy.
  • a refrigerant inlet nozzle (34a) is provided at the lower part of the inflow side header (35a), and the refrigerant flows from the nozzle (34a) into the inflow side header (35a).
  • a refrigerant outlet nozzle (34b) is provided at the upper part of the outflow side header (35b) so that the refrigerant in the outflow side header (35b) flows out of the refrigerant outlet nozzle (34b). ing.
  • the refrigerant turn header (36) is disposed along the vertical direction on the other side of the core (31) (the right side in FIG. 13).
  • the refrigerant turn header (36) is formed of an elongated aluminum or aluminum alloy pipe member having a long cross section in the front-rear direction, and the front half corresponds to the outflow header (35b) and the latter half. Are arranged so as to correspond to the inflow side header (35a).
  • the core (31) has a first path (P1) constituting the latter half and a second path (P2) constituting the front half.
  • Each path (PI) (P2) includes a heat exchange tube (12) disposed along the left-right direction, One tophine (13) is alternately stacked in the vertical direction, and each layer is arranged.
  • the heat exchange tube (12) is constituted by the inter-passage heat exchange tube shown in FIGS.
  • the heat exchange tube (12) can also be constituted by an extruded tube shown in FIG.
  • each heat exchange tube (12) is connected to the inflow side header (35a), and the other end side is the second half of the refrigerant turn header (36).
  • the second path (P2) is arranged in parallel on the front side of the first path (P1), and one end of each heat exchange tube (12) is connected to the outflow header (35b). At the same time, the other end is connected to the front half of the refrigerant turn header (35).
  • this heat exchanger (10) for example, fins (13) or headers (35a) (35b) (36) made of an aluminum brazing sheet in which a brazing material is clad on at least one side of a core material, etc. It is constituted by. After the heat exchange tubes (12), fins (13), and headers (35a) (35b) (36) are temporarily assembled into a heat exchanger shape, the temporarily assembled products are collectively brazed in the furnace. As a result, the whole is joined and integrated, and the heat exchanger (30) is manufactured.
  • the heat exchanger (30) of the present embodiment uses a non-azeotropic mixed refrigerant mainly composed of carbon dioxide, for example, a mixed refrigerant of carbon dioxide and dimethyl ether, as described above.
  • the heat exchanger (30) of the present embodiment is used as a refrigerant cooler (condenser) in a refrigeration cycle for a car air conditioner, for example, the refrigerant (R) compressed by the compressor is heated. It is introduced into the inflow side header (35a) in the exchanger (30) and then introduced into each heat exchange tube (12) of the first path (P1). Subsequently, the refrigerant (R) is cooled by exchanging heat with the outside air (A) while passing through each heat exchange tube (12) in the first path (P1), and is then cooled to the refrigerant turn header (36). ) Will be introduced in the second half.
  • the refrigerant (R) introduced into the second half of the refrigerant turn header (36) goes around the first half and is introduced into each heat exchange tube (12) of the second path (P2). Thereafter, the refrigerant (R) is cooled by exchanging heat with the outside air (A) while passing through the heat exchange tubes (12) of the second path (P2). Rejected and introduced into the outflow header (35b).
  • the refrigerant temperature is the first.
  • the air A temperature is lower when passing the first pass than when passing the second pass, whereas the temperature of the air A is higher when passing the first pass than when passing the second pass. That is, in the cooling process, the refrigerant (R) whose temperature decreases and the air (A) whose temperature rises are made to face each other in a pseudo manner, so that the refrigerant (R) and air (A) are in the first and second passes.
  • PI While passing through (P2), the temperature difference between the two can be secured, and heat can be exchanged efficiently.
  • the refrigerant (R) cooled by the heat exchanger (30) flows out of the refrigerant outlet nozzle (34b) of the outflow side header (35b) and is depressurized by the expansion valve. Inflow. Then, the refrigerant passes through the evaporator and evaporates, thereby absorbing heat from the outside air and cooling the outside air. Further, the refrigerant flowing out from the evaporator returns to the compressor.
  • the heat exchanger (30) of the present embodiment is used as an evaporator of a refrigeration cycle
  • the refrigerant (R) passes through the first and second passes (PI) (P2) in this order.
  • air (A) passes through the second and first passes (P2) (P1) in this order to lower the temperature. Accordingly, as described above, a constant temperature difference between the refrigerant (R) and the air (A) can be secured in the entire evaporation process, and the heat exchange efficiency can be improved.
  • the heat exchange (30) of the present embodiment when using a mixed refrigerant of diacid-carbon and dimethyl ether, which decreases in temperature in the cooling process and increases in temperature in the evaporation process,
  • a pseudo counter flow method is adopted in which the flow direction of the refrigerant (R) is substantially opposed to the flow direction of the air (A). Therefore, it is possible to ensure a certain temperature difference between the refrigerant (R) and the air (A) over the entire cooling process or the entire evaporation process, and to exchange heat efficiently.
  • FIG. 15 is a perspective view showing a heat exchanger (40) according to a fourth embodiment of the present invention
  • FIG. 16 is a plan view showing the heat exchanger (40).
  • the heat exchanger (40) of the fourth embodiment includes an inflow header (45a), an outflow header (45b), and first and second refrigerant turn headers (46a) (46b).
  • a core (41) having three paths (PI) to (P3) It is prepared as a typical component.
  • the first path (P1), the second path (P2), and the third path (P3) are arranged in parallel in order of the leeward (rearward) force to form the core (41).
  • the inflow side header (45a) is arranged corresponding to the first path (P1) on one side (right side) of the core (41), and each header of the first path (P1) is placed on the header (45a).
  • One end of the heat exchange tube (12) is connected in communication.
  • the first refrigerant turn header (46a) is arranged corresponding to the first and second paths (PI) (P2) on the other side (left side) of the core (41), and the header (46a)
  • the other end of each heat exchange tube (12) in the first path (P1) is connected to the second half of the first path (P1), and the other end of each heat exchange tube (12) in the second path (P2) is connected to the first half. Connected and connected.
  • the second refrigerant turn header (46b) is arranged corresponding to the second and third paths (P2) (P3) on one side (right side) of the core (41), and the header (46b)
  • P2 second and third paths
  • P3 third path
  • One end of each heat exchange tube (12) in the second path (P2) is connected to the second half of the pipe
  • one end of each heat exchange tube (13) in the third path (P3) is connected to the first half. It has been.
  • the outflow side header (45b) is arranged corresponding to the third path (P3) on the other side (left side) of the core (41), and the header (45b) has the third path (P3).
  • the other end of each heat exchange tube (12) is connected in communication!
  • the refrigerant inlet nozzle (44a) is provided at the lower part of the inflow side header (45a), and the refrigerant outlet nozzle (44b) is provided at the upper part of the outflow side header (45b). .
  • the refrigerant (R) introduced into the inflow side header (45a) passes through the first path (P1), and the first refrigerant turn header (46a ), Passes through the second path (P2), and then passes back through the second refrigerant turn header (46b), passes through the third path (P3), and then passes through the outflow header (45b). Leaked.
  • the refrigerant (R) is passed in the order of the first to third passes (P1) to (P3), while the outside air (A) is passed in the order of the third to first passes (P3) to (P1).
  • the refrigerant (R) is cooled (condensed) or evaporated by heat exchange between (R) and air (A).
  • the flow of the refrigerant (R) is similar to the above when using a non-azeotropic mixed refrigerant containing diacid-carbon that changes in temperature during the cooling or evaporation process. Since the counter counter flow method is adopted in which the direction is substantially opposite to the flow direction of air (A), the refrigerant (R) and air (A) are used throughout the cooling or evaporation process. A certain temperature difference can be reliably ensured between them, and heat can be exchanged efficiently.
  • the heat exchanger and related technology of the present invention can be employed in a refrigeration system for a car air conditioner, for example.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L’invention concerne un échangeur de chaleur dans lequel on fait passer un agent réfrigérant (R) mélangé non azéotrope contenant du dioxyde de carbone par des tubes d’échangeur de chaleur (12), l’échange de chaleur s’effectuant entre l’agent réfrigérant (R) et l’air (A). Les tubes (12) de l’échangeur de chaleur sont agencés en parallèle aux sens longitudinaux des tubes (12) parallèles au sens de débit de l’air (A). Le sens d’écoulement de l’agent réfrigérant (R) traversant les tubes (12) est opposé au sens d’écoulement de l’air (A). La présente invention vise ainsi un échangeur de chaleur capable d’atteindre un échange de chaleur efficace bien qu’il utilise un agent réfrigérant mélangé non azéotrope contenant du dioxyde de carbone.
PCT/JP2006/324055 2005-12-02 2006-12-01 Échangeur de chaleur WO2007063978A1 (fr)

Priority Applications (1)

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DE112006003241T DE112006003241T5 (de) 2005-12-02 2006-12-01 Wärmetauscher

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2005-349054 2005-12-02
JP2005349054A JP2007155183A (ja) 2005-12-02 2005-12-02 熱交換器

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WO2007063978A1 true WO2007063978A1 (fr) 2007-06-07

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JP (1) JP2007155183A (fr)
DE (1) DE112006003241T5 (fr)
WO (1) WO2007063978A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015039894A1 (fr) * 2013-09-17 2015-03-26 Volkswagen Aktiengesellschaft Échangeur thermique
WO2015063857A1 (fr) * 2013-10-29 2015-05-07 三菱電機株式会社 Échangeur thermique et climatiseur
CN114072297A (zh) * 2019-07-01 2022-02-18 三菱重工制冷空调系统株式会社 空调单元、热交换器及空调机

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009006674B4 (de) 2009-01-29 2021-12-09 Rheinmetall Landsysteme Gmbh Kondensatorvorrichtung für eine Kühlanlage
US10907903B2 (en) 2016-01-21 2021-02-02 Samsung Electronics Co., Ltd. Air conditioner with flow direction changing mechanism

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10185471A (ja) * 1996-12-26 1998-07-14 Showa Alum Corp 熱交換器
JP2000104085A (ja) * 1998-09-29 2000-04-11 Nippon Mitsubishi Oil Corp ジメチルエーテルを冷媒とする冷凍機用潤滑油
JP2001012821A (ja) * 1999-06-25 2001-01-19 Denso Corp サーペンタイン型蒸発器
JP2001050685A (ja) * 1999-08-06 2001-02-23 Sanyo Electric Co Ltd 熱交換器
JP2001336896A (ja) * 2000-05-30 2001-12-07 Matsushita Electric Ind Co Ltd 熱交換器および冷凍サイクル装置
JP2003090690A (ja) * 2001-09-18 2003-03-28 Hitachi Ltd 積層型熱交換器及び冷凍サイクル
JP2004198063A (ja) * 2002-12-20 2004-07-15 Sanyo Electric Co Ltd 非共沸混合冷媒および冷凍サイクル、並びに冷凍装置
JP2004225961A (ja) * 2003-01-21 2004-08-12 Denso Corp マルチフロー型熱交換器

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4016544B2 (ja) 1999-09-29 2007-12-05 株式会社デンソー 超臨界蒸気圧縮式冷凍サイクル用の放熱器
JP4383968B2 (ja) 2004-06-14 2009-12-16 日立アプライアンス株式会社 電気洗濯機

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH10185471A (ja) * 1996-12-26 1998-07-14 Showa Alum Corp 熱交換器
JP2000104085A (ja) * 1998-09-29 2000-04-11 Nippon Mitsubishi Oil Corp ジメチルエーテルを冷媒とする冷凍機用潤滑油
JP2001012821A (ja) * 1999-06-25 2001-01-19 Denso Corp サーペンタイン型蒸発器
JP2001050685A (ja) * 1999-08-06 2001-02-23 Sanyo Electric Co Ltd 熱交換器
JP2001336896A (ja) * 2000-05-30 2001-12-07 Matsushita Electric Ind Co Ltd 熱交換器および冷凍サイクル装置
JP2003090690A (ja) * 2001-09-18 2003-03-28 Hitachi Ltd 積層型熱交換器及び冷凍サイクル
JP2004198063A (ja) * 2002-12-20 2004-07-15 Sanyo Electric Co Ltd 非共沸混合冷媒および冷凍サイクル、並びに冷凍装置
JP2004225961A (ja) * 2003-01-21 2004-08-12 Denso Corp マルチフロー型熱交換器

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015039894A1 (fr) * 2013-09-17 2015-03-26 Volkswagen Aktiengesellschaft Échangeur thermique
CN105518406A (zh) * 2013-09-17 2016-04-20 大众汽车有限公司 热交换器
CN105518406B (zh) * 2013-09-17 2018-01-16 大众汽车有限公司 热交换器
WO2015063857A1 (fr) * 2013-10-29 2015-05-07 三菱電機株式会社 Échangeur thermique et climatiseur
AU2013404239B2 (en) * 2013-10-29 2016-11-03 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus
JPWO2015063857A1 (ja) * 2013-10-29 2017-03-09 三菱電機株式会社 熱交換器、及び、空気調和装置
US10054376B2 (en) 2013-10-29 2018-08-21 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus
CN114072297A (zh) * 2019-07-01 2022-02-18 三菱重工制冷空调系统株式会社 空调单元、热交换器及空调机
CN114072297B (zh) * 2019-07-01 2023-10-13 三菱重工制冷空调系统株式会社 空调单元、热交换器及空调机

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