WO2013186983A1 - Echangeur de chaleur à stockage de froid - Google Patents

Echangeur de chaleur à stockage de froid Download PDF

Info

Publication number
WO2013186983A1
WO2013186983A1 PCT/JP2013/003040 JP2013003040W WO2013186983A1 WO 2013186983 A1 WO2013186983 A1 WO 2013186983A1 JP 2013003040 W JP2013003040 W JP 2013003040W WO 2013186983 A1 WO2013186983 A1 WO 2013186983A1
Authority
WO
WIPO (PCT)
Prior art keywords
cold storage
melting point
regenerator
refrigerant
heat exchanger
Prior art date
Application number
PCT/JP2013/003040
Other languages
English (en)
Japanese (ja)
Inventor
貴志 壇上
山田　淳司
井上　誠司
西田　伸
Original Assignee
株式会社デンソー
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 株式会社デンソー filed Critical 株式会社デンソー
Priority to US14/407,844 priority Critical patent/US20150168047A1/en
Publication of WO2013186983A1 publication Critical patent/WO2013186983A1/fr

Links

Images

Classifications

    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements
    • 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
    • F28D1/05383—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits
    • 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
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • F28D20/026—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat with different heat storage materials not coming into direct contact
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat
    • 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
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D2020/0004—Particular heat storage apparatus
    • F28D2020/0013—Particular heat storage apparatus the heat storage material being enclosed in elements attached to or integral with heat exchange conduits
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • the present disclosure relates to a cold storage heat exchanger used in a refrigeration cycle apparatus.
  • a refrigeration cycle apparatus is used as an air conditioner. Attempts have been made to provide limited cooling even when the refrigeration cycle apparatus is stopped. For example, in a vehicle air conditioner, a refrigeration cycle apparatus is driven by a traveling engine. For this reason, if the engine stops while the vehicle is temporarily stopped, the refrigeration cycle apparatus stops. In order to improve fuel efficiency, so-called idle stop vehicles that stop the engine while the vehicle is stopped, such as waiting for a signal, are increasing. In such an idle stop vehicle, there is a problem that the refrigeration cycle apparatus stops while the vehicle is stopped (the engine is stopped), thereby impairing the comfort in the passenger compartment. In addition, there is also a problem that if the engine is restarted even when the vehicle is stopped in order to maintain a feeling of air conditioning, improvement in fuel efficiency is hindered.
  • Patent Documents 1 to 5 disclose techniques for solving such problems.
  • the indoor heat exchanger in order to maintain the air conditioning feeling even when the engine is stopped, the indoor heat exchanger has a cold storage function. Thus, cold energy is stored while the vehicle is running, and this cold air is used while the vehicle is stopped.
  • Patent Document 1 describes a cool storage container that encloses a cool storage material arranged behind the air flow of a conventional evaporator.
  • Patent Documents 2 to 5 describe a system in which a small-capacity cold storage container is provided adjacent to a tube constituting a refrigerant flow path of an evaporator, and a cold storage material is enclosed therein.
  • the evaporator with a cool storage function of patent documents 2-5 collects cold air in the cool storage material by solidifying the cool storage material in the cool storage container during the operation of the air-conditioning compressor. And during the idle stop, the solid cool storage material is melted and the cool air is released into the air, so that the temperature change of the blown air is suppressed until the cool storage material is completely melted, and the air conditioning feeling is maintained. Can do.
  • the present disclosure has been made in view of the above-described problems, and an object thereof is to provide a cold storage heat exchanger that can maintain a cold storage function in a wide range of air temperatures.
  • a cold storage heat exchanger that exchanges heat with air flowing around
  • the cold storage heat exchanger includes a refrigerant passage through which a refrigerant flows, a refrigerant
  • a cold storage container that houses therein a cold storage material that exchanges heat with the refrigerant flowing through the passage to keep the amount of heat from the refrigerant, and the cold storage container contains a plurality of cold storage materials having different melting points.
  • the plurality of regenerator materials include a regenerator material having a high melting point and a regenerator material having a low melting point, and the regenerator material having a high melting point is provided upstream of the regenerator material having a low melting point.
  • a plurality of cool storage materials having different melting points are accommodated in the cool storage container.
  • fusing point is provided in the upstream of an air flow rather than the cool storage material with low melting
  • FIG. 3 is an enlarged cross-sectional view showing a part of a III-III cross section of FIG. 1. It is sectional drawing which shows the cool storage container 47 of 1st Embodiment. It is a figure for demonstrating the cool storage state of two cool storage materials 50a, 50b of 1st Embodiment. It is an expanded sectional view showing a part of section of evaporator 40A of a 2nd embodiment.
  • the evaporator 40 constitutes a refrigeration cycle apparatus (not shown).
  • the refrigeration cycle apparatus is used for, for example, a vehicle air conditioner.
  • the refrigeration cycle apparatus includes a compressor, a radiator, a decompressor, and an evaporator 40. These components are connected in an annular shape by piping and constitute a refrigerant circulation path.
  • the compressor is driven by a power source for running the vehicle. For this reason, when the power source stops, the compressor also stops.
  • the compressor sucks the refrigerant from the evaporator 40, compresses it, and discharges it to the radiator.
  • the radiator cools the high-temperature refrigerant.
  • the radiator is also called a condenser.
  • the decompressor decompresses the refrigerant cooled by the radiator.
  • the decompressor can be provided by a fixed throttle, a temperature expansion valve, or an ejector.
  • the evaporator 40 evaporates the refrigerant decompressed by the decompressor and cools the medium.
  • the evaporator 40 cools the air supplied to the passenger compartment.
  • the refrigeration cycle apparatus can further include an internal heat exchange for exchanging heat between the high-pressure side liquid refrigerant and the low-pressure side gas refrigerant, and a receiver or accumulator tank element for storing excess refrigerant.
  • the power source can be provided by an internal combustion engine or an electric motor.
  • the evaporator 40 is a cold storage heat exchanger and has a refrigerant passage member branched into a plurality of branches.
  • the refrigerant passage member is provided by a metal passage member such as aluminum.
  • the refrigerant passage member is provided by headers 41 to 44 positioned in a pair and a plurality of refrigerant tubes 45 connecting the headers 41 to 44.
  • the first header 41 and the second header 42 form a pair, and are arranged in parallel at a predetermined distance from each other.
  • the third header 43 and the fourth header 44 also form a set and are arranged in parallel with a predetermined distance from each other.
  • a plurality of refrigerant tubes 45 are arranged at equal intervals between the first header 41 and the second header 42. Each refrigerant pipe 45 communicates with the corresponding header at its end.
  • a first heat exchanging portion 48 is formed by the first header 41, the second header 42, and a plurality of refrigerant tubes 45 arranged therebetween.
  • a plurality of refrigerant tubes 45 are arranged at equal intervals between the third header 43 and the fourth header 44.
  • Each refrigerant pipe 45 communicates with the corresponding header at its end.
  • a second heat exchanging portion 49 is formed by the third header 43, the fourth header 44, and a plurality of refrigerant tubes 45 arranged therebetween.
  • the evaporator 40 has a first heat exchange unit 48 and a second heat exchange unit 49 arranged in two layers. With respect to the air flow direction, the second heat exchange unit 49 is arranged on the upstream side, and the first heat exchange unit 48 is arranged on the downstream side.
  • a joint (not shown) as a refrigerant inlet is provided at the end of the first header 41.
  • the inside of the first header 41 is partitioned into a first partition and a second partition by a partition plate (not shown) provided approximately at the center in the length direction.
  • the plurality of refrigerant tubes 45 are divided into a first group and a second group.
  • the refrigerant is supplied to the first section of the first header 41.
  • the refrigerant is distributed from the first section to a plurality of refrigerant tubes 45 belonging to the first group.
  • the refrigerant flows into the second header 42 through the first group and is collected.
  • the refrigerant is distributed again from the second header 42 to the plurality of refrigerant tubes 45 belonging to the second group.
  • the refrigerant flows into the second section of the first header 41 through the second group.
  • a joint (not shown) as a refrigerant outlet is provided.
  • the inside of the third header 43 is partitioned into a first partition and a second partition by a partition plate (not shown) provided substantially at the center in the length direction.
  • the plurality of refrigerant tubes 45 are divided into a first group and a second group.
  • the first section of the third header 43 is adjacent to the second section of the first header 41.
  • the first section of the third header 43 and the second section of the first header 41 are in communication.
  • the refrigerant flows from the second section of the first header 41 into the first section of the third header 43.
  • the refrigerant is distributed from the first section to a plurality of refrigerant tubes 45 belonging to the first group.
  • the refrigerant flows into the fourth header 44 through the first group and is collected.
  • the refrigerant is distributed again from the fourth header 44 to the plurality of refrigerant tubes 45 belonging to the second group.
  • the refrigerant flows into the second section of the third header 43 through the second group.
  • coolant in a U shape is formed.
  • the refrigerant in the second section of the third header 43 flows out from the refrigerant outlet and flows toward the compressor.
  • the refrigerant pipe 45 is a multi-hole pipe having a plurality of refrigerant passages 45a through which the refrigerant flows.
  • the refrigerant tube 45 is also called a flat tube. This multi-hole tube can be obtained by an extrusion manufacturing method.
  • the plurality of refrigerant passages 45 a extend along the longitudinal direction of the refrigerant pipe 45 and open at both ends of the refrigerant pipe 45.
  • the plurality of refrigerant tubes 45 are arranged in a row.
  • the plurality of refrigerant tubes 45 are arranged so that their main surfaces face each other.
  • the plurality of refrigerant tubes 45 partition an air passage 460 for exchanging heat with air between two adjacent refrigerant tubes 45 and an accommodating portion 461 for accommodating a cold storage container 47 described later. .
  • the evaporator 40 includes fins 46 for increasing the contact area with the air supplied to the passenger compartment.
  • the fins 46 are provided by a plurality of corrugated fins 46.
  • the fins 46 are disposed in an air passage 460 that is defined between two adjacent refrigerant tubes 45.
  • the fin 46 is thermally coupled to the two adjacent refrigerant tubes 45.
  • the fins 46 are joined to the two adjacent refrigerant tubes 45 by a joining material excellent in heat transfer.
  • a brazing material can be used as the bonding material.
  • the fin 46 has a shape in which a thin metal plate such as aluminum is bent in a wave shape, and includes an air passage 460 called a louver.
  • the evaporator 40 further includes a plurality of cold storage containers 47.
  • the cold storage container 47 has a flat cylindrical shape.
  • the cold storage container 47 is closed by squeezing the cylinder in the thickness direction at both ends in the longitudinal direction, and spaces for accommodating the cold storage materials 50a and 50b are formed inside.
  • the cold storage container 47 has a wide main surface on both surfaces.
  • the two main walls that provide these two main surfaces are each arranged in parallel with the refrigerant pipe 45. And it arrange
  • tube 45 may contact at least one surface, and this embodiment both surfaces.
  • a plurality of cold storage containers 47 are disposed between two adjacent refrigerant pipes 45, and in this embodiment, two cold storage cases 60 are arranged.
  • Each cold storage case 60 is arranged along the flow direction of the intake air.
  • the plurality of cool storage cases 60 are arranged to be different cool storage cases 60 on the upstream side and the downstream side of the air flow.
  • Each cold storage case 60 accommodates cold storage materials 50a and 50b having different melting points independently.
  • each of the cold storage cases 60 is provided with one or more sealing ports 61 for sealing the cold storage materials 50a and 50b.
  • the sealing port 61 is provided on the upstream side (windward side) or the downstream side (leeward side) of the air flow in the outer periphery of the cold storage case 60.
  • the cold storage case 47 is referred to.
  • the cold storage container 47 is thermally coupled to two refrigerant tubes 45 disposed on both sides thereof.
  • the cold storage container 47 is joined to the two adjacent refrigerant pipes 45 by a joining material excellent in heat transfer.
  • a resin material such as a brazing material or an adhesive can be used.
  • the cold storage container 47 is brazed to the refrigerant pipe 45.
  • a large amount of brazing material is disposed between the cold storage container 47 and the refrigerant pipe 45 in order to connect them with a wide cross-sectional area.
  • This brazing material can be provided by placing a brazing foil between the cold storage container 47 and the refrigerant pipe 45. As a result, the cold storage container 47 exhibits good heat conduction with the refrigerant pipe 45.
  • each cold storage container 47 is substantially equal to the thickness of the air passage 460. Therefore, the thickness of the cold storage container 47 is substantially equal to the thickness of the fin 46.
  • the fin 46 and the cold storage container 47 can be interchanged. As a result, the arrangement pattern of the plurality of fins 46 and the plurality of cold storage containers 47 can be set with a high degree of freedom.
  • the thickness of the cold storage container 47 is clearly larger than the thickness of the refrigerant pipe 45.
  • This configuration is effective for accommodating a large amount of cool storage material 50a, 50b.
  • the lengths of the cold storage containers 47 are equal to each other. Further, the length in which the two cold storage cases 60 are arranged has substantially the same length as the fins 46. As a result, the cold storage container 47 occupies substantially the entire longitudinal direction of the accommodating portion 461 defined between the two adjacent refrigerant tubes 45. Accordingly, the two cold storage cases 60 arranged have the same area in contact with the refrigerant pipe 45. In other words, the two cold storage cases 60 arranged have the same area for heat exchange with the refrigerant pipe 45. Further, the gap between the cold storage container 47 and the headers 41 to 44 can be filled with a section of the fin 46 or a filler such as resin.
  • the plurality of refrigerant tubes 45 are arranged at substantially constant intervals.
  • a plurality of gaps are formed between the plurality of refrigerant tubes 45.
  • a plurality of fins 46 and a plurality of cold storage containers 47 are arranged with a predetermined regularity.
  • a part of the gap is an air passage 460.
  • the remaining part of the gap is the accommodating part 461 of the cold storage container 47.
  • 10% or more and 50% or less is the accommodating portion 461.
  • a cool storage container 47 is disposed in the housing portion 461.
  • the cold storage containers 47 are arranged almost uniformly distributed throughout the evaporator 40.
  • the two refrigerant tubes 45 located on both sides of the cold storage container 47 define an air passage 460 for exchanging heat with air on the side opposite to the cold storage container 47.
  • two refrigerant tubes 45 are disposed between the two fins 46, and one cold storage container 47 including two cold storage cases 60 is disposed between the two refrigerant tubes 45. Yes.
  • the cold storage container 47 is made of metal such as aluminum and aluminum alloy.
  • a material containing a metal having a lower ionization tendency than hydrogen as a main material or a component is used.
  • the cold storage materials 50a and 50b are materials that exchange heat with the refrigerant flowing through the refrigerant passage 45a to keep the amount of heat from the refrigerant.
  • the cold storage materials 50a and 50b are retained by solidifying the heat from the refrigerant, and are released to the outside by melting the retained heat.
  • the cold storage material 50a having a high melting point is provided upstream of the cold storage material 50b having a low melting point. Therefore, in FIG. 3, the cool storage material 50a of the upper cool storage case 60 has a higher melting point than the cool storage material 50b of the lower cool storage case 60.
  • the melting point of the high-melting-point regenerator material 50a which is a regenerator material having a high melting point, may be not less than the cooling temperature zone during cooling, and may be not less than 5 degrees Celsius and not more than 25 degrees Celsius.
  • the melting point of the low melting point regenerator material 50b which is a regenerator material having a low melting point, may be 0 degrees Celsius or more and 15 degrees Celsius or less. Further, when the melting point of the high melting point regenerator material 50a is 5 degrees Celsius or more and 15 degrees Celsius or less, the low melting point regenerator material 50b has a melting point of 0 degrees Celsius or more and lower than the melting point of the high melting point regenerator material 50a.
  • the melting point of the low melting point regenerator material 50b may be 0 ° C. or higher and 10 ° C. or lower so that it can be solidified and melted even at low temperatures such as in winter.
  • the necessary heat quantity of the two cold storage materials 50a and 50b may be about 200 kJ / kg or more in consideration of the capacity of the cold storage container 47. As a result, it is possible to secure the necessary cold storage capacity during idle stop.
  • organic materials have low thermal conductivity and large supercooling except for paraffinic materials.
  • chemical heat storage chemical stability, toxic poison, corrosiveness, reaction promoting means (pressure holding, stirring required). Therefore, in this embodiment, two types of paraffin are used as the cold storage materials 50a and 50b.
  • the paraffin used for the high melting point regenerator material 50a may have 16 or 15 carbon atoms.
  • the paraffin used for the low melting-point cold storage material 50b should just have 15 or 14 carbon atoms.
  • the carbon number of the paraffin of the high melting point regenerator material 50a is 16
  • the carbon number of the low melting point regenerator material 50b may be 15 or 14
  • the carbon number of the paraffin of the high melting point regenerator material 50a is 15, The number of carbon atoms in the paraffin of the melting point regenerator material 50b may be 14.
  • the compressor When there is an air conditioning request from the passenger, for example, a cooling request, the compressor is driven by a power source.
  • the compressor sucks the refrigerant from the evaporator 40, compresses it, and discharges it.
  • the refrigerant discharged from the compressor is radiated by the radiator.
  • the refrigerant discharged from the radiator is decompressed by the decompressor and supplied to the evaporator 40.
  • the refrigerant evaporates in the evaporator 40, cools the cold storage container 47, and cools the surrounding air through the fins 46.
  • the power source is stopped to reduce energy consumption, and the compressor is stopped.
  • the refrigerant in the evaporator 40 gradually loses its cooling capacity.
  • the regenerator materials 50a and 50b gradually cool and cool the air.
  • the heat of the air is conducted to the cold storage materials 50a and 50b through the fins 46, the refrigerant pipe 45, and the cold storage container 47.
  • the refrigeration cycle apparatus cools the cold storage materials 50a and 50b again, and the cold storage materials 50a and 50b store cold.
  • the refrigerant temperature is the high melting point regenerator 50a (in FIG. 5).
  • A) is below the melting point of both of the low melting point regenerator material 50b (B in FIG. 5) and solidifies to cool.
  • the solidified cold storage material melts and releases the cool air accumulated while being released into the air, thereby suppressing the temperature rise of the blown air and extending the idle stop time.
  • the refrigerant temperature is higher than when the load is high.
  • the high-melting-point regenerator material 50a can solidify and store cold air when the air conditioner is activated.
  • the high-melting-point regenerator material 50a is released while the cold air accumulated while being melted is released into the air, thereby suppressing the temperature rise of the blown air and extending the idling stop time.
  • cool storage container 47 two cool storage materials 50a and 50b are separately accommodated as the plurality of cool storage materials 50a and 50b having different melting points. Yes. And the cool storage material 50a with high melting
  • the sealing port 61 is provided on the upstream side or the downstream side of the air flow in the outer periphery of the cold storage case 60. Therefore, since the sealing port 61 is not provided in the air passage 460, it is possible to prevent a ventilation resistance.
  • a second embodiment will be described using FIG. 6 and FIG.
  • the present embodiment is characterized in that the cold storage cases 60A are arranged so as to contact each other. Since it is the structure which is contacting in this way, space can be utilized more effectively. Therefore, the amount of the regenerator materials 50a and 50b that can be filled can be increased.
  • the operations and effects in the other configurations are the same as those in the first embodiment.
  • the present embodiment is characterized in that the inside of the cold storage container 47C is partitioned by the partition 70, and the cold storage materials 50a and 50b having different melting points are accommodated in the partitioned spaces.
  • the cool storage container 47C is provided with one sealing port 61 for sealing the cool storage materials 50a and 50b. Therefore, two kinds of cool storage materials 50a and 50b are sealed from one sealing port 61. Therefore, the configuration is simplified, and handling as the cold storage container 47C is facilitated.
  • the sealing port 61 is provided on the upstream side or the downstream side of the air flow in the outer periphery of the cold storage container 47C, and is provided on the leeward side in the present embodiment.
  • the present embodiment is characterized in that the cold storage cases 60E are integrally formed so as to be in contact with each other, and the two sealing ports 61 are on the same side. Even with such a configuration, the same operations and effects as those of the second embodiment described above can be achieved.
  • a sixth embodiment will be described with reference to FIG.
  • the present embodiment is characterized in that the cold storage cases 60F are integrally formed so as to be in contact with each other, and the two sealing ports 61 are on the same side. Furthermore, the one inlet 61 is constituted by a pipe 61F. Even with such a configuration, the same operations and effects as those of the second embodiment described above can be achieved.
  • a seventh embodiment will be described with reference to FIG.
  • the present embodiment is characterized in that the cold storage case 60G is arranged on one surface of the refrigerant passage 45a.
  • the configuration shown in FIG. 12 is a so-called drone cup type. By arranging it on one side of the refrigerant passage 45a, the entire space can be saved. Even with such a configuration, it is possible to achieve the same operations and effects as in the first embodiment. (Eighth embodiment)
  • an eighth embodiment will be described with reference to FIGS. 13 and 14.
  • This embodiment is also characterized in that cold storage cases 60H and 60I are arranged on one side of the refrigerant passage 45a, as in the seventh embodiment.
  • the two cold storage cases 60H and 60I extend along the air flow direction and are arranged along the air flow direction. Moreover, in the example shown in FIG.
  • the cool storage case 60H is arrange
  • the cold storage case 60I is disposed so as to be in contact with the air flow direction.
  • one of the adjacent cool storage containers 47J is characterized in that the high melting point cold storage material 50a is accommodated and the other is accommodated in the low melting point cold storage material 50b.
  • This embodiment can be applied when the cooling capacity of the evaporator 40J is sufficiently high.
  • the cold storage container 47J for storing the high melting point cold storage material 50a and the cold storage container 47J for storing the low melting point cold storage material 50b are alternately arranged between the refrigerant tubes 45. 15 and 16 show a cold storage container 47J in which the high melting point cold storage material 50a is accommodated.
  • the refrigerant temperature is the high melting point regenerator 50a (A in FIG. 17). ), Lower than both melting points of the low-melting-point regenerator material 50b (B in FIG. 17), and solidifies to cool. And during idle stop, the solidified cold storage material melts and releases the cool air accumulated while being released into the air, thereby suppressing the temperature rise of the blown air and extending the idle stop time.
  • the refrigerant temperature is higher than when the load is high.
  • the high-melting-point regenerator material 50a can solidify and store cold air when the air conditioner is activated.
  • the high-melting-point regenerator material 50a is released while the cold air accumulated while being melted is released into the air, thereby suppressing the temperature rise of the blown air and extending the idling stop time.
  • the high melting point regenerator material 50a is disposed on the windward side and the low melting point regenerator material 50b is disposed on the leeward side. be able to.
  • the cooling capacity of the evaporator 40J is sufficiently high as in the present embodiment and the temperature of the evaporator 40J decreases substantially uniformly in the air flow direction, it is not necessary to arrange the high melting point regenerator 50a only on the windward side. . Therefore, even if the single cold storage container 47J is arranged in the air flow direction as in the present embodiment, the same operations and effects as those in the first embodiment can be achieved.
  • the cold storage containers 47J having different melting points are alternately arranged (high melting point-low melting point-high melting point ...), but are not limited to each other, for example, not one by one but two by two. They may be arranged alternately (high melting point-high melting point-low melting point-low melting point-high melting point-high melting point ...), or may be alternately arranged in units of three. In other words, at least some of the cool storage materials 50a and 50b accommodated in the plurality of cool storage containers 47J may be configured to have a different melting point from the cool storage material 50b accommodated in the other cool storage containers. .
  • the number of the cold storage containers 47J for storing the high melting point cold storage material 50a and the number of the cold storage containers 47J for storing the low melting point cold storage material 50b are the same.
  • the melting point and the capacity of the cool storage material 50 accommodated in each cool storage container 47J may be selected as appropriate.
  • the cold storage materials 50a and 50b are two types, but are not limited to two types, and may be three or more types. As a result, cold storage can be performed in stages, and a wider range of air-conditioning temperature can be accommodated.
  • the refrigerant pipe 45 can be provided by a multi-hole extruded pipe or a pipe formed by bending a plate material on which dimples are formed. Furthermore, the fins can be omitted. Such a heat exchanger is also called a finless type. Instead of fins, protrusions extending from the refrigerant pipe may be provided to promote heat exchange with air.
  • the cold storage case 60 may not be arranged on the outer periphery of the refrigerant pipe 45, and the cold storage case may be arranged in the refrigerant passage.
  • the number of cold storage cases 60 may be one.
  • a heat exchanger may be placed horizontally and a regenerator material having a high melting point and a high specific gravity and a regenerator material having a low melting point and a low specific gravity may be disposed and enclosed in a single container. Accordingly, a cold storage material having a high melting point can exist upstream of the air flow without preparing a plurality of cold storage cases and dividing them.
  • regenerator materials there are a plurality of types of regenerator materials. However, a mixture of the respective regenerator materials may be employed.
  • the present disclosure can be applied to an evaporator having various flow paths.
  • the present disclosure may be applied to an evaporator such as a one-way type or a front and rear U-turn type.
  • the present disclosure may be applied to refrigeration cycle apparatuses such as refrigeration, heating, and hot water supply. Furthermore, the present disclosure may be applied to a refrigeration cycle apparatus including an ejector.
  • an inner fin may be provided inside the cold storage container 47.
  • an opening that exposes the top of the inner fin may be provided in the outer shell, and the top of the inner fin may be directly joined to the refrigerant pipe.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'invention porte sur un échangeur de chaleur à stockage de froid (40), lequel échangeur échange de la chaleur avec de l'air s'écoulant à la périphérie de l'échangeur de chaleur, et lequel échangeur de chaleur comprend : des passages de réfrigérant (45a) dans lesquels circule un réfrigérant ; et des récipients de stockage de froid (47, 47C, 47D, 47E, 47F, 47J) dans lesquels sont renfermés des matériaux de stockage de froid (50a, 50b) qui échangent de la chaleur avec le réfrigérant circulant dans les passages de réfrigérant (45a) et qui conservent une quantité de chaleur. Une pluralité des matériaux de stockage de froid (50a, 50b) ayant des points de fusion différents sont renfermés dans les récipients de stockage de froid (47, 47C, 47D, 47E, 47F, 47J).
PCT/JP2013/003040 2012-06-14 2013-05-13 Echangeur de chaleur à stockage de froid WO2013186983A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US14/407,844 US20150168047A1 (en) 2012-06-14 2013-05-13 Cold storage heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012-135042 2012-06-14
JP2012135042A JP2013256262A (ja) 2012-06-14 2012-06-14 蓄冷熱交換器

Publications (1)

Publication Number Publication Date
WO2013186983A1 true WO2013186983A1 (fr) 2013-12-19

Family

ID=49757835

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2013/003040 WO2013186983A1 (fr) 2012-06-14 2013-05-13 Echangeur de chaleur à stockage de froid

Country Status (3)

Country Link
US (1) US20150168047A1 (fr)
JP (1) JP2013256262A (fr)
WO (1) WO2013186983A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015137807A (ja) * 2014-01-22 2015-07-30 株式会社デンソー 蓄冷熱交換器
WO2016174852A1 (fr) * 2015-04-30 2016-11-03 株式会社デンソー Evaporateur
JP2016211837A (ja) * 2015-04-30 2016-12-15 株式会社デンソー 蒸発器
CN106255861A (zh) * 2014-05-23 2016-12-21 株式会社电装 热交换器
WO2017208760A1 (fr) * 2016-06-01 2017-12-07 株式会社デンソー Échangeur de chaleur régénératif
CN109405616A (zh) * 2018-11-01 2019-03-01 扬州大学 一种相变储能套管式地热换热器
CN110605953A (zh) * 2018-11-11 2019-12-24 南京酷朗电子有限公司 快速置换式储能模块

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5525726B2 (ja) * 2008-12-26 2014-06-18 株式会社ケーヒン・サーマル・テクノロジー 蓄冷機能付きエバポレータ
JP6458680B2 (ja) * 2015-02-02 2019-01-30 株式会社デンソー 熱交換器
JP6406116B2 (ja) * 2015-04-28 2018-10-17 株式会社デンソー 車両用空調装置
WO2017057174A1 (fr) * 2015-10-01 2017-04-06 株式会社デンソー Échangeur de chaleur à accumulation de froid
JP6409836B2 (ja) 2015-10-01 2018-10-24 株式会社デンソー 蓄冷熱交換器
JP6888904B2 (ja) * 2015-11-24 2021-06-18 ダイムラー・アクチェンゲゼルシャフトＤａｉｍｌｅｒ ＡＧ 冷凍サイクルシステム
DE112017002560B4 (de) 2016-05-19 2023-10-19 Denso Corporation Kälteenergiespeicherverdampfer und Fahrzeugkältekreislaufvorrichtung, die mit diesem versehen ist
JP6579050B2 (ja) * 2016-07-08 2019-09-25 株式会社デンソー 蓄冷熱交換器、空調ユニット
JP6699507B2 (ja) 2016-10-24 2020-05-27 株式会社デンソー 空調装置
JP2018090109A (ja) * 2016-12-05 2018-06-14 株式会社デンソー 蒸発器
IT201900010215A1 (it) * 2019-06-26 2020-12-26 Mta Spa Dispositivo essiccatore per il trattamento di gas, in particolare aria
DE202019105225U1 (de) * 2019-09-20 2020-12-22 Akg Verwaltungsgesellschaft Mbh Wärmeaustauscher

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5833097A (ja) * 1981-08-21 1983-02-26 Hitachi Ltd 蓄熱装置
JP2003080933A (ja) * 2001-09-13 2003-03-19 Denso Corp 車両用空調装置
JP2004069126A (ja) * 2002-08-05 2004-03-04 Inoac Corp 蓄冷剤容器
JP2010091250A (ja) * 2008-09-12 2010-04-22 Denso Corp 蓄冷熱交換器
JP2010234837A (ja) * 2009-03-30 2010-10-21 Nissan Motor Co Ltd 車両用空調装置

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06234967A (ja) * 1993-02-09 1994-08-23 Nippon Petrochem Co Ltd 蓄冷熱剤
US20030131623A1 (en) * 2001-09-05 2003-07-17 Suppes Galen J. Heat pump using phase change materials
FR2847973B1 (fr) * 2002-11-29 2006-01-27 Valeo Climatisation Echangeur de chaleur a inertie thermique pour circuit de fluide caloporteur, notamment de vehicule automobile.
FR2861166B1 (fr) * 2003-10-21 2006-11-24 Valeo Climatisation Echangeur de chaleur utilisant un fluide d'accumulation
FR2945859B1 (fr) * 2009-05-19 2011-06-17 Valeo Systemes Thermiques Dispositif d'echange thermique contenant un materiau de stockage thermique
JP5408017B2 (ja) * 2009-06-05 2014-02-05 株式会社デンソー 蓄冷熱交換器
US9150081B2 (en) * 2009-06-10 2015-10-06 Delphi Technologies, Inc. Evaporator phase change thermal siphon
US20120042687A1 (en) * 2010-08-23 2012-02-23 Showa Denko K.K. Evaporator with cool storage function

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5833097A (ja) * 1981-08-21 1983-02-26 Hitachi Ltd 蓄熱装置
JP2003080933A (ja) * 2001-09-13 2003-03-19 Denso Corp 車両用空調装置
JP2004069126A (ja) * 2002-08-05 2004-03-04 Inoac Corp 蓄冷剤容器
JP2010091250A (ja) * 2008-09-12 2010-04-22 Denso Corp 蓄冷熱交換器
JP2010234837A (ja) * 2009-03-30 2010-10-21 Nissan Motor Co Ltd 車両用空調装置

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015137807A (ja) * 2014-01-22 2015-07-30 株式会社デンソー 蓄冷熱交換器
CN106255861A (zh) * 2014-05-23 2016-12-21 株式会社电装 热交换器
EP3147617A4 (fr) * 2014-05-23 2017-06-21 Denso Corporation Échangeur de chaleur
CN106255861B (zh) * 2014-05-23 2018-01-09 株式会社电装 热交换器
WO2016174852A1 (fr) * 2015-04-30 2016-11-03 株式会社デンソー Evaporateur
JP2016211837A (ja) * 2015-04-30 2016-12-15 株式会社デンソー 蒸発器
US10677537B2 (en) 2015-04-30 2020-06-09 Denso Corporation Evaporator
CN107532861A (zh) * 2015-04-30 2018-01-02 株式会社电装 蒸发器
JPWO2017208760A1 (ja) * 2016-06-01 2018-10-18 株式会社デンソー 蓄冷熱交換器
CN109070697A (zh) * 2016-06-01 2018-12-21 株式会社电装 蓄冷热交换器
WO2017208760A1 (fr) * 2016-06-01 2017-12-07 株式会社デンソー Échangeur de chaleur régénératif
US11073342B2 (en) 2016-06-01 2021-07-27 Denso Corporation Regenerative heat exchanger
CN109405616A (zh) * 2018-11-01 2019-03-01 扬州大学 一种相变储能套管式地热换热器
CN109405616B (zh) * 2018-11-01 2020-03-31 扬州大学 一种相变储能套管式地热换热器
CN110605953A (zh) * 2018-11-11 2019-12-24 南京酷朗电子有限公司 快速置换式储能模块
CN110605953B (zh) * 2018-11-11 2020-10-30 南京酷朗电子有限公司 快速置换式储能方法

Also Published As

Publication number Publication date
US20150168047A1 (en) 2015-06-18
JP2013256262A (ja) 2013-12-26

Similar Documents

Publication Publication Date Title
WO2013186983A1 (fr) Echangeur de chaleur à stockage de froid
JP5444782B2 (ja) 蓄冷熱交換器
CN102264564B (zh) 带蓄冷功能的蒸发器
JP6281394B2 (ja) 蓄冷熱交換器
WO2010150774A1 (fr) Évaporateur avec fonction de stockage de froid
US9109841B2 (en) Air to refrigerant heat exchanger with phase change material
JP5276954B2 (ja) 蓄冷機能付きエバポレータ
JP5274175B2 (ja) 蓄冷熱交換器
JP5764335B2 (ja) 蓄冷機能付きエバポレータ
JP6183100B2 (ja) 蓄冷熱交換器
WO2014030306A1 (fr) Échangeur de chaleur à stockage de froid
CN105452793A (zh) 用于热交换束的具有相变材料的容器的管道，特别是用于车辆的空调系统的蒸发器
JP2011051393A (ja) 蓄冷熱交換器およびその製造方法
JP5552309B2 (ja) 蓄冷機能付きエバポレータ
KR101611694B1 (ko) 관-핀 축열 증발기
JP2012126149A (ja) 蓄冷機能付きエバポレータ
JP6658885B2 (ja) 蓄冷熱交換器
JP6206209B2 (ja) 蓄冷熱交換器
JP2010243066A (ja) 蓄冷熱交換器
JP6573030B2 (ja) 蓄冷熱交換器
JP2014034037A (ja) 蓄冷熱交換器およびその製造方法
JP6214242B2 (ja) 熱交換器
JP2013200073A (ja) 蓄冷機能付きエバポレータ
JP6126361B2 (ja) 蓄冷機能付き空気冷却器
JP6327386B2 (ja) 蓄冷熱交換器

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 13803492

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 14407844

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 13803492

Country of ref document: EP

Kind code of ref document: A1