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WO2018008298A1 - Échangeur de chaleur à accumulation de froid - Google Patents

Échangeur de chaleur à accumulation de froid Download PDF

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Publication number
WO2018008298A1
WO2018008298A1 PCT/JP2017/020241 JP2017020241W WO2018008298A1 WO 2018008298 A1 WO2018008298 A1 WO 2018008298A1 JP 2017020241 W JP2017020241 W JP 2017020241W WO 2018008298 A1 WO2018008298 A1 WO 2018008298A1
Authority
WO
WIPO (PCT)
Prior art keywords
air
blower
region
storage material
cold storage
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2017/020241
Other languages
English (en)
Japanese (ja)
Inventor
山田　淳司
西田　伸
太田　貴之
貴志 檀上
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
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 Denso Corp filed Critical Denso Corp
Publication of WO2018008298A1 publication Critical patent/WO2018008298A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • 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
    • 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
    • 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
    • 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

  • This disclosure relates to a cold storage heat exchanger.
  • a cooling storage heat exchanger in which a cooling storage material is uniformly added to a cooling heat exchanger (For example, refer to Patent Document 1).
  • This vehicle air conditioner can cool the regenerator material while the vehicle is running, and can continue cooling by dissipating heat from the regenerator material during idle stop of the vehicle.
  • the vehicle air conditioner includes a blower 50, an evaporator 40 disposed on the air flow downstream side of the blower 50, and a heater core 60 disposed on the air flow downstream side of the evaporator 40. And an air conditioning case 70 for storing these.
  • the air blown from the blower 50 is cooled by the evaporator 40, then heated by the heater core 60, and the temperature-adjusted air is blown out from the air outlet 71 provided in the air conditioning case 70.
  • a step 70a is formed in the air conditioning case 70 so that the pressure loss of the air flowing into the part of the evaporator 40 away from the blower 50 is increased, and the air volume distribution of the air flowing out of the evaporator 40 is made uniform.
  • the cooling performance is degraded in such a configuration that the pressure loss of the air flowing into the evaporator 40 is increased.
  • the air flow path of the air conditioning case is divided into left and right sides, and the left and right independent control for independently controlling the temperature of the air blown from the right air flow channel and the left air flow channel, respectively.
  • a temperature control type vehicle air conditioner There is a temperature control type vehicle air conditioner.
  • This disclosure is intended to provide a more comfortable cooling feeling.
  • a plurality of refrigerant tubes arranged in one direction, fins disposed in an air passage formed between the plurality of refrigerant tubes, and a plurality of refrigerant tubes are formed.
  • a regenerator container that houses the regenerator material, and the core part is a first unit in which the ratio of the number of regenerator containers to the number of refrigerant tubes is a predetermined ratio.
  • a second region in which the ratio of the number of cold storage material containers to the number of refrigerant tubes is less than a predetermined ratio.
  • the core portion has a first region in which the ratio of the number of regenerator containers to the number of refrigerant tubes is a predetermined ratio, and the ratio of the number of regenerator containers to the number of refrigerant tubes is less than a predetermined ratio. And a second region.
  • FIG. 3 is a left side view of FIG. 2.
  • FIG. 4 is an enlarged sectional view showing a part of the IV-IV section of FIG. 2.
  • FIG. 5 is an enlarged cross-sectional view showing a part of a VV cross section of FIG. 3. It is a figure showing the result of having evaluated each temperature change of the rough side and dense side of a cool storage material container. It is a layout figure of the vehicle air conditioner of 2nd Embodiment.
  • FIG. 1 is a block diagram illustrating a configuration of a refrigeration cycle apparatus using a cold storage heat exchanger according to the first embodiment of the present disclosure.
  • the refrigeration cycle apparatus 1 is used in a vehicle air conditioner.
  • the refrigeration cycle apparatus 1 includes a compressor 10, a radiator 20, a decompressor 30, and an evaporator 40. These components are connected in an annular shape by piping and constitute a refrigerant circulation path.
  • the compressor 10 is driven by an internal combustion engine that is a power source 2 for traveling the vehicle. For this reason, when the power source 2 stops, the compressor 10 also stops.
  • the compressor 10 sucks the refrigerant from the evaporator 40, compresses it, and discharges it to the radiator 20.
  • the radiator 20 cools the high-temperature refrigerant.
  • the radiator 20 is also called a condenser.
  • the decompressor 30 decompresses the refrigerant cooled by the radiator 20.
  • the decompressor 30 can be provided by a fixed throttle, a temperature expansion valve, or an ejector.
  • the evaporator 40 evaporates the refrigerant decompressed by the decompressor 30 and cools the medium.
  • the evaporator 40 cools the air supplied to the passenger compartment.
  • the refrigeration cycle apparatus 1 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 that stores excess refrigerant.
  • the power source 2 can be provided by an internal combustion engine or an electric motor.
  • FIG. 2 is a layout diagram of the vehicle air conditioner of the present embodiment.
  • the vehicle air conditioner includes a blower 50 for blowing air, an evaporator 40 disposed on the downstream side of the air flow of the blower 50, and a heater core disposed on the downstream side of the air flow of the evaporator 40. 60 and an air-conditioning case 70 for storing these components.
  • the blower 50 corresponds to a blower.
  • the evaporator 40 of this embodiment functions as a cold storage heat exchanger.
  • the air blown from the blower 50 is cooled by the evaporator 40, heated by the heater core 60, and the temperature-adjusted air is blown out from the air outlet 71 provided in the air conditioning case 70.
  • the direction of the air blown from the blower 50 is changed to the core part 400 side at a part away from the blower 50, and the part away from the blower 50 is more core than the part near the blower 50.
  • the air volume flowing into the section 400 is configured to increase.
  • FIG. 3 is an arrow view of the evaporator 40 as seen from the direction of arrow III in FIG.
  • FIG. 4 is a left side view of FIG.
  • FIG. 5 is an enlarged cross-sectional view showing a part of the VV cross section of FIG.
  • FIG. 6 is an enlarged cross-sectional view showing a part of the VI-VI cross section of FIG. 5 and 6 are enlarged cross-sectional views of a portion where one cold storage material container 47 is arranged for two refrigerant tubes 45.
  • FIG. Moreover, the arrow which shows the up-down, left-right, and front-back in FIG. 2, FIG. 3 represents the direction of the vehicle which mounts a vehicle air conditioner.
  • the evaporator 40 has a refrigerant passage member branched into a plurality of parts.
  • the refrigerant passage member is provided by a metal passage member such as aluminum.
  • the refrigerant passage member is provided by headers 41, 42, 43, 44 positioned in a pair, and a plurality of refrigerant tubes 45 connecting the headers.
  • 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 41, 42 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 43, 44 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 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 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 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 as a refrigerant outlet is provided at the end of the third header 43.
  • the inside of the third header 43 is partitioned into a first partition and a second partition by a partition plate 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 10.
  • the refrigerant pipe 45 is a multi-hole pipe having a plurality of refrigerant passages therein.
  • 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 extend along the longitudinal direction of the refrigerant pipe 45 and open to both ends of the refrigerant pipe 45.
  • the plurality of refrigerant tubes 45 are arranged in a row. In each 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 for exchanging heat with air between two adjacent refrigerant tubes 45 and an accommodating portion for accommodating a cold storage material container 47 described later.
  • the evaporator 40 includes a plurality of refrigerant tubes 45, fins 46 disposed in an air passage formed between the plurality of refrigerant tubes 45, and a cold storage material disposed in an air passage formed between the plurality of refrigerant tubes 45.
  • the core part 400 which has the cool storage material container 47 which accommodates 80 is provided.
  • the fins 46 are for increasing the contact area with the air supplied to the passenger compartment.
  • the fins 46 are constituted by corrugated fins 46.
  • the fins 46 are arranged in an air passage formed 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 called a louver.
  • the evaporator 40 further has a plurality of cold storage material containers 47.
  • the cold storage material container 47 is made of metal such as aluminum.
  • the cold storage material container 47 has a flat cylindrical shape.
  • the cold storage material container 47 is closed by squeezing the cylinder in the thickness direction at both ends in the longitudinal direction, thereby defining a room for accommodating the cold storage material 80 therein.
  • the cool storage material 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.
  • the cold storage material container 47 is disposed in an air passage formed between two adjacent refrigerant pipes 45.
  • the cool storage material container 47 is thermally coupled to two refrigerant tubes 45 disposed on both sides thereof.
  • the cool storage material 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 material container 47 is brazed to the refrigerant pipe.
  • a large amount of brazing material is disposed between the cold storage material 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 material foil between the cold storage material container 47 and the refrigerant pipe 45. As a result, the cool storage material container 47 exhibits good heat conduction with the refrigerant pipe 45.
  • the thickness T of the cold storage material container 47 is substantially equal to the thickness of the air passage. Therefore, the thickness T of the cold storage material container 47 is substantially equal to the thickness of the fin 46.
  • the thickness T of the cool storage material container 47 is clearly larger than the thickness of the refrigerant pipe 45. This configuration is effective for accommodating a large amount of the cold storage material 80.
  • the cold storage material container 47 has substantially the same length L as the fins 46. As a result, the cool storage material container 47 occupies substantially the entire longitudinal direction of the accommodating portion partitioned between the two adjacent refrigerant tubes 45.
  • the gap between the cold storage material container 47 and the headers 41, 42, 43, 44 is preferably filled with a piece of fin 46 or a filler such as resin.
  • the cold storage material container 47 has an outer shell 47a that provides the outer surface thereof and a plurality of inner pillars 47b.
  • the inner pillar 47b extends from the main wall toward the interior of the room that houses the cold storage material 80.
  • the inner pillar 47 b connects between the two large main walls of the cold storage material container 47.
  • the inner pillar 47 b extends along the longitudinal direction of the cold storage material container 47.
  • the plurality of inner pillars 47b divide the room in the cool storage material container 47 into a plurality of small rooms arranged along the air flow direction. These small rooms communicate with each other at both ends of the cold storage material container 47.
  • the cool storage material 80 is accommodated in the plurality of rooms.
  • the sectional area of each small chamber is sufficiently larger than the refrigerant passage in the refrigerant pipe 45.
  • the plurality of refrigerant tubes 45 are arranged in one direction 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 material containers 47 are arranged in the plurality of gaps.
  • the cool storage material container 47 has a larger ventilation resistance than the fins 46. Therefore, when the cool storage material container 47 in which the cool storage material 80 is stored in the gap between the two refrigerant tubes 45 is disposed, the ventilation resistance becomes larger than when the fins 46 are disposed in the gap between the two refrigerant tubes 45.
  • the air volume of the air blown from the blower 50 is higher in the right part away from the blower 50 than in the left part near the blower 50 in the core part 400. Many wind speeds are also fast.
  • the air volume refers to the flow rate of air per unit area.
  • the vehicle air conditioner of the present embodiment does not form a step in the air conditioning case 70 in order to make the air volume distribution of the air flowing out from the evaporator 40 uniform, but between the refrigerant pipes 45 in the evaporator 40.
  • the ratio of the cold storage material containers 47 to be arranged is uneven on the left and right of the evaporator 40.
  • the regenerator container 47 is concentrated in the right region away from the blower 50 and where the amount of air blown from the blower 50 is large. Is arranged. Therefore, in FIG. 3, the cool storage material container 47 is roughly arranged in the left region where the wind speed is slow, and the cool storage material container 47 is densely arranged in the right region where the wind speed is fast.
  • the core part 400 of the evaporator 40 of the present embodiment includes the first region A in which the ratio of the number of the regenerator containers 47 to the number of the refrigerant tubes 45 is a predetermined ratio, and the regenerator material for the number of the refrigerant tubes 45.
  • the ratio of the number of the cold storage material containers 47 to the number of the refrigerant tubes 45 is 5/22.
  • one cold storage material container 47 is arranged for two refrigerant pipes 45 and one cold storage material container 47 is arranged for six refrigerant pipes 45. There are some parts.
  • the ratio of the number of the cold storage material containers 47 to the number of the refrigerant tubes 45 is 4/22.
  • one cold storage material container 47 is arranged for the six refrigerant tubes 45.
  • the air flow distribution of the air flowing out from the evaporator 40 is made uniform without forming a step in the air conditioning case 70, and a uniform velocity distribution can be obtained.
  • FIG. 7 shows the result of evaluating each temperature change on the rough side of the cool storage material container 47 and the dense side of the cool storage material container 47 when the compressor 10 is turned on after a predetermined period of time after the compressor 10 was turned off. Is. Evaluation was performed by arranging temperature sensors at the air outlets 71 on the downstream side of the air flow on the rough side of the cold storage material container 47 and on the dense side of the cold storage material container 47, respectively.
  • the temperatures on the rough side of the cold storage material container 47 and the dense side of the cold storage material container 47 are about 1 ° C. For this reason, low-temperature air is blown into the vehicle interior from the air outlet 71 located on the air flow downstream side of the coarse side of the cold storage material container 47 and the dense side of the cold storage material container 47.
  • the temperatures on the rough side of the cold storage material container 47 and the dense side of the cold storage material container 47 gradually increase in the same manner.
  • the respective temperature rise widths on the rough side of the cold storage material container 47 and the dense side of the cold storage material container 47 are reduced from above about 12 ° C., respectively.
  • the temperature rise becomes smaller after the temperature exceeds 12 ° C. because of the effect of allowing the cool storage material 80 to cool.
  • the temperature of the second region B on the coarse side of the cool storage material container 47 is slightly higher than the temperature on the dense side of the cool storage material container 47.
  • the evaporator 40 of the present embodiment is arranged so that the cool storage material containers 47 are not uniform on the left and right, but the cool storage material containers 47 are also in the second region B where the cool storage material containers 47 are rough. It has been found that the cooling performance can be obtained in the same manner as in the first region A in which is dense.
  • the refrigerant in the core part 400 is kept constant in a low pressure state by the cold storage material 80, and the cooling performance of the evaporator 40 is the core part. This is considered to be uniform within 400.
  • the entire evaporator 40 is kept at a low temperature and the entire evaporator 40 is kept at a low temperature by the cool storage material 80. Even in the second region B where the temperature becomes rough, it is considered that the same cooling performance as that in the first region A where the cool storage material container 47 is dense can be obtained.
  • the core unit 400 includes the first region A in which the ratio of the number of the regenerator containers 47 to the number of the refrigerant tubes 45 is a predetermined ratio, and the number of the regenerator containers 47 relative to the number of the refrigerant tubes 45.
  • the core part 400 cools the air sent from the blower 50 provided in the air-conditioning case 70, and the 1st area
  • the direction of the air blown from the blower 50 is changed to the core part 400 at a part away from the blower 50, and the part away from the blower 50 is closer to the core part than the part near the blower 50.
  • the air volume of the air that flows in is increased.
  • the region A in which the ratio of the number of the cold storage material containers 47 to the number of the refrigerant tubes 45 is a predetermined ratio is formed in a part away from the blower 50.
  • the vehicle air conditioner having the air conditioning case 70 configured to increase the air volume of the air flowing into the core portion in the part far from the blower 50 than in the part close to the blower 50, it flows out of the evaporator 40. It is possible to make the air volume distribution of the air uniform.
  • FIG. 8 is a layout diagram of the vehicle air conditioner of the present embodiment.
  • FIG. 9 is an arrow view of the evaporator 40 as a cold storage heat exchanger as seen from the direction of the arrow IX in FIG.
  • the air flow path 72 of the air conditioning case 70 is divided into left and right portions by a partition plate 73, from a right air passage 72 a located on the right side of the partition plate 73 and a left air passage 72 b located on the left side of the partition plate 73.
  • the temperature of the blown air that is blown out is controlled independently.
  • the vehicle air conditioner independently controls the temperature of the air flowing out from the air outlet provided on the driver's seat side in the passenger compartment and the air flowing out from the air outlet provided on the passenger seat side. It is configured as a vehicle type air conditioner.
  • the right air passage 72a is connected to an air outlet (not shown) provided on the driver's seat side of the vehicle via a duct
  • the left air passage 72b is an air outlet (not shown) provided on the passenger seat side of the vehicle. And connected through a duct.
  • the evaporator 40 and the heater core 60 are housed in the air conditioning case 70 so as to straddle the right air passage 72a and the left air passage 72b, respectively.
  • the first region A in which the ratio of the number of the regenerator containers 47 to the number of the refrigerant tubes 45 is a predetermined ratio is provided in the left air passage 72b that communicates with the air outlet provided on the passenger seat side. Is arranged. Specifically, in the region A, seven cold storage material containers 47 are arranged for the 22 refrigerant tubes 45. Therefore, the ratio of the number of the cold storage material containers 47 to the number of the refrigerant tubes 45 is 7/22.
  • the regenerator container 47 is not disposed in a portion of the core portion 400 that is located in the right air passage 72a that communicates with the air outlet provided on the driver's seat side.
  • the maximum cooling performance on the driver's seat side, which is frequently used, is ensured by not arranging the cool storage material container 47 in the region located in the right air passage 72a.
  • the cool storage material container 47 is not arranged in the region B located in the right air passage 72a communicating with the air outlet provided on the driver's seat side, the cooling performance on the driver's seat side at the time of idling stop is lowered. There is a concern to do.
  • the evaporator 40 is provided by the cool storage material 80 stored in the cool storage material container 47 disposed in the left air passage 72b that communicates with the air outlet provided on the passenger seat side. Since the whole is kept at a low temperature, a cooling feeling can be obtained on the driver's seat as well as on the passenger's seat.
  • FIG. 10 is a diagram showing the relationship between the cooling performance of the evaporator 40 and the cold storage material container occupancy rate in the core unit 400.
  • the cooling performance of the evaporator 40 is the maximum cooling performance.
  • the ratio of the number of the regenerator containers 47 to the number of the refrigerant tubes 45 increases, the number of the fins 46 decreases, so that the contact area between the fins 46 and the air decreases and the cooling performance decreases. That is, by eliminating the cold storage material container 47 disposed in the left air passage 72b communicating with the air outlet provided on the driver's seat side, it is possible to suppress a decrease in the cooling performance on the driver's seat side.
  • the region A in which the ratio of the number of the regenerator containers 47 to the number of the refrigerant tubes 45 is a predetermined ratio is the blower provided on the passenger seat side. It arrange
  • FIG. 11 is an arrow view of the evaporator 40 as a cold storage heat exchanger viewed from the direction of the arrow IX in FIG.
  • the layout of the vehicle air conditioner of this embodiment is the same as that shown in FIG.
  • the regenerator container 47 is disposed at a predetermined ratio in a portion of the core portion 400 that is located in the left air passage 72b that communicates with the air outlet on the passenger seat side.
  • the cool storage material container 47 is not disposed in a portion located in the right air passage 72a communicating with the seat-side air outlet.
  • the regenerative heat exchanger of the present embodiment includes a right air passage that communicates with a portion of the core portion 400 that is located in the left air passage 72b that communicates with the air outlet on the passenger seat side and the air outlet on the driver seat side.
  • the cool storage material containers 47 are arranged in both of the parts located at 72a.
  • the ratio of the number of the regenerator containers to the number of the refrigerant tubes 45 is smaller in the region B than in the region A.
  • a region A in which the ratio of the number of the cold storage material containers 47 to the number of the refrigerant tubes 45 is arranged at a predetermined ratio is arranged in the left air passage 72b that communicates with the air outlet provided on the passenger seat side in the core portion 400.
  • the ratio of the number of the cold storage material containers 47 to the number of the refrigerant tubes 45 is 7/22.
  • the region A in which the ratio of the number of the regenerator containers 47 to the number of the refrigerant tubes 45 is a predetermined ratio is arranged in the air passage 72b for flowing air to the air outlet on the passenger seat side. Furthermore, the 2nd area
  • the region A in which the ratio of the number of the regenerator containers 47 to the number of the refrigerant tubes 45 is a predetermined ratio is the blower provided on the passenger seat side. It arrange
  • the region B in which the ratio of the number of the regenerator containers 47 to the number of the refrigerant tubes 45 is smaller than a predetermined ratio is arranged in the air passage 72a for flowing air to the air outlet provided on the driver's seat side.
  • the maximum cooling performance on the driver's seat side is lower than that in the second embodiment, not only the cool storage material 80 stored in the cool storage material container 47 provided in the area A on the passenger seat side, but also the driving Since the entire evaporator 40 is kept at a low temperature by the cool storage material 80 housed in the cool storage material container 47 provided in the seat-side region B, the cool storage performance can be improved.
  • FIG. 12 is an arrow view of the evaporator 40 as a cold storage heat exchanger viewed from the direction of arrow III in FIG.
  • the first embodiment as shown in FIG. 2, in the core portion 400 of the evaporator 40, the right side region A in which the wind speed is faster is higher in the refrigerant tube 45 than the left side region B in which the wind speed is slow.
  • the ratio of the number of the cool storage material containers 47 to the number is increasing.
  • the right region B where the wind speed is fast is higher than the left region A where the wind speed is slow.
  • the ratio of the number of the cool storage material containers 47 to the number of is reduced.
  • the first region A is arranged in the right region where the wind speed is fast
  • the second region B is arranged in the left region where the wind speed is slow.
  • Region B is arranged, and region A is arranged in the left region where the wind speed is slow.
  • the left region where the wind speed is slow has a smaller amount of heat exchange than the right region where the wind speed is fast, and therefore contributes less to the cooling performance. That is, if the cool storage material container 47 is concentrated and arranged in the right region where the wind speed is fast, the cooling performance is greatly reduced. However, if the cool storage material container 47 is concentrated and placed in the left region where the wind speed is slow, the cooling performance is reduced. The degree of decrease is small.
  • the region A in which the cool storage material containers 47 are concentrated and arranged in the left region where the amount of heat exchange is small the degree of deterioration of the cooling performance of the entire evaporator 40 can be reduced.
  • the direction of the air blown from the blower 50 is changed to the core part 400 at a part away from the blower 50, and the part away from the blower 50 is closer to the core part than the part near the blower 50.
  • the air volume of the air that flows in is increased.
  • the region B in which the ratio of the number of the regenerator containers 47 to the number of the refrigerant tubes 45 is small is formed in a portion close to the blower 50. Therefore, the degree of deterioration of the cooling performance of the entire evaporator 40 can be reduced.
  • the vehicle air conditioner having the air conditioning case 70 configured such that the air volume flowing into the core portion 400 is larger in the part away from the blower 50 than in the part near the blower 50.
  • the present disclosure can also be applied to a vehicle air conditioner having a configuration different from that of the air conditioning case 70.
  • the plurality of refrigerant tubes arranged in one direction and the fins arranged in the air passage formed between the plurality of refrigerant tubes.
  • a cold storage material container that houses the cold storage material and is disposed in an air passage formed between the plurality of refrigerant tubes.
  • the core portion includes a first region in which a ratio of the number of cold storage material containers to the number of refrigerant tubes is a predetermined ratio, and a second ratio in which the ratio of the number of cold storage material containers to the number of refrigerant tubes is less than a predetermined ratio. And a region.
  • a core part cools the air ventilated from the air blower provided in the air-conditioning case, and the 1st area
  • a core part cools the air ventilated from the air blower provided in the air-conditioning case, and the 1st area
  • the region where the air volume is low and the air velocity is low has a small contribution to the cooling performance because the amount of heat exchange is less than the region where the air volume is high and the air velocity is high. That is, if the cool storage container is concentrated in the right area where the wind speed is fast, the cooling performance is greatly reduced, but if the cool storage container is concentrated in the left area where the wind speed is slow, the cooling performance is degraded. The degree of is small. Therefore, by arranging the region A in which the cool storage material containers 47 are concentrated and arranged in the left region where the air volume is small and the heat exchange amount is small, the degree of deterioration of the cooling performance of the entire evaporator can be reduced.
  • the direction of the air ventilated from a blower changes to the core part side in the site
  • the first area is formed in a part away from the blower. Therefore, it is possible to make the air volume distribution of the air flowing out of the evaporator uniform.
  • the air-conditioning case has a direction in which the direction of air blown from the blower is changed to the core side at a portion away from the blower, and the portion away from the blower is more core than the portion near the blower.
  • the first area is formed in a portion close to the blower. Therefore, in a vehicle air conditioner having an air conditioning case configured so that the air volume flowing into the core portion is greater in the part away from the fan than in the part close to the fan, the air volume distribution of the air flowing out from the evaporator Can be made uniform.
  • the independent temperature for independently controlling the temperature of the air flowing out from the air outlet provided on the driver seat side in the passenger compartment and the air flowing out from the air outlet provided on the passenger seat side. It is used for a control-type vehicle air conditioner, and in the core portion, the first area is arranged in an air passage that allows air to flow to the air outlet provided on the passenger seat side, and the second area is on the driver seat side. It arrange

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

Abstract

Un échangeur de chaleur à accumulation de froid est équipé d'une unité centrale (400) qui comporte les éléments suivants : une pluralité de tuyaux de fluide frigorigène (45) alignés dans un sens; des ailettes (46) disposés dans des passages d'air formés entre la pluralité de tuyaux de fluide frigorigène; et des contenants de matériau de stockage de froid (47) recevant un matériau de stockage de froid sont disposés dans les passages d'air formés entre la pluralité de tuyaux de liquide frigorigène. L'unité centrale comporte une première région (A) dans laquelle le rapport entre le nombre de contenants de matériau de stockage de froid et le nombre de tuyaux de réfrigérant est réglé pour être égal au rapport prescrit, et une seconde région (B) dans laquelle le rapport entre le nombre de contenants de matériau de stockage de froid et le nombre de tuyaux de réfrigérant est inférieur au rapport prescrit.
PCT/JP2017/020241 2016-07-08 2017-05-31 Échangeur de chaleur à accumulation de froid Ceased WO2018008298A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-136169 2016-07-08
JP2016136169A JP2019147398A (ja) 2016-07-08 2016-07-08 蓄冷熱交換器

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WO2018008298A1 true WO2018008298A1 (fr) 2018-01-11

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JP (1) JP2019147398A (fr)
WO (1) WO2018008298A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09123748A (ja) * 1994-09-22 1997-05-13 Denso Corp 自動車用空調装置
JP2002370526A (ja) * 2001-06-15 2002-12-24 Denso Corp 車両用空調装置
JP2006503253A (ja) * 2002-10-10 2006-01-26 ベール ゲーエムベーハー ウント コー カーゲー 冷媒蒸発器
JP2010091250A (ja) * 2008-09-12 2010-04-22 Denso Corp 蓄冷熱交換器
JP2013124050A (ja) * 2011-12-15 2013-06-24 Denso Corp 車両用空調装置
US20130248166A1 (en) * 2012-03-21 2013-09-26 Delphi Technologies, Inc. Phase change material evaporator charging control
JP2014098528A (ja) * 2012-11-15 2014-05-29 Japan Climate Systems Corp 蓄冷機能付きエバポレータ

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH09123748A (ja) * 1994-09-22 1997-05-13 Denso Corp 自動車用空調装置
JP2002370526A (ja) * 2001-06-15 2002-12-24 Denso Corp 車両用空調装置
JP2006503253A (ja) * 2002-10-10 2006-01-26 ベール ゲーエムベーハー ウント コー カーゲー 冷媒蒸発器
JP2010091250A (ja) * 2008-09-12 2010-04-22 Denso Corp 蓄冷熱交換器
JP2013124050A (ja) * 2011-12-15 2013-06-24 Denso Corp 車両用空調装置
US20130248166A1 (en) * 2012-03-21 2013-09-26 Delphi Technologies, Inc. Phase change material evaporator charging control
JP2014098528A (ja) * 2012-11-15 2014-05-29 Japan Climate Systems Corp 蓄冷機能付きエバポレータ

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