WO2017057174A1 - Échangeur de chaleur à accumulation de froid - Google Patents

Échangeur de chaleur à accumulation de froid Download PDF

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Publication number
WO2017057174A1
WO2017057174A1 PCT/JP2016/077976 JP2016077976W WO2017057174A1 WO 2017057174 A1 WO2017057174 A1 WO 2017057174A1 JP 2016077976 W JP2016077976 W JP 2016077976W WO 2017057174 A1 WO2017057174 A1 WO 2017057174A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
refrigerant pipe
cold storage
joined
storage material
Prior art date
Application number
PCT/JP2016/077976
Other languages
English (en)
Japanese (ja)
Inventor
淳 安部井
聡也 長沢
鳥越　栄一
直久 石坂
河地　典秀
佑輔 鬼頭
西村　健
長屋　誠一
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
Priority claimed from JP2016173410A external-priority patent/JP6409836B2/ja
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Priority to DE112016004451.8T priority Critical patent/DE112016004451B8/de
Priority to CN201680057193.1A priority patent/CN108139173B/zh
Priority to US15/765,101 priority patent/US10696128B2/en
Publication of WO2017057174A1 publication Critical patent/WO2017057174A1/fr

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    • 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
    • B60H1/00321—Heat exchangers for air-conditioning devices
    • B60H1/00335—Heat exchangers for air-conditioning devices of the gas-air type
    • 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
    • B60H1/3204—Cooling devices using compression
    • B60H1/3227—Cooling devices using compression characterised by the arrangement or the type of heat exchanger, e.g. condenser, evaporator
    • 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
    • B60H1/00492—Heating, cooling or ventilating [HVAC] devices comprising regenerative heating or cooling means, e.g. heat accumulators
    • B60H1/005—Regenerative cooling means, e.g. cold accumulators
    • 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
    • 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
    • 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 compressor that compresses and discharges a refrigerant, a radiator that cools a refrigerant that has reached a high temperature, and a refrigerating heat exchanger that forms a refrigeration cycle apparatus together with a decompressor that decompresses the cooled refrigerant and evaporates the refrigerant. .
  • 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 provide limited cooling during such a temporary stop, a cold storage heat exchanger in which a cold storage material is added to the evaporator of the refrigeration cycle apparatus has been proposed. For example, a cold storage heat exchanger described in Patent Document 1 is known.
  • a compressor for compressing and discharging the refrigerant is present on the downstream side of the refrigerant flow with respect to the cold storage heat exchanger.
  • the liquid refrigerant returns to the compressor, it causes a failure, and therefore it is generally necessary to completely evaporate the refrigerant at the outlet of the cold storage heat exchanger.
  • the regenerative heat exchanger there is a so-called superheat zone where the refrigerant temperature rapidly changes to a high temperature due to the refrigerant becoming a gas monolayer near the outlet of the refrigerant passage and the pressure exceeding the saturated vapor pressure. .
  • the regenerative heat exchanger may have an overheat zone at any location on the refrigerant passage.
  • This disclosure is intended to provide a cold storage heat exchanger that is less susceptible to the influence of the overheating region and can secure the cold storage performance even when the overheating region exists.
  • a cold storage heat exchanger includes a refrigerant passage through which a refrigerant is circulated, a plurality of refrigerant tubes arranged at intervals from each other, a cold storage material adjacent to the plurality of refrigerant tubes, A heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe to the cold storage material in an overheated region of the refrigerant generated in the refrigerant passage.
  • This configuration can suppress heat transfer from the refrigerant pipe to the regenerator material in the overheated region of the refrigerant generated in the refrigerant passage, so that the regenerator material is less likely to cool due to the influence of the overheated region where the refrigerant temperature becomes high. Can be avoided. As a result, even when the overheated region exists, it is difficult to be affected by the overheated region, and the cold storage performance can be secured.
  • FIG. 1 is a block diagram showing a configuration of a refrigeration cycle apparatus 1 using an evaporator as a cold storage heat exchanger according to the first embodiment.
  • FIG. 2 is a plan view of an evaporator as a cold storage heat exchanger in FIG.
  • FIG. 3 is a side view of the evaporator as the cold storage heat exchanger in FIG. 1.
  • FIG. 4 is a diagram schematically showing the flow of the refrigerant in the evaporator.
  • FIG. 5 is a schematic diagram in which the evaporator is disassembled into the windward and leeward sides in the air flow direction.
  • FIG. 6 is a plan view schematically illustrating the flow of the refrigerant in the evaporator.
  • FIG. 1 is a block diagram showing a configuration of a refrigeration cycle apparatus 1 using an evaporator as a cold storage heat exchanger according to the first embodiment.
  • FIG. 2 is a plan view of an evaporator as a cold storage heat exchanger in FIG.
  • FIG. 7 is a diagram showing the transition of the refrigerant temperature in the refrigerant passage in the evaporator.
  • 8 is a cross-sectional view taken along the line VIII-VIII in FIG. 3, and is a cross-sectional view of the cold storage material container, the refrigerant pipe, and the air passage.
  • FIG. 9 is a cross-sectional view schematically showing the shape of the inner fin that functions as a heat transfer suppressing portion.
  • 10 is a cross-sectional view taken along line A1-A1 in FIG.
  • FIG. 11 is a cross-sectional view schematically showing a modified example of the shape of the inner fin.
  • FIG. 12 is a cross-sectional view schematically showing a modification of the shape of the inner fin.
  • FIG. 13 is a diagram illustrating an example in which the flow of the refrigerant illustrated in FIG. 4 is different.
  • FIG. 14 is a schematic diagram in which the evaporator shown in FIG. 13 is disassembled into the windward and leeward sides in the air flow direction.
  • FIG. 15 is a plan view schematically showing the refrigerant flow of the evaporator shown in FIG.
  • FIG. 16 is a diagram showing the transition of the refrigerant temperature in the refrigerant passage in the evaporator shown in FIG.
  • FIG. 17 is a diagram showing an example in which the refrigerant flow shown in FIG. 4 is made different.
  • FIG. 18 is a diagram illustrating an example in which the flow of the refrigerant illustrated in FIG. 4 is varied.
  • FIG. 19 is a diagram showing an example in which the refrigerant flow shown in FIG. 4 is made different.
  • FIG. 20 is a diagram illustrating an example in which the flow of the refrigerant illustrated in FIG. 4 is different.
  • FIG. 21 is a cross-sectional view schematically illustrating the shape of a cold storage material container that functions as a heat transfer suppression unit in the evaporator according to the second embodiment. 22 is a cross-sectional view taken along line A2-A2 in FIG.
  • FIG. 23 is a cross-sectional view schematically showing a modification of the shape of the cool storage material container.
  • FIG. 24 is a cross-sectional view schematically showing the shape of a cold storage material container that functions as a heat transfer suppression unit in the evaporator according to the third embodiment.
  • FIG. 25 is a cross-sectional view taken along line A3-A3 in FIG.
  • FIG. 26 is a cross-sectional view schematically showing a modified example of the shape of the cool storage material container and the inner fin.
  • FIG. 27 is a cross-sectional view schematically showing the shape of the inner fin that functions as a heat transfer suppressing unit in the evaporator according to the fourth embodiment.
  • 28 is a cross-sectional view taken along line A4-A4 in FIG.
  • FIG. 29 is a cross-sectional view schematically showing the shape of a cold storage material container that functions as a heat transfer suppression unit in the evaporator according to the fifth embodiment.
  • 30 is a cross-sectional view taken along line A5-A5 in FIG. FIG.
  • FIG. 31 is a cross-sectional view schematically showing the shape of a cold storage material container that functions as a heat transfer suppression unit in the evaporator according to the sixth embodiment.
  • 32 is a cross-sectional view taken along line A6-A6 in FIG.
  • FIG. 33 is a diagram schematically showing a refrigerant flow in the evaporator according to the seventh embodiment.
  • FIG. 34 is a schematic diagram in which the evaporator shown in FIG. 33 is disassembled into the windward side and the leeward side in the air flow direction.
  • FIG. 35 is a plan view schematically showing the refrigerant flow of the evaporator shown in FIG. FIG.
  • FIG. 36 is a diagram schematically illustrating the refrigerant flow in the evaporator according to the comparative example of the seventh embodiment.
  • FIG. 37 is a schematic diagram in which the evaporator shown in FIG. 36 is disassembled into the windward and leeward sides in the air flow direction.
  • FIG. 38 is a plan view schematically showing the refrigerant flow of the evaporator shown in FIG.
  • FIG. 39 is a diagram schematically illustrating the refrigerant flow in the evaporator according to the modification of the seventh embodiment.
  • FIG. 40 is a plan view schematically showing the flow of refrigerant in the evaporator shown in FIG.
  • FIG. 41 is a diagram schematically illustrating the refrigerant flow in the evaporator according to the modification of the seventh embodiment.
  • FIG. 40 is a plan view schematically showing the flow of refrigerant in the evaporator shown in FIG.
  • FIG. 41 is a diagram schematically illustrating the refrigerant flow in the
  • FIG. 42 is a plan view schematically showing the refrigerant flow of the evaporator shown in FIG.
  • FIG. 43 is a cross-sectional view schematically showing the shape of the inner fin functioning as a heat transfer suppressing unit in the evaporator according to the eighth embodiment.
  • 44 is a cross-sectional view taken along line A7-A7 in FIG. 45 is a cross-sectional view along B7-B7 in FIG.
  • FIG. 46 is a cross-sectional view schematically showing the shape of a cold storage material container that functions as a heat transfer suppression unit in the evaporator according to the ninth embodiment.
  • 47 is a cross-sectional view taken along line A8-A8 in FIG. 48 is a cross-sectional view along B8-B8 in FIG.
  • FIG. 49 is a cross-sectional view schematically showing the shape of a cold storage material container that functions as a heat transfer suppression unit in the evaporator according to the tenth embodiment.
  • 50 is a cross-sectional view taken along line A9-A9 in FIG. 51 is a cross-sectional view along B9-B9 in FIG.
  • FIG. 52 is a plan view schematically showing a refrigerant flow in the evaporator according to the eleventh embodiment.
  • FIG. 53 is a plan view schematically showing a refrigerant flow in the evaporator according to the twelfth embodiment.
  • FIG. 54 is a plan view schematically showing a refrigerant flow in the evaporator according to the thirteenth embodiment.
  • FIG. 55 is a schematic diagram showing the internal configuration of the cool storage material container of the evaporator according to the fourteenth embodiment.
  • FIG. 56 is a diagram schematically showing the configuration of the cool storage material container of the evaporator according to the fifteenth embodiment.
  • the refrigeration cycle apparatus 1 is used in a vehicle air conditioner. As shown in FIG. 1, 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 cold storage heat exchanger according to the first embodiment is applied as the evaporator 40.
  • the cold storage heat exchanger 40 according to the present embodiment is also expressed as “evaporator 40”.
  • 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 heat 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.
  • the vertical direction on the paper surface of FIGS. 2 and 3 is represented as “the height direction”, the upper side thereof is represented as “upper side”, and the lower side is represented as “lower side”.
  • the height direction is typically the gravitational direction, but may be another direction.
  • the right and left direction on the paper surface of FIG. 2 is represented as “inflow direction” in which the refrigerant flows, the right side thereof is represented as “front side”, and the left side is represented as “back side”.
  • the left-right direction on the paper surface of FIG. 3 is represented as “flow direction” in which air flows through the air passage 53, the left side thereof is represented as “windward”, and the right side is represented as “leeward side”.
  • the evaporator 40 has a refrigerant passage member branched into a plurality.
  • the refrigerant passage member is provided by a metal passage member such as aluminum.
  • the refrigerant passage member is provided by a first header 41, a second header 42, a third header 43, a fourth header 44, which are positioned in a pair, and a plurality of refrigerant pipes 45 connecting the headers. Yes.
  • the first header 41, the second header 42, the third header 43, and the fourth header 44 are disposed so as to extend along the inflow direction.
  • the plurality of refrigerant tubes 45 are arranged so as to extend along a height direction orthogonal to the inflow direction.
  • the first header 41 and the second header 42 form a pair, and are arranged in parallel along the inflow direction, separated from each other by a predetermined distance in the height direction.
  • the third header 43 and the fourth header 44 also form a pair and are arranged in parallel along the inflow direction with a predetermined distance from each other in the height direction.
  • the first header 41 and the third header 43 are arranged on the upper side in the height direction, and the second header 42 and the fourth header 44 are arranged on the lower side in the height direction.
  • 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 first header 41 and second header 42 at one end thereof.
  • 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 third header 43 and fourth header 44 at the other 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 part 48 and a second heat exchange part 49 arranged in two layers.
  • the second heat exchanging part 49 is arranged on the leeward side
  • the first heat exchanging part 48 is arranged on the leeward side.
  • tube 45 is arrange
  • a joint as a refrigerant inlet is provided at the end of the first header 41 (the end on the near side in the inflow direction).
  • the inside of the first header 41 is partitioned into a first partition and a second partition by a partition plate provided at substantially the center in the length direction (inflow direction).
  • the plurality of refrigerant tubes 45 are divided into a first group G1 corresponding to the first section and a second group G2 corresponding to the second section.
  • 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 G1.
  • the refrigerant flows into the second header 42 through the first group G1 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 G2.
  • the refrigerant flows into the second section of the first header 41 through the second group G2.
  • a joint as a refrigerant outlet is provided at the end of the third header 43 (in this embodiment, the end on the near side in the inflow direction, but it may be the back end).
  • 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 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 plurality of refrigerant tubes 45 are divided into a third group G3 corresponding to the first section and a fourth group G4 corresponding to the second section.
  • 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 third group G3.
  • the refrigerant flows into the fourth header 44 through the third group G3 and is collected.
  • the refrigerant is distributed again from the fourth header 44 to the plurality of refrigerant tubes 45 belonging to the fourth group G4.
  • the refrigerant flows into the second section of the third header 43 through the fourth group G4.
  • 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 or a manufacturing method in which a plate is bent.
  • 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. As shown in FIG. 8, the plurality of refrigerant pipes 45 are accommodated between two adjacent refrigerant pipes 45 for accommodating an air passage 53 for exchanging heat with air and a cold storage material container 47 described later.
  • the section is divided.
  • the evaporator 40 includes fin members for increasing the contact area with the air supplied to the passenger compartment.
  • the fin member is provided by a plurality of corrugated fins 46.
  • the fins 46 are disposed in an air passage 53 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 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 cool storage material container 47 divides a room for accommodating the cool storage material 50 inside by combining two middle plates.
  • 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 cool storage material container 47 is disposed between two adjacent refrigerant tubes 45.
  • the cold storage material container 47 is disposed between two refrigerant pipes 45 adjacent to each other along the inflow direction.
  • 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 45.
  • a 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 using a material clad with the brazing material or by arranging a brazing material foil between the cold storage material container 47 and the refrigerant pipe 45.
  • the cool storage material container 47 exhibits good heat conduction with the refrigerant pipe 45.
  • the surface of the cold storage material container 47 may be uneven, and the protrusion may be joined to the refrigerant pipe 45.
  • 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 cool storage material containers 47 are arranged with a predetermined regularity.
  • 2 and 8 exemplify a configuration in which two fins 46 (air passages 53) and one cold storage material container 47 are repeatedly arranged in this order, but other arrangements may be employed.
  • a part of the gap is an air passage 53.
  • the remaining part of the gap is an accommodating part. Fins 46 are disposed in the air passage 53, and a cold storage material container 47 is disposed in the housing portion.
  • the two refrigerant tubes 45 located on both sides of the cold storage material container 47 define an air passage for exchanging heat with air on the side opposite to the cold storage material container 47.
  • two refrigerant tubes 45 are disposed between the two fins 46, and one cold storage material container 47 is disposed between the two refrigerant tubes 45.
  • the cold storage material container 47 and the two refrigerant tubes 45 located on both sides thereof constitute one cold storage unit.
  • the evaporator 40 is provided with a plurality of cold storage units having the same configuration. These cold storage units are arranged at equal intervals. Moreover, the some cool storage unit is arrange
  • the cold storage material container 47 is joined to both the refrigerant pipes 45 of the first heat exchange unit 48 and the second heat exchange unit 49 along the air flow direction.
  • the cold storage material container 47 has an outer shell 47a as shown in FIG.
  • the outer shell 47a has a shape obtained by bending a plate material into a flat cylindrical shape.
  • a corrugated inner fin 47b is accommodated in the outer shell 47a.
  • the inner fins 47b have a shape in which a thin metal plate such as aluminum is bent into a wave shape.
  • the plurality of top portions of the inner fins 47b are brazed to the inner surfaces of the main walls (wall portions having a main surface joined to the refrigerant pipe 45 as an outer surface) on both sides in the inflow direction of the outer shell 47a.
  • the inner fin 47b extends along the longitudinal direction (height direction) of the cold storage material container 47, and the peaks and valleys of the inner fin 47b extend along the flow direction. According to this configuration, the inner fins 47 b increase the contact area between the cold storage material 50 and the cold storage material container 47. Details of the shape of the inner fin 47b will be described later.
  • the first header 41 is also referred to as an inlet-side passage where the inlet of the refrigerant passage is provided.
  • the 3rd header 43 is described also as the exit side channel
  • the first header 41 and the third header 43 are arranged in parallel along the flow direction at the same position in the height direction, and collectively referred to as a first header tank 51.
  • the second header 42 and the fourth header 44 are arranged in parallel along the flow direction at the same position in the height direction, and are collectively referred to as a second header tank 52.
  • the refrigerant flowing into the first section of the first header 41 flows into the first section of the second header 42 through the refrigerant pipe 45 of the first group G1 (the first section 41). 1 turn).
  • the refrigerant that has flowed into the first section of the second header 42 flows into the second section of the second header 42.
  • the refrigerant flowing into the second section of the second header 42 flows into the second section of the first header 41 through the refrigerant pipe 45 of the second group G2 (second turn). Since the second section of the first header 41 and the second section of the third header 43 communicate with each other, the refrigerant flowing into the second section of the first header 41 flows into the second section of the third header 43.
  • the refrigerant that has flowed into the second section of the third header 43 flows into the second section of the fourth header 44 through the refrigerant pipe 45 of the third group G3 (third turn).
  • the refrigerant that has flowed into the second section of the fourth header 44 flows into the first section of the fourth header 44.
  • the refrigerant flowing into the first section of the fourth header 44 flows into the first section of the third header 43 through the refrigerant pipe 45 of the fourth group G4 (fourth turn).
  • the refrigerant flowing into the first section of the third header 43 flows out to the outside. That is, the evaporator 40 of this embodiment has a configuration having a so-called four-turn type refrigerant passage.
  • the compressor 10 for compressing and discharging the refrigerant exists downstream of the evaporator 40 in the refrigerant flow.
  • the liquid refrigerant returns to the compressor 10, it causes a failure, and therefore it is generally necessary to completely evaporate the refrigerant at the outlet of the evaporator 40.
  • the refrigerant becomes a gas monolayer, and a portion where the refrigerant temperature rapidly changes to a high temperature due to the pressure exceeding the saturated vapor pressure, a so-called superheat zone S exists.
  • FIG. 7 shows an example of the characteristic of the refrigerant temperature in the four-turn type refrigerant passage.
  • the horizontal axis in FIG. 7 represents the position of the refrigerant passage, the left side (origin side) of the axis represents the inlet, and the right side represents the outlet.
  • the vertical axis in FIG. 7 represents the refrigerant temperature at each flow path position.
  • the refrigerant temperature decreases after being introduced into the refrigerant passage, but suddenly changes to a high temperature at a substantially intermediate position of the fourth turn (that is, the fourth group G4). Has occurred.
  • the superheat zone S is generated in a substantially half region on the upper side in the height direction in the refrigerant pipe 45 of the fourth group G4.
  • the regenerator container 47 is joined to both the refrigerant pipes 45 of the first heat exchange part 48 and the second heat exchange part 49 along the flow direction.
  • the conventional cool storage material container 47 only the cool storage material 50 in the contact portion with the refrigerant pipe 45 of the fourth group G4, that is, the upwind side coolant pipe 45 in the flow direction, is hardly stored due to the influence of the superheat zone S. Therefore, a difference arises in how to cool the internal regenerator 50 between the windward side and the leeward side in the flow direction.
  • the shape of the inner fin 47 b is configured not to be joined to the cold storage material container 47 in the superheated region S of the refrigerant.
  • the inner fin 47b is connected to the inner wall surface of the outer shell 47a of the regenerator container 47 in the portion of the regenerator container 45 that is joined to the refrigerant pipe 45 where the superheat area S is generated. In the part which is not joined and contacts the refrigerant pipe 45 other than the superheated region S, it is joined to the inner wall surface.
  • a portion where the top of the inner fin 47 b is joined to the cold storage material container 47 is represented by a solid line, and a portion where the top of the inner fin 47 b is not joined to the cold storage material container 47 is represented by a dotted line.
  • the plurality of refrigerant tubes 45 are arranged with at least two refrigerant tubes 45 along the air flow direction of the air passage 53.
  • the cool storage material container 47 is formed so as to be joined to the at least two refrigerant tubes 45 arranged along the flow direction.
  • the inner fins 47 b are formed so as to overlap the at least two refrigerant tubes 45 when viewed from the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cold storage material container 47.
  • Inner fin 47b includes a portion in contact with superheat zone S of refrigerant pipe 45 in cold storage material container 47 joined to at least two refrigerant pipes 45 including refrigerant pipe 45 in which superheat zone S is generated, and flows.
  • the region overlapping this portion is not joined to the inner wall of the regenerator material container 47, and the other region is joined to the inner wall of the regenerator material container 47.
  • the inner fin 47b is not joined to the cold storage material container 47, that is, the refrigerant pipe 45 in the superheat region S, so that the heat from the superheated refrigerant is not easily transmitted to the inside of the cold storage material 50. Further, since the inner fin 47b itself is also disposed (floating) in the regenerator container 47 in the superheat region S, the cold heat of the refrigerant in the non-superheat region is transferred to the regenerator material 50 in the superheat region via the inner fin 47b. Is also reported.
  • the cool storage material 50 in the cool storage material container 47 can be cooled well. This eliminates the inconvenience that the regenerator material 50 in the regenerator container 47 in the superheat zone S does not cool and the temperature distribution is allowed to cool in the evaporator (evaporator 40), and that it cannot be stored due to the overheat region. can do.
  • the inner fin 47b is not joined to the cold storage material container 47 in the superheat zone S, so that the inner fin 47b is a refrigerant in the superheat zone S generated by the evaporation of the refrigerant in the vicinity of the outlet of the refrigerant passage. It functions as a “heat transfer suppression unit” that suppresses heat transfer from the tube 45 to the cold storage material 50. And by providing such an inner fin 47b, the heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S can be suppressed, and the cold storage material 50 is affected by the influence of the superheat zone S where the refrigerant temperature becomes high. The situation where it becomes difficult to get cold can be avoided. As a result, the evaporator 40 as the cold storage heat exchanger of the first embodiment is less susceptible to the influence of the superheat zone S even when the superheat zone S exists, and can secure the cold storage performance.
  • the joint ratio between the inner fin 471 b and the inner wall surface of the outer shell 471 a of the cold storage material container 471 is relatively low at the portion where the inner fin 471 b contacts the superheated region S of the refrigerant pipe 45. It can be set as the structure joined so that the joining rate with an inner wall surface may become relatively high in the part which contacts other than the superheat zone S of the refrigerant
  • the joining rate is relatively low means that the number of the ridges and valleys of the inner fin 471b that are joined to the inner wall surface of the outer shell 471a is relatively small, and “the joining rate is relatively high”. Means that the number of the ridges and valleys of the inner fin 471b that are joined to the inner wall surface of the outer shell 471a is relatively large.
  • the evaporator 401 becomes Heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S can be suppressed, and the same effect as the evaporator 40 of the first embodiment can be obtained.
  • the wave shape of the inner fin 47b follows the longitudinal direction (height direction) of the cool storage material container 47, ie, the peak and valley of the inner fin 47b extend along a flow direction.
  • the inner fin 47b may have a wave shape continuous in a different direction.
  • the wave shape of the inner fin 472b is continuous in the short direction (flow direction) of the cold storage material container 472, that is, the peaks and valleys of the inner fin 472b are in the height direction. It can be set as the structure extended along.
  • the ridges and valleys of the inner fins 472b are not joined to the inner wall surface of the outer shell 472a of the regenerator container 472 in the portion that contacts the superheated area S of the refrigerant pipe 45 along the height direction, and the refrigerant pipe 45 is overheated. In the portion that comes into contact with other than the area S, it is joined to the inner wall surface.
  • the evaporator 402 can suppress the heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S, and the same effect as the evaporator 40 of the first embodiment can be obtained.
  • the four-turn system is exemplified as the configuration of the refrigerant passage inside the evaporator 40, but is not limited thereto.
  • the refrigerant flowing into the first header 41A flows into the second header 42A through the refrigerant pipe 45 of the first heat exchanging section 48 (first turn). Since the second header 42A and the fourth header 44A communicate with each other, the refrigerant that has flowed into the second header 42A flows into the fourth header 44A.
  • the refrigerant that has flowed into the fourth header 44A flows into the third header 43A through the refrigerant pipe 45 of the second heat exchange section 49 (second turn).
  • the refrigerant flowing into the third header 43A flows out to the outside. That is, the regenerator heat exchanger 40A has a so-called two-turn refrigerant path.
  • FIG. 16 shows an example of the refrigerant temperature characteristic in the two-turn refrigerant passage.
  • the refrigerant temperature decreases after being introduced into the refrigerant passage, but rapidly changes to a high temperature at the second half position of the second turn, and the superheated region S is generated in the subsequent portions.
  • the superheat zone S is generated in a region on the upper side in the height direction of the refrigerant pipe 45 of the second heat exchange unit 49.
  • the inner fins 47b of the first embodiment can also be applied to those constituting a refrigerant flow such as the cold storage heat exchanger 40A, and can function as a heat transfer suppression unit.
  • the cold storage heat exchanger 40A is configured to eliminate the internal sections of the first header 41A, the second header 42A, the third header 43A, and the fourth header 44A, but may be configured to increase the internal sections.
  • the first header 41B, the second header 42B, the third header 43B, and the fourth header 44B are each divided into three sections.
  • the refrigerant that has flowed into the first section of the first header 41B flows through the refrigerant pipe 45 into the first section of the second header 42B (first turn).
  • the refrigerant that has flowed into the first section of the second header 42B flows into the second section of the second header 42B.
  • the refrigerant that has flowed into the second section of the second header 42B flows through the refrigerant pipe 45 into the second section of the first header 41B (second turn).
  • the refrigerant that has flowed into the second section of the first header 41B flows into the third section of the first header 41B.
  • the refrigerant that has flowed into the third section of the first header 41B flows into the third section of the second header 42B through the refrigerant pipe 45 (third turn). Since the third section of the second header 42B and the third section of the fourth header 44B communicate with each other, the refrigerant flowing into the third section of the second header 42B flows into the third section of the fourth header 44B.
  • the refrigerant flowing into the third section of the fourth header 44B flows through the refrigerant pipe 45 and into the third section of the third header 43B (fourth turn).
  • the refrigerant that has flowed into the third section of the third header 43B flows into the second section of the third header 43B.
  • the refrigerant flowing into the second section of the third header 43B flows through the refrigerant pipe 45 and into the second section of the fourth header 44B (fifth turn).
  • the refrigerant that has flowed into the second section of the fourth header 44B flows into the first section of the fourth header 44B.
  • the refrigerant flowing into the first section of the fourth header 44B flows through the refrigerant pipe 45 and into the first section of the third header 43B (sixth turn).
  • the refrigerant that has flowed into the first section of the third header 43B flows out to the outside. That is, the regenerative heat exchanger 40B has a so-called six-turn refrigerant path.
  • the inner fins 47b of the first embodiment can also be applied to those constituting a refrigerant flow such as the cold storage heat exchanger 40B, and can function as a heat transfer suppression unit.
  • the refrigerant inlet / outlet ports are provided in the first header 41, 41A, 41B and the third header 43, 43A, 43B, which are arranged on the upper side in the direction of gravity (height direction). .
  • the form of the refrigerant inlet / outlet is not limited to these, and the top and bottom of the cold storage heat exchangers 40, 40A, 40B may be reversed.
  • the first header 41R and the third header 43R are disposed on the lower side in the direction of gravity (height direction), and the second header 42R and the fourth header 44R are disposed on the upper side in the direction of gravity. Is arranged.
  • the refrigerant that has flowed into the first section of the first header 41R flows through the refrigerant pipe 45 into the first section of the second header 42R (first turn).
  • the refrigerant that has flowed into the first section of the second header 42R flows into the second section of the second header 42R.
  • the refrigerant that has flowed into the second section of the second header 42R flows through the refrigerant pipe 45 and into the second section of the first header 41R. (2nd turn)
  • the refrigerant flowing into the second section of the first header 41R flows into the second section of the third header 43R.
  • the refrigerant that has flowed into the second section of the third header 43R flows through the refrigerant pipe 45 into the second section of the fourth header 44R (third turn).
  • the refrigerant that has flowed into the second section of the fourth header 44R flows into the first section of the fourth header 44R.
  • the refrigerant that has flowed into the first section of the fourth header 44R flows through the refrigerant pipe 45 into the first section of the third header 43R (fourth turn).
  • the refrigerant flowing into the first section of the third header 43R flows out to the outside. That is, the cold storage heat exchanger 40R has a configuration having a so-called four-turn refrigerant passage, and the arrangement of the cold storage heat exchanger 40 in the height direction is changed.
  • a cold storage heat exchanger 40RA shown in FIG. 19 is obtained by reversing the cold storage heat exchanger 40A shown in FIG.
  • the regenerator heat exchanger 40RA has a so-called two-turn type refrigerant passage, and the first header 41RA and the third header 43RA are arranged on the lower side in the direction of gravity (height direction), and the second header 42RA and the fourth header 44RA is arranged on the upper side in the direction of gravity.
  • the cold storage heat exchanger 40RB has a so-called six-turn refrigerant passage, and the first header 41RB and the third header 43RB are arranged on the lower side in the direction of gravity (height direction), and the second header 42RB and the fourth header 44RB is arranged on the upper side in the direction of gravity.
  • the second embodiment will be described with reference to FIGS.
  • the evaporator 140 of the second embodiment is different from the evaporator 40 of the first embodiment in the configuration of a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheated region S.
  • the shape of the regenerator container 147 is a structure that does not join the refrigerant pipe 45 in the refrigerant overheating region S, and the regenerator container 147 having this structure is heated. Functions as a transmission suppression unit.
  • the evaporator 140 of 2nd Embodiment differs from the evaporator 40 of 1st Embodiment by the point which does not provide an inner fin in the inside of the cool storage material container 147.
  • the regenerator container 147 joined to the refrigerant tube 45 in which the superheat zone S is generated is not joined to the refrigerant tube 45 in the portion (region 147c) in contact with the superheat zone S of the refrigerant tube 45.
  • 45 is formed at an interval, and is joined to the refrigerant pipe 45 at a portion (outer shell 147a) in contact with the refrigerant pipe 45 other than the superheat zone S.
  • a region 147 c of the outer shell 147 a of the cold storage material container 147 that overlaps the superheated region S is recessed in a direction in which the surface is separated from the refrigerant pipe 45. The shape is illustrated.
  • the plurality of refrigerant tubes 45 are arranged with at least two refrigerant tubes 45 along the air flow direction of the air passage 53.
  • the cool storage material container 147 is formed so as to be joined to at least two refrigerant tubes 45 arranged along the flow direction.
  • the cold storage material container 147 joined to at least two refrigerant tubes 45 including the refrigerant tube 45 in which the superheat zone S is generated includes a portion that contacts the superheat zone S of the refrigerant tube 45 and when viewed from the flow direction. In the region 147c that overlaps with this portion, it is not joined to the refrigerant tube 45 but is spaced from the refrigerant tube 45, and in the other region 147a, it is joined to the refrigerant tube 45.
  • the regenerator container 147 since the regenerator container 147 is not joined to the refrigerant pipe 45 in the superheat region S, the heat from the overheated refrigerant is not easily transmitted to the inside of the regenerator 50. Moreover, since the cool storage material container 147 itself is in contact with the non-superheated region, the cold heat of the refrigerant in the non-superheated region is also transmitted to the cool storage material 50 in the superheated region S. Thereby, the evaporator 140 of 2nd Embodiment can have an effect similar to the evaporator 40 of 1st Embodiment.
  • the shape of the cool storage material container 147 of 2nd Embodiment is not limited to the above thing,
  • tube 45 in the superheat zone S to the cool storage material 50 via the cool storage material container 147 is superheat zone S.
  • Any other configuration may be used as long as it is relatively smaller than the heat transfer amount. In other words, it is only necessary that the heat transfer performance of the regenerator container 147 in the superheat zone S can be made relatively lower than the other parts. For example, as shown in FIG.
  • the joint ratio with the refrigerant pipe 45 is relatively low in a portion (area 1471 c) where the cold storage material container 1471 contacts the superheated area S of the refrigerant pipe 45. It can be set as the structure joined so that the joining rate with the refrigerant
  • the ratio of the portion joined to the refrigerant pipe 45 in the outer surface of the cool storage material container 1471 is relatively large.
  • the evaporator 1401 Heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S can be suppressed, and the same effect as the evaporator 40 of the first embodiment can be obtained.
  • the evaporator 240 of the third embodiment is different from the evaporator 40 of the first embodiment in the configuration of a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheated region S.
  • the shape of the regenerator container 247 is a structure that does not join the refrigerant pipe 45 in the refrigerant overheating region S, and the regenerator container 247 having this structure is heated. Functions as a transmission suppression unit.
  • the evaporator 240 of 3rd Embodiment is an evaporator of 1st Embodiment that the inner fin 247b provided in the inside of the cool storage material container 247 is joined to the inner wall face of the outer shell 247a over the whole area of a longitudinal direction. Different from 40.
  • the inner fin 247b is disposed so as to extend along the longitudinal direction (height direction) inside the cold storage material container 247, and is joined to the inner wall of the cold storage material container 247.
  • the regenerator container 247 joined to the refrigerant pipe 45 in which the superheat zone S is generated is not joined to the refrigerant pipe 45 at a portion (region 247 c) in contact with the superheat zone S of the refrigerant pipe 45 and spaced from the refrigerant pipe 45. It is formed and joined to the refrigerant pipe 45 at a portion (outer shell 147a) that is in contact with the refrigerant pipe 45 other than the superheat zone S.
  • the cool storage material container 247 is formed so as to be joined to at least two refrigerant pipes 45 arranged along the flow direction.
  • the inner fins 247b are formed so as to overlap the at least two refrigerant tubes 45 when viewed from the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cool storage material containers 247.
  • the regenerator container 247 joined to the at least two refrigerant tubes 45 including the refrigerant tube 45 in which the superheat zone S is generated includes a portion in contact with the superheat zone S of the refrigerant tube 45 and is viewed from the flow direction. Sometimes, the region 247c overlapping with this portion is not joined to the refrigerant tube 45 but is spaced from the refrigerant tube 45, and the other region 247a is joined to the refrigerant tube 45.
  • the regenerator container 247 is not joined to the refrigerant pipe 45 in the superheat zone S, and the inner fins 247b joined inside the regenerator container 247 are also not joined to the refrigerant pipe 45. It becomes difficult for the heat from the refrigerant to be transmitted to the inside of the regenerator 50. Further, since the inner fins 247b themselves are also arranged in the regenerator container 47 in the superheat region S, the cold heat of the refrigerant in the non-superheat region is also transmitted to the regenerator material 50 in the superheat region S via the inner fins 247b.
  • the evaporator 240 of 3rd Embodiment can have an effect similar to the evaporator 40 of 1st Embodiment.
  • the inner fin 247b is not joined to the inner wall surface of the outer shell 247a of the regenerator container 247 at the portion where the inner fin 247b is in contact with the superheated region S of the refrigerant pipe 45 as in the first embodiment. It is good also as a structure. With this configuration, the inner fin 247b is not joined to the regenerator container 247, that is, the refrigerant pipe 45 in the superheat region S, so that the heat from the overheated refrigerant is more difficult to be transmitted to the inside of the regenerator 50.
  • the shape of the cool storage material container 247 of 3rd Embodiment is not limited to the above thing,
  • tube 45 in the superheat zone S to the cool storage material 50 via the cool storage material container 247 is superheat zone S.
  • Any other configuration may be used as long as it is relatively smaller than the heat transfer amount.
  • the joining ratio with the refrigerant pipe 45 is joined so as to be relatively low, and the joining ratio with the refrigerant pipe 45 is relative to the portion (outer shell 2471a) in contact with the refrigerant pipe 45 other than the superheated area S. It can be set as the structure joined so that it may become high.
  • the evaporator 2401 Heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S can be suppressed, and the same effect as the evaporator 40 of the first embodiment can be obtained.
  • FIG. A configuration similar to that described with reference to the first embodiment can be applied. Specifically, as shown in FIG. 26, in the evaporator 2401, the joint ratio between the inner fin 2471 b and the inner wall surface of the outer shell 2471 a of the regenerator container 2471 is relative to the portion where the inner fin 2471 b contacts the superheated region S of the refrigerant pipe 45.
  • the evaporator 2401 can suppress heat transfer from the refrigerant pipe 45 to the cool storage material 50 in the superheat zone S, and The same effect as the evaporator 40 of 1 embodiment is acquired.
  • the evaporator 240 in the evaporator 240, a configuration in which the wave shape of the inner fin 247b is continuous in the short direction (flow direction) of the cold storage material container 247, That is, the configuration may be such that the peaks and valleys of the inner fin 247b extend along the height direction. Even in this configuration, the evaporator 240 can suppress heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat zone S, and the same effect as the evaporator 40 of the first embodiment can be obtained.
  • a fourth embodiment will be described with reference to FIGS. 27 and 28.
  • the evaporator 340 of the fourth embodiment is different from the inner fin 47b in the evaporator 40 of the first embodiment in the shape of the inner fin 347b as a heat transfer suppressing unit.
  • the refrigerant pipe 45 when the refrigerant pipe 45 is arranged on the windward side and the leeward side in the flow direction, the superheat zone S generally occurs on the windward side, and therefore only the windward side.
  • the inner fin 347b is different from the first embodiment in that the inner fin 347b is not joined to the cold storage material container 347.
  • the plurality of refrigerant tubes 45 are arranged with at least two refrigerant tubes 45 along the air flow direction of the air passage 53.
  • the cool storage material container 347 is formed so as to be joined to at least two refrigerant tubes arranged along the flow direction.
  • the inner fins 347b are formed so as to overlap the at least two refrigerant tubes 45 when viewed from the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cool storage material containers 347.
  • the inner fins 347b are disposed in the entire region in the longitudinal direction in the region of the cold storage material container 347 joined to at least two refrigerant tubes 45 including the refrigerant tubes 45 in which the superheat zone S is generated, in a region overlapping with the refrigerant tubes 45 in which the superheat zone S is not generated. It is joined to the inner wall of the cold storage material container 347 over the whole.
  • the evaporator 340 of the fourth embodiment has the same effect as that of the first embodiment. Further, since the inner fin 347b is in contact with the refrigerant tube 45 in the non-superheated region on the leeward side, cold heat can be transmitted from the leeward side to the leeward side, and heat transfer from the refrigerant tube 45 to the cold storage material 50 can be further suppressed.
  • FIG. The evaporator 440 of the fifth embodiment is different from the cold storage material container 147 in the evaporator 140 of the second embodiment in the shape of the cold storage material container 447 as a heat transfer suppression unit. Specifically, as shown in FIGS. 29 and 30, when the refrigerant pipe 45 is arranged on the windward side and the leeward side in the flow direction, the superheat zone S generally occurs on the windward side, and therefore only the windward side. However, it differs from the second embodiment in that the cold storage material container 447 is not joined to the refrigerant pipe 45.
  • At least two refrigerant tubes 45 are arranged in the evaporator 440 along the air flow direction of the air passage 53.
  • the cool storage material container 447 is formed so as to be joined to at least two refrigerant tubes 45 arranged along the flow direction.
  • the regenerator container 447 joined to at least two refrigerant pipes 45 including the refrigerant pipe 45 in which the superheat zone S is generated extends in the extending direction (height direction) in a region overlapping with the refrigerant pipe 45 in which the superheat zone S does not occur.
  • the refrigerant pipe 45 is joined over the entire area.
  • the portion (region 447c) of the refrigerant tube 45 that is in contact with the superheat zone S is not joined to the refrigerant tube 45 and is spaced from the refrigerant tube 45.
  • the other portion 447a is joined to the refrigerant pipe 45.
  • the evaporator 440 of the fifth embodiment has the same effects as those of the second embodiment. Further, since the cold storage container 447 is in contact with the refrigerant tube 45 in the non-superheated area on the leeward side, cold heat can be transmitted from the leeward side to the leeward side, and heat transfer from the refrigerant tube 45 to the cold storage material 50 is further suppressed. it can. Moreover, since the capacity
  • the sixth embodiment will be described with reference to FIGS. 31 and 32.
  • the evaporator 540 of the sixth embodiment is different from the cold storage material container 247 in the evaporator 240 of the third embodiment in the shape of the cold storage material container 547 as a heat transfer suppression unit.
  • the superheat zone S generally occurs on the windward side, and therefore only the windward side.
  • the regenerator container 547 is not joined to the refrigerant pipe 45.
  • the plurality of refrigerant tubes 45 are arranged with at least two refrigerant tubes 45 along the air flow direction of the air passage 53.
  • the cool storage material container 547 is formed so as to be joined to at least two refrigerant tubes 45 arranged along the flow direction.
  • the inner fins 547b are formed so as to overlap the at least two refrigerant tubes 45 when viewed from the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cold storage material containers 547.
  • the regenerator container 547 joined to at least two refrigerant tubes 45 including the refrigerant tube 45 in which the superheat zone S is generated extends in the extending direction (height direction) in a region overlapping with the refrigerant tube 45 in which the superheat zone S does not occur.
  • the refrigerant pipe 45 is joined over the entire area. Further, in the region overlapping with the refrigerant tube 45 where the superheat zone S is generated, the portion (region 547c) of the refrigerant tube 45 that is in contact with the superheat zone S is not joined to the refrigerant tube 45 and is formed at an interval from the refrigerant tube 45.
  • the other portion 547a is joined to the refrigerant pipe 45.
  • the evaporator 540 of the sixth embodiment has the same effects as those of the third embodiment.
  • the regenerator container 547 and the inner fins 547b are in contact with the refrigerant tube 45 in the non-superheated area on the leeward side, cold heat can be transmitted from the leeward side to the leeward side, and heat transfer from the refrigerant tube 45 to the regenerator material 50 It can be further suppressed.
  • capacitance of the cool storage material container 547 can be increased from 3rd Embodiment, more cool storage materials 50 can be accommodated.
  • the target superheat zone S1 is different from the superheat zone S of the first to sixth embodiments.
  • the evaporator 1040 (cold heat storage heat exchanger) according to the seventh embodiment suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat region S1 generated due to uneven flow rate of the refrigerant passage when the refrigerant flow rate is low.
  • the refrigerant flowing into the first header 2041 flows into the second header 2042 through the refrigerant pipe 45 of the first heat exchange unit 48 (first turn). Since the second header 2042 and the fourth header 2044 communicate with each other, the refrigerant flowing into the second header 2042 flows into the fourth header 2044.
  • the refrigerant flowing into the fourth header 2044 flows into the third header 2043 through the refrigerant pipe 45 of the second heat exchange unit 49 (second turn).
  • the refrigerant flowing into the third header 2043 flows out to the outside.
  • the refrigerant when the refrigerant flow rate is low, the refrigerant easily flows only into the refrigerant pipe 45 on the near side in the inflow direction, which is in the vicinity of the inlet of the refrigerant passage, and the refrigerant is hardly supplied to the refrigerant pipe 45 on the far side in the inflow direction. For this reason, when the flow rate of the refrigerant in the refrigerant passage is small, the overheating region S1 exists in the region on the back side in the inflow direction.
  • the superheat zone S2 (second superheat zone) shown in FIG. 37 is a superheat zone that occurs in the vicinity of the outlet targeted in the first to sixth embodiments.
  • the evaporator 1040 of the seventh embodiment is characterized by the structure of the refrigerant passage so as to be less affected by the superheated region S1 and to ensure the cold storage performance of the cold storage material 50.
  • the basic configuration of the evaporator 1040 is the same as that of the evaporator 1040 of the first embodiment, but the configuration of the refrigerant passage is different. More specifically, the first header 1041, the second header 1042, the third header 1043, The internal section of the fourth header 1044 and the communication relationship with each other are different.
  • the first header 1041 unlike the first header 41 of the first embodiment, the first section and the second section are communicated. Therefore, the refrigerant supplied to the first header 1041 is distributed to the plurality of refrigerant tubes 45 belonging to the first group G1 and the second group G2. The refrigerant flows into the first section of the second header 1042 through the refrigerant pipe 45 of the first group G1, and flows into the second section of the second header 1042 through the refrigerant pipe 45 of the second group G2.
  • the second header 1042 is sealed so that communication between the first section and the second section is impossible, unlike the second header 42 of the first embodiment.
  • the 4th header 1044 is sealed between the 1st division and the 2nd division so that communication is impossible.
  • the first section of the second header 42 located on the near side in the inflow direction and on the leeward side in the flow direction communicates with the first section of the fourth header 1044 located on the back side in the inflow direction and on the upwind side in the flow direction.
  • the second section of the second header 42 located on the rear side in the inflow direction and on the leeward side in the flow direction is communicated with the second section of the fourth header 1044 located on the front side in the inflow direction and on the upwind side in the flow direction.
  • the refrigerant flows from the first section of the second header 1042 to the first section of the fourth header 1044 and flows from the second section of the second header 1042 to the second section of the fourth header 1044.
  • the first section and the second section are communicated.
  • the refrigerant flowing into the first section of the fourth header 1044 is distributed to the plurality of refrigerant tubes 45 belonging to the third group G3, and the refrigerant flowing into the second section of the fourth header 1044 is transferred to the fourth group G4. It is distributed to the plurality of refrigerant tubes 45 to which it belongs.
  • the refrigerant flows into the third header 1043 through the refrigerant tubes 45 of the third group G3 and the fourth group G4, and is collected.
  • the refrigerant in the third header 1043 flows out from the refrigerant outlet and flows toward the compressor 10.
  • the refrigerant passage is positioned in the inflow direction of the refrigerant introduced from the first header 1041 at the upper side in the height direction in the second header tank 52 at the lower side in the height direction.
  • the structure which replaces is taken. That is, the refrigerant introduced from the front side in the inflow direction through the refrigerant pipe 45 of the first group G1 is replaced to the back side in the inflow direction, and the refrigerant pipe 45 of the second group G2 is connected from the back side in the inflow direction.
  • the refrigerant introduced through is replaced with the front side in the inflow direction. As shown in FIGS.
  • the schematic shape of the refrigerant passage in the second header tank 52 is an X-shape when viewed from the height direction, and the schematic shape of the refrigerant passage in the evaporator 1040.
  • the typical shape is obtained by intersecting two two-turn refrigerant passages.
  • the configuration of the refrigerant passage of the seventh embodiment is referred to as a “replacement flow method”.
  • the configuration of the refrigerant flow of the replacement flow method of the seventh embodiment can be expressed as follows.
  • the evaporator 1040 includes a first header tank 51 formed so that one end sides of the plurality of refrigerant tubes 45 communicate with each other and the arrangement direction (inflow direction) of the refrigerant tubes 45 and the cold storage material container 47 is a longitudinal direction; And a second header tank 52 formed so that the other end side of the tube 45 communicates with the inflow direction as a longitudinal direction.
  • the plurality of refrigerant tubes 45 are arranged in two rows so as to form a pair along the air flow direction of the air passage 53.
  • the interior of the first header tank 51 is divided into a first header 1041 and a third header 1043.
  • the first header 1041 is an inlet-side passage that communicates with the refrigerant pipe 45 disposed on the downstream side in the flow direction among the plurality of refrigerant pipes 45 and has an inlet of the refrigerant passage at one end in the longitudinal direction.
  • the third header 1043 is an outlet-side passage that communicates with the refrigerant pipe 45 disposed on the upstream side in the flow direction and that has an outlet of the refrigerant passage at one end (or the other end) in the longitudinal direction.
  • the plurality of refrigerant tubes 45 are divided into a first group G1, a second group G2, a third group G3, and a fourth group G4.
  • the refrigerant pipe 45 of the first group G1 communicates with the first header 1041 as an inlet side passage, and is disposed on one end side in the longitudinal direction (front side in the inflow direction).
  • the refrigerant pipe 45 of the second group G2 communicates with the first header 1041 as an inlet side passage, and is disposed on the other end side in the longitudinal direction (back side in the inflow direction).
  • the refrigerant pipe 45 of the third group G3 communicates with a third header 1043 as an outlet side passage and is disposed on the other end side in the longitudinal direction.
  • the refrigerant pipe 45 of the fourth group G4 communicates with a third header 1043 serving as an outlet-side passage and is disposed on one end side in the longitudinal direction.
  • the second header tank 52 communicates the first group G1 and the third group G3, communicates the second group G2 and the fourth group G4, and extends from the first header 1041 to the near side and the far side in the inflow direction.
  • the introduced refrigerant is replaced with the back side and the near side, respectively, and led out to the third header 1043.
  • the superheat zone S1 is a superheat zone that occurs in the second group G2 and the fourth group G4 of the plurality of refrigerant tubes 45 due to uneven flow rate of the refrigerant passage when the refrigerant flow rate is low. As shown in FIG.
  • a single regenerator container 47 is joined to both the second group G2 in which the superheat zone S1 is generated and the third group G3 in which the superheat zone S1 is not generated. Can be realized. Similarly, it is possible to realize a structure in which a single regenerator container 47 is joined to both the first group G1 where the superheat zone S1 does not occur and the fourth group G4 where the superheat zone S1 occurs.
  • the first group G1 and the third group G3 A refrigerant flow having a relatively high flow rate can be provided over the entire area in the inflow direction via the refrigerant pipe 45. That is, the refrigerant can be satisfactorily flowed to the back side in the inflow direction even when the refrigerant has a low flow rate.
  • the single cool storage material container 47 is joined to two refrigerant pipes 45 arranged in parallel in the flow direction, and a refrigerant having a relatively high flow rate flows through one of these refrigerant pipes 45. Thereby, even if the overheating region S1 occurs in the other of the two refrigerant tubes 45 to which the regenerator container 47 is joined, the cold energy in the non-overheating region can be transmitted to the regenerator material 50 in the overheating region S1.
  • the cool storage material 50 in the cool storage material container 47 can be cooled well.
  • the refrigerant pipe 45 in which the superheat zone S1 is generated and the refrigerant pipe in which no superheat zone is generated are obtained by changing the position of the refrigerant inflow direction in the second header tank 52 by the refrigerant flow of the replacement flow method.
  • the refrigerant passage structure 1045 is characterized in that a single cold storage material container 47 is joined to both of them.
  • the refrigerant passage structure 1045 functions as a “heat transfer suppression unit” that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat region S1 that is generated due to uneven flow of the refrigerant passage when the flow rate of the refrigerant is low.
  • the evaporator 1040 as the cold storage heat exchanger of the seventh embodiment is less susceptible to the influence of the superheat zone S1 even when the superheat zone S1 exists, and can secure the cold storage performance.
  • the surface of the cold storage material container 47 may be uneven, and the protrusion may be joined to the refrigerant pipe 45.
  • the refrigerant passage structure 1045 having one set of refrigerant flow in the inflow direction of the refrigerant in the second header tank 52 is illustrated as an example.
  • Other configurations may be used as long as they include a replacement flow type refrigerant passage.
  • the evaporator 1040A shown in FIG. 39 and FIG. 40 uses a pair of replacement flow methods and a conventional two-turn method in combination.
  • the evaporator 1040B shown in FIG. 41 and FIG. 42 is provided along the inflow direction in which two sets of refrigerant passages of a replacement flow method are used in combination.
  • a plurality of replacement flow-type refrigerant passages can be provided along the inflow direction.
  • the structure of the refrigerant passages of the evaporator 1040A and the evaporator 1040B can also realize the same structure as the refrigerant passage structure 1045 of the seventh embodiment, and thus the same effects as the evaporator 1040 of the seventh embodiment can be achieved. it can.
  • the eighth embodiment will be described with reference to FIGS. 43 to 45.
  • the evaporator 1140 according to the eighth embodiment is configured as a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheated region S1 generated due to uneven flow of the refrigerant passage when the refrigerant is at a low flow rate. It differs from the evaporator 1040 of 7th Embodiment by the point which has also added the function by the inner fin 1147b in addition to the structure of 7th Embodiment. Specifically, as shown in FIGS.
  • the inner fin 1147b is not in contact with the superheat zone S1.
  • the evaporator 1040 of the seventh embodiment Different from the evaporator 1040 of the seventh embodiment.
  • Inner fins 1147b are arranged so as to extend along the longitudinal direction (height direction) of the cool storage material container 1147 inside the cool storage material container 1147.
  • Inner fin 1147b is an inner wall of regenerator container 1147 at the portion where refrigerant storage container 1147 joins second group G2 and fourth group G4 of refrigerant pipe 45 where superheat zone S1 occurs (cross section B7-B7 in FIG. 43). Not joined with. Further, in the portion where the first group G1 and third group G3 of the refrigerant pipe 45 where the superheat zone S1 does not occur and the cool storage material container 1147 contact (cross section A7-A7 in FIG. 43), the inner wall of the cool storage material container 1147 is joined. Is done.
  • This inner fin 1147b functions as a heat transfer suppression unit.
  • the evaporator 1140 of the eighth embodiment has the same effects as those of the seventh embodiment. Moreover, since the inner fin 1147b is not in contact with the cold storage material container 1147 in the superheat zone S1, the heat in the superheat zone S1 is not easily transmitted to the cold storage material 50 in the cold storage material vessel 1147. For this reason, the cool storage material inside the cool storage material container 1147 can be more suitably cooled by the cold heat of the non-superheat region without being affected by the heat of the superheat region S1.
  • the joining structure of the inner fin 1147b and the cool storage material container 1147 of the eighth embodiment is not limited to the above, and the heat transfer amount from the refrigerant pipe 45 to the cool storage material 50 through the inner fin 1147b in the superheat region S1 is superheated.
  • Other configurations may be used as long as they are relatively smaller than the heat transfer amount other than the region S1.
  • it is only necessary that the heat transfer performance of the inner fin 1147b in the superheat region S1 can be made relatively lower than other portions.
  • the inner fin 1171 b is joined to the inner wall surface of the outer shell 1147 a of the regenerator container 1147 at a portion where the inner fin 1171 b is in contact with the superheated region S 1 of the refrigerant pipe 45. It can be set as the structure joined so that a rate may be relatively low, and in the part which contacts except the overheating area S1 of the refrigerant
  • the ridges and valleys of the inner fins 1147b are not joined to the inner wall surface of the outer shell 1147a of the regenerator container 1147 along the flow direction, and are not joined to the superheat region of the refrigerant tube 45. Those in contact with other than S1 are joined to the inner wall surface. Even in this configuration, heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheated region S1 can be suppressed, and the same effect as the evaporator 1140 of the present embodiment can be obtained.
  • FIG. The evaporator 1240 according to the ninth embodiment is configured as a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat region S1 that is generated due to uneven flow rate of the refrigerant passage when the flow rate of the refrigerant is low. It differs from the evaporator 1040 of 7th Embodiment by the point which has also added the function by the cool storage material container 1247 in addition to the structure of 7th Embodiment. Specifically, as shown in FIGS.
  • the regenerator container 1247 that is in contact with the superheat zone S1 (the leeward side rear side, the windward front side) is not joined to the refrigerant pipe 45 that generates the superheat zone S1.
  • the evaporator 1240 of 9th Embodiment differs from the evaporator 1040 of 7th Embodiment by the point which does not provide an inner fin in the inside of the cool storage material container 1247.
  • the regenerator container 1247 has a refrigerant in a portion (cross section B8-B8 in FIG. 46, region 1247c) in contact with the second group G2 and the fourth group G4 of the refrigerant pipe 45 in which the superheat zone S1 is generated. It is not joined to the pipe 45 and is formed at a distance from the refrigerant pipe 45. Further, the refrigerant pipe 45 is joined to the refrigerant pipe 45 at a portion (cross section A8-A8 in FIG. 46, outer shell 1247a) of the refrigerant pipe 45 that does not generate the superheat zone S1 and is in contact with the first group G1 and the third group G3.
  • This cool storage material container 1247 functions as a heat transfer suppression unit.
  • the evaporator 1240 of the ninth embodiment has the same effects as those of the seventh embodiment. Further, since the regenerator container 1247 is not in contact with the refrigerant pipe 45 in the overheat region S1, the heat in the overheat region S1 is not easily transmitted to the regenerator material 50 in the regenerator container 1247. For this reason, the cool storage material 50 inside the cool storage material container 1247 can be cooled more suitably by the cold heat of the non-superheat region without being affected by the heat of the superheat region S1.
  • the shape of the cool storage material container 1247 of 9th Embodiment is not limited to the above thing,
  • tube 45 in the superheat zone S1 to the cool storage material 50 via the cool storage material container 1247 is superheat zone S1.
  • Any other configuration may be used as long as it is relatively smaller than the heat transfer amount.
  • the heat transfer performance of the cool storage material container 1247 in the superheat region S1 only needs to be relatively lower than other portions. For example, similarly to the configuration described in the second embodiment with reference to FIG.
  • the joining rate with the refrigerant tube 45 is It is configured to be joined so as to be relatively low, and to be joined so that the joining ratio with the refrigerant pipe 45 is relatively high in a portion (outer shell 1247a) in contact with the refrigerant pipe 45 other than the superheated region S1. it can.
  • the refrigerant in the superheat zone S1 can be obtained by relatively reducing the heat transfer amount of the cold storage material container 1247 in the superheat zone S1 or by relatively reducing the joining rate between the cool storage material vessel 1247 and the refrigerant pipe 45. Heat transfer from the tube 45 to the cold storage material 50 can be suppressed, and the same effect as the evaporator 1240 of this embodiment can be obtained.
  • the tenth embodiment will be described with reference to FIGS. 49 to 51.
  • the evaporator 1340 of the tenth embodiment is configured as a heat transfer suppression unit that suppresses heat transfer from the refrigerant pipe 45 to the cold storage material 50 in the superheat region S1 that is generated due to uneven flow of the refrigerant passage when the refrigerant is at a low flow rate. It differs from the evaporator 1040 of 7th Embodiment by the point which has also added the function by the cool storage material container 1247 in addition to the structure of 7th Embodiment. Specifically, as shown in FIGS.
  • the regenerator container 1247 that is in contact with the superheat zone S1 (the leeward side rear side, the windward front side) is not joined to the refrigerant pipe 45 that generates the superheat zone S1. This differs from the evaporator 1040 of the seventh embodiment.
  • the inner fin 1347b is arranged so as to extend along the longitudinal direction (height direction) of the cold storage material container 1347 inside the cold storage material container 1347, and the inner wall of the cold storage material container 1347 and the entire area in the longitudinal direction. Are joined.
  • the regenerator container 1347 is not joined to the refrigerant pipe 45 at a portion (cross section B9-B9 in FIG. 49, region 1347c) of the refrigerant pipe 45 where the superheated area S1 is in contact with the second group G2 and the fourth group G4. It is formed at a distance from the refrigerant pipe 45.
  • the refrigerant pipe 45 is joined to the refrigerant pipe 45 at a portion (cross section A9-A9 in FIG. 49, outer shell 1347a) of the refrigerant pipe 45 that does not generate the superheat zone S1 and is in contact with the first group G1 and the third group G3.
  • This cool storage material container 1347 functions as a heat transfer suppression unit.
  • the evaporator 1340 of the tenth embodiment has the same effects as those of the seventh embodiment. Further, since the regenerator material container 1347 is not in contact with the refrigerant pipe 45 in the overheat region S1, the heat in the overheat region S1 is not easily transmitted to the regenerator material 50 in the regenerator material container 1347. Moreover, since the inner fin 1347b is provided in the inside of the cool storage material container 1347, it is easy to convey the cold on the non-superheated side to the superheated region side. For this reason, the cool storage material 50 inside the cool storage material container 1347 can be more suitably cooled by the cold heat of the non-superheat region without being affected by the heat of the superheat region S1.
  • the inner fin 1347b includes the second group G2 and the fourth group G4 of the refrigerant pipe 45 in which the superheat zone S1 is generated and the cold storage material container 1347. It is good also as a structure which is not joined with the inner wall of the cool storage material container 1347 in the part (area
  • the shape of the cool storage material container 1347 of 10th Embodiment is not limited to the said thing,
  • tube 45 in the superheat zone S1 to the cool storage material 50 via the cool storage material container 1247 is superheat zone S1.
  • Any other configuration may be used as long as it is relatively smaller than the heat transfer amount.
  • the heat transfer performance of the cool storage material container 1347 in the superheat region S1 only needs to be relatively lower than other portions. For example, similarly to the configuration described in the second embodiment with reference to FIG.
  • the joint ratio with the refrigerant pipe 45 in the portion (region 1347 c) where the cold storage material container 21347 is in contact with the superheated area S ⁇ b> 1 of the refrigerant pipe 45. are connected so as to be relatively low, and in a portion (outer shell 1347a) in contact with the refrigerant pipe 45 other than the superheated region S1, the joining ratio with the refrigerant pipe 45 is relatively high. Can do.
  • the refrigerant in the superheat zone S1 can be obtained by relatively reducing the heat transfer amount of the cold storage material container 1347 in the superheat zone S1 or by relatively reducing the joining rate between the cool storage material vessel 1347 and the refrigerant pipe 45. Heat transfer from the tube 45 to the cold storage material 50 can be suppressed, and the same effect as the evaporator 1340 of this embodiment can be obtained.
  • FIG. A configuration similar to that described with reference to the first embodiment can be applied.
  • the inner fin 1347b is joined so that the joining ratio with the inner wall surface of the outer shell 1347a of the regenerator container 1347 is relatively low at the portion where the inner fin 1347b is in contact with the superheated region S1 of the refrigerant tube 45. It can be set as the structure joined so that a joining rate with an inner wall surface may become relatively high in the part which contacts other than superheat zone S1.
  • the heat transfer from the refrigerant pipe 45 to the cool storage material 50 in the superheated region S1 can be suppressed by relatively reducing the joining rate between the inner fins 1347b and the cool storage material container 1347, and the evaporator according to the present embodiment.
  • the same effect as 1340 is obtained.
  • the eleventh embodiment will be described with reference to FIG.
  • the evaporator 1440 according to the eleventh embodiment includes other portions (the first group in the present embodiment) that are in contact with the second group G2 and the fourth group G4 where the superheat zone S1 is generated, among the plurality of refrigerant tubes 45.
  • the high melting point regenerator material 50A having a relatively high melting point compared to G1) is arranged, and further, the high melting point regenerator material 50A is also arranged in the portion that contacts the third group G3 where the superheat zone S2 is generated. This differs from the evaporator 1040 of the seventh embodiment (see FIGS. 33 to 35).
  • the refrigerant flow structure 1045 of the replacement flow type in the second group G2 and the fourth group G4 of the plurality of refrigerant pipes 45 due to uneven flow rate of the refrigerant passage when the refrigerant flow rate is low.
  • An overheating zone S1 occurs.
  • the superheat zone S2 is generated by the same mechanism as the superheat zone S of the first to sixth embodiments.
  • a high-melting-point regenerator is provided inside the regenerator container 47 in contact with the refrigerant tubes 45 (that is, the second group G2, the third group G3, and the fourth group G4) in which these superheat zones S1 and S2 are generated.
  • the material 50A is accommodated.
  • the regenerator container 47 that contacts both the first group G1 and the fourth group G4 of the refrigerant pipe 45 is in contact with the first group G1 (half of the leeward side in the flow direction).
  • Is filled with a normal regenerator material 50 Is filled with a normal regenerator material 50
  • a portion (half of the windward side in the flow direction) in contact with the fourth group G4 is filled with a high-melting regenerator material 50A.
  • Such a configuration can be realized, for example, by incorporating a partition plate at a substantially intermediate position in the flow direction of the cool storage material container 47 and partitioning the internal space of the single cool storage material container 47.
  • the entire internal space may be simply filled with the high melting point regenerator material 50A.
  • the temperature difference from the refrigerant that cools the regenerator material increases, so the regenerator material becomes easier to cool (is more likely to solidify).
  • the temperature of the refrigerant in the normal region of the refrigerant pipe 45 is ⁇ 3 ° C.
  • the temperature of the refrigerant in the superheated areas S1 and S2 of the refrigerant pipe 45 is 0 ° C.
  • a cold storage material that exchanges heat with the refrigerant in the normal region of the refrigerant pipe 45 is used.
  • the melting point is assumed to be 5 ° C.
  • the melting point of the regenerator material that exchanges heat with the refrigerant in the superheat regions S1 and S2 of the refrigerant pipe 45 is the same as the melting point of the regenerator material in the normal region, the regenerator material is relatively in the overheat regions S1 and S2. It becomes difficult to solidify, and the solidification property of the regenerator material in the superheat regions S1 and S2 is lower than the normal region.
  • the melting point of the regenerator material in the superheat regions S1 and S2 is set higher than the melting point of the regenerator material in the normal region by the temperature difference (here, + 3 ° C.) between the refrigerant in the normal region and the superheat regions S1 and S2.
  • the solidification property of the regenerator material in the superheat regions S1 and S2 is equivalent to that in the normal region.
  • the melting point of the regenerator material in the superheat regions S1 and S2 is higher than the temperature difference between the refrigerant in the normal region and the superheat regions S1 and S2 with respect to the melting point of the regenerator material in the normal region, the regenerator in the superheat regions S1 and S2 The solidification of the material is improved over the normal range.
  • the evaporator 1440 of the eleventh embodiment exchanges heat with the regenerator material by arranging the high-melting-point regenerator material 50A in the portion that contacts the refrigerant pipe 45 where the superheat zones S1 and S2 are generated.
  • the solidification of the regenerator material can be made uniform without depending on whether the refrigerant is in the superheated region S1, S2 or the normal region. Thereby, it can make it difficult to receive to the influence of overheating region S1, S2, and can improve the thermal storage / radiation performance of the evaporator 1440.
  • the high-melting-point regenerator material 50A is filled in the entire height direction of the regenerator container 47 in contact with the third group G3 of the refrigerant pipe 45 in which the superheat zone S2 is generated.
  • the configuration has been illustrated, at least a portion in contact with the superheated region S2 may be the high melting point regenerator material 50A.
  • it is good also as a structure which accommodates 50 A of high melting-point regenerator materials only in the part which contacts the vicinity of the exit side channel
  • a partition plate is built in along a portion (for example, a quarter region on the windward side in the flow direction and on the upper side in the height direction) that overlaps the superheat region S2 of the cold storage material container 47. This can be realized by dividing the internal space of one cold storage material container 47.
  • the twelfth embodiment will be described with reference to FIG.
  • the evaporator 1540 of the twelfth embodiment is that the high-melting-point regenerator material 50A is disposed in a portion of the plurality of refrigerant tubes 45 that comes into contact with the second group G2 and the fourth group G4 where the superheat zone S1 is generated.
  • the evaporator 1040 of the seventh embodiment see FIGS. 33 to 35.
  • the high melting point regenerator material 50A is not disposed in the portion that contacts the third group G3 where the overheated region S2 is generated.
  • the regenerator container 47 in contact with both the second group G2 and the third group G3 of the refrigerant pipe 45 is, as shown in FIG. 53, a portion in contact with the third group G3 (half of the windward side in the flow direction). ) Is filled with the normal melting point regenerator material 50, and the portion (half on the leeward side in the flow direction) in contact with the second group G2 is filled with the high melting point regenerator material 50A.
  • tube 45 is the same as that of the 11th Embodiment demonstrated with reference to FIG.
  • the evaporator 1540 of the twelfth embodiment has a configuration in which the high melting point regenerator material 50A is disposed in a portion that contacts the refrigerant pipe 45 in which the superheat zone S1 is generated.
  • the solidification property of the regenerator material can be made uniform without depending on whether the refrigerant that exchanges heat with the regenerator material is the superheat region S1 or the normal region. Thereby, it can be made hard to receive the influence of overheating region S1, and there can exist an effect that the heat storage and heat dissipation performance can be improved.
  • each of the two types of refrigerating material having the melting points has the same freezing method, and as a result, it is possible to make the blow-off temperature distribution uniform during heat dissipation.
  • the thirteenth embodiment will be described with reference to FIG.
  • the evaporator 1640 of the thirteenth embodiment differs from the evaporator 40 of the first embodiment in that the portion of the regenerator material in contact with the superheat zone S is the high melting point regenerator material 50A.
  • the superheated area S is generated by the evaporation of.
  • the high-melting-point regenerator material 50A is accommodated in the regenerator container 47 that comes into contact with the refrigerant pipe 45 (that is, the fourth group G4) in which the superheat zone S is generated.
  • At least a portion of the regenerator material in contact with the superheat region S may be the high melting point regenerator material 50A.
  • the high melting point regenerator material 50A is the first refrigerating pipe 45 in the superheat region S.
  • the structure filled up in the whole height direction of the cool storage material container 47 which contacts the 4th group G4 may be sufficient, and the structure filled only in the part which contacts the superheat zone S may be sufficient.
  • the evaporator 1640 of the thirteenth embodiment has a configuration in which the high melting point regenerator material 50A is arranged in a portion that contacts the refrigerant pipe 45 where the superheat zone S is generated, similarly to the evaporator 1440 of the eleventh embodiment. Therefore, in the four-turn type refrigerant passage structure, whether the refrigerant that exchanges heat with the cold storage material is in the superheated region S or the normal region, as in the refrigerant flow structure 1045 of the replacement flow type in the eleventh embodiment.
  • the solidification property of the regenerator material can be made uniform without depending on. Thereby, it can be made hard to receive the influence of the superheat zone S, and there can exist an effect that the heat storage and heat dissipation performance can be improved.
  • the configuration of the thirteenth embodiment can also be applied to the other second to sixth embodiments related to the four-turn refrigerant passage structure.
  • the fourteenth embodiment will be described with reference to FIG.
  • the evaporator 1740 of the fourteenth embodiment is provided with a pair of partition plates 47d that divide the internal space along the longitudinal direction (that is, the height direction) that is the direction in which the refrigerant pipe 45 extends, inside the cold storage material container 47. This is different from the above embodiments.
  • one of the pair of partition plates 47d (the right side plate in FIG. 55) is an end portion on one side of the cold storage material container 47 in the longitudinal direction (the lower side in the height direction in FIG. 55). Have gaps.
  • the other of the pair of partition plates 47d (the left plate in FIG. 55) has a gap at the end of the other side in the longitudinal direction of the cold storage material container 47 (the upper side in the height direction in FIG. 55).
  • the partition plates 47d are arranged at substantially equal intervals along the flow direction.
  • the cool storage material container 47 is equipped with the cool storage material enclosure pipe 47e in the side wall close
  • the cool storage material 50 is enclosed inside via the cool storage material sealing pipe 47e.
  • the internal space is not filled with the cool storage material 50 as a countermeasure against freezing and expansion, and the cool storage material container 47 is filled.
  • a gap of about 15% is provided on the upper side of the inside.
  • a space having a height of about C1 remains at the upper end of the internal space.
  • the superheat regions S and S2 described in the above embodiment are mainly generated on the upper side in the height direction of the refrigerant pipe 45. For this reason, in the conventional configuration, the upper side in the height direction of the cold storage material container 47 is difficult to cool, and there is a possibility that a cooling failure may occur.
  • the internal space of the cold storage material container 47 is divided into three by a pair of partition plates 47d, and the divided regions are connected in series. For this reason, when the cool storage material 50 is injected so as to provide a gap of about 15% as a measure against freezing and expansion, a space 47f is created only in the region where the cool storage material sealing pipe 47e communicates, as shown in FIG. In the two regions on the back side, the regenerator material 50 is filled over the entire region in the height direction.
  • the height c2 from the upper end is larger than the conventional height c1, but if the entire internal space of the cool storage material container 47 is viewed, there is a position where the cool storage material 50 does not exist in the height direction. No longer.
  • the cool storage material 50 is disposed over the entire region in the height direction. Thereby, it can prevent that a clearance gap is made in the upper end in the cool storage material container 47, and the cooling remaining part of the height direction upper side of the cool storage material container 47 can be eliminated.
  • At least one pair of the pair of partition plates 47d may be provided inside the cold storage material container 47, and a plurality of pairs of partition plates may be provided.
  • the fifteenth embodiment will be described with reference to FIG.
  • the cold storage material container 47 joined to the refrigerant pipe 45 in which the superheat zone S is generated is not provided in the portion of the refrigerant pipe 45 that contacts the superheat zone S. It differs from the evaporator 40 of 1st Embodiment by the point provided only in the part which contacts except the superheat zone S.
  • FIG. 1st Embodiment differs from the evaporator 40 of 1st Embodiment by the point provided only in the part which contacts except the superheat zone S.
  • the superheated area S is generated by the evaporation of.
  • the refrigerant tube 45 in which the superheat zone S is generated that is, the cold storage container 47 that is in contact with the refrigerant tube 45 of the fourth group G4, is a region in which the superheat zone S is generated ( It is not arranged in the vicinity of the outlet of the refrigerant passage.
  • the evaporator 1840 of the fifteenth embodiment can divide the heat exchange between the refrigerant in the superheat zone S and the cold storage material 50, and can improve the cooling efficiency.
  • the solidification of the regenerator material 50 is promoted, and the cooling time is made longer than that of the conventional product, so that the off time of the air conditioner can be increased when the vehicle on which the evaporator 1840 is mounted is idled.
  • the configuration of the fifteenth embodiment can also be applied to the other second to sixth embodiments related to the four-turn type refrigerant passage structure.
  • the method for reducing the influence of cold storage due to the superheat zones S and S2 generated by the evaporation of the refrigerant in the vicinity of the outlet of the refrigerant passage is the seventh to tenth embodiments. It is also possible to combine with the structure of.
  • the regenerator material container 47 is disposed between the two refrigerant tubes 45, joined to the two refrigerant tubes 45, and opposite to the regenerator material container 47 in each refrigerant tube 45.
  • the configuration in which the air passage 53 is provided is illustrated, the configuration is not limited to this configuration.
  • the refrigerant pipe 45 and the cold storage material container 47 may be formed as an integral member so as to extend in the same direction, and the air passage 53 may be provided in a gap between these members.
  • the configuration in which the cold storage material 50 is accommodated in the cold storage material container 47 is illustrated, but is not limited thereto.
  • a configuration in which the regenerator material 50 is not accommodated in the regenerator material container 47 and is in direct contact with the refrigerant tube 45 a configuration in which heat transfer from the refrigerant tube 45 to the regenerator material 50 can be performed directly.

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

Abstract

Selon l'invention, un évaporateur (40) sous la forme d'un échangeur de chaleur à accumulation de froid comprend : une pluralité de tuyaux (45) de frigorigène qui sont disposés espacés les uns des autres et qui comportent tous un passage de frigorigène à travers lequel circule un frigorigène; un matériau d'accumulation de froid (50) adjacent à la pluralité de tuyaux (45) de frigorigène; et une ailette interne (47b) qui sert de section d'inhibition de transmission de chaleur qui inhibe une transmission de chaleur des tuyaux (45) de frigorigène au matériau d'accumulation de froid (50) dans une région (S) de surchauffe de frigorigène créée dans le passage de frigorigène.
PCT/JP2016/077976 2015-10-01 2016-09-23 Échangeur de chaleur à accumulation de froid WO2017057174A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE112016004451.8T DE112016004451B8 (de) 2015-10-01 2016-09-23 Kältespeicherwärmetauscher
CN201680057193.1A CN108139173B (zh) 2015-10-01 2016-09-23 蓄冷热交换器
US15/765,101 US10696128B2 (en) 2015-10-01 2016-09-23 Cold storage heat exchanger

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JP2015195818 2015-10-01
JP2015-195818 2015-10-01
JP2016-173410 2016-09-06
JP2016173410A JP6409836B2 (ja) 2015-10-01 2016-09-06 蓄冷熱交換器

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WO2017057174A1 true WO2017057174A1 (fr) 2017-04-06

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CN109070697B (zh) 2016-06-01 2021-10-08 株式会社电装 蓄冷热交换器

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005195316A (ja) * 2003-12-08 2005-07-21 Showa Denko Kk 熱交換器
JP2006029697A (ja) * 2004-07-16 2006-02-02 Denso Corp 冷媒蒸発器
JP2007113904A (ja) * 2005-09-20 2007-05-10 Denso Corp 蓄冷タンク装置およびそれを用いた冷凍サイクル装置
JP2013217573A (ja) * 2012-04-09 2013-10-24 Denso Corp 蓄冷機能付き車両用熱交換器
JP2013256262A (ja) * 2012-06-14 2013-12-26 Denso Corp 蓄冷熱交換器
JP2015007518A (ja) * 2013-06-26 2015-01-15 サンデン株式会社 蓄冷熱交換器
JP2015010740A (ja) * 2013-06-27 2015-01-19 サンデン株式会社 蓄冷熱交換器及びその製造方法

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5444782B2 (ja) 2008-09-12 2014-03-19 株式会社デンソー 蓄冷熱交換器
JP6115896B2 (ja) 2013-06-26 2017-04-19 サンデンホールディングス株式会社 蓄冷材容器
JP2015195818A (ja) 2014-03-31 2015-11-09 株式会社大一商会 遊技機
JP2016173410A (ja) 2015-03-16 2016-09-29 株式会社リコー 画像形成装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005195316A (ja) * 2003-12-08 2005-07-21 Showa Denko Kk 熱交換器
JP2006029697A (ja) * 2004-07-16 2006-02-02 Denso Corp 冷媒蒸発器
JP2007113904A (ja) * 2005-09-20 2007-05-10 Denso Corp 蓄冷タンク装置およびそれを用いた冷凍サイクル装置
JP2013217573A (ja) * 2012-04-09 2013-10-24 Denso Corp 蓄冷機能付き車両用熱交換器
JP2013256262A (ja) * 2012-06-14 2013-12-26 Denso Corp 蓄冷熱交換器
JP2015007518A (ja) * 2013-06-26 2015-01-15 サンデン株式会社 蓄冷熱交換器
JP2015010740A (ja) * 2013-06-27 2015-01-19 サンデン株式会社 蓄冷熱交換器及びその製造方法

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