WO2016170751A1 - Échangeur de chaleur à accumulation de froid - Google Patents

Échangeur de chaleur à accumulation de froid Download PDF

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Publication number
WO2016170751A1
WO2016170751A1 PCT/JP2016/001971 JP2016001971W WO2016170751A1 WO 2016170751 A1 WO2016170751 A1 WO 2016170751A1 JP 2016001971 W JP2016001971 W JP 2016001971W WO 2016170751 A1 WO2016170751 A1 WO 2016170751A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
header
cold storage
heat exchanger
header tank
Prior art date
Application number
PCT/JP2016/001971
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English (en)
Japanese (ja)
Inventor
淳 安部井
佑輔 鬼頭
河地　典秀
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株式会社デンソー
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Publication of WO2016170751A1 publication Critical patent/WO2016170751A1/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
    • B60H1/32—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
    • 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 has been proposed. For example, a cold storage heat exchanger described in Patent Document 1 is known.
  • the cold storage material is arranged only in the air flow path in order to increase the cooling efficiency of the cold storage material to cool the air when the engine is stopped.
  • the air flow passage is originally intended to exchange heat by circulating air, it is necessary to place the regenerator material in a range that does not excessively affect the air flow rate, and there is a limit to increasing the regenerator material. was there.
  • the present disclosure has been made in view of the above, and an object thereof is to provide a cold storage heat exchanger that can increase the amount of the cold storage material while reducing the influence on the air flow.
  • the cold storage heat exchanger that evaporates the refrigerant includes a plurality of refrigerants each having a refrigerant passage through which the refrigerant circulates and arranged to form an air passage with a space between each other.
  • the first header tank provided so that one end sides of the plurality of refrigerant flow paths communicate with each other, and the other end side of the plurality of refrigerant flow paths communicate with each other.
  • the second header tank thus formed, and a regenerator material that cools by evaporating the refrigerant decompressed by the decompressor when the compressor is driven and cools when the compressor is stopped.
  • the regenerator material is arranged in a region that does not hinder the air flow in the air passage.
  • the refrigerant that is cooled by evaporating the refrigerant depressurized by the pressure reducer when the compressor is driven is disposed in a region that does not obstruct the air flow in the air passage while being cooled when the compressor is stopped.
  • the amount of the regenerator material can be increased while reducing the influence on the air flow.
  • FIG. 4 is a cross-sectional view showing a IV-IV cross section of FIG. 2.
  • FIG. 5 is a cross-sectional view showing a VV cross section of FIG. 3.
  • FIG. 5 is a cross-sectional view corresponding to FIG. 4 illustrating an evaporator according to a second embodiment of the present disclosure. It is sectional drawing equivalent to FIG. 5 which shows the evaporator which concerns on 2nd Embodiment of this indication. It is sectional drawing equivalent to FIG.
  • FIG. 4 which shows the evaporator which concerns on 3rd Embodiment of this indication. It is sectional drawing equivalent to FIG. 4 which shows the evaporator which concerns on 4th Embodiment of this indication. It is sectional drawing equivalent to FIG. 5 which shows the evaporator which concerns on 4th Embodiment of this indication. It is sectional drawing equivalent to FIG. 5 which shows the evaporator which concerns on 5th Embodiment of this indication. It is a perspective view showing a refrigerant channel and a cool storage material of an evaporator concerning a 6th embodiment of this indication. It is a figure which shows typically the flow of the refrigerant
  • FIG. 1 is a block diagram illustrating a configuration of a refrigeration cycle apparatus 1 using an evaporator 40 (cold storage heat exchanger) as a first embodiment of the present disclosure.
  • the refrigeration cycle apparatus 1 is used in a vehicle air conditioner.
  • the refrigeration cycle apparatus 1 includes a compressor 10, a radiator 20, a decompressor 30, and an evaporator 40. These components are connected in an annular shape by piping and constitute a refrigerant circulation path.
  • the compressor 10 is driven by an internal combustion engine that is a power source 2 (PS) 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.
  • PS power source 2
  • 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.
  • FIG. 2 is a plan view of an evaporator 40 as a cold storage heat exchanger according to the first embodiment.
  • FIG. 3 is a side view of FIG.
  • FIG. 4 is an enlarged cross-sectional view showing a part of the IV-IV cross section of FIG.
  • FIG. 5 is an enlarged cross-sectional view showing a part of the VV cross section of FIG.
  • 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, and a fourth header 44 that are positioned in pairs, and a plurality of refrigerant flow paths 45 that connect the headers. ing.
  • the first header 41 and the second header 42 form a pair, and are arranged in parallel with a predetermined distance from each other.
  • the third header 43 and the fourth header 44 also form a set and are arranged in parallel with a predetermined distance from each other.
  • the first header 41 and the third header 43 are disposed above the refrigerant flow path 45 in the gravity direction, and the second header 42 and the fourth header 44 are disposed below the refrigerant flow path 45 in the gravity direction.
  • a plurality of refrigerant flow paths 45 are arranged at equal intervals between the first header 41 and the second header 42. Each refrigerant channel 45 communicates with the corresponding first header 41 and second header 42 at one end thereof.
  • a first heat exchange section 48 is formed by the first header 41, the second header 42, and a plurality of refrigerant flow paths 45 arranged therebetween.
  • a plurality of refrigerant flow paths 45 are arranged at equal intervals between the third header 43 and the fourth header 44. Each refrigerant channel 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 flow paths 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 exchange unit 49 is arranged on the upstream side
  • the first heat exchange unit 48 is arranged on the downstream side.
  • a joint as a refrigerant inlet is provided at the end of the first header 41.
  • the inside of the first header 41 is partitioned into a first partition and a second partition by a partition plate provided substantially at the center in the length direction.
  • the plurality of refrigerant flow paths 45 are divided into a first group corresponding to the first section and a second group 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 flow paths 45 belonging to the first group.
  • the refrigerant flows into the second header 42 through the first group and is collected.
  • the refrigerant is distributed again from the second header 42 to the plurality of refrigerant flow paths 45 belonging to the second group.
  • the refrigerant flows into the second section of the first header 41 through the second group.
  • a joint as a refrigerant outlet is provided at the end of the third header 43.
  • the inside of the third header 43 is partitioned into a first partition and a second partition by a partition plate provided substantially at the center in the length direction.
  • the plurality of refrigerant flow paths 45 are divided into a first group corresponding to the first section and a second group corresponding to the second section.
  • the first section of the third header 43 is adjacent to the second section of the first header 41.
  • the first section of the third header 43 and the second section of the first header 41 are in communication.
  • the refrigerant flows from the second section of the first header 41 into the first section of the third header 43.
  • the refrigerant is distributed from the first section to a plurality of refrigerant flow paths 45 belonging to the first group.
  • the refrigerant flows into the fourth header 44 through the first group and is collected.
  • the refrigerant is distributed again from the fourth header 44 to the plurality of refrigerant flow paths 45 belonging to the second group.
  • the refrigerant flows into the second section of the third header 43 through the second group.
  • coolant in a U shape is formed.
  • the refrigerant in the second section of the third header 43 flows out from the refrigerant outlet and flows toward the compressor 10.
  • the refrigerant flow path 45 is a multi-hole pipe having a plurality of refrigerant passages therein.
  • the refrigerant channel 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 flow path 45 and open at both ends of the refrigerant flow path 45.
  • the plurality of refrigerant flow paths 45 are arranged in a row. In each row, the plurality of refrigerant channels 45 are arranged so that their main surfaces face each other.
  • the plurality of refrigerant flow paths 45 partition an air passage for heat exchange with air and an accommodating portion for accommodating a cold storage material container, which will be described later, between two refrigerant flow paths 45 adjacent to each other. .
  • 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 partitioned between two adjacent refrigerant flow paths 45.
  • the fin 46 is thermally coupled to the two adjacent refrigerant flow paths 45.
  • the fins 46 are joined to the two adjacent refrigerant flow paths 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 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 flow path 45.
  • the cool storage material container 47 is disposed between two adjacent refrigerant flow paths 45.
  • the plurality of refrigerant flow paths 45 are arranged at substantially constant intervals.
  • a plurality of gaps are formed between the plurality of refrigerant flow paths 45.
  • a plurality of fins 46 and a plurality of cool storage material containers 47 are arranged with a predetermined regularity.
  • a part of the gap is an air passage.
  • the remaining part of the gap is an accommodating part.
  • a cold storage material container 47 is disposed in the housing portion.
  • FIGS. 4 and 5 a first embodiment in which the cool storage material is arranged so as not to disturb the air flow in the air passage will be described with reference to FIGS.
  • one end of the coolant channel 45 is inserted into the first header 41 and the third header 43.
  • Side plates 50 are provided outside the plurality of refrigerant flow paths 45 arranged.
  • a partition wall 411 is provided inside the first header 41.
  • the partition wall 411 is provided in close contact with the inner wall of the first header 41.
  • the partition wall 411 partitions the inside of the first header 41 into two or more spaces.
  • One end of the refrigerant channel 45 is provided so as to penetrate the partition wall 411 from the lower side (lower in the gravitational direction) to the upper side (upward in the gravitational direction) shown in the drawing.
  • the plurality of refrigerant passages of the refrigerant flow channel 45 communicate with at least one of the spaces partitioned by the partition wall 411.
  • the cold storage material 60 is disposed in a lower space between the partition wall 411 and the inner wall of the first header 41 and from which one end of the coolant channel 45 does not protrude.
  • the cold storage material 60 may be arranged in a space in the first header 41 where the plurality of refrigerant passages of the refrigerant flow path 45 are not in communication.
  • a partition wall 431 is provided inside the third header 43.
  • the partition wall 431 is provided in close contact with the inner wall of the third header 43.
  • the partition wall 431 partitions the inside of the third header 43 into two or more spaces.
  • One end of the refrigerant channel 45 is provided so as to penetrate the partition wall 431 from the lower side (lower in the gravitational direction) to the upper side (upward in the gravitational direction) shown in the drawing.
  • the plurality of refrigerant passages of the refrigerant channel 45 communicate with at least one of the spaces partitioned by the partition wall 431.
  • the cold storage material 60 is disposed in a lower space between the partition wall 431 and the inner wall of the first header 43 and from which one end of the refrigerant channel 45 does not protrude.
  • the cool storage material 60 may be arranged in a space in the third header 43 where the plurality of refrigerant passages of the refrigerant flow path 45 are not in communication.
  • the cool storage material 60 is replaced with the first header 41 and the third header by a simple method of providing the partition wall 411 and the partition wall 431 inside the first header 41 and the third header 43 arranged above the gravity direction. 43 can be disposed inside. Since the cold storage material 60 is disposed only in the space below the gravity direction where the refrigerant flow path 45 does not protrude from the partition wall 411 and the partition wall 431, the cold storage material 60 can exhibit the cold storage effect without inhibiting the flow of the refrigerant. it can.
  • the refrigerant stops flowing when the automobile on which the refrigeration cycle apparatus 1 is mounted stops.
  • the refrigerant remaining in the evaporator 40 evaporates and gasifies, it is cooled by the regenerator 60 and liquefied again. It is supplied again into the refrigerant flow path 45.
  • cold air can be supplied through the first heat exchange unit 48 and the second heat exchange unit 49 which are the core portions.
  • the cold storage material 61 is disposed inside the first header 41 and the third header 43 and between the refrigerant flow path 45, the inner wall of the first header 41, and the inner wall of the third header 43.
  • the cold storage material 61 is filled in a cylindrical container, and is arranged at a predetermined distance from one end of the refrigerant flow path 45.
  • the regenerator material 61 is disposed in the first header 41 and the third header 43 in a manner that can affect the flow of the refrigerant. Therefore, as shown in FIG. 7, it is preferable to dispose the cold storage material 61 in the vicinity of the inlet portion 412 that is the inlet of the refrigerant to the first header 41.
  • the cool storage agent 61 may be disposed so as to overlap the side plate 50 close to the inlet portion 412 in the longitudinal direction of the refrigerant flow path 45.
  • the refrigerant supplied to the evaporator 40 is a liquid refrigerant
  • the refrigerant flowing out of the evaporator 40 is a gas refrigerant. Since the increase in pressure loss is low for liquid refrigerant and high for gas refrigerant, the effect of pressure loss can be reduced by disposing the regenerator 61 in the vicinity of the inlet 412 to which liquid refrigerant is supplied.
  • the refrigerant stops flowing when the automobile on which the refrigeration cycle apparatus 1 is mounted stops.
  • the regenerator material It is cooled by 61, liquefied again, and supplied again into the refrigerant flow path 45.
  • cold air can be supplied through the first heat exchange unit 48 and the second heat exchange unit 49 which are the core portions.
  • the cold storage material 62 is disposed outside the first header 41 and the third header 43 and between the outer peripheral surface of the first header 41 and the outer peripheral surface of the third header 43, and the holding unit 70 and the holding unit 71. ing. A pair of recesses along the longitudinal direction of the first header 41 and the third header 43 is formed between the first header 41 and the third header 43, and the holding unit 70 closes and holds one of the recesses. The portion 71 closes the other concave portion.
  • the cold storage material 62 is disposed in a space in which a pair of concave portions are closed by the holding portions 70 and 71.
  • the regenerator material 62 of the third embodiment is disposed outside the first header 41 and the third header 43, and thus has no effect on the flow of the refrigerant.
  • the mechanism of cold air supply when the refrigerant stops flowing when the automobile on which the refrigeration cycle apparatus 1 is mounted is the same as in the first embodiment and the second embodiment.
  • a fourth embodiment in which the cold storage material is arranged so as not to hinder the air flow in the air passage will be described with reference to FIGS. 9 and 10.
  • the cold storage material 63 is disposed outside the first header 41 and the third header 43 and between the outer peripheral surface of the first header 41 and the outer peripheral surface of the third header 43 and the packing 75 (holding portion). Yes.
  • a packing 75 is provided in order to maintain airtightness (wind leakage inhibiting property) with the housing case.
  • the packing 75 is provided so as to cover the outer circumferences of the first header 41 and the third header 43.
  • the cold storage material 63 is disposed along the inner surface of the packing 75 and is in partial contact with the first header 41 and the third header 43.
  • the refrigerant flow path 45 in which the cold storage material 64 is arranged instead of the side plate 50 is arranged on the outermost side of the plurality of refrigerant flow paths 45.
  • the cold storage material 64 is disposed along the outer surface of the refrigerant flow path 45 disposed on the outermost side. In this way, by cooling a part of the refrigerant flow paths 45 with the cold storage material 64, the inside of the refrigerant flow path 45 in contact with the cold storage material 64 can maintain the two-phase state of the liquid refrigerant and the gas refrigerant.
  • the cool storage material 64 is preferably provided on the joint side where the gas refrigerant flows out of the evaporator 40.
  • the plurality of refrigerant channels 45 are arranged in two rows so as to form a pair along the air passage.
  • the cool storage material 65 is arrange
  • the refrigerant stops flowing when the automobile on which the refrigeration cycle apparatus 1 is mounted, but when the temperature of the refrigerant remaining in the refrigerant flow path 45 rises, it is cooled by the cold storage material 65 and liquefied again into the refrigerant flow path 45. Liquid refrigerant remains.
  • cold air can be supplied through the first heat exchange unit 48 and the second heat exchange unit 49 which are the core portions.
  • the cold storage container 47 arrange
  • FIG. 13 schematically shows the refrigerant flow in each of the above-described embodiments.
  • the first header 41, the second header 42, the third header 43, and the fourth header 44 are each divided into two sections, a first section and a second section.
  • the refrigerant that has flowed into the first section of the first header 41 flows into the first section of the second header 42 through the refrigerant flow path 45.
  • 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 that has flowed into the second section of the second header 42 flows into the second section of the first header 41 through the refrigerant flow path 45.
  • 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 flow path 45.
  • 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 flow path 45.
  • the refrigerant flowing into the first section of the third header 43 flows out to the outside.
  • the embodiment of the present disclosure is not limited to the refrigerant flow described above. As shown in FIG. 14, the first header 41A, the second header 42A, the third header 43A, and the fourth header 44A can be eliminated.
  • the refrigerant that has flowed into the first header 41A flows into the second header 42A through the refrigerant flow path 45. 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 through the refrigerant flow path 45 into the third header 43A. The refrigerant flowing into the third header 43A flows out to the outside.
  • the cold storage agents 60, 61, 62, 63, 64, and 65 can also be applied to those constituting the refrigerant flow, such as the cold storage heat exchanger 40A.
  • 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 flow path 45 into the first section of the second header 42B.
  • 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 flow path 45 into the second section of the first header 41B.
  • 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 through the refrigerant flow path 45 into the third section of the second header 42B.
  • the refrigerant flowing into the third section of the second header 42B flows into the third section of the fourth header 44B.
  • the refrigerant that has flowed into the third section of the fourth header 44B flows through the refrigerant flow path 45 into the third section of the third header 43B.
  • 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 that has flowed into the second section of the third header 43B flows through the refrigerant flow path 45 into the second section of the fourth header 44B.
  • 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 that has flowed into the first section of the fourth header 44B flows through the refrigerant flow path 45 into the first section of the third header 43B.
  • the refrigerant that has flowed into the first section of the third header 43B flows out to the outside.
  • the cold storage agents 60, 61, 62, 63, 64, and 65 can also be applied to a refrigerant that constitutes a refrigerant flow such as the cold storage heat exchanger 40B.
  • 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.
  • 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 arranged on the lower side in the gravity direction, and the second header 42R and the fourth header 44R are arranged on the upper side in the gravity direction. .
  • the refrigerant that has flowed into the first section of the first header 41R flows through the refrigerant flow path 45 into the first section of the second header 42R.
  • 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 flow path 45 into the second section of the first header 41R.
  • 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 flow path 45 into the second section of the fourth header 44R.
  • 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 flow path 45 into the first section of the third header 43R.
  • the refrigerant flowing into the first section of the third header 43R flows out to the outside.
  • the second header 42R and the fourth header 44R correspond to the first header tank of the present disclosure, and the first header 41R and the third header 43R are the second header of the present disclosure. Corresponds to the header tank. Therefore, the cool storage agents 60, 61, 62, and 63 are provided in the second header 42R and the fourth header 44R.
  • a cold storage heat exchanger 40RA shown in FIG. 17 is obtained by reversing the cold storage heat exchanger 40A shown in FIG.
  • the cold storage heat exchanger 40RA includes a second header 42RA and a fourth header 44RA corresponding to the first header tank of the present disclosure, and a first header 41RA and a third header 43RA corresponding to the second header tank of the present disclosure. I have. Therefore, the cool storage agents 60, 61, 62, and 63 are provided in the second header 42RA and the fourth header 44RA.
  • a cold storage heat exchanger 40RB shown in FIG. 18 is obtained by reversing the cold storage heat exchanger 40B shown in FIG.
  • the cold storage heat exchanger 40RB includes a second header 42RB and a fourth header 44RB corresponding to the first header tank of the present disclosure, and a first header 41RB and a third header 43RB corresponding to the second header tank of the present disclosure. I have. Therefore, the cool storage agents 60, 61, 62, and 63 are provided in the second header 42RB and the fourth header 44RB.
  • regenerator material is arranged in a region that does not inhibit the air flow
  • regenerator material may also be arranged in a region that inhibits the air flow.

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

Abstract

La présente invention concerne un échangeur de chaleur à accumulation de froid comprenant : une pluralité de trajets d'écoulement de fluide frigorigène (45) qui présentent des voies de passage de fluide frigorigène et qui sont disposés de telle sorte que des voies de passage d'air sont formées en créant des intervalles entre les voies de passage de fluide frigorigène ; des ailettes (46) disposées sur les voies de passage d'air ; un premier réservoir de colonne avec lequel un côté d'extrémité de la pluralité de voies de passage de fluide frigorigène communique ; un second réservoir de colonne avec lequel l'autre côté d'extrémité de la pluralité de voies de passage de fluide frigorigène communique ; et un matériau d'accumulation de froid (60) qui est refroidi par évaporation d'un fluide frigorigène qui a été décompressée par un décompresseur lorsqu'un compresseur est entraîné, mais peut rayonner le froid lorsque le compresseur est arrêté. Le matériau d'accumulation de froid est disposé dans une région où l'écoulement d'air des voies de passage d'air n'est pas entravé. Grâce à cette configuration, il est possible d'augmenter la quantité de matériau d'accumulation de froid disposée tout en réduisant l'influence sur la circulation d'air.
PCT/JP2016/001971 2015-04-21 2016-04-11 Échangeur de chaleur à accumulation de froid WO2016170751A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015-086613 2015-04-21
JP2015086613A JP6540190B2 (ja) 2015-04-21 2015-04-21 蓄冷熱交換器

Publications (1)

Publication Number Publication Date
WO2016170751A1 true WO2016170751A1 (fr) 2016-10-27

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JP2015148392A (ja) * 2014-02-07 2015-08-20 株式会社ケーヒン・サーマル・テクノロジー 熱交換器
FR3056732A1 (fr) * 2016-09-29 2018-03-30 Valeo Systemes Thermiques Boite collectrice pour echangeur de chaleur avec materiau a changement de phase encapsule dans des tubes
WO2018060646A1 (fr) * 2016-09-28 2018-04-05 Valeo Systemes Thermiques Boite collectrice comprenant un matériau à changement de phase et échangeur de chaleur comprenant une telle boite collectrice

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KR102161528B1 (ko) * 2017-06-05 2020-10-06 한온시스템 주식회사 축냉 열교환기
JP2019124392A (ja) * 2018-01-15 2019-07-25 株式会社デンソー 蓄熱装置
JP6954138B2 (ja) * 2018-01-15 2021-10-27 株式会社デンソー 蓄熱装置
JP2019152377A (ja) * 2018-03-02 2019-09-12 株式会社デンソー 熱交換器

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015148392A (ja) * 2014-02-07 2015-08-20 株式会社ケーヒン・サーマル・テクノロジー 熱交換器
WO2018060646A1 (fr) * 2016-09-28 2018-04-05 Valeo Systemes Thermiques Boite collectrice comprenant un matériau à changement de phase et échangeur de chaleur comprenant une telle boite collectrice
FR3056732A1 (fr) * 2016-09-29 2018-03-30 Valeo Systemes Thermiques Boite collectrice pour echangeur de chaleur avec materiau a changement de phase encapsule dans des tubes

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