WO2018088166A1 - 内部熱交換器一体型アキュムレータ及びこれを用いた冷凍サイクル - Google Patents

内部熱交換器一体型アキュムレータ及びこれを用いた冷凍サイクル Download PDF

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Publication number
WO2018088166A1
WO2018088166A1 PCT/JP2017/037909 JP2017037909W WO2018088166A1 WO 2018088166 A1 WO2018088166 A1 WO 2018088166A1 JP 2017037909 W JP2017037909 W JP 2017037909W WO 2018088166 A1 WO2018088166 A1 WO 2018088166A1
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WO
WIPO (PCT)
Prior art keywords
heat exchange
temperature refrigerant
low
internal heat
exchange pipe
Prior art date
Application number
PCT/JP2017/037909
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English (en)
French (fr)
Japanese (ja)
Inventor
俊 堀込
Original Assignee
サンデンホールディングス株式会社
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Application filed by サンデンホールディングス株式会社 filed Critical サンデンホールディングス株式会社
Priority to DE112017005621.7T priority Critical patent/DE112017005621T5/de
Publication of WO2018088166A1 publication Critical patent/WO2018088166A1/ja

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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
    • B60H1/00492—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
    • B60H1/00321—Heat exchangers for air-conditioning devices
    • B60H1/00335—Heat exchangers for air-conditioning devices of the gas-air type
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/06—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with the heat-exchange conduits forming part of, or being attached to, the tank containing the body of fluid
    • 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
    • F28D20/0034—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0016—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being bent
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D2020/0065—Details, e.g. particular heat storage tanks, auxiliary members within tanks
    • F28D2020/0078—Heat exchanger arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2270/00—Thermal insulation; Thermal decoupling
    • 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 invention relates to an internal heat exchanger integrated accumulator used in a refrigeration circuit of a vehicle air conditioner and a refrigeration cycle using the accumulator.
  • an air conditioner used in a vehicle such as a passenger car constitutes a refrigeration cycle by connecting a compressor 1, an evaporator 2, a gas cooler 3, an expansion valve 4, and an accumulator 5 with refrigerant pipes as shown in FIG.
  • the refrigerant is circulated to the refrigeration circuit by the compressor 1.
  • the refrigeration efficiency is improved by exchanging heat between the low-temperature refrigerant flowing out from the evaporator 2 and the high-temperature refrigerant flowing out from the gas cooler 3 by the internal heat exchanger 6 (for example, patents). Reference 1).
  • An internal heat exchanger-integrated accumulator 7 shown in FIG. 17 is obtained by partitioning a cylindrical main body 7a into two upper and lower spaces 7c and 7d by a partition wall 7b, and disposing a heat exchange pipe 7e in the upper space 7c. After the low-temperature refrigerant flowing into the lower space from the outside is gas-liquid separated, the gaseous low-temperature refrigerant flows into the upper space 7c through the communication hole 7f of the partition wall 7b, and the upper space 7c. Heat is exchanged between the low-temperature refrigerant flowing through the inside and the high-temperature refrigerant flowing through the heat exchange pipe 7e.
  • the cylindrical body 7a is partitioned into two upper and lower spaces by the partition wall 7b, so that the height of the upper space 7c can be increased. Accordingly, the refrigerant flow distance from the communication hole 7f of the partition wall 7b to the refrigerant outlet of the upper space 7c is shortened. For this reason, the low-temperature refrigerant cannot sufficiently exchange heat with the heat exchange pipe 7e in the upper space 7c, and there is a problem in that the heat radiation effect from the heat exchange pipe 7e to the low-temperature refrigerant is low.
  • the heat exchange pipe 7e since the heat exchange pipe 7e is merely disposed in the upper space 7c, the heat exchange pipe 7e can exchange heat only with the surrounding low-temperature refrigerant. Also, there is a problem that the heat radiation effect from the heat exchange pipe 7e to the low-temperature refrigerant is low.
  • the present invention has been made in view of the above-mentioned problems, and an object of the present invention is to use an internal heat exchanger integrated accumulator capable of improving the heat exchange efficiency between a low-temperature refrigerant and a heat exchange pipe, and the same. It is to provide a refrigeration cycle.
  • an internal heat exchanger-integrated accumulator of the present invention is provided in a cylindrical outer member extending in the vertical direction, a cylindrical inner member disposed in the outer member, and the inner member.
  • An accumulator chamber, an internal heat exchange chamber provided between the outer member and the inner member, and a heat exchange pipe disposed in the internal heat exchange chamber, and the low-temperature refrigerant flowing from the outside into the accumulator chamber After gas-liquid separation in the room, gaseous low-temperature refrigerant is allowed to flow into the internal heat exchange chamber, and heat exchange is performed between the low-temperature refrigerant flowing through the internal heat exchange chamber and the high-temperature refrigerant flowing through the heat exchange pipe.
  • An internal heat exchanger integrated accumulator wherein the outer member, the inner member and the heat exchange pipe are formed of aluminum, and the heat exchange pipe is disposed between the outer member and the inner member.
  • the outer member and the inner member are formed so as to spiral in the circumferential direction, and the heat exchange pipe is brazed to the inner circumferential surface of the outer member and the outer circumferential surface of the inner member over the circumferential direction of the outer member and the inner member.
  • the heat exchange pipe is formed between the outer member and the inner member so as to extend spirally in the circumferential direction of the outer member and the inner member, and the low-temperature refrigerant is circulated between the spiral portions of the heat exchange pipe. Since the spiral refrigerant flow passage is formed, the heat exchange pipe is formed with a sufficient length, and the low-temperature refrigerant flows through the spiral refrigerant flow passage along the heat exchange pipe. The distribution distance of the low-temperature refrigerant in the heat exchange chamber is increased.
  • the low-temperature refrigerant in the refrigerant flow passage and the high-temperature refrigerant in the heat exchange pipe flow in opposite directions, the flows of the low-temperature refrigerant and the high-temperature refrigerant in the internal heat exchange chamber are opposed to each other.
  • at least the outer member, the inner member, and the heat exchange pipe are formed of aluminum, brazing is possible, and the heat exchange pipe is disposed on the inner peripheral surface of the outer member and the outer peripheral surface of the inner member.
  • the outer member, the inner member and the heat exchange pipe are firmly joined by brazing.
  • the heat exchange pipe can be formed to a sufficient length, and the circulation distance of the low-temperature refrigerant in the internal heat exchange chamber can be increased, so that the low-temperature refrigerant and the heat exchange pipe are sufficiently connected. Heat exchange can be performed, and the heat radiation effect from the heat exchange pipe to the low-temperature refrigerant can be enhanced.
  • the flow of the low-temperature refrigerant and the high-temperature refrigerant in the internal heat exchange chamber can be counterflowed, which is extremely advantageous for improving the heat exchange efficiency between the low-temperature refrigerant and the high-temperature refrigerant.
  • the outer member, the inner member, and the heat exchange pipe can be firmly joined by brazing, the strength of the entire accumulator can be increased. As a result, sufficient strength can be ensured even if the plate thickness of the outer member and the inner member is reduced, so that the weight can be reduced by reducing the thickness of the member.
  • the perspective view of the internal heat exchanger integrated accumulator which shows the 1st Embodiment of this invention
  • Front sectional view of the internal heat exchanger integrated accumulator Disassembled perspective view of accumulator with integrated internal heat exchanger Front sectional view of the main part of the internal heat exchanger integrated accumulator
  • Front sectional view of the internal heat exchanger integrated accumulator Front sectional view of the internal heat exchanger integrated accumulator
  • Configuration diagram of refrigeration cycle with an internal heat exchanger integrated accumulator Partial schematic side view of a vehicle with an internal heat exchanger integrated accumulator Partial schematic side view of a vehicle equipped with a conventional internal heat exchanger integrated accumulator
  • the perspective view of the internal heat exchanger integrated accumulator which shows the 2nd Embodiment of this invention.
  • FIGS. 1 to 8 show a first embodiment of the present invention, which shows an aluminum internal heat exchanger integrated accumulator used in a vehicle air conditioner.
  • the internal heat exchanger integrated accumulator 10 of this embodiment is provided in a cylindrical outer member 20 extending in the vertical direction, a cylindrical inner member 30 disposed in the outer member 20, and the inner member 30.
  • the heat exchange chambers 50 are partitioned from each other in the radial direction of the outer member 20 via the inner member 30.
  • the outer member 20 is formed in a vertically long cylindrical shape having an upper end opened, and the upper end is closed by a circular upper surface plate 21.
  • the upper surface plate 21 is provided with an inflow pipe 22 through which a low-temperature refrigerant flows.
  • the inflow pipe 22 passes through the center of the upper surface plate 21 and extends vertically in and out of the outer member 20.
  • the upper surface plate 21 is provided with a hole 21 a that passes through one end side of the heat exchange pipe 60, and the hole 21 a is disposed on the peripheral side of the upper surface plate 21.
  • the bottom surface of the outer member 20 is provided with an outflow pipe 23 through which the low-temperature refrigerant flows out.
  • the outflow pipe 23 extends downward from the bottom surface of the outer member 20.
  • a hole 20 a through which the other end of the heat exchange pipe 60 is inserted is provided on the bottom surface of the outer member 20, and the hole 20 a is disposed on the peripheral side of the bottom surface of the outer member 20.
  • the inner member 30 is formed in a vertically long cylindrical shape having an outer diameter smaller than that of the outer member 20, and the upper end and the lower end thereof are opened.
  • the inner member 30 is disposed concentrically with the outer member 20 so as to have a uniform circumferential distance between the outer peripheral surface of the inner member 30 and the inner peripheral surface of the outer member 20, and the lower end thereof is joined to the bottom surface of the outer member 20. ing.
  • the inner member 30 is formed such that the upper end is positioned lower than the upper surface plate 21 of the outer member 20, and a gap is formed between the upper end of the inner member 30 and the upper surface plate 21 of the outer member 20.
  • the outflow pipe 23 provided on the bottom surface of the outer member 20 is disposed between the inner member 30 and the outer member 20.
  • the inner member 30 is provided with an oil outflow hole 31 through which lubricating oil flows out.
  • the oil outflow hole 31 is disposed on the lower end side of the peripheral surface of the inner member 30.
  • the accumulator chamber 40 is a space surrounded by the inner peripheral surface of the inner member 30 and the bottom surface of the outer member 20, and stores liquid low-temperature refrigerant flowing from the inflow pipe 22.
  • the lower end side of the inflow pipe 22 is disposed so as to extend from the center in the radial direction of the inner member 30 into the accumulator chamber 40.
  • the internal heat exchange chamber 50 includes a space between the outer member 20 and the inner member 30 and circulates a gaseous low-temperature refrigerant flowing from the inflow pipe 22.
  • the heat exchange pipe 60 is formed so as to extend spirally in the circumferential direction of the outer member 20 and the inner member 30 from the upper end side to the lower end side of the internal heat exchange chamber 50, and the outer member 20 is formed on the lower end side thereof.
  • a straight inflow pipe portion 61 extending through the bottom surface of the outer member 20 and extending outward is formed at the upper end of the straight inflow pipe portion 61 extending through the upper surface plate 21 of the outer member 20. Is formed.
  • the spiral portion 63 of the heat exchange pipe 60 is disposed between the outer member 20 and the inner member 30, and is disposed on the inner peripheral surface of the outer member 20 and the outer peripheral surface of the inner member 30 so as to wind the inner member 30. As shown in FIG. 4, the contact portion between the outer member 20 and the inner member 30 is joined over the circumferential direction of the outer member 20 and the inner member 30 by brazing 60a.
  • a spiral portion 63 of the heat exchange pipe 60 is disposed in the internal heat exchange chamber 50, and a spiral refrigerant flow passage 51 is formed in the internal heat exchange chamber 60 by the spiral portion 63 of the heat exchange pipe 60. . That is, the refrigerant flow passage 51 is formed between the spiral portion 63 of the heat exchange pipe 60 and the peripheral surfaces of the outer member 20 and the inner member 30, and the low-temperature refrigerant flowing from above the inner heat exchange chamber 50
  • the outside of the heat exchange pipe 60 flows along the spiral portion 63 of the heat exchange pipe 60 and flows out from the lower end of the internal heat exchange chamber 50 to the outside through the outflow pipe 23.
  • the internal heat exchanger integrated accumulator 10 configured as described above is used in the refrigeration cycle shown in FIG. 7, and a carbon dioxide refrigerant is used as a refrigerant in the refrigeration cycle. That is, in the internal heat exchanger integrated accumulator 10, the refrigerant discharge side of the evaporator 2 is connected to the inflow pipe 22, and the refrigerant suction side of the compressor 1 is connected to the outflow pipe 23.
  • the refrigerant suction side of the expansion valve 4 is connected to the outflow pipe portion 61 of the heat exchange pipe 60, and the refrigerant discharge side of the gas cooler 3 is connected to the inflow pipe portion 62 of the heat exchange pipe 60.
  • low-temperature refrigerant low-pressure refrigerant
  • high-temperature refrigerant high-pressure refrigerant
  • the high-temperature refrigerant flowing through the heat exchange pipe 60 becomes a low-temperature refrigerant through the expansion valve 4 and flows into the evaporator 2, absorbs heat from the external air by the evaporator 2, then flows into the accumulator chamber 30, and from the accumulator chamber 30 to the internal heat exchange chamber. After 50, it is sucked into the compressor 1.
  • the gas-liquid mixed low-temperature refrigerant flows into the accumulator chamber 30 from the inflow pipe 22, and the gaseous low-temperature refrigerant R 1, liquid low-temperature refrigerant R 2, and lubricating oil J are sequentially supplied from above.
  • the gas and liquid are separated by the accumulation, and only the gaseous low-temperature refrigerant R 1 flows out from the upper end of the accumulator chamber 30 to the internal heat exchange chamber 50.
  • the low-temperature refrigerant that has flowed into the internal heat exchange chamber 50 flows through the refrigerant flow passage 51 from the upper side to the lower side of the internal heat exchange chamber 50 and flows out from the outflow pipe 23 to the outside.
  • the low-temperature refrigerant in the internal heat exchange chamber 50 flows through the spiral refrigerant flow passage 51 along the heat exchange pipe 60, the high-temperature refrigerant in the heat exchange pipe 60 and the low-temperature refrigerant in the refrigerant flow passage 51. Heat is efficiently exchanged with the refrigerant. Further, the lubricating oil J collected in the lower part of the accumulator chamber 30 flows out from the oil outflow hole 31 to the bottom of the internal heat exchange chamber 50 and flows out from the outflow pipe 23 together with the low-temperature refrigerant.
  • the high-temperature refrigerant flowing from the inflow pipe portion 61 into the heat exchange pipe 60 of the internal heat exchange chamber 50 flows through the spiral portion 63 of the heat exchange pipe 60 while flowing through the refrigerant flow path. After radiating heat to the 51 gaseous low-temperature refrigerant, it flows out from the outflow pipe portion 62 to the outside. At that time, the low-temperature refrigerant circulates in the internal heat exchange chamber 50 from the upper side to the lower side, and the high-temperature refrigerant flows in the heat exchange pipe 60 from the lower side to the upper side. The flow of the refrigerant and the high-temperature refrigerant becomes an opposite flow.
  • the internal heat exchanger integrated accumulator 10 is installed in the engine room of the vehicle S as shown in FIG. At this time, since the outflow side of the high-temperature refrigerant and the inflow side of the low-temperature refrigerant are arranged on the upper end side of the outer member 20, the air inside the vehicle via the high-temperature refrigerant outflow side pipe 10a and the low-temperature refrigerant inflow side pipe 10b. It is connected to the evaporator 2 in the harmony unit 8 with the shortest distance.
  • the refrigerant outflow side of the compressor 1 and the refrigerant outflow side of the gas cooler 3 are arranged in the lower part of the engine room, but the high temperature refrigerant inflow side and the low temperature refrigerant outflow side of the accumulator 10 are on the lower end side of the outer member 20. Since it is arranged, it is connected to the compressor 1 and the gas cooler 3 through the shortest distance via the high-temperature refrigerant inflow pipe 10c and the low-temperature refrigerant outflow pipe 10d. That is, as shown in FIG.
  • the internal heat exchanger integrated accumulator 9 has the high-temperature refrigerant inflow side and outflow side and the low-temperature refrigerant inflow side and outflow side all at the upper end. Therefore, the outflow side of the high-temperature refrigerant and the inflow side of the low-temperature refrigerant are at the shortest distance from the evaporator 2 in the air conditioning unit 8 inside the vehicle via the outflow-side pipe 9a of the high-temperature refrigerant and the inflow-side pipe 9b of the low-temperature refrigerant.
  • the high-temperature refrigerant inflow side and the low-temperature refrigerant outflow side of the accumulator 9 are connected to each other through the high-temperature refrigerant inflow pipe 9c and the low-temperature refrigerant outflow pipe 9d. And the refrigerant outflow side of the gas cooler 3. Therefore, the length of the pipe is longer than that of the present embodiment by the amount corresponding to the rising portion H1 of the high temperature refrigerant inflow side piping 9c and the rising portion H2 of the low temperature refrigerant outflow side piping 9d.
  • the heat exchange pipe 60 is formed between the outer member 20 and the inner member 30 so as to extend spirally in the circumferential direction of the outer member 20 and the inner member 30, and heat exchange is performed. Since the refrigerant flow passage 51 that circulates the low-temperature refrigerant is formed between the spiral portions 63 of the pipe 60, the heat exchange pipe 60 can be formed with a sufficient length, and the low-temperature refrigerant can be moved along the heat exchange pipe 60. The spiral refrigerant flow passage 51 can be circulated.
  • the low-temperature refrigerant and the heat exchange pipe 60 can sufficiently exchange heat, and the heat exchange pipe 60 to the low-temperature refrigerant can be exchanged.
  • the heat dissipation effect can be enhanced.
  • the low-temperature refrigerant in the refrigerant flow passage 51 and the high-temperature refrigerant in the heat exchange pipe 60 are circulated in opposite directions, the flows of the low-temperature refrigerant and the high-temperature refrigerant in the internal heat exchange chamber 50 face each other.
  • the heat exchange efficiency between the low-temperature refrigerant and the high-temperature refrigerant is extremely advantageous.
  • the outer member 20, the inner member 30, and the heat exchange pipe 60 are made of aluminum, brazing can be performed and strength can be improved. That is, since the heat exchange pipe 60 is brazed to the inner peripheral surface of the outer member 20 and the outer peripheral surface of the inner member 30 in the circumferential direction of the outer member 20 and the inner member 30, the outer member 20, the inner member 30, and the heat exchange The pipe 60 can be firmly joined, and the strength of the entire accumulator can be increased. Thereby, even if the plate thickness of the outer member 20 and the inner member 30 is reduced, sufficient strength can be ensured, and the weight can be reduced by reducing the thickness of the member.
  • the high temperature refrigerant outflow side and the low temperature refrigerant inflow side are arranged on the upper end side of the outer member 20, and the high temperature refrigerant inflow side and the low temperature refrigerant outflow side are arranged on the lower end side of the outer member 20. Even when the refrigerant outflow side of the gas cooler 3 and the refrigerant outflow side of the gas cooler 3 are arranged in the lower part of the engine room, the high-temperature refrigerant inflow pipe 10c and the low-temperature refrigerant outflow pipe 10d are connected to the compressor 1 and the gas cooler 3 with the shortest distance. It is possible to reduce the cost and pressure loss by shortening the piping.
  • FIG. 10 shows a second embodiment of the present invention, and the same components as those in the first embodiment are denoted by the same reference numerals.
  • the inner member 30 is formed so that the upper end is positioned lower than the upper surface plate 21 of the outer member 20, and the low-temperature refrigerant is interposed between the upper end of the inner member 30 and the upper surface plate 21 of the outer member 20.
  • the inner member 70 of the present embodiment is formed to have the same height as the outer member 20, and the upper end of the inner member 70 is joined to the upper surface plate 21.
  • An outflow hole 71 through which the low-temperature refrigerant in the accumulator chamber 30 flows out to the internal heat exchange chamber 50 is provided on the upper side surface of the inner member 70.
  • 11 and 12 show a third embodiment of the present invention, and the same reference numerals are given to the same components as those in the first embodiment.
  • the spiral portions 63 of the heat exchange pipe 60 are shown at regular intervals.
  • the heat exchange pipe 80 of the present embodiment is provided between the inflow pipe portion 81 and the outflow pipe portion 82.
  • the interval P between the spiral portions 83 is formed so that the downstream side is gradually wider than the upstream side in the circulation direction of the high-temperature refrigerant.
  • the downstream side of the refrigerant cross-sectional area of the refrigerant flow passage 51 of the low-temperature refrigerant formed between the spiral portions 83 of the heat exchange pipe 80 is gradually larger than the upstream side in the refrigerant flow direction. Even if the volume is increased by being heated by the exchange pipe 80, there is an advantage that the pressure loss of the refrigerant flow passage 51 can be suppressed.
  • the flow passage cross-sectional area of the heat exchange pipe 80 is S1
  • the flow passage cross-sectional area of the refrigerant flow passage 51 is S2
  • the ratio of the flow passage cross-sectional areas is S1: S2.
  • the refrigerant flow passage 51 is formed so that S2 becomes 5 or more when S1 is 4. That is, the ratio S1: S2 of the flow path cross-sectional area of the portion where the interval P of the spiral portion 83 is the smallest (the most upstream side of the refrigerant flow passage 51) is 4: 5, and as it goes to the downstream side of the refrigerant flow passage 51.
  • the flow passage cross-sectional area S2 of the refrigerant flow passage 51 is formed so as to gradually increase.
  • the flow passage sectional area S2 of the refrigerant flow passage 51 becomes larger than the flow passage sectional area of the heat exchange pipe 80 with respect to S1, so that the flow amount of the low temperature refrigerant with respect to the high temperature refrigerant in the internal heat exchange chamber 50 is sufficiently increased.
  • the high-temperature refrigerant in the heat exchange pipe 80 and the low-temperature refrigerant in the refrigerant flow passage 51 can always exchange heat efficiently.
  • the configuration in which the refrigerant flow passage 51 is formed so that S2 is 5 or more when the ratio of the channel cross-sectional area is S1: S2 and S1 is 4, can be applied to other embodiments. it can.
  • FIG. 13 shows a fourth embodiment of the present invention, and the same components as those in the first embodiment are denoted by the same reference numerals.
  • a heat insulating layer 32 is provided between the accumulator chamber 40 and the heat exchange pipe 60, and the heat insulating layer 32 is formed by applying a well-known heat insulating paint to the inner surface of the inner member 30.
  • the heat insulating layer 32 insulates between the accumulator chamber 40 and the heat exchange pipe 60, so that the liquid low-temperature refrigerant R 2 ⁇ stored in the accumulator chamber 40 evaporates by heating the heat exchange pipe 60. Therefore, the liquid low-temperature refrigerant R2 can be reliably stored in the accumulator chamber 40.
  • the heat of the high-temperature refrigerant in the heat exchange pipe 60 is not taken away by the low-temperature refrigerant in the accumulator chamber 40, the low-temperature refrigerant in the refrigerant flow passage 51 of the internal heat exchange chamber 50 is sufficiently heated by the high-temperature refrigerant.
  • the heat exchange efficiency of the internal heat exchange chamber 50 is not lowered.
  • the heat insulating paint is used for the heat insulating layer 32, the heat insulating layer 32 can be easily formed by applying the heat insulating paint to the inner surface of the inner member 30, and the productivity can be improved.
  • FIG. 14 shows a fifth embodiment of the present invention, in which components equivalent to those in the first embodiment are denoted by the same reference numerals.
  • This embodiment is another embodiment in which a heat insulating layer is provided between the accumulator chamber 40 and the heat exchange pipe 60. That is, the inner member 30 of the present embodiment is formed by inner and outer double cylindrical members 33 and 34 having a gap, and a heat insulating layer 35 made of an air layer is formed between the cylindrical members 33 and 34. As a result, as in the fourth embodiment, the effect of the heat insulating layer 35 can be obtained, and the heat insulating layer 35 can be formed only by the cylindrical members 33 and 34. Therefore, a common material ( Aluminum) can be used, and processing and assembly can be easily performed.
  • a common material Aluminum
  • FIG. 15 shows a sixth embodiment of the present invention, and the same components as those in the first embodiment are denoted by the same reference numerals.
  • the internal heat exchanger integrated accumulator 10 of this embodiment is provided in a cylindrical outer member 90 extending in the vertical direction, a cylindrical inner member 100 disposed in the outer member 90, and the inner member 100.
  • the heat exchange chambers 120 are partitioned from each other in the radial direction of the outer member 90 via the inner member 100.
  • the outer member 90 is formed in a vertically long cylindrical shape having an upper end opened, and the upper end is closed by a circular upper surface plate 91.
  • the upper surface plate 21 is provided with an inflow pipe 92 through which a low-temperature refrigerant flows.
  • the inflow pipe 92 extends through the center of the upper surface plate 91 in and out of the outer member 90.
  • An outflow pipe 93 through which the low-temperature refrigerant flows out is provided on the lower side surface of the outer member 90, and the outflow pipe 93 extends from the side surface of the outer member 90 to the outside.
  • the inner member 100 is formed in a vertically long cylindrical shape having an outer diameter smaller than that of the outer member 90 and has an upper end opened.
  • the inner member 100 is arranged concentrically with the outer member 90 so as to have a uniform circumferential distance between the outer peripheral surface and the inner peripheral surface of the outer member 20, and the lower end side penetrates the bottom surface of the outer member 90. Then, it extends below the outer member 90.
  • the inner member 100 is formed such that the upper end is positioned lower than the upper surface plate 91 of the outer member 90, and a gap is formed between the upper end of the inner member 100 and the upper surface plate 91 of the outer member 20. .
  • the outflow pipe 93 of the outer member 90 extends downward from the outer member 90, bends in the lateral direction, extends to the lower side of the inner member 100, and is further bent downward.
  • An oil outflow pipe 101 for outflowing lubricating oil is provided on the bottom surface of the inner member 100, and the oil outflow pipe 101 is connected to the outflow pipe 93.
  • the accumulator chamber 110 is a space surrounded by the inner peripheral surface of the inner member 100 and the bottom surface of the outer member 90, and stores liquid low-temperature refrigerant flowing from the inflow pipe 92.
  • the lower end side of the inflow pipe 92 is disposed so as to extend from the center in the radial direction of the inner member 100 into the accumulator chamber 110.
  • the internal heat exchange chamber 120 is a space between the outer member 90 and the inner member 100 and circulates a gaseous low-temperature refrigerant flowing from the inflow pipe 92.
  • the accumulator chamber 110 is formed longer than the internal heat exchange chamber 120. .
  • the heat exchange pipe 130 is formed so as to extend spirally in the circumferential direction of the outer member 90 and the inner member 100 from the upper end side to the lower end side of the internal heat exchange chamber 120, and the outer member 90 is disposed on the lower end side thereof.
  • a straight inflow pipe portion 131 extending through the bottom surface of the outer member 90 is formed at the upper end side thereof, and a straight outflow pipe portion 132 extending through the upper surface plate 91 of the outer member 90 to the outside. Is formed.
  • the spiral portion 133 of the heat exchange pipe 130 is disposed between the outer member 90 and the inner member 100, and is disposed on the inner peripheral surface of the outer member 90 and the outer peripheral surface of the inner member 100 so as to wind the inner member 100.
  • the outer member 90 and the inner member 100 are joined together in the circumferential direction of the outer member 90 and the inner member 100 by brazing.
  • a spiral portion 133 of the heat exchange pipe 130 is disposed in the internal heat exchange chamber 120, and a spiral refrigerant flow passage 121 is formed in the internal heat exchange chamber 130 by the spiral portion 133 of the heat exchange pipe 130. . That is, the refrigerant flow passage 121 is formed between the spiral portion 133 of the heat exchange pipe 130 and the peripheral surfaces of the outer member 90 and the inner member 100, and the low-temperature refrigerant flowing from above the inner heat exchange chamber 120
  • the heat exchange pipe 130 is circulated along the spiral portion 133 of the heat exchange pipe 130 and flows out from the lower end of the internal heat exchange chamber 120 through the outflow pipe 93.
  • the spiral portion 133 of the heat exchange pipe 130 is not disposed on the lower side of the accumulator chamber 110.
  • the liquid low-temperature refrigerant R2 stored in the lower side of the accumulator chamber 110 does not evaporate due to the heating of the heat exchange pipe 130, and the liquid low-temperature refrigerant R2 ⁇ ⁇ is reliably stored in the accumulator chamber 110. I can keep it.
  • the heat of the high-temperature refrigerant in the heat exchange pipe 130 is not taken away by the liquid low-temperature refrigerant R2 in the accumulator chamber 110, the low-temperature refrigerant in the refrigerant flow passage 121 of the internal heat exchange chamber 120 is removed by the high-temperature refrigerant.
  • the heat can be sufficiently heated and the heat exchange efficiency of the internal heat exchange chamber 120 is not lowered.
  • SYMBOLS 10 Internal heat exchanger integrated accumulator, 20 ... Outer member, 30 ... Inner member, 32 ... Thermal insulation layer, 33, 34 ... Cylindrical member, 35 ... Thermal insulation layer, 40 ... Accumulator chamber, 50 ... Internal heat exchange chamber, 51 ... Refrigerant flow path, 60 ... Heat exchange pipe, 63 ... Spiral part, 70 ... Inner member, 80 ... Heat exchange pipe, 83 ... Spiral part, 90 ... Outer member, 100 ... Inner member, 110 ... Accumulator chamber, DESCRIPTION OF SYMBOLS 120 ... Internal heat exchange chamber, 121 ... Refrigerant flow path, 130 ... Heat exchange pipe, 133 ... Spiral part.

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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)
PCT/JP2017/037909 2016-11-08 2017-10-20 内部熱交換器一体型アキュムレータ及びこれを用いた冷凍サイクル WO2018088166A1 (ja)

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DE112017005621.7T DE112017005621T5 (de) 2016-11-08 2017-10-20 Energiespeicher mit integriertem internem Wärmetauscher und Kältekreislauf der denselben verwendet

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112519534A (zh) * 2020-12-22 2021-03-19 苏州市活跃量子生物科技有限公司 一种汽车空调蓄冷节能系统

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EP3757485B1 (de) * 2018-02-24 2023-08-02 Zhejiang Sanhua Intelligent Controls Co., Ltd. Gas-flüssigkeitsabscheider
CN108759202B (zh) * 2018-07-30 2023-10-27 东莞市艾瑞科热能设备有限公司 一种气液分离器
KR102711202B1 (ko) * 2019-10-08 2024-09-30 한온시스템 주식회사 열교환기
CN112432400A (zh) * 2020-01-20 2021-03-02 浙江三花智能控制股份有限公司 气液分离器及热管理系统
CN113514266B (zh) * 2021-05-21 2022-09-27 中国石油大学(北京) 低温工况下绕管式换热器内流型观测实验装置

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52165360U (de) * 1976-06-07 1977-12-14
JPS5417158U (de) * 1977-07-05 1979-02-03
JP2000227289A (ja) * 1999-02-01 2000-08-15 Behr Gmbh & Co 一体型ヘッダ・熱交換器組立体
US20030121648A1 (en) * 2001-12-28 2003-07-03 Visteon Global Technologies, Inc. Counter-flow heat exchanger with optimal secondary cross-flow
JP2004100974A (ja) * 2002-09-05 2004-04-02 Zexel Valeo Climate Control Corp アキュムレータ及びこれを用いた冷凍サイクル
JP2004526934A (ja) * 2001-05-24 2004-09-02 ハラ・クライメート・コントロール・カナダ・インコーポレーテッド 内部熱交換器アキュムレータ
JP2007278688A (ja) * 2006-04-06 2007-10-25 Visteon Global Technologies Inc 螺旋形規格化フィンチューブを持つ内部熱交換器
EP2136160A2 (de) * 2008-06-19 2009-12-23 Behr GmbH & Co. KG Integrierte, einen Sammler und einen inneren Wärmeübertrager umfassende Baueinheit sowie ein Verfahren zur Herstellung der Baueinheit
JP2010169387A (ja) * 2008-12-22 2010-08-05 Valeo Systemes Thermiques 内部熱交換器とアキュムレータの複合装置
JP2017219212A (ja) * 2016-06-03 2017-12-14 サンデンホールディングス株式会社 内部熱交換器一体型アキュムレータ及びこれを用いた冷凍サイクル

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52165360U (de) * 1976-06-07 1977-12-14
JPS5417158U (de) * 1977-07-05 1979-02-03
JP2000227289A (ja) * 1999-02-01 2000-08-15 Behr Gmbh & Co 一体型ヘッダ・熱交換器組立体
JP2004526934A (ja) * 2001-05-24 2004-09-02 ハラ・クライメート・コントロール・カナダ・インコーポレーテッド 内部熱交換器アキュムレータ
US20030121648A1 (en) * 2001-12-28 2003-07-03 Visteon Global Technologies, Inc. Counter-flow heat exchanger with optimal secondary cross-flow
JP2004100974A (ja) * 2002-09-05 2004-04-02 Zexel Valeo Climate Control Corp アキュムレータ及びこれを用いた冷凍サイクル
JP2007278688A (ja) * 2006-04-06 2007-10-25 Visteon Global Technologies Inc 螺旋形規格化フィンチューブを持つ内部熱交換器
EP2136160A2 (de) * 2008-06-19 2009-12-23 Behr GmbH & Co. KG Integrierte, einen Sammler und einen inneren Wärmeübertrager umfassende Baueinheit sowie ein Verfahren zur Herstellung der Baueinheit
JP2010169387A (ja) * 2008-12-22 2010-08-05 Valeo Systemes Thermiques 内部熱交換器とアキュムレータの複合装置
JP2017219212A (ja) * 2016-06-03 2017-12-14 サンデンホールディングス株式会社 内部熱交換器一体型アキュムレータ及びこれを用いた冷凍サイクル

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112519534A (zh) * 2020-12-22 2021-03-19 苏州市活跃量子生物科技有限公司 一种汽车空调蓄冷节能系统

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