EP1586834B1 - Heat exchanger with the receiver tank - Google Patents

Heat exchanger with the receiver tank Download PDF

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Publication number
EP1586834B1
EP1586834B1 EP03814545A EP03814545A EP1586834B1 EP 1586834 B1 EP1586834 B1 EP 1586834B1 EP 03814545 A EP03814545 A EP 03814545A EP 03814545 A EP03814545 A EP 03814545A EP 1586834 B1 EP1586834 B1 EP 1586834B1
Authority
EP
European Patent Office
Prior art keywords
receiver tank
refrigerant
tank
heat exchanger
outlet
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03814545A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1586834A4 (en
EP1586834A1 (en
Inventor
Osamu c/o Oyama Regional Office KAMOSHIDA
Yoshihiko c/o Oyama Regional Office SENO
Keiji c/o Oyama Regional Office YAMAZAKI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr Thermal Systems Japan Ltd
Original Assignee
Showa Denko KK
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
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Application filed by Showa Denko KK filed Critical Showa Denko KK
Publication of EP1586834A1 publication Critical patent/EP1586834A1/en
Publication of EP1586834A4 publication Critical patent/EP1586834A4/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F28F9/0256—Arrangements for coupling connectors with flow lines
    • 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
    • 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
    • F25B39/04—Condensers
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
    • F28F9/0253—Massive connectors, e.g. blocks; Plate-like connectors with multiple channels, e.g. with combined inflow and outflow channels
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0441—Condensers with an integrated receiver containing a drier or a filter
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F25B2339/0446—Condensers with an integrated receiver characterised by the refrigerant tubes connecting the header of the condenser to the receiver; Inlet or outlet connections to receiver
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/17—Size reduction
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/32—Weight
    • 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
    • F25B41/00—Fluid-circulation arrangements

Definitions

  • the present invention relates to a heat exchanger with a receiver tank for refrigeration cycle for use in an automobile, household, or business air-conditioning system.
  • the so-called receiver dryer to which a function of removing the moisture contained in the refrigerant is given by forming a drying agent filled layer therein has been widely used.
  • a sandwich type in which spaces 133 and 134 above and below the drying agent filled layer 132 are provided within the vertical type tank 131 as shown in Figs. 14A and 14B
  • a bag type in which the drying agent filled layer 132 is provided at one side within the vertical type tank 131 as shown in Fig. 14D .
  • Fig. 14A shows a suction pipe type receiver tank in which the refrigerant introduced into the upper side space 133 via the top refrigerant inlet 135 is introduced into the lower side space 134 after passing through the drying agent filled layer 132, and the liquefied refrigerant separated from the gaseous refrigerant is discharged from the top refrigerant outlet 137 through the suction pipe 136.
  • FIG. 14B shows a supplying pipe type receiver tank in which the refrigerant introduced via the bottom refrigerant inlet 135 is introduced into the upper side space 133 through the supplying pipe 138, then introduced into the lower side space 134 after passing the drying agent filled layer 132, and the liquefied refrigerant separated from the gaseous refrigerant is discharged from the bottom refrigerant outlet 137 through the suction pipe 136. Furthermore, Fig.
  • 14C shows an inlet-outlet facing type in which the refrigerant introduced into the upper side space 133 via the top refrigerant inlet 135 is introduced into the lower side space 134 after passing through the drying agent filled layer 132, and the liquefied refrigerant separated from the gaseous refrigerant is discharged from the bottom refrigerant outlet 137.
  • the refrigerant introduced via the side refrigerant inlet 135 comes into contact with the drying agent filled layer 132, and the liquefied refrigerant separated from the gaseous refrigerant at the bottom of the tank is discharged from the bottom refrigerant outlet 137.
  • an air conditioning system In an air conditioning system, it has always been a conventional issue to improve the space efficiency and enhance the performance. Especially, in an automobile air conditioning system, it has been required to reduce the entire system size to effectively utilize the limited vehicle body space. To cope with it, it is necessary to decrease the refrigerant amount sealed in the refrigerant cycle, while enhancing the stability of performance against load fluctuations (overcharge toughness) and inhibiting performance deterioration due to the continuous running (deterioration of leakage toughness). To satisfy the above, it is desired to keep the steady area, i.e., the stable area in the refrigerant subcooled state with respect to the refrigerant sealed amount, as large as possible.
  • the refrigerant flow speed in the tank is faster than that in the sandwich type receiver tank and the flow turbulence is large. Therefore, the refrigerant liquid surface near the refrigerant outlet 137 becomes more unstable, causing easier outflow of the gaseous refrigerant, which in turn causes the same problems as mentioned above.
  • US 2002/124593 A1 discloses a receiver-tank provided with a vertical tank main body, an inlet and an outlet being provided in an inlet-and-outlet forming member as a bottom wall of the tank main body, a desiccant-filled-layer as a flow-resistance layer being provided in a lower part of the tank main body, and an upper space being formed above the desiccant-filled-layer.
  • a suction pipe is provided in the tank main body with the lower end connected with the outlet and the upper end opened toward the upper space.
  • the present invention aims to solve the problems of the aforementioned prior art, and provide a heat exchanger with a receiver tank for a refrigeration cycle capable of decreasing the size and weight, the refrigerant amount, the structural complexity and the cost and also capable of stably supplying refrigerant to the following cycle portion.
  • the present invention provides a heat exchanger with a receiver tank according to claim 1. Further embodiments of the invention are described in the dependent claims.
  • the condensed refrigerant in a gas-liquid mixed state decreases in flow speed by passing through the resistance layer.
  • the liquid refrigerant which is slower in flow speed as compared with gaseous refrigerant is sufficiently decreased in flow speed at the time of reaching the tank inside space after passing through the resistance layer, and therefore liquid stagnation is generated without causing any turbulence in the tank inside space.
  • the gaseous refrigerant is decreased in flow speed while going through the resistance layer upwards.
  • the gaseous refrigerant goes up through the liquid stagnation formed in the tank inside space as gentle bubbles when it reaches the liquid stagnation without causing any turbulence.
  • the bubbles vanish smoothly at the boundary between the liquid stagnation and the gaseous refrigerant, and goes up to be accumulated as gaseous refrigerant.
  • the receiver tank according to the present invention since only the liquefied refrigerant can be discharged, it becomes possible to attain an appropriate refrigerant sealed amount in the refrigeration cycle at an earlier stage, resulting in an enlarged stable region ranging from the most appropriate refrigeration point to the excessive point by utilizing the surplus space in the receiver tank as a buffering space, which in turn can operate the entire refrigeration cycle in a stabilized state.
  • the tank main body it is not required to dispose any piping such as a refrigerant suction pipe. This results in a reduced number of parts and simplified structure.
  • a dented stepped portion is formed at an upper end opening periphery of the receiver tank inlet hole located at a lower wall upper surface side of the tank main body.
  • an upper surface position of the resistance layer is set to be lower than the upper end opening position of the receiver tank refrigerant outlet hole.
  • the liquid stagnation can be formed in the tank main body in a more stabilized manner.
  • the resistance layer has a number of dispersing passages for dispersing the refrigerant in a radial direction of the tank main body.
  • the resistance layer a layer formed by filling a number of particle-shaped substances, a layer formed by woven fabric or nonwoven fabric in which a number of line-like members are knitted or secured, a layer made of a porous members or plate or made of laminating them, or a combination thereof, can be preferably employed.
  • the resistance layer is constituted by a filter layer made of fiber tangled member.
  • the resistance layer can also be functioned as a filter for removing impurities contained in the refrigerant.
  • an inlet side strainer is disposed on the upper end opening of the receiver inlet hole at a lower face side of the resistance layer.
  • the inlet side strainer prevents impurities from entering into the refrigerant inlet hole, thereby preventing clogging of the inlet apertures.
  • resistance can be given to the refrigerant to be introduced into the tank main body, further decreasing the flow speed of the refrigerant, which enables formation of the liquid stagnation in a more stabilized manner.
  • an outlet side strainer is disposed on the upper end opening of the receiver tank outlet hole.
  • the inlet side strainer prevents impurities from entering into the refrigerant inlet hole, thereby preventing clogging of the inlet apertures.
  • a metal mesh sheet can be preferably used as the inlet side and outlet side strainers.
  • a pressing member for holding the resistance layer in a downwardly pressed manner is provided in the tank main body.
  • the resistance layer can be assuredly mounted in the tank main body in a downwardly pressed state.
  • the tank main body is provided with an inlet-outlet member constituting a lower portion including the lower wall and a main tank member constituting an intermediate portion and an upper portion.
  • a drying agent filled layer is disposed in a fixed state in an upper side portion of the tank inside space.
  • water contents contained in the refrigerant can be removed in the receiver tank, which enables the first invention to utilize as a receiver dryer.
  • a drying agent filled members is disposed in a free state in an upper side portion of the tank inside space.
  • the condensed refrigerant in a gas-liquid mixed state forms liquid stagnation without causing any turbulence in the tank inside space, and the gaseous refrigerant goes up in the liquid as calm bubbles and vanishes without causing the liquid surface. Accordingly, since only the stable liquefied refrigerant can be discharged, it becomes possible to attain an appropriate sealed amount of refrigerant in the refrigeration cycle at an earlier stage, enabling reduction in size and weight and reduction in refrigerant amount. Furthermore, stable refrigerant can be supplied to the following cycle portion. Furthermore, since the receiver tank does not require to provide any inner piping such as a refrigerant suction pipe, the number of parts can be decreased, resulting in simplified structure, reduced cost and easy assembly.
  • Fig. 1 is a front view showing both sides of a heat exchanger with a receiver tank according to an embodiment of this invention.
  • this heat exchanger is provided with a heat exchanger main body 10 of a multi-flow type, a receiver tank 3, and a block flange 4 which is a connecting member for connecting the receiver tank 3 to the heat exchanger main body 10.
  • the heat exchanger main body 10 is provided with a pair of headers 11 disposed vertically at a certain distance. Between these headers 11, a plurality of flat tubes 12 as heat exchanging tubes are disposed horizontally with their both ends connected to the headers 11 in a fluid communication at certain intervals in an up-and-down direction. Furthermore, between the adjacent flat tubes 12 and at the outside of the outermost flat tube 12, a corrugate fin 13 is disposed respectively. At the outside of the outermost corrugate fin 13, a side plate 14 is disposed.
  • a flange-like partitioning portion 50 of the block flange 4 is mounted at a certain height position of one of the headers 11 of the heat exchanger main body 10.
  • a partitioning plate 16 is mounted at the same height position of the other header 11 as that of the aforementioned partitioning portion 50.
  • the flat tubes 12 located above the partitioning plate 16 and partitioning portion 50 constitute a condensing portion 1
  • the flat tubes 12 located below the partitioning plate 16 and partitioning portion 50 constitute a subcooling portion 2 independent with respect to the aforementioned condensing portion 1.
  • refrigerant turning partitioning plates 17 are mounted at certain height positions, so that the condensing portion 1 is divided into three passes, i.e., the first to third passes P1 to P3, in the heat exchanging main body 10 of this embodiment.
  • a condensing portion inlet 1a corresponding to the first pass P1 is provided, and at the lower portion thereof, a subcooling portion outlet 2b corresponding to the subcooling portion 2 is provided.
  • the receiver tank 3 includes a tank main body 30 equipped with a main tank member 31 constituting the upper and middle portions of the tank main body 30 and an outlet-inlet member 32 constituting the lower portion of the tank main body 30.
  • the main tank member 31 has a vertically extended shape with the upper end closed and the lower end opened.
  • the outlet-inlet member 32 has a cylindrical shape with the upper end opened and the lower end closed with a lower wall 321.
  • one half side region of the upper side of the lower wall 321 is downwardly dented and constituted as a lower dented stepped portion 330, and the other half thereof is constituted as a higher portion 340.
  • a receiver tank inlet hole 3a penetrating the lower wall in the up-and-down direction.
  • the upper end of this receiver tank inlet hole 3a is opened to the bottom surface of the dented stepped portion 330.
  • an inlet side protruded portion 332 is formed in a downwardly protruded manner. At the lower end face of this protruded portion 332, the lower end of the receiver tank inlet hole 3a is opened.
  • a receiver tank outlet hole 3b penetrating the lower wall in the up-and-down direction.
  • the upper end of this receiver tank outlet hole 3b is opened at the higher portion 340.
  • an outlet side dented portion 342 is formed in an upwardly dented manner. At the bottom of this dented portion 342, the lower end of the receiver tank outlet hole 3b is opened.
  • an inlet side strainer 333 made of a metal mesh sheet is disposed so as o close the receiver tank inlet hole 3a. Furthermore, on the upper surface of this strainer 333, a filter layer 335 made of nonwoven fabric as a resistance layer for decreasing the flow speed of the refrigerant is disposed so as to be filled in the dented stepped portion 330.
  • a hat-shaped outlet side strainer 343 made of a metal mesh sheet is disposed so as to close the upper end portion of the receiver tank outlet hole 3b.
  • a pressing member 350 is disposed at the upper surface side of the lower wall of the outlet-inlet member 32.
  • This pressing member 350 is constituted by a metal press molded member with a circular bottom plate and a peripheral wall portion upwardly extending from the external peripheral edge portion of the circular bottom plate. This pressing member 350 is formed to have a size capable of being fitted in the outlet-inlet member 320.
  • a first region 353 which is one half side of the bottom wall of the pressing member 350 is formed in a downwardly protruded manner so as to correspond to the dented stepped portion 330. In this region, a number of refrigerant passing apertures 353a are formed. In a second region 354 which is the other half side of the bottom wall, an aperture 354a corresponding to the receiver tank outlet hole 3b is formed.
  • This pressing member 350 is fitted in the outlet-inlet member 32 from the upper end opening portion thereof, so that the filter layer 335 is pressed from the above in the first region 353. Furthermore, in a state in which the outlet side strainer 343 is fitted in the aperture 354a formed in the second region 353, the peripheral portion of the outlet side strainer 343 is pressed from the above by the peripheral portion of the aperture formed in the second region 353. The pressing member 350 is held in a state in which the pressing member 350 is pressed against the lower wall 321 side when the protrusion 325 formed on the inner peripheral surface of the inlet-outlet member 23 is engaged with the upper end of the peripheral wall portion of the pressing member 350.
  • the upper surface position of the filter layer 335 is set to be lower than the upper end opening position of the receiver tank outlet hole 3b.
  • a multi-bored plate 311 is fixed via the fixing member 315, and a certain amount of drying agents in the shape of spherical particle such as molecular sieve is filled above the multi-bored plate 311, so that an upper drying agent filled layer 312 as a drying agent filled member is formed.
  • An upper end opening portion of the outlet-inlet member 32 is fixed to the lower opening portion of the main tank member 31, thereby forming a receiver tank 3 according to this embodiment.
  • a block flange 4 for connecting the receiver tank 3 to a heat exchanger main body 10 is provided with a main body 41, an embedding portion 42 integrally protruded sideways from the main body 41.
  • an inlet side dented portion 45 capable of being fitted by the inlet side protruded portion 332 of the receiver tank 3 and an outlet side protruded portion 46 capable of fitting into the inlet side dented portion 342 of the receiver tank 3 are formed.
  • an inlet passage 4a for communicating the condensing portion 1 with the receiver tank 3 and an outlet passage 4b for communicating the receiver tank 3 with the subcooling portion 3 are provided.
  • the one end (inlet side end) of the inlet passage 4a is opened at the upper end of the embedding portion 42, and the other end (outlet side end) thereof is opened at the bottom surface in the inlet side dented portion 45.
  • the inlet passage 4a includes an inlet side half thereof constituting a refrigerant descending passage 40a inclined obliquely downward and an outlet side half hereof constituting a refrigerant ascending passage ascending vertically.
  • the one end (inlet side end) of the outlet passage 4b is opened at the upper end of the outlet side protruded portion 46, and the other end (outlet side end) thereof is opened at the side external surface of the embedding portion 42.
  • an outwardly extended flange-like partitioning portion 50 is integrally formed on the upper end periphery of the embedding portion 42 of the block flange 4.
  • This flange-like partitioning portion 50 has an external contour capable of fitting to the internal surface of one of the headers 11.
  • the embedding portion 42 of the block flange 4 is embedded in one of the headers 11 between the condensing portion 1 and the subcooling portion 2 in a manner such that the embedding portion 42 is fitted therein from the side of the header, so that the peripheral portions 41a and 41a formed at the embedding portion side of the flange main body 41 are fixed to the header 11 in an airtight manner.
  • the external peripheral edge of the flange-like partitioning portion 50 formed at the upper portion of the embedding portion is secured to the internal peripheral surface of the header 11 along the circumferential direction in a continuous manner.
  • This flange-like partitioning portion 50 constitutes a partitioning member for partitioning the inside of one of the headers into the condensing portion 1 and the subcooling portion 2 as mentioned above.
  • the inlet side end portion of the inlet passage 4a is opened to and communicated with the condensing portion 1 so as to constitute a condensing portion outlet 1b
  • the outlet side end portion of the outlet passage 4b is opened to and communicated with the subcooling portion 2 so as to constitute a subcooling portion inlet 2a.
  • the outlet side end portion of the inlet passage 4a is positioned at a height corresponding to the upper end portion of the subcooling portion 2, and that the outlet side end portion of the inlet passage 4a is positioned at a height lower than the inlet side end portion of the inlet passage 4a, i.e., the condensing portion outlet 1b.
  • the protruded portion 332 of the receiver tank 3 is air-tightly fitted in the dented portion 45 of the block flange 4, and the protruded portion 46 of the block flange 4 is air-tightly fitted in the dented portion 342 of the receiver tank 3, whereby the lower end of the receiver tank 3 is assembled to the block flange 4.
  • the upper portion of the receiver tank 3 is fixed to one of the headers 11 via the bracket 6.
  • the inlet passage 4a and the outlet passage 4b of the block flange 4 constitute a refrigerant passage respectively.
  • each of the core components such as the header 11, the flat tube 12, the fin 13, the side plate 14, the receiver tank 3 and the block flange 4 is made of aluminum (or its alloy) or constituted by an aluminum brazing sheet, etc., and these components are integrally secured by brazing them in a furnace in a provisionally assembled manner with brazing materials.
  • the flange-like partitioning portion 50 of the block flange 4 is secured to the internal peripheral surface of the header 11 at the time of the aforementioned integral brazing.
  • the heat exchanger with the receiver tank of the aforementioned structure is used as a condenser for use in an automobile air-conditioning refrigeration system together with a compressor, a decompressing means such as an expansion valve and an evaporator.
  • a compressor a decompressing means such as an expansion valve and an evaporator.
  • the high temperature and high pressure gaseous refrigerant is introduced into the condensing portion 1 via the condensing inlet 1a and condensed therein by exchanging heat with the ambient air while passing through the first to third passes P1-P3 in a zigzag manner.
  • This condensed refrigerant is introduced into the inlet passage 4a of the block flange 4 via the condensing portion outlet 1b, and then introduced into the receiver tank 3 via the receiver tank inlet hole 3a.
  • the refrigerant introduced into the receiver tank inlet hole 3a is immediately and widely diffused and decreased in flow speed immediately after being introduced into the tank via the upper end of the inlet hole 3a, and then goes through the inlet side strainer 333 and goes up through the filter layer 335.
  • the filter layer functions as a resistance layer against the refrigerant flow
  • the refrigerant is further decreased in raising speed dramatically, and goes up while changing the flow directions by passing through the fibers of the nonwoven fabric constituting the filter layer 335. Due to this rectification function, the local high speed flow and uneven flow will be vanished, resulting in an entirely even upward flow.
  • the refrigerant is introduced into the tank inside space 310 by passing through the refrigerant passing apertures 353a.
  • the liquefied refrigerant introduced into the tank inside space 310 forms a liquid stagnation R without causing any turbulence.
  • Gas (gaseous refrigerant) mixed into or generated in the liquefied refrigerant flowing upward through the filter layer 335 suddenly decreases in flow speed when going up through the filter layer 335 and reaches the liquid stagnation R.
  • the gas goes up through the liquid and smoothly vanishes without causing any turbulence of the liquid surface.
  • the gas further goes up beyond the boundary between the gas and the liquid and accumulates as gaseous refrigerant.
  • the refrigerant introduced into the receiver tank outlet hole 3b is introduced in the outlet passage 4b of the block flange 4 and then introduced into the subcooling portion 2 after passing through the outlet passage 4b.
  • the liquefied refrigerant introduced in the subcooling portion 2 is subcooled by the ambient air while passing through the subcooling portion 2, and then discharged from the subcooling portion outlet 2b.
  • the liquefied refrigerant discharged from the heat exchanger with the receiver tank is evaporated in the evaporator by absorbing heat from the ambient air, and then returns to the compressor.
  • a prescribed refrigeration performance can be secured by circulating the refrigerant in the refrigeration cycle of the refrigeration system.
  • the liquefied refrigerant introduced in the receiver tank 3 is slow in flow speed and therefore calmly forms the liquid stagnation R and the gases vanish smoothly and effectively.
  • the liquefied refrigerant can be stably supplied to the subcooling portion of the heat exchanger, enabling a stable operation of the refrigeration cycle, which in turn results in excellent refrigeration performance.
  • the receiver tank can be decreased in diameter and enhanced in performance, resulting in miniaturized entire refrigeration system, enhanced performance and deceased refrigerant amount.
  • the receiver tank 3 does not require to provide any inner piping such as a refrigerant suction pipe, the number of parts can be decreased, resulting in simplified structure, reduced cost and easy assembly.
  • the filter layer forms a resistance layer, it is not necessary to further provide a resistance layer, resulting in further decreased number of parts, further simplified structure and further reduced cost.
  • the receiver tank connecting block flange 4 is secured to the header 11 of the heat exchanger main body 10 with the embedding portion 42 embedded in the header, the installation space can be eliminated. As a result, miniaturization can be attained.
  • the flange-like partitioning portion 50 is integrally formed at around the inlet of the inlet passage 4a located at the upper end of the embedding portion 42, and one of the headers 11 is divided into the condensing portion 1 and the subcooling portion 2 with the partitioning portion 50. Therefore, a partitioning member for partitioning the condensing portion 1 and the subcooling portion 2 is not required, resulting in decreased number of parts, simplified assembling, and cost reduction.
  • the receiver tank 4 to be secured to the block flange 4 can be disposed closer to the header 11. As a result, the entire heat exchanger can be further reduced in size.
  • the inlet side of the inlet passage 4a is inclined downwardly and the outlet side end of the inlet passage 4a is positioned lower than the inlet side end. Therefore, the overall installation position of the receiver tank 3 can be lowered, which allows the use of the longer receiver tank 3. Accordingly, sufficiently large tank capacity of the receiver tank 3 can be secured, which in turn enlarges the stable region in the subcooling state of the refrigerant. This prevents excessive or insufficient sealed amount of refrigerant, resulting in stabilized refrigeration performance and enhanced refrigeration performance.
  • receiver tank 3 a long size receiver tank can be employed. Therefore, a receiver tank with a smaller diameter can be employed while securing sufficient tank capacity, which in turn can attain further miniaturization.
  • the descending passage 40a of the inlet passage 4a formed in the block flange 4 is inclined relative to the axis of the header 11 and the upper end face of the descending passage 40a is positioned so as to be perpendicular to the axis of the header 11. Therefore, the upper end opening area of the descending passage 40a can be formed to be larger than the passage cross-sectional area of the descending passage 40a.
  • the upper end opening area of the descending passage 40a can be formed to be large, enabling efficient and smooth introduction of refrigerant, decreased pressure loss, and stable refrigeration supply, which in turn can further improve the refrigeration performance.
  • the upper end opening area (condensing portion outlet 1b) of the descending passage 40a is set to be large, i.e., 62 mm 2 .
  • the inlet-outlet member is formed separately from the tank main body, the present invention is not limited to it and can also be applied to a receiver tank in which an inlet-outlet portion is integrally formed to a tank main body.
  • the number of passes of the heat exchanger main body, the number of heat exchanging tubes of each pass, etc. are not limited to the above.
  • the receiver tank 3 is attached to a heat exchanger integrally provided with a subcooling portion.
  • the present invention is not limited to it.
  • the receiver tank 3 can be attached to a heat exchanger such as a condenser with no subcooling portion.
  • receiver tank 3 is attached to a heat exchanger, it is not necessary to employ a block flange.
  • the receiver tank 3 can be connected using refrigerant pipes.
  • the drying agent layer 312 is provided at the upper end portion of the tank main body 30, the present invention is not limited to it.
  • the drying agent layer 312 can be fixed at an intermediate portion or a lower portion of the tank main body 30.
  • the drying agent layer can be disposed in the tank main body in a free state.
  • the filter layer 335 it is not always necessary to use nonwoven fabric.
  • Another fiber tangled member such as woven fabric and knitted fabric, can be used.
  • a filter layer made of drying agent such as molecular sieve can be used. In short, anything can be used so long as it gives resistance to refrigerant flow.
  • a receiver tank for refrigeration cycle, a heat exchanger with the receiver tank, and a condensation device for refrigeration cycle according to the present invention can be preferably used for automobile, household or business air-conditioning systems.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Power Engineering (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
EP03814545A 2002-12-27 2003-12-17 Heat exchanger with the receiver tank Expired - Lifetime EP1586834B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2002378979A JP4091416B2 (ja) 2002-12-27 2002-12-27 冷凍サイクル用レシーバタンク、レシーバタンク付き熱交換器及び冷凍サイクル用凝縮装置
JP2002378979 2002-12-27
PCT/JP2003/016219 WO2004061377A1 (ja) 2002-12-27 2003-12-17 冷凍サイクル用レシーバタンク、レシーバタンク付き熱交換器及び冷凍サイクル用凝縮装置

Publications (3)

Publication Number Publication Date
EP1586834A1 EP1586834A1 (en) 2005-10-19
EP1586834A4 EP1586834A4 (en) 2010-06-16
EP1586834B1 true EP1586834B1 (en) 2012-03-28

Family

ID=32708361

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03814545A Expired - Lifetime EP1586834B1 (en) 2002-12-27 2003-12-17 Heat exchanger with the receiver tank

Country Status (9)

Country Link
EP (1) EP1586834B1 (ja)
JP (1) JP4091416B2 (ja)
KR (1) KR20050088139A (ja)
CN (1) CN100476321C (ja)
AT (1) ATE551577T1 (ja)
AU (1) AU2003301504A1 (ja)
BR (1) BR0317793B1 (ja)
WO (1) WO2004061377A1 (ja)
ZA (1) ZA200505559B (ja)

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007074796A1 (ja) * 2005-12-28 2007-07-05 Showa Denko K.K. 熱交換器およびその製造方法
JP4669792B2 (ja) * 2006-02-14 2011-04-13 昭和電工株式会社 冷凍サイクル用受液器
JP4909625B2 (ja) * 2006-04-25 2012-04-04 昭和電工株式会社 冷凍サイクル用受液器
KR101320453B1 (ko) 2007-11-02 2013-10-22 한라비스테온공조 주식회사 리시버드라이어의 하부캡 결합구조
JP5432476B2 (ja) * 2008-05-29 2014-03-05 株式会社不二工機 レシーバドライヤ
CN201852383U (zh) * 2010-11-17 2011-06-01 浙江三花汽车控制系统有限公司 一种热交换器及其贮液器
JP5960955B2 (ja) 2010-12-03 2016-08-02 現代自動車株式会社Ｈｙｕｎｄａｉ Ｍｏｔｏｒ Ｃｏｍｐａｎｙ 車両用コンデンサ
JP5594170B2 (ja) * 2011-02-02 2014-09-24 株式会社デンソー 冷媒用除水装置
KR101074119B1 (ko) 2011-07-18 2011-10-17 양운재 유압탱크
CN102538323B (zh) * 2012-02-27 2014-04-02 浙江三花汽车零部件有限公司 空调制冷系统及其贮液器
JP6039946B2 (ja) * 2012-07-13 2016-12-07 株式会社ケーヒン・サーマル・テクノロジー コンデンサ
DE102013218529A1 (de) * 2013-09-16 2015-03-19 Volkswagen Aktiengesellschaft Trocknervorrichtung und Verflüssiger für eine Kältemaschine sowie Verfahren zur Herstellung eines Verflüssigers für eine Kältemaschine
DE102013224036A1 (de) * 2013-11-25 2015-05-28 MAHLE Behr GmbH & Co. KG Wärmeübertrager
CN104329823B (zh) * 2014-08-27 2016-09-14 无锡溥汇机械科技有限公司 一种制冷剂储蓄装置与具有制冷剂储蓄装置的制冷系统
JP6434276B2 (ja) * 2014-10-31 2018-12-05 株式会社不二工機 レシーバドライヤ
CN107208946B (zh) * 2014-12-22 2020-05-01 C·邱 用于改善热交换系统效率的装置
JP6850058B2 (ja) * 2016-07-12 2021-03-31 マーレベーアサーマルシステムズジャパン株式会社 コンデンサ
CN105972882A (zh) * 2016-07-25 2016-09-28 瑞安市凯优汽车配件有限公司 一种储液干燥瓶
CN107796149B (zh) * 2016-09-12 2020-09-29 浙江三花汽车零部件有限公司 一种贮液器
JP6587602B2 (ja) * 2016-12-27 2019-10-09 株式会社不二工機 冷媒容器
US10563890B2 (en) 2017-05-26 2020-02-18 Denso International America, Inc. Modulator for sub-cool condenser
KR102454994B1 (ko) * 2017-12-25 2022-10-17 쯔지앙 산후아 오토모티브 컴포넌츠 컴퍼니 리미티드 액체 저장 용기 및 그 제조 방법

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JPH0914799A (ja) * 1995-06-29 1997-01-17 Showa Alum Corp 受液器およびその製造方法
DE19712714A1 (de) * 1997-03-26 1998-10-01 Behr Gmbh & Co Einsatz für ein Sammlerprofil eines Kondensators
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US6494059B2 (en) * 2000-08-11 2002-12-17 Showa Denko K.K. Receiver tank for use in refrigeration cycle, heat exchanger with said receiver tank, and condensing apparatus for use in refrigeration cycle

Also Published As

Publication number Publication date
AU2003301504A1 (en) 2004-07-29
CN1732364A (zh) 2006-02-08
ZA200505559B (en) 2006-06-28
BR0317793A (pt) 2005-11-22
WO2004061377A1 (ja) 2004-07-22
EP1586834A4 (en) 2010-06-16
ATE551577T1 (de) 2012-04-15
JP4091416B2 (ja) 2008-05-28
CN100476321C (zh) 2009-04-08
EP1586834A1 (en) 2005-10-19
KR20050088139A (ko) 2005-09-01
BR0317793B1 (pt) 2014-12-23
JP2004211921A (ja) 2004-07-29

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