Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
  • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
  • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
  • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
• • 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
  • 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
  • F25B43/006—Accumulators
• • 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
  • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
  • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
  • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
  • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
  • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
  • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
  • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
  • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
• • 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
  • F25B2309/00—Gas cycle refrigeration machines
  • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
  • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
• • 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
  • F25B2500/18—Optimization, e.g. high integration of refrigeration components
• • 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
  • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
  • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel

Definitions

• FIG. 1 shows a prior art vapor compression system having a compressor 1, a gas cooler 2, an expansion device 3, and an evaporator 4.
• evaporator 4 refrigerant passes through a series of heat exchanger tubes 5 in a heat exchange relationship with air being cooled as desired.
• Refrigerants typically enters tubes 5 through a header 6 and exits tubes 5 into a header 7.
• Refrigerant collected in header 7 then flows to an accumulator 8 where liquid phase refrigerant and oil separate from vapor phase refrigerant, and vapor is drawn back to compressor 1.
• a refrigeration system which includes a compressor for driving a refrigerant along a flow path in at least a first mode of system operation; a first heat exchanger along the flow path downstream of the compressor in the first mode; a second heat exchanger along the flow path upstream of the compressor in the first mode; and an expansion device in the flow path downstream of the first heat exchanger and upstream of the second heat exchanger in the first mode, wherein the second heat exchanger includes a combined header and accumulator for collecting liquid and vapor refrigerant.
• the combined header and accumulator serves to conserve space which is particularly advantageous, for example in transcritical vapor compression systems.
• a method for operating a refrigeration system in accordance with the present invention comprises operating a compressor to drive a refrigerant along a flow path, sequentially, to a first heat exchanger, an expansion device, a second heat exchanger, a combined header and accumulator, and back to the compressor, wherein flow is directly from the second heat exchanger to the combined header and accumulator, and wherein flow is directly from the combined header and accumulator to the compressor.
• FIG. 1 is an illustration of a prior art vapor compression system
• Fig. 2 is a schematic illustration of a system having a combined accumulator and header according to the invention
• FIG. 3 is a schematic illustration of an alternative embodiment of the combined accumulator and header according to the invention.
• Fig. 4 is a schematic illustration of a further alternative embodiment of the combined accumulator and header in accordance with the present invention.
• the invention relates to a heat exchanger configuration for a vapor compression system and, more particularly, to a space-saving combination of the refrigerant accumulator and the heat exchanger header in a transcritical vapor compression cycle.
• heat rejection occurs at a pressure above the critical pressure of the refrigerant. During the heat rejection the refrigerant does not condense.
• the charge management in a transcritical system is usually accomplished by adding an accumulator to the evaporator outlet, following an outlet header (See Fig. 1).
• Fig. 2 shows the vapor compression system 10 in accordance with the present invention which includes a compressor 12, a first heat exchanger or gas cooler 14, an expansion device 16 and a second heat exchanger or evaporator 18.
• evaporator 18 includes an inlet header 20 as in conventional devices, but that evaporator 18 also includes a combined header and accumulator 22 which combines the functions of separate outlet header 7 and accumulator 8 as illustrated in Fig. 1. This advantageously allows for conservation of space while providing the desired functions of both the header and the accumulator of this device.
• combined header and accumulator 22 in accordance with the present invention is a single chamber which defines a lower liquid refrigerant zone 24 and an upper vapor refrigerant zone 26. Flow enters the combined header and accumulator 22 directly from tubes 28 of second heat exchanger 18.
• Fig. 2 shows lower liquid refrigerant zone 24 defined at a location which is lower than the inlet from the lower most tube 30. This advantageously prevents masking and/or back-flow of liquid refrigerant with respect to lower most tube 30.
• this chamber is defined by side, front, back, top and bottom walls around the end of the heat exchanger tubes.
• combined header and accumulator 22 advantageously has an inner conduit 32 which extends from a bottom surface of combined accumulator and header 22 upwardly above the expected liquid level of liquid within lower liquid refrigerant zone 24.
• Compressor 12 draws vapor phase refrigerant out of vapor refrigerant zone 26 and through conduit 32 to the compressor suction line.
• a lower portion 34 of conduit 32 is preferably provided with a pin hole 36 which advantageously allows oil within the lower liquid refrigerant zone 24 to be drawn back to compressor 12 as desired.
• the heat exchangers 14, 18 of the present invention can be provided as any known type of heat exchanger, preferably as refrigerant-air heat exchangers.
• suitable heat exchangers include but are not limited to wire on tube heat exchangers, fin heat exchangers, and the like.
• the system of the present invention is particularly well suited to a transcritical vapor compression system, for example, a system which uses CO 2 as working fluid.
• a transcritical vapor compression system for example, a system which uses CO 2 as working fluid.
• other refrigerants particularly those with similar properties to CO 2 under expected operating conditions, can be used and are considered to be well within the broad scope of the present invention.
• Expansion device 16 can be any suitable expansion device known to a person of skill in the art.
• a pressure regulator for example a pressure regulator such as that disclosed in commonly owned and simultaneously filed PCT Application bearing attorney docket number 05-258-WO and entitled HIGH SIDE PRESSURE REGULATION FOR TRANSCRITICAL VAPOR COMPRESSION SYSTEM, is also well within the scope of the present invention and is considered to be an expansion device as used herein.
• Header and accumulator 22 can advantageously be incorporated into heat exchanger 18 as shown in Fig. 2.
• header and accumulator 22 can be a separate structure defining a chamber and communicated with heat exchanger 18, preferably through direct flow from tubes of the heat exchanger into the chamber.
• Fig. 3 shows a further alternative embodiment of the present invention, having the same basic components as the embodiment of Fig. 2.
• evaporator 18 is divided into two components 38, 40, and combined header and accumulator 22 is connected to each component 38, 40 through a short flow conduit 42.
• Conduit 42 is preferably very short, most preferably having a length of less than about 5 inches.
• Fig. 4 shows a further embodiment of the present invention, wherein system 10 includes the same components as those described in connection with Figs. 2 and 3.
• refrigerant fed from expansion device 16 to evaporator 18 flows through a single conduit 48 to combined header and accumulator 22 in accordance with the present invention. From this point, vapor phase refrigerant is drawn back to compressor 12 as desired.
• Embodiments of the invention as indicated in Figs. 2 - 4 of the present invention integrate the accumulator and the evaporator outlet header into a single chamber.
• This single chamber performs the function of both the header and accumulator of the conventional system of Fig. 1.
• the functions normally performed in the separate header and accumulator are now performed in the same space. This design reduces the space requirements for the accumulator as well as the overall tubing length and the number of tube connections.

Applications Claiming Priority (2)

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• 2005
  • 2005-12-30 US US11/908,450 patent/US20080190122A1/en not_active Abandoned
  • 2005-12-30 CN CNA2005800491549A patent/CN101203720A/zh active Pending
  • 2005-12-30 JP JP2008501868A patent/JP2008533430A/ja active Pending
  • 2005-12-30 WO PCT/US2005/047574 patent/WO2006101569A2/en active Search and Examination
  • 2005-12-30 EP EP05856047A patent/EP1864059A2/en not_active Withdrawn

Non-Patent Citations (1)

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