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WO2008112569A2 - Système de réfrigération - Google Patents

Système de réfrigération Download PDF

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Publication number
WO2008112569A2
WO2008112569A2 PCT/US2008/056275 US2008056275W WO2008112569A2 WO 2008112569 A2 WO2008112569 A2 WO 2008112569A2 US 2008056275 W US2008056275 W US 2008056275W WO 2008112569 A2 WO2008112569 A2 WO 2008112569A2
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
evaporator
receiver
condenser
pressure
Prior art date
Application number
PCT/US2008/056275
Other languages
English (en)
Other versions
WO2008112569A3 (fr
Inventor
Alexander Cohr Pachai
John Ritmann
Istvan Knoll
Original Assignee
Johnson Controls Technology Company
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
Application filed by Johnson Controls Technology Company filed Critical Johnson Controls Technology Company
Publication of WO2008112569A2 publication Critical patent/WO2008112569A2/fr
Publication of WO2008112569A3 publication Critical patent/WO2008112569A3/fr

Links

Classifications

    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
    • 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
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/16—Receivers
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/22—Refrigeration systems for supermarkets
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/226—Transversal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2220/00—Closure means, e.g. end caps on header boxes or plugs on conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2280/00—Mounting arrangements; Arrangements for facilitating assembling or disassembling of heat exchanger parts
    • F28F2280/02—Removable elements

Definitions

  • the application generally relates to refrigeration systems.
  • the application relates more specifically to configurations and control processes for multistage refrigeration systems.
  • Multistage refrigeration systems can be used when several evaporators are needed to provide various temperatures for a single application.
  • a multistage refrigeration system can be used to provide the necessary cooling for both refrigerated cases and freezer cases in a supermarket.
  • a multistage refrigeration system can also be used to provide an evaporator temperature lower than that attainable by a single-stage system, e.g., a vapor compression system.
  • a multistage refrigeration system can be used in an industrial process to provide temperatures of between -20 deg C and -50 deg C or colder, as may be required in a plate freezer application.
  • One type of multistage refrigeration system can involve the interconnection of two or more closed loop refrigeration systems in which the heat- absorbing stage, e.g., evaporator, of one system is in a heat exchange relationship with the heat-rejecting stage, e.g., condenser, of the other system.
  • the heat-absorbing stage e.g., evaporator
  • the heat-rejecting stage e.g., condenser
  • One of the primary purposes of a multistage refrigeration system having the heat-absorbing stage of one system in a heat exchange relationship with the heat-rejecting stage of the other system is to permit the attaining of temperatures in the heat-rejecting or heat- absorbing stage of one of the systems that exceeds that which can be attainable if only a single system is used with conventional heat-rejecting or heat-absorbing loads.
  • the present invention relates to a multistage refrigeration system having a first system, a second system and a third system.
  • the first system is configured to circulate a first system refrigerant through a first system compressor, a first system condenser, an intermediate vessel and a first system evaporator.
  • the second system is configured to circulate a second refrigerant through a second system condenser, a second system evaporator, a second system receiver and a second system pump.
  • the first refrigerant in the first system evaporator exchanges heat with the second refrigerant in the second system condenser.
  • the intermediate vessel in the first system cools refrigerant from the first system condenser and provides gas to the first system compressor and has a liquid reservoir of the first refrigerant.
  • the third system is configured to circulate a third refrigerant through a third system condenser, third system evaporator, third system receiver and a third system pump.
  • the third refrigerant in the third system condenser exchanges heat with the liquid in the intermediate vessel reservoir.
  • the present invention also relates to a multistage refrigeration system having a first system, a second system and a third system.
  • the first system is configured to circulate a first refrigerant through a first system compressor, a first system condenser and a first system evaporator.
  • the second system is configured to circulate a second refrigerant through a second system compressor, a second system condenser, a second system evaporator, a second system receiver and a second system pump.
  • the second refrigerant is carbon dioxide, and the second system is operated in a transcritical region of carbon dioxide.
  • the first refrigerant in the first system evaporator exchanges heat with the carbon dioxide in the second system condenser.
  • the third system comprises a pressure regulator, a receiver and a heat exchanger.
  • the third system is configured to receive liquid carbon dioxide from the second system condenser and to provide vapor carbon dioxide at an intermediate pressure to the second system compressor.
  • the intermediate pressure is a pressure greater than a suction pressure of the second system compressor and less than a discharge pressure of the second system compressor.
  • the present invention further relates to a multistage heat exchanger system having a first system and a second system.
  • the first system is configured to circulate a first refrigerant through a compressor, a condenser, a first evaporator and a second evaporator.
  • the second system is configured to circulate a second refrigerant.
  • the second system having a first circuit and a second circuit.
  • the first circuit being configured to circulate the second refrigerant through a compressor, a condenser, a heat exchanger and an evaporator.
  • the second circuit being configured to circulate the second refrigerant through a compressor, a condenser, a heat exchanger and an evaporator.
  • the first refrigerant in the first evaporator of the first system exchanges heat with the second refrigerant in the heat exchanger of the first circuit of the second system.
  • the first refrigerant in the second evaporator of the first system exchanges heat with the second refrigerant in the heat exchanger of the second circuit of the second system.
  • the present invention also relates to a multistage refrigeration system having a first system, a second system, a sensor and a controller.
  • the first system is configured to circulate a first refrigerant through a first system compressor, a first system condenser and a first system evaporator.
  • the second system is configured to circulate a second refrigerant through a second system condenser, a second system evaporator, a receiver and a pump.
  • the first refrigerant in the first system evaporator exchanges heat with the second refrigerant in the second system condenser.
  • the sensor provides a signal representative of the pressure in the receiver.
  • the controller is configured to receive the signal from the pressure sensor and to control the pressure in the receiver in response to the signal from the pressure sensor to prevent the pressure in the receiver from exceeding a predetermined level during a start-up process for the multistage refrigeration system.
  • the present invention still further relates a method for controlling the pressure of a receiver of a second stage system during start-up of a multistage refrigeration system having a first stage system and a second stage system.
  • the method includes measuring a pressure in the receiver, determining whether the pressure in the receiver is increasing, adjusting a flow from the receiver to an evaporator in response to the determination of whether the pressure in the receiver is increasing, and determining whether the multistage refrigeration system is operating at full capacity.
  • the steps of measuring, determining and adjusting are repeated in response to a determination that the multistage refrigeration system is not operating at full capacity.
  • FIGS. 1 and 2 show exemplary embodiments of commercial and industrial applications incorporating a refrigeration system.
  • FIG. 3 shows a perspective view of an exemplary embodiment of a refrigeration system.
  • FIG. 4 shows a side elevational view of the refrigeration system shown in FIG.
  • FIG. 5 schematically illustrates an exemplary embodiment of a multistage refrigeration system.
  • FIG. 6 schematically illustrates an enlarged view of an exemplary embodiment of the piping detail shown in FIG. 5.
  • FIG. 7 schematically illustrates an exemplary embodiment of a multistage refrigeration system.
  • FIG. 8 schematically illustrates another exemplary embodiment of a multistage refrigeration system.
  • FIG. 9 schematically illustrates another exemplary embodiment of a multistage refrigeration system.
  • FIG. 10 schematically illustrates another exemplary embodiment of a multistage refrigeration system.
  • FIG. 11 schematically illustrates an embodiment of a second stage system for a multistage refrigeration system.
  • FIG. 12 shows a control process for controlling the pressure in a receiver of a second stage system during start-up of a multistage refrigeration system.
  • FIG. 13 schematically illustrates an exemplary embodiment of a portion of the second stage system for implementing the control process of FIG. 12.
  • FIG. 14 schematically illustrates another exemplary embodiment of a portion of the second stage system for implementing the control process of FIG. 12.
  • FIG. 15 schematically illustrates another exemplary embodiment of a portion of the second stage system for implementing the control process of FIG. 12.
  • FIG. 16 schematically illustrates another exemplary embodiment of a portion of the second stage system for implementing the control process of FIG. 12.
  • FIGS. 1 and 2 show several exemplary applications for a multistage refrigeration system (also referred to as a cascade refrigeration system or a multi- pressure refrigeration system).
  • Multistage refrigeration systems can include a first stage system (also referred to as a high side system) and a second stage system (also referred to as a low side system) that are interconnected by a heat exchanger.
  • Multistage refrigeration systems can be used to provide different levels of cooling capacity and/or achieve low temperatures that are difficult to achieve with a single vapor compression cycle.
  • FIG. 1 shows a multistage refrigeration system 10 that can provide both refrigeration and freezing capacity for a supermarket 12 in a commercial setting.
  • the second stage system of multistage refrigeration system 10 can have evaporators incorporated into refrigerated cases or displays 14 and freezer cases or displays 16 that are accessible by a person shopping in supermarket 12.
  • refrigerated cases or displays 14 can be used to keep produce or dairy products at a preselected temperature and can be operated at a temperature between about 2 deg C and about 7 deg C
  • freezer cases or displays 16 can be used to keep frozen items at a preselected temperature and can be operated at a temperature between about -20 deg C and about -30 deg C.
  • the second stage system of multistage refrigeration system 10 can have an evaporator 18 in a freezer storage area 20 of supermarket 12 and can have an evaporator 22 in a refrigerated storage area 24 of supermarket 12.
  • freezer storage area 20 can be used to store items to be subsequently placed in freezer cases or displays 16 at a preselected temperature and can be operated at a temperature between about -20 deg C and about 30 deg C
  • refrigerated storage area 24 can be used to store items to be subsequently placed in refrigerated cases or displays 14 at a preselected temperature and can be operated at a temperature between about 2 deg C and about 7 deg C.
  • FIG. 2 depicts multistage refrigeration system 10 supplying freezing capacity to a plate freezer 28 in a factory or industrial setting 26.
  • Plate freezer 28 may have horizontal or vertical plates 30 to freeze flat products, such as pastries, fish fillets, and beef patties, as well as irregular-shaped vegetables that are packaged in brick-shaped containers, such as asparagus, cauliflower, spinach, and broccoli.
  • the product may be firmly pressed between metal plates 30 that are cooled to subfreezing temperatures by internally circulating refrigerant from the second stage system through thin channels within plates 30. A high rate of heat transfer can be obtained between the product and plates 30.
  • plate freezers 28 may provide cooling temperatures of between about -20 deg C and about - 50 deg C or colder and can be used, for example, when rapid freezing is desired to retain product flavor and freshness.
  • FIGS. 1 and 2 show exemplary applications only and multistage refrigeration systems are used in many other environments as well.
  • FIGS. 3 and 4 show a multistage refrigeration system that is also shown schematically in FIG. 5.
  • the multistage refrigeration system can include a first stage system 32 and a second stage system 34 that are interconnected by a heat exchanger 36.
  • Heat exchanger 36 can be a plate heat exchanger, a shell and tube heat exchanger, a plate and shell heat exchanger or any other suitable type of heat exchanger.
  • First stage system 32 can be a vapor compression system that circulates a refrigerant through a compressor 38, a condenser 40, a receiver 42 (optional), an expansion device 44 and an evaporator 46 that is incorporated into heat exchanger 36.
  • fluids that can be used as refrigerants in first stage system 32 are carbon dioxide (CO2; e.g., R-744), nitrous oxide (N2O; e.g., R -744a), ammonia (NH3; e.g., R-717), hydrofluorocarbon (HFC) based refrigerants (e.g., R-410A, R- 407C, R-404A, R-134a), other low global warming potential (GWP) refrigerants, and any other suitable type of refrigerant.
  • CO2 carbon dioxide
  • N2O nitrous oxide
  • NH3 e.g., R-717
  • HFC hydrofluorocarbon
  • GWP low global warming potential
  • Second stage system 34 can be a vapor compression system that circulates a refrigerant through a compressor 48, a condenser 50 that is incorporated into heat exchanger 36, a receiver or separatoi 52, a pump 54, and a first expansion device 56 and a first evaporator 58 that can be in parallel with a valve 60, which may be a regulation valve, solenoid valve, or any other type of valve, and second evaporator 62.
  • second stage system portion 34 can be operated with only first expansion device 56 and first evaporator 58.
  • second stage system portion 34 can be operated as a volatile system by removing compressor 48, first expansion device 56 and first evaporator 58.
  • Some examples of fluids that can be used as refrigerants in second stage system portion 34 are carbon dioxide (CO2; for example, R-744), nitrous oxide (N2O; for example, R-744A), or mixtures of carbon dioxide and nitrous oxide, or hydrocarbon based refrigerants (for example, R- 170).
  • CO2 carbon dioxide
  • N2O nitrous oxide
  • R- 170 hydrocarbon based refrigerants
  • compressor 38 compresses a refrigerant vapor and delivers the compressed vapor to condenser 40 through a discharge line.
  • Compressor 38 can be a screw compressor, reciprocating compressor, centrifugal compressor, rotary compressor, swing link compressor, scroll compressor, turbine compressor or any other suitable type of compressor.
  • the vapor phase refrigerant enters condenser 40 and transfers heat to a fluid, e.g., water from a cooling tower. The heat transfer causes the vapor phase refrigerant to condense to a liquid phase refrigerant.
  • the liquid phase refrigerant exiting condenser 40 can be stored in receiver 42 before flowing through expansion device 44 to evaporator 46, which is incorporated in heat exchanger 36.
  • First stage system 32 can be operated as a transcritical or supercritical system. During transcritical operation, first stage system 32 can be operated partly below (sub-critical) and partly above (supercritical) the critical pressure of the refrigerant circulated in first stage system 32.
  • the discharge pressure of compressor 38 can be greater than the critical pressure of the refrigerant, e.g., 73 bar at 31 deg C for carbon dioxide.
  • the refrigerant is maintained as a single phase refrigerant (vapor phase) in the high pressure side of first stage system 32 and is first converted into the liquid phase when it is expanded in expansion device 44.
  • the refrigerant from compressor 38 flows to a gas cooler (which can operate as a condenser in low ambient temperatures permitting the system to operate sub- critical) that cools the refrigerant by heat exchange with another fluid.
  • the cooling of the refrigerant gradually increases the density of the refrigerant.
  • the high side pressure can be modulated to control capacity or to optimize the coefficient of performance by regulating the refrigerant charge and/or by regulating the total internal high side volume of refrigerant.
  • compressor 48 compresses a refrigerant vapor and delivers the compressed vapor to condenser 50 through a discharge line.
  • Compressor 48 can be a screw compressor, reciprocating compressor, centrifugal compressor, rotary compressor, swing link compressor, scroll compressor, turbine compressor or any other suitable type of compressor.
  • the vapor refrigerant enters condenser 50 and transfers heat to the fluid being circulated in evaporator 46. The heat transfer causes the vapor phase refrigerant to condense to a liquid phase refrigerant.
  • the liquid phase refrigerant exits condenser 50 and flows to receiver 52. From receiver 52, the refrigerant is circulated in parallel to a first expansion device 56 and a first evaporator 58 and to a valve 60 and a second evaporator 62 by pump 54.
  • first evaporator 58 the liquid refrigerant from first expansion device 56 absorbs heat from a cooling load, e.g., a fluid, and undergoes a phase change to a refrigerant vapor.
  • the refrigerant vapor exits first evaporator 58 and returns to compressor 48 to complete the cycle.
  • second evaporator 62 the liquid refrigerant from valve 60 absorbs heat from a cooling load, e.g., a fluid, and may undergo a phase change to a refrigerant vapor.
  • the amount of refrigerant liquid provided to second evaporator 62 may exceed the heat exchange capabilities of the cooling load, causing less than all of the liquid refrigerant to undergo a phase change.
  • the refrigerant exiting second evaporator 62 may be a mixture of vapor phase refrigerant and liquid phase refrigerant.
  • the refrigerant exiting second evaporator 62 regardless of the phase, returns to receiver 52.
  • Receiver 52 can also have a connection to the discharge line from compressor 48 to provide refrigerant vapor from receiver 52 to the discharge line and subsequently to condenser 50.
  • Compressor 38 of first stage system 32 and compressor 48 of second stage system 34 can each be driven by a motor or drive mechanism.
  • the motor used with compressor 38 or compressor 48 can be powered by a variable speed drive (VSD) or can be powered directly from an alternating current (AC) or direct current (DC) power source.
  • VSD variable speed drive
  • AC alternating current
  • DC direct current
  • the VSD if used, receives AC power having a particular fixed line voltage and fixed line frequency from the AC power source and provides power having a variable voltage and frequency to the motor.
  • the motor used with compressor 38 or compressor 48 can be any type of electric motor that can be powered by a VSD or directly from an AC or DC power source.
  • the motor used with compressor 38 or compressor 48 can be a switched reluctance motor, an induction motor, an electronically commutated permanent magnet motor, or any other suitable motor type.
  • other drive mechanisms such as steam or gas turbines or engines and associated components can be used to drive the motor used with compressor 38 or compressor 48.
  • FIG. 6 shows an enlarged view of the piping connection detail of FIG. 5.
  • the vapor phase refrigerant from compressor 48 is injected through nozzle 70 into a connection 72.
  • Connection 72 connects two incoming lines, one from receiver 52 and one from compressor 48, to heat exchanger 36.
  • the vapor phase refrigerant from compressor 48 can mix with vapor phase refrigerant from receiver 52.
  • the mixture of the vapor phase refrigerant from compressor 48 and receiver 52 can then pass through a venturi 74.
  • a pressure drop occurs that is intended to draw additional refrigerant gas from receiver 52 into connection 72.
  • FIG. 7 shows an embodiment of a multistage refrigeration system with a second stage system that can be implemented as a volatile system.
  • the multistage refrigeration system of FIG. 7 has a first stage system 80 that can circulate a refrigerant, e.g., ammonia, through compressors 38, condenser 40, an intermediate vessel 82, an expansion device 44, an evaporator 46 that is incorporated in heat exchanger 36 and a second compressor 84.
  • the refrigerant vapor in first stage system 80 exits by compressors 38 and flows to condenser 40.
  • the refrigerant vapor in condenser 40 transfers heat to a fluid, e.g., water, and condenses to a refrigerant liquid.
  • a valve 86 e.g., a float valve, can be incorporated into the fluid connection between condenser 40 and intermediate vessel 82 or within condenser 40. Alternatively, in some embodiments, the valve may be incorporated within the condenser. Valve 86 can be used to control the level of liquid refrigerant in condenser 40 by opening or closing based on the level of liquid refrigerant in condenser 40.
  • the liquid refrigerant flows through intermediate vessel 82 and transfers heat to liquid refrigerant that may be stored, as a reservoir, in the bottom of intermediate vessel 82.
  • the liquid refrigerant from condenser 40 can be cooled as a result of the heat transferred to the liquid refrigerant stored in the reservoir in intermediate vessel 82.
  • the liquid refrigerant flows through expansion device 44 and into evaporator 46, which is incorporated in heat exchanger 36.
  • evaporator 46 the liquid refrigerant absorbs heat from the fluid circulating within second stage system 34 and changes phases to become a refrigerant vapor.
  • the refrigerant vapor exits evaporator 46, is compressed by second compressor 84, and is circulated to intermediate vessel 82 where the refrigerant vapor is injected into the liquid refrigerant located in the reservoir of intermediate vessel 82.
  • the refrigerant vapor can then be cooled by the liquid refrigerant in the reservoir 82 as the refrigerant vapor bubbles up through the liquid refrigerant, exits the top of intermediate vessel 82, and enters compressors 38.
  • the temperature of the liquid refrigerant and the refrigerant vapor in intermediate vessel 82 may correspond to the saturation temperature of the refrigerant since both liquid phase refrigerant and vapor phase refrigerant are present in intermediate vessel 82.
  • the flow connection line that circulates liquid refrigerant from condenser 40 through intermediate vessel 82 can have an additional connection line 88 that serves as an inlet to the liquid refrigerant reservoir located in intermediate vessel 82. Connection line 88 can be controlled by a valve 90. Valve 90 can be opened when the level of the liquid refrigerant in the reservoir is less than a preselected minimum level, e.g., the level is below the discharge connection from compressor 84, as determined by a level sensor in the intermediate vessel 82.
  • Second stage system 34 can circulate a refrigerant, e.g., carbon dioxide, through a receiver or separator 52, one or more pumps 54, one or more evaporators (not shown) and a condenser 50 that is incorporated in heat exchanger 36.
  • a refrigerant e.g., carbon dioxide
  • Liquid refrigerant in receiver 52 is circulated to the evaporators by pumps 54.
  • the liquid refrigerant undergoes a phase change to a refrigerant vapor and returns to the receiver 52.
  • vapor refrigerant is circulated to condenser 50 to transfer heat to the fluid in evaporator 46 of first stage system 80.
  • the vapor refrigerant condenses to become a refrigerant liquid.
  • the refrigerant liquid from condenser 50 can then flow to receiver 52 to be circulated to the evaporators by pumps 54.
  • the second stage system may circulate a glycol solution or a brine solution.
  • FIGS. 8 and 9 show embodiments of a multistage refrigeration system with an additional third stage system that can be implemented as a volatile system.
  • the multistage refrigeration systems of FIGS. 8 and 9 are similar to the multistage refrigeration system of FIG. 7 except that an additional third stage system has been included.
  • a third stage system 92 is interconnected with first stage system 80 by a heat exchanger 94.
  • Third stage system 92 can circulate a refrigerant, e.g., carbon dioxide, through a receiver or separator 96, a pump 98, one or more evaporators (not shown) and a condenser 100 that is incorporated in heat exchanger 94.
  • Liquid refrigerant in receiver 96 is circulated to the evaporators by pump 98. In the evaporators, the liquid refrigerant undergoes a phase change to a vapor phase refrigerant and returns to receiver 96.
  • the vapor refrigerant is circulated to condenser 100, which is incorporated into heat exchanger 94.
  • the vapor refrigerant transfers heat to the liquid refrigerant flowing within heat exchanger 94 causing the vapor refrigerant to condense into a liquid.
  • the liquid refrigerant that receives heat from the vapor refrigerant flows to heat exchanger 94 from the reservoir in intermediate vessel 82, absorbs heat from the vapor refrigerant, and returns to the reservoir in intermediate vessel 82.
  • the liquid refrigerant is circulated through heat exchanger 94 by a pump 102.
  • the refrigerant that returns to intermediate vessel 82 from heat exchanger 94 may be in a vapor and/or liquid state.
  • a third stage system 104 is interconnected with first stage system 80 in intermediate vessel 82.
  • Third stage system 104 can circulate a refrigerant, e.g., carbon dioxide, through a receiver or separator 96, a pump 98, one or more evaporators (not shown) and a condenser 106 that is incorporated into intermediate vessel 82.
  • a refrigerant e.g., carbon dioxide
  • Liquid refrigerant in receiver 96 is circulated to the evaporators by pump 98.
  • the liquid refrigerant undergoes a phase change to a refrigerant vapor and returns to the receiver 96.
  • the vapor refrigerant is circulated to condenser 106 to transfer heat to the liquid in the reservoir of intermediate vessel 82, which causes the vapor refrigerant to condense into a refrigerant liquid.
  • the liquid refrigerant exiting condenser 106 is then returned to receiver 96.
  • the liquid refrigerant in the reservoir that receives heat from the vapor refrigerant vessel may undergo a phase change to a refrigerant vapor.
  • the refrigerant vapor is returned to compressors 38 through the top of intermediate vessel 82.
  • FIG. 10 shows another embodiment of a multistage system.
  • the multistage system of FIG, 8 includes a first stage system 110, a second stage system 112 and a third stage system 114.
  • First stage system 110 is interconnected with second stage system 112 by a heat exchanger 116.
  • First stage system 110 is also interconnected with third stage system 114 by a heat exchanger 118.
  • Second stage system 112 is interconnected with third stage system 114 by a heat exchanger 121.
  • First stage system 110 can be a vapor compression system that circulates a refrigerant, e.g., carbon dioxide, through a compressor 38, a condenser or gas cooler 40, a heat exchanger 120, a first expansion device 44, an evaporator 122, a second expansion device 124, an evaporator 126 incorporated into heat exchanger 116, a third expansion device 128, an evaporator 130 incorporated into heat exchanger 118 and receiver 132.
  • a refrigerant e.g., carbon dioxide
  • first stage system 121 when operated sub-critically, the compressed refrigerant vapor from compressor 38 can be provided to condenser 40.
  • the refrigerant vapor transfers heat to a fluid, e.g., air or water, and condenses to a refrigerant liquid as a result.
  • the condensed liquid refrigerant from condenser 40 then flows into heat exchanger 120 to be further cooled by entering into a heat exchange relationship with the refrigerant vapor from receiver 132.
  • the refrigerant liquid exiting heat exchanger 120 can flow to one of three paths connected to three separate evaporators.
  • the refrigerant liquid can flow through first expansion device 44 and first evaporator 122.
  • the refrigerant liquid can flow through second expansion device 124 and evaporator 126 incorporated into heat exchanger 116.
  • the refrigerant liquid can flow through third expansion device 128 and evaporator 130 incorporated into heat exchanger 118.
  • first evaporator 122 the liquid refrigerant absorbs heat from a fluid, e.g., air or water, and undergoes a phase change to a refrigerant vapor.
  • the refrigerant vapor from evaporator 122 can then be circulated to receiver 132 to remove any refrigerant liquid that may be present in the refrigerant vapor.
  • the liquid refrigerant absorbs heat from the fluid being circulated in heat exchanger 134 by second stage system 112, and undergoes a phase change to a refrigerant vapor.
  • the vapor refrigerant exits second evaporator 126 and can flow to receiver 132.
  • third evaporator 130 the liquid refrigerant absorbs heat from the fluid being circulated in heat exchanger 136 by third stage system 114, and undergoes a phase change to a refrigerant vapor.
  • the refrigerant vapor exiting each of the three evaporators, 122, 126, and 130 is collected in receiver 132.
  • Refrigerant vapor exiting receiver 132 is circulated to heat exchanger 120 to be heated by the refrigerant liquid from condenser 40 before being circulated to compressor 38 to complete the cycle.
  • first stage system 110 can be operated transcritically.
  • the compressed refrigerant vapor from compressor 38 can be provided to gas cooler 40 where the refrigerant vapor transfers heat to a fluid, e.g., air or water, and is cooled to a lower temperature.
  • the cooled vapor refrigerant from gas cooler 40 then flows into heat exchanger 120 to be further cooled by entering into a heat exchange relationship with the refrigerant vapor from receiver 132.
  • the cooled refrigerant vapor from heat exchanger 120 is then expanded to a refrigerant liquid and refrigerant vapor in first expansion device 44, second expansion device 124 or third expansion device 128.
  • Second stage system 112 can be vapor compression system that circulates a refrigerant, e.g., carbon dioxide, through a compressor 48, a condenser 138, a heat exchanger 134 that is incorporated into heat exchanger 116, a first expansion device 56, an evaporator 58, a second expansion device 140 and heat exchanger 121.
  • a refrigerant e.g., carbon dioxide
  • the compressed refrigerant vapor from compressor 48 can flow to condenser 138.
  • the refrigerant vapor transfers heat to a fluid, e.g., air or water, and condenses to a refrigerant liquid.
  • the condensed liquid refrigerant then flows into heat exchanger 134 incorporated into heat exchanger 116 to be further cooled by entering into a heat exchange relationship with the refrigerant liquid circulated in evaporator 126.
  • the liquid refrigerant exiting heat exchanger 134 can flow through one of two paths. On the first path, the refrigerant can flow through expansion device 56 to evaporator 58, and on the second path, the refrigerant can flow through expansion device 140 to heat exchanger 121.
  • the liquid refrigerant absorbs heat from a fluid, e.g., air or water, and undergoes a phase change to a refrigerant vapor.
  • the refrigerant vapor from evaporator 58 can then return to compressor 48 to complete the cycle.
  • the liquid refrigerant absorbs heat from the fluid from heat exchanger 136 of third stage system 114 and undergoes a phase change to a refrigerant vapor.
  • the refrigerant vapor exits heat exchanger 121 and then flows to compressor 48 to complete the cycle.
  • Third stage system 114 can be a vapor compression system that circulates a refrigerant, e.g., carbon dioxide, through a compressor 49, a condenser 142, a heat exchanger 136 that is incorporated into heat exchanger 118, heat exchanger 121, a first expansion device 55 and one or more evaporators 57, 59.
  • a refrigerant e.g., carbon dioxide
  • the refrigerant vapor from compressor 49 can flow to condenser 142 where the refrigerant vapor transfer heat to a fluid, e.g., air or water, and condenses into a refrigerant liquid.
  • condenser 138 of second stage system 112 and condenser 142 of third stage system 114 can be integrated into a single unit that uses the same fluid for heat exchange while still maintaining circuit separation between second stage system 112 and third stage system 114.
  • the condensed liquid refrigerant from condenser 142 then flows into heat exchanger 136, which is incorporated into heat exchanger 118 to be further cooled by entering into a heat exchange relationship with the refrigerant liquid circulated in evaporator 130 by first stage system 110. After exiting heat exchanger 136, the liquid refrigerant flows through heat exchanger 121.
  • the liquid refrigerant enters into a heat exchange relationship with fluid from heat exchanger 134 of second stage system 112 and is cooled by the heat exchange with the fluid from heat exchanger 134 of second stage system 114.
  • the refrigerant liquid exits heat exchanger 121 and flows through expansion device 55 to evaporators 57 and 59 where the liquid refrigerant enters into a heat exchange relationship with a fluid, e.g., air or water to change from a liquid phase to a vapor phase refrigerant.
  • the refrigerant vapor from evaporators 57 and 59 can then return to compressor 49 to complete the cycle.
  • FIG. 11 shows an embodiment of a second stage system employed in a multistage system.
  • the second stage system can include a compressor 150 and heat exchanger 36 that receives refrigerant vapor from compressor 150.
  • heat exchanger 36 the refrigerant vapor transfers heat to a fluid from a first stage system to condense into liquid phase refrigerant.
  • the liquid refrigerant exiting heat exchanger 36 flows to a receiver 152.
  • a valve 154 e.g., a float valve, can be used to control the flow of liquid refrigerant from heat exchanger 36 to receiver 152.
  • Valve 154 can be used to control the amount of liquid refrigerant flowing to receiver 152 by opening or closing based on the level of liquid refrigerant in heat exchanger 36.
  • Liquid refrigerant in receiver 152 flows to a heat exchanger 156.
  • the liquid refrigerant can absorb heat from a glycol solution or a brine solution that is in fluid communication with one or more evaporators (not shown) to change phases into a vapor phase refrigerant.
  • the refrigerant vapor After exiting heat exchanger 156 the refrigerant vapor returns to receiver 152.
  • the refrigerant vapor can be returned to the receiver using a siphon effect based on the temperature and pressure differences between the heat exchanger and the receiver.
  • the vapor refrigerant within receiver 152 can be returned to compressor 150.
  • a pressure regulating valve 158 can be used to control the flow of vapor refrigerant from receiver 152 to compressor 150 to maintain a desired pressure level in receiver 152. If the pressure in receiver 152 is below a desired threshold pressure, pressure regulating valve 158 can remain closed until the pressure in receiver 152 exceeds the desired pressure threshold. Once the desired pressure threshold is exceeded, pressure regulating valve 158 opens and provides vapor refrigerant to compressor 150 to lower the pressure in receiver 152.
  • compressor 150 can be screw compressor and the return of the refrigerant gas from receiver 152 to compressor 150 can be through an economizer port for compressor 150. The economizer port can be located in compressor 150 to provide fluid communication to a suction chamber of compressor 150 or to a discharge chamber of compressor 150.
  • FIG. 12 shows a control process for controlling the pressure in a receiver of a second stage system during start-up of a multistage refrigeration system.
  • the control process begins by measuring the pressure in a receiver of a second stage system (step 200). The measured pressure is then compared to previous pressure measurements to determine if the pressure in the receiver is increasing (step 202). If the pressure in the receiver is increasing, the flow of refrigerant fluid from the receiver to the evaporators of the second stage system can be decreased (step 204). The flow of refrigerant fluid from the receiver to the evaporators can be decreased by adjusting the position of a three-way valve (see FIG. 13, e.g. valve 304), by adjusting the position of a valve and opening and closing additional valves (see FIG.
  • valves 308, 310, 312 and 314) by turning off the pump (see FIG. 15, e.g. pump 54), by decreasing the operating speed of a variable speed pump (see FIG. 16), or by any other suitable technique or apparatus.
  • the pressure in the receiver is not increasing (or is decreasing)
  • the flow of refrigerant fluid from the receiver to the evaporators of the second stage system can be increased (step 206).
  • the flow of refrigerant fluid from the receiver to the evaporators can be increased by adjusting the position of a three-way valve (see FIG. 13), by opening and closing additional valves (see FIG. 14), by turning on the pump (or by leaving the pump operate) (see FIG.
  • step 208 a determination is made as to whether the multistage refrigeration system is operating at full capacity.
  • the multistage refrigeration system can be determined to be at full capacity when both the first stage compressors and the second stage compressors are at full capacity and the second stage pumps are at full capacity. If the multistage refrigeration system is not at full capacity, the process repeats, starting with measuring the pressure in the second stage system receiver. If the multistage refrigeration system is at full capacity, then the process ends.
  • FIGS. 13 through 16 show different embodiments for implementing the control process of FIG. 12.
  • a sensor 300 can be located in a second stage system receiver 52 to measure the pressure in second stage system receiver 52.
  • a signal from sensor 300 representative of the pressure in second stage system receiver 52 can be provided to a controller 302.
  • Controller 302 can then process the signal from the sensor in accordance with the control process of FIG. 12 to limit the pressure in second stage system receiver 302. It is to be understood that while the pressure in the second stage system receiver is measured in FIGS. 13-16, any parameters that can correspond to or can be converted to a pressure measurement can also be used.
  • FIG. 13 shows an exemplary embodiment for limiting the pressure in second stage system receiver 52 employing a three-way valve 304 and a return line 306 that is connected to second stage system receiver 52.
  • the three-way valve 304 can be located between pump 54 for second stage system receiver 52 and the evaporators for the second stage system.
  • the return line 306 can be connected to the three-way valve 304.
  • the three-way valve 304 can then be controlled to regulate the amount of refrigerant fluid entering the evaporators and returning to second stage system receiver 52 through return line 306.
  • controller 302 can position three-way valve 304 to permit more flow to the evaporators and less (or no) flow to return line 306.
  • controller 302 can position three-way valve 304 to permit less (or no) flow to the evaporators and more flow to return line 306.
  • FIG. 14 shows an exemplary embodiment for limiting the pressure in second stage system receiver 52 employing return line 306 that is connected to second stage system receiver 52, a valve 308 disposed in return line 306, a valve 310 in the line between pump 54 and the evaporators, and valves valve 312 and 314 in a bypass flow configuration around valve 310.
  • pump 54 can provide full flow of refrigerant fluid to the evaporators.
  • valve 310 is closed and valve 308 and valve 314 are open, the position of valve 312 can control the amount of refrigerant flow to the evaporators from pump 54 and the amount of refrigerant flow through return line 306 to second stage system receiver 52.
  • controller 302 can close valve 310 (or keep valve 310 closed), open valves 308 and 314 (or keep valves 308 and 314 open) and position valve 312 to permit more refrigerant flow to the evaporators and less refrigerant flow back to second stage system receiver 52 through return line 306.
  • controller 302 can close valve 310 (or keep valve 310 closed), open valves 308 and 314 (or keep valves 308 and 314 open) and position valve 312 to permit less refrigerant flow to the evaporators and more refrigerant flow back to second stage system receiver 52 through return line 306.
  • FIG. 15 shows an embodiment for limiting the pressure in second stage system receiver 52 by providing control signals to pump 54 to start or stop pump 54.
  • Pump 54 when operating, provides refrigerant fluid to the evaporators.
  • controller 302 When the amount of refrigerant flow is to be increased to the evaporators, controller 302 either permits pump 54 to continue operating or starts pump 54 if it was not operating.
  • controller 302 stops pump 54.
  • FIG. 16 shows an embodiment for limiting the pressure in second stage system receiver 52 employing a variable speed pump 320 and a variable speed drive 322.
  • the variable speed pump 320 is used to provide the refrigerant fluid to the evaporators.
  • the speed of the variable speed pump 320 can be controlled by signals sent to variable speed pump 320 by variable speed drive 322.
  • Variable speed pump 320 can be controlled to regulate the amount of refrigerant fluid that variable speed pump 320 provides to the evaporators.
  • controller 302 can send signals to variable speed drive 322 to increase the speed of variable speed pump 320.
  • controller 302 can send signals to variable speed drive 322 to decrease the speed of variable speed pump 320.

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  • Engineering & Computer Science (AREA)
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  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Defrosting Systems (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Lubricants (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Compressor (AREA)
  • Central Heating Systems (AREA)

Abstract

L'invention concerne un système de réfrigération à étages multiples. Le système de réfrigération à étages multiples comprend un premier système configuré pour faire circuler un premier réfrigérant à travers un premier circuit et un second système configuré pour faire circuler un second réfrigérant à travers un second circuit. Les systèmes sont agencés de sorte que de la chaleur soit échangée par un premier réfrigérant dans un premier évaporateur de système avec un second réfrigérant dans un second condenseur de système.
PCT/US2008/056275 2007-03-09 2008-03-07 Système de réfrigération WO2008112569A2 (fr)

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US89405207P 2007-03-09 2007-03-09
US60/894,052 2007-03-09
US91717507P 2007-05-10 2007-05-10
US60/917,175 2007-05-10

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PCT/US2008/056275 WO2008112569A2 (fr) 2007-03-09 2008-03-07 Système de réfrigération
PCT/US2008/056222 WO2008112549A2 (fr) 2007-03-09 2008-03-07 Échangeur de chaleur
PCT/US2008/056270 WO2008112566A2 (fr) 2007-03-09 2008-03-07 Système de réfrigération
PCT/US2008/056233 WO2008112554A1 (fr) 2007-03-09 2008-03-07 Système de réfrigération
PCT/US2008/056287 WO2008112572A1 (fr) 2007-03-09 2008-03-07 Système de réfrigération
PCT/US2008/056273 WO2008112568A2 (fr) 2007-03-09 2008-03-07 Compresseur
PCT/US2008/056338 WO2008112591A2 (fr) 2007-03-09 2008-03-08 Système de réfrigération
PCT/US2008/056342 WO2008112594A2 (fr) 2007-03-09 2008-03-08 Système de compression de vapeur
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PCT/US2008/056233 WO2008112554A1 (fr) 2007-03-09 2008-03-07 Système de réfrigération
PCT/US2008/056287 WO2008112572A1 (fr) 2007-03-09 2008-03-07 Système de réfrigération
PCT/US2008/056273 WO2008112568A2 (fr) 2007-03-09 2008-03-07 Compresseur
PCT/US2008/056338 WO2008112591A2 (fr) 2007-03-09 2008-03-08 Système de réfrigération
PCT/US2008/056342 WO2008112594A2 (fr) 2007-03-09 2008-03-08 Système de compression de vapeur
PCT/US2008/056340 WO2008112593A1 (fr) 2007-03-09 2008-03-08 Système de réfrigération

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WO2008112568A3 (fr) 2008-12-24
WO2008112549A2 (fr) 2008-09-18
WO2008112569A3 (fr) 2008-11-27
WO2008112591A2 (fr) 2008-09-18
WO2008112572A1 (fr) 2008-09-18
WO2008112568A2 (fr) 2008-09-18
WO2008112591A3 (fr) 2008-12-11
WO2008112566A2 (fr) 2008-09-18
WO2008112566A3 (fr) 2009-02-05
WO2008112549A3 (fr) 2008-12-24
WO2008112594A3 (fr) 2008-11-13
WO2008112593A1 (fr) 2008-09-18
WO2008112554A1 (fr) 2008-09-18

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