US20110094250A1 - refrigeration installation for cooling at least one piece of furniture and/or a walk-in cooler, and for heating at least one room of premises, and an air heat exchanger for such an installation - Google Patents

refrigeration installation for cooling at least one piece of furniture and/or a walk-in cooler, and for heating at least one room of premises, and an air heat exchanger for such an installation Download PDF

Info

Publication number
US20110094250A1
US20110094250A1 US12/999,446 US99944609A US2011094250A1 US 20110094250 A1 US20110094250 A1 US 20110094250A1 US 99944609 A US99944609 A US 99944609A US 2011094250 A1 US2011094250 A1 US 2011094250A1
Authority
US
United States
Prior art keywords
circuit
pressure
refrigeration
heat exchanger
unit
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.)
Abandoned
Application number
US12/999,446
Other languages
English (en)
Inventor
Jean-Marc Gourgouillat
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.)
2F2C
Original Assignee
2F2C
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 2F2C filed Critical 2F2C
Assigned to 2F2C reassignment 2F2C ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GOUROUILLAT, JEAN-MARC
Assigned to 2F2C reassignment 2F2C ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GOURGOUILLAT, JEAN-MARC
Publication of US20110094250A1 publication Critical patent/US20110094250A1/en
Abandoned legal-status Critical Current

Links

Images

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
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • 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
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control

Definitions

  • the present invention relates to the technical field of refrigeration installations that are used for cooling various substances, and in particular foodstuffs.
  • a refrigeration installation comprising high-pressure and low-pressure refrigerant fluid circuits connected to one or more refrigeration units such as a reach-in coolers or refrigerated display cabinets, or indeed walk-in coolers.
  • the refrigeration installation further comprises a compression unit that sucks in refrigerant fluid from the low-pressure circuit and delivers it once compressed into the high-pressure circuit. Downstream from the compression unit, the installation further comprises an exterior condenser at which the refrigerant fluid is cooled before being re-directed towards the refrigeration unit or towards an intermediate storage tank.
  • Such an installation is fully satisfactory as regards keeping fragile substances or foodstuffs at low temperature settings.
  • the heat extracted from the refrigeration units and resulting from the work of the compression unit is dissipated to the outside, constituting a total loss of energy that, in view of energy costs and of sustainable development requirements, is unsatisfactory.
  • Patent Application EP 0 431 797 proposes to adapt, in a unit heater, a condenser circuit fed with a gaseous high-pressure refrigerant fluid in such manner as to recover heat for the purpose of heating premises.
  • a condenser circuit fed with a gaseous high-pressure refrigerant fluid in such manner as to recover heat for the purpose of heating premises.
  • the installation proposed by Application EP 0 431 797 does not make it possible to have enough heat to achieve, on its own, satisfactory heating in the winter.
  • Patent Application EP 1 921 401 proposes a refrigeration installation from which the extracted heat is recovered for the purpose of heating a heat accumulator that is in communication with a central-heating water circuit and/or with a hot-water circuit.
  • the installation disclosed in Patent Application EP 1 921 401 further comprises an exterior evaporator that, during the winter period, makes it possible to take from the outside the extra heat necessary for satisfying heating needs.
  • the heat extracted by the installation disclosed in EP 1 921 401 is removed mainly to an exterior condenser that is totally independent of the exterior evaporator.
  • Patent Application EP 1 921 401 makes provision to place the interior heat exchanger for the heating in series with the exterior condenser, and upstream therefrom, thereby detrimentally affecting the energy efficiency of the installation and requiring a large quantity of refrigerant fluid in the liquid state to fill the circuit downstream from the heat exchanger when the refrigerant fluid is fully condensed therein.
  • the invention provides a refrigeration installation having refrigerant fluid and comprising at least:
  • a refrigeration unit comprising at least one evaporator disposed in a piece of furniture or in a walk-in cooler, and connected to the high-pressure and low-pressure circuits;
  • an air-conditioning unit comprising at least one heat exchanger that is disposed inside a room of premises, and that further comprises at least one condenser connected to the high-pressure and low-pressure circuits;
  • an exterior unit comprising at least one air heat exchanger that is disposed outside and that comprises a condensation tube circuit connected to the high-pressure and low-pressure circuits;
  • a main compression unit connected to the high-pressure and low-pressure circuits
  • control unit that controls at least operation of the refrigeration installation.
  • the refrigeration installation is characterized in that:
  • the air heat exchanger of the exterior unit further comprises:
  • an evaporation tube circuit adapted to be fed with low-pressure refrigerant fluid only and connected to the high-pressure and low-pressure circuits;
  • thermally conductive fins interconnecting the evaporation tube circuit and the condensation tube circuit by being secured to the evaporation and condensation tube circuits;
  • condensation tube circuit being adapted to be fed with high-pressure refrigerant fluid only and being dimensioned so as to dissipate all of the heat resulting from keeping each refrigeration unit at temperature settings when a summer temperature prevails outside;
  • control unit is adapted to place the installation:
  • auxiliary compression unit is available for extracting heat from the exterior unit, and the power of each other compression unit is available for extracting heat from each refrigeration unit;
  • the compression units are dimensioned so that their cumulative power is sufficient for maintaining each refrigeration unit at temperature settings when a summer temperature prevails outside and when the installation is in purely refrigeration mode.
  • Such a refrigeration installation of the invention is particularly suitable for cooling refrigeration units and for heating a room or some other portion of premises with the heat recovered from the refrigeration units and resulting from the compression of the refrigerant fluid.
  • implementing an auxiliary compression unit makes it possible, when the heat recovered from the refrigeration units is not sufficient to heat the room satisfactorily, to take from the outside the heat that is lacking and that is necessary to reach the satisfactory heating level.
  • the heat exchanger of each air-conditioning unit may be of any suitable type.
  • the heat exchanger of each air-conditioning unit or of each of some units only may be a heat exchanger making it possible to heat a heat transfer liquid, such as, for example, but not exclusively, the water of a heating circuit, or indeed the water of a hot-water system.
  • the heat exchanger of each air-conditioning unit, or of each of some units only may also be an air heat exchanger or “unit heater”.
  • Implementing such an air heat exchanger offers the advantage of heating the air directly without using an intermediate heat transfer fluid, and makes it possible to procure optimum efficiency and to simplify implementation and use of the refrigeration installation of the invention.
  • the installation of the invention is also suitable for implementing a plurality of air-conditioning units having different types of heat exchanger.
  • the high-pressure and low-pressure circuits may comprise a main high-pressure circuit, a secondary high-pressure circuit, and a main low-pressure circuit.
  • the evaporator of the air-conditioning unit is then fed with refrigerant fluid by the main high-pressure circuit via an expansion valve and is connected to the main low-pressure circuit.
  • the evaporation circuit of the exterior unit is fed by the main high-pressure circuit via an expansion valve and is connected to an auxiliary low-pressure circuit, while the condensation circuit of the exterior unit is connected to the main high-pressure circuit upstream from the evaporators.
  • the main compression unit sucks in refrigerant fluid from the main low-pressure circuit and delivers compressed refrigerant fluid to the main high-pressure circuit
  • the auxiliary compression unit sucks in refrigerant fluid from the auxiliary compression unit and delivers compressed refrigerant fluid to the main high-pressure circuit.
  • the installation may further comprise an isolation valve that is controlled to open or close the communication between the auxiliary low-pressure circuit and the evaporation circuit of the exterior heat exchanger, and a bypass circuit that connects the main low-pressure circuit to the secondary low-pressure circuit and that is equipped with a bypass valve controlled to open or close the bypass circuit.
  • the control unit is then adapted:
  • control unit is adapted to go from the combined operating mode to the purely refrigeration operating mode and vice versa as a function of the refrigeration needs.
  • the installation further comprises defrosting means for defrosting the heat exchanger of the exterior unit, which means are adapted so that, when the installation is operating in combined mode, they temporarily feed the condensation circuit of the exterior unit.
  • defrosting means makes it possible to preserve the effectiveness of the exterior heat exchanger in particular when said heat exchanger is used as a heat source during the winter period.
  • condensation circuit designed to withstand the high pressures of the refrigerant fluid, makes it possible to avoid using defrosting by cycle reversal at the evaporation circuit, thereby offering the advantage firstly of not being obliged to dimension the evaporation circuit for high pressures, and secondly of avoiding subjecting the evaporation circuit to the thermal shock resulting from rapidly going from a negative temperature to a positive temperature, e.g. greater than 30° C. and, furthermore, of avoiding the risks of sucking in liquid on re-starting in heat pump mode.
  • the fins interconnecting the condensation circuit and the evaporation circuit damp the expansion differences between the condensation circuit and the evaporation circuit during defrosting stages, thereby reducing the mechanical stresses to which these circuits are subjected.
  • the invention makes it possible to optimize their dimensioning for their nominal rated operating conditions with acceptable head loss, and fluid speeds that are under control, making it possible for good oil return to be achieved, thereby contributing to the performance of the refrigeration installation as a whole.
  • the installation further comprises:
  • frost assessment means for assessing the frost on the exterior heat exchanger
  • At least one controlled valve for feeding the condensation circuit of the air heat exchanger
  • control unit is adapted to cause a feed valve for feeding the condensation circuit to open whenever the frost on the heat exchanger exceeds a certain threshold.
  • frost detection may be performed in various manners such as, for example, by monitoring the load on a forced-flow fan motor of the heat exchanger so as to deduce from any increase in load on the motor that frost has appeared on the heat exchanger.
  • the frost assessment means comprise means for measuring the humidity in the air entering and exiting from the heat exchanger.
  • control unit is adapted to reverse the direction of operation of an extractor fan equipping the exterior heat exchanger at the end of defrosting thereof. This rotation reversal makes it possible to obtain optimum drying of the heat exchanger of the exterior unit.
  • the installation may be adapted to activities requiring a plurality of low temperature levels, such as, for example, activities in which it is necessary to keep some substances cool at positive temperatures and also to keep some substances frozen at negative temperatures.
  • the refrigeration installation of the invention then further comprises:
  • a secondary refrigeration unit comprising at least one evaporator that is disposed in a piece of furniture or in a walk-in cooler, that is fed with refrigerant fluid by the main high-pressure circuit via an expansion valve, and that is connected to the secondary low-pressure circuit;
  • a secondary compression unit that sucks in refrigerant fluid from the secondary low-pressure circuit and that delivers compressed refrigerant fluid into the main high-pressure circuit
  • control unit being adapted to cause the secondary compression unit to operate.
  • the auxiliary compression unit power is not sufficient to cool the room under summer outside temperature conditions.
  • At least one unit heater of the air-conditioning unit is adapted to be reversible and to operate as a condenser or as an evaporator, and the installation further comprises means for feeding refrigerant fluid to each unit heater operating as an evaporator.
  • the auxiliary compression unit has sufficient power to cool the room with summer outside temperatures.
  • the invention also provides an air heat exchanger for a refrigeration installation of the invention, which air heat exchanger comprises:
  • condensation tube circuit adapted to be fed with high-pressure refrigerant fluid only
  • thermally conductive fins interconnecting the evaporation tube circuit and the condensation tube circuit by being secured to the evaporation and condensation tube circuits.
  • the condensation circuit has heat exchange power that is sufficient to remove heat in the summer period, i.e. the absolute value of the thermal power of the condensation tube circuit is greater than or equal to the absolute value of the thermal power of the evaporation tube circuit.
  • the heat exchanger of the invention offers the advantage of having an evaporation circuit that is distinct from the condensation circuit so that each of these circuits is appropriately dimensioned for optimally performing its condensing function or its evaporating function, unlike a heat exchanger in which the circuit is adapted for combined operation either as a condenser or as an evaporator.
  • the design of the heat exchanger of the invention thus enables it to procure optimum energy efficiency.
  • implementing fins that are common to the evaporation circuit and to the condensation circuit makes it possible to optimize the heat exchanges during defrosting that can then be shorter than the defrosting time in a design consisting merely in juxtaposing a condenser and an evaporator one above the other.
  • the fins mechanically damp differential expansion phenomena during defrosting.
  • the thermal power of the condensation tube circuit has a value lying in the range 1 times the absolute value of the thermal power of the evaporation tube circuit to 5 times said absolute value.
  • the heat exchange surface area of the condensation tube circuit represents in the range 50% of the sum of the heat exchange surface areas of the condensation and evaporation tube circuits to 80% of said sum.
  • the condensation circuit under normal conditions of use, is situated at least in part below the evaporation circuit. This configuration makes it possible to make advantageous use of convection phenomena so as to accelerate defrosting of the evaporation circuit.
  • the condensation circuit and the evaporation circuit comprise loops or tube sheets and certain loops or sheets of the evaporation circuit are superposed on and interleaved between the loops or sheets of the condensation circuit.
  • the fins extend substantially vertically.
  • the evaporation and condensation circuits have rectilinear main tubes that are inclined by a few degrees relative to the horizontal, thereby facilitating run-off of water.
  • the condensation circuit comprises at least one tube sheet that forms the first tube sheet starting from the bottom of the heat exchanger.
  • This first tube sheet advantageously forms a surface on which a fraction of the water present in the air condenses or is deposited, thereby reducing the load of the air flowing in the heat exchanger, and thus reducing the speed at which frost appears on the evaporation circuit.
  • the heat exchanger further comprises at least one electric fan for forcing air to flow through the heat exchanger.
  • FIG. 1 is a diagrammatic view of a refrigeration installation of the invention
  • FIG. 2 is a longitudinal section view a heat exchanger of the invention that is suitable for being implemented in the installation shown in FIG. 1 ;
  • FIG. 3 is a cross-section view of the heat exchanger on line III-III of FIG. 2 ;
  • FIG. 4 is a diagrammatic view of another embodiment of a refrigeration installation of the invention.
  • a refrigeration installation of the invention includes a main high-pressure refrigerant fluid circuit 2 on which a high-pressure tank 3 is disposed from which a branch 2 a extends for feeding at least one and generally more main refrigeration units R P with high-pressure refrigerant fluid.
  • a refrigeration unit R P includes at least one evaporator disposed in a piece of furniture or in a walk-in cooler. The evaporator is then fed with refrigerant fluid in the liquid state by the main high-pressure circuit 2 a via an expansion valve. The evaporator is also connected to a main low-pressure circuit 4 .
  • the refrigeration installation 1 also includes at least one and, in the example shown, three air-conditioning units 5 disposed inside one or more rooms of premises.
  • each air-conditioning unit comprises at least one air heat exchanger or unit heater equipped with at least one condenser 6 that is connected to the main high-pressure circuit 2 upstream from the evaporators of the refrigeration units R P and, in the example shown, also upstream from the tank 3 of high-pressure refrigerant fluid.
  • the installation 1 also includes a main compression unit 10 that sucks in the refrigerant fluid from the main low-pressure circuit 4 so as to deliver it as compressed into the main high-pressure circuit 2 upstream from the condensers 6 , from the high-pressure tank 3 , and, naturally, from the evaporators that it feeds.
  • the main compression unit 10 comprises at least one and, in the example shown, three compressors 11 connected in parallel to the high-pressure circuit 2 and to the low-pressure circuit 4 . Operation of the compression unit 10 is then controlled by a control unit 12 .
  • the refrigeration installation as defined above operates in the following manner.
  • each main refrigeration unit R P Since each main refrigeration unit R P is provided with an independent regulator device, it causes a valve to open for feeding its evaporator with high-pressure refrigerant fluid via an expansion valve as and when necessary to maintain a setpoint temperature in it. Operation of the refrigeration unit induces an increase in pressure in the main low-pressure circuit 4 that the control unit 12 detects in order to trigger operation of the main compression unit 10 that then sucks in low-pressure refrigerant fluid in a low-pressure gas state so as to deliver it in the high-pressure gas state to the main high-pressure circuit 2 . On exiting from the main compression unit 10 , the refrigerant fluid finds itself in the main high-pressure circuit 2 in the gas state and at a high temperature of the order of in the range 60° C. to 80° C.
  • the invention proposes to use the heat from the high-pressure refrigerant fluid in the gas state to heat one or more rooms of premises via the unit heaters 5 that have their condensers 6 fed via the valves 13 controlled by the control unit 12 .
  • the refrigerant fluid On exiting from the condensers, the refrigerant fluid is in the high-pressure liquid state.
  • those portions of the main high-pressure circuit in which the high-pressure refrigerant fluid is in the gas state are referenced 2
  • those portions in which the refrigerant fluid is mainly in the liquid state are referenced 2 a .
  • the heat recovered at the refrigeration units can, in some situations, in particular in the winter period, be insufficient for heating the premises to an acceptable or indeed comfortable setpoint temperature.
  • the term “the winter period” is used to mean a period in which the average outside temperature is less than 18° C.
  • the invention then proposes to take the heat or the calories that are lacking from the outside.
  • an exterior unit 15 is implemented that comprises at least one heat exchanger 17 that comprises an evaporation circuit 18 connected to the main high-pressure circuit 2 via an expansion valve 19 .
  • the evaporation circuit 18 is also connected to an auxiliary low-pressure circuit 20 that feeds an auxiliary compression unit 21 .
  • the auxiliary compression unit 21 comprises at least one and, in the example shown, two compressors 22 that are connected in parallel to the auxiliary low-pressure circuit 20 and to the main high-pressure circuit 2 .
  • the auxiliary compression unit 20 then sucks in via the auxiliary low-pressure circuit 20 the refrigerant fluid in the gas state coming from the evaporator 18 of the heat exchanger 17 so as to compress it and to deliver it into the main circuit 2 .
  • the auxiliary compression unit 20 is then controlled by the control unit 12 that modulates operation of one of or both of the compressors 22 depending on needs.
  • the auxiliary compression unit 21 and the exterior heat exchanger 5 operate as a heat pump and take from the outside air the extra heat necessary for maintaining the setpoint temperature in the premises by means of the air-conditioning units 5 .
  • the refrigeration installation of the invention makes it possible, by itself, in a combined refrigeration and heat pump operating mode, firstly to cool the refrigeration units and secondly to heat the premises. Such a combined operating mode thus makes it possible to achieve serious energy savings for heating the
  • the evaporator 16 Insofar as the temperature at the surface of the evaporator 18 is negative in view of the expansion of the refrigerant fluid in it, then after a certain operating time, the evaporator 16 is covered in frost coming from condensation and freezing of the water present in the outside atmosphere. It is thus necessary to defrost the condenser 18 regularly.
  • the invention proposes to perform this defrosting by using the heat from the compressed refrigerant fluid exiting from the compression units.
  • the invention proposes to associate a condenser 25 with the evaporator 18 .
  • the condenser 25 fed with high-pressure refrigerant fluid by the main high-pressure circuit 2 by being connected thereto firstly downstream from the compression units and secondly upstream from the tank 3 and from the evaporators of the main refrigeration units R P .
  • the evaporator 18 comprises a tube circuit 30 for evaporating the refrigerant fluid, which circuit is formed by tube sheets 32 comprising rectilinear main tubes as shown more particularly in FIG. 2 .
  • the condenser 25 comprises a tube circuit for condensing the refrigerant fluid, which circuit is made up of sheets 35 of tubes 36 comprising rectilinear main tubes as shown in FIG. 2 .
  • the tube circuits 30 and 35 are then connected together via thermally conductive fins 40 that, in the example shown, extend substantially vertically.
  • the thermal link by conduction that is provided by the fins 40 that are common to the evaporation circuit 30 and to the condensation circuit 35 guarantees that the defrosting is highly effective.
  • the tube sheets of the condensation circuit 35 and of the evaporation circuit 30 are superposed on and interleaved with one another.
  • the first sheet of the heat exchanger 17 starting from the bottom is formed by tubes of the condensation circuit in such a manner as to form a condensation surface for condensing the water vapor present in the air while the exterior unit 15 is operating.
  • the heat exchanger 17 is situated inside a covered frame 41 equipped at its top with at least one and, in the example shown, with two fans 43 forcing air to flow through the exterior unit 15 .
  • the rectilinear portions of the tubes and the fins may be inclined relative respectively to the horizontal and to the vertical by an angle a of a few degrees, e.g. in the range 3° to 5°. This inclination may be obtained by inclining the frame as a whole.
  • the installation may have a bypass 55 connecting the outlet of the auxiliary compression unit 21 upstream from the suction inlet of the main compression unit 10 via a constant-pressure cock 56 controlled by the unit 12 .
  • the condenser 25 is used regularly to defrost the evaporator 18 .
  • This regular operation can be achieved at predefined time intervals independently of the appearance of any frost on the evaporator 18 or, conversely, be a function of the needs when frost actually appears or a function of the forecast appearance of frost.
  • the refrigeration installation 1 may implement means for assessing the frost.
  • frost assessment means may be formed in any suitable manner.
  • the frost assessment means may comprise means 45 for monitoring the load on the fans 43 that, when said load exceeds a predetermined threshold, deduce therefrom that frost has appeared.
  • the frost that deposits on the tubes 30 and on the fins 40 progressively obstructs the heat exchanger 17 , making it more difficult for air to flow therethrough so that the load on the fans 43 increases.
  • the frost detection means may also comprise a system that measures the humidity of the air entering or leaving the exterior unit 15 so as to deduce therefrom whether any frost has appeared.
  • the frost assessment means may also comprise a system for measuring the humidity and the temperature of the outside air so as to act, as a function of those measurements, to forecast appearance of frost.
  • the frost assessment means are connected to the control unit 12 that, whenever necessary, triggers a defrosting cycle.
  • the unit 12 causes the condenser 25 to be fed with hot high-pressure refrigerant fluid.
  • This feeding is achieved via a branch of the main high-pressure circuit 2 that is controlled by a cock 46 controlled by the unit 12 .
  • the cock 46 then makes it possible to admit into the feed circuit of the condenser 25 high-pressure refrigerant gas coming directly from the compression units 10 and 21 .
  • Control of the cocks 46 and 48 then makes it possible to mix the high-pressure gas coming from the compression units with the high-pressure fluid coming from the tank 3 so as to modulate the temperature of the fluid in the condenser 25 in order to bring the condenser and the fins progressively from a negative temperature to a positive temperature that is higher but that is less than the temperature of the compressed refrigerant gas exiting from the compression units.
  • the unit 12 can maintain the temperature of the refrigerant fluid feeding the condenser 25 at values lying approximately in the range 40° C. to 60° C., while the maximum temperature at the outlets of the compression units is about 80° C. Such a gradual rise in temperature prevents the heat exchanger 15 from being subjected to a thermal shock that is too large.
  • the unit 12 can also cause the fans 41 to operate in such a manner as to blow the outside air downwards to contribute to drying the heat exchanger 17 .
  • the auxiliary compression unit 21 is used to extract heat from the outside environment.
  • the auxiliary compression unit 21 can be used to reinforce the main compression unit for the purpose of compressing the refrigerant gas coming from the refrigeration units R P .
  • the refrigeration installation includes a bypass circuit 50 connecting the main high-pressure circuit 4 to the auxiliary low-pressure circuit 20 via a cock 51 controlled by the unit 12 .
  • the auxiliary low-pressure circuit 20 Upstream from the junction with the bypass 50 , the auxiliary low-pressure circuit 20 also has a cock 52 controlled by the unit 12 .
  • the unit 12 causes the cock 52 to close and the cock 51 to open, and causes the auxiliary compression unit 21 to operate as a function of needs.
  • the power of said auxiliary compression unit is then available for refrigeration, the condenser 25 also being dimensioned to enable the heat extracted from the refrigeration units R P to be removed to the outside. It can thus be understood that the power of the condenser 25 is then greater than or equal to the power of the evaporator 18 .
  • the thermal power of the condensation tube circuit 25 may, for example, have a value lying in the range 1 times the absolute value of the thermal power of the evaporation tube circuit 18 to 5 times said absolute value.
  • This power ratio can be obtained by making the heat exchanger 17 of the exterior unit 15 in such a manner that the heat exchange surface area of the condensation tube circuit 25 represents in the range 50% of the sum of the heat exchange surface areas of the condensation and evaporation tube circuits 25 and 18 to 80% of said sum.
  • the cocks 45 and 47 are closed, and the condenser 25 is fed via a constant-pressure cock 53 controlled by the unit 12 .
  • the evaporator 18 is not fed with refrigerant fluid and the valve and the cock 19 are thus closed.
  • the capacity of the installation of the invention to operate either in combined mode or in purely refrigeration mode makes it possible to dimension the main and auxiliary compression units 10 and 21 with cumulative power just sufficient to guarantee optimum refrigeration in the summer period.
  • the term “the summer period” is used to mean a period during which the average daytime temperature is greater than 18° C.
  • the residual power available at the auxiliary compression unit 21 may advantageously be used, in the winter period, for operation as a heat pump for heating the premises.
  • the refrigeration unit only has main low-pressure and high-pressure refrigeration circuits that feed refrigeration units that operate within the same temperature ranges, either positive or negative.
  • a refrigeration installation of the invention can be required to feed both positive-temperature refrigeration units and also negative-temperature refrigeration units.
  • an installation of the invention may also have at least one secondary refrigeration unit R S comprising at least one evaporator disposed in a piece of furniture or in a refrigerated room fed with refrigerant fluid by a main high-pressure circuit 2 downstream from the tank 3 .
  • the evaporator of the secondary refrigeration unit R S is connected to a secondary low-pressure circuit 60 that feeds a secondary compression unit 61 sucking in the refrigerant fluid from the secondary low-pressure circuit 60 so as to deliver it into the main high-pressure circuit 2 .
  • the secondary compression unit 61 then comprises at least one and, in the example, two compressors 62 that are controlled by the control unit 12 . Operation of the refrigeration installation of the invention including such a secondary low-pressure circuit 60 and a secondary compression unit 61 is then substantially analogous to the operation described above as regards the combined and the purely refrigeration operating modes.
  • the refrigeration installation includes a liquid heat exchanger 63 connected firstly to the high-pressure circuit 2 in parallel with the heat exchangers 5 and secondly to a circuit 64 through which a heat transfer liquid flows.
  • the liquid heat exchanger 63 that is fed under the control of a valve 65 controlled by the control unit UC then makes it possible to heat the liquid in the circuit 64 .
  • the condenser 25 is placed on the main high-pressure circuit 2 in parallel with the heat exchangers 6 and/or 63 .
  • suction lines 67 and 68 controlled by valves 68 and 69 that are controlled by the unit 12 .
  • the suction lines 67 and 68 are also connected, via an expansion member 70 , to the main low-pressure circuit 4 immediately upstream from the main compression unit 10 .
  • This configuration makes it possible to reduce the quantity of refrigerant fluid used by the installation compared with installations in which no partial emptying of the liquid phase is possible.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
  • Defrosting Systems (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
US12/999,446 2008-07-03 2009-07-03 refrigeration installation for cooling at least one piece of furniture and/or a walk-in cooler, and for heating at least one room of premises, and an air heat exchanger for such an installation Abandoned US20110094250A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0854525 2008-07-03
FR0854525A FR2933484A1 (fr) 2008-07-03 2008-07-03 Procede de refrigeration d'au moins un meuble et/ou une chambre frigorifique et de chauffage d'au moins un local, installation et echangeur de chaleur pour sa mise en oeuvre
PCT/FR2009/051311 WO2010001071A2 (fr) 2008-07-03 2009-07-03 Installation de réfrigération d'au moins un meuble et/ou une chambre frigorifique et de chauffage d'au moins un local, et échangeur de chaleur à air pour cette installation

Publications (1)

Publication Number Publication Date
US20110094250A1 true US20110094250A1 (en) 2011-04-28

Family

ID=40292449

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/999,446 Abandoned US20110094250A1 (en) 2008-07-03 2009-07-03 refrigeration installation for cooling at least one piece of furniture and/or a walk-in cooler, and for heating at least one room of premises, and an air heat exchanger for such an installation

Country Status (7)

Country Link
US (1) US20110094250A1 (de)
EP (1) EP2310769B1 (de)
AT (1) ATE543059T1 (de)
DK (1) DK2310769T3 (de)
FR (1) FR2933484A1 (de)
PL (1) PL2310769T3 (de)
WO (1) WO2010001071A2 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11371761B2 (en) * 2020-04-13 2022-06-28 Haier Us Appliance Solutions, Inc. Method of operating an air conditioner unit based on airflow

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5042268A (en) * 1989-11-22 1991-08-27 Labrecque James C Refrigeration
US20040020230A1 (en) * 2001-07-02 2004-02-05 Osamu Kuwabara Heat pump
US20090120108A1 (en) * 2005-02-18 2009-05-14 Bernd Heinbokel Co2-refrigerant device with heat reclaim
US20090320504A1 (en) * 2005-06-23 2009-12-31 Carrier Corporation Method for Defrosting an Evaporator in a Refrigeration Circuit
US20100251738A1 (en) * 2007-08-28 2010-10-07 Masaaki Takegami Refrigeration apparatus
US20110048054A1 (en) * 2009-08-28 2011-03-03 Sanyo Electric Co., Ltd. Air conditioner

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2902585A1 (de) * 1979-01-24 1980-08-07 Costan Kuehlmoebel Gmbh Kaelteanlage
US4332137A (en) * 1979-10-22 1982-06-01 Carrier Corporation Heat exchange apparatus and method having two refrigeration circuits
JP4055449B2 (ja) * 2002-03-27 2008-03-05 三菱電機株式会社 熱交換器およびこれを用いた空気調和機
JP4650086B2 (ja) * 2005-04-28 2011-03-16 ダイキン工業株式会社 蓄熱熱回収装置
AT504135B1 (de) * 2006-11-13 2008-03-15 Arneg Kuehlmoebel Und Ladenein Verfahren zur wärmerückgewinnung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5042268A (en) * 1989-11-22 1991-08-27 Labrecque James C Refrigeration
US20040020230A1 (en) * 2001-07-02 2004-02-05 Osamu Kuwabara Heat pump
US20090120108A1 (en) * 2005-02-18 2009-05-14 Bernd Heinbokel Co2-refrigerant device with heat reclaim
US20090320504A1 (en) * 2005-06-23 2009-12-31 Carrier Corporation Method for Defrosting an Evaporator in a Refrigeration Circuit
US20100251738A1 (en) * 2007-08-28 2010-10-07 Masaaki Takegami Refrigeration apparatus
US20110048054A1 (en) * 2009-08-28 2011-03-03 Sanyo Electric Co., Ltd. Air conditioner

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11371761B2 (en) * 2020-04-13 2022-06-28 Haier Us Appliance Solutions, Inc. Method of operating an air conditioner unit based on airflow

Also Published As

Publication number Publication date
FR2933484A1 (fr) 2010-01-08
WO2010001071A3 (fr) 2010-04-08
DK2310769T3 (da) 2012-02-20
EP2310769A2 (de) 2011-04-20
EP2310769B1 (de) 2012-01-25
PL2310769T3 (pl) 2012-05-31
ATE543059T1 (de) 2012-02-15
WO2010001071A2 (fr) 2010-01-07

Similar Documents

Publication Publication Date Title
CN203177546U (zh) 热源型蒸发式冷凝器及蒸发冷热泵空调机组
US4502292A (en) Climatic control system
CN105020815B (zh) 一种蒸发冷凝式冷暖空调
CN103175349A (zh) 热源型蒸发式冷凝器及蒸发冷热泵空调机组
CN203785152U (zh) 一种蒸发冷凝式冷暖空调
CN108844265A (zh) 一种节能节水型热水喷淋除霜系统
CN108775663A (zh) 空气源热泵空调器用无风机且内置蓄热介质的室内换热器
CN106705203B (zh) 一种采用热泵和电热复合的户用热管散热装置
JP2005188924A (ja) ヒートポンプ装置
US20110094250A1 (en) refrigeration installation for cooling at least one piece of furniture and/or a walk-in cooler, and for heating at least one room of premises, and an air heat exchanger for such an installation
US20110209491A1 (en) Reversible system for recovering of heat energy by sampling and transfer of calories from one or more media into one or more other such media
CN105953485A (zh) 一种换热方法和系统及具有化霜功能的热泵系统
CN211424781U (zh) 一种热气融霜系统
CN113405274A (zh) 一种超低温风冷模块机系统
KR100937202B1 (ko) 건조기 및 냉동창고를 겸한 냉동기 유니트
KR101260198B1 (ko) 냉매의 잠열을 이용한 무적상 공기열 보일러
KR100452807B1 (ko) 폐열회수식 냉난방 겸용 공기조화기
CN208720413U (zh) 空气源热泵空调器用无风机且内置蓄热介质的室内换热器
CN1337552A (zh) 风冷热泵式空调器的防结冰装置
CN2436854Y (zh) 风冷热泵式空调器的防结冰装置
CN109931666A (zh) 一种蒸发冷凝式冷暖空调
CN203837339U (zh) 具有高效换热设计的热泵用翅片盘管
CN104154617B (zh) 无室外机家用空调器及其在冰箱上的应用
CN215216774U (zh) 一种减少结霜的空气源热泵换热单元和空调系统
EP1821050A2 (de) Kombiniertes Kühl- und Klimatisierungssystem

Legal Events

Date Code Title Description
AS Assignment

Owner name: 2F2C, FRANCE

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:GOURGOUILLAT, JEAN-MARC;REEL/FRAME:025512/0462

Effective date: 20101117

Owner name: 2F2C, FRANCE

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:GOUROUILLAT, JEAN-MARC;REEL/FRAME:025511/0856

Effective date: 20101120

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO PAY ISSUE FEE