EP2310769B1 - Einrichtung zum kühlen mindestens eines möbelstücks und/oder einer kältekammer und zum heizen mindestens eines raums und luftwärmetauscher für diese einrichtung - Google Patents

Einrichtung zum kühlen mindestens eines möbelstücks und/oder einer kältekammer und zum heizen mindestens eines raums und luftwärmetauscher für diese einrichtung Download PDF

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Publication number
EP2310769B1
EP2310769B1 EP09772753A EP09772753A EP2310769B1 EP 2310769 B1 EP2310769 B1 EP 2310769B1 EP 09772753 A EP09772753 A EP 09772753A EP 09772753 A EP09772753 A EP 09772753A EP 2310769 B1 EP2310769 B1 EP 2310769B1
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EP
European Patent Office
Prior art keywords
circuit
refrigeration
unit
pressure
heat exchanger
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Not-in-force
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EP09772753A
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English (en)
French (fr)
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EP2310769A2 (de
Inventor
Jean-Marc Gourgouillat
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2F2C
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2F2C
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Priority to PL09772753T priority Critical patent/PL2310769T3/pl
Publication of EP2310769A2 publication Critical patent/EP2310769A2/de
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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 refrigerating plants used to provide refrigeration of various products and in particular food products.
  • a refrigeration plant comprising high and low pressure refrigerant circuits connected to one or more refrigeration units such as a cabinet or a cabinet. refrigerated showcase or a cold room.
  • the refrigeration plant further comprises a compression unit which draws the refrigerant from the low pressure circuit and delivers it compressed into the high pressure circuit.
  • the installation further comprises, downstream of the compression unit, an external condenser at which the refrigerant is cooled before being redirected to the refrigeration unit or an intermediate storage tank.
  • Such an installation gives full satisfaction with regard to its preservation function at low setpoint temperatures of fragile products or foodstuffs.
  • the external dissipation of the heat extracted at the refrigeration units and resulting from the work of the compression group constitutes a dry energy loss which, taking into account the energy costs and the requirements of sustainable development, is not satisfactory.
  • a demand EP 0 431 797 proposed to adapt, in a fan heater, a condensation circuit supplied with high-pressure gas refrigerant so as to recover the heat for heating premises.
  • the installation proposed by the request EP 0 431 797 born It does not provide enough heat to ensure adequate heating in winter alone.
  • a demand EP 1 921 401 then proposed a refrigeration plant whose heat extracted is recovered for heating a heat accumulator which is in connection with a central heating water circuit and / or a hot water circuit.
  • Installation, according to demand EP 1 921 401 furthermore includes an external evaporator which allows, during the winter period, to take outside the additional heat necessary to satisfy the heating needs.
  • the heat extracted by the installation according to EP 1 921 401 is evacuated for the most part at an external condenser completely independent of the external evaporator.
  • this installation provides for a defrosting of the external evaporator by cycle inversion, which also affects the performance of the installation in that the design of the outdoor evaporator must then result from a compromise between its operating modes. in evaporator and condenser.
  • the demand EP 1 921 401 plans to place the indoor heat exchanger for series heating with the external condenser and upstream of the latter, which penalizes the energy efficiency of the installation and requires the implementation of a large amount of liquid refrigerant to fill the circuit downstream of the heat exchanger when the refrigerant is completely condensed in the latter.
  • EP 1921401 presents an installation according to the preamble of claim 1.
  • the invention relates to a refrigerant refrigeration plant having the features of claim 1.
  • Such a refrigeration plant according to the invention is particularly suitable for cooling the refrigeration units and for heating a room with the heat recovered at the refrigeration units and resulting from the compression of the refrigeration unit.
  • Refrigerant In this regard, the implementation of an auxiliary compression group allows, when the heat recovered at the refrigeration units is not sufficient to heat the room satisfactorily, to take out the missing heat and necessary to reach the satisfactory heating level.
  • the exchanger of each air conditioning unit can be of any suitable nature.
  • the exchanger of each air conditioning unit, or of certain units only can be an exchanger for heating a heat transfer liquid, such as for example but not exclusively, the water of a heating circuit, or sanitary water.
  • the exchanger of each air conditioning unit, or some units only can also be an air heat exchanger also called air heater.
  • air heat exchanger also called air heater.
  • the use of such an air exchanger has the advantage of directly heating the air without the use of an intermediate heat transfer fluid and makes it possible to have optimum efficiency and to simplify the implementation and the operation of the refrigeration plant according to the invention.
  • the installation according to the invention is also likely to implement several air conditioning units having different types of exchangers.
  • the high and low pressure circuits can comprise a main high pressure circuit, a secondary high pressure circuit and a main low pressure circuit.
  • the evaporator of the air conditioning unit will then be supplied with refrigerant by the main high pressure circuit via a pressure reducer and connected to the main low pressure circuit.
  • the evaporation circuit of the outdoor unit will be fed by the main high pressure circuit via a holder and connected to an auxiliary low pressure circuit while the condensation circuit of the outdoor unit is connected to the main high pressure circuit upstream of the evaporators.
  • the main compression unit will draw the refrigerant from the main low pressure circuit and drive the compressed refrigerant back into the main high pressure circuit while the auxiliary compression unit draws the refrigerant from the auxiliary low pressure circuit and delivers the compressed refrigerant into the compressor.
  • main high pressure circuit The main compression unit will draw the refrigerant from the main low pressure circuit and drive the compressed refrigerant back into the main high pressure circuit while the auxiliary compression unit draws the refrigerant from the auxiliary low pressure circuit and delivers the compressed refrigerant into the compressor. main high pressure circuit.
  • control unit is adapted to switch from the mixed mode of operation to the mode of operation of pure refrigeration and vice versa depending on refrigeration needs.
  • the installation comprises defrosting means of the exchanger of the outdoor unit adapted to ensure, in the context of the mixed mode operation of the installation, the temporary supply of the condensation circuit of the outdoor unit.
  • de-icing means makes it possible to preserve the efficiency of the external heat exchanger, especially when the latter is used as a source of heat in the winter period.
  • the use of the condensation circuit, designed to withstand high pressures, of the refrigerant makes it possible to avoid resorting to a cycle reversal defrosting at the level of the evaporation circuit, which has the advantage, on the one hand, of not having to size the evaporation circuit for high pressures, on the other hand, to avoid subjecting the evaporation circuit to thermal shock resulting from a rapid transition from a negative temperature to a positive temperature, by for example, more than 30 ° and, moreover, to avoid the risks of suction of liquid during the restart in heat pump.
  • the fins connecting the condensation and evaporation circuits dampen the differences in expansion between the condensation and evaporation circuits during deicing phases, thus reducing the mechanical stresses experienced by these circuits.
  • the invention makes it possible, by separating the evaporation and condensation circuits of the outdoor unit, to optimize their dimensioning for their nominal operating speed with correct pressure losses, controlled fluid velocities allowing a good oil return which contributes to the performance of the entire refrigeration
  • the detection of frost can be carried out in different ways, for example by monitoring the load of a forced ventilation motor of the exchanger to deduce from the increase in the engine load an appearance of frost on the exchanger.
  • the frost evaluation means comprise means for measuring the humidity of the air entering and leaving the exchanger.
  • control unit is adapted to control a reversal of the operating direction of a extractor fan equipping the external exchanger at the end of defrosting thereof. This inversion of rotation makes it possible to obtain optimal drying of the exchanger of the outdoor unit.
  • the implementation of the secondary compression group discharging the compressed refrigerant in the same high-pressure main circuit as the other compression groups makes it possible to use all of the thermal energy recovered by the set of compression groups to ensure heating the premises where the unit heaters are located.
  • the auxiliary compression group power is not sufficient to ensure the cooling of the room under summer outdoor temperature conditions.
  • At least one heater of the air conditioning unit is adapted to be reversible and operate as a condenser or evaporator, and the installation comprises means for supplying refrigerant each unit heater operating as an evaporator .
  • the auxiliary compression group has sufficient power to ensure the cooling of the room with a summer outdoor temperature.
  • This exchanger of the installation according to the invention has the advantage of having a separate evaporation circuit of the condensation circuit so that each of these circuits is perfectly sized to optimally ensure its function as a condenser or evaporator unlike a heat exchanger whose circuit would be adapted to have a mixed operation either in condenser or in evaporator.
  • the design of the exchanger according to the invention therefore allows it to obtain optimum energy efficiency.
  • the use of vanes common to the evaporation and condensation circuits makes it possible to optimize the heat exchange during the defrosting phase, the duration of which can then be shortened compared to the defrosting time in the context of a defrosting mode. construction that would consist of simply juxtapose one above the other a condenser and an evaporator.
  • the fins provide mechanical damping of the differential expansion phenomena during the defrosting phases.
  • the thermal power of the tubular condensation circuit has a value of between 1 and 5 times the absolute value of the thermal power of the evaporation tubular circuit.
  • the exchange surface of the tubular condensation circuit has between 50% and 80% of the sum of the exchange surfaces of the condensation and evaporation tubular circuits.
  • the condensation and evaporation circuits comprise loops or sheets of tubes and certain loops or layers of the evaporation circuit are superimposed and interposed between loops or layers of the condensation circuit. .
  • the fins have a substantially vertical orientation.
  • the condensation circuit comprises at least one tube ply which forms the first ply of tube starting from the bottom of the exchanger.
  • This first sheet of tube advantageously forms a surface on which a portion of the water present in the air will condense or settle, thereby reducing the charge of the air circulating in the exchanger and thus reducing the speed of Frost appears on the evaporation circuit.
  • a refrigeration plant according to the invention as illustrated in FIG. figure 1 and designated generally by reference 1, comprises a main high-pressure circuit 2 refrigerant on which is disposed a high-pressure reservoir 3 from which extends a branch 2 a supply refrigerant at high pressure minus one and usually several main refrigeration units R p .
  • a refrigeration unit R p comprises at least one evaporator disposed in a piece of furniture or a refrigerating chamber. This evaporator is then supplied with refrigerant liquid by the main high pressure circuit 2a via an expander. The evaporator is furthermore connected to a main low-pressure circuit 4.
  • the refrigerating installation 1 also comprises at least one or according to the example illustrated three air conditioning units 5 arranged inside one or more premises.
  • each air conditioning unit comprises at least one air exchanger or air heater equipped with at least one condenser 6 which is connected to the main high pressure circuit 2 upstream of the evaporators of the refrigeration units Rp and, according to the example illustrated, also upstream of the tank 3 of high pressure refrigerant.
  • the installation 1 further comprises a main compression unit 10 which sucks the refrigerant from the main low pressure circuit 4 to discharge it compressed into the main high pressure circuit 2 upstream of the condensers 6, the high pressure reservoir 3 and, of course , evaporators that it feeds.
  • the main compression unit 10 comprises at least one and, according to the illustrated example, three compressors 11 connected in parallel to the high pressure 2 and low pressure circuits 4. The operation of the compression unit 10 is then controlled by a control unit 12.
  • the refrigeration system operates in the following manner.
  • Each main refrigeration unit Rp is provided with a self-regulating device, it controls the opening of a valve supplying its evaporator high pressure refrigerant via a regulator as necessary to maintain a set temperature within it.
  • the operation of the refrigeration unit induces a pressure increase in the main low pressure circuit 4 that the control unit 12 detects to trigger the operation of the main compression unit 10 which then sucks the low pressure refrigerant into a gaseous state low pressure to discharge it in the gaseous state high pressure in the main high pressure circuit 2.
  • the refrigerant is within the main high pressure circuit 2 in the gaseous state and at a high temperature of
  • the invention proposes to use the heat of the high-pressure gas refrigerant to heat one or more rooms by means of the air heaters 5 whose condensers 6 are fed by valves. 13 controlled by the control unit 12.
  • the air heaters 5 whose condensers 6 are fed by valves. 13 controlled by the control unit 12.
  • the refrigerant will be in the high pressure liquid state.
  • the heat recovered at the refrigeration units can, in some cases especially in winter, not be sufficient to heat the premises to an acceptable or even comfortable setpoint temperature.
  • Winter period means a period during which the average outdoor temperature is below 18 ° C.
  • the invention then proposes to take away the heat or missing calories.
  • an outdoor unit 15 comprising at least one heat exchanger 17 which comprises an evaporation circuit 18 connected to the main high pressure circuit 2 via a pressure reducer 19.
  • the evaporation circuit 18 is also connected to an auxiliary low-pressure circuit 20 which supplies an auxiliary compression unit 21.
  • the auxiliary compression unit 21 comprises at least one and, according to the illustrated example, two compressors 22 which are connected in parallel to the auxiliary low-pressure circuit 20 and to the circuit 2.
  • the auxiliary compression unit 20 then draws via the auxiliary low-pressure circuit 20 the refrigerant in the gaseous state from the evaporator 18 of the exchanger 17 to compress it and pump it back into the main circuit 2.
  • the auxiliary compression group 20 is then driven by the unit of controls 12 which modulates the operation of one or both compressors 22 as needed.
  • the auxiliary compression unit 21 and the external heat exchanger 5 operate in a heat pump and take the external heat necessary to maintain the set temperature in the rooms by means of the air conditioning units 5.
  • the refrigeration system according to the invention allows to ensure alone, in a mixed operating mode refrigeration / heat pump, on the one hand the cooling of the refrigeration units and, on the other hand, the heating of the premises. Such a mixed mode of operation therefore allows for significant energy savings for space heating.
  • the evaporator 16 Insofar as the temperature at the surface of the evaporator 18 is negative in view of the expansion of the refrigerant within it, after a certain operating time, the evaporator 16 will be covered with frost resulting from the condensation and the freezing of the water present in the external atmosphere. It is therefore necessary to ensure defrosting of the condenser 18 on a regular basis.
  • the invention proposes to carry out this defrosting by using the heat of the refrigerant compressed at the outlet of the compression groups.
  • the invention proposes to associate a condenser 25 to the evaporator 18.
  • the condenser 25 supplied with high pressure refrigerant gas by the main high pressure circuit 2 by being connected thereto, on the one hand, downstream of the groups of compression and, on the other hand, upstream of the tank 3 and the evaporators of the main refrigeration units Rp.
  • the evaporator 18 comprises a tubular circuit 30 for evaporation of the refrigerant formed by tube plies 32 comprising rectilinear main tubes as more particularly shown in FIG. figure 2 .
  • the condenser 25 comprises a tubular circuit for condensing the fluid refrigerant which consists of webs 35 of tubes 36 having rectilinear main tubes as shown in FIG. figure 2 .
  • the tubular circuits 30 and 35 are then interconnected by thermally conductive fins 40 which have, according to the example shown, a substantially vertical orientation.
  • the thermal conduction link provided by the fins 40 which are common to the evaporation and condensation circuits 35 guarantees a very high efficiency of the defrosting.
  • the tube plies of the condensation and evaporation circuits are superimposed and interposed between each other.
  • the first ply of the exchanger 17 from the bottom is formed by tubes of the condensation circuit so as to form a condensation surface of the water vapor present in the air during Of the operation of the outdoor unit 15.
  • the exchanger 17 is located inside a chassis frame 41 equipped in the upper part of at least one and, according to the illustrated example, two fans 43 forcing the circulation of air inside the outdoor unit 15.
  • the rectilinear parts of the tubes and the fins may be inclined relative to the horizontal respectively the vertical of an angle a of a few degrees, for example from 3 ° to 5 °. This inclination can be obtained by the inclination of the entire chassis.
  • the installation may include a branch 55 connecting the outlet of the auxiliary compression unit 21 upstream of the suction of the main compression unit 10 via a constant pressure valve 56 controlled by the unit 12.
  • the condenser 25 is used regularly to defrost the evaporator 18. This regular operation can be provided according to a predefined time interval regardless of the possible occurrence of frost on the evaporator 18 or on the contrary depending on the needs in case of actual appearance of frost or the forecast of the appearance of frost.
  • the refrigerating plant 1 can implement means for evaluating the ice.
  • frost evaluation means may be formed in any suitable manner.
  • the frost evaluation means may comprise means 45 for monitoring the load of the fans 43 which, when the latter exceeds a predetermined threshold, deduce the appearance of frost. Indeed, the frost being deposited on the tubes 30 and the fins 40 will progressively obstruct the exchanger 17 making it more difficult the circulation of air so that the load of the fans 43 increases.
  • the frost detection means may also include a system that measures the hydrometry of the inlet and outlet air of the outdoor unit 15 to deduce the possible occurrence of frost.
  • the frost evaluation means may also include a system for measuring the hydrometry and the outside air temperature, depending on the latter, predicting the appearance of frost.
  • the frost evaluation means are connected to the control unit 12 which, when necessary, triggers a defrost cycle.
  • the unit 12 controls the supply of the condenser 25 in high pressure refrigerant hot.
  • This supply is provided by a branch of the main high pressure circuit 2 controlled by a valve 46 controlled by the unit 12.
  • the valve 46 then allows admission into the supply circuit of the condenser 25 of high pressure refrigerant gas directly compression groups 10 and 21.
  • it can also be provided a bypass line 47 for sampling high pressure refrigerant downstream of the tank 3. This The bypass 47 is then controlled by a valve 48 controlled by the unit 12.
  • the control valves 46 and 48 then ensures a mixture between high pressure gas from the compression groups and the high pressure fluid from the reservoir 3 to modulate the temperature of the fluid within the condenser 25 to bring the condenser and fins progressively from a negative temperature to a temperature positive higher but lower than the temperature of the refrigerant gas compressed at the output of the compression groups.
  • the unit 12 can maintain the temperature of the refrigerant supplying the condenser 25 to values of the order of 40 ° to 60 ° while the maximum temperature at the output of the compression groups is of the order of 80 ° C. Such a gradual rise in temperature avoids subjecting the exchanger 15 too much heat shock.
  • the unit 12 can also control the operation of the fans 41 so as to blow down the outside air to contribute to the drying of the exchanger 17.
  • the auxiliary compression unit 21 is used to extract heat from the outside environment.
  • the auxiliary compression group 21 can be used in reinforcement of the main compression group to compress the refrigerant gas from the refrigeration units Rp.
  • the refrigeration plant comprises a bypass circuit 50 connecting the main low pressure circuit 4 to the auxiliary low pressure circuit 20 via a controlled valve 51 by the unit 12.
  • the auxiliary low pressure circuit 20 also comprises upstream of the junction with the bypass 50 a controlled valve 52 by the unit 12.
  • the unit 12 controls the closing of the valve 52 and the opening of the valve 51 as well as the operation of the auxiliary compression group 21 in function needs.
  • the power of the latter will then be available for refrigeration, the condenser 25 being further dimensioned to allow external evacuation of the heat extracted at the refrigeration units Rp. It will therefore 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 tubular circuit 25 may for example have a value of between 1 to 5 times the absolute value of the thermal power of the evaporation tubular circuit 18 This power ratio can be obtained by producing the exchanger 17 of the outdoor unit 15 so that the exchange surface of the condensation tubular circuit 25 has between 50% and 80% of the sum of the exchange surfaces of the tubular condensation and evaporation circuits 18.
  • the valves 45 and 47 will be closed and the supply of the condenser 25 will be provided by a valve 53 at constant pressure controlled by the unit 12.
  • the evaporator 18 will not be supplied with refrigerant and the valve and the valve 19 will be closed.
  • the ability of the installation according to the invention to operate in mixed mode or in pure refrigeration mode allows to size the main compression group 10 and auxiliary 21 with a cumulative power just sufficient to ensure optimal refrigeration in summer. Summer is defined as a period during which the average daytime temperature is above 18 ° C. Since, in winter, the power required to ensure adequate refrigeration is lower than that required during the summer period, the residual power available at the auxiliary compression group 21 may advantageously be used, in winter, for a cooling operation. heat pump for space heating.
  • the refrigeration unit comprises only low and high pressure main circuits which supply refrigeration units operating in the same temperature ranges, either positive or negative.
  • a refrigeration plant according to the invention may have to supply positive temperature refrigeration units and negative temperature refrigeration units.
  • an installation according to the invention may also comprise at least one secondary refrigerating unit R s comprising at least one evaporator disposed in a refrigerated unit or refrigerated room supplied by the main high pressure circuit 2 downstream of the tank 3.
  • L The evaporator of the secondary refrigeration unit R s is connected to a secondary low pressure circuit 60 which supplies a secondary pressure group 61 drawing the refrigerant from the secondary low pressure circuit 60 to discharge into the main high pressure circuit 2.
  • the group secondary compression device 61 then comprises at least and, according to the example, two compressors 62 which are controlled by the control unit 12.
  • the operation of the refrigeration plant according to the invention comprising such a secondary low pressure circuit 60 and a secondary compression group 61 is then substantially similar to that described previously with regard to the modes of mixed operation and pure refrigeration.
  • the refrigeration plant comprises a liquid exchanger 63 connected on the one hand to the high-pressure circuit 2 in parallel with the exchangers 5 and on the other hand to a circuit 64 for circulating a heat-transfer liquid.
  • the liquid exchanger 63 whose supply is controlled by a valve 65 controlled by the control unit UC, then allows heating of the liquid of the circuit 64.
  • the condenser 25 is placed on the main high pressure circuit 2 in parallel with the exchangers 6 and / or 63.
  • suction lines 67 and 68 controlled by valves 68 and 69 controlled by the unit 12.
  • the suction lines 67 and 68 are further connected, via an expansion member 70, the main low pressure circuit 4 just upstream of the main compression group 10. This arrangement reduces the amount of refrigerant implemented by the installation compared to facilities where no partial emptying of the liquid phase is possible.

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  • 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)

Claims (11)

  1. Kühleinrichtung mit Kühlfluid, umfassend mindestens:
    - Hochdruckschaltungen (2) und Niederdruckschaltungen (4),
    - eine Kühleinheit (Rp) mit mindestens einem in einem Möbelstück oder einer Kältekammer angeordneten und an die Hoch- und Niederdruckschaltungen (2, 4) angeschlossenen Verdampfer,
    - eine Belüftungseinheit (5) mit mindestens einem im Inneren eines Raums angeordneten und mindestens einen Kondensator (6) aufweisenden Wärmetauscher, der an die Hoch- und Niederdruckschaltungen (2, 4) angeschlossen ist,
    - eine externe Einheit (15) mit mindestens einem außen angeordneten und eine röhrenförmige Kondensationsschaltung (25, 35) aufweisenden Luftwärmetauscher (17), die an die Hoch- und Niederdruckschaltungen (2, 4) angeschlossen ist,
    - eine an die Hoch- und Niederdruckschaltungen (2, 4) angeschlossene Hauptkompressionsgruppe (10),
    - eine an die Hoch- und Niederdruckschaltungen (2, 4) angeschlossene Nebenkompressionsgruppe (21),
    - eine die die Funktion der Kühleinrichtung steuernde Steuereinheit (12),
    dadurch gekennzeichnet, dass:
    - der mindestens eine Luftwärmetauscher der externen Einheit (15) folgendes umfasst:
    ■ eine röhrenförmige Verdampferschaltung (18, 30), vorgesehen zum Speisen nur mit Niederdruckkühlfluid und zum Anschließen an die Nieder- und Hochdruckschaltungen,
    ■ Wärme leitende Rippen (40), die den röhrenförmigen Verdampfungsschaltung (18, 30) und die röhrenförmige Kondensationsschaltung (25, 35) verbinden, wobei sie mit den röhrenförmigen Verdampfungs- und Kondensationsschaltungen fest verbunden sind,
    ■ wobei de röhrenförmige Kondensationsschaltung (25, 35) dazu vorgesehen ist, nur mit Hochdruckkühlfluid gespeist zu werden, und derart dimensioniert ist, dass sie die gesamte Wärme, die im Bereich jeder Kühleinheit von der Aufrechterhaltung der Solltemperaturen stammt, wenn außen sommerliche Temperaturen herrschen, verbreitet,
    - wobei die Steuereinheit (12) dazu vorgesehen ist, die Einrichtung in folgende Modi zu bringen:
    ■ entweder in einen reinen Kühlfunktionsmodus, in dem die Leistung aller Kompressionsgruppen für den Entzug der Wärme nur im Bereich jeder Kühleinheit verfügbar ist,
    ■ oder in einen gemischten Kühl-/Wärmepumpenmodus, in dem die Leistung der Hilfskompressionsgruppe für den Entzug der Wärme im Bereich der externen Einheit verfügbar ist, und die Leistung jeder weiteren Kompressionsgruppe für den Entzug der Wärme im Bereich jeder Kühleinheit verfügbar ist,
    - wobei die Kompressionsgruppen derart dimensioniert sind, dass ihre kumulierten Leistungen ausreichen, um im Bereich jeder Kühleinheit die Solltemperaturen aufrecht zu erhalten, wenn außen sommerliche Temperaturen herrschen, und sich die Einrichtung im reinen Kühlmodus befindet.
  2. Kühleinrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die Steuereinheit (12) dazu vorgesehen ist, vom gemischten Funktionsmodus in den reinen Kühlmodus und umgekehrt in Abhängigkeit von den Kühlbedürfnissen überzugehen.
  3. Kühleinrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Steuereinheit dazu vorgesehen ist, im gemischten Funktionsmodus die Versorgung der Kondensationsschaltung (25, 35) der externen Einheit :(15) zu steuern, um eine Enteisung der externen Einheit (15) zu gewährleisten.
  4. Kühleinrichtung nach Anspruch 3, dadurch gekennzeichnet, dass sie Mittel zur Bewertung der Vereisung auf dem mindestens einen Wärmetauscher umfasst, und dass die Steuereinheit (12) dazu vorgesehen ist, die Versorgung der Kondensationsschaltung (25, 35) zu steuern, wenn die Vereisung auf dem mindestens einen Wärmetauscher eine gewisse Schwelle überschreitet.
  5. Kühleinrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass sie folgendes umfasst:
    - eine Nebenniederdruckschaltung (60) für ein Kühlfluid,
    - eine Nebenkühleinheit (Rp) mit mindestens einem in einem Möbelstück oder einer Kältekammer angeordneten und an die Hoch- und Niederdruckschaltungen (2, 4) angeschlossenen Verdampfer,
    - eine Nebenkompressionsgruppe (61), die das Kühlfluid aus der Nebenniederdruckschaltung (60) ansaugt und das komprimierte Kühlfluid in die Hochdruckschaltung (2) befördert,
    und dass die Steuereinheit (12) dazu vorgesehen ist, die Funktion der Nebenkompressionsgruppe zu steuern.
  6. Kühleinrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Absolutwert der Wärmeleistung der röhrenförmigen Schaltung des mindestens einen Luftwärmetauschers größer oder gleich dem Absolutwert der Wärmeleistung der röhrenförmigen Verdampfungsschaltung des mindestens einen Luftwärmetauschers ist.
  7. Kühleinrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass die Wärmeleistung der röhrenförmigen Kondensationsschaltung des mindestens einen Luftwärmetauschers einen Wert zwischen 1 bis 5-mal den Absolutwert der Wärmeleistung der röhrenförmigen Verdampfungsschaltung des mindestens einen Luftwärmetauschers besitzt.
  8. Kühleinrichtung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die Austauschfläche der röhrenförmigen Kondensationsschaltung des mindestens einen Luftwärmetauschers zwischen 50% und 80% der Summe der Austauschflächen der röhrenförmigen Kondensations- und Vordampfungsschaltungen beträgt.
  9. Kühleinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Kondensations- (25, 35) und Verdampfungsschaltungen (18, 30) Schleifen oder Lagen von Rohren umfassen, und dass gewisse Schleifen oder Lagen der Verdampfungsschaltung (18, 30) übereinander und zwischen Schleifen oder Lagen der Kondensationsschaltung (25, 35) angeordnet sind.
  10. Kühleinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Rippen (40) eine im Wesentlichen vertikale Ausrichtung aufweisen.
  11. Kühleinrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Kondensationsschaltung (25, 35) mindestens eine Rohrschicht umfasst, die ausgehend vom unteren Bereich des mindesiens einen Luftwärmetauschers die erste Rohrschicht der externen Einheit (15) bildet.
EP09772753A 2008-07-03 2009-07-03 Einrichtung zum kühlen mindestens eines möbelstücks und/oder einer kältekammer und zum heizen mindestens eines raums und luftwärmetauscher für diese einrichtung Not-in-force EP2310769B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL09772753T PL2310769T3 (pl) 2008-07-03 2009-07-03 Instalacja do chłodzenia co najmniej jednej szafy i/lub komory chłodniczej i do ogrzewania co najmniej jednego pomieszczenia, i powietrzny wymiennik ciepła do tej instalacji

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
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 (2)

Publication Number Publication Date
EP2310769A2 EP2310769A2 (de) 2011-04-20
EP2310769B1 true EP2310769B1 (de) 2012-01-25

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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)

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* 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

Family Cites Families (11)

* 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
US5042268A (en) * 1989-11-22 1991-08-27 Labrecque James C Refrigeration
EP1403598B1 (de) * 2001-07-02 2008-12-24 Sanyo Electric Co., Ltd. Wärmepumpe
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
WO2006087011A1 (en) * 2005-02-18 2006-08-24 Carrier Corporation Co2-refrigeration device with heat reclaim
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
WO2007001284A1 (en) * 2005-06-23 2007-01-04 Carrier Corporation Method for defrosting an evaporator in a refrigeration circuit
AT504135B1 (de) * 2006-11-13 2008-03-15 Arneg Kuehlmoebel Und Ladenein Verfahren zur wärmerückgewinnung
WO2009028193A1 (ja) * 2007-08-28 2009-03-05 Daikin Industries, Ltd. 冷凍装置
EP3273184A1 (de) * 2009-08-28 2018-01-24 Sanyo Electric Co., Ltd. Klimaanlage

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
US20110094250A1 (en) 2011-04-28
PL2310769T3 (pl) 2012-05-31
ATE543059T1 (de) 2012-02-15
WO2010001071A2 (fr) 2010-01-07

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