EP2310769A2 - Facility for cooling at least one item of furniture and/or a refrigerating chamber and for heating at least one room, and air heat exchanger for this facility - Google Patents

Facility for cooling at least one item of furniture and/or a refrigerating chamber and for heating at least one room, and air heat exchanger for this facility

Info

Publication number
EP2310769A2
EP2310769A2 EP09772753A EP09772753A EP2310769A2 EP 2310769 A2 EP2310769 A2 EP 2310769A2 EP 09772753 A EP09772753 A EP 09772753A EP 09772753 A EP09772753 A EP 09772753A EP 2310769 A2 EP2310769 A2 EP 2310769A2
Authority
EP
European Patent Office
Prior art keywords
circuit
tubular
refrigeration
condensation
evaporation
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.)
Granted
Application number
EP09772753A
Other languages
German (de)
French (fr)
Other versions
EP2310769B1 (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
Priority to PL09772753T priority Critical patent/PL2310769T3/en
Publication of EP2310769A2 publication Critical patent/EP2310769A2/en
Application granted granted Critical
Publication of EP2310769B1 publication Critical patent/EP2310769B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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 system 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.
  • an application EP 0 431 797 proposed to adapt, in a heater, a condensation circuit fed with high-pressure gas refrigerant so as to recover the heat for heating premises .
  • the installation proposed by the application EP 0 431 797 does not It does not provide enough heat to ensure adequate heating in winter alone.
  • An application EP 1 921 401 then proposed a refrigeration plant whose extracted heat is recovered for heating a heat accumulator which is in connection with a central heating water circuit and / or a hot water circuit. health.
  • the installation, according to the application EP 1 921 401 furthermore comprises an external evaporator which makes it possible, during the winter period, to take outside the additional heat necessary to satisfy the heating requirements.
  • the heat extracted by the installation according to EP 1 921 401 is largely discharged at an external condenser completely independent of the external evaporator.
  • this installation makes it possible to obtain additional heat under satisfactory conditions through heat pump operation, it nevertheless has the drawback of not offering sufficient power to cover the heating requirements of the premises so that it is provided complementary electric heating means which penalizes the environmental performance of the installation.
  • 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 application EP 1 921 401 provides for placing the indoor heat exchanger for heating in series 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 fully condensed therein.
  • a new type of refrigeration plant that allows, on the one hand, to recover at least a portion of the heat available in the refrigerant for heating premises and, on the other hand, to possibly supplement this heat input in economically and ecologically satisfactory conditions and which has, moreover, equivalent electrical power absorbed performance superior to those known refrigeration installations and lower maintenance costs.
  • the invention relates to a refrigerant refrigerant installation comprising at least:
  • a refrigeration unit comprising at least one evaporator arranged in a cabinet or a refrigerating chamber and connected to the high and low pressure circuits,
  • an air conditioning unit comprising at least one exchanger which is arranged inside a room and which comprises at least one condenser connected to the high and low pressure circuits,
  • an outdoor unit comprising at least one air exchanger which is arranged outside and which comprises a condensation circuit connected to the high and low pressure circuits,
  • control unit that controls at least the operation of the installation.
  • the refrigerating unit is characterized in that:
  • the air exchanger of the outdoor unit comprises: a tubular evaporation circuit adapted to be fed only with low pressure refrigerant and connected to the high and low pressure circuits,
  • thermally conductive fins connecting the tubular evaporation circuit and the tubular condensation circuit being integral with the tubular evaporation and condensation circuits, the tubular condensation circuit being adapted to be fed only with high pressure refrigerant and sized to dissipate all the heat resulting from the maintenance, at each refrigeration unit, of the set temperatures when outside a summer temperature,
  • control unit is adapted to place the installation:
  • the compression units are dimensioned so that their cumulative powers are sufficient to maintain, at each refrigeration unit, the set temperatures when outside a summer temperature and the installation is in pure refrigeration mode .
  • 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.
  • the implementation of such an air exchanger has the advantage of directly heating the air without implementation of an intermediate heat transfer fluid and provides optimal performance and 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. 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.
  • the installation may also include a controlled isolation valve for opening or closing the communication between the auxiliary low-pressure circuit and the evaporation circuit of the external exchanger, as well as a branch circuit which connects the main low-pressure circuit. to the secondary low pressure circuit and which is equipped with a controlled bypass valve to open or close the bypass circuit.
  • the control unit is then adapted to:
  • 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 installation comprises:
  • the control unit is adapted to control the opening of a valve supply of the condensation circuit when the frost on the exchanger exceeds a certain threshold.
  • 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 plant can be adapted to activities requiring several levels of cold such as, for example, activities where it is necessary to keep fresh products at positive temperatures as well as products frozen at negative temperatures.
  • the refrigeration plant according to the invention then comprises:
  • a secondary refrigeration unit comprising at least one evaporator arranged in a piece of furniture or a cold room and supplied with refrigerant by the main high pressure circuit via a pressure reducer and connected to the secondary low pressure circuit,
  • a secondary compression group which sucks the refrigerant from the secondary low pressure circuit and which discharges the compressed refrigerant into the main high pressure circuit, the control unit being adapted to control the operation of the secondary compression group.
  • 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 all the 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.
  • the invention also relates to an air exchanger for a refrigeration plant according to the invention, this air exchanger comprises:
  • tubular condensation circuit adapted to be fed only with high-pressure refrigerant
  • tubular evaporation circuit adapted to be fed only with low pressure refrigerant
  • the condensation circuit has a sufficient exchange power to ensure heat dissipation in the summer period, that is to say that the absolute value of the thermal power of the tubular condensation circuit is greater than or equal to to the absolute value of the thermal power of the evaporation tubular circuit.
  • the exchanger according to the invention has the advantage of having an evaporation circuit separate from the condensation circuit so that each of these circuits is perfectly sized to optimally ensure its function of condenser or evaporator at the difference of 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 exchanges 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 evapo ration tubular circuits.
  • the condensation circuit under normal conditions of use the condensation circuit is located at least partly below the evaporation circuit. This arrangement makes it possible to take advantage of the convection phenomena to accelerate the defrosting of the evaporation circuit.
  • 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 evaporation and condensation circuits have rectilinear main tubes which are inclined by a few degrees with respect to the horizontal, which favors the runoff of the water.
  • 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.
  • the heat exchanger comprises at least one electric fan ensuring a forced circulation of air in the exchanger.
  • the various features, variants, shapes and embodiments of the plant and / or the exchanger can be associated with each other in various combinations to the extent that they are not incompatible or exclusive of each other. .
  • Figure 1 is a schematic view of a refrigeration plant according to the invention.
  • FIG. 2 is a longitudinal section of a heat exchanger according to the invention that can be implemented as part of the installation illustrated in FIG.
  • FIG. 3 is a cross-section of the exchanger along line III-III of FIG. 2.
  • FIG 4 is a schematic view of another embodiment of a refrigeration plant according to the invention.
  • a refrigeration plant according to the invention as illustrated in Figure 1 and generally designated by the reference 1, comprises a main high pressure circuit 2 of refrigerant on which is disposed a high pressure tank 3 from which extends a branch 2 a high pressure refrigerant fluid supply of at least one and usually several main refrigeration units R p.
  • Such a refrigeration unit R p comprises at least one evaporator disposed in a piece of furniture or a refrigerating chamber.
  • 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 R p and, according to illustrated example, 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 R p 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 within it a set temperature .
  • 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 is implemented 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 compression and, secondly, upstream of the tank 3 and the evaporators of the main refrigeration units R p .
  • the evaporator 18 comprises a tubular circuit 30 for evaporating the refrigerant formed by tube plies 32 comprising rectilinear main tubes, as shown more particularly in FIG. 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 Figure 2.
  • the tubular circuits 30 and 35 are then interconnected by thermally conductive fins 40 which have, according to the illustrated example, 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 sheets 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 angle ⁇ 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. During such a defrosting 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.
  • a bypass line 47 for sampling high pressure refrigerant downstream of the tank 3.
  • 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 0 C. such a gradual rise of the temperature avoids subjecting the exchanger 15 an excessive thermal 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 may be used in reinforcement of the main compression group to compress the refrigerant gas from refrigeration units R p .
  • the refrigeration system 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 comprises also upstream of the junction with the bypass 50 a valve 52 controlled by the unit 12.
  • the unit 12 controls the closing of the valve 52 and the opening of the valve 51 and the operation of the auxiliary compression group 21 as needed.
  • 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 R p .
  • 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 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 condensation and evaporation tubular 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 operation in winter. 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 refrigeration unit R s comprising at least one evaporator disposed in a cabinet or a refrigerated premises supplied with refrigerant by the high circuit main pressure 2 downstream of the tank 3.
  • 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 in the main high pressure circuit 2.
  • the secondary compression group 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 refrigerating installation 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 circulation circuit 64. 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.

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)
  • Devices For Blowing Cold Air, Devices For Blowing Warm Air, And Means For Preventing Water Condensation In Air Conditioning Units (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Defrosting Systems (AREA)

Abstract

The air exchanger comprises at least one tubular circuit for evaporating a refrigerant and thermally conducting fins (40) fastened to the tubular evaporation circuit and at least one tubular circuit (35) for condensing a refrigerant, which is connected via thermally conducting fins (40) to the evaporation circuit.

Description

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 Refrigeration installation of at least one piece of furniture and / or a cooling chamber and heating of at least one room, and an air heat exchanger for this installation
La présente invention concerne le domaine technique des installations frigorifiques utilisées pour assurer la réfrigération de produits divers et notamment de produits alimentaires.The present invention relates to the technical field of refrigerating plants used to provide refrigeration of various products and in particular food products.
Dans le domaine ci-dessus, il est connu de mettre en œuvre, notamment dans les grandes surfaces alimentaires, une installation frigorifique comprenant des circuits haute et basse pression de fluide frigorigène raccordés à une ou plusieurs unités de réfrigération telle qu'une armoire ou une vitrine réfrigérée ou encore une chambre froide. L'installation frigorifique comprend en outre un groupe de compression qui aspire le fluide frigorigène du circuit basse pression et le refoule comprimé dans le circuit haute pression. L'installation comprend par ailleurs, en aval du groupe de compression, un condenseur extérieur au niveau duquel le fluide frigorigène est refroidi avant d'être redirigé vers l'unité de réfrigération ou un réservoir de stockage intermédiaire. Une telle installation donne pleinement satisfaction en ce qui concerne sa fonction de conservation à des températures de consigne basses de produits fragiles ou de denrées alimentaires. Toutefois, la dissipation à l'extérieur de la chaleur extraite au niveau des unités de réfrigération et résultant du travail du groupe de compression constitue une perte sèche d'énergie qui, compte tenu des coûts de l'énergie et des impératifs de développement durable, n'est pas satisfaisante.In the above field, it is known to implement, especially in large food surfaces, a refrigeration system 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. However, 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.
Afin de remédier à cet inconvénient de gaspillage d'énergie, une demande EP 0 431 797 a proposé d'adapter, dans un aérotherme, un circuit de condensation alimenté en fluide frigorigène haute pression gazeux de manière à en récupérer la chaleur pour chauffer des locaux. Cependant, l'installation proposée par la demande EP 0 431 797 ne permet pas de disposer de suffisamment de chaleur pour assurer, seule, un chauffage satisfaisant en hiver.In order to overcome this drawback of energy wastage, an application EP 0 431 797 proposed to adapt, in a heater, a condensation circuit fed with high-pressure gas refrigerant so as to recover the heat for heating premises . However, the installation proposed by the application EP 0 431 797 does not It does not provide enough heat to ensure adequate heating in winter alone.
Une demande EP 1 921 401 a alors proposé une installation frigorifique dont la chaleur extraite est récupérée pour assurer le chauffage d'un accumulateur de chaleur qui est en relation avec un circuit d'eau de chauffage central et/ou un circuit d'eau chaude sanitaire. L'installation, selon la demande EP 1 921 401, comprend en outre un évaporateur extérieur qui permet, durant la période hivernale, de prélever à l'extérieur la chaleur supplémentaire nécessaire pour satisfaire les besoins de chauffage. Pendant la période estivale, la chaleur extraite par l'installation selon EP 1 921 401 est évacuée en majeure partie au niveau d'un condenseur extérieur totalement indépendant de l'évaporeur extérieur. Si cette installation permet d'obtenir un complément de chaleur dans des conditions satisfaisantes par un fonctionnement en pompe à chaleur, elle présente toutefois l'inconvénient de ne pas offrir une puissance suffisante pour couvrir les besoins de chauffage des locaux de sorte qu'il est prévu des moyens de chauffage électrique complémentaire ce qui pénalise les performances environnementales de l'installation. De plus, cette installation prévoit un dégivrage de l'évaporateur extérieur par inversion de cycle ce qui affecte également les performances de l'installation dans la mesure où la conception de l'évaporateur extérieur doit alors résulter d'un compromis entre ses modes de fonctionnement en évaporateur et en condenseur. Enfin, la demande EP 1 921 401 prévoit de placer l'échangeur de chaleur intérieur pour le chauffage en série avec le condenseur extérieur et en amont de ce dernier, ce qui pénalise le rendement énergétique de l'installation et impose la mise en œuvre d'une quantité importante de fluide frigorigène liquide pour remplir le circuit en aval de l'échangeur de chaleur lorsque le fluide frigorigène est intégralement condensé dans ce dernier. Ainsi, il est apparu le besoin d'un nouveau type d'installation frigorifique qui permette, d'une part, d'assurer une récupération d'une partie au moins de la chaleur disponible au niveau du fluide frigorigène pour chauffer des locaux et, d'autre part, d'éventuellement compléter cet apport de chaleur dans des conditions économiquement et écologiquement satisfaisantes et qui présente, par ailleurs, à puissance électrique absorbée équivalente des performances supérieures à celles des installations frigorifiques connues ainsi que des coûts de maintenance moindres. Afin d'atteindre cet objectif, l'invention concerne une installation frigorifique à fluide frigorigène comprenant au moins :An application EP 1 921 401 then proposed a refrigeration plant whose extracted heat is recovered for heating a heat accumulator which is in connection with a central heating water circuit and / or a hot water circuit. health. The installation, according to the application EP 1 921 401, furthermore comprises an external evaporator which makes it possible, during the winter period, to take outside the additional heat necessary to satisfy the heating requirements. During the summer, the heat extracted by the installation according to EP 1 921 401 is largely discharged at an external condenser completely independent of the external evaporator. Although this installation makes it possible to obtain additional heat under satisfactory conditions through heat pump operation, it nevertheless has the drawback of not offering sufficient power to cover the heating requirements of the premises so that it is provided complementary electric heating means which penalizes the environmental performance of the installation. In addition, 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. Finally, the application EP 1 921 401 provides for placing the indoor heat exchanger for heating in series 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 fully condensed therein. Thus, it has emerged the need for a new type of refrigeration plant that allows, on the one hand, to recover at least a portion of the heat available in the refrigerant for heating premises and, on the other hand, to possibly supplement this heat input in economically and ecologically satisfactory conditions and which has, moreover, equivalent electrical power absorbed performance superior to those known refrigeration installations and lower maintenance costs. In order to achieve this objective, the invention relates to a refrigerant refrigerant installation comprising at least:
- des circuits haute pression et basse pression,- high pressure and low pressure circuits,
- une unité de réfrigération comprenant au moins un évaporateur disposé dans un meuble ou une chambre frigorifique et raccordé aux circuits haute et basse pression,a refrigeration unit comprising at least one evaporator arranged in a cabinet or a refrigerating chamber and connected to the high and low pressure circuits,
- une unité de climatisation comprenant au moins un échangeur qui est disposé à l'intérieur d'un local et qui comprend au moins un condenseur raccordé aux circuits haute et basse pression,an air conditioning unit comprising at least one exchanger which is arranged inside a room and which comprises at least one condenser connected to the high and low pressure circuits,
- une unité extérieure comprenant au moins un échangeur à air qui est disposé à l'extérieur et qui comprend un circuit de condensation raccordé aux circuits haute et basse pression,an outdoor unit comprising at least one air exchanger which is arranged outside and which comprises a condensation circuit connected to the high and low pressure circuits,
- un groupe de compression principal raccordé aux circuits haute et basse pression,a main compression unit connected to the high and low pressure circuits,
- un groupe de compression auxiliaire raccordé aux circuits haute et basse pression,an auxiliary compression group connected to the high and low pressure circuits,
- une unité de commande qui pilote au moins le fonctionnement de l'installation.- a control unit that controls at least the operation of the installation.
Selon l'invention, l'unité frigorifique est caractérisée en ce que :According to the invention, the refrigerating unit is characterized in that:
- l'échangeur à air de l'unité extérieure comprend : - un circuit tubulaire d'évaporation adapté pour être alimenté uniquement en fluide frigorigène basse pression et raccordé aux circuits haute et basse pression,- the air exchanger of the outdoor unit comprises: a tubular evaporation circuit adapted to be fed only with low pressure refrigerant and connected to the high and low pressure circuits,
- des ailettes thermiquement conductrices reliant le circuit tubulaire d'évaporation et le circuit tubulaire de condensation en étant solidaire des circuits tubulaires d'évaporation et de condensation, le circuit tubulaire de condensation étant adapté pour être alimenté uniquement en fluide frigorigène haute pression et dimensionné pour dissiper l'intégralité de la chaleur résultant du maintien, au niveau de chaque unité de réfrigération, des températures de consigne lorsque il règne à l'extérieur une température estivale,thermally conductive fins connecting the tubular evaporation circuit and the tubular condensation circuit being integral with the tubular evaporation and condensation circuits, the tubular condensation circuit being adapted to be fed only with high pressure refrigerant and sized to dissipate all the heat resulting from the maintenance, at each refrigeration unit, of the set temperatures when outside a summer temperature,
- l'unité de commande est adaptée pour placer l'installation :- the control unit is adapted to place the installation:
- soit dans un mode de fonctionnement de réfrigération pure, dans lequel la puissance de tous les groupes de compression est disponible pour de l'extraction de chaleur uniquement au niveau de chaque unité de réfrigération,- either in a pure refrigeration operating mode, in which the power of all compression units is available for heat extraction only at each refrigeration unit,
- soit dans un mode de fonctionnement mixte, réfrigération/pompe à chaleur, dans lequel la puissance du groupe de compression auxiliaire est disponible pour de l'extraction de chaleur au niveau de l'unité extérieure et la puissance de chaque autre groupe de compression est disponible pour de l'extraction de chaleur au niveau de chaque unité de réfrigération,- either in a mixed operation mode, refrigeration / heat pump, in which the power of the auxiliary compression group is available for heat extraction at the outdoor unit and the power of each other compression group is available for heat extraction at each refrigeration unit,
- les groupes de compression sont dimensionnés pour que leurs puissances cumulées soient suffisantes pour maintenir, au niveau de chaque unité de réfrigération, les températures de consigne lorsque il règne à l'extérieur une température estivale et que l'installation est en mode de réfrigération pure.the compression units are dimensioned so that their cumulative powers are sufficient to maintain, at each refrigeration unit, the set temperatures when outside a summer temperature and the installation is in pure refrigeration mode .
Une telle installation frigorifique selon l'invention est particulièrement adaptée au refroidissement des unités de réfrigération et au chauffage d'un local avec la chaleur récupérée au niveau des unités de réfrigération et résultant de la compression du fluide frigorigène. A cet égard, la mise en œuvre d'un groupe de compression auxiliaire permet, lorsque la chaleur récupérée au niveau des unités de réfrigération n'est pas suffisante pour chauffer le local de façon satisfaisante, de prélever à l'extérieur la chaleur manquante et nécessaire pour atteindre le niveau de chauffage satisfaisant.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.
Selon l'invention, l'échangeur de chaque unité de climatisation peut être de toute nature appropriée. Ainsi, l'échangeur de chaque unité de climatisation, ou de certaines unités seulement, peut être un échangeur permettant le chauffage d'un liquide caloporteur, tel que par exemple mais non exclusivement, l'eau d'un circuit de chauffage, ou encore de l'eau sanitaire. L'échangeur de chaque unité de climatisation, ou de certaines unités seulement, peut également être un échangeur de chaleur à air également appelé aérotherme. La mise en œuvre d'un tel échangeur à air présente l'avantage de chauffer directement l'air sans mise en œuvre d'un fluide caloporteur intermédiaire et permet de disposer d'un rendement optimal et de simplifier la mise en œuvre et l'exploitation de l'installation frigorifique selon l'invention. Bien entendu, l'installation selon l'invention est aussi susceptible de mettre en œuvre plusieurs unités de climatisation ayant des types d'échangeurs différents.According to the invention, the exchanger of each air conditioning unit can be of any suitable nature. Thus, 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. The implementation of such an air exchanger has the advantage of directly heating the air without implementation of an intermediate heat transfer fluid and provides optimal performance and simplify the implementation and the operation of the refrigeration plant according to the invention. Of course, the installation according to the invention is also likely to implement several air conditioning units having different types of exchangers.
Par ailleurs, la mise en œuvre d'une unité extérieure conçue pour permettre, tout à la fois, une évacuation totale de la chaleur en été et une récupération de chaleur d'appoint en hiver avec des circuits reliés par des ailettes permet d'obtenir une unité extérieure à double fonction compacte.Furthermore, the implementation of an outdoor unit designed to allow, at the same time, a total evacuation of the heat in summer and extra heat recovery in winter with circuits connected by fins makes it possible to obtain an outdoor unit with compact dual function.
Diverses formes de réalisation de l'installation peuvent être envisagées. Ainsi les circuits haute et basse pression peuvent comprendre un circuit haute pression principal, un circuit haute pression secondaire et un circuit basse pression principal. L'évaporateur de l'unité de climatisation sera alors alimenté en fluide frigorigène par le circuit haute pression principal via un détendeur et raccordé au circuit basse pression principal. Le circuit d'évapo ration de l'unité extérieure sera alimenté par le circuit haute pression principal via un détenteur et raccordé à un circuit basse pression auxiliaire tandis que le circuit de condensation de l'unité extérieure est raccordé au circuit haute pression principal en amont des évaporateurs. Le groupe de compression principal aspirera le fluide frigorigène du circuit basse pression principal et refoulera le fluide frigorigène comprimé dans le circuit haute pression principal tandis que le groupe de compression auxiliaire aspira le fluide frigorigène du circuit basse pression auxiliaire et refoulera le fluide frigorigène comprimé dans le circuit haute pression principal.Various embodiments of the installation can be envisaged. Thus 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. 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.
L'installation peut également comprendre une vanne d'isolation pilotée pour ouvrir ou fermer la communication entre le circuit basse pression auxiliaire et le circuit d'évaporation de l'échangeur extérieur, ainsi qu'un circuit de dérivation qui raccorde le circuit basse pression principal au circuit basse pression secondaire et qui est équipé d'une vanne de dérivation pilotée pour ouvrir ou fermer le circuit de dérivation. L'unité de commande est alors adaptée pour :The installation may also include a controlled isolation valve for opening or closing the communication between the auxiliary low-pressure circuit and the evaporation circuit of the external exchanger, as well as a branch circuit which connects the main low-pressure circuit. to the secondary low pressure circuit and which is equipped with a controlled bypass valve to open or close the bypass circuit. The control unit is then adapted to:
- dans le mode de fonctionnement de réfrigération pure, fermer la vanne d'isolation et ouvrir la vanne de dérivation, de sorte que la puissance du groupe de compression auxiliaire est disponible pour de l'extraction de chaleur uniquement au niveau de chaque l'unité de réfrigération,- in the pure refrigeration operating mode, close the isolation valve and open the bypass valve, so that the power of the auxiliary compression group is available for heat extraction only at each unit refrigeration,
- dans le mode de fonctionnement mixte, réfrigération / pompe à chaleur, ouvrir la vanne d'isolation et fermer la vanne de dérivation, de sorte que la puissance du groupe de compression auxiliaire est disponible pour de l'extraction de chaleur au niveau de l'unité extérieure.- in the mixed operation mode, refrigeration / heat pump, open the isolation valve and close the bypass valve, so that the power of the auxiliary compression group is available for heat extraction at the level of the outdoor unit.
Selon une variante de l'invention, l'unité de commande est adaptée pour passer du mode de fonctionnement mixte au mode de fonctionnement de réfrigération pure et inversement en fonction des besoins de réfrigération.According to a variant of the invention, the 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.
Il doit être noté que la surface importante du circuit de condensation, résultant de son dimensionnement pour l'évacuation de chaleur en été, permet d'obtenir une très grande efficacité pour un dégivrage de l'unité extérieure lors de son fonctionnement en mode mixte. A cet effet, selon une variante de réalisation de l'invention, l'installation comprend des moyens de dégivrage de l'échangeur de l'unité extérieure adaptés pour assurer, dans le cadre du fonctionnement en mode mixte de l'installation, l'alimentation temporaire du circuit de condensation de l'unité extérieure. La mise en œuvre de tels moyens de dégivrage permet de préserver l'efficacité de l'échangeur thermique extérieur notamment lorsque ce dernier est utilisé comme source de chaleur en période hivernale. L'utilisation du circuit de condensation, conçu pour supporter les hautes pressions, du fluide frigorigène permet d'éviter de recourir à un dégivrage par inversion de cycle au niveau du circuit d'évaporation ce qui présente l'avantage, d'une part, de ne pas devoir dimensionner le circuit d'évaporation pour les hautes pressions, d'autre part, d'éviter de soumettre le circuit d'évaporation au choc thermique résultant d'un passage rapide d'une température négative à une température positive, par exemple, supérieure à 30° et, par ailleurs, d'éviter les risques d'aspiration de liquide lors du redémarrage en pompe à chaleur. De plus, les ailettes reliant les circuits de condensation et d'évaporation amortissent les différences de dilation entre les circuits de condensation et d'évaporation lors des phases de dégivrage réduisant ainsi les contraintes mécaniques subies par ces circuits. L'invention permet, par séparation des circuits d'évaporation et de condensation de l'unité extérieure, d'optimiser leur dimensionnement pour leur régime de fonctionnement nominal avec des pertes de charge correctes, des vitesses de fluide maîtrisées permettant un bon retour d'huile ce qui contribue aux performances de l'ensemble de l'installation frigorifique.It should be noted that the large surface of the condensation circuit, resulting from its dimensioning for the heat dissipation in summer, makes it possible to obtain a very high efficiency for defrosting the outdoor unit during its operation in mixed mode. For this purpose, according to an alternative embodiment of the invention, 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. The implementation of such 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. In addition, 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 system.
Selon une caractéristique de l'invention, l'installation comprend :According to one characteristic of the invention, the installation comprises:
- des moyens d'évaluation du givre sur l'échangeur extérieur, - au moins une vanne pilotée d'alimentation du circuit de condensation de l'échangeur à air, et l'unité de commande est adaptée pour piloter en ouverture d'une vanne d'alimentation du circuit de condensation lorsque le givre sur l'échangeur dépasse un certain seuil. Selon l'invention, la détection du givre peut être réalisée de différentes manière comme par exemple en surveillant la charge d'un moteur de ventilation forcée de l'échangeur pour déduire de l'augmentation de la charge du moteur une apparition de givre sur l'échangeur. Selon une autre forme de réalisation, les moyens d'évaluation du givre comprennent des moyens de mesure de l'humidité de l'air en entrée et en sortie de l'échangeur.- Frost evaluation means on the external exchanger, - at least one controlled valve for supplying the condenser circuit of the air exchanger, and the control unit is adapted to control the opening of a valve supply of the condensation circuit when the frost on the exchanger exceeds a certain threshold. According to the invention, 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. According to another embodiment, the frost evaluation means comprise means for measuring the humidity of the air entering and leaving the exchanger.
Selon une caractéristique de l'invention, l'unité de commande est adaptée pour commander une inversion du sens de fonctionnement d'un ventilateur extracteur équipant l'échangeur extérieur en fin de dégivrage de ce dernier. Cette inversion de rotation permet d'obtenir un séchage optimal de l'échangeur de l'unité extérieure.According to one characteristic of the invention, the 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.
Selon un mode de réalisation, l'installation peut être adaptée à des activités nécessitant plusieurs niveaux de froid telles que, par exemple, des activités où il est nécessaire de conserver des produits frais à des températures positives ainsi que des produits congelés à des températures négatives. L'installation frigorifique selon l'invention comprend alors:According to one embodiment, the plant can be adapted to activities requiring several levels of cold such as, for example, activities where it is necessary to keep fresh products at positive temperatures as well as products frozen at negative temperatures. . The refrigeration plant according to the invention then comprises:
- un circuit basse pression secondaire de fluide frigorigène,a secondary refrigerant low pressure circuit,
- une unité frigorifique secondaire comprenant au moins un évaporateur disposé dans un meuble ou un local frigorifique et alimenté en fluide frigorigène par le circuit haute pression principal via un détendeur et raccordé au circuit basse pression secondaire,a secondary refrigeration unit comprising at least one evaporator arranged in a piece of furniture or a cold room and supplied with refrigerant by the main high pressure circuit via a pressure reducer and connected to the secondary low pressure circuit,
- un groupe de compression secondaire qui aspire le fluide frigorigène du circuit basse pression secondaire et qui refoule le fluide frigorigène comprimé dans le circuit haute pression principal, l'unité de commande étant adaptée pour piloter le fonctionnement du groupe de compression secondaire.- A secondary compression group which sucks the refrigerant from the secondary low pressure circuit and which discharges the compressed refrigerant into the main high pressure circuit, the control unit being adapted to control the operation of the secondary compression group.
La mise en œuvre du groupe de compression secondaire refoulant le fluide frigorigène comprimé dans le même circuit principal haute pression que les autres groupes de compression permet d'utiliser l'intégralité de l'énergie thermique récupérée par l'ensemble des groupes de compression pour assurer le chauffage du ou des locaux dans lesquels sont situés les aérothermes.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 all the compression groups to ensure heating the premises where the unit heaters are located.
Selon une caractéristique de l'invention, la puissance de groupe de compression auxiliaire n'est pas suffisante pour assurer le refroidissement du local dans des conditions de température extérieure estivales.According to one characteristic of the invention, the auxiliary compression group power is not sufficient to ensure the cooling of the room under summer outdoor temperature conditions.
Selon un mode de réalisation de l'invention, au moins un aérotherme de l'unité de climatisation est adapté pour être réversible et fonctionner en condenseur ou en évaporateur, et l'installation comprend des moyens pour alimenter en fluide frigorigène chaque aérotherme fonctionnant en évaporateur.According to one embodiment of the invention, 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 .
Selon une variante de ce mode de réalisation, le groupe de compression auxiliaire possède une puissance suffisante pour assurer le refroidissement du local avec une température extérieure estivale.According to a variant of this embodiment, the auxiliary compression group has sufficient power to ensure the cooling of the room with a summer outdoor temperature.
L'invention concerne aussi un échangeur à air pour une installation frigorifique conforme à l'invention, cet échangeur à air comprend :The invention also relates to an air exchanger for a refrigeration plant according to the invention, this air exchanger comprises:
- un circuit tubulaire de condensation adapté pour être alimenté uniquement en fluide frigorigène haute pression, - un circuit tubulaire d'évaporation adapté pour être alimenté uniquement en fluide frigorigène basse pression,a tubular condensation circuit adapted to be fed only with high-pressure refrigerant, a tubular evaporation circuit adapted to be fed only with low pressure refrigerant,
- des ailettes thermiquement conductrices reliant le circuit tubulaire d'évaporation et le circuit tubulaire de condensation en étant solidaires des circuits tubulaires d'évaporation et de condensation.- Thermally conductive fins connecting the tubular evaporation circuit and the tubular condensation circuit being integral with the tubular evaporation and condensation circuits.
Selon l'invention le circuit de condensation présente une puissance d'échange suffisante pour assurer l'évacuation de chaleur en période estivale, c'est-à-dire que la valeur absolue de la puissance thermique du circuit tubulaire de condensation est supérieure ou égale à la valeur absolue de la puissance thermique du circuit tubulaire d'évaporation.According to the invention, the condensation circuit has a sufficient exchange power to ensure heat dissipation in the summer period, that is to say that the absolute value of the thermal power of the tubular condensation circuit is greater than or equal to to the absolute value of the thermal power of the evaporation tubular circuit.
L'échangeur selon l'invention présente l'avantage de disposer d'un circuit d'évaporation distinct du circuit de condensation de sorte que chacun de ces circuits est parfaitement dimensionné pour assurer de façon optimale sa fonction de condenseur ou d'évaporateur à la différence d'un échangeur de chaleur dont le circuit serait adapté pour avoir un fonctionnement mixte soit en condenseur soit en évaporateur. La conception de l'échangeur selon l'invention lui permet donc d'obtenir un rendement énergique optimal. Par ailleurs, la mise en œuvre d'ailettes communes aux circuits d'évaporation et de condensation permet d'optimiser les échanges thermiques en phase de dégivrage dont la durée peut alors être raccourcie par rapport au temps de dégivrage dans le cadre d'un mode de construction qui consisterait à simplement juxtaposer l'un au dessus de l'autre un condenseur et un évaporateur. De plus, comme cela a été dit précédemment, les ailettes assurent un amortissement mécanique des phénomènes de dilatation différentielle lors des phases de dégivrages.The exchanger according to the invention has the advantage of having an evaporation circuit separate from the condensation circuit so that each of these circuits is perfectly sized to optimally ensure its function of condenser or evaporator at the difference of 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. Furthermore, the use of vanes common to the evaporation and condensation circuits makes it possible to optimize the heat exchanges 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. In addition, as mentioned above, the fins provide mechanical damping of the differential expansion phenomena during the defrosting phases.
Selon une caractéristique de l'invention, la puissance thermique du circuit tubulaire de condensation possède une valeur comprise entre 1 à 5 fois à la valeur absolue de la puissance thermique du circuit tubulaire d'évaporation. Selon une autre caractéristique de l'invention, la surface d'échange du circuit tubulaire de condensation présente entre 50 % et 80 % de la somme des surfaces d'échange des circuits tubulaires de condensation et d'évapo ration. Selon un mode de réalisation de l'échangeur à air, en conditions normales d'utilisation le circuit de condensation est situé en partie au moins en dessous du circuit d'évaporation. Cette disposition permet de mettre à profit les phénomènes de convection pour accélérer le dégivrage du circuit d'évaporation. Selon un autre mode de réalisation de l'échangeur, les circuits de condensation et d'évaporation comprennent des boucles ou des nappes de tubes et certaines boucles ou nappes du circuit d'évaporation sont superposées et intercalées entre des boucles ou nappes du circuit de condensation.According to one characteristic of the invention, 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. According to another characteristic of the invention, the exchange surface of the tubular condensation circuit has between 50% and 80% of the sum of the exchange surfaces of the condensation and evapo ration tubular circuits. According to one embodiment of the air exchanger, under normal conditions of use the condensation circuit is located at least partly below the evaporation circuit. This arrangement makes it possible to take advantage of the convection phenomena to accelerate the defrosting of the evaporation circuit. According to another embodiment of the exchanger, 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. .
Selon une forme de réalisation de l'échangeur, les ailettes possèdent une orientation sensiblement verticale.According to one embodiment of the exchanger, the fins have a substantially vertical orientation.
Selon une variante de l'invention, les circuits d'évaporation et de condensation possèdent des tubes principaux rectilignes qui sont inclinés de quelques degrés par rapport à l'horizontale, ce qui favorise le ruissellement de l'eau. Selon une autre variante de l'invention, le circuit de condensation comprend au moins une nappe de tube qui forme la première nappe de tube en partant du bas de l'échangeur. Cette première nappe de tube forme de manière avantageuse une surface sur laquelle une partie de l'eau présente dans l'air se condensera ou se déposera, se réduisant ainsi la charge de l'air circulant dans l'échangeur et réduisant donc la vitesse d'apparition de givre sur le circuit d'évaporation.According to a variant of the invention, the evaporation and condensation circuits have rectilinear main tubes which are inclined by a few degrees with respect to the horizontal, which favors the runoff of the water. According to another variant of the invention, 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.
Selon une caractéristique de l'invention, l'échangeur de chaleur comprend au moins un ventilateur électrique assurant une circulation forcée de l'air dans l'échangeur. Bien entendu les différentes caractéristiques, variantes, formes et modes de réalisation de l'installation et/ou de l'échangeur peuvent être associées les unes avec les autres selon diverses combinaisons dans la mesure où elles ne sont pas incompatibles ou exclusives les unes des autres.According to one characteristic of the invention, the heat exchanger comprises at least one electric fan ensuring a forced circulation of air in the exchanger. Of course, the various features, variants, shapes and embodiments of the plant and / or the exchanger can be associated with each other in various combinations to the extent that they are not incompatible or exclusive of each other. .
Par ailleurs, diverses autres caractéristiques et avantages de l'invention ressortent de la description effectuée en référence aux dessins annexés qui illustrent des exemples non limitatifs de réalisation d'un échangeur à air et d'installations frigorifiques selon l'invention.Moreover, various other features and advantages of the invention emerge from the description with reference to the accompanying drawings which illustrate non-limiting examples of embodiment of an air exchanger and refrigeration plants according to the invention.
La figure 1 est une vue schématique d'une installation frigorifique selon l'invention.Figure 1 is a schematic view of a refrigeration plant according to the invention.
La figure 2 est une coupe longitudinale d'un échangeur de chaleur selon l'invention susceptible d'être mis en œuvre dans le cadre de l'installation illustrée à la figure 1.FIG. 2 is a longitudinal section of a heat exchanger according to the invention that can be implemented as part of the installation illustrated in FIG.
La figure 3 est une coupe transversale de l'échangeur selon la ligne III-III de la figure 2.FIG. 3 is a cross-section of the exchanger along line III-III of FIG. 2.
La figure 4 est une vue schématique d'une autre forme de réalisation d'une installation frigorifique selon l'invention. Une installation frigorifique selon l'invention, telle qu'illustrée à la figure 1 et désignée dans son ensemble par la référence 1, comprend un circuit haute pression principal 2 de fluide frigorigène sur lequel est disposé un réservoir haute pression 3 à partir duquel s'étend une branche 2a d'alimentation en fluide frigorigène haute pression d'au moins une et généralement plusieurs unités de réfrigération principales Rp. Une telle unité de réfrigération Rp comprend au moins un évaporateur disposé dans un meuble ou une chambre frigorifique.Figure 4 is a schematic view of another embodiment of a refrigeration plant according to the invention. A refrigeration plant according to the invention, as illustrated in Figure 1 and generally designated by the reference 1, comprises a main high pressure circuit 2 of refrigerant on which is disposed a high pressure tank 3 from which extends a branch 2 a high pressure refrigerant fluid supply of at least one and usually several main refrigeration units R p. Such a refrigeration unit R p comprises at least one evaporator disposed in a piece of furniture or a refrigerating chamber.
Cet évaporateur est alors alimenté en liquide frigorigène par le circuit haute pression principal 2a via un détendeur. L'évaporateur est en outre raccordé à un circuit basse pression principal 4. L'installation frigorifique 1 comprend également au moins une ou selon l'exemple illustré trois unités de climatisation 5 disposées à l'intérieur d'un ou plusieurs locaux. Selon l'exemple illustré, chaque unité de climatisation comprend au moins un échangeur à air ou aérotherme équipé d'au moins un condenseur 6 qui est raccordé au circuit haute pression principal 2 en amont des évaporateurs des unités de réfrigération Rp et, selon l'exemple illustré, en amont également du réservoir 3 de fluide frigorigène haute pression. L'installation 1 comprend en outre un groupe de compression principal 10 qui aspire le fluide frigorigène du circuit basse pression principal 4 pour le refouler comprimé dans le circuit haute pression principal 2 en amont des condenseurs 6, du réservoir haute pression 3 et, bien entendu, des évaporateurs qu'il alimente. Le groupe de compression principal 10 comprend au moins un et, selon l'exemple illustré, trois compresseurs 11 raccordés en parallèle aux circuits haute pression 2 et basse pression 4. Le fonctionnement de le groupe de compression 10 est alors piloté par une unité de commande 12.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. According to the illustrated example, 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 R p and, according to illustrated example, 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.
Telle qu'ainsi constituée, l'installation frigorifique fonctionne de la manière suivante.As so constituted, the refrigeration system operates in the following manner.
Chaque unité de réfrigération principale Rp étant pourvue d'un dispositif autonome de régulation, elle commande l'ouverture d'une vanne alimentant son évaporateur en fluide frigorigène haute pression via un détendeur autant que de besoin pour maintenir en son sein une température de consigne. Le fonctionnement de l'unité de réfrigération induit une augmentation de pression dans le circuit basse pression principal 4 que l'unité de commandes 12 détecte pour déclencher le fonctionnement du groupe de compression principale 10 qui aspire alors le fluide frigorigène basse pression dans un état gazeux basse pression pour le refouler à l'état gazeux haute pression dans le circuit haute pression principal 2. En sortie du groupe de compression principal 10, le fluide frigorigène se trouve au sein du circuit haute pression principal 2 à l'état gazeux et à une température élevée de l'ordre de 60° à 80° C. L'invention se propose alors d'utiliser la chaleur du fluide frigorigène haute pression gazeux pour chauffer un ou plusieurs locaux par l'intermédiaire des aérothermes 5 dont les condenseurs 6 sont alimentés par des vannes 13 pilotées par l'unité de commandes 12. Ainsi, l'intégralité de la chaleur récupérée au niveau des unités de réfrigération est utilisée pour chauffer les locaux. En sortie des condenseurs le fluide frigorigène sera à l'état liquide haute pression. Pour faciliter la compréhension les parties du circuit principal haute pression dans lesquelles le fluide frigorigène haute pression est à l'état gazeux sont référencées 2 tandis que les parties où le fluide frigorigène est principalement à l'état liquide sont référencées 2a.Each main refrigeration unit R p 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 within it a set temperature . 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. At the output of the main compression group 10, the refrigerant is within the main high pressure circuit 2 in the gaseous state and at a high temperature of The invention then 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. Thus, all the heat recovered at the refrigeration units is used to heat the premises. At the outlet of the condensers the refrigerant will be in the high pressure liquid state. To facilitate understanding the principal parts of the high-pressure circuit in which the high-pressure refrigerant fluid is in the gaseous state are referenced 2, while the portions where the refrigerant is mainly in the liquid state are referenced 2a.
La chaleur récupérée au niveau des unités de réfrigération peut, dans certains cas notamment en période hivernale, ne pas être suffisante pour chauffer les locaux à une température de consigne acceptable voire confortable. Par période hivernale, il faut entendre une période pendant laquelle la température extérieure moyenne est inférieure à 18°C. L'invention propose alors de prélever à l'extérieur la chaleur ou les calories manquantes. A cet effet il est mis en œuvre une unité extérieure 15 comprenant au moins un échangeur de chaleur 17 qui comprend un circuit d'évaporation 18 raccordé au circuit haute pression principal 2 via un détendeur 19. Le circuit d'évaporation 18 est également raccordé à un circuit basse pression auxiliaire 20 qui alimente un groupe de compression auxiliaire 21. Le groupe de compression auxiliaire 21 comprend au moins un et, selon l'exemple illustré, deux compresseurs 22 qui sont raccordés en parallèle au circuit basse pression auxiliaire 20 et au circuit haute pression principal 2. Le groupe de compression auxiliaire 20 aspire alors via le circuit basse pression auxiliaire 20 le fluide frigorigène à l'état gazeux en provenance de l'évaporateur 18 de l'échangeur 17 pour le comprimer et le refouler dans le circuit principal 2. Le groupe de compression auxiliaire 20 est alors pilotée par l'unité de commandes 12 qui module le fonctionnement d'un seul ou des deux compresseurs 22 en fonction des besoins. Ainsi, le groupe de compression auxiliaire 21 et l'échangeur extérieur 5 fonctionnent en pompe à chaleur et prélèvent au niveau de l'air extérieur la chaleur complémentaire nécessaire pour maintenir la température de consigne dans les locaux au moyen des unités de climatisation 5. Ainsi, l'installation frigorifique selon l'invention permet d'assurer seule, dans un mode de fonctionnement mixte réfrigération/ pompe à chaleur, d'une part le refroidissement des unités de réfrigération et, d'autre part, le chauffage des locaux. Un tel mode de fonctionnement mixte permet donc de réaliser de sérieuses économies d'énergie pour le chauffage des locaux.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. For this purpose an outdoor unit 15 is implemented 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. Thus, 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.
Dans la mesure où la température à la surface de l'évaporateur 18 est négative compte tenu de la détente du fluide frigorigène en son sein, au bout d'un certain temps de fonctionnement, l'évaporateur 16 sera recouvert du givre provenant de la condensation et du gel de l'eau présente dans l'atmosphère extérieure. Il est donc nécessaire d'assurer un dégivrage du condenseur 18 de façon régulière.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.
L'invention propose de réaliser ce dégivrage en utilisant la chaleur du fluide frigorigène comprimé en sortie des groupes de compression. A cet effet, l'invention propose d'associer un condenseur 25 à l'évaporateur 18. Le condenseur 25 alimenté en gaz frigorigène haute pression par le circuit principal haute pression 2 en y étant raccordé, d'une part, en aval des groupes de compression et, d'autre part, en amont du réservoir 3 et des évaporateurs des unités de réfrigération principales Rp. Selon une forme préférée de réalisation et comme cela ressort des figures 2 et 3, l'évaporateur 18 comprend un circuit tubulaire 30 d'évaporation du fluide frigorigène formé par des nappes de tube 32 comprenant des tubes principaux rectilignes comme le montre plus particulièrement la figure 2. De la même manière, le condenseur 25 comprend un circuit tubulaire de condensation du fluide frigorigène qui est constitué par des nappes 35 de tubes 36 possédant des tubes principaux rectilignes comme le montre la figure 2. Les circuits tubulaires 30 et 35 sont alors reliés entre eux par des ailettes thermiquement conductrices 40 qui présentent, selon l'exemple illustré, une orientation sensiblement verticale. La liaison thermique par conduction assurée par les ailettes 40 qui sont communes aux circuits d'évaporation 30 et de condensation 35 garantie une très grande efficacité du dégivrage. Afin d'optimiser encore la qualité des échanges thermiques et donc l'efficacité du dégivrage selon la forme de réalisation illustrée, les nappes de tubes des circuits de condensation 35 et d'évaporation 30 sont superposées et intercalées les unes entres les autres. De plus, selon l'exemple illustré, la première nappe de l'échangeur 17 en partant du bas est formée par des tubes du circuit de condensation de manière à former une surface de condensation de la vapeur d'eau présente dans l'air lors du fonctionnement de l'unité extérieure 15. Enfin, il pourra être remarqué que de manière habituelle pour l'homme du métier, l'échangeur 17 est situé à l'intérieur d'un châssis carrossé 41 équipé en partie haute d'au moins un et, selon l'exemple illustré, de deux ventilateurs 43 forçant la circulation de l'air à l'intérieur de l'unité extérieure 15. De plus, afin de favoriser l'élimination de l'eau liquide résultant du dégivrage ou de la condensation, les parties rectilignes des tubes et les ailettes pourront être inclinées par rapport à l'horizontale respectivement la verticale d'un angle α de quelques degrés, par exemple de 3° à 5°. Cette inclinaison pourra être obtenue par l'inclinaison de l'ensemble du châssis.The invention proposes to carry out this defrosting by using the heat of the refrigerant compressed at the outlet of the compression groups. For this purpose, 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 compression and, secondly, upstream of the tank 3 and the evaporators of the main refrigeration units R p . According to a preferred embodiment and as can be seen in FIGS. 2 and 3, the evaporator 18 comprises a tubular circuit 30 for evaporating the refrigerant formed by tube plies 32 comprising rectilinear main tubes, as shown more particularly in FIG. 2. In the same way, 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 Figure 2. The tubular circuits 30 and 35 are then interconnected by thermally conductive fins 40 which have, according to the illustrated example, 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. In order to further optimize the quality of the heat exchange and therefore the efficiency of the defrosting according to the illustrated embodiment, the tube sheets of the condensation and evaporation circuits are superimposed and interposed between each other. In addition, according to the illustrated example, 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. Finally, it may be noted that, in the usual manner for those skilled in the art, 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. In addition, to promote the elimination of liquid water resulting from deicing or the condensation, the rectilinear parts of the tubes and the fins may be inclined relative to the horizontal respectively the vertical angle α a few degrees, for example from 3 ° to 5 °. This inclination can be obtained by the inclination of the entire chassis.
Dans le mode de fonctionnement mixte exposé ci-dessus, il peut également être prévu, lorsque la température extérieure est particulièrement basse, une compression étagée du fluide frigorigène provenant de l'évaporateur de l'échangeur extérieur. A cet effet, l'installation peut comprendre une dérivation 55 raccordant la sortie du groupe de compression auxiliaire 21 en amont de l'aspiration du groupe de compression principal 10 par l'intermédiaire d'un robinet à pression constante 56 piloté par l'unité 12.In the mixed mode of operation described above, it can also be provided, when the outside temperature is particularly low, a stepped compression of the refrigerant from the evaporator of the external exchanger. For this purpose, 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.
Par ailleurs, lors du fonctionnement de l'installation en mode mixte, le condenseur 25 est utilisé régulièrement pour assurer le dégivrage de l'évaporateur 18. Ce fonctionnement régulier peut être assuré selon un intervalle de temps prédéfini indépendamment de l'apparition éventuelle de givre sur l'évaporateur 18 ou au contraire en fonction des besoins en cas d'apparition effective de givre ou de la prévision de l'apparition de givre.Furthermore, during the operation of the mixed mode installation, 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.
A cet effet, l'installation frigorifique 1 peut mettre en œuvre des moyens d'évaluation du givre. De tels moyens d'évaluation du givre peuvent être formés de toute manière appropriée. Par exemple, les moyens d'évaluation du givre peuvent comprendre des moyens 45 de surveillance de la charge des ventilateurs 43 qui lorsque cette dernière dépasse un seuil prédéterminé en déduisent l'apparition de givre. En effet, le givre se déposant sur les tubes 30 et les ailettes 40 va obstruer progressivement l'échangeur 17 y rendant plus difficile la circulation de l'air de sorte que la charge des ventilateurs 43 augmente.For this purpose, the refrigerating plant 1 can implement means for evaluating the ice. Such frost evaluation means may be formed in any suitable manner. For example, 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.
Les moyens de détection de givre peuvent également comprendre un système qui mesure l'hydrométrie de l'air d'entrée et de sortie de l'unité extérieure 15 pour en déduire l'apparition éventuelle de givre. Les moyens d'évaluation du givre peuvent également comprendre un système de mesure de l'hydrométrie et de la température de l'air extérieur pour en fonction de ces dernières, prévoir l'apparition du givre. Bien entendu, les moyens d'évaluation du givre sont raccordés à l'unité de commande 12 qui, lorsque cela est nécessaire, déclenche un cycle de dégivrage. Pendant un tel cycle de dégivrage, l'unité 12 commande l'alimentation du condenseur 25 en fluide frigorigène haute pression chaud. Cette alimentation est assurée par une branche du circuit principal haute pression 2 commandé par un robinet 46 piloté par l'unité 12. Le robinet 46 permet alors l'admission dans le circuit d'alimentation du condenseur 25 de gaz frigorigène haute pression en provenance directe des groupes de compression 10 et 21. Afin d'éviter un choc thermique trop important au niveau de l'échangeur 17, il peut également être prévu une ligne de dérivation 47 permettant un prélèvement de liquide frigorigène haute pression en aval du réservoir 3. Cette dérivation 47 est alors commandée par un robinet 48 piloté par l'unité 12. La commande des robinets 46 et 48 permet alors d'assurer un mélange entre du gaz haute pression en provenance des groupes de compression et du fluide haute pression en provenance du réservoir 3 pour moduler la température du fluide au sein du condenseur 25 pour amener le condenseur et les ailette progressivement d'une température négative à une température positive plus élevée mais inférieure à la température du gaz frigorigène comprimé en sortie des groupes de compression. Ainsi, l'unité 12 pourra maintenir la température du fluide frigorigène d'alimentation du condenseur 25 à des valeurs de l'ordre de 40° à 60° tandis que la température maximale en sortie des groupes de compression est de l'ordre de 800C. Une telle montée progressive de la température évite de faire subir à l'échangeur 15 un choc thermique trop important.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. Of course, the frost evaluation means are connected to the control unit 12 which, when necessary, triggers a defrost cycle. During such a defrosting 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. In order to avoid excessive thermal shock at the exchanger 17, 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. Thus, 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 0 C. such a gradual rise of the temperature avoids subjecting the exchanger 15 an excessive thermal shock.
Lorsque le dégivrage est fini, l'unité 12 peut également commander le fonctionnement des ventilateurs 41 de manière à souffler vers le bas l'air extérieur pour contribuer au séchage de l'échangeur 17.When the defrost is finished, 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.
Dans le mode de fonctionnement mixte de réfrigération/pompe à chaleur précédemment décrit, le groupe de compression auxiliaire 21 est utilisé pour extraire de la chaleur du milieu extérieur. Toutefois, selon l'invention, lorsqu'il n'est plus nécessaire de chauffer les locaux comme par exemple en période estivale, le groupe de compression auxiliaire 21 pourra être utilisé en renfort du groupe de compression principal pour comprimer le gaz frigorigène en provenance des unités de réfrigération Rp. A cet effet, l'installation frigorifique comprend un circuit de dérivation 50 reliant le circuit basse pression principal 4 au circuit basse pression auxiliaire 20 par l'intermédiaire d'un robinet commandé 51 par l'unité 12. Le circuit basse pression auxiliaire 20 comprend également en amont de la jonction avec la dérivation 50 un robinet 52 commandé par l'unité 12. Ainsi, dans un mode de fonctionnement qui pourra être qualifié de réfrigération pure, l'unité 12 commande la fermeture du robinet 52 et l'ouverture du robinet 51 ainsi que le fonctionnement du groupe de compression auxiliaire 21 en fonction des besoins. La puissance de ce dernier sera alors disponible pour la réfrigération, le condenseur 25 étant en outre dimensionné pour permettre l'évacuation à l'extérieur de la chaleur extraite au niveau des unités de réfrigération Rp. Il sera donc compris que la puissance du condenseur 25 est alors supérieure ou égale à la puissance de l'évaporateur 18. La puissance thermique du circuit tubulaire de condensation 25 peut par exemple posséder une valeur comprise entre 1 à 5 fois à la valeur absolue de la puissance thermique du circuit tubulaire d'évaporation 18. Ce rapport de puissance peut être obtenu en réalisant l'échangeur 17 de l'unité extérieure 15 de manière que la surface d'échange du circuit tubulaire de condensation 25 présente entre 50 % et 80 % de la somme des surfaces d'échange des circuits tubulaires de condensation 25 et d'évaporation 18.In the previously described mixed refrigeration / heat pump operation mode, the auxiliary compression unit 21 is used to extract heat from the outside environment. However, according to the invention, when it is no longer necessary to heat the premises as for example in the summer period, the auxiliary compression group 21 may be used in reinforcement of the main compression group to compress the refrigerant gas from refrigeration units R p . For this purpose, the refrigeration system 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 comprises also upstream of the junction with the bypass 50 a valve 52 controlled by the unit 12. Thus, in an operating mode that can be qualified as pure refrigeration, the unit 12 controls the closing of the valve 52 and the opening of the valve 51 and the operation of the auxiliary compression group 21 as needed. 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 R p . 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 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 condensation and evaporation tubular circuits 18.
Par ailleurs, en mode de réfrigération pure, les robinets 45 et 47 seront fermés et l'alimentation du condenseur 25 sera assurée par un robinet 53 à pression constante commandée par l'unité 12. De plus, dans ce mode de fonctionnement dit de réfrigération pure, l'évaporateur 18 ne sera pas alimenté en fluide frigorigène et la vanne et le robinet 19 sera donc fermé. La faculté de l'installation selon l'invention à fonctionner en mode mixte ou en mode de réfrigération pure permet de dimensionner les groupes de compression principal 10 et auxiliaire 21 avec une puissance cumulée juste suffisante pour assurer une réfrigération optimale en période estivale. Par période estivale, il faut entendre une période pendant laquelle la température moyenne en journée est supérieure à 18°C. Dans la mesure où en période hivernale, la puissance nécessaire pour assurer une réfrigération adaptée est inférieure à celle nécessaire en période estivale, la puissance résiduelle disponible au niveau du groupe de compression auxiliaire 21 peut avantageusement être utilisée, en période hivernale, pour un fonctionnement en pompe à chaleur pour le chauffage des locaux.Furthermore, in pure refrigeration mode, 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. Moreover, in this mode of operation called refrigeration pure, 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 operation in winter. heat pump for space heating.
Selon l'exemple décrit en relation avec la figure 1, l'unité de réfrigération comprend uniquement des circuits principaux basse et haute pression qui alimentent des unités de réfrigération fonctionnant dans des mêmes gammes de températures, soit positives soit négatives. Cependant, une installation de réfrigération conforme à l'invention peut devoir alimenter des unités de réfrigération à température positive et des unités de réfrigération à température négative. A cet effet et comme le montre la figure 4, une installation conforme à l'invention peut également comprendre au moins une unité frigorifique secondaire Rs comprenant au moins un évaporateur disposé dans un meuble ou un local frigorifié alimenté en fluide frigorigène par le circuit haute pression principal 2 en aval du réservoir 3. L'évaporateur de l'unité de réfrigération secondaire Rs est raccordé à un circuit basse pression secondaire 60 qui alimente un groupe de pression secondaire 61 aspirant le fluide frigorigène du circuit basse pression secondaire 60 pour refouler dans le circuit haute pression principale 2. Le groupe de compression secondaire 61 comprend alors au moins et, selon l'exemple, deux compresseurs 62 qui sont pilotés par l'unité de commande 12. Le fonctionnement de l'installation frigorifique selon l'invention comprenant un tel circuit basse pression secondaire 60 et un groupe de compression secondaire 61 est alors sensiblement analogue à celui décrit précédemment pour ce qui concerne les modes de fonctionnement mixte et de réfrigération pure.According to the example described with reference to FIG. 1, 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. However, a refrigeration plant according to the invention may have to supply positive temperature refrigeration units and negative temperature refrigeration units. For this purpose and as shown in Figure 4, an installation according to the invention may also comprise at least one secondary refrigeration unit R s comprising at least one evaporator disposed in a cabinet or a refrigerated premises supplied with refrigerant by the high circuit main pressure 2 downstream of the tank 3. 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 in the main high pressure circuit 2. The secondary compression group 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.
Il sera noté que selon l'exemple illustré figure 4, l'installation frigorifique comprend un échangeur à liquide 63 raccordé d'une part au circuit haute pression 2 en parallèle avec les échangeurs 5 et d'autre part à un circuit 64 de circulation d'un liquide caloporteur. L'échangeur à liquide 63, dont l'alimentation est contrôlée par une vanne 65 pilotée par l'unité de commande UC, permet alors un chauffage du liquide du circuit 64.It will be noted that according to the example illustrated in FIG. 4, the refrigerating installation 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 circulation circuit 64. 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.
Il sera en outre remarqué que le condenseur 25 est placé sur le circuit principal haute pression 2 en parallèle avec les échangeurs 6 et/ou 63. Ainsi, selon les phases de fonctionnement, il est possible de vider la phase liquide du fluide frigorigène des parties de circuit non utilisées par l'intermédiaire de lignes d'aspiration 67 et 68 commandées par des vannes 68 et 69 pilotées par l'unité 12. Les lignes d'aspiration 67 et 68 sont de plus raccordées, via un organe de détente 70, au circuit basse pression principal 4 juste en amont du groupe de compression principal 10. Cette disposition permet de réduire la quantité de fluide frigorigène mise en œuvre par l'installation par rapport aux installations où aucune vidange partielle de la phase liquide n'est possible.It will further be noted that the condenser 25 is placed on the main high pressure circuit 2 in parallel with the exchangers 6 and / or 63. Thus, depending on the operating phases, it is possible to empty the liquid phase of the refrigerant from the parts circuit not used via 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.
Bien entendu, diverses autres modifications peuvent être apportées à l'invention dans le cadre des revendications. Of course, various other modifications may be made to the invention within the scope of the claims.

Claims

REVENDICATIONS
1. Installation frigorifique à fluide frigorigène comprenant au moins : - des circuits haute pression (2) et basse pression (4),1. Refrigerant refrigerant installation comprising at least: - high pressure (2) and low pressure (4) circuits,
- une unité de réfrigération (Rp) comprenant au moins un évaporateur disposé dans un meuble ou une chambre frigorifique et raccordé aux circuits haute et basse pression (2,4),- a refrigeration unit (R p ) comprising at least one evaporator arranged in a cabinet or a refrigerating chamber and connected to the high and low pressure circuits (2, 4),
- une unité de climatisation (5) comprenant au moins un échangeur qui est disposé à l'intérieur d'un local et qui comprend au moins un condenseur (6) raccordé aux circuits haute et basse pression (2,4),an air conditioning unit (5) comprising at least one exchanger which is arranged inside a room and which comprises at least one condenser (6) connected to the high and low pressure circuits (2, 4),
- une unité extérieure (15) comprenant au moins un échangeur à air ( 17) qui est disposé à l'extérieur et qui comprend un circuit tubulaire de condensation (25,35) raccordé aux circuits haute et basse pression (2,4),- an outdoor unit (15) comprising at least one air exchanger (17) which is arranged outside and which comprises a tubular condensation circuit (25,35) connected to the high and low pressure circuits (2,4),
- un groupe de compression principal (10) raccordé aux circuits haute et basse pression (2,4)- a main compression group (10) connected to the high and low pressure circuits (2,4)
- un groupe de compression auxiliaire (21) raccordé aux circuits haute et basse pression (2,4), - une unité de commande (12) qui pilote le fonctionnement de l'installation frigorifique, caractérisée en ce que :an auxiliary compression unit (21) connected to the high and low pressure circuits (2,4); a control unit (12) which controls the operation of the refrigerating installation, characterized in that:
- l'échangeur à air de l'unité extérieure (15) comprend :the air exchanger of the outdoor unit (15) comprises:
- un circuit tubulaire d'évaporation (18,30) adapté pour être alimenté uniquement en fluide frigorigène basse pression et raccordé aux circuits haute et basse pression,a tubular evaporation circuit (18, 30) adapted to be fed only with low pressure refrigerant and connected to the high and low pressure circuits,
- des ailettes (40) thermiquement conductrices reliant le circuit tubulaire d'évaporation (18,30) et le circuit tubulaire de condensation (25,35) en étant solidaire des circuits tubulaires d'évaporation et de condensation,thermally conductive fins (40) connecting the tubular evaporation circuit (18, 30) and the tubular condensation circuit (25, 35) while being integral with the tubular evaporation and condensation circuits,
FEUILLE RECTIFIÉE (RÈGLE 91) ISA/ EP dimensionné pour dissiper l'intégralité de la chaleur résultant du maintien, au niveau de chaque unité de réfrigération, des températures de consigne lorsque il règne à l'extérieur une température estivale, - l'unité de commande (12) est adaptée pour placer l'installation :RECTIFIED SHEET (RULE 91) ISA / EP dimensioned to dissipate all the heat resulting from the maintenance, at each refrigeration unit, of the set temperatures when outside a summer temperature prevails, - the control unit (12) is adapted to place the installation:
- soit dans un mode de fonctionnement de réfrigération pure, dans lequel la puissance de tous les groupes de compression est disponible pour de l'extraction de chaleur uniquement au niveau de chaque unité de réfrigération, - soit dans un mode de fonctionnement mixte, réfrigération/pompe à chaleur, dans lequel la puissance du groupe de compression auxiliaire est disponible pour de l'extraction de chaleur au niveau de l'unité extérieure et la puissance de chaque autre groupe de compression est disponible pour de l'extraction de chaleur au niveau de chaque unité de réfrigération,- either in a pure refrigeration operating mode, in which the power of all compression groups is available for heat extraction only at each refrigeration unit, - or in a mixed operating mode, refrigeration / heat pump, in which the power of the auxiliary compression group is available for heat extraction at the outdoor unit and the power of each other compression group is available for heat extraction at the level of each refrigeration unit,
- les groupes de compression sont dimensionnés pour que leurs puissances cumulées soient suffisantes pour maintenir, au niveau de chaque unité de réfrigération, les températures de consigne lorsque il règne à l'extérieur une température estivale et que l'installation est en mode de réfrigération pure.the compression units are dimensioned so that their cumulative powers are sufficient to maintain, at each refrigeration unit, the set temperatures when outside a summer temperature and the installation is in pure refrigeration mode .
2. Installation frigorifique selon la revendication 1, caractérisée en ce que l'unité de commande (12) est adaptée pour passer du mode de fonctionnement mixte au mode de fonctionnement de réfrigération pure et inversement en fonction des besoins de réfrigération. 2. Refrigerating plant according to claim 1, characterized in that the control unit (12) is adapted to switch from the mixed operating mode to the pure refrigeration operating mode and vice versa depending on the refrigeration requirements.
3. Installation frigorifique selon la revendication 1 ou 2, caractérisée en ce que l'unité de commande est adaptée pour, en mode de fonctionnement mixte, piloter l'alimentation du circuit de condensation(25,35) de l'unité extérieure (15) afin d'assurer un dégivrage de l'unité extérieure (15). Cooling plant according to Claim 1 or 2, characterized in that the control unit is adapted to control, in mixed operating mode, the supply of the condensing circuit (25, 35) of the outdoor unit (15). ) to ensure defrosting of the outdoor unit (15).
4. Installation frigorifique selon la revendication 3, caractérisée en ce qu'elle comprend des moyens d'évaluation du givre sur l'échangeur, et en ce que l'unité de commande (12) est adaptée pour piloter en l'alimentation du circuit de condensation (25,35) lorsque le givre sur l'échangeur dépasse un certain seuil.4. Refrigeration plant according to claim 3, characterized in that it comprises means for evaluating the frost on the exchanger, and in that the control unit (12) is adapted to drive in the supply of the condensation circuit (25, 35) when the frost on the exchanger exceeds a certain threshold.
5. Installation frigorifique selon l'une des revendications 1 à 4, caractérisée en ce qu'elle comprend :5. Refrigeration plant according to one of claims 1 to 4, characterized in that it comprises:
- un circuit basse pression secondaire (60) de fluide frigorigène,a secondary low pressure circuit (60) for refrigerant,
- une unité frigorifique secondaire (Rs) comprenant au moins un évaporateur disposé dans un meuble ou un local frigorifique et alimenté en fluide frigorigène par le circuit haute pression et raccordé au circuit basse pression secondaire (60),- a secondary refrigeration unit (R s ) comprising at least one evaporator disposed in a cabinet or a refrigerated room and supplied with refrigerant by the high pressure circuit and connected to the secondary low pressure circuit (60),
- un groupe de compression secondaire (61) qui aspire le fluide frigorigène du circuit basse pression secondaire (60) et qui refoule le fluide frigorigène comprimé dans le circuit haute pression (2), et en ce que l'unité de commande (12) est adaptée pour piloter le fonctionnement du groupe de compression secondaire.a secondary compression unit (61) which sucks the refrigerant from the secondary low pressure circuit (60) and which delivers the compressed refrigerant into the high pressure circuit (2), and that the control unit (12) is adapted to control the operation of the secondary compression group.
6. Installation frigorifique selon l'une des revendications 1 à 5, caractérisée en ce que la valeur absolue de la puissance thermique du circuit tubulaire de condensation de l'échangeur à air est supérieure ou égale à la valeur absolue de la puissance thermique du circuit tubulaire d'évaporation de l'échangeur à air.6. Refrigeration plant according to one of claims 1 to 5, characterized in that the absolute value of the thermal power of the tubular condensation circuit of the air exchanger is greater than or equal to the absolute value of the thermal power of the circuit. tubular evaporation of the air exchanger.
7. Installation frigorifique selon l'une des revendications 1 à 6, caractérisée en ce que la puissance thermique du circuit tubulaire de condensation de l'échangeur à air possède une valeur comprise entre 1 à 5 fois à la valeur absolue de la puissance thermique du circuit tubulaire d'évaporation de l'échangeur à air.7. Refrigeration plant according to one of claims 1 to 6, characterized in that the thermal power of the tubular condensation circuit of the air exchanger has a value between 1 to 5 times the absolute value of the thermal power of the tubular evaporation circuit of the air exchanger.
8. Installation frigorifique selon l'une des revendications 1 à 7, caractérisée la surface d'échange du circuit tubulaire de condensation de l'échangeur à air présente entre 50 % et 80 % de la somme des surfaces d'échange des circuits tubulaires de condensation et d'évaporation. 8. Refrigeration plant according to one of claims 1 to 7, characterized the exchange surface of the tubular condensation circuit of the air exchanger has between 50% and 80% of the sum of the exchange surfaces of the tubular circuits of condensation and evaporation.
9. Echangeur extérieur à air pour une installation frigorifique selon l'une des revendications 1 à 8, caractérisé en ce qui comprend :9. External air exchanger for a refrigeration plant according to one of claims 1 to 8, characterized in that comprises:
- un circuit tubulaire de condensation (25,35) adapté pour être alimenté uniquement en fluide frigorigène haute pression, - un circuit tubulaire d'évaporation (18,30) adapté pour être alimenté uniquement en fluide frigorigène basse pression,a tubular condensation circuit (25, 35) adapted to be fed only with high-pressure refrigerant; a tubular evaporation circuit (18, 30) adapted to be fed only with low-pressure refrigerant,
- des ailettes (40) thermiquement conductrices reliant le circuit tubulaire d'évaporation (18,30) et le circuit tubulaire de condensation (25,35) en étant solidaire des circuits tubulaires d'évaporation et de condensation, la valeur absolue de la puissance thermique du circuit tubulaire de condensation étant supérieure ou égale à la valeur absolue de la puissance thermique du circuit tubulaire d'évaporation.thermally conductive fins (40) connecting the tubular evaporation circuit (18, 30) and the tubular condensation circuit (25, 35) while being integral with the tubular evaporation and condensation circuits, the absolute value of the power thermal of the tubular condensation circuit being greater than or equal to the absolute value of the thermal power of the tubular evaporation circuit.
10. Echangeur extérieur à air selon la revendication 9, caractérisé en ce que, la puissance thermique du circuit tubulaire de condensation possède une valeur comprise entre 1 à 5 fois à la valeur absolue de la puissance thermique du circuit tubulaire d'évaporation.10. External air exchanger according to claim 9, characterized in that, the thermal power of the tubular condensation circuit has a value between 1 to 5 times to the absolute value of the thermal power of the evaporation tubular circuit.
11. Echangeur extérieur à air selon la revendication 9 ou 10, caractérisé en ce que la surface d'échange du circuit tubulaire de condensation présente entre 50 % et 80 % de la somme des surfaces d'échange des circuits tubulaires de condensation et d'évaporation.11. External air exchanger according to claim 9 or 10, characterized in that the exchange surface of the tubular condensation circuit has between 50% and 80% of the sum of the exchange surfaces of the tubular condensation circuits and evaporation.
12. Echangeur de chaleur selon l'une des revendications 9 à 11, caractérisé en ce que les circuits de condensation (25,35) et d'évaporation (18,30) comprennent des boucles ou des nappes de tubes et en ce que certaines boucles ou nappes du circuit d'évaporation (18,30) sont superposées et intercalées entre des boucles ou nappes du circuit de condensation (25,35).12. Heat exchanger according to one of claims 9 to 11, characterized in that the condensation (25,35) and evaporation (18,30) circuits comprise loops or sheets of tubes and that certain loops or plies of the evaporation circuit (18, 30) are superimposed and interposed between loops or plies of the condensation circuit (25, 35).
13. Echangeur de chaleur selon l'une des revendications 9 à 12, caractérisé en ce que les ailettes (40) possèdent une orientation sensiblement verticale. 13. Heat exchanger according to one of claims 9 to 12, characterized in that the fins (40) have a substantially vertical orientation.
14. Echangeur de chaleur selon l'une des revendications 9 à 13, caractérisé en ce que le circuit de condensation (25,35) comprend au moins une nappe de tube qui forme la première nappe de tube en partant du bas de l'échangeur. 14. Heat exchanger according to one of claims 9 to 13, characterized in that the condensation circuit (25,35) comprises at least one tube ply which forms the first ply of tube from the bottom of the exchanger .
EP09772753A 2008-07-03 2009-07-03 Facility for cooling at least one item of furniture and/or a refrigerating chamber and for heating at least one room, and air heat exchanger for this facility Not-in-force EP2310769B1 (en)

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PL09772753T PL2310769T3 (en) 2008-07-03 2009-07-03 Facility for cooling at least one item of furniture and/or a refrigerating chamber and for heating at least one room, and air heat exchanger for this facility

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FR0854525A FR2933484A1 (en) 2008-07-03 2008-07-03 METHOD OF REFRIGERATING AT LEAST ONE FURNITURE AND / OR A REFRIGERATING CHAMBER AND HEATING AT LEAST ONE LOCAL, INSTALLATION AND HEAT EXCHANGER FOR ITS IMPLEMENTATION
PCT/FR2009/051311 WO2010001071A2 (en) 2008-07-03 2009-07-03 Facility for cooling at least one item of furniture and/or a refrigerating chamber and for heating at least one room, and air heat exchanger for this facility

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ATE543059T1 (en) 2012-02-15
PL2310769T3 (en) 2012-05-31
EP2310769B1 (en) 2012-01-25
WO2010001071A2 (en) 2010-01-07
US20110094250A1 (en) 2011-04-28
FR2933484A1 (en) 2010-01-08
DK2310769T3 (en) 2012-02-20
WO2010001071A3 (en) 2010-04-08

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