EP2894419B1 - Dispositif de climatisation d'un compartiment, notamment pour un véhicule ferroviaire, et procédé de dégivrage du dispositif - Google Patents

Dispositif de climatisation d'un compartiment, notamment pour un véhicule ferroviaire, et procédé de dégivrage du dispositif Download PDF

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EP2894419B1
EP2894419B1 EP15150505.4A EP15150505A EP2894419B1 EP 2894419 B1 EP2894419 B1 EP 2894419B1 EP 15150505 A EP15150505 A EP 15150505A EP 2894419 B1 EP2894419 B1 EP 2894419B1
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Prior art keywords
branch
primary
heat
circuit
heat exchanger
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EP15150505.4A
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German (de)
English (en)
French (fr)
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EP2894419A1 (fr
Inventor
Rami Abou Eid
Josselin Chan
Philippe Chevalier
Francis Mortreux
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Alstom Transport Technologies SAS
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Alstom Transport Technologies SAS
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Priority to PL15150505T priority Critical patent/PL2894419T3/pl
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    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61D—BODY DETAILS OR KINDS OF RAILWAY VEHICLES
    • B61D27/00—Heating, cooling, ventilating, or air-conditioning
    • B61D27/0018—Air-conditioning means, i.e. combining at least two of the following ways of treating or supplying air, namely heating, cooling or ventilating
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/06—Removing frost
    • 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
    • F25B2400/06—Several compression cycles arranged in parallel
    • F25B2400/061—Several compression cycles arranged in parallel the capacity of the first system being different from the second
    • 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
    • F25B2400/24—Storage receiver heat

Definitions

  • the present invention relates to a device for air conditioning a compartment, in particular for a rail vehicle, and a method for defrosting such a device.
  • An air conditioning device for a compartment comprising a heat pump circuit
  • Said heat pump circuit conventionally comprises a first heat exchanger with the air from the compartment, a compressor, a second heat exchanger with outside air, and an expansion valve, arranged in series in a closed circuit to form a loop. .
  • a refrigerant circulates in this heat pump circuit, and exchanges heat, on the one hand with the air in the compartment in the first heat exchanger, and on the other hand with the outside air in the second heat exchanger. heat.
  • each heat exchanger has fins increasing the exchange surface with the air.
  • the humidity contained in the outside air can be deposited on the fins of the second heat exchanger in the form of frost. It then happens that this frost fills the spaces between the fins, then covers the second heat exchanger with a layer of frost capable of obstructing the passage of air. In this case, the performance of the heat pump circuit is greatly reduced.
  • a known solution for ensuring the defrosting of the second heat exchanger consists in reversing the cycle of the heat pump, so that the refrigerant takes heat from the first heat exchanger, and supplies heat to the second heat exchanger in such a way. to melt the frost.
  • the thermal comfort inside the compartment may decrease, since the heat pump circuit takes heat from this compartment via the first heat exchanger.
  • an electric heater is generally activated to compensate for this heat withdrawal.
  • a known solution provides for a thermal storage tank connected to the heat pump circuit, intended to promote defrosting.
  • the heat is taken from the thermal storage tank rather than from the air in the compartment.
  • the compartment is no longer heated anyway during defrosting, which can lead to a reduction in thermal comfort in this compartment.
  • such a device generally requires oversized components to perform satisfactorily.
  • such a solution is also not very advantageous.
  • the object of the invention is in particular to remedy these drawbacks, by providing an air conditioning device allowing defrosting of the external heat exchanger without reducing the thermal comfort in the compartment, and this without requiring the use of an electric heater. additional.
  • document JP 64-10062 A and also the document JP 2002 327968 A describe an air conditioning device according to the preamble of claim 1.
  • the subject of the invention is in particular an air conditioning device for a compartment, according to claim 1. Thanks to the two heat pump circuits, both connected to the thermal storage tank, and having independent operations, it is possible to provide numerous advantageous operating modes.
  • the thermal storage tank can be recharged with heat by one of the heat pump circuits, while the other heat pump circuit performs the heating of the compartment.
  • the presence of the thermal storage tank has no effect on the thermal comfort inside the compartment.
  • said other circuit operates in a configuration for heating the compartment and for storing heat in the storage tank, in which a refrigerant circulating in this circuit takes heat from the second heat exchanger of this circuit and restores heat from 'on the one hand to the first heat exchanger of this circuit, and on the other hand to the storage tank.
  • the figure shows an air conditioning device 10 for a compartment, in particular for a rail vehicle.
  • the term “compartment” covers any enclosed space that can be air-conditioned, for example a passenger compartment of a rail vehicle, a cockpit of a rail vehicle, a passenger compartment of a motor vehicle, an aeronautical or maritime vehicle compartment. , or a room in a building.
  • the air conditioning device 10 comprises two heat pump circuits, namely a primary circuit 12 and a secondary circuit 12 'of similar heat pump.
  • the primary heat pump circuit 12 comprises, conventionally, a first primary heat exchanger 14 with the air from the compartment, a primary compressor 16, a second primary heat exchanger 18 with outside air, and a device primary expansion valve 20.
  • a primary refrigerant circulates in this primary circuit 12.
  • the first primary heat exchanger 14 is equipped with a first primary ventilation device 15, able to generate an air flow passing through this first primary heat exchanger 14.
  • the second primary heat exchanger 18 is equipped with a second primary ventilation device 19, suitable for generating an air flow passing through this second primary heat exchanger 18.
  • This primary heat pump circuit 12 is advantageously reversible, that is to say that it can be used to increase or to reduce the temperature in the compartment.
  • the air in the compartment can form a hot source or a cold source of the heat pump, depending on its mode of operation.
  • the structure of the primary circuit 12, which will be described below, is suitable for such a reversible operation.
  • the primary circuit 12 comprises a first branch 22, connected to the first primary heat exchanger 14, a second branch 24 extending between the first primary heat exchanger 14 and the primary expansion device 20, a third branch 26, s 'extending between the primary expansion device 20 and the second primary heat exchanger 18, and a fourth branch 28 connected to the second primary heat exchanger 18.
  • the primary circuit 12 comprises a primary compressor branch 30, on which the primary compressor 16 is arranged.
  • This primary compressor branch 30 extends between an inlet part 30A and an outlet part 30B.
  • the primary refrigerant can only flow in one direction in the primary compressor 16, therefore in one direction in the primary compressor branch 30.
  • the primary circuit 12 comprises a primary inversion device 32, suitable for connecting, alternately, said input part 30A to the first branch 22 and said output part 30B to the fourth branch 28, or said input part 30A to the fourth branch 28 and said outlet portion 30B to the first branch 22.
  • the primary refrigerant can flow from the primary compressor 16 to the first one. primary heat exchanger 14 or from the primary compressor 16 to the second primary heat exchanger 18.
  • each of these first 32A and second 32B three-way valves is suitable for allowing fluid communication of the inlet part 30A, respectively the outlet part 30B, with the first 22 or the fourth 28 branch.
  • These first 32A and second 32B valves are controlled so that when the inlet part 30A is connected to one of the first 22 or fourth 28 branches, then the outlet part 30B is connected to the other of these first 22. or fourth 28 branch.
  • the primary compressor branch 30 comprises a conventional buffer accumulator 34.
  • the primary expansion device 20 since an expansion valve also operates only in one direction of circulation of refrigerant, the primary expansion device 20 also has a reversible structure.
  • the primary regulator device 20 comprises a first primary regulator 34 carried by a first regulator branch 36, having an inlet connected to the second branch 24 and an outlet connected to the third branch 26, and a second primary regulator 38, carried by a second regulator branch 40, parallel to the first regulator branch 36, said second primary regulator 38 having an inlet connected to said third branch 26 and an outlet connected to said second branch 24.
  • each regulator branch 36, 40 advantageously comprises a respective non-return valve 42, 44, arranged in series with the first 34 or second 38 corresponding primary regulator, and oriented in the same direction as this first 34 or second 38 corresponding primary regulator.
  • this refrigerant passes through one or the other of the first 36 and second 40 branches of the expansion valve.
  • a thermal storage tank 46 is connected to the primary circuit 12, in parallel with said first primary heat exchanger 14.
  • the thermal storage tank 46 comprises an enclosure 48 filled with a fluid, in particular a liquid, for thermal storage, and a first hollow heat exchange element 50, housed in the enclosure 48, and communicating with the circuit heat pump primary 12.
  • the first hollow element 50 is connected on the one hand to said first branch 22 of the primary circuit 12 by means of a first primary duct 52, and on the other hand connected to said second branch 24 of the primary circuit. 12 via a second primary duct 54.
  • the first primary duct 52 is connected to the first branch 22 at a first primary branch 56, and the second primary duct 54 is connected to the second branch 24 at a second primary branch 57.
  • the first branch 22 comprises a first primary valve 58, in particular a solenoid valve , arranged between said first primary branch 56 and the first primary exchanger 14, and the first primary duct 52 comprises a second primary valve 60, in particular a solenoid valve.
  • the thermal storage tank 46 is housed in the compartment, and it is able to exchange heat with the air in this compartment.
  • the thermal storage tank 46 is equipped with a ventilation device 62, suitable for generating an air flow passing through this thermal storage tank 46, in order to promote the exchange of heat between the air in the compartment this storage tank. thermal storage 46.
  • the secondary heat pump circuit 12 will now be described below.
  • the secondary heat pump circuit 12 ' comprises, conventionally, a first secondary heat exchanger 14' with the air from the compartment, a secondary compressor 16 ', a second secondary heat exchanger 18' with outside air , and a secondary pressure reducing device 20 '.
  • a secondary refrigerant circulates in this secondary circuit 12 '.
  • the first secondary heat exchanger 14 ' is equipped with a first secondary ventilation device 15', capable of generating an air flow passing through this first secondary heat exchanger 14 '.
  • the second secondary heat exchanger 18 ' is equipped with a second secondary ventilation device 19', capable of generating an air flow passing through this second secondary heat exchanger 18 '.
  • This secondary heat pump circuit 12 ' is advantageously reversible, that is to say it can be used to increase or to reduce the temperature in the compartment.
  • the air in the compartment can form a hot source or a cold source of the heat pump, depending on its mode of operation.
  • the structure of the secondary circuit 12 ' which will be described below, is suitable for such reversible operation.
  • the secondary circuit 12 ' comprises a first branch 22', connected to the first secondary heat exchanger 14 ', a second branch 24' extending between the first secondary heat exchanger 14 and the secondary expansion device 20 ', a third branch 26 ', extending between the secondary expansion device 20' and the second secondary heat exchanger 18 ', and a fourth branch 28' connected to the second secondary heat exchanger 18 '.
  • the secondary circuit 12 ' comprises a secondary compressor branch 30', on which the secondary compressor 16 'is arranged.
  • This secondary compressor branch 30 ' extends between an inlet part 30A' and an outlet part 30B '.
  • the primary refrigerant can circulate only in one direction in the secondary compressor 16 ', therefore in only one direction in the secondary compressor branch 30'.
  • the secondary circuit 12 ' comprises a secondary inversion device 32', suitable for connecting, alternately, said input part 30A 'to the first branch 22' and said output part 30B 'to the fourth branch 28', or said inlet portion 30A 'to the fourth branch 28' and said outlet portion 30B 'to the first branch 22'.
  • the secondary refrigerant can circulate from the secondary compressor 16' to the first secondary heat exchanger 14 'or from the secondary compressor 16' to second secondary heat exchanger 18 '.
  • each of these first 32A 'and second 32B' three-way valves is suitable for allowing fluid communication of the inlet part 30A ', respectively the outlet part 30B', with the first 22 'or the fourth 28'. plugged.
  • These first 32A 'and second 32B' valves are controlled so that when the inlet part 30A 'is connected to one of the first 22' or fourth 28 'branch, then the outlet part 30B' is connected to the one. 'other of these first 22' or fourth 28 'branch.
  • the secondary compressor branch 30 ' comprises a conventional buffer accumulator 34'.
  • the secondary expansion device 20 ′ since an expansion valve also only operates in one direction of circulation of refrigerant, the secondary expansion device 20 ′ also has a reversible structure.
  • the secondary regulator device 20 ' comprises a first secondary regulator 34' carried by a first regulator branch 36 ', having an inlet connected to the second branch 24' and an outlet connected to the third branch 26 ', and a second secondary regulator 38 ', carried by a second regulator branch 40', parallel to the first regulator branch 36 ', said second secondary regulator 38' having an inlet connected to said third branch 26 'and an outlet connected to said second branch 24 '.
  • each regulator branch 36 ', 40' advantageously comprises a respective non-return valve 42 ', 44', arranged in series with the first 34 'or second 38' corresponding secondary regulator, and oriented in the same direction as this first 34 'or second 38' corresponding secondary regulator.
  • this refrigerant passes through one or the other of the first 36' and second 40 'of the expansion valve branches.
  • the thermal storage tank 46 is also connected to the secondary circuit 12 ', in parallel with said first secondary heat exchanger 14'.
  • thermal storage tank 46 a second hollow heat exchange element 64, housed in the enclosure 48, and communicating with the secondary heat pump circuit 12 '.
  • the second hollow element 64 is connected on the one hand to said first branch 22 'of the secondary circuit 12' by means of a first secondary duct 52 ', and on the other hand connected to said second branch 24 'of the secondary circuit 12 via a second secondary duct 54'.
  • the first secondary duct 52 ' is connected to the first branch 22' at a first secondary branch 56 ', and the second secondary duct 54' is connected to the second branch 24 'at a second secondary branch 57'.
  • the second branch 24' comprises a first secondary valve 58 ', in particular a solenoid valve, arranged between said second secondary branch 57 'and the first secondary exchanger 14', and the second secondary duct 54 'comprises a second secondary valve 60', in particular a solenoid valve.
  • each heat pump circuit 12, 12 will be described. More particularly, the various operating configurations of the primary circuit 12 will be described, the operating configurations of the secondary circuit 12 being identical.
  • a first operating configuration of circuit 12 is a heating configuration of the compartment.
  • the inversion device 32 is controlled to connect the input part 30A of the compressor branch 30 to the fourth branch 28 and to the output part 30B of this compressor branch 30 to the first branch. 22.
  • first solenoid valve 58 is open to allow the passage of refrigerant from the compressor 16 to the first heat exchanger 14.
  • the second solenoid valve 60 is closed to prevent the circulation of the refrigerant to the heat storage tank 46.
  • the circuit 12 operates like a conventional heat pump. Indeed, in a manner known per se, the refrigerant leaves hot from the compressor 16, then circulates through the first branch 22 to the first heat exchanger 14, where the refrigerant transfers heat to the air in the compartment.
  • the refrigerant then circulates through the second branch 24, then through the expansion valve branch 36 corresponding to this direction of circulation, where the refrigerant is further cooled when its pressure decreases in the expansion valve 34.
  • the refrigerant then circulates, through the third branch 26, to the second heat exchanger 18 to take heat there from the outside air.
  • the thus heated refrigerant then circulates in the fourth branch 28 to the compressor 16, in which it is compressed so as to increase its pressure, and therefore its temperature. The cycle then continues as described previously.
  • a second operating configuration of circuit 12 is a heat storage configuration in heat storage tank 46.
  • the first solenoid valve 58 of circuit 12 is closed, and the second solenoid valve 60 is open.
  • the refrigerant leaving the compressor 16 circulates to the heat storage tank 46, where it gives up heat to the heat storage liquid.
  • circuit 12 in this storage configuration is similar to that of the heating configuration described above, except that the refrigerant transfers its heat to the heat storage liquid rather than to the air in the compartment. .
  • a third operating configuration of circuit 12 is a heating and storage configuration.
  • the first 58 and second 60 solenoid valves are open.
  • the refrigerant leaving the compressor 16 separates into two separate flows at the first branch 56, to circulate on the one hand to the heat storage tank 46 and on the other hand to the first heat exchanger 14.
  • part of the refrigerant leaving the compressor 16 circulates to the heat storage tank 46, where it transfers heat to the heat storage liquid, and another part of the refrigerant leaving the compressor 16 circulates to first heat exchanger 14, where it transfers heat to the air in the compartment.
  • the compartment is heated less than in the first heating configuration, and the tank is heated less than in the second heat storage configuration.
  • a fourth operating configuration of circuit 12 is a configuration for cooling the air in the compartment. Indeed, thanks to the inversion device 32, the heat pump circuit 12 is reversible.
  • the inversion device 32 is controlled so that the inlet part 30A of the compressor branch 30 is connected to the first branch 22 and the outlet part 30B of this compressor branch 30 is connected to the fourth branch 28.
  • the refrigerant leaving the compressor 16 circulates to the second heat exchanger 18, where it transfers heat to the outside air.
  • the refrigerant thus cooled then circulates through the third branch 26, then through the expansion valve branch 40 corresponding to this direction of operation, where the refrigerant is further cooled when its pressure decreases in the expansion valve 38.
  • the refrigerant then circulates through the second branch 24 to the first heat exchanger 14, where it takes heat from the air in the compartment.
  • the refrigerant finally circulates to the compressor 16, where a new cycle can begin.
  • a fifth operating configuration of circuit 12 is a cold storage configuration in heat storage tank 46.
  • the first solenoid valve 58 of circuit 12 is closed, and the second solenoid valve 60 is open.
  • the refrigerant leaving the expansion valve 38 circulates to the heat storage tank 46, where it takes heat from the heat storage liquid.
  • circuit 12 in this cold storage configuration is similar to that of the cooling configuration described previously, except that the refrigerant takes heat from the heat storage liquid rather than from the heat storage liquid. compartment air.
  • this fifth operating configuration can also be used for defrosting the second heat exchanger 18.
  • the heat taken from the heat storage liquid can be returned to the second heat exchanger 18 to cause the melting of the heat exchanger. frosted.
  • a sixth operating configuration of circuit 12 is a cooling and cold storage configuration.
  • the first 58 and second 60 solenoid valves are open.
  • the refrigerant leaving the expansion valve 38 separates into two separate flows at the second branch 57, to circulate on the one hand to the heat storage tank 46 and on the other hand to the first heat exchanger 14.
  • the compartment is cooled less than in the fourth cooling configuration, and the tank is cooled less than in the fifth cold storage configuration.
  • a first mode of operation of the air conditioning device 10 is used in the event of extreme cold, when the demand for heating in the compartment is high.
  • the primary 12 and secondary 12 'circuits are both in their first compartment heating configuration.
  • the two heat pump circuits 12 and 12 'thus operate in parallel, thus allowing more efficient heating than a single heat pump circuit.
  • a second operating mode of the air conditioning system is used when the demand for heating in the compartment is moderate.
  • This third operating mode is preferred to the second operating mode, when the heat demand in the compartment is the same, but it is desired to store heat in the tank 46.
  • the compartment is heated more than in the third operating mode, but the heat storage liquid is heated less than in this third operating mode.
  • a fifth operating mode is used when the heat demand in the compartment is even lower.
  • the corresponding ventilation device 62 is activated so that the heat storage liquid transfers its heat to the air in the compartment.
  • This sixth operating mode can only be used when the heat storage liquid has been heated beforehand, for example by one of the third to fifth operating modes described above.
  • the heat stored in the tank 46 is delivered in parallel with the heating of the compartment by one, the other or both heat pump circuits.
  • An eighth operating mode corresponds to the defrosting of one of the second outdoor exchangers 18, 18 ', and this without heat being taken from the air in the compartment.
  • the circuit 12, 12 ', the second heat exchanger 18, 18' of which requires defrosting operates in the fifth cold storage configuration.
  • the refrigerant takes heat from the storage tank 46, rather than from the air in the compartment, and returns this heat to said second heat exchanger 18, 18 ', which makes it possible to perform its defrost.
  • the other heat pump circuit 12, 12 operates in the first heating configuration of the compartment, as described previously.
  • the thermal comfort in the compartment is identical to that which would be obtained with a conventional air conditioning device comprising only one heat pump circuit in the heating configuration.
  • the ventilation devices 15, 19 of the first 14 and of the second 18 heat exchangers are deactivated.
  • it is not desirable to ventilate in the compartment during defrosting in order to avoid a reduction in the sensation of heat felt by the occupants of the compartment.
  • the air conditioning device 10 also allows the air in the compartment to be cooled. Indeed, thanks to the inversion device 32, each heat pump circuit is reversible.
  • a fourteenth operating mode one or the other or both heat pump circuits 12, 12 'operates in the compartment air cooling configuration, and the storage tank ventilation device 46 is activated. so that the storage liquid also draws heat from the air in the compartment.
  • This operating mode can only be used when the heat storage liquid has been cooled beforehand, in particular by one of the eleventh to thirteenth operating modes described above.
  • the two circuits 12, 12 ' are deactivated, for example for reasons of energy saving, and only the ventilation device of the reservoir 46 is activated, so that the storage liquid draws heat from the air in the compartment.
  • This operating mode can only be used when the heat storage liquid has been cooled beforehand, in particular by one of the eleventh to thirteenth operating modes described above.
  • the ventilation devices 15, 15 'linked to the first heat exchangers 14, 14' are activated while the two heat pump circuits 12, 12 'are deactivated, in order to provide a cooling function. ventilation in the compartment.
  • a ventilation function can be used alone, or in combination with the activation of the ventilation device of the reservoir 46 as in the fifteenth operating mode described above.
  • the air conditioning device 10 could include more than two heat pump circuits, all connected to the same storage tank 46.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
EP15150505.4A 2014-01-08 2015-01-08 Dispositif de climatisation d'un compartiment, notamment pour un véhicule ferroviaire, et procédé de dégivrage du dispositif Active EP2894419B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL15150505T PL2894419T3 (pl) 2014-01-08 2015-01-08 Urządzenie do klimatyzacji przedziału, w szczególności do pojazdu kolejowego, oraz sposób odszraniania urządzenia

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1450117A FR3016206B1 (fr) 2014-01-08 2014-01-08 Dispositif de climatisation d'un compartiment, notamment pour un vehicule ferroviaire

Publications (2)

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EP2894419A1 EP2894419A1 (fr) 2015-07-15
EP2894419B1 true EP2894419B1 (fr) 2020-12-16

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US (1) US9994238B2 (pl)
EP (1) EP2894419B1 (pl)
CA (1) CA2876724C (pl)
FR (1) FR3016206B1 (pl)
PL (1) PL2894419T3 (pl)

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JP5575192B2 (ja) * 2012-08-06 2014-08-20 三菱電機株式会社 二元冷凍装置
EP3098540B1 (en) * 2014-01-23 2020-10-07 Mitsubishi Electric Corporation Heat pump apparatus
DE212016000038U1 (de) * 2015-01-09 2017-08-11 Trane International Inc. Wärmepumpe
CN104807231A (zh) * 2015-05-12 2015-07-29 上海海洋大学 一种可切换双级和复叠的船用节能超低温制冷系统
FR3041288B1 (fr) * 2015-09-21 2019-01-25 Alstom Transport Technologies Dispositif perfectionne de climatisation, notamment pour un compartiment de vehicule ferroviaire
ITUA20162463A1 (it) * 2016-04-11 2017-10-11 Begafrost S R L Sistema di sbrinamento dell'evaporatore esterno per impianti a pompa di calore.
WO2017183160A1 (ja) * 2016-04-21 2017-10-26 三菱電機株式会社 排熱回収式空気調和装置
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US20150191182A1 (en) 2015-07-09
PL2894419T3 (pl) 2021-08-02
FR3016206B1 (fr) 2016-02-05
CA2876724A1 (fr) 2015-07-08
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US9994238B2 (en) 2018-06-12
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