Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
  • B60H1/00—Heating, cooling or ventilating [HVAC] devices
  • B60H1/00492—Heating, cooling or ventilating [HVAC] devices comprising regenerative heating or cooling means, e.g. heat accumulators
  • B60H1/005—Regenerative cooling means, e.g. cold accumulators
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
  • B60H1/00—Heating, cooling or ventilating [HVAC] devices
  • B60H1/32—Cooling devices
  • B60H1/3204—Cooling devices using compression
• • 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
  • F25B40/00—Subcoolers, desuperheaters or superheaters
• • 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
  • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B60—VEHICLES IN GENERAL
  • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
  • B60H1/00—Heating, cooling or ventilating [HVAC] devices
  • B60H1/32—Cooling devices
  • B60H1/3204—Cooling devices using compression
  • B60H1/3205—Control means therefor
  • B60H1/322—Control means therefor for improving the stop or idling operation of the engine
• • 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 invention relates to a thermal system for a motor vehicle, in particular an air-conditioning system for a motor vehicle.
• ventilating, heating and / or air-conditioning apparatus for a passenger compartment of a motor vehicle generally comprise a closed thermodynamic loop comprising at least, according to the direction of circulation of a cooling fluid, an evaporator on the air, a compressor, a condenser and a valve or expansion device.
• a closed thermodynamic loop comprising at least, according to the direction of circulation of a cooling fluid, an evaporator on the air, a compressor, a condenser and a valve or expansion device.
• the air is cooled by passing on the evaporator before being expelled to the passenger compartment by pipes.
• the ventilation devices are poor, or do not work at all.
• the pressure level prevailing in the storage devices is equivalent to that of the evaporator at its pressure drop, which is penalizing during the storage phase.
• the subject of the invention is thus a thermal system for a motor vehicle, in particular an air-conditioning system for a motor vehicle, this system comprising:
• a main thermal circuit comprising a compressor arranged to compress a refrigerant circulating in this circuit and an evaporator arranged to cool a flow of air flowing in contact with the evaporator, this cooling being obtained by heat exchange between the air flow to cool and refrigerant circulating in this evaporator,
• a secondary thermal device comprising a frigory storage unit, a device creating a detent between the outlet of the evaporator and the inlet of the frigory storage unit, and a pump, this secondary device being arranged in a manner:
• the invention which is in particular to prevent the exchange of refrigerant between the secondary thermal device and the main thermal circuit during normal operation, this normal operation is not affected by an unwanted passage of refrigerant through the cold storage unit, which would have had the effect of reducing the performance of air conditioning.
• This also makes it possible not to degrade the performance of the storage unit because it is maintained at a pressure lower than that of the evaporator when it is filled with frigories.
• the pump is arranged to be bypassed when the frigory storage unit receives frigories of the refrigerant which passes through it. The pump is then stopped.
• the secondary thermal device comprises at least a first bypass valve arranged to selectively prevent refrigerant circulation between the frigory storage unit and the main thermal circuit in normal mode.
• the secondary thermal device is arranged so that the flow direction of the refrigerant in the cold storage unit is reversed respectively: when this frigory storage unit receives frigories of the refrigerant which passes through it and
• the first bypass valve is a 3-way valve arranged at a junction between the secondary thermal device and the main thermal circuit.
• This 3-way valve can be replaced by two 2-way valves, if desired.
• the secondary thermal device comprises a second bypass valve, in particular a two-way valve, arranged to be traversed selectively by refrigerant which flows from the evaporator of the main thermal circuit to the storage unit of frigories to allow a relaxation that will transfer frigories of the refrigerant to the storage unit of frigories in storage mode.
• the secondary thermal device comprises a secondary branch on which is disposed this second bypass valve, this branch making fluid junction with a primary branch on which are arranged the cold storage unit and the pump.
• this junction between the primary branch and the secondary branch is disposed between the frigory storage unit and the pump.
• the secondary thermal device comprises a non-return valve disposed on the primary branch downstream of the pump. This valve or non-return valve can be integrated in the pump.
• the secondary thermal device is arranged so that:
• the cold storage unit In operating mode of the main thermal circuit without use of the secondary thermal device, the cold storage unit is bypassed and the pump is stopped.
• the cold storage unit In operating mode of the main thermal circuit with charging in frigories of the cold storage unit of the secondary thermal device by expansion through the expansion device, the cold storage unit is traversed by refrigerant and the pump is when stationary, the storage unit and the evaporator being preferably in series,
• the compressor In operating mode of the secondary thermal device to return frigories to the evaporator of the main thermal circuit, the compressor is stopped or runs at low speed, the refrigerant storage unit is traversed by refrigerant and the pump is running,
• cold boost mode namely in operating mode of the secondary thermal device to restore frigories to the evaporator of the main thermal circuit, whose compressor operates at low or high load, the cold storage unit is refrigerant and the pump is running.
• the secondary thermal device is arranged so that the flow direction of the refrigerant in the cold storage unit is the same respectively:
• a non-return valve is disposed at the outlet of the frigory storage unit.
• two bypass valves are provided.
• one of the bypass valves is disposed at the entrance of the frigory storage unit, on a primary branch, and allows relaxation.
• the other of the bypass valves is arranged between the evaporator and the pump, on a secondary branch to allow the bypass, or bypass, of the cold storage unit in normal mode .
• the two bypass valves can be replaced by a 3-way valve.
• the conduit leading the refrigerant flow from the cold storage unit to the pump can be located downstream or upstream of the non-return valve thus allowing the refrigerant pump to be arranged. directly at the outlet of the frigory storage unit.
• the frigory storage unit is arranged to be at a lower pressure than the evaporator.
• the second bypass valve disposed between the evaporator and the frigory storage unit is arranged to generate two pressure levels respectively for the evaporator and the storage unit.
• this second bypass valve may be a variable passage section valve, a single passage section valve or a three way valve.
• This valve can be an on / off valve that precedes a calibrated orifice. To maintain the comfort of passenger unchanged, the pressure must remain stable at the evaporator.
• an expansion device either thermostatic or electrical, is arranged upstream of the evaporator to generate an expansion of the refrigerant before it passes through the evaporator.
• the opening of this expansion device is controlled by overheating at the inlet of an internal heat exchanger or at the compressor inlet or at the outlet of the evaporator.
• the cold storage unit is arranged inside an HVAC or outside an HVAC.
• the system comprises an air path disposed parallel to the evaporator, a path through which air can circulate bypassing the evaporator, and this air can, at the exit of this path, be mix with air from the evaporator.
• the passage section of this track is particularly controlled by a component.
• This flap is in particular in parallel with the evaporator.
• the position of the valve downstream of the evaporator can help to adjust the air temperature at the evaporator outlet by mixing the cold air from the evaporator and the warmer air coming from the track. aforementioned air.
• the valve may be for example a simple closing valve with a fixed diameter.
• the 2-way valve is, for example, arranged to generate a fixed pressure drop so as to protect the evaporator from the formation of ice.
• the valve protects the evaporator from icing, and the flap regulates the air temperature at the outlet of the evaporator.
• FIG. 1 illustrates, schematically and partially, a first embodiment of the system according to the invention
• FIGS. 2 to 4 illustrate the system of FIG. 1 during different modes of operation
• FIG. 5 illustrates, schematically and partially, a second embodiment of the system according to the invention
• FIG. 6 schematically and partially illustrates a third embodiment of the system according to the invention
• FIG. 7 illustrates an operation of the system of FIG.
• FIGS. 2a, 3a and 4a are Mollier diagrams corresponding to the operating phases of FIGS. 2, 3 and 4, respectively,
• FIG. 1 represents an air conditioning system 1 which comprises, according to the direction of closed-circuit circulation of a refrigerant such as R134A: a compressor 2, a condenser 3, a storage bottle 4, an internal heat exchanger 5, an expansion or expansion device 6 and an evaporator on the air 10. These components form a main thermal circuit 20.
• a refrigerant such as R134A: a compressor 2, a condenser 3, a storage bottle 4, an internal heat exchanger 5, an expansion or expansion device 6 and an evaporator on the air 10.
• the evaporator 10 is placed in an air circulation duct leading to different zones of the passenger compartment to be cooled or heated. such as an area for defogging the windshield, an aeration zone and a foot zone.
• the compressor 2 is arranged to compress the refrigerant circulating in this circuit 20 and the evaporator 10 is arranged to cool a flow of air flowing in contact with the evaporator, this cooling being obtained by heat exchange between the air flow. to cool and refrigerant circulating in this evaporator.
• the system 1 further comprises a secondary thermal device 21 comprising a frigory storage unit 22, an expansion or pressure loss device 27 and a pump 23, this secondary device being arranged in such a way as:
• the storage unit 22 can be maintained at a pressure lower than that of the evaporator when it is filled with frigories,
• Figures 2a, 3a and 4a are Mollier diagrams corresponding to the phases of operation of Figures 2, 3 and 4, respectively.
• the secondary thermal device 21 comprises a first bypass valve 25 or 35 or 37, arranged to selectively prevent refrigerant circulation between the cold storage unit 22 and the main thermal circuit 20, in normal mode.
• the secondary thermal device 21 is arranged so that:
• the pump 23 In the frigory storage phase in the frigory storage unit 22 (FIG. 3), the pump 23 is arranged to be bypassed and is then stopped.
• the secondary thermal device 21 is arranged so that the direction of circulation of the refrigerant in the frigory storage unit 22 is reversed respectively:
• this frigory storage unit 22 receives frigories of the refrigerant which passes through it (phase of storage of frigories illustrated in FIG. 3) and
• the first bypass valve 25 is a 3-way valve arranged at a junction between the secondary thermal device 21 and the main thermal circuit 20.
• valve 25 prevents the flow to the secondary thermal device 21 which is not used.
• the valve 25 allows circulation of the frigory storage unit 22 to the compressor 2.
• the valve 25 allows the evaporator 10 to be circulated to the cold storage unit 22.
• the secondary thermal device 21 comprises a second bypass valve 27, which is a two-way valve, arranged to be selectively traversed by refrigerant which flows from the evaporator 10 of the main thermal circuit to the frigory storage unit 22 to enable refrigerants to be transferred from the refrigerant to the frigory storage unit via a refrigerant. relaxation in this valve.
• the valve 27 is blocking in the operating phases of Figures 2 and 4, and passing in the operating phase of Figure 3.
• the second bypass valve 27 is arranged to generate two pressure levels respectively for the evaporator 10 and the storage unit 22.
• This second bypass valve may be a variable flow section valve, a single passage section valve or a 3-way valve (35b).
• the secondary thermal device 21 comprises a secondary branch 28 on which this second bypass valve 27 is arranged, this branch 28 making a fluid junction 30 with a primary branch 29 on which the frigory storage unit 22 and the pump 23 are arranged.
• This junction 30 between the primary branch 28 and the secondary branch 29 is arranged between the frigory storage unit 22 and the pump 23.
• the secondary thermal device 21 comprises a non-return valve 31 disposed on the primary branch 29 downstream of the pump 23.
• a non-return valve 31 disposed on the primary branch 29 downstream of the pump 23.
• the secondary thermal device 21 is arranged such that the direction of circulation of the refrigerant in the frigory storage unit 22 is the same, respectively:
• this frigory storage unit 22 restores frigories to the refrigerant that passes through it.
• bypass and expansion valves 35 is disposed at the inlet of the cold storage unit 22, on a primary branch 29.
• the other of the bypass valves 36 is disposed between the evaporator
• valves 35 and 36 can be replaced by a 3-way valve 35b (see Figure 5a).
• a check valve 37 is disposed at the outlet of the frigory storage unit 22.
• the cold storage unit 22 is arranged to be at a lower pressure than that of the evaporator.
• An expansion device 39 is arranged upstream of the evaporator 10 to generate an expansion of the refrigerant before it passes through the evaporator 10.
• the frigory storage unit 22 is arranged inside an HVAC or outside an HVAC.
• the system comprises an air channel 40 arranged parallel to the evaporator 10, a channel through which air can circulate bypassing the evaporator 10, and this air can, on leaving in this way, mix with the air coming from the evaporator.
• the position of the valve 27 downstream of the evaporator can help to adjust the temperature of the air at the outlet of the evaporator by mixing the cold air coming from the evaporator and the warmer air coming from the evaporator. see above air. This is advantageous during the frigory storage phase.
• the valve may be for example a simple closing valve with a fixed diameter.
• the 2-way valve referenced 27 is for example arranged to generate a fixed pressure drop so as to protect the evaporator from ice formation.
• the refrigerant may be a material, in this case a fluid, with a phase change for working in latent heat in order to reduce the necessary mass and to limit the temperature variations of the storage.
• the refrigerant is a two-phase fluid type R134a or 1234yf.
• the storer may contain a phase change material to limit temperature variations.
• the valves 27 or 35 provide an intermediate expansion so that the pressure of the compressor and that of the storage unit are different.
• the duct leading refrigerant flow of the frigory storage unit 22 to the pump 23 may be located downstream or upstream of the check valve or check valve 37 thus allowing the refrigerant pump to be disposed directly at the outlet of the frigory storage unit.

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Air-Conditioning For Vehicles (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=57121408

Family Applications (1)

Country Status (3)

Families Citing this family (2)

Family Cites Families (8)

• 2016
  • 2016-08-26 FR FR1657952A patent/FR3055251B1/fr not_active Expired - Fee Related
• 2017
  • 2017-08-22 EP EP17764427.5A patent/EP3504075A1/de not_active Withdrawn
  • 2017-08-22 WO PCT/FR2017/052255 patent/WO2018037186A1/fr unknown

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