EP3924674A1 - Dispositif de gestion thermique de véhicule automobile électrique ou hybride - Google Patents
Dispositif de gestion thermique de véhicule automobile électrique ou hybrideInfo
- Publication number
- EP3924674A1 EP3924674A1 EP20705430.5A EP20705430A EP3924674A1 EP 3924674 A1 EP3924674 A1 EP 3924674A1 EP 20705430 A EP20705430 A EP 20705430A EP 3924674 A1 EP3924674 A1 EP 3924674A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- refrigerant
- expansion device
- internal
- bifluid
- 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.)
- Pending
Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 250
- 239000012530 fluid Substances 0.000 claims abstract description 146
- 239000013529 heat transfer fluid Substances 0.000 claims abstract description 102
- 238000004378 air conditioning Methods 0.000 claims abstract description 59
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 51
- 238000010438 heat treatment Methods 0.000 claims abstract description 24
- 238000009423 ventilation Methods 0.000 claims abstract description 23
- 238000001816 cooling Methods 0.000 description 67
- 230000002441 reversible effect Effects 0.000 description 17
- 239000002826 coolant Substances 0.000 description 12
- 239000012071 phase Substances 0.000 description 11
- 239000007791 liquid phase Substances 0.000 description 8
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 239000003638 chemical reducing agent Substances 0.000 description 3
- 239000002274 desiccant Substances 0.000 description 3
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 2
- 238000007791 dehumidification Methods 0.000 description 2
- 238000005485 electric heating Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 1
- WGCNASOHLSPBMP-UHFFFAOYSA-N hydroxyacetaldehyde Natural products OCC=O WGCNASOHLSPBMP-UHFFFAOYSA-N 0.000 description 1
- 238000005191 phase separation Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
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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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
- F25B5/04—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in series
-
- 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
- B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
- B60H1/00278—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit for the battery
-
- 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
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H1/00885—Controlling the flow of heating or cooling liquid, e.g. valves or pumps
-
- 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
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H1/00899—Controlling the flow of liquid in a heat pump system
- B60H1/00921—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant does not change and there is an extra subcondenser, e.g. in an air duct
-
- 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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
-
- 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
- F25B6/00—Compression machines, plants or systems, with several condenser circuits
- F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
-
- 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
- B60H1/00271—HVAC devices specially adapted for particular vehicle parts or components and being connected to the vehicle HVAC unit
- B60H2001/00307—Component temperature regulation using a liquid flow
-
- 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
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H2001/00928—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising a secondary circuit
-
- 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
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H2001/00942—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising a plurality of heat exchangers, e.g. for multi zone heating or cooling
-
- 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
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H2001/00949—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising additional heating/cooling sources, e.g. second evaporator
-
- 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
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H2001/00957—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices comprising locations with heat exchange within the refrigerant circuit itself, e.g. cross-, counter-, or parallel heat exchange
-
- 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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
-
- 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
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0403—Refrigeration circuit bypassing means for the condenser
-
- 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
- F25B2400/04—Refrigeration circuit bypassing means
- F25B2400/0409—Refrigeration circuit bypassing means for the evaporator
Definitions
- the invention relates to the field of motor vehicles and more particularly to a thermal management device for an electric or hybrid motor vehicle.
- a thermal management device comprising an air conditioning circuit.
- a refrigerant fluid passes successively through a compressor, a first heat exchanger, called a condenser, placed in contact with a flow of air outside the motor vehicle to release heat, a device expansion valve and a second heat exchanger, called an evaporator, placed in contact with a flow of air inside the motor vehicle to cool it.
- indirect is meant here that the air conditioning circuit comprises two circulation loops for two distinct fluids (such as for example a refrigerant fluid and glycol water) in order to carry out the various heat exchanges.
- the air conditioning circuit thus comprises a first refrigerant fluid loop in which a refrigerant fluid circulates, a second heat transfer fluid loop in which a heat transfer fluid circulates, and a bifluid heat exchanger arranged jointly on the first refrigerant loop and on the second heat transfer fluid loop, so as to allow heat exchange between said loops.
- Such an air conditioning circuit allows use according to different operating modes.
- the thermal management of elements such as batteries and electronic components is carried out by a secondary thermal management loop.
- this architecture may not be sufficient to allow thermal comfort throughout the vehicle, in particular when the passenger compartment is large or when different temperatures are required in different areas of the passenger compartment.
- One of the aims of the present invention is therefore to at least partially remedy the drawbacks of the prior art and to provide an improved thermal management device allowing refined management of the temperature of the passenger compartment of the motor vehicle.
- the present invention therefore relates to a thermal management device comprising an indirect air conditioning circuit for a motor vehicle comprising:
- a first refrigerant fluid loop in which circulates a refrigerant fluid, said first refrigerant fluid loop comprising in the direction of circulation of the refrigerant fluid a compressor, a bifluid heat exchanger, a first expansion device, a first heat exchanger arranged within a first heating, ventilation and air conditioning device and intended to be crossed by a first flow of air inside the motor vehicle, a second expansion device, a second heat exchanger intended to be traversed by a flow of air outside the motor vehicle, and
- first bypass pipe connecting a first connection point disposed downstream of the first heat exchanger, between said first heat exchanger and the second heat exchanger, to a second connection point disposed downstream of the second heat exchanger, between said second heat exchanger and the compressor, said first bypass line comprising a first shut-off valve
- a second bypass pipe connecting a third connection point arranged upstream of the first expansion device between the compressor and said first expansion device, to a fourth connection point arranged on the first bypass pipe or upstream of the first heat exchanger internal heat between the second connection point and said first internal heat exchanger, said second bypass pipe comprising a third expansion device arranged upstream of a first cooler,
- the bifluid heat exchanger being arranged jointly on the one hand on the first loop of refrigerant fluid downstream of the compressor, between said compressor and the first expansion device, and on the other hand on the second loop of heat transfer fluid.
- the third bypass pipe connects a fifth connection point arranged downstream of the first expansion device, between said first expansion device and the first heat exchanger, to a sixth connection point arranged downstream of the first heat exchanger, between said first heat exchanger and the first bypass pipe.
- the third bypass line has a shut-off valve.
- the third bypass pipe connects a fifth connection point disposed upstream of the first expansion device, between the second bypass pipe and said first expansion device, to a sixth point of
- connection disposed downstream of the first heat exchanger, between said first heat exchanger and the first bypass pipe, said third bypass pipe comprising a fourth expansion device disposed upstream of the first additional heat exchanger.
- the fourth expansion device is a pressure reducer
- thermostatic whose thermostatic bulb is positioned at the outlet of the first additional heat exchanger.
- the fourth expansion device is an electronic expansion valve controlled by an electronic control unit.
- the second heat transfer fluid loop comprises:
- a first heat transfer fluid circulation pipe comprising a third heat exchanger arranged in the first heating, ventilation and air conditioning device and intended to be crossed by a first flow of air inside the motor vehicle, and connecting a first junction point arranged downstream of the bifluid heat exchanger and a second junction point arranged upstream of said bifluid heat exchanger,
- a second heat transfer fluid circulation pipe comprising a fourth heat exchanger intended to be traversed by a flow of air outside the motor vehicle, and connecting the first junction point disposed downstream of the bifluid heat exchanger and the second junction point disposed upstream of said bifluid heat exchanger, and
- a pump arranged downstream or upstream of the bifluid heat exchanger, between the first junction point and the second junction point.
- the second heat transfer fluid loop comprises a third heat transfer fluid circulation pipe comprising a second additional heat exchanger arranged in the second heating, ventilation and air conditioning device and connecting a third junction point arranged downstream of the first junction point, between said first junction point and the third heat exchanger, at a fourth junction point arranged downstream of the third heat exchanger, between said third heat exchanger and the second junction point.
- the first refrigerant fluid loop comprises a fourth circulation pipe connecting a seventh connection point arranged upstream of the second expansion device, between the first connection point and said second expansion device, to an eighth connection point disposed downstream of the second heat exchanger, between said second heat exchanger and the first internal heat exchanger, said fourth circulation pipe comprising a fifth expansion device disposed upstream of a fifth heat exchanger.
- the first refrigerant fluid loop comprises a fifth circulation pipe connecting a ninth connection point arranged downstream of the bifluid heat exchanger, between said bifluid heat exchanger and the first heat exchanger. internal, to a tenth connection point arranged upstream of the first internal heat exchanger, between said first internal heat exchanger and the ninth
- said fifth circulation pipe comprising a sixth heat exchanger intended to be traversed by an external air flow.
- FIG. 1 shows a schematic representation of an indirect reversible air conditioning circuit according to a first embodiment
- FIG. 2 shows a schematic representation of an indirect reversible air conditioning circuit according to a second embodiment
- FIG. 3 shows a schematic representation of an indirect reversible air conditioning circuit according to a third embodiment
- FIG. 4 shows a schematic representation of an indirect reversible air conditioning circuit according to a fourth embodiment
- FIG. 5 shows a schematic representation of an indirect reversible air conditioning circuit according to a fifth embodiment
- Figure 6 shows an expansion device according to an alternative embodiment
- FIG. 7 shows a schematic representation of the second heat transfer fluid loop of the indirect reversible air conditioning circuit of FIGS. 1 to 6, according to an alternative embodiment
- FIG. 8 shows a schematic representation of an indirect reversible air conditioning circuit according to a sixth embodiment
- Figure 9 shows the indirect reversible air conditioning circuit of Figure 2 according to a first cooling mode
- FIG. 10 shows the indirect reversible air conditioning circuit of FIG. 2 according to a second cooling mode
- FIG. 11 shows the indirect reversible air conditioning circuit of FIG. 2 according to a third cooling mode
- FIG. 12 shows the indirect reversible air conditioning circuit of FIG. 2 according to a fourth cooling mode
- FIG. 13 shows the indirect reversible air conditioning circuit of FIG. 2 according to a fifth cooling mode
- Figure 14 shows the indirect reversible air conditioning circuit of Figure 2 according to a sixth cooling mode
- FIG. 15 shows the indirect reversible air conditioning circuit of FIG. 2 according to a seventh cooling mode
- first element or second element as well as first parameter and second parameter or even first criterion and second criterion etc.
- first element or second element as well as first parameter and second parameter or even first criterion and second criterion etc.
- indexing does not imply a priority of one element, parameter or criterion over another and such names can easily be interchanged without departing from the scope of the present description.
- This indexation does not imply an order in time, for example, to assess this or that criterion.
- placed upstream is meant that one element is placed before another with respect to the direction of flow of a fluid.
- placed downstream is meant that one element is placed after another relative to the direction of flow of the fluid.
- FIG. 1 shows a thermal management device comprising an indirect air conditioning circuit 1 for a motor vehicle.
- This indirect air conditioning circuit 1 comprises in particular:
- a bifluid heat exchanger 5 arranged jointly on the first loop of refrigerant fluid A and on the second loop of coolant B, so as to allow heat exchanges between said first loop of coolant A and said second loop of coolant fluid B.
- the first refrigerant fluid loop A more particularly comprises, in the direction of circulation of the refrigerant fluid:
- first flow of interior air 300 is meant here an air flow intended for the passenger compartment of the motor vehicle.
- the first heat exchanger 9 is thus arranged in a first heating, ventilation and air conditioning device X.
- external air flow 200 is meant a flow of air which comes from the outside of the motor vehicle.
- the second heat exchanger 13 can thus be placed on the front face of the motor vehicle.
- the first bypass pipe 30 can more specifically connect a first connection point 31 and a second connection point 32.
- the first connection point 31 is preferably arranged, in the direction of circulation of the refrigerant fluid, downstream of the first heat exchanger 9, between said first heat exchanger 9 and the second heat exchanger 13. More particularly, and as illustrated. in FIG. 1, the first connection point 31 is arranged between the first heat exchanger 9 and the second expansion device 11. However, it is quite possible to imagine that the first connection point 31 is arranged between the second expansion device 11 and the second heat exchanger 13 as long as the refrigerant has the possibility of bypassing said second expansion device 11 or of passing through it without suffering a loss of pressure.
- the second connection point 32 is preferably arranged downstream of the second heat exchanger 13, between said heat exchanger 13 and the compressor 3.
- the second control device expansion 11 may in particular include a stop function, that is to say it is able to block the flow of refrigerant when it is closed.
- An alternative may be to have a shut-off valve between the second expansion device 11 and the first connection point 31.
- Another alternative can also be to have a three-way valve at the first connection point 31.
- the first refrigerant fluid loop A can also include a non-return valve 23 disposed downstream of the second heat exchanger 13, between said second heat exchanger 13 and the second connection point 32 in order to prevent the refrigerant fluid coming from the first bypass pipe 30 from flowing back to the second heat exchanger 13.
- shut-off valve non-return valve, three-way valve or expansion device with shut-off function
- mechanical or electromechanical elements which can be controlled by an electronic control unit on board the motor vehicle.
- the first refrigerant fluid loop A also comprises a first internal heat exchanger 19 (IHX for “internai heat exchanger”) allowing heat exchange between the high pressure refrigerant fluid at the outlet of the bifluid heat exchanger 5 and the fluid low-pressure refrigerant at the outlet of the second heat exchanger 13 or of the first bypass pipe 30.
- This first internal heat exchanger 19 comprises in particular an inlet and an outlet of low-pressure refrigerant fluid coming from the second connection point 32, as well as an inlet and an outlet for high pressure refrigerant from the bifluid heat exchanger 5.
- high pressure refrigerant fluid is understood to mean a refrigerant fluid which has undergone an increase in pressure at the level of the compressor 3 and which has not yet undergone a loss of pressure due to one of the expansion devices.
- low-pressure refrigerant is meant a refrigerant that has undergone a pressure loss and at a pressure close to that at the inlet of the compressor 3.
- the first refrigerant fluid loop A also comprises a second internal heat exchanger 19 ′ (IHX for “internai heat exchanger”) allowing heat exchange between the high pressure refrigerant fluid at the outlet of the first internal heat exchanger 19 and the fluid. low-pressure refrigerant circulating in the first bypass pipe 30.
- This second internal heat exchanger 19 ' comprises in particular an inlet and an outlet for low-pressure refrigerant fluid coming from the first connection point 31, as well as an inlet and a outlet of high pressure refrigerant fluid from the first internal heat exchanger 19.
- the low pressure side of the second internal heat exchanger 19 ' can be disposed downstream of the first shut-off valve 33.
- At least one of the first 19 or second 19 'internal heat exchangers may be a coaxial heat exchanger, ie comprising two coaxial tubes and between which the heat exchanges take place.
- the first internal heat exchanger 19 can be a coaxial internal heat exchanger with a length between 50 and 120mm while the second internal heat exchanger 19 'can be a coaxial internal heat exchanger with a length of between between 200 and 700mm.
- the first refrigerant fluid loop A can also include a dehydrating bottle 14 disposed downstream of the bifluid heat exchanger 5, more precisely between said bifluid heat exchanger 5 and the first internal heat exchanger 19.
- a dehydrating bottle 14 disposed. on the high pressure side of the air conditioning circuit that is to say downstream of the bifluid heat exchanger 5 and upstream of an expansion device, has a smaller size as well as a reduced cost compared to other phase separation solutions such as an accumulator which would be placed on the low pressure side of the air conditioning circuit, i.e. upstream of the compressor 3, in particular upstream of the first internal heat exchanger 19.
- the first 7 and second 11 expansion devices can be electronic expansion valves, that is to say in which the pressure of the refrigerant fluid at the outlet is controlled by an actuator which fixes the opening section of the expansion device, thus fixing the pressure of the expansion device. fluid at the outlet.
- Such an electronic expansion valve is in particular capable of letting the refrigerant fluid pass without loss of pressure when said expansion device is fully open.
- the first expansion device 7 is a pressure reducer
- the electronic controllable by a control unit integrated into the vehicle and the second expansion device 11 is a thermostatic expansion valve.
- the second expansion device 11 may in particular be a thermostatic expansion valve incorporating a stop function.
- said first 7 and second 11 expansion devices can be bypassed by a bypass pipe A ', comprising in particular a shut-off valve 25, as illustrated in FIG. 6.
- This bypass pipe A' allows the refrigerant fluid to bypass said first 7 and second 11 expansion devices without suffering a loss of pressure.
- at least the second expansion device 11 is a pressure reducer
- the first expansion device 7 can also include a stop function or else include a downstream stop valve in order to block or not the passage of the refrigerant fluid.
- the first refrigerant fluid loop A also comprises a second bypass pipe 40 of the first expansion device 7 and of the first heat exchanger 9.
- This second bypass pipe 40 comprises a third expansion device 17 arranged in upstream of a first cooler 15.
- This first cooler 15 can be arranged jointly on a secondary thermal management loop.
- the secondary thermal management loop can more particularly be a loop in which circulates a heat transfer fluid and connected to heat exchangers or cold plates at the level of batteries and / or electronic elements.
- the first cooler 15 can also be a heat exchanger directly in contact with the elements to be cooled, such as the batteries.
- the third expansion device 17 may also include a stop function in order to allow or not the refrigerant fluid to pass through the second bypass line 40.
- An alternative is to have a stop valve on the second bypass line 40, in upstream of the third expansion device 17.
- the second bypass pipe 40 is connected on the one hand upstream of the first expansion device 7. This connection is made at a third connection point 41 arranged upstream of the first expansion device 7, between the second expansion device. heat 19 'and said first expansion device 7.
- the second bypass pipe 40 is connected on the other hand to the first bypass pipe 30, upstream of the first shut-off valve 33 and of the second internal heat exchanger 19 '.
- This connection is made at a fourth connection point 42 arranged between the first connection point 31 and the first shut-off valve 33 when the latter is arranged upstream of the second internal heat exchanger 19 'as in FIG. 1.
- bypass 40 is connected on the other hand to the first bypass pipe 30, upstream of the second heat exchanger 19 'and downstream of the first shut-off valve 33.
- the fourth connection point 42 is then arranged between the first valve stop 33 and the second heat exchanger 19 'when the first stop valve 33 is disposed upstream of the second internal heat exchanger 19' as in Figure 2.
- FIG. 3 shows a third embodiment where the second bypass pipe 40 is connected on the one hand upstream of the first expansion device 7 and on the other hand downstream of the second expansion device 19 ', between said second expansion device. expansion 19 'and the first internal heat exchanger 19.
- the third connection point 41 is thus also arranged upstream of the first expansion device 7, between the second heat exchanger 19' and said first expansion device 7.
- the fourth connection point 42 is disposed downstream of the first bypass pipe 30, between the second connection point 32 and the first internal heat exchanger 19.
- the fourth connection point 42 is arranged on the first bypass pipe 30, downstream of the first shut-off valve 33 and of the second internal heat exchanger 19 '.
- the first refrigerant fluid loop also includes a third
- This third bypass pipe 80 comprises in particular a first additional heat exchanger 9 'arranged in a second heating, ventilation and air conditioning device Y.
- This second heating, ventilation and air conditioning device Y can by example be placed within the motor vehicle in order to generate a second flow of interior air 300 ′ intended for the rear seats.
- bypass 80 connects a fifth connection point 81 to a sixth connection point 82.
- the fifth connection point 81 is arranged downstream of the first expansion device 7, between said first expansion device 7 and the first heat exchanger 9.
- the sixth connection point 82 is for its part disposed downstream of the first heat exchanger 9, between said first heat exchanger 9 and the first bypass pipe 30.
- This first embodiment allows by means of a single expansion device, here the first expansion device 7, to control the pressure of the refrigerant fluid going to the first heat exchanger 9 and / or to the first additional heat exchanger 9 '. It is thus possible to use only a single expansion device thereby reducing the manufacturing cost and also making it possible to simplify the control of the thermal management device.
- the third bypass line 80 may also include a shut-off valve 83 in order to control whether or not the refrigerant is circulating in the third bypass line 80.
- the third bypass pipe 80 connects a fifth connection point 81 to a sixth connection point 82.
- the fifth connection point 81 is arranged upstream of the first expansion device 7, between the second bypass pipe 40 and said first expansion device 7.
- the sixth connection point 82 is for its part disposed downstream of the first heat exchanger 9, between said first heat exchanger 9 and the first bypass pipe 30.
- the third bypass pipe 80 comprises a fourth expansion device 87 disposed upstream of the first 9 'additional heat exchanger.
- the fourth expansion device 87 can be a thermostatic expansion valve (with or without a stop function), the thermostatic bulb of which is positioned at the outlet of the first additional heat exchanger 9 '.
- the fourth expansion device 87 can also be an electronic expansion valve controlled, for example, by an electronic control unit.
- This second embodiment makes it possible to independently control the pressure of the refrigerant fluid going to the first heat exchanger 9 and to the first additional heat exchanger 9 '.
- the first refrigerant fluid loop A also comprises a fourth bypass pipe 100.
- This fourth bypass pipe 100 comprises a fifth expansion device 107 disposed upstream of a fifth heat exchanger 105.
- This fifth heat exchanger 105 can also be arranged jointly on a secondary thermal management loop.
- the secondary thermal management loop can more particularly be a loop in which a heat transfer fluid circulates and connected to heat exchangers or cold plates at the level of batteries and / or electronic elements.
- the fifth heat exchanger 105 can also be a heat exchanger directly in contact with the elements to be cooled, such as the batteries.
- the fifth expansion device 107 can also include a stop function in order to allow or not the refrigerant fluid to pass through the fourth bypass line 100.
- the fifth expansion device 107 can be a thermostatic expansion valve whose thermostatic bulb is positioned at the outlet of the fifth exchanger. heat 105.
- the fifth expansion device 107 can also be an electronic expansion valve controlled by an electronic control unit.
- the fourth bypass pipe 100 is connected on the one hand upstream of the first expansion device 7. This connection is made at a seventh connection point 101 arranged upstream of the first expansion device 7, between the first pressure point. connection 31 of the first bypass pipe 30 and said first expansion device 7.
- the fourth bypass pipe 100 is connected on the other hand downstream of the second heat exchanger 13. This connection is made at a seventh point of connection 102 disposed downstream of the second heat exchanger 13, between said second heat exchanger 13 and the second connection point 32 of the first bypass pipe 30, more precisely downstream of the non-return valve 23.
- the first refrigerant fluid loop A may include the fifth circulation line 110 connecting a ninth connection point 111 to a tenth connection point 112.
- the ninth connection point 111 is disposed downstream of the 'bifluid heat exchanger 5, between said bifluid heat exchanger 5 and the first internal heat exchanger 19.
- the tenth connection point 112 is for its part disposed upstream of the first internal heat exchanger 19, between said first heat exchanger internal 19 and the ninth connection point 111.
- the fifth circulation pipe 110 comprises a sixth heat exchanger 114.
- This sixth heat exchanger 114 is intended to be traversed by the external air flow 200.
- the sixth heat exchanger 114 can in particular be placed on the front face of the motor vehicle. , upstream of the second heat exchanger 13.
- the indirect air conditioning circuit 1 and more precisely the first refrigerant fluid loop A comprises a device for redirecting the refrigerant fluid at the outlet of the bifluid heat exchanger 5 directly to the first internal heat exchanger 19 and / or to the fifth pipe traffic 110.
- the device for redirection of the refrigerant fluid at the outlet of the bifluid heat exchanger 5 may comprise:
- shut-off valve 112b disposed on the fifth circulation line 110 downstream of the ninth connection point 111, between the ninth connection point 111 and the sixth heat exchanger 114.
- the device for redirection of the refrigerant fluid at the outlet of the bifluid heat exchanger 5 comprises a three-way valve arranged at the ninth connection point 111.
- the fifth circulation line 110 may also include a non-return valve 113 disposed downstream of the sixth heat exchanger 114, between said sixth heat exchanger 114 and the tenth connection point 112. This non-return valve 113 is positioned so as to block the refrigerant from the tenth connection point 112.
- the second heat transfer fluid loop B can include:
- a first heat transfer fluid circulation pipe 50 comprising a third heat exchanger 54 intended to be crossed by a first flow of air 300 inside the motor vehicle, and connecting a first junction point 61 arranged downstream of the heat exchanger bifluid heat 5 and a second junction point 62 arranged upstream of the bifluid heat exchanger 5,
- a second circulation pipe 60 for heat transfer fluid comprising a fourth heat exchanger 64 intended to be traversed by a flow of air 200 outside the motor vehicle, and connecting the first junction point 61 arranged downstream of the heat exchanger bifluid 5 and the second junction point 62 arranged upstream of the bifluid heat exchanger 5, and
- a pump 18 disposed downstream or upstream of the bifluid heat exchanger 5, between the first junction point 61 and the second junction point 62.
- the indirect reversible air conditioning circuit 1 comprises, within the second heat transfer fluid loop B, a device for redirecting the heat transfer fluid from the bifluid heat exchanger 5 to the first circulation pipe 50 and / or to the second circulation pipe. circulation 60.
- said device for redirection of the coolant from the bifluid heat exchanger 5 may in particular include a fourth shut-off valve 63 disposed on the second circulation pipe 60 in order to block or not the heat transfer fluid and prevent it from circulating in said second circulation line 60.
- the thermal management device may also include, at the level of the first heating, ventilation and air conditioning device X, a shutter 310 for obstructing the first interior air flow 300 passing through the third heat exchanger 54.
- This embodiment makes it possible in particular to limit the number of valves on the second heat transfer fluid loop B and thus makes it possible to limit production costs.
- the device for redirection of the heat transfer fluid from the bifluid heat exchanger 5 may in particular include:
- a fourth stop valve 63 disposed on the second circulation pipe 60 in order to block or not the heat transfer fluid and to prevent it from circulating in said second circulation pipe. circulation 60 (therefore in the fourth heat exchanger 64), and
- a fifth shut-off valve 53 disposed on the first circulation pipe 50 in order to block or not the heat transfer fluid and prevent it from circulating in said first circulation pipe 50 (therefore in the third heat exchanger 54).
- the second heat transfer fluid loop B may also include an electric heating element 55 for the heat transfer fluid.
- Said electric heating element 55 is in particular arranged, in the direction of circulation of the heat transfer fluid, downstream of the bifluid heat exchanger 5, between said bifluid heat exchanger 5 and the first junction point 61.
- the second heat transfer fluid loop B may also include a third heat transfer fluid circulation pipe 90 comprising a second additional heat exchanger 54 ′ disposed in the second heating, ventilation and ventilation device. air conditioning Y.
- This third circulation pipe 90 connects a third junction point 91 to a fourth junction point 92.
- the third junction point 91 is disposed downstream of the first junction point 61, between said first junction point 61 and the third heat exchanger 54.
- the fourth junction point 92 is for its part disposed downstream of the third heat exchanger 54, between said third heat exchanger 54 and the second junction point 62.
- This second additional heat exchanger 54 'allows in particular the heating or dehumidification of the second interior air flow 100 '.
- the present invention also relates to various modes of operation of the indirect reversible air conditioning circuit 1, illustrated in FIGS. 9 to 15.
- FIGS. 9 to 15 only the elements in which the refrigerant fluid and / or the heat transfer fluid circulate are represented.
- the direction of circulation of the refrigerant and / or the heat transfer fluid is represented by arrows.
- the first cooling mode is the first cooling mode
- FIG. 9 shows a first cooling mode in which the first refrigerant fluid loop A is according to the first embodiment as illustrated in FIG. 2.
- the refrigerant fluid circulates successively in:
- the heat transfer fluid at the outlet of the bifluid heat exchanger 5 circulates in the fourth heat exchanger 64 of the second circulation pipe 60.
- a portion of the coolant at the outlet of the bifluid heat exchanger 5 circulates in the third heat exchanger 54 of the first circulation pipe 50 and another portion of the coolant at the outlet of the exchanger.
- Bifluid heat 5 circulates in the fourth heat exchanger 64 of the second circulation line 50.
- the obstruction flap 310 is closed so as to prevent the first interior air flow 300 from circulating in the third heat exchanger 54.
- the refrigerant fluid at the inlet of the compressor 3 is in the gas phase.
- the refrigerant fluid undergoes compression as it passes through the compressor 3. Said refrigerant fluid is then said to be at high pressure.
- the high pressure refrigerant fluid passes through the bifluid heat exchanger 5 and undergoes a loss of heat energy due to its passage in the liquid phase and the transfer of this heat energy to the heat transfer fluid of the second heat transfer fluid loop B.
- the high pressure refrigerant then loses heat energy while remaining at constant pressure.
- the high pressure refrigerant then passes through the first internal heat exchanger 19 where it loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid from the first bypass line 30.
- the high pressure refrigerant then passes into the second internal heat exchanger 19 'where it again loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid passing through the first bypass line 30.
- the high-pressure refrigerant fluid passes into the first expansion device 7.
- the high-pressure refrigerant fluid undergoes an isenthalpic pressure loss and passes into a state of two-phase mixing.
- the refrigerant is now said to be at low pressure.
- the refrigerant does not pass into the second bypass line 40 because the third expansion device 17 is closed.
- the refrigerant does not pass through the third bypass line 80 because the stop valve 83 is closed.
- the low-pressure refrigerant then passes the first heat exchanger 9 where it gains heat energy by cooling the first internal air flow 300.
- the refrigerant returns to the gaseous state.
- the refrigerant fluid On leaving the first heat exchanger 9, the refrigerant fluid is redirected to the first bypass line 30 because the first shut-off valve 33 is open. So that the refrigerant does not pass into the second heat exchanger 13, the second expansion device 11 is closed.
- the low pressure refrigerant fluid then passes into the second internal heat exchanger 19 'where it gains heat energy from the high pressure refrigerant fluid passing through the second internal heat exchanger 19'.
- the low pressure refrigerant then passes into the first internal heat exchanger 19 where it again gains heat energy from the high pressure refrigerant flowing through the first internal heat exchanger 19.
- the low pressure refrigerant then returns. to compressor 3.
- This first cooling mode is useful for cooling the first interior air flow 300.
- the two internal heat exchangers 19 and 19 ' are active and their effects are added.
- the use of the internal heat exchangers 19 and 19 'one after the other makes it possible to reduce the heat energy of the refrigerant at the inlet of the first expansion device 7.
- the refrigerant in the liquid state at the outlet of the bifluid heat exchanger 5 is cooled by the refrigerant fluid in the gaseous state and at low pressure leaving the first heat exchanger 9.
- the difference in heat energy at the terminals of this heat exchanger increases significantly, which allows the times, an increase in the cooling power available at the first heat exchanger 9 and this therefore leads to an improvement in the coefficient of performance (or COP for “coefficient of performance”).
- the addition of heat energy to the refrigerant at low pressure at the first 19 and second 19 'internal heat exchangers makes it possible to limit the proportion of refrigerant fluid. in the liquid phase before entering the compressor 3, in particular when the air conditioning circuit 1 comprises a dehydrating bottle 14 arranged downstream of the bifluid heat exchanger 5.
- the heat transfer fluid gains heat energy from the refrigerant fluid at the bifluid heat exchanger 5.
- a portion of the heat transfer fluid circulates in the first circulation pipe 50 and passes through the third heat exchanger 54.
- the heat transfer fluid does not however lose heat energy because the obstruction flap 310 is closed and blocks the first interior air flow 300 so that it does not pass through the third heat exchanger 54.
- Another portion of the heat transfer fluid circulates in the second circulation pipe 60 and passes through the fourth heat exchanger 64.
- the heat transfer fluid loses heat energy at the level of said fourth heat exchanger 64 by releasing it into the flow of outside air. 200.
- the fourth stop valve 63 is open to allow the passage of the heat transfer fluid.
- An alternative solution so that the heat transfer fluid does not exchange with the first internal air flow 300 at the level of the third heat exchanger 54, is to provide, as in FIG. 7, the first circulation pipe 50 of the fifth stop valve 53 and to close it so as to prevent the heat transfer fluid from circulating in said first circulation pipe 50.
- Figure 10 shows a second cooling mode.
- This second cooling mode is identical to the first cooling mode of FIG. 9, with the difference that at the outlet of the first expansion device 7, a first part of the low-pressure refrigerant fluid passes through the first heat exchanger 9 and a first part second part of the refrigerant fluid passes into the third bypass line 80.
- the stop valve 83 of the third bypass line 80 is open.
- the refrigerant returns to the gaseous state.
- the two parts of the refrigerant meet upstream of the first bypass pipe 30.
- This second cooling mode makes it possible to cool the first internal air flow 300 via the first heat exchanger 9 within the first heating, ventilation and air conditioning device X, as well as the second internal air flow 300 ′ via the first additional heat exchanger 9 'within the second heating, ventilation and air conditioning device Y.
- FIG. 11 shows a third mode of cooling.
- This third cooling mode is identical to the second cooling mode in FIG. 10, with the difference that at the outlet of the second internal heat exchanger 19 ', a first part of the high pressure refrigerant fluid is redirected to the first expansion device. 7 and a second part of the high pressure refrigerant fluid is redirected into the second bypass line 40.
- This second part of the high pressure refrigerant fluid passes through the third expansion device 17 and undergoes an isenthalpic pressure loss and goes into a state of two-phase mixture.
- the refrigerant is now said to be at low pressure.
- the low pressure refrigerant then passes the first cooler 15 where it gains heat energy by cooling elements such as batteries.
- the refrigerant returns to the gaseous state.
- This third cooling mode makes it possible to cool the first internal air flow 300 via the first heat exchanger 9 within the first heating, ventilation and air conditioning device X, as well as the second internal air flow 300 ′ via the first additional heat exchanger 9 'within the second heating, ventilation and air conditioning device Y. It also makes it possible to cool elements such as the batteries via the first cooler 15.
- FIG. 12 shows a fourth cooling mode in which the first refrigerant fluid loop A is according to the second embodiment as illustrated in FIG. 4.
- the refrigerant fluid circulates successively in:
- the heat transfer fluid at the outlet of the bifluid heat exchanger 5 circulates in the fourth heat exchanger 64 of the second circulation pipe 60.
- a portion of the coolant at the outlet of the bifluid heat exchanger 5 circulates in the third heat exchanger 54 of the first circulation pipe 50 and another portion of the coolant at the outlet of the exchanger. of bifluid heat 5 circulates in the fourth heat exchanger 64 of the second circulation pipe 60.
- the obstruction flap 310 is closed so as to prevent the first internal air flow 300 from circulating in the third heat exchanger 54.
- the refrigerant fluid at the inlet of the compressor 3 is in the gas phase.
- the refrigerant fluid undergoes compression as it passes through the compressor 3. Said refrigerant fluid is then said to be at high pressure.
- the high pressure refrigerant fluid passes through the bifluid heat exchanger 5 and undergoes a loss of heat energy due to its passage in the liquid phase and the transfer of this heat energy to the heat transfer fluid of the second heat transfer fluid loop B.
- the high pressure refrigerant then loses heat energy while remaining at constant pressure.
- the high pressure refrigerant then passes through the first internal heat exchanger 19 where it loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid from the first bypass line 30.
- the high pressure refrigerant then passes into the second internal heat exchanger 19 'where it again loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid passing through the first bypass line 30.
- the refrigerant does not pass into the second bypass line 40 because the third expansion device 17 is closed.
- the high pressure refrigerant fluid passes into the first expansion device 7 where it experiences a loss of isenthalpic pressure and passes into a state of two-phase mixing.
- the refrigerant is now said to be at low pressure.
- the refrigerant does not pass in the third bypass line 80 because the fourth expansion device 87 is closed.
- the low-pressure refrigerant then passes the first heat exchanger 9 where it gains heat energy by cooling the first internal air flow 300.
- the refrigerant returns to the gaseous state.
- the refrigerant fluid On leaving the first heat exchanger 9, the refrigerant fluid is redirected to the first bypass line 30 because the first shut-off valve 33 is open. So that the refrigerant does not pass into the second heat exchanger 13, the second expansion device 11 is closed.
- the low pressure refrigerant fluid then passes into the second internal heat exchanger 19 'where it gains heat energy from the high pressure refrigerant fluid passing through the second internal heat exchanger 19'.
- the low pressure refrigerant then passes into the first internal heat exchanger 19 where it again gains heat energy from the high pressure refrigerant flowing through the first internal heat exchanger 19.
- the low pressure refrigerant then returns. to compressor 3.
- this fourth cooling mode is useful for cooling the first indoor air flow 300.
- the two internal heat exchangers 19 and 19 ' are active and their effects are added.
- the use of the internal heat exchangers 19 and 19 'one after the other makes it possible to reduce the heat energy of the refrigerant at the inlet of the first expansion device 7.
- the refrigerant in the liquid state at the outlet of the bifluid heat exchanger 5 is cooled by the refrigerant fluid in the gaseous state and at low pressure leaving the first heat exchanger 9.
- the difference in heat energy at the terminals of this heat exchanger increases significantly, which allows the times, an increase in cooling capacity available at the first heat exchanger 9 and an improvement in the coefficient of performance (or COP for “coefficient of performance”).
- the addition of heat energy to the refrigerant at low pressure at the level of the first 19 and second 19 'internal heat exchangers makes it possible to limit the proportion of refrigerant in the liquid phase before it enters the compressor 3, in particular when the air conditioning circuit 1 comprises a desiccant bottle 14 arranged downstream of the bifluid heat exchanger 5.
- the heat transfer fluid gains heat energy from the refrigerant fluid at the bifluid heat exchanger 5.
- a portion of the heat transfer fluid circulates in the first circulation pipe 50 and passes through the third heat exchanger 54.
- the heat transfer fluid does not however lose heat energy because the blocking flap 310 is closed and blocks the first interior air flow 300 so that it does not pass through the third heat exchanger 54.
- Another portion of the heat transfer fluid circulates in the second circulation pipe 60 and passes through the fourth heat exchanger 64.
- the heat transfer fluid loses heat energy at the level of said fourth heat exchanger 64 by releasing it into the flow of outside air. 200.
- the fourth stop valve 63 is open to allow the passage of the heat transfer fluid.
- An alternative solution so that the heat transfer fluid does not exchange with the first internal air flow 300 at the level of the third heat exchanger 54, is to provide, as in FIG. 7, the first circulation pipe 50 of the fifth stop valve 53 and to close it so as to prevent the heat transfer fluid from circulating in said first circulation pipe 50.
- FIG. 13 shows a fifth cooling mode in which the first refrigerant fluid loop A is according to the second embodiment as illustrated in FIG. 4.
- the refrigerant fluid circulates successively in:
- a first part of the refrigerant fluid passes through the first expansion device 7, where the refrigerant fluid undergoes a pressure loss and passes at low pressure, and through the first heat exchanger 9, at which the refrigerant fluid collects heat energy of the first internal air flow 300 by cooling the latter,
- a second part of the refrigerant fluid passes through the third bypass line 80, the fourth expansion device 87, where the refrigerant undergoes a pressure loss and passes at low pressure, and through the first additional heat exchanger 9 ', to the level at which the refrigerant fluid captures heat energy from the second internal air flow 300 ′ by cooling the latter,
- the heat transfer fluid at the outlet of the bifluid heat exchanger 5 circulates in the fourth heat exchanger 64 of the second circulation pipe 60.
- a portion of the coolant at the outlet of the bifluid heat exchanger 5 circulates in the third heat exchanger 54 of the first circulation pipe 50 and another portion of the coolant at the outlet of the exchanger. of bifluid heat 5 circulates in the fourth heat exchanger 64 of the second circulation pipe 60.
- the obstruction flap 310 is closed so as to prevent the first internal air flow 300 from circulating in the third heat exchanger 54.
- the refrigerant fluid at the inlet of the compressor 3 is in the gas phase.
- the refrigerant fluid undergoes compression as it passes through the compressor 3. Said refrigerant fluid is then said to be at high pressure.
- the high pressure refrigerant fluid passes through the bifluid heat exchanger 5 and undergoes a loss of heat energy due to its passage in the liquid phase and the transfer of this heat energy to the heat transfer fluid of the second heat transfer fluid loop B.
- the high pressure refrigerant then loses heat energy while remaining at constant pressure.
- the high pressure refrigerant then passes through the first internal heat exchanger 19 where it loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid from the first bypass line 30.
- the high pressure refrigerant then passes into the second internal heat exchanger 19 'where it again loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid passing through the first bypass line 30.
- a first part of the high pressure refrigerant fluid passes into the first expansion device 7 where it undergoes an isenthalpic pressure loss and passes into a two-phase mixing state.
- the refrigerant is now said to be at low pressure.
- the low-pressure refrigerant then passes the first heat exchanger 9 where it gains heat energy by cooling the first internal air flow 300.
- the refrigerant returns to the gaseous state.
- the refrigerant isenthalpic and goes into a state of two-phase admixture.
- the refrigerant is now said to be at low pressure.
- the low pressure refrigerant then passes the first additional heat exchanger 9 ’where it gains heat energy by cooling the second interior air flow 300’.
- the refrigerant returns to the gaseous state.
- the low pressure refrigerant fluid then passes into the second internal heat exchanger 19 'where it gains heat energy from the high pressure refrigerant fluid passing through the second internal heat exchanger 19'.
- the low pressure refrigerant then passes into the first internal heat exchanger 19 where it again gains heat energy from the high pressure refrigerant passing through. the first internal heat exchanger 19. The low-pressure refrigerant then returns to the compressor 3.
- this fifth cooling mode is useful for cooling the first indoor airflow 300 as well as the second indoor airflow 300 ’.
- the two internal heat exchangers 19 and 19 ' are active and their effects are added.
- the use of the internal heat exchangers 19 and 19 'one after the other makes it possible to reduce the heat energy of the refrigerant at the inlet of the first expansion device 7.
- the refrigerant in the liquid state at the outlet of the bifluid heat exchanger 5 is cooled by the refrigerant fluid in the gaseous state and at low pressure leaving the first heat exchanger 9 and the first additional heat exchanger 9 '.
- the difference in heat energy at the terminals of these two heat exchangers increases appreciably, which at the same time allows an increase in the cooling capacity available and therefore leads to a
- the addition of heat energy to the refrigerant at low pressure at the level of the first 19 and second 19 'internal heat exchangers makes it possible to limit the proportion of refrigerant in the liquid phase before it enters the compressor 3, in particular when the air conditioning circuit 1 comprises a desiccant bottle 14 arranged downstream of the bifluid heat exchanger 5.
- the heat transfer fluid gains heat energy from the refrigerant fluid at the bifluid heat exchanger 5.
- a portion of the heat transfer fluid circulates in the first circulation pipe 50 and passes through the third heat exchanger 54.
- the heat transfer fluid does not however lose heat energy because the obstruction flap 310 is closed and blocks the first interior air flow 300 so that it does not pass through the third heat exchanger 54.
- Another portion of the heat transfer fluid circulates in the second circulation pipe 60 and passes through the fourth heat exchanger 64.
- the heat transfer fluid loses heat energy at the level of said fourth heat exchanger 64 by releasing it into the flow of outside air. 200.
- the fourth stop valve 63 is open to allow the passage of the heat transfer fluid.
- An alternative solution so that the heat transfer fluid does not exchange with the first internal air flow 300 at the level of the third heat exchanger 54, is to provide, as in FIG. 7, the first circulation pipe 50 of the fifth stop valve 53 and to close it so as to prevent the heat transfer fluid from circulating in said first circulation pipe 50.
- FIG. 14 shows a sixth mode of cooling.
- This sixth cooling mode is identical to the fifth cooling mode of FIG. 13, with the difference that at the outlet of the second internal heat exchanger 19 ', a first part of the high pressure refrigerant fluid is redirected to the fifth connection point. 81 and a second part of the high pressure refrigerant fluid is redirected into the second bypass line 40.
- This second part of the high pressure refrigerant fluid passes through the third expansion device 17 and undergoes isenthalpic pressure loss and goes into a state of two-phase mixture.
- the refrigerant is now said to be at low pressure.
- the low pressure refrigerant then passes the first cooler 15 where it gains heat energy by cooling elements such as batteries.
- the refrigerant returns to the gaseous state.
- This sixth cooling mode makes it possible to cool the first internal air flow 300 via the first heat exchanger 9 within the first heating, ventilation and air conditioning device X, as well as the second interior air flow 300 'via the first additional heat exchanger 9' within the second heating, ventilation and air conditioning device Y. It also makes it possible to cool elements such as the batteries via the first cooler 15.
- FIG. 15 shows a seventh cooling mode in which the first refrigerant fluid loop A is according to the second embodiment as illustrated in FIG. 4.
- the fluid refrigerant circulates successively in:
- the heat transfer fluid at the outlet of the bifluid heat exchanger 5 circulates in the fourth heat exchanger 64 of the second circulation pipe 60.
- a portion of the coolant at the outlet of the bifluid heat exchanger 5 circulates in the third heat exchanger 54 of the first circulation pipe 50 and another portion of the coolant at the outlet of the exchanger. of bifluid heat 5 circulates in the fourth heat exchanger 64 of the second circulation pipe 60.
- the obstruction flap 310 is closed so as to prevent the first internal air flow 300 from circulating in the third heat exchanger 54.
- the refrigerant fluid at the inlet of the compressor 3 is in the gas phase.
- the refrigerant fluid undergoes compression as it passes through the compressor 3. Said refrigerant fluid is then said to be at high pressure.
- the high pressure refrigerant fluid passes through the bifluid heat exchanger 5 and undergoes a loss of heat energy due to its passage in the liquid phase and the transfer of this heat energy to the heat transfer fluid of the second heat transfer fluid loop B.
- the high pressure refrigerant then loses heat energy while remaining at constant pressure.
- the high pressure refrigerant then passes through the first internal heat exchanger 19 where it loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid from the first bypass line 30.
- the high pressure refrigerant then passes into the second internal heat exchanger 19 'where it again loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid passing through the first bypass line 30.
- the refrigerant does not pass into the first heat exchanger 9 because the first expansion device 17 is closed.
- the high pressure refrigerant then passes through the third bypass line 80 and into the fourth expansion device 87 where it experiences a loss of isenthalpic pressure and goes into a two-phase mixing state.
- the refrigerant is now said to be at low pressure.
- the refrigerant does not pass into the second bypass line 40 because the third expansion device 17 is closed.
- the low pressure refrigerant then passes the first additional heat exchanger 9 ’where it gains heat energy by cooling the second interior air flow 300’.
- the refrigerant returns to the gaseous state.
- the refrigerant fluid is redirected to the first bypass line 30 because the first shut-off valve 33 is open. So that the refrigerant does not pass into the second heat exchanger 13, the second expansion device 11 is closed.
- the low pressure refrigerant then passes into the second internal heat exchanger 19 'where it gains G heat energy from the high pressure refrigerant flowing through the second internal heat exchanger 19'.
- the low pressure refrigerant then passes into the first internal heat exchanger 19 where it again gains heat energy from the high pressure refrigerant flowing through the first internal heat exchanger 19.
- the low pressure refrigerant then returns. to the compressor 3.
- This seventh cooling mode is useful for cooling the second interior air flow 300 '.
- the two internal heat exchangers 19 and 19 ' are active and their effects add up.
- the use of the internal heat exchangers 19 and 19 'one after the other makes it possible to reduce the heat energy of the refrigerant at the inlet of the fourth expansion device 87.
- the refrigerant in the liquid state at the outlet of the heat exchanger bifluid 5 is cooled by the refrigerant fluid in the gaseous state and at low pressure leaving the first additional heat exchanger 9 '.
- the addition of heat energy to the refrigerant at low pressure at the level of the first 19 and second 19 'internal heat exchangers makes it possible to limit the proportion of refrigerant in the liquid phase before it enters the compressor 3, in particular when the air conditioning circuit 1 comprises a desiccant bottle 14 arranged downstream of the bifluid heat exchanger 5.
- the heat transfer fluid gains heat energy from the refrigerant fluid at the bifluid heat exchanger 5.
- a portion of the heat transfer fluid circulates in the first circulation pipe 50 and passes through the third heat exchanger 54.
- the heat transfer fluid does not however lose heat energy because the obstruction flap 310 is closed and blocks the first interior air flow 300 so that it does not pass through the third heat exchanger 54.
- Another portion of the heat transfer fluid circulates in the second circulation pipe 60 and passes through the fourth heat exchanger 64.
- the heat transfer fluid loses heat energy at the level of said fourth heat exchanger 64 by releasing it into the flow of outside air. 200.
- the fourth stop valve 63 is open to allow the passage of the heat transfer fluid.
- An alternative solution so that the heat transfer fluid does not exchange with the first internal air flow 300 at the level of the third heat exchanger 54, is to provide, as in FIG. 7, the first circulation pipe 50 of the fifth stop valve 53 and to close it so as to prevent the heat transfer fluid from circulating in said first circulation pipe 50.
- a seventh alternative cooling mode in which, at the outlet of the second internal heat exchanger 19 ', the refrigerant fluid also circulates in the second bypass pipe 40, undergoes a loss. pressure and passes into the first cooler 15 in order to cool elements such as batteries.
- This seventh cooling mode is only possible due to the fact that the third bypass pipe 80 comprises a fourth expansion device 87 dedicated to subjecting the refrigerant fluid to a pressure loss upstream of the first additional heat exchanger 9 '.
- this seventh cooling mode to be possible in the first embodiment illustrated in FIGS. 1 to 3, it would be necessary to add a controllable shut-off valve between the fifth point of
- connection 81 and the first heat exchanger 9 in order to block the refrigerant and redirect it exclusively to the third bypass line 80.
- the thermal management device can regulate the temperature of two distinct interior air flows and thus provide differentiated comfort according to predefined zones in the passenger compartment of the motor vehicle.
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Abstract
Description
Claims
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FR1901420A FR3092652B1 (fr) | 2019-02-13 | 2019-02-13 | Dispositif de gestion thermique de véhicule automobile électrique ou hybride |
PCT/FR2020/050084 WO2020165512A1 (fr) | 2019-02-13 | 2020-01-22 | Dispositif de gestion thermique de véhicule automobile électrique ou hybride |
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US (1) | US11867443B2 (fr) |
EP (1) | EP3924674A1 (fr) |
CN (1) | CN113424000B (fr) |
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Publication number | Priority date | Publication date | Assignee | Title |
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FR2830926B1 (fr) * | 2001-10-12 | 2004-04-02 | Peugeot Citroen Automobiles Sa | Dispositif de regulation thermique pour vehicule automobile, notamment de type electrique ou hybride |
KR101813924B1 (ko) * | 2011-03-29 | 2018-01-02 | 엘지전자 주식회사 | 제습 기능을 갖는 재배장치용 공기조화기 |
JP6075058B2 (ja) * | 2012-12-25 | 2017-02-08 | 株式会社デンソー | 冷凍サイクル装置 |
FR3037639B1 (fr) * | 2015-06-22 | 2019-03-22 | Valeo Systemes Thermiques | Dispositif de gestion thermique |
FR3052236B1 (fr) * | 2016-06-07 | 2019-05-10 | Valeo Systemes Thermiques | Circuit de climatisation de vehicule automobile |
FR3064946B1 (fr) * | 2017-04-05 | 2019-04-05 | Valeo Systemes Thermiques | Circuit de climatisation inversible indirect de vehicule automobile et procede de fonctionnement correspondant |
-
2019
- 2019-02-13 FR FR1901420A patent/FR3092652B1/fr active Active
-
2020
- 2020-01-22 US US17/430,586 patent/US11867443B2/en active Active
- 2020-01-22 CN CN202080014043.9A patent/CN113424000B/zh active Active
- 2020-01-22 EP EP20705430.5A patent/EP3924674A1/fr active Pending
- 2020-01-22 WO PCT/FR2020/050084 patent/WO2020165512A1/fr unknown
Also Published As
Publication number | Publication date |
---|---|
FR3092652A1 (fr) | 2020-08-14 |
CN113424000A (zh) | 2021-09-21 |
FR3092652B1 (fr) | 2021-02-19 |
US20220128273A1 (en) | 2022-04-28 |
US11867443B2 (en) | 2024-01-09 |
CN113424000B (zh) | 2023-04-11 |
WO2020165512A1 (fr) | 2020-08-20 |
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