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
  • B60H1/00271—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
  • B60H1/00899—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
• • 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
  • B60H1/3228—Cooling devices using compression characterised by refrigerant circuit configurations
  • B60H1/32284—Cooling devices using compression characterised by refrigerant circuit configurations comprising two or more secondary circuits, e.g. at evaporator and condenser side
• • 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
  • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
  • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
• • 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
  • F25B41/30—Expansion means; Dispositions thereof
  • F25B41/31—Expansion 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
  • F25B41/00—Fluid-circulation arrangements
  • F25B41/40—Fluid line arrangements
  • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
• • 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
  • F25B49/00—Arrangement or mounting of control or safety devices
  • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
• • 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
  • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
• • 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
  • B60H2001/00949—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
  • B60H1/32—Cooling devices
  • B60H2001/3286—Constructional features
  • B60H2001/3291—Locations with heat exchange within the refrigerant circuit itself
• • 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
• • 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
  • F25B2400/0411—Refrigeration circuit bypassing means for the expansion valve or capillary tube

Definitions

• the present invention relates to the field of thermal conditioning systems.
• Such systems can in particular be fitted to a motor vehicle.
• these systems make it possible to achieve thermal regulation of various parts of the vehicle, such as the passenger compartment or an electrical energy storage battery, in the case of an electrically powered vehicle.
• Heat exchanges are mainly managed by the compression and expansion of a refrigerant fluid within several heat exchangers.
• Thermal conditioning systems commonly use a refrigerant loop and a coolant loop exchanging heat with the refrigerant. Such systems are thus called indirect.
• Patent EP2933586 B1 is an example.
• the refrigerant loop is formed so that the refrigerant transfers heat to a heat transfer liquid in a two-fluid heat exchanger, then passes through a heat exchanger located in the passenger compartment, also called an evaporator. This heat exchanger cools the passenger compartment.
• the heating of the passenger compartment is ensured in particular by a heating radiator which dissipates the heat of the coolant in the flow of air sent to the passenger compartment.
• the refrigerant circuit comprises a main loop as well as multiple bypass branches that allow multiple combinations of circulation of the refrigerant. Many operating modes can thus be obtained, such as for example the cooling of the air in the passenger compartment, the heating of the air in the passenger compartment, the dehumidification of the air in the passenger compartment, or even the cooling vehicle batteries.
• thermo conditioning system comprising:
• a heat transfer liquid circuit configured to circulate a heat transfer liquid
• a refrigerant circuit configured to circulate a refrigerant fluid, the refrigerant circuit comprising:
• a main loop comprising successively, depending on the direction in which the refrigerant fluid travels:
• a two-fluid heat exchanger arranged jointly on the refrigerant circuit and on the heat transfer liquid circuit so as to allow heat exchange between the refrigerant fluid and the heat transfer liquid
• a first heat exchanger configured to exchange heat with a first air flow
• a first bypass branch connecting a first connection point arranged on the main loop downstream of the two-fluid exchanger and upstream of the first expansion device to a second connection point arranged on the main loop downstream of the first heat exchanger and upstream of the compression device, the first bypass branch successively comprising a second expansion device and a second heat exchanger,
• a second bypass branch connecting a third connection point arranged on the main loop downstream of the first connection point and upstream of the first expansion device to a fourth connection point arranged on the main loop downstream of the first heat exchanger. heat and upstream of the second connection point, the second bypass branch successively comprising a third expansion device and a third heat exchanger, the main loop comprising a first internal heat exchanger configured to allow heat exchange between the refrigerant fluid at high pressure downstream of the dual-fluid heat exchanger and upstream of the first connection point, and the low-pressure refrigerant fluid downstream of the second connection point, the refrigerant fluid circuit being configured so that the refrigerant fluid at the outlet of the first heat exchanger joins the compression device only via the fourth connection point and the second connection point.
• the second heat exchanger is configured to exchange heat with a second airflow.
• the first airflow is an airflow inside a passenger compartment of a motor vehicle.
• the second air flow is a flow of air outside the passenger compartment of a motor vehicle.
• the third heat exchanger is configured to be thermally coupled with a first element of an electric traction chain of a motor vehicle.
• the first element of the vehicle's electric powertrain is configured to exchange heat with a coolant circulating in an auxiliary coolant loop.
• the first element of the vehicle's electric powertrain is an electrical energy storage battery.
• the first element of the vehicle's electric traction chain comprises an electric vehicle traction motor.
• the first element of the vehicle's electric traction chain is an electronic module for controlling an electric traction motor of the vehicle.
• the second heat exchanger is configured to be thermally coupled with a first element of an electric traction chain of a motor vehicle.
• the third heat exchanger is configured to exchange heat with a second airflow.
• the first airflow is an airflow inside a passenger compartment of a motor vehicle and the second airflow is an airflow outside the passenger compartment of a motor vehicle.
• the main loop comprises a second internal heat exchanger configured to allow heat exchange between the high-pressure refrigerant fluid downstream of the first connection point and upstream of the third connection point, and the low-pressure refrigerant fluid downstream of the fourth connection point and upstream of the second connection point.
• the main loop A comprises a fourth expansion device disposed downstream of the first heat exchanger and upstream of the second connection point.
• the fourth expansion device can be arranged downstream of the first heat exchanger and upstream of the fourth connection point.
• the fourth expansion device can also be arranged downstream of the fourth connection point and upstream of the second connection point.
• the fourth expansion device is for example an electronic expansion valve.
• the main loop comprises a first check valve disposed downstream of the first heat exchanger and upstream of the fourth connection point.
• a coolant circuit length between the first check valve and the fourth connection point is less than 10 centimeters.
• the first bypass branch comprises a second check valve disposed downstream of the second heat exchanger.
• the main loop comprises a first check valve disposed downstream of the fourth connection point and upstream of the second connection point.
• the main loop includes a refrigerant fluid accumulation device located downstream of the two-fluid heat exchanger.
• the refrigerant fluid accumulation device is arranged upstream of the first internal exchanger.
• the coolant circuit has a fourth heat exchanger configured to exchange heat with the first air flow.
• the coolant circuit has a fifth heat exchanger configured to exchange heat with the second air flow.
• the main loop comprises a third internal heat exchanger configured to allow heat exchange between the high-pressure refrigerant fluid downstream of the third connection point and the low-pressure refrigerant fluid upstream of the fourth connection point.
• the coolant circuit includes a primary loop and a secondary loop.
• the fourth heat exchanger is arranged on the primary coolant loop.
• the fifth heat exchanger is arranged on the secondary coolant loop.
• the secondary loop comprises a bypass branch extending between a first connection point arranged on the primary loop upstream of the fourth heat exchanger to a second connection point arranged on the primary loop downstream of the fourth heat exchanger .
• the coolant circuit includes a coolant circulation pump.
• the disclosure also relates to a method of operating a thermal conditioning system as described above, in a mode called extended energy recovery mode, in which the refrigerant fluid circulates in the compression device where it passes to high pressure, and circulates successively in the two-fluid exchanger where it yields heat to the heat transfer liquid, in the third expansion device where it passes to low pressure, in the third heat exchanger where it absorbs heat, and returns to the compression device.
• the disclosure also relates to a method of operating a thermal conditioning system as described above, in a mode called extended energy recovery mode, in which the refrigerant fluid circulates in the compression device where it passes at high pressure, and circulates successively in the two-fluid exchanger where it yields heat to the heat transfer liquid, in the second expansion device where it passes at low pressure, in the second heat exchanger where it absorbs heat, and returns to the compression device.
• extended energy recovery mode in which the refrigerant fluid circulates in the compression device where it passes at high pressure, and circulates successively in the two-fluid exchanger where it yields heat to the heat transfer liquid, in the second expansion device where it passes at low pressure, in the second heat exchanger where it absorbs heat, and returns to the compression device.
• the disclosure also relates to a method of operating a thermal conditioning system as described above, in a so-called parallel dehumidification mode, in which the refrigerant fluid circulates in the compression device where it passes at high pressure, and circulates in the two-fluid exchanger where it yields heat to the coolant, is divided between a first flow circulating in the first bypass branch and a second flow circulating in the main loop, the first flow circulates in the second expansion device where it passes at low pressure, into the second heat exchanger where it absorbs heat from the second air flow, joins the main loop at the second connection point, the second flow circulates successively in the first expansion device where the refrigerant switches to an intermediate pressure, the intermediate pressure being lower than the high pressure and higher than the low pres tion, in the first heat exchanger where it absorbs heat from the first air flow, in the fourth expansion device where it passes at low pressure, the first flow of refrigerant fluid at low pressure and the second flow of fluid low-pressure refrigerant come together at the second connection point
• the disclosure also relates to a thermal conditioning system comprising:
• a heat transfer liquid circuit configured to circulate a heat transfer liquid
• a refrigerant circuit configured to circulate a refrigerant fluid, the refrigerant circuit comprising:
• a main loop comprising successively, depending on the direction in which the refrigerant fluid travels:
• a two-fluid heat exchanger arranged jointly on the refrigerant circuit and on the heat transfer liquid circuit so as to allow heat exchange between the refrigerant fluid and the heat transfer liquid
• a first heat exchanger configured to exchange heat with a first air flow
• a first bypass branch connecting a first connection point arranged on the main loop downstream of the two-fluid exchanger and upstream of the first expansion device to a second connection point arranged on the main loop downstream of the first heat exchanger and upstream of the compression device, the first bypass branch successively comprising a second expansion device and a second heat exchanger,
• a second bypass branch connecting a third connection point arranged on the main loop downstream of the first connection point and upstream of the first expansion device to a fourth connection point arranged on the main loop downstream of the first heat exchanger and upstream of the second connection point, the second bypass branch successively comprising a third expansion device and a third heat exchanger, the main loop comprising a first internal heat exchanger configured to allow a heat exchange between the refrigerant at high pressure downstream of the dual-fluid exchanger and upstream of the first connection point and the low-pressure refrigerant fluid downstream of the second connection point, the refrigerant circuit being configured so that the refrigerant fluid at the outlet of the first heat exchanger joins the compression device only via the fourth connection point and the second connection point, in which the second heat exchanger is configured to be thermally coupled with a first element of an electric traction chain of a vehicle automobile, in which the third heat exchanger is configured to exchange heat with a second air flow, in which the first air flow is an air flow inside a passenger compartment of a motor vehicle
• FIG. 1 is a schematic view of a thermal conditioning system according to a first embodiment of the invention
• FIG. 2 is a schematic view of a thermal conditioning system according to a second embodiment of the invention.
• FIG. 3 is a schematic view of a thermal conditioning system according to a variant embodiment of the first embodiment
• FIG. 4 is a schematic view of a thermal conditioning system according to a variant embodiment of the second embodiment
• FIG. 5 is a schematic view of a thermal conditioning system according to a third embodiment of the invention.
• FIG. 6 is a schematic view of a thermal conditioning system according to a variant embodiment of the third embodiment
• FIG. 7 is a schematic view of a thermal conditioning system according to a fourth embodiment of the invention
• FIG. 8 is a schematic view of the thermal conditioning system of Figure 4 operating according to an operating mode called extended energy recovery mode
• FIG. 9 is a schematic view of the thermal conditioning system of Figure 5 operating according to an operating mode called extended energy recovery mode
• FIG. 10 is a schematic view of the thermal conditioning system of FIG. 4 operating according to an operating mode called parallel dehumidification mode.
• a first element upstream of a second element means that the first element is placed before the second element with respect to the direction of circulation, or course, of a fluid.
• a first element downstream of a second element means that the first element is placed after the second element with respect to the direction of circulation, or travel, of the fluid in question.
• the term “a first element is upstream of a second element” means that the refrigerant successively passes through the first element, then the second element, without passing through the compression device. In other words, the refrigerant fluid leaves the compression device, possibly crosses one or more elements, then crosses the first element, then the second element, then returns to the compression device, possibly after having crossed other elements.
• An electronic control unit receives information from various sensors measuring in particular the physical characteristics of the refrigerant at various points in the refrigerant circuit.
• the pressure and temperature of the refrigerant fluid are examples of characteristics measured.
• the electronic control unit also receives instructions from the occupants of the vehicle, such as the desired temperature inside the passenger compartment.
• the electronic control unit implements control laws allowing the control of the various actuators of the system, in order to ensure the control of the thermal conditioning system 100 so as to ensure the instructions received while optimizing the thermodynamic performance.
• Each of the expansion devices used can be an electronic expansion valve, a thermostatic expansion valve, or a calibrated orifice.
• the passage section allowing the refrigerant fluid to pass can be adjusted continuously between a closed position and a maximum open position.
• the system control unit drives an electric motor which moves a movable shutter controlling the section of passage offered to the refrigerant fluid.
• Each of the regulators can be sealed in the closed position.
• Each of the expansion valves can also have a non-zero leakage rate, and a shut-off valve can be added in series so as to interrupt the circulation of the refrigerant fluid.
• the compression device 3 can be an electric compressor, that is to say a compressor whose moving parts are driven by an electric motor.
• the compression device 3 comprises a suction side of the low-pressure refrigerant fluid, also called inlet 3a of the compression device, and a discharge side of the high-pressure refrigerant fluid, also called outlet 3b of the compression device 3.
• the internal moving parts of the compressor 3 cause the refrigerant fluid to pass from a low pressure on the inlet side 3a to a high pressure on the outlet side 3b. After expansion in one or more expansion devices, the refrigerant fluid joins the inlet 3a of the compressor 3 and begins a new thermodynamic cycle.
• connection point 11 to 14 allows the refrigerant to pass through one or other of the circuit portions joining at this connection point.
• the distribution of the refrigerant between the circuit portions joining at a connection point is achieved by varying the opening or closing of the shut-off valve, non-return valve or expansion device included on each of the joining branches.
• each connection point is a means of redirecting the refrigerant fluid arriving at this connection point.
• the non-return valves and the expansion devices thus make it possible to selectively direct the refrigerant fluid into the different branches of the refrigerant circuit, in order to ensure different modes of operation, as will be described later.
• the refrigerant used by the refrigerant circuit 2 is here a chemical fluid such as R1234yf.
• Other refrigerants can also be used, such as R134a, or even R290.
• thermal conditioning system 100 comprising:
• a heat transfer liquid circuit 1 configured to circulate a heat transfer liquid
• a refrigerant circuit 2 configured to circulate a refrigerant fluid, the refrigerant circuit 2 comprising:
• a main loop A comprising successively, depending on the direction of travel of the refrigerant fluid:
• a compression device 3
• a two-fluid heat exchanger 4 arranged jointly on the refrigerant circuit 2 and on the heat transfer liquid circuit 1 so as to allow heat exchange between the refrigerant fluid and the heat transfer liquid,
• a first heat exchanger 6 configured to exchange heat with a first airflow F1
• a first bypass branch B connecting a first connection point 11 arranged on the main loop A downstream of the two-fluid exchanger 4 and upstream of the first expansion device 5 to a second connection point 12 arranged on the main loop A in downstream of the first heat exchanger 6 and upstream of the compression device 3, the first bypass branch B successively comprising a second expansion device 7 and a second heat exchanger 8,
• a second branch C connecting a third connection point 13 arranged on the main loop A downstream of the first connection point 11 and upstream of the first expansion device 5 to a fourth connection point 14 arranged on the main loop A in downstream of the first heat exchanger 6 and upstream of the second connection point 12, the second bypass branch C successively comprising a third expansion device 9 and a third heat exchanger 10, the main loop A comprising a first internal heat exchanger 17 configured to allow heat exchange between the high-pressure refrigerant fluid downstream of the two-fluid heat exchanger 4 and upstream of the first connection point 11 and the low-pressure refrigerant fluid downstream of the second connection point 12, the circuit refrigerant fluid 2 being configured so that the refrigerant fluid leaving the first heat exchanger 6 joins the disp compression device 3 only passing through the fourth connection point 14 and the second connection point 12.
• the refrigerant fluid leaving the first heat exchanger 6 always joins the compression device 3 without leaving the main loop A.
• normal operating mode is meant an operation without failure of a component, where all the elements of the system are operational as well as correctly assembled together.
• the refrigerant fluid exiting from the first heat exchanger 6 can only reach the compression device 3 by passing through the fourth connection point 14 and through the second connection point 12.
• the refrigerant fluid exiting from the first heat exchanger 6 first passes through the fourth connection point 14, then through the second connection point 12, then joins the low pressure inlet of the compressor 3.
• the refrigerant circuit 2 has no branch of derivation which would allow the refrigerant fluid leaving the first heat exchanger 6 to join the compression device 3 without passing successively through the fourth connection point 14 and then through the second connection point 12.
• the first heat exchanger 6 has a coolant inlet 6a and a coolant outlet 6b.
• the main loop portion A between the outlet 6b of the first heat exchanger 6 and the fourth connection point 14 does not include any other connection point making it possible to redirect the refrigerant fluid.
• a device having exactly one inlet and one outlet, such as an expansion device, a stop valve or a non-return valve can be arranged on this portion of the main loop, as will be detailed later.
• the first bypass branch B is arranged in parallel with a portion of the main loop A comprising the first expansion device 5 and the first heat exchanger 6.
• the second bypass branch C is arranged in parallel of the portion of the main loop A comprising the first expansion device 5 and the first heat exchanger 6.
• the first bypass branch B and the second bypass branch C are arranged parallel to each other.
• the second heat exchanger 8 is configured to exchange heat with a second air flow F2.
• the first airflow F1 is an interior airflow Fi to a passenger compartment of a motor vehicle.
• the second flow of air F2 is a flow of air Fe outside the passenger compartment of a motor vehicle.
• Interior air flow Fi means an air flow intended for the passenger compartment of the motor vehicle.
• This indoor air flow can circulate in a heating, ventilation and/or air conditioning installation, frequently referred to by the English term “FIVAC”, for “Fleating, Ventilating and Air Conditioning”. This installation has not been shown in the various figures.
• a first motor-fan unit, not shown, is placed in the heating, ventilation and/or air conditioning installation in order to increase, if necessary, the flow rate of the interior air flow Fi.
• exterior air flow Fe is meant an air flow that is not intended for the passenger compartment of the vehicle. In other words, this air flow Fe remains outside the passenger compartment of the vehicle.
• a second motor-fan unit also not shown, can be activated in order to increase the flow rate of the outside air flow Fe if necessary.
• the air flow provided by the first as well as by the second motor-fan unit can be adjusted for example by the electronic control unit of the thermal conditioning system 100.
• the third heat exchanger 10 is configured to be thermally coupled with a first element 25 of an electric traction chain of a motor vehicle.
• the first element 25 of the electric traction chain of the vehicle is configured to exchange heat with a coolant flowing in an auxiliary loop 26 of coolant.
• the first element 25 of the electric traction chain of the vehicle is here an electric energy storage battery.
• the battery 25 can supply the energy necessary for the traction of the vehicle.
• the auxiliary coolant loop 26 is isolated from the rest of the coolant circuit 1 . In other words, the heat transfer liquid circulating in the auxiliary loop 26 cannot mix with the heat transfer liquid of the circuit 1 .
• the first element 25 of the electric traction chain of the vehicle comprises an electric traction motor of the vehicle.
• the first element 25 of the electric traction chain of the vehicle is an electronic module for controlling an electric traction motor of the vehicle.
• the second heat exchanger 8 is configured to be thermally coupled with a first element 25 of an electric traction chain of a motor vehicle.
• the third heat exchanger 10 is configured to exchange heat with a second air flow F2.
• the first airflow F1 is an airflow Fi inside a passenger compartment of a motor vehicle and the second airflow F2 is an airflow outside Fe in the passenger compartment of a vehicle automobile.
• the third embodiment and its variant differs from the first and from the second embodiment by the role of the second heat exchanger 8 and the third heat exchanger 10 which is exchanged.
• the general architecture of the refrigerant circuit remains the same.
• a first heat exchange section 17a of the first internal heat exchanger 17 is arranged on the main loop A between the two-fluid exchanger 4 and the first connection point 11.
• a second heat exchange section 17b of the first heat exchanger internal heat exchanger 17 is arranged on the main loop A downstream of the second connection point 12.
• the first heat exchange section 17a and the second heat exchange section 17b are thermally coupled so as to carry out a heat exchange between the fluid high pressure refrigerant and low pressure refrigerant.
• the main loop A comprises a second internal heat exchanger 18 configured to allow heat exchange between the high pressure refrigerant fluid downstream of the first connection point 11 and in upstream of the third connection point 13, and the low-pressure refrigerant fluid downstream of the fourth connection point 14 and upstream of the second connection point 12.
• a first heat exchange section 18a of the second internal heat exchanger 18 is arranged on the main loop A between the first connection point 11 and the third point connection 13.
• a second heat exchange section 18b of the second internal heat exchanger 18 is arranged on the main loop A downstream of the fourth connection point 14 and upstream of the second connection point 12.
• the first heat exchange section 18a and the second heat exchange section 18b are thermally coupled.
• the main loop A comprises a fourth expansion device 15 disposed downstream of the first heat exchanger 6 and upstream of the second connection point 12.
• the fourth expansion device 15 is more precisely arranged downstream of the first heat exchanger 6 and upstream of the fourth connection point 14.
• the fourth expansion device 15 is for example an electronic expansion valve.
• the fourth expansion device 15 allows operating modes in which the pressure of the refrigerant fluid is higher in the first heat exchanger 6 than in the second heat exchanger 8.
• the fourth expansion device 15 is arranged between the fourth connection point 14 and the second connection point 12, that is to say downstream from the fourth connection point 14 and upstream from the second connection point 12.
• the main loop A comprises a first check valve 21 disposed downstream of the first heat exchanger 6 and upstream of the fourth connection point 14.
• the first variant illustrated in Figure 3 differs from the first embodiment, illustrated in Figure 1, by the addition of the first non-return valve 21 .
• the non-return valve 21 blocks a circulation of refrigerant fluid from the fourth connection point 14 to the outlet 6b of the first heat exchanger 6.
• a coolant circuit length between the first check valve 21 and the fourth connection point 14 is here less than 10 centimeters. This reduced distance makes it possible to minimize the quantity of refrigerant fluid comprised between the fourth connection point 14 and the first non-return valve 21 , while allowing easy mechanical integration of the first non-return valve 21 .
• the first bypass branch B comprises a second check valve 22 disposed downstream of the second heat exchanger 8.
• the second check valve return 22 is arranged upstream of the second connection point 12.
• the second non-return valve 22 blocks a circulation of refrigerant fluid from the second connection point 12 to the second heat exchanger 8.
• the main loop A comprises a first check valve 21 disposed downstream of the fourth connection point 14 and upstream of the second connection point 12.
• the check valve -return 21 blocks a flow of coolant from the second connection point 12 to the fourth connection point 14.
• the first bypass branch B has no check valve.
• the main loop A comprises a refrigerant accumulation device 23 arranged downstream of the two-fluid exchanger 4.
• the refrigerant fluid accumulation device 23 is arranged upstream of the first internal exchanger 17.
• the device accumulation of coolant 23 is here a dehydrating bottle.
• the coolant circuit 1 includes a fourth heat exchanger 16 configured to exchange heat with the first airflow F1.
• the heat transfer liquid circuit 1 also comprises a fifth heat exchanger 20 configured to exchange heat with the second air flow F2.
• the fourth heat exchanger 16 can thus heat the passenger compartment , by dissipating heat in the air flow Fi intended to supply the interior of the passenger compartment.
• the fourth heat exchanger 16 is arranged downstream of the first heat exchanger 6 in a flow direction of the interior air flow Fi.
• the fifth heat exchanger 20 can dissipate the heat originating from the condensation of the refrigerant fluid in the two-fluid exchanger 4. This operation can occur, for example, when the conditioning system thermal operates in cabin cooling mode, in which the first heat exchanger 6 operates as an evaporator.
• the fifth heat exchanger 20 is arranged upstream of the second heat exchanger 8 according to a direction of flow of the outside air flow Fe. In other words, the fifth heat exchanger 20 receives an air flow which does not have been affected by heat exchange with another heat exchanger.
• the main loop A comprises a third internal heat exchanger 19 configured to allow heat exchange between the high-pressure refrigerant fluid downstream of the third connection point 13 and the low-pressure refrigerant fluid upstream of the fourth connection point 14.
• a first heat exchange section 19a of the third internal heat exchanger 19 is arranged on the main loop A between the third connection point 13 and the first expansion device 5.
• a second heat exchange section 19b of the third internal heat exchanger 19 is arranged on the main loop A downstream of the first heat exchanger 6 and upstream of the fourth connection point 14.
• the first heat exchange section 19a and the second heat exchange section 19b are thermally coupled .
• the main loop A comprises a fourth expansion device 15 or a first non-return valve 21
• the second heat exchange section 19b is arranged downstream of the fourth expansion device 15, respectively of the first non-return valve 21 .
• the third internal exchanger 19 completes the action of the first internal exchanger 17 and of the second internal exchanger 18, and increases the enthalpy variation of the refrigerant fluid between the outlet 3b of the compression device 3 and the inlet of the first expansion device 5 .
• the coolant circuit 1 comprises a primary loop 41 and a secondary loop 42.
• the fourth heat exchanger 16 is arranged on the primary loop 41 of coolant.
• the fifth heat exchanger 20 is arranged on the secondary loop 42 of coolant liquid.
• the secondary loop 42 comprises a bypass branch 43 extending between a first connection point 31 arranged on the primary loop 41 upstream of the fourth heat exchanger 16 to a second connection point 32 arranged on the primary loop 41 downstream of the fourth heat exchanger 16.
• the fifth heat exchanger 20 is arranged on the bypass branch 43.
• the secondary loop 42 is formed by the bypass branch 43 and by the primary loop portion 41 extending between the second connection point 32 and the first connection point 31 .
• the coolant circuit 1 comprises a circulation pump 33 of coolant.
• the heat transfer liquid circulation pump 33 is arranged between the second connection point 32 and the two-fluid exchanger 4.
• the circulation pump 33 is configured to circulate the heat transfer liquid from the two-fluid exchanger 4 to the second connection point 32
• the heat transfer liquid circulation pump 33 is arranged on a portion common to the primary loop 41 and to the secondary loop 42.
• Shut-off valves not shown, allow circulation of the heat transfer liquid either only in the primary loop 41, either only in the secondary loop 42, or jointly in the primary loop 41 and in the secondary loop 42.
• FIG. 8 diagrams a method of operating a thermal conditioning system according to the first and second embodiments, in a mode called extended energy recovery mode, in which the refrigerant fluid circulates in the cooling device.
• compression 3 where it passes at high pressure, and circulates successively in the two-fluid exchanger 4 where it yields heat to the coolant liquid, in the third expansion device 9 where it passes at low pressure, in the third heat exchanger 10 where it absorbs heat, and returns to the compression device 3.
• the first expansion device 5 is in the closed position so as to prevent the circulation of refrigerant fluid in the first heat exchanger 6.
• the second expansion device 7 is in the closed position of so as to prevent the circulation of refrigerant fluid in the second heat exchanger 8.
• the fourth expansion device 15 is of a type having a closed position providing zero flow, the latter is also in the closed position, so as to prevent the refrigerant fluid coming from the fourth connection point 14 from reaching the first exchanger 6 by crossing the fourth expansion 15. An accumulation of liquid refrigerant fluid in the first heat exchanger 6, when the latter receives a flow of fresh air, is thus avoided.
• the third expansion device 9 is in a position allowing the passage of refrigerant fluid in the third heat exchanger 10.
• the heat dissipated by the element 25 of the traction chain is recovered at the level of the third heat exchanger 10.
• the degree opening of the third expansion device 9 is adjusted according to the quantity of heat to be exchanged in the third heat exchanger 10.
• the heat recovered in the heat transfer liquid circuit 1 at the level of the two-fluid exchanger 4 is dissipated in the fourth heat exchanger 16 and allows the heating of the passenger compartment.
• the second non-return valve 22 prevents the low-pressure refrigerant fluid leaving the third heat exchanger 10 from being able, at the level of the second connection point 12, to reach the second exchanger 8 and accumulate there.
• the refrigerant fluid present in the second heat exchanger 8 is likely to condense. Thanks to the non-return valve, an accumulation of liquid refrigerant in the second heat exchanger 8 is thus avoided.
• the amount of refrigerant required to operate the thermal conditioning system is reduced.
• the volume required for the accumulation device 23 is reduced.
• the variation, depending on the operating modes employed, of the mass of refrigerant fluid circulating in the refrigerant circuit 2 is minimized, which allows more stable operation of the thermal conditioning system. This mode of operation makes it possible to carry out, in a cold environment, energy recovery from the first element 25 of the traction chain without destabilizing the operation of the thermal conditioning system.
• Figure 9 illustrates a method of operating a thermal conditioning system according to the third embodiment, in a mode said extended energy recovery mode, in which the refrigerant fluid circulates in the compression device 3 where it passes at high pressure, and successively circulates in the two-fluid exchanger 4 where it yields heat to the heat transfer liquid, in the second expansion device 7 where it passes at low pressure, into the second heat exchanger 8 where it absorbs heat, and returns to the compression device 3.
• the first expansion device 5 is in the closed position so as to prevent the circulation of refrigerant fluid in the first heat exchanger 6.
• the third expansion device 9 is in the closed position so as to prevent the circulation of refrigerant fluid in the third heat exchanger 10.
• the second expansion device 7 is in a position allowing the passage of refrigerant fluid in the second heat exchanger 8.
• the degree of opening of the second expansion device 7 is adjusted according to the quantity of heat to be exchanged in the second heat exchanger 8.
• the main loop A comprises a single non-return valve 21 arranged between the fourth connection point 14 and the second connection point 12.
• the non-return valve 21 prevents the refrigerant fluid from t at low pressure at the outlet of the second heat exchanger 8 can join the first exchanger 6 and the third exchanger 10 and condense there when the temperature of the outside air flow Fe is low, for example 0°C. An accumulation of liquid refrigerant fluid in the third heat exchanger 10 as well as in the first heat exchanger 6 is thus avoided.
• a single non-return valve 21 is sufficient to block a circulation of refrigerant fluid to two separate heat exchangers, since this single non-return valve 21 prevents a circulation of refrigerant fluid from the second connection point 12 to the fourth connection point 14 As before, the non-return valve 21 prevents condensation of refrigerant fluid in the inactive heat exchangers due to the closed position of the expansion devices supplying them with refrigerant fluid.
• the energy recovery mode from the first element 25 of the traction chain is optimized, since it is possible to recover the heat from the first element 25 in order to to heat the passenger compartment, even when the ambient temperature is negative, without destabilizing the operation of the thermal conditioning system 100.
• FIG. 10 illustrates a method of operating a thermal conditioning system according to the second embodiment, in a so-called parallel dehumidification mode, in which the refrigerant fluid circulates in the compression device 3 where it passes to high pressure, and circulates in the two-fluid heat exchanger 4 where it yields heat to the heat transfer liquid, is divided between a first flow circulating in the first bypass branch B and a second flow circulating in the main loop A, the first flow circulates in the second expansion device 7 where it passes at low pressure, into the second heat exchanger 8 where it absorbs heat from the second air flow F2, joins the main loop A at the second connection point 12, the second flow circulates successively in the first expansion device 5 where the refrigerant passes to an intermediate pressure, the intermediate pressure being lower than the high pressure and higher eur at low pressure, in the first heat exchanger 6 where it absorbs heat from the first air flow F1, in the fourth expansion device 15 where it passes at low pressure, the first flow of refrigerant at low pressure and the second flow of low-pressure ref
• the pressure of the refrigerant fluid is higher in the first heat exchanger 6 than in the second heat exchanger 8.
• the outside temperature corresponding to the temperature of the outside air flow Fe is negative
• the heat recovered from the exterior air flow Fe is transferred to the heat transfer liquid of circuit 1 and makes it possible to heat the interior air flow at the level of the fourth heat exchanger 16.
• This mode of operation makes it possible to dehumidify the air of the passenger compartment in a wide range of ambient temperatures, which allows optimization of energy consumption in conditions of real use of the vehicle.
• the fourth expansion device 15 allows operation of the thermal conditioning system with a pressure in the first exchanger 6 and in the third exchanger 10 which is higher than the pressure in the second exchanger 8.
• the fourth exchanger 15 makes it possible to expand the refrigerant fluid at the outlet of the first exchanger 6 and of the third exchanger 10 .

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• 2022
  • 2022-05-19 WO PCT/EP2022/063600 patent/WO2022248336A1/fr active Application Filing
  • 2022-05-19 EP EP22729661.3A patent/EP4347284A1/de active Pending
  • 2022-05-19 CN CN202280051214.4A patent/CN117940295A/zh active Pending

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