Thermal conditioning system

Abstract

The invention relates to a thermal conditioning system (100) for a motor vehicle, comprising a refrigerant circuit (10) configured for circulating a refrigerant, the refrigerant circuit (10) having a main loop (A) comprising successively, according to the direction of refrigerant flow: - a compressor (7), - a first heat exchanger (1) thermally coupled with a first airflow (F1), - a first expansion valve (31), - a second heat exchanger (2) thermally coupled with an element (25) of an electric powertrain of a motor vehicle, - a second expansion valve (32), - a third heat exchanger (3) configured to exchange heat with an interior airflow (Fi) to a vehicle passenger compartment, - a refrigerant storage device (9). Abstract figure: Figure 7

Description

Title of the invention: Thermal conditioning system Technical field

[0001] The present invention relates to the field of thermal conditioning systems. Such systems can, for example, be fitted to motor vehicles. These systems make it possible to ensure thermal regulation of various parts of the vehicle, such as the passenger compartment or an electrical energy storage battery, when the vehicle is electrically powered. Heat exchanges are managed mainly by the compression and expansion of a refrigerant circulating in a circuit in which several heat exchangers are arranged. A compressor delivers the refrigerant in a high-pressure state and allows circulation of the refrigerant in the circuit. The refrigerant can absorb heat or give off heat at various heat exchangers arranged on the circuit. Prior art

[0002] So-called chemical refrigerants generally have a high global warming potential (GWP coefficient), which is a disadvantage. It is possible to use carbon dioxide as a refrigerant, which by definition has a global warming coefficient equal to one. The use of such a refrigerant is therefore advantageous. However, the thermodynamic properties of this gas mean that the nominal operating pressure in the circuit is higher than with traditional refrigerants such as fluorinated refrigerants. The compressor must therefore be able to ensure high discharge pressures, which makes it a more expensive component.

[0003] Furthermore, it is desirable that the thermal conditioning system can operate in numerous operating modes, so as to optimize the management of thermal exchanges under varied vehicle operating conditions. Known thermal conditioning systems generally have a high degree of complexity, without allowing all the desired operating modes. It is therefore desirable to have thermal conditioning systems with an optimized architecture, allowing a wider range of operating modes while being simpler to implement, so as to reduce their cost. Summary

[0004] For this purpose, a thermal conditioning system for a motor vehicle is proposed, comprising a refrigerant circuit configured to circulate a refrigerant fluid, the refrigerant fluid circuit comprising a main loop comprising successively according to the direction of circulation of the refrigerant fluid: - a compressor, - a first heat exchanger thermally coupled with a first air flow, - a first expansion valve, - a second heat exchanger thermally coupled with an element of an electric drive train of a motor vehicle, - a second expansion valve, - a third heat exchanger configured to exchange heat with an air flow inside a passenger compartment of the vehicle, - a refrigerant fluid accumulation device.

[0005] This refrigerant circuit architecture makes it possible to simply ensure numerous operating modes. In particular, this architecture makes it possible to cool the passenger compartment of a vehicle, while heating or cooling the element of the electric powertrain.

[0006] According to one embodiment of the thermal conditioning system, the first air flow is an air flow outside a passenger compartment of the vehicle.

[0007] According to an exemplary embodiment, the first heat exchanger exchanges heat with the outside air flow.

[0008] According to an exemplary embodiment, the element of the electric powertrain of the vehicle comprises an electrical energy storage battery.

[0009] Alternatively or additionally, the element of the electric traction chain of the vehicle comprises an electric traction motor of the vehicle.

[0010] As a further variant or in a complementary manner, the element of the electric traction chain of the vehicle comprises an electronic unit for controlling the electric traction motor of the vehicle.

[0011] The first regulator is for example an electronic regulator. Similarly, the second regulator can be an electronic regulator.

[0012] According to one embodiment, the thermal conditioning system comprises a first bypass branch connecting a first connection point arranged on the main loop downstream of the first exchanger and upstream of the second expansion valve to a second connection point arranged on the main loop downstream of the third heat exchanger and upstream of the accumulation device, the first bypass branch comprising a fourth heat exchanger thermally coupled with an air flow outside the passenger compartment of the vehicle.

[0013] According to one embodiment of the thermal conditioning system, the first air flow is an air flow inside a passenger compartment of the vehicle.

[0014] According to one embodiment, the first branch of derivation comprises a third expansion valve located upstream of the fourth heat exchanger.

[0015] The addition of the first branch branch makes it possible to add operating modes to the thermal conditioning system.

[0016] According to one embodiment of the thermal conditioning system, the first connection point is arranged on the main loop downstream of the first exchanger and upstream of the first expander.

[0017] According to one embodiment, the first connection point is arranged on the main loop downstream of the second exchanger and upstream of the second regulator.

[0018] According to an exemplary embodiment, the fourth heat exchanger exchanges heat with the outside air flow.

[0019] According to another exemplary embodiment, the fourth heat exchanger exchanges heat with a heat transfer liquid of a first heat transfer liquid circuit, the first heat transfer liquid circuit comprising a fifth heat exchanger configured to exchange heat with the outside air flow.

[0020] According to an exemplary embodiment, the first heat exchanger exchanges heat with the interior air flow.

[0021] According to another exemplary embodiment, the first heat exchanger exchanges heat with a heat transfer liquid of a second heat transfer liquid circuit, the second heat transfer liquid circuit comprising a sixth heat exchanger configured to exchange heat with the interior air flow.

[0022] The second heat transfer fluid circuit may comprise a heat exchanger configured to exchange heat with the outside air flow. Thus, the first heat exchanger is also thermally coupled with a second air flow, outside a vehicle passenger compartment. The first heat exchanger can thus be thermally coupled with the indoor air flow or with the outdoor air flow. The heat exchanger configured to exchange heat with the outside air flow can be the fifth exchanger. In other words, the first heat exchanger is also thermally coupled with a second flow of air outside a passenger compartment of the vehicle via a fifth exchanger arranged on a heat transfer fluid circuit.

[0023] According to one embodiment, the thermal conditioning system comprises a second bypass branch connecting a third connection point arranged on the first bypass branch downstream of the fourth exchanger to a fourth connection point arranged on the main loop downstream of the first connection point and upstream of the first expansion device.

[0024] According to another embodiment, the thermal conditioning system comprises a second bypass branch connecting a third connection point connection arranged on the main loop downstream of the compressor and upstream of the first exchanger to a fourth connection point arranged on the first bypass branch between the fourth exchanger and the second connection point.

[0025] The addition of the second bypass branch allows for further operating modes to be added to the thermal conditioning system.

[0026] According to one embodiment, the thermal conditioning system comprises a third bypass branch connecting a fifth connection point arranged on the main loop downstream of the second heat exchanger and upstream of the second expansion valve to a sixth connection point arranged on the first bypass branch between the first connection point and the fourth heat exchanger.

[0027] The third branch branch may include a third regulator.

[0028] The addition of the third bypass branch allows further operating modes to be added to the thermal conditioning system.

[0029] The third regulator may be an electronic regulator.

[0030] According to one embodiment of the thermal conditioning system, the main loop comprises an internal exchanger configured to allow heat exchange between the refrigerant circulating between the first exchanger and the first expansion valve and the refrigerant circulating downstream of the accumulation device and upstream of an inlet of the compressor.

[0031] According to another embodiment, the thermal conditioning system comprises an internal exchanger configured to allow heat exchange between the refrigerant circulating in the first bypass branch between the fourth exchanger and the first connection point and the refrigerant circulating in the main loop downstream of the accumulation device and upstream of an inlet of the compressor.

[0032] The internal exchanger makes it possible to increase heat exchanges and thus the thermodynamic performance of the thermal conditioning system.

[0033] According to an exemplary embodiment of the thermal conditioning system, the main loop comprises a first shutoff valve arranged downstream of the compressor and upstream of the first expander.

[0034] The first shut-off valve may be arranged between the first connection point and the fourth connection point.

[0035] In another exemplary embodiment, the first shut-off valve is arranged between the third connection point and the first heat exchanger.

[0036] According to an exemplary embodiment of the thermal conditioning system, the first bypass branch comprises a second shut-off valve arranged between the second connection point and the third connection point.

[0037] According to an exemplary embodiment, the second bypass branch comprises a third stop valve.

[0038] According to an exemplary embodiment of the thermal conditioning system, the first bypass branch comprises a fourth shutoff valve. The fourth shut-off valve is located between the fourth connection point and the sixth connection point.

[0039] The different shut-off valves make it possible to selectively isolate or connect different portions of the refrigerant circuit, and thus to achieve different operating modes.

[0040] The first shut-off valve is for example an electrically controlled valve.

[0041] Similarly, the second stop valve, the third stop valve and the fourth shut-off valves can be electrically operated valves.

[0042] Each shut-off valve is a two-way valve. Each shut-off valve can be a two-position valve.

[0043] According to one embodiment of the thermal conditioning system, the second bypass branch comprises a first one-way valve configured to allow circulation of refrigerant fluid through the first one-way valve only from the third connection point to the fourth connection point.

[0044] According to another embodiment, the main loop comprises a first one-way valve configured to allow circulation of refrigerant fluid through the first one-way valve only from the first exchanger to the first connection point.

[0045] According to one embodiment of the thermal conditioning system, the main loop comprises a second one-way valve configured to allow circulation of refrigerant fluid from the third exchanger to the second connection point and configured to prohibit circulation of refrigerant fluid from the second connection point to the third exchanger.

[0046] According to one embodiment, the first bypass branch comprises a third one-way valve configured to allow circulation of refrigerant fluid through the third one-way valve only from the sixth connection point to the first connection point.

[0047] Each one-way valve is for example a non-return valve.

[0048] The various one-way valves contribute to selectively isolating or connecting different portions of the refrigerant circuit so as to achieve different operating modes.

[0049] According to a variant, the thermal conditioning system comprises a fourth bypass branch connecting a seventh connection point arranged on the main loop between the fifth connection point and the second expansion valve to an eighth connection point arranged on the main loop between the third heat exchanger and the second connection point, the fourth bypass branch comprising a fifth shut-off valve.

[0050] The addition of the fourth bypass branch allows for further operating modes to be added to the thermal conditioning system.

[0051] The seventh connection point can be confused with the fifth connection point.

[0052] The eighth connection point can be confused with the second connection point.

[0053] The invention further relates to a method of operating a thermal conditioning system as described above, in a mode known as passenger compartment cooling and battery cooling in which: - a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates successively in the main loop, in the first exchanger where it gives off heat to the outside air flow, in the first expansion valve where it passes at intermediate pressure, in the second exchanger where it receives heat, in the second expansion valve where it passes at low pressure, in the third exchanger where it receives heat from the inside air flow, in the accumulation device, and returns to the compressor.

[0054] The invention also relates to a method of operating a thermal conditioning system described above, in a mode known as passenger compartment cooling and battery cooling in which: - a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates successively in the main loop, in the first exchanger where it gives off heat, in the first expansion valve where it passes at intermediate pressure, in the second exchanger where it receives heat, in the second expansion valve where it passes at low pressure, in the third exchanger where it receives heat from the interior air flow, in the accumulation device, and returns to the compressor, - a flow of heat transfer fluid circulates in the first exchanger where it receives heat, then in the fifth exchanger where it gives off heat to the outside air flow, and returns to the first exchanger.

[0055] The invention further relates to a method of operating a thermal conditioning system as described above, in a so-called battery cooling mode in which: - a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates successively in the main loop, in the second bypass branch, in the first bypass branch, in the fourth heat exchanger where it gives off heat to the outside air flow, in the main loop, in the first expansion valve where it passes at low pressure, in the second exchanger where it receives heat, in the fourth bypass branch, in the main loop, in the accumulation device, and returns to the compressor.

[0056] The invention also relates to a method of operating a thermal conditioning system according to other embodiments already described, in the so-called passenger compartment dehumidification and battery heating mode in which: - a flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates successively in the main loop, in the first exchanger where it gives off heat, in the first expansion valve, in the second exchanger where it gives off heat, in the second expansion valve where it passes at low pressure, in the third exchanger where it receives heat from the interior air flow, in the accumulation device, and returns to the compressor.

[0057] The invention also relates to a method of operating a thermal conditioning system according to an embodiment already described, in the so-called heat pump and battery heating mode in which: - a flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates successively in the main loop, in the first exchanger where it gives off heat to the internal air flow, in the first expansion valve, in the second exchanger where it gives off heat, in the first bypass branch, in the third expansion valve where it passes at low pressure, in the fourth heat exchanger where it receives heat from the external air flow, in the main loop, in the accumulation device, and returns to the compressor.

[0058] The invention also relates to a method of operating a thermal conditioning system according to another embodiment described previously, in the so-called heat pump and battery heating mode in which: - a flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates successively in the main loop, in the first exchanger where it gives off heat to the internal air flow, in the first expansion valve, in the second exchanger where it gives off heat, in the third bypass branch, in the third expansion valve where it passes at low pressure, in the second bypass branch, in the fourth heat exchanger where it receives heat from the external air flow, in the main loop, in the accumulation device, and returns to the compressor. Brief description of the drawings

[0059] Other characteristics, details and advantages will appear on reading the detailed description below, and on analyzing the attached drawings, in which:

[0060] [Fig-1] is a schematic view of a thermal conditioning system according to a first embodiment of the invention,

[0061] [Fig.2] is a schematic view of a thermal conditioning system according to a variant of the first embodiment of the invention,

[0062] [Fig.3] is a schematic view of a thermal conditioning system according to a second embodiment of the invention,

[0063] [Fig.4] is a schematic view of a thermal conditioning system according to a first variant of the second embodiment of the invention,

[0064] [Fig.5] is a schematic view of a thermal conditioning system according to a second variant of the second embodiment of the invention,

[0065] [Fig.6] is a schematic view of a thermal conditioning system according to a third embodiment of the invention,

[0066] [Fig.7] is a schematic view of a thermal conditioning system according to a fourth embodiment of the invention,

[0067] [Fig.8] is a schematic view of a thermal conditioning system according to a variant of the fourth embodiment of the invention,

[0068] [Fig.9] is a schematic view of the thermal conditioning system of the [Fig.2], operating according to a first operating mode, called passenger compartment cooling and battery cooling mode,

[0069] [Fig. 10] is a schematic view of the thermal conditioning system of [Fig.3], operating according to the first operating mode, called passenger compartment cooling and battery cooling mode,

[0070] [Fig. 11] is a schematic view of the thermal conditioning system of [Fig.8], operating in a second operating mode, called battery cooling mode,

[0071] [Fig. 12] is a schematic view of the thermal conditioning system of [Fig.6], operating according to a third operating mode, called passenger compartment dehumidification and battery heating mode,

[0072] [Fig. 13] is a schematic view of the thermal conditioning system of [Fig.7], operating according to the third operating mode, called passenger compartment dehumidification and battery heating mode,

[0073] [Fig. 14] is a schematic view of the thermal conditioning system of [Fig.5], operating in a fourth operating mode, called heat pump and battery heating mode,

[0074] [Fig. 15] is a schematic view of the thermal conditioning system of [Fig.7], operating according to the fourth operating mode, called heat pump mode. heat and battery heating. Description of the embodiments

[0075] In order to facilitate the reading of the figures, the different elements are not necessarily represented to scale. In these figures, identical elements bear the same references. Certain elements or parameters may be indexed, that is to say designated for example by first element or second element, or even first parameter and second parameter, etc. This indexing is intended to differentiate similar, but not identical, elements or parameters. This indexing does not imply a priority of one element or parameter over another and the names may be interchanged.

[0076] In the following description, the expression "a first element upstream of a second element" means that the first element is placed before the second element relative to the direction of circulation, or path, of a fluid. Similarly, the term "a first element downstream of a second element" means that the first element is placed after the second element relative to the direction of circulation, or path, of the fluid in question. In the case of the refrigerant circuit, the term "a first element is upstream of a second element" means that the refrigerant passes successively through the first element, then the second element, without passing through the compression device. In other words, the refrigerant leaves the compression device, possibly passes through one or more elements, then passes through the first element, then the second element, then returns to the compression device, possibly after passing through other elements.

[0077] The expression "a second element is placed between a first element and a third element" means that the shortest path to go from the first element to the third element passes through the second element.

[0078] When it is specified that a subsystem comprises a given element, this does not exclude the presence of other elements in this subsystem.

[0079] The thermal conditioning system 100 which will be described comprises an electronic control unit, not shown, receiving information from various sensors measuring in particular the characteristics of the refrigerant fluid at various points in the circuit. The electronic control unit also receives instructions issued by the occupants of the vehicle, such as for example the desired temperature inside the passenger compartment. The electronic control unit can also receive instructions from other electronic subsystems, such as for example the electrical energy storage battery management system. The electronic control unit implements control laws allowing the various actuators to be controlled, in order to ensure control of the thermal conditioning system 100 so as to ensure the instructions received.

[0080] A compression device 7, also called a compressor, makes it possible to circulate a refrigerant fluid in a refrigerant fluid circulation circuit 10. The compression device 7 may be an electric compressor, i.e. a compressor whose moving parts are driven by an electric motor. The compression device 7 comprises a suction side for the refrigerant fluid at low pressure, also called the inlet 7a of the compression device, and a discharge side for the refrigerant fluid at high pressure, also called the outlet 7b of the compression device 7. The internal moving parts of the compressor 7 cause the refrigerant fluid to pass from a low pressure on the inlet side 7a to a high pressure on the outlet side 7b. After expansion in one or more expansion members and circulation in at least part of the circuit, the refrigerant fluid returns to the inlet 7a of the compressor 7 and begins a new thermodynamic cycle.

[0081] The refrigerant circuit 10 forms a closed circuit in which the refrigerant can circulate. The refrigerant circuit 10 is sealed when it is in a nominal operating state, that is to say without fault or leak. Each connection point of the circuit 10 allows the refrigerant to pass into 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 done by adjusting the opening or closing of the stop valves, non-return valves or expansion devices included on each of these portions. In other words, each connection point is a means of redirecting the refrigerant arriving at this connection point.Various shut-off valves and non-return valves thus make it possible to selectively direct the refrigerant fluid into the different branches of the refrigerant circuit, in order to ensure different operating modes, as will be described later.

[0082] The refrigerant fluid used by the refrigerant circuit 10 is here a natural fluid, such as R744. R290 can also be used. A chemical refrigerant fluid such as R1234yf, or 134a can also be used.

[0083] Interior air flow Fi is understood to mean an air flow to the passenger compartment of the motor vehicle. This interior air flow Fi can circulate in a heating, ventilation and / or air conditioning installation, frequently referred to by the English term "HVAC", for "Heating, Ventilating and Air Conditioning". This installation has not been shown in the various figures. A first motor-fan unit, not shown, is arranged in the heating, ventilation and / or air conditioning installation in order to increase the flow rate of the interior air flow Fi if necessary.

[0084] External air flow Fe is understood to mean an air flow which 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 rate provided by the first as well as by the second motor-fan unit can be adjusted in real time according to the heat exchange requirements, for example by the electronic control unit of the thermal conditioning system 100.

[0085] The term “first exchanger” is equivalent to the term “first heat exchanger”. Similarly, the term “internal exchanger” is equivalent to the term "internal heat exchanger". The term "accumulation device" is equivalent to the term "refrigerant accumulation device".

[0086] The heat transfer liquid circuit(s) also form one or more closed and sealed circuits in which a heat transfer liquid can circulate.

[0087] The term "loop" means a closed circuit for circulating fluid. Starting from any initial point in a loop and following this loop, we return to this initial point. A branch branch consists of exactly one input and one output. A branch branch is connected at each end to a portion of the circuit. Each connection is made at a connection point. A branch branch can connect two separate points in the same loop. A branch branch can also connect a loop and another branch branch. A branch branch can also connect two other branch branches.

[0088] [Fig. 1] schematically represents a first embodiment of a thermal conditioning system 100 for a motor vehicle. The thermal conditioning system 100 comprises a refrigerant circuit 10 configured to circulate a refrigerant. The refrigerant circuit 10 comprises a main loop A comprising successively, according to the direction of circulation of the refrigerant: - a compressor 7, - a first heat exchanger 1 thermally coupled with a first air flow Fl, - a first regulator 31, - a second heat exchanger 2 thermally coupled with an element 25 of an electric traction chain of a motor vehicle, - a second regulator 32, - a third heat exchanger 3 configured to exchange heat with an interior air flow Fi to a passenger compartment of the vehicle, - a refrigerant fluid accumulation device 9.

[0089] This refrigerant circuit architecture makes it possible to simply ensure numerous operating modes. In particular, this architecture makes it possible to cool the passenger compartment of a vehicle, while at the same time heating or cooling the element 25 of the electric powertrain, depending on the level of expansion provided by the first expansion valve 31.

[0090] The third exchanger 3, also called the passenger compartment evaporator, is arranged in the heating, ventilation and / or air conditioning system of the vehicle.

[0091] According to the first embodiment illustrated in [Fig.l] and according to the variant illustrated in [Fig.2], the first air flow Fl is an external air flow Fe to a passenger compartment of the vehicle.

[0092] According to the example of Figures 1 and 2, the first heat exchanger 1 exchanges heat with the outside air flow Fe. In this case, the first exchanger 1 is arranged for example on the front of the vehicle, just behind the grille in order to directly receive the air flow resulting from the vehicle's movement.

[0093] According to the examples illustrated in the various figures, the element 25 of the electric traction chain of the vehicle comprises an electrical energy storage battery. Alternatively or additionally, the element 25 of the electric traction chain of the vehicle may comprise an electric traction motor of the vehicle. Alternatively or additionally, the element 25 of the electric traction chain of the vehicle comprises an electronic unit for controlling the electric traction motor of the vehicle.

[0094] The first regulator 31 is for example an electronic regulator. Similarly, the second regulator 32 can be an electronic regulator. In an electronic expansion valve, the flow area for passing the refrigerant can be continuously adjusted between a minimum opening position and a maximum opening position. To achieve this, an electronic expansion valve control module drives an electric motor that moves a movable shutter controlling the flow area offered to the refrigerant. The minimum opening position can be a closed position, i.e. a position in which the flow of refrigerant through the expansion valve is interrupted. The flow rate of refrigerant through the expansion valve is then zero.

[0095] According to the second, third and fourth embodiments and their variants, illustrated in Figures 3 to 8, the thermal conditioning system 100 comprises a first bypass branch B connecting a first connection point 11, 11' arranged on the main loop A downstream of the first exchanger 1 and upstream of the second expansion valve 32 to a second connection point 12 arranged on the main loop A downstream of the third heat exchanger 3 and upstream of the accumulation device 9. The first branch of bypass B comprises a fourth heat exchanger 4 thermally coupled with an outside air flow Fe to the passenger compartment of the vehicle.

[0096] According to the embodiments of the thermal conditioning system 100 of FIGS. 3 to 8, the first air flow Fl is an interior air flow Fi to a passenger compartment of the vehicle. In this case, the first exchanger 1 is arranged in the heating, ventilation and / or air conditioning system of the vehicle. The first exchanger 1 is arranged downstream of the third exchanger 3 according to the flow direction of the interior air flow Fi.

[0097] According to the second embodiment and its variants, as well as according to the third embodiment, illustrated in Figures 3 to 6, the first branch branch B comprises a third expansion valve 33 arranged upstream of the fourth heat exchanger 4. The third regulator is arranged between the first connection point 11' and the fourth exchanger 4. Adding the first branch of bypass B allows operating modes to be added to the thermal conditioning system.

[0098] According to the second embodiment of the thermal conditioning system 100 and according to its first variant, as well as according to the third embodiment and according to the fourth embodiment, illustrated respectively in Figures 3, 4, 6 and 7, the first connection point 11 is arranged on the main loop A downstream of the first exchanger 1 and upstream of the first expander 31.

[0099] According to the variant of the second embodiment, illustrated in [Fig.5], the first connection point 11' is arranged on the main loop A downstream of the second exchanger 2 and upstream of the second regulator 32.

[0100] The thermal coupling between the fourth heat exchanger 4 and the outside air flow Fe can be of the so-called direct type or of the so-called indirect type.

[0101] According to the second embodiment, the third embodiment, and according to the fourth embodiment and its variant, the fourth heat exchanger 4 exchanges heat with the outside air flow Fe. This configuration is thus illustrated in [Fig.3] as well as in figures 6 to 8. The thermal coupling between the fourth heat exchanger 4 and the outside air flow Fe is then said to be direct.

[0102] According to the first variant and the second variant of the second embodiment, the fourth heat exchanger 4 exchanges heat with a heat transfer liquid of a first heat transfer liquid circuit 21, the first heat transfer liquid circuit 21 comprising a fifth heat exchanger 5 configured to exchange heat with the outside air flow Fe. This configuration is illustrated in Figures 4 and 5. The thermal coupling between the fourth heat exchanger 4 and the outside air flow Fe is then said to be indirect, since it is achieved by means of a heat transfer fluid. The heat transfer fluid is, for example, a mixture of water and glycol. A circulation pump, not shown, makes it possible to circulate the heat transfer fluid in the first circuit 21. The pump is, for example, an electric pump, which makes it possible to vary the flow rate of heat transfer fluid in the first heat transfer fluid circuit 21 on demand.

[0103] Similarly, the thermal coupling between the first heat exchanger 1 and the interior air flow Fi may be direct or indirect.

[0104] According to the exemplary embodiments of FIGS. 3, 6 and 8, the first heat exchanger 1 exchanges heat with the interior air flow Fi. The thermal coupling between the first heat exchanger 1 and the interior air flow Fi is then said to be direct.

[0105] According to the exemplary embodiments of Figures 4, 5 and 7, the first heat exchanger 1 exchanges heat with a heat transfer liquid of a second heat transfer liquid circuit 22, the second heat transfer liquid circuit 22 comprising a sixth heat exchanger 6 configured to exchange heat with the interior air flow Fi. The thermal coupling between the first heat exchanger 1 and the interior air flow Fi is then said to be indirect, since it is achieved by means of a heat transfer fluid. The heat transfer fluid is, for example, a mixture of water and glycol. The sixth heat exchanger 6 is arranged in the heating, ventilation and / or air conditioning system of the vehicle. The sixth exchanger 6 plays the same role as the first exchanger 1 when the interior air flow Fi passes through it.

[0106] According to the second variant of the second embodiment, illustrated in [Fig.5], the first heat exchanger 1 is also thermally coupled with a second air flow Fe outside a passenger compartment of the vehicle, by means of a fifth exchanger 5 arranged on a circuit 22 of heat transfer liquid. More specifically, the second heat transfer fluid circuit 22 comprises a heat exchanger configured to exchange heat with the outside air flow Fe. This heat exchanger configured to exchange heat with the outside air flow Fe is here the fifth exchanger 5. The fifth exchanger 5 comprises a first heat exchange section arranged on the first heat transfer liquid circuit 21, and a second heat exchange section arranged on the second heat transfer liquid circuit 22. Each heat exchange section allows a heat exchange between the heat transfer liquid circulating in the corresponding circuit, and the outside air flow Fe. According to another variant not shown, the exchanger of the second circuit 22 configured to exchange heat with the outside air flow Fe may be an exchanger separate from the fifth exchanger 5.

[0107] According to the example of [Fig.5], the second heat transfer liquid circuit 22 comprises a circulation pump 23. The second heat transfer liquid circuit 22 also comprises a three-way valve 40. The three-way valve 40 makes it possible to direct the heat transfer liquid coming from the first exchanger 1 to the sixth exchanger 6 or to the fifth exchanger 5. The first exchanger 1 can thus be selectively coupled to the interior air flow, via the sixth exchanger 6, or to the exterior air flow, via the fifth exchanger 5, depending on the position of the three-way valve 40 circulation imposed by the three-way valve 40.

[0108] According to the second embodiment, illustrated in [Fig. 3], the thermal conditioning system 100 comprises a second bypass branch C connecting a third connection point 13 arranged on the first bypass branch B downstream of the fourth exchanger 4 to a fourth connection point 14 arranged on the main loop A downstream of the first connection point 11 and upstream of the first expansion device 31. The second branch C is not present in the variants of the second embodiment, illustrated in Figures 4 and 5.

[0109] According to the third embodiment and according to the fourth embodiment, as well as its variant, illustrated in Figures 6 to 8, the thermal conditioning system 100 comprises a second bypass branch C' connecting a third connection point 13 arranged on the main loop A downstream of the compressor 7 and upstream of the first exchanger 1 to a fourth connection point 14 arranged on the first bypass branch B between the fourth exchanger 4 and the second connection point 12.

[0110] The addition of the second branch of bypass C makes it possible to add further operating modes to the thermal conditioning system. The third connection point 13 is located between the outlet 7b of the compressor 7 and the first exchanger 1. The fourth connection point 14 is located between the fourth exchanger 4 and the second connection point 12.

[0111] According to the fourth embodiment and its variant, shown diagrammatically in Figures 7 and 8, the thermal conditioning system 100 comprises a third branch of branch D connecting a fifth connection point 15 arranged on the main loop A downstream of the second heat exchanger 2 and upstream of the second expansion valve 32 to a sixth connection point 16 arranged on the first branch branch B between the first connection point 11 and the fourth heat exchanger 4.

[0112] The third branch of derivation D comprises a third regulator 33'. The third regulator 33 may be an electronic regulator.

[0113] The addition of the third branch of bypass D allows further operating modes to be added to the thermal conditioning system.

[0114] The fifth connection point 15 is located between the second exchanger 2 and the second regulator 32. The sixth connection point 16 is located between the first connection point 11 and the fourth exchanger 4.

[0115] The thermal conditioning system 100 may comprise an internal exchanger 8, 8'.

[0116] According to the variant of the first embodiment, illustrated in [Fig. 2], as well as in the other embodiments illustrated in Figures 3 to 5 and 7 to 8, the main loop A comprises an internal exchanger 8 configured to allow heat exchange between the refrigerant circulating between the first exchanger 1 and the first expansion valve 31 and the refrigerant circulating downstream of the accumulation device 9 and upstream of an inlet 7a of the compressor 7.

[0117] The internal exchanger makes it possible to improve the thermal performance of the thermal conditioning system 100 by increasing the enthalpy variation during the thermodynamic cycle carried out by the refrigerant fluid.

[0118] The internal exchanger 8 comprises a first heat exchange section 8a arranged on the main refrigerant loop between the first exchanger 1 and the first expansion valve 31. The internal exchanger 8 comprises a second heat exchange section 8b arranged on the main refrigerant loop A between the accumulator 9 and the inlet 7a of the compressor 7. The internal exchanger 8 is configured to allow heat exchange between the low-pressure refrigerant in the second heat exchange section 8b and the high-pressure refrigerant in the first heat exchange section 8a.

[0119] According to the second embodiment, [Fig.3], the first heat exchange section 8a is downstream of the fourth connection point 14. According to the first variant of the second embodiment, [Fig.4], the first heat exchange section 8a is downstream of the first connection point 11.

[0120] According to the third embodiment, corresponding to [Fig.6], the thermal conditioning system 100 comprises an internal exchanger 8' configured to allow heat exchange between the refrigerant fluid circulating in the first bypass branch B between the fourth exchanger 4 and the first connection point 11 and the refrigerant circulating in the main loop A downstream of the accumulation device 9 and upstream of an inlet 7a of the compressor 7.

[0121] The internal exchanger 8' comprises a first heat exchange section 8a' arranged on the first bypass branch B between the first connection point 11 and the third expansion valve 33. The internal exchanger 8 comprises a second heat exchange section 8b arranged on the main refrigerant loop A between the accumulator 9 and the inlet 7a of the compressor 7. The internal exchanger 8' is configured to allow heat exchange between the low pressure refrigerant in the second heat exchange section 8b' and the high pressure refrigerant in the first heat exchange section 8a'.

[0122] According to the example illustrated, an internal exchanger is present in all embodiments except the first embodiment, illustrated in [Fig.l]. The presence of the internal exchanger is however not essential. Variants of the second, third, fourth embodiment in which the internal exchanger is not present can be produced.

[0123] The thermal conditioning system 100 comprises a set of shutoff valves for selectively blocking or allowing the circulation of the refrigerant fluid. The different shutoff valves make it possible to selectively isolate or connect different portions of the refrigerant circuit 10, so as to allow different operating modes of the thermal conditioning system 100 to be carried out.

[0124] According to the second embodiment, as well as the third and fourth embodiments of the thermal conditioning system 100, the main loop A comprises a first stop valve 41, 41' arranged downstream of the compressor 7 and upstream of the first expander 31.

[0125] The first shut-off valve 41 may be arranged between the first connection point 11 and the fourth connection point 14. This configuration corresponds to the second embodiment, [Fig.3].

[0126] The first shut-off valve 41' can be arranged between the third connection point 13 and the first heat exchanger 1. This is the configuration of figures 6 to 8.

[0127] According to the second embodiment, as well as the third and fourth embodiments of the thermal conditioning system 100, the first bypass branch B comprises a second stop valve 42 arranged between the second connection point 12 and the third connection point 13. The first variant of the second embodiment, as well as the second variant, illustrated in Figures 4 and 5, do not include a shut-off valve on the first branch of derivation B.

[0128] According to the third and fourth embodiments, the second bypass branch C' comprises a third stop valve 43. The third shut-off valve 43 is arranged between the third connection point 13 and the fourth connection point 14.

[0129] According to the variant of the fourth embodiment of the thermal conditioning system 100, illustrated in [Fig.8], the first bypass branch B comprises a fourth stop valve 44.

[0130] The fourth shut-off valve 44 is arranged between the fourth connection point 14 and the sixth connection point 16.

[0131] The first stop valve 41,41' is for example an electrically controlled valve. Likewise, the second shutoff valve 42, the third shutoff valve 43 and the fourth shutoff valve 44 may be electrically operated valves. Each shut-off valve 41, 41', 42, 43, 44 is a two-way valve here. In other words, in the example illustrated each shut-off valve includes exactly one refrigerant inlet and one refrigerant outlet.

[0132] Each shutoff valve may be a two-position valve. A two-position valve is a valve with two stable equilibrium positions. In a first position corresponding to a closed state of the valve, the fluid passage section is zero and the circulation of fluid through the valve is blocked. According to a second position corresponding to an open state of the valve, the fluid passage section is maximum and the circulation of fluid through the valve is authorized.

[0133] Alternatively, the first shutoff valve 41' and the third shutoff valve 43 may be proportional valves. A proportional valve comprises a movable shutter whose position can vary continuously between a closed position and a maximum open position. A proportional valve thus not only allows the circulation of fluid to be selectively authorized or prohibited, but also allows the flow of fluid passing through the valve to be continuously adjusted.

[0134] In addition to the shutoff valves already described, the thermal conditioning system 100 comprises a set of one-way valves. A one-way valve allows fluid to flow through this valve in only one direction of flow. The various one-way valves contribute to selectively isolating or connecting different portions of the refrigerant circuit 10 so as to realize different operating modes.

[0135] According to the second embodiment, shown diagrammatically in [Fig. 3], the second bypass branch C comprises a first one-way valve 47 configured to allow circulation of refrigerant fluid through the first one-way valve 47 only from the third connection point 13 to the fourth connection point 14.

[0136] In other words, the first one-way valve 47 is configured to allow circulation of refrigerant fluid through the first one-way valve 47 from the third connection point 13 to the fourth connection point 14. and configured to prohibit circulation of refrigerant fluid through the first one-way valve 47 from the fourth connection point 14 to the third connection point 13.

[0137] According to the second and third embodiments, the main loop A comprises a first one-way valve 47' configured to allow circulation of refrigerant fluid through the first one-way valve 47' only from the first exchanger 1 to the first connection point 11.

[0138] In other words, the main loop A comprises a first one-way valve 47' configured to allow circulation of refrigerant fluid through the first one-way valve 47' of the first exchanger 1 to the first connection point 11 and configured to prohibit circulation of refrigerant fluid through the first one-way valve 47' of the first connection point 11 to the first exchanger 1.

[0139] According to the third and fourth embodiments, the main loop A comprises a second one-way valve 48 configured to allow circulation of refrigerant fluid through the second one-way valve 48 only from the third exchanger 3 to the second connection point 12.

[0140] In other words, the main loop A comprises a second one-way valve 48 configured to allow circulation of refrigerant fluid through the second one-way valve 48 of the third exchanger 3 to the second connection point 12, and configured to prohibit circulation of refrigerant fluid through the second one-way valve 48 of the second connection point 12 to the third exchanger 3.

[0141] According to the variant of the fourth embodiment, [Fig.8], the second one-way valve 48 is arranged between the third exchanger 3 and the eighth connection point 18.

[0142] According to the fourth embodiment and according to its variant, the first bypass branch B comprises a third one-way valve 49 configured to allow circulation of refrigerant fluid through the third one-way valve tional 49 only from the sixth connection point 16 to the first connection point 11.

[0143] In other words, the first bypass branch B comprises a third one-way valve 49 configured to allow circulation of refrigerant fluid through the third one-way valve 49 from the sixth connection point 16 to the first connection point 11 and configured to prohibit circulation of refrigerant fluid through the third one-way valve 49 from the first connection point 11 to the sixth connection point 16.

[0144] Each one-way valve 47, 48, 49 is for example a non-return valve. A check valve is a passive member reacting to the pressure difference existing between its inlet and its outlet. No electrical control is necessary.

[0145] The variant of the fourth embodiment, illustrated in [Fig.8], differs from the fourth embodiment by the presence of an additional bypass branch E and by the presence of an additional stop valve 44.

[0146] According to this variant, the thermal conditioning system 100 comprises a fourth bypass branch E connecting a seventh connection point 17 arranged on the main loop A between the fifth connection point 15 and the second expansion valve 32 to an eighth connection point 18 arranged on the main loop A between the third heat exchanger 3 and the second connection point 12. The fourth bypass branch E comprises a fifth stop valve 45.

[0147] The addition of the fourth bypass branch E allows the low-pressure refrigerant fluid coming from the second exchanger 2 to return to the accumulator 9 then the inlet 7a of the compressor 7 without passing through the second expansion valve 2 or the third exchanger 3. The pressure drop of the low-pressure circuit is thus reduced, which makes it possible to improve the thermodynamic performance in cooling mode of the element 25 alone.

[0148] The fifth shutoff valve 45 may be a two-position valve. The fifth shutoff valve 45 may also be a proportional valve. In this case, this valve makes it possible to adjust the quantity of refrigerant fluid which bypasses the third exchanger 3.

[0149] In the example shown, the seventh connection point 17 is the same as the fifth connection point 15. Similarly, the eighth connection point 18 is confused with the second connection point 12.

[0150] Figures 9 to 15 illustrate several operating modes of a thermal conditioning system according to different embodiments. In these figures, the portions of the refrigerant circuit 10 in which a The flow rates of refrigerant fluid circulated are in solid thick lines, while the portions in which the refrigerant fluid does not circulate are in thin dotted lines.

[0151] [Fig.9] illustrates a method of operating a thermal conditioning system 100 according to the first embodiment, in a first operating mode called passenger compartment cooling and battery cooling mode.

[0152] According to this mode of operation: - a total flow Q of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates successively in the main loop A, in the first exchanger 1 where it gives up heat to the outside air flow Fe, in the first expansion valve 31 where it passes at intermediate pressure, in the second exchanger 2 where it receives heat, in the second expansion valve 32 where it passes at low pressure, in the third exchanger 3 where it receives heat from the inside air flow Fi, in the accumulation device 9, and returns to the compressor 7.

[0153] The high-pressure refrigerant fluid passes through the first exchanger 1 and dissipates heat into the outside air flow Fe. The high-pressure refrigerant then passes through the first heat exchange section 8a of the internal exchanger 8. The cooled refrigerant fluid then undergoes two successive expansions, the first in the first expansion valve 31 then the second in the second expansion valve 32. The intermediate pressure refrigerant flow after the first expansion receives heat at the second exchanger 2, which cools the element 25 of the vehicle's electric powertrain. The low pressure refrigerant flow after the second expansion receives heat at the third exchanger 3, which cools the interior air flow Fi. Element 25 of the powertrain and the passenger compartment are jointly cooled. The respective level of expansion achieved by each of the expansion valves 31, 32 makes it possible to adjust the cooling power supplied on the one hand to the element 25 of the electric drive train and supplied on the other hand to the passenger compartment of the vehicle, i.e. to adjust the distribution of the cooling power. In all operating modes, the intermediate pressure is lower than the high pressure and results from an expansion. Similarly, the low pressure is lower than the high pressure and the intermediate pressure, and also results from an expansion. The refrigerant fluid coming from the accumulator 9 passes through the second heat exchange section 8b of the internal exchanger 8 before being re-drawn by the compressor 7.

[0154] [Fig. 10] illustrates a method of operating a thermal conditioning system 100 according to the second variant of the second embodiment, in the first operating mode called passenger compartment cooling mode and cooling- battery development.

[0155] According to this mode of operation: - a total flow Q of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates successively in the main loop A, in the first exchanger 1 where it gives off heat, in the first expansion valve 31 where it passes at intermediate pressure, in the second exchanger 2 where it receives heat, in the second expansion valve 32 where it passes at low pressure, in the third exchanger 3 where it receives heat from the interior air flow Fi, in the accumulation device 9, and returns to the compressor 7; - a flow D of heat transfer fluid circulates in the first exchanger 1 where it receives heat, then in the fifth exchanger 5 where it gives off heat to the outside air flow Fe, and returns to the first exchanger 1.

[0156] The high-pressure refrigerant fluid at the outlet of the compressor 7 passes through the first exchanger 1 and supplies heat to the heat transfer fluid of the circuit 22. The high-pressure refrigerant fluid is thus cooled. The cooled, high-pressure refrigerant then passes through the first heat exchange section 8a of the internal exchanger 8. As was the case with the first embodiment, in this mode of operation the refrigerant undergoes two successive expansions, the first in the first expansion valve 31 then the second in the second expansion valve 32. The level of expansion achieved by each of the expanders 31, 32 makes it possible to adjust the cooling power supplied on the one hand to the element 25 of the electric powertrain of the vehicle and on the other hand to the passenger compartment of the vehicle. The third expansion valve 33 is in the closed position, there is no circulation of refrigerant fluid in the bypass branch B and in the fourth exchanger 4. The refrigerant circulates only in the main loop A. The refrigerant fluid from the third exchanger 3 joins the accumulator 9 then passes through the second heat exchange section 8b of the internal exchanger 8 before joining the inlet 7a of the compressor 7. The heat transferred to the heat transfer fluid of the circuit 22 is dissipated in the outside air flow Fe. For this, the three-way valve 40 directs the heat transfer fluid from the first exchanger 1 to the fifth exchanger 5, and prevents the circulation of heat transfer fluid in the sixth exchanger 6. The circulation pump 23 is activated. The arrows designated by the sign D diagram the circulation of heat transfer fluid.

[0157] [Fig. 11] illustrates a method of operating a thermal conditioning system 100 according to the variant of the fourth embodiment, in a second operating mode called battery cooling mode.

[0158] According to this mode of operation: - a total flow Q of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates successively in the main loop A, in the second bypass branch C', in the first bypass branch B, in the fourth heat exchanger 4 where it gives off heat to the outside air flow Fe, in the main loop A, in the first expansion valve 31 where it passes at low pressure, in the second exchanger 2 where it receives heat, in the fourth bypass branch E, in the main loop A, in the accumulation device 9, and returns to the compressor 7.

[0159] The first shutoff valve 41' is in the closed position, and the third shutoff valve 43 is in the open position. Thus, the high-pressure refrigerant fluid from the compressor 7 is directed to the second bypass branch C'. The refrigerant from the third shut-off valve 43 leaves the second bypass branch C' at the fourth connection point 14 and joins the first bypass branch B. The second shut-off valve 42 is in the closed position, the refrigerant therefore flows from the fourth connection point 14 to the sixth connection point 16. The high-pressure refrigerant passes through the fourth exchanger 4 and dissipates heat into the outside air flow Fe, thus being cooled. The cooled refrigerant fluid then undergoes expansion by passing through the first expansion valve 31 and passes at low pressure. The low-pressure refrigerant flow receives heat and evaporates at the second exchanger 2, which cools the element 25 of the electric powertrain of the vehicle. The second expansion valve 32 is in the closed position and blocks the circulation of refrigerant fluid in the third exchanger 3. The fifth shutoff valve 45 is in the open position. The low-pressure refrigerant fluid coming from the second exchanger 2 is thus directed into the fourth bypass branch E without passing through the main loop portion A extending between the seventh connection point 17 and the eighth connection point 18 and comprising the second expansion valve 32 and the third exchanger 3. The pressure drop to reach the accumulator 9 is thus reduced, which makes it possible to increase the cooling power which can be provided by the second exchanger 2. The second one-way valve 48 prevents the low-pressure refrigerant from flowing from the eighth connection point 18 to the third exchanger 3 and accumulating there. The circulation in the internal exchanger 8 is the same as before.

[0160] It is also possible to partially open the third expansion valve 33', so that part of the refrigerant fluid coming from the fourth exchanger 4 circulates in the third bypass branch D, and therefore does not contribute to the heat exchanges in the internal exchanger 8. The efficiency of the internal exchanger 8 can thus be controlled by adjusting the opening of the third expansion valve 33', so as to adjust the flow rate of refrigerant circulating in the third bypass branch D and bypassing the internal exchanger 8. By reducing the efficiency of the internal exchanger 8, the temperature of the gaseous refrigerant at the inlet 7a of the compressor 7 can be limited, which also makes it possible to maintain the discharge temperature at the outlet 7b of the compressor 7 below an acceptable upper limit. The thermal stresses of the compressor 7 can thus be limited.

[0161] [Fig. 12] and [Fig. 13] illustrate a third mode of operation called passenger compartment dehumidification and battery heating mode. [Fig. 12] relates to the third embodiment and [Fig. 13] relates to the fourth embodiment.

[0162] According to this mode of operation: - a flow Q of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates successively in the main loop A, in the first exchanger 1 where it gives off heat, in the first expansion valve 31, in the second exchanger 2 where it gives off heat, in the second expansion valve 32 where it passes at low pressure, in the third exchanger 3 where it receives heat from the interior air flow Fi, in the accumulation device 9, and returns to the compressor 7.

[0163] The third stop valve 43 is in the closed position and the first stop valve 41' is in the open position, so as to direct the flow of refrigerant fluid coming from the compressor 7 to the first exchanger 1, via the main branch. At the third connection point 13, the circulation of refrigerant fluid in the second bypass branch C' is blocked. When the architecture of the refrigerant circuit 10 corresponds to the third embodiment, [Fig. 12], the second stop valve 42 is in the closed position, and prevents the refrigerant coming from the first exchanger 1 from circulating in the first bypass branch B from the first connection point 11. When the architecture of the refrigerant circuit 10 corresponds to the fourth embodiment, [Fig. 13], the third one-way valve 49 prevents the refrigerant coming from the first exchanger 1 from circulating in the first bypass branch B. The third expansion valve 33' and the second stop valve 42 are in the closed position. The high-pressure refrigerant circulates in the first exchanger 1, and heats the heat transfer fluid of the second circuit 22. The heated heat transfer fluid gives off heat to the interior air flow Fi at the sixth exchanger 6. The first expansion valve 31 is preferably in the maximum open position, and the refrigerant fluid does not undergo expansion there. The second expansion valve 32 expands the fluid refrigerant to a low pressure state. The third expansion valve 33 is in the closed position. The third bypass branch D is not traversed by the refrigerant fluid. It is also possible to cause a partial expansion of the refrigerant fluid at the level of the first expansion valve 31, so as to obtain different condensation pressures in the first exchanger 1 and in the second exchanger 2, and thus different temperature levels. The indoor air flow Fi is heated at the sixth exchanger 6 using the heat supplied by the refrigerant at the first exchanger 1. The indoor air flow Fi is also cooled at the third exchanger 3, which makes it possible to dehumidify the indoor air flow Fi. The heat released by the refrigerant fluid at the level of the second exchanger 2 makes it possible to heat the element 25 of the traction chain. The outside air flow Fe provides the heat necessary for the evaporation of the refrigerant in the fourth exchanger 4.

[0164] [Fig. 14] illustrates a method of operating a thermal conditioning system 100 according to the second variant of the second embodiment, in a fourth operating mode called heat pump and battery heating mode.

[0165] According to this mode of operation: - a flow Q of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates successively in the main loop A, in the first exchanger 1 where it gives off heat to the interior air flow Fi, in the first expansion valve 31, in the second exchanger 2 where it gives off heat, in the first bypass branch B, in the third expansion valve 33 where it passes at low pressure, in the fourth heat exchanger 4 where it receives heat from the exterior air flow Fe, in the main loop A, in the accumulation device 9, and returns to the compressor 7.

[0166] As previously, the first expansion valve 31 is preferably in the maximum open position, and the refrigerant fluid does not undergo expansion. The third expansion valve 33 expands the refrigerant fluid to a low pressure state. The second expansion valve 32 is in the closed position, and the refrigerant fluid coming from a second exchanger 2 does not circulate in the third expansion valve 3. At the first connection point 11', the refrigerant leaves the main loop A and takes the first bypass branch B. The interior air flow Fi is heated at the sixth exchanger 6 thanks to the heat transmitted by the refrigerant fluid to the heat transfer fluid of the second circuit 22 at the first exchanger 1. The heat released by the refrigerant fluid at the level of the second exchanger 2 allows also to heat element 25 of the traction chain. The outside air flow Fe provides the heat necessary for the evaporation of the refrigerant in the fourth exchanger 4. The total heating power supplied by the thermal conditioning system 100 can be divided between a power supplied to the indoor air flow Fi and a power supplied to the element 25. This distribution can be controlled by the respective expansion level of the first expansion valve 31 and the third expansion valve 33, as well as by controlling the indoor air flow Fi. The circulation of the refrigerant fluid in the internal exchanger 8 is the same as that already described. As for the previous operating mode, the first expansion valve 31 can be in the partially open position so as to achieve partial expansion of the refrigerant fluid at the first expansion valve 31. The condensation pressure in the first exchanger 1 can thus be different from the condensation pressure in the second exchanger 2, and different temperature levels can be obtained in the first exchanger 1 and the second exchanger 2.

[0167] [Fig. 15] illustrates a method of operating a thermal conditioning system 100 according to the fourth embodiment, in the fourth operating mode called heat pump and battery heating mode.

[0168] According to this mode of operation: - a flow Q of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates successively in the main loop A, in the first exchanger 1 where it gives off heat to the interior air flow Fi, in the first expansion valve 31, in the second exchanger 2 where it gives off heat, in the third bypass branch D, in the third expansion valve 33' where it passes at low pressure, in the second bypass branch B, in the fourth heat exchanger 4 where it receives heat from the exterior air flow Fe, in the main loop A, in the accumulation device 9, and returns to the compressor 7.

[0169] The heat exchanges take place in the same way when the architecture of the refrigerant circuit 10 corresponds to the fourth embodiment, and are identical to what was previously described for the second variant of the second embodiment. The refrigerant from the second exchanger 2 circulates in the third branch D and is expanded by the third expansion valve 33'. At the fifth connection point 15, the refrigerant leaves the main loop A and is redirected to the third branch D. At the sixth connection point 16, the refrigerant leaves the third branch D and joins the first branch B. At the second connection point 17, the refrigerant leaves the main loop A and is redirected to the third branch D. At the sixth connection point 18, the refrigerant leaves the third branch D and joins the first branch B. connection 12, the refrigerant fluid coming from the fourth exchanger 4 joins the main loop A. The third one-way valve 49 prevents the high-pressure refrigerant from the first exchanger 1 from circulating in the first bypass branch B, because the refrigerant cannot circulate from the first connection point 11 to the sixth connection point 16. The second shutoff valve 42 is in the open position, and the third shutoff valve 43 is in the closed position.

Claims

Claims

1. Thermal conditioning system (100) for a motor vehicle, comprising a refrigerant circuit (10) configured to circulate a refrigerant, the refrigerant circuit (10) comprising a main loop (A) successively comprising, according to the direction of circulation of the refrigerant: - a compressor (7), - a first heat exchanger (1) thermally coupled with a first air flow (Fl), - a first expansion valve (31), - a second heat exchanger (2) thermally coupled with an element (25) of an electric powertrain of a motor vehicle, - a second expansion valve (32), - a third heat exchanger (3) configured to exchange heat with an interior air flow (Fi) in a passenger compartment of the vehicle, - a refrigerant accumulation device (9).

2. A thermal conditioning system (100) according to claim 1, wherein the first airflow (Fl) is an exterior airflow (Fe) to a passenger compartment of the vehicle.

3. Thermal conditioning system (100) according to claim 1, comprising a first bypass branch (B) connecting a first connection point (11, 11') arranged on the main loop (A) downstream of the first exchanger (1) and upstream of the second expansion valve (32) to a second connection point (12) arranged on the main loop (A) downstream of the third heat exchanger (3) and upstream of the accumulation device (9), the first bypass branch (B) comprising a fourth heat exchanger (4) thermally coupled with an outside air flow (Fe) to the passenger compartment of the vehicle.

4. A thermal conditioning system (100) according to claim 3, wherein the first airflow (Fl) is an interior airflow (Fi) to a passenger compartment of the vehicle.

5. Thermal conditioning system (100) according to claim 3 or 4, wherein the first bypass branch (B) comprises a third expansion valve (33) disposed upstream of the fourth heat exchanger (4).

6. Thermal conditioning system (100) according to one of the claims- indications 3 to 5, in which the first connection point (11) is arranged on the main loop (A) downstream of the first exchanger (1) and upstream of the first regulator (31).

7. Thermal conditioning system (100) according to one of claims 3 to 5, in which the first connection point (11') is arranged on the main loop (A) downstream of the second exchanger (2) and upstream of the second expansion valve (32), and in which the first heat exchanger (1) is also thermally coupled with a second air flow (Fe) outside a passenger compartment of the vehicle, via a fifth exchanger (5) arranged on a circuit (22) of heat transfer liquid.

8. Thermal conditioning system (100) according to one of claims 3 to 6, comprising a second bypass branch (C) connecting a third connection point (13) arranged on the first bypass branch (B) downstream of the fourth exchanger (4) to a fourth connection point (14) arranged on the main loop (A) downstream of the first connection point (11) and upstream of the first expansion device (31).

9. Thermal conditioning system (100) according to one of claims 3 to 6, comprising a second bypass branch (C') connecting a third connection point (13) arranged on the main loop (A) downstream of the compressor (7) and upstream of the first exchanger (1) to a fourth connection point (14) arranged on the first bypass branch (B) between the fourth exchanger (4) and the second connection point (12).

10. Thermal conditioning system (100) according to the preceding claim, comprising a third bypass branch (D) connecting a fifth connection point (15) arranged on the main loop (A) downstream of the second heat exchanger (2) and upstream of the second expansion valve (32) to a sixth connection point (16) arranged on the first bypass branch (B) between the first connection point (11) and the fourth heat exchanger (4), in which the third bypass branch (D) comprises a third expansion valve (33').

11. Thermal conditioning system (100) according to one of claims 1 to 10, in which the main loop (A) comprises an internal exchanger (8) configured to allow heat exchange between the refrigerant fluid circulating between the first exchanger (1) and the first expansion valve (31) and the refrigerant fluid circulating downstream of the accumulation device (9) and upstream of an inlet (7a) of the compressor (7).

12. Thermal conditioning system (100) according to one of claims 1 to 10, comprising an internal exchanger (8') configured to allow heat exchange between the refrigerant circulating in the first bypass branch (B) between the fourth exchanger (4) and the first connection point (11) and the refrigerant circulating in the main loop (A) downstream of the accumulation device (9) and upstream of an inlet (7a) of the compressor (7).

13. Thermal conditioning system (100) according to one of the preceding claims in combination with claim 8, wherein: - the main loop (A) comprises a first shutoff valve (41, 41') arranged downstream of the compressor (7) and upstream of the first expander (31), and - the first bypass branch (B) comprises a second shutoff valve (42) arranged between the second connection point (12) and the third connection point (13).

14. Thermal conditioning system (100) according to one of the preceding claims, wherein the main loop (A) comprises: - a first one-way valve (47') configured to allow circulation of refrigerant fluid through the first one-way valve (47') only from the first exchanger (1) to the first connection point (11), and - a second one-way valve (48) configured to allow circulation of refrigerant fluid from the third exchanger (3) to the second connection point (12) and configured to prohibit circulation of refrigerant fluid from the second connection point (12) to the third exchanger (3).

15. Thermal conditioning system (100) according to one of the preceding claims in combination with claim 10, comprising a fourth bypass branch (E) connecting a seventh connection point (17) arranged on the main loop (A) between the fifth connection point (15) and the second expansion valve (32) to an eighth connection point (18) arranged on the main loop (A) between the third heat exchanger (3) and the second connection point (12),

16.

17.

18. the fourth branch branch (E) comprising a fifth stop valve (45). Method of operating a thermal conditioning system (100) according to claim 1, in a mode called passenger compartment cooling and battery cooling in which: - a total flow rate (Q) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates successively in the main loop (A), in the first exchanger (1) where it gives up heat to the outside air flow (Fe), in the first expansion valve (31) where it passes at intermediate pressure, in the second exchanger (2) where it receives heat, in the second expansion valve (32) where it passes at low pressure, in the third exchanger (3) where it receives heat from the inside air flow (Fi), in the accumulation device (9), and returns to the compressor (7). Method of operating a thermal conditioning system (100) according to claim 7, in a mode called passenger compartment cooling and battery cooling in which: - a total flow rate (Q) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates successively in the main loop (A), in the first exchanger (1) where it gives off heat, in the first expansion valve (31) where it passes at intermediate pressure, in the second exchanger (2) where it receives heat, in the second expansion valve (32) where it passes at low pressure, in the third exchanger (3) where it receives heat from the interior air flow (Fi), in the accumulation device (9), and returns to the compressor (7), - a flow (D) of heat transfer fluid circulates in the first exchanger (1) where it receives heat, then in the fifth exchanger (5) where it gives off heat to the outside air flow (Fe), and returns to the first exchanger (1). Method of operating a thermal conditioning system (100) according to claim 15, in a so-called battery cooling mode in which: - a total flow rate (Q) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates successively in the main loop (A), in the second bypass branch (C'), in the first bypass branch (B), in the fourth heat exchanger (4) where it gives off heat to the outside air flow (Fe), in the main loop (A), in the first expansion valve (31) where it passes at low

19.

20.

21. pressure, in the second exchanger (2) where it receives heat, in the fourth bypass branch (E), in the main loop (A), in the accumulation device (9), and returns to the compressor (7). Method of operating a thermal conditioning system (100) according to claim 9 or 10, in a mode called passenger compartment dehumidification and battery heating in which: - a flow (Q) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates successively in the main loop (A), in the first exchanger (1) where it gives off heat, in the first expansion valve (31), in the second exchanger (2) where it gives off heat, in the second expansion valve (32) where it passes at low pressure, in the third exchanger (3) where it receives heat from the interior air flow (Fi), in the accumulation device (9), and returns to the compressor (7). Method of operating a thermal conditioning system (100) according to claim 7, in a so-called heat pump and battery heating mode in which: - a flow (Q) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates successively in the main loop (A), in the first exchanger (1) where it gives off heat to the interior air flow (Fi), in the first expansion valve (31), in the second exchanger (2) where it gives off heat, in the first bypass branch (B), in the third expansion valve (33) where it passes at low pressure, in the fourth heat exchanger (4) where it receives heat from the exterior air flow (Fe), in the main loop (A), in the accumulation device (9), and returns to the compressor (7). Method for operating a thermal conditioning system (100) according to claim 9 or 10, in a so-called heat pump and battery heating mode in which: - a flow (Q) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates successively in the main loop (A), in the first exchanger (1) where it gives off heat to the interior air flow (Fi), in the first expansion valve (31), in the second exchanger (2) where it gives off heat, in the third bypass branch (D), in the third expansion valve (33') where it passes at low pressure, in the second bypass branch (B), in the fourth heat exchanger (4) where it receives heat from the exterior air flow (Fe), in the main loop (A), in the device accumulation (9), and returns to the compressor (7).

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