Thermal conditioning system

Abstract

The invention relates to a thermal conditioning system (100) for a motor vehicle, comprising a refrigerant circuit (10) comprising: - a main loop (A) comprising, successively: -- a compressor (7), -- a first exchanger (1) thermally coupled with an internal air flow (Fi) to a passenger compartment of the vehicle, -- a first expansion valve (31), -- a second expansion valve (32), -- a second exchanger (2) thermally coupled with an external air flow (Fe) to the passenger compartment of the vehicle, -- a refrigerant accumulation device (8), -- a first bypass branch (B) of the main loop (A), which branch comprises a third expansion valve (33), -- a second bypass branch (C) of the main loop (A), which branch comprises successively a fourth expansion valve (34) and a third exchanger (3), wherein the main loop (A) comprises an internal exchanger (6) configured to allow heat to be exchanged between the refrigerant circulating between the first expansion valve (31) and the second expansion valve (32) and the refrigerant downstream of the accumulation device (8) and upstream of an inlet (7a) of the compressor (7).

Description

Description Title: THERMAL CONDITIONING SYSTEM Technical field [1] 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. Prior art [2] So-called chemical refrigerants generally have a high global warming potential (GWP), which is a disadvantage. Carbon dioxide can be used as a refrigerant, which by definition has a global warming coefficient of one. The thermodynamic properties of this gas mean that the compressor discharge pressure is generally in the range of 80 to 130 bar, so that the system provides sufficient thermal power. The discharge temperature of the refrigerant for this pressure range can in some applications be problematic for the compressor, as it is too high. In addition, this high discharge temperature can also be problematic for certain components through which the high-pressure, high-temperature refrigerant circulates. [3] In addition, in the case of an electric vehicle, it may be necessary to be able to heat the battery, in particular in order to be able to charge it quickly in cold ambient temperatures, especially negative ones. Dedicated heating devices can be used. Such dedicated devices increase the price and weight of the thermal conditioning system. [4] There is therefore a need for a thermal conditioning system to control the discharge temperature of the refrigerant fluid and to heat the battery. Summary [5] For this purpose, a thermal conditioning system for a motor vehicle is proposed, comprising a refrigerant circuit configured to circulate a refrigerant, the refrigerant 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 an air flow inside a passenger compartment of the vehicle, -- a first regulator, -- a second regulator, -- a second heat exchanger configured to exchange heat with an air flow outside the vehicle passenger compartment, -- a refrigerant fluid accumulation device, A first bypass branch connecting a first connection point arranged on the main loop downstream of a compressor outlet and upstream of the first exchanger to a second connection point arranged on the main loop downstream of the second heat exchanger and upstream of the accumulation device, the first bypass branch comprising a third expansion valve, - A second bypass branch connecting a third connection point arranged on the main loop between the first exchanger and the second expansion valve to a fourth connection point arranged on the main loop downstream of the second exchanger and upstream of the accumulation device, the second bypass branch successively comprising a fourth expansion valve and a third heat exchanger, in which the main loop comprises an internal exchanger configured to allow heat exchange between the refrigerant circulating between the first expansion valve and the second expansion valve and the refrigerant fluid downstream of the accumulation device and upstream of a compressor inlet. [6] In some operating modes of the thermal conditioning system, the refrigerant circulating between the first expansion valve and the second expansion valve circulates from the first expansion valve to the second expansion valve. [7] In other modes of operation, the refrigerant circulating between the first expansion valve and the second expansion valve circulates from the second expansion valve to the first expansion valve. [8] This refrigerant circuit architecture allows heat to be transferred to the indoor air flow at the first heat exchanger and selectively absorb heat or transfer heat to the outdoor air flow at the second exchanger, by controlling the pressure at the inlet of the second exchanger. The second exchanger can selectively absorb a controlled amount of heat from the ambient air, or transfer a controlled amount of heat to the ambient air. In both cases, the efficiency of the internal heat exchanger can also be controlled, which allows the compressor discharge temperature to be controlled. [9] The features listed in the following paragraphs can be implemented independently of each other or in any technically possible combination:

[0010] According to one embodiment, the first heat exchanger is configured to exchange heat with an airflow interior to a passenger compartment of the vehicle.

[0011] According to an alternative embodiment, the first heat exchanger is configured to exchange heat with a heat transfer fluid circulating in a closed heat transfer fluid circuit, the heat transfer fluid circuit comprising a heat exchanger configured to exchange heat with an air flow inside the passenger compartment of the vehicle.

[0012] The internal heat exchanger comprises a first heat exchange section arranged on the main loop between the first expansion valve and the second expansion valve, as well as a second heat exchange section arranged on the main loop downstream of the accumulator and upstream of the compressor inlet. The internal heat exchanger is configured to allow heat exchange between the refrigerant in the first heat exchange section and the refrigerant in the second heat exchange section.

[0013] According to one embodiment, the third heat exchanger is thermally coupled with an element of an electric powertrain of a motor vehicle.

[0014] The third heat exchanger allows the vehicle's electric powertrain element to be selectively cooled or heated.

[0015] According to an exemplary embodiment, the element of the electric powertrain of the vehicle comprises an electrical energy storage battery.

[0016] Alternatively or additionally, the element of the vehicle's electric powertrain comprises an electric vehicle traction motor.

[0017] Alternatively or additionally, the element of the vehicle's electric drive train comprises an electronic unit for controlling the vehicle's electric traction motor.

[0018] According to an exemplary embodiment, the third heat exchanger is thermally coupled with the element of the electric traction chain by means of a heat transfer fluid circulating in a heat transfer fluid circuit.

[0019] The first regulator is, for example, an electronic regulator. Similarly, the second regulator, the third regulator, the fourth regulator can be electronic regulators.

[0020] According to one embodiment, the thermal conditioning system comprises: - A third branch connecting a fifth connection point arranged on the main loop between the second regulator and the first regulator to a sixth connection point arranged on the main loop between the second connection point and the fourth connection point, the third branch successively comprising a fifth expansion valve and a fourth heat exchanger configured to exchange heat with the indoor airflow.

[0021] The fourth heat exchanger can cool the interior airflow to the passenger compartment, so as to cool the passenger compartment.

[0022] In this embodiment, the refrigerant circuit may comprise a first one-way valve disposed on the main loop between the sixth connection point and the fourth connection point. The first one-way valve is configured to allow circulation of refrigerant from the sixth connection point to the fourth connection point and configured to prohibit circulation of refrigerant from the fourth connection point to the sixth connection point.

[0023] The first one-way valve is for example a check valve.

[0024] According to another embodiment, the thermal conditioning system comprises: - A third branch branch connecting a fifth connection point arranged on the second branch branch between the third connection point and the fourth expansion valve to a sixth connection point arranged on the second branch branch between the third exchanger and the fourth connection point, the third branch branch successively comprising a fifth expansion valve and a fourth heat exchanger configured to exchange heat with the interior air flow.

[0025] With this arrangement of the third bypass branch, the fourth heat exchanger can selectively cool the interior airflow to the passenger compartment or heat this interior airflow.

[0026] The fourth exchanger is arranged upstream of the first exchanger according to the direction of flow of the interior air.

[0027] In this embodiment, the refrigerant circuit comprises a first one-way valve arranged on the third bypass branch between the fourth exchanger and the sixth connection point. The first one-way valve is configured to allow circulation of refrigerant fluid from the fifth connection point to the sixth connection point and configured to prohibit circulation of refrigerant fluid from the sixth connection point to the fifth connection point.

[0028] According to one embodiment, the thermal conditioning system comprises: - A fourth branch connection connecting a seventh connection point located on the main loop downstream of the first connection point and upstream of the first exchanger to an eighth connection point located on the second branch connection downstream of the fourth regulator and upstream of the fourth connection point, the fourth branch connection comprising a sixth regulator.

[0029] The fourth bypass branch allows the high-pressure, high-temperature refrigerant at the compressor outlet to return to the compressor inlet without passing through the first or second exchanger. The fourth bypass branch returns the high-pressure refrigerant to the accumulator inlet. The flow circulating in the fourth bypass branch increases the total flow of refrigerant supplied by the compressor and thus increases the heating thermal power provided by the refrigerant.

[0030] According to an alternative embodiment of the thermal conditioning system, the eighth connection point is arranged downstream of the third exchanger.

[0031] According to another embodiment, the eighth connection point is arranged upstream of the third exchanger.

[0032] According to yet another variant embodiment, the thermal conditioning system comprises a fourth bypass branch connecting a seventh connection point arranged on the main loop downstream of the first connection point and upstream of the first exchanger to an eighth connection point arranged on the main loop downstream of the fourth connection point and upstream of the accumulation device, the fourth bypass branch comprising a sixth expansion valve.

[0033] According to one embodiment, the thermal conditioning system comprises: - A fifth branch connection connecting a ninth connection point located on the second branch connection downstream of the third exchanger and upstream of the fourth connection point to a tenth connection point located on the main loop between the third connection point and the second regulator.

[0034] According to an alternative embodiment of the thermal conditioning system, the tenth connection point is arranged between the first expansion valve and the internal exchanger.

[0035] According to an alternative embodiment of the thermal conditioning system, the tenth connection point is arranged between the internal exchanger and the second expansion valve.

[0036] The refrigerant circuit comprises a second one-way valve disposed on the fifth branch branch. The second one-way valve is configured to allow refrigerant to flow from the ninth connection point to the tenth connection point and configured to prohibit refrigerant to flow from the tenth connection point to the ninth connection point.

[0037] The fifth bypass branch allows the high-pressure or intermediate-pressure refrigerant fluid leaving the third exchanger to join the main loop and from there reach the compressor inlet. The fifth bypass branch thus allows the refrigerant fluid to provide heat to the element of the electric traction chain at the third exchanger, i.e. it allows heating of the element of the electric traction chain.

[0038] The second one-way valve is, for example, a check valve.

[0039] The ninth connection point can be confused with the sixth connection point.

[0040] According to one embodiment of the thermal conditioning system, the second branch branch comprises a seventh regulator arranged between the ninth connection point and the fourth connection point.

[0041] The seventh expansion valve expands the refrigerant from the third exchanger before it mixes with the refrigerant leaving the fourth exchanger. The fourth exchanger can therefore operate at a higher pressure than the third exchanger, and therefore at a higher temperature.

[0042] When the fourth branch is present, the seventh regulator is arranged between the ninth connection point and the eighth connection point.

[0043] According to an exemplary embodiment of the thermal conditioning system, the fifth branch branch includes an eighth regulator.

[0044] The eighth expansion valve allows the refrigerant fluid coming from the third exchanger to be expanded before it enters the first heat exchange section of the internal exchanger, and therefore controls the heat exchange in the internal exchanger.

[0045] The eighth regulator is, for example, a calibrated orifice.

[0046] According to one embodiment, the first regulator is arranged between the first exchanger and the third connection point.

[0047] According to another embodiment, the first regulator is arranged between the tenth connection point and the third connection point.

[0048] The refrigerant circuit may include a third one-way valve arranged on the main loop between the first exchanger and the third connection point. The third one-way valve is configured to allow circulation of refrigerant fluid from the first exchanger to the third connection point and configured to prohibit circulation of refrigerant fluid from the third connection point to the first exchanger.

[0049] The third one-way valve is, for example, a check valve.

[0050] The main loop includes a first shutoff valve disposed between the first connection point and the first heat exchanger.

[0051] The first shut-off valve is located between the first connection point and the seventh connection point.

[0052] The main loop includes a second shut-off valve located between the second connection point and the fourth connection point.

[0053] The second shut-off valve is arranged between the second connection point and the sixth connection point.

[0054] The first shut-off valve is an electrically operated valve. The second shut-off valve is an electrically operated valve.

[0055] The first shut-off valve is a two-way valve. Similarly, the second shut-off valve is a two-way valve.

[0056] According to one embodiment, the thermal conditioning system comprises a refrigerant distribution module comprising: - a first refrigerant fluid inlet, - a second refrigerant fluid inlet, - a first refrigerant fluid outlet, - a second refrigerant outlet, - a first channel connecting the first input to the first output, - a second channel connecting the second input to a connection point arranged on the first channel between the first input and the first output, - a third channel connecting the second output to the connection point, - a seventh regulator placed on the first channel between the connection point and the first outlet, - a one-way valve arranged on the second channel between the connection point and the second outlet, in which: the first channel partly forms the second branch, the second channel partly forms the third branch of the diversion, the third channel partly forms the fifth branch of the diversion.

[0057] The integration of certain components and part of the refrigerant circulation circuit in the form of a distribution module facilitates the mechanical integration of the components and reduces the overall size.

[0058] The channels of the refrigerant distribution module are formed by internal recesses of a metal block.

[0059] The refrigerant distribution module may include an eighth expansion valve located on the third channel.

[0060] According to another embodiment, the thermal conditioning system comprises a refrigerant distribution module comprising: - a first refrigerant fluid inlet, - a second refrigerant fluid inlet / outlet, - a third refrigerant fluid inlet / outlet, - a first channel connecting the second input / output to the third input / output, - a second channel connecting the first input to a connection point arranged on the first channel between the second input / output and the third input / output, - the first regulator, - a one-way valve arranged on the second channel between the first inlet and the connection point, in which: the first regulator is arranged on the first channel between the third inlet / outlet and the connection point, the first channel partly forms the main loop, the second channel partly forms the fifth bypass branch.

[0061] The channels of the refrigerant distribution module are formed by internal recesses of a metal block.

[0062] The refrigerant distribution module may include an eighth expansion valve arranged on the second channel.

[0063] The invention also relates to a method of operating a thermal conditioning system as described previously, in a mode known as passenger compartment dehumidification and battery cooling in which: — a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and is divided between: -- a second flow circulating in the main loop, successively in the first exchanger where it gives off heat to the interior air flow, in the first expansion valve where it passes to intermediate pressure, -- a third flow circulating in the first branch of the bypass, successively in the third expansion valve where it passes at intermediate pressure, in the second exchanger where it gives off heat to the flow of outside air, in the second expansion valve, in the internal exchanger, and is divided between: — a fourth flow circulating in the third bypass branch, successively in the fifth regulator where it passes at low pressure, in the fourth exchanger where it receives heat from the interior air flow, in the main loop, — a fifth flow circulating in the main loop and joining the second flow, the second flow and the fifth flow forming a sixth flow circulating in the second bypass branch, successively in the fourth expansion valve where it passes at low pressure, in the third exchanger where it receives heat, and joins the fourth flow, the sixth flow and the fourth flow forming the total flow, the total flow formed circulates in the main loop, successively in the accumulation device, in the internal exchanger, and returns to the compressor.

[0064] The intermediate pressure value is lower than the high pressure value.

[0065] The low pressure value is lower than the intermediate pressure value.

[0066] The invention also relates to a method of operating a thermal conditioning system as described previously, in a so-called mode of battery heating with energy recovery from outside air in which: - a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates in the main loop, in the first exchanger, in the second bypass branch, successively in the fourth expansion valve where it passes at intermediate pressure, in the third heat exchanger where it gives off heat, in the fifth bypass branch, in the main loop successively in the internal exchanger, in the second expansion valve where it passes at low pressure, in the second exchanger where it receives heat from the outside air flow, in the accumulation device, in the internal exchanger, and returns to the compressor.

[0067] In this operating mode, the total flow of refrigerant can transfer heat to the indoor air flow at the first exchanger.

[0068] In this operating mode, the total flow of refrigerant can also circulate in the first exchanger without giving up heat to the interior air flow.

[0069] The invention also relates to a method of operating a thermal conditioning system as already described, in a mode known as battery heating and passenger compartment heating with recovery of energy from the outside air in which: - a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates in the main loop, in the first exchanger where it gives off heat to the interior air flow, and is divided between: -- a second flow circulating in the second branch of the bypass, successively in the fourth regulator where it passes at intermediate pressure, in the third heat exchanger where it gives off heat, -- a third flow circulating in the third bypass branch, successively in the fifth expansion valve where it passes at intermediate pressure, in the fourth heat exchanger where it gives off heat to the internal air flow, and joins the second flow, the second flow and the third flow forming the total flow, the total flow formed circulating in the fifth bypass branch, in the main loop successively in the internal exchanger, in the second expansion valve where it passes at low pressure, into the second exchanger where it receives heat from the outside air flow, into the accumulation device, into the internal exchanger, and returns to the compressor.

[0070] The invention also relates to a method of operating a thermal conditioning system as described, in a mode known as passenger compartment dehumidification with recovery of energy from the outside air in which: - a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates in the main loop, in the first exchanger where it gives off heat to the interior air flow, and is divided between: -- a second flow circulating in the third branch of the bypass, successively in the fifth regulator where it passes at intermediate pressure, in the fourth heat exchanger where it receives heat from the internal air flow, in the main loop, in the seventh regulator where it passes at low pressure, -- a third flow circulating in the main loop, successively in the first expansion valve, in the internal exchanger, in the second expansion valve where it passes at low pressure, in the second heat exchanger where it receives heat from the outside air flow, and joins the second flow, the second flow and the third flow forming the total flow, the total flow formed circulating in the main loop A successively in the accumulation device, in the internal exchanger, and returns to the compressor.

[0071] The fourth exchanger and the second exchanger both operate as evaporators. At the fourth exchanger, the refrigerant receives heat from the indoor airflow, in order to cool and dehumidify it. At the second exchanger, the refrigerant receives heat from the outdoor airflow, this heat contributing to heating the indoor airflow at the first exchanger. The pressure in the fourth exchanger can be higher than the pressure in the second exchanger, since the refrigerant from the fourth exchanger undergoes an expansion by passing through the seventh expansion valve before joining the refrigerant from the second exchanger. The evaporation temperature in the fourth exchanger can therefore be higher. than that in the second exchanger. It is therefore possible to recover heat at the second exchanger even at negative ambient temperatures, without risking icing the fourth exchanger.

[0072] The invention also relates to a method of operating a thermal conditioning system as described previously, in a mode known as accelerated heating of the passenger compartment and the battery in which: - a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, circulates in the main loop and is divided between: -- a second flow circulating in the main loop, in the first exchanger where it gives off heat to the interior air flow, in the second bypass branch, successively in the fourth expansion valve where it passes to intermediate pressure, in the third heat exchanger where it gives off heat, in the seventh expansion valve where it passes to low pressure, -- a third flow circulating in the fourth branch of the bypass, in the sixth expander where it undergoes expansion, and joins the second flow, the second flow and the third flow thus forming the total flow, the total flow formed circulates in the main loop, successively in the accumulation device, in the internal exchanger and returns to the compressor.

[0073] The invention also relates to a method of operating a thermal conditioning system as described above, in a mode known as passenger compartment heating and energy recovery in which: - a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates in the main loop, in the first exchanger where it gives off heat to the interior air flow, and is divided between: -- a second flow circulating in the second branch of the bypass, successively in the fourth regulator where it passes to a first intermediate pressure, in the third heat exchanger where it receives heat, in the seventh regulator where it passes to low pressure, -- a third flow circulating in the main loop, successively in the first regulator where it passes to a second intermediate pressure greater than or equal to the first intermediate pressure, in the internal exchanger, in the second expansion valve where it passes at low pressure, in the second exchanger where it receives heat from the outside air flow, and joins the second flow, the second flow and the third flow thus forming the total flow, the total flow formed circulates in the main loop, successively in the accumulation device, in the internal exchanger and returns to the compressor. Brief description of the drawings

[0074] Other features, details and advantages will become apparent upon reading the detailed description below, and upon analyzing the attached drawings, in which:

[0075] [Fig. 1] is a schematic view of a thermal conditioning system according to a first embodiment of the invention,

[0076] [Fig. 2] is a schematic view of a thermal conditioning system according to a first variant of the first embodiment of the invention,

[0077] [Fig. 3] is a schematic view of a thermal conditioning system according to a second variant of the first embodiment of the invention,

[0078] [Fig. 4] is a schematic view of a thermal conditioning system according to a second embodiment of the invention,

[0079] [Fig. 5] is a schematic view of a thermal conditioning system according to a first variant of the second embodiment of the invention,

[0080] [Fig. 6] is a schematic view of a thermal conditioning system according to a second variant of the second embodiment of the invention,

[0081] [Fig. 7] is a schematic view of a thermal conditioning system according to a third variant of the second embodiment of the invention,

[0082] [Fig. 8] is a schematic view of a thermal conditioning system according to a fourth variant of the second embodiment of the invention,

[0083] [Fig. 9] is a schematic view of the thermal conditioning system of Figure 1, operating according to a first operating mode, called passenger compartment dehumidification and battery cooling mode,

[0084] [Fig. 10] is a schematic view of the thermal conditioning system of Figure 4, operating in a second mode of operation, called battery heating mode with energy recovery from the outside air,

[0085] [Fig. 1 1 ] is a schematic view of the thermal conditioning system of Figure 5, operating in a third mode of operation, called battery heating mode and passenger compartment heating with recovery of energy from the outside air,

[0086] [Fig. 12] is a schematic view of the thermal conditioning system of Figure 5, operating in a fourth mode of operation, called passenger compartment dehumidification mode with energy recovery from the outside air,

[0087] [Fig. 13] is a schematic view of the thermal conditioning system of Figure 4, operating in a fourth operating mode, called accelerated heating mode of the passenger compartment and the battery,

[0088] [Fig. 14] is a schematic view of the thermal conditioning system of Figure 4, operating in one mode, called passenger compartment heating and energy recovery mode. Description of the embodiments

[0089] To facilitate reading the figures, the different elements are not necessarily represented to scale. In these figures, identical elements have the same references. Some elements or parameters may be indexed, i.e. designated for example by first element or second element, or 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.

[0090] 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 with respect 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 with respect 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.

[0091] The expression "a second element is placed between a first element and a third element" means that the shortest path from the first element to the third element or from the third element to the first element passes through the second element.

[0092] When it is specified that a subsystem includes a given element, this does not exclude the presence of other elements in this subsystem.

[0093] The thermal conditioning system 100 which will be described comprises an electronic control unit 60 receiving information from various sensors measuring in particular the characteristics of the refrigerant fluid at various points in the circuit. The electronic control unit 60 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 60 can also receive instructions from other electronic subsystems, such as for example the electrical energy storage battery management system. The electronic control unit 60 implements control laws allowing the control of the various actuators, in order to ensure the control of the thermal conditioning system 100 so as to ensure the instructions received.

[0094] A compression device 7, also called a compressor, makes it possible to circulate a refrigerant fluid in a refrigerant circulation circuit 10. The compression device 7 may be an electric compressor, that is to say a compressor whose moving parts are driven by an electric motor. The compression device 7 comprises a suction side for the low-pressure refrigerant fluid, also called the inlet 7a of the compression device, and a side discharge of the refrigerant fluid at high pressure, also called 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 devices 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.

[0095] 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, i.e. without defects or leaks. 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 achieved by adjusting the opening or closing of the shut-off 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.

[0096] The refrigerant used by the refrigerant circuit 10 is here a natural fluid, such as R744. It is also possible to use a chemical refrigerant, such as R1234yf, or R134a.

[0097] Each refrigerant fluid expansion device, also called an expansion valve, can be an electronic expansion valve. In an electronic expansion valve, the flow area for passing the refrigerant fluid can be continuously adjusted between a closed position and a maximum open position. To do this, an electronic expansion valve control module drives an electric motor that moves a movable shutter controlling the flow area offered to the refrigerant fluid. In the closed position, also called the closed position, the circulation of refrigerant fluid is interrupted, i.e. the flow of refrigerant fluid passing through the electronic expansion valve is zero. In the fully open position, the refrigerant passes through the expansion valve without undergoing expansion.

[0098] 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.

[0099] Outside air flow Fe is understood to mean 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 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 unit 60 for controlling the thermal conditioning system 100.

[0100] 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".

[0101] The heat transfer fluid circuit(s) also form one or more closed and sealed circuits in which a heat transfer fluid can circulate.

[0102] Figure 1 shows a thermal conditioning system 100 for a motor vehicle, comprising 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 fluid: - a compressor 7, -- a first heat exchanger 1 thermally coupled with an interior air flow Fi to a passenger compartment of the vehicle, -- a first regulator 31, -- a second regulator 32, -- a second heat exchanger 2 configured to exchange heat with an outside air flow Fe to the passenger compartment of the vehicle, -- a refrigerant fluid accumulation device 8, A first bypass branch B connecting a first connection point 11 arranged on the main loop A downstream of an outlet 7b of the compressor 7 and upstream of the first exchanger 1 to a second connection point 12 arranged on the main loop A downstream of the second heat exchanger 2 and upstream of the accumulation device 8, the first bypass branch B comprising a third expansion valve 33, - A second bypass branch C connecting a third connection point 13 arranged on the main loop A between the first exchanger 1 and the second expansion valve 32 to a fourth connection point 14 arranged on the main loop A downstream of the second exchanger 2 and upstream of the accumulation device 8, the second bypass branch C successively comprising a fourth expansion valve 34 and a third heat exchanger 3. The main loop A comprises an internal exchanger 6 configured to allow heat exchange between the refrigerant circulating between the first expansion valve 31 and the second expansion valve 32 and the refrigerant downstream of the accumulation device 8 and upstream of an inlet 7a of the compressor 7.

[0103] The accumulation device 8, also called an accumulator, forms a storage volume for liquid refrigerant. The accumulation device 8 makes it possible to compensate for variations depending on the operating conditions in the quantity of refrigerant circulating in the circuit 10. The accumulation device 8 also makes it possible to separate the liquid phase and the gaseous phase of the refrigerant so as to supply the compressor 7 with refrigerant in gaseous form.

[0104] According to certain operating modes of the thermal conditioning system 100, the refrigerant circulating between the first expansion valve 31 and the second expansion valve 32 circulates from the first expansion valve 31 to the second expansion valve 32. According to other modes of operation of the thermal conditioning system 100, the refrigerant circulating between the first expansion valve 31 and the second expansion valve 32 circulates from the second expansion valve 32 to the first expansion valve 31.

[0105] This refrigerant circuit architecture makes it possible to transfer heat to the indoor air flow Fi at the first heat exchanger 1 and to selectively absorb heat or transfer heat to the outdoor air flow Fe at the second exchanger 2, while controlling the pressure at the inlet of the second exchanger 2. The second exchanger 2 can selectively absorb a controlled amount of heat from the outdoor air Fe, or transfer a controlled amount of heat to the outdoor air Fe. In both cases, the efficiency of the internal heat exchanger 6 can be controlled by controlling the pressure at the inlet of the internal exchanger 6, which makes it possible to control the discharge temperature of the compressor 7. Discharge temperature is understood to mean the temperature of the refrigerant at the outlet of the compressor 7.

[0106] According to one embodiment, the first heat exchanger 1 is configured to exchange heat with an interior air flow Fi to a passenger compartment of the vehicle. The thermal coupling between the first heat exchanger 1 and the interior air flow Fi is said to be direct. Indeed, the air flow Fi is in contact with the walls of the heat exchanger in which the refrigerant circulates. In this embodiment, the first exchanger 1 is arranged in the heating, ventilation and / or air conditioning system of the vehicle.

[0107] According to an alternative embodiment, shown in FIG. 2, the first heat exchanger 1 is configured to exchange heat with a heat transfer fluid circulating in a closed heat transfer fluid circuit 30. The heat transfer fluid circuit 30 comprises a heat exchanger 1 B configured to exchange heat with an interior air flow Fi in the passenger compartment of the vehicle. The thermal coupling between the first heat exchanger 1 and the interior air flow Fi is in this case called indirect, since it is achieved by means of a heat transfer fluid which transfers the heat supplied by the refrigerant fluid to the air flow Fi supplying the passenger compartment of the vehicle. The heat transfer fluid circulating in the circuit 30 is, for example, a mixture of water and glycol. According to this variant, the heat exchanger 1 B, also called a heating radiator, is arranged in the heating, ventilation and / or air conditioning system of the vehicle.

[0108] The second exchanger 2 is for example arranged in the front face of the vehicle, in order to directly receive the flow of outside air. The second exchanger 2 can be arranged just behind the grille of the vehicle. The grille can include a movable flap making it possible to control, that is to say to vary on demand, the passage section of the flow of outside air in the grille.

[0109] The internal heat exchanger 6 comprises a first heat exchange section 6a arranged on the main loop A between the first expansion valve 31 and the second expansion valve 32. The internal heat exchanger 6 also comprises a second heat exchange section 6b arranged on the main loop A downstream of the accumulator 8 and upstream of the inlet 7a of the compressor 7. The internal heat exchanger 6 is configured to allow heat exchange between the refrigerant in the first heat exchange section 6a and the refrigerant in the second heat exchange section 6b.

[0110] The refrigerant circulating at high pressure in the main loop A can thus transfer heat to the refrigerant circulating at a lower pressure in the main loop A.

[0111] The third heat exchanger 3 is thermally coupled with an element 25 of an electric drive train of a motor vehicle.

[0112] The third heat exchanger 3 makes it possible to selectively cool or heat the element 25 of the electric powertrain of the vehicle. The element 25 of the electric powertrain of the vehicle can thus be maintained, or placed, in a preferred temperature range corresponding to the optimal operation of the element.

[0113] Element 25 of the electric drive train of the vehicle here comprises an electrical energy storage battery.

[0114] Alternatively or additionally, the element 25 of the electric traction chain of the vehicle comprises an electric traction motor of the vehicle.

[0115] 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.

[0116] According to the illustrated example, the third heat exchanger 3 is thermally coupled with the element 25 of the electric traction chain by means of a heat transfer liquid circulating in a heat transfer liquid circuit 40.

[0117] The heat transfer fluid circulating in the heat transfer fluid circuit 40 can exchange heat on the one hand with the refrigerant fluid circulating in the third heat exchanger 3 and on the other hand with the element 25 of the electric powertrain of the vehicle. The heat transfer fluid thus allows a heat transfer between the refrigerant fluid and the element 25 of the electric powertrain. For example, the heat transfer fluid circulates between the battery cells, or inside the wall of the electric motor, or the electric motor. The heat transfer fluid circuit 40 and the heat transfer fluid circuit 30 are not connected. In other words, the heat transfer fluid of the circuit 40 does not mix with the heat transfer fluid of the circuit 30. The heat transfer fluid of the circuit 40 may be a dielectric fluid. When the heat transfer fluid of the circuit 40 is a dielectric liquid, it may be in direct contact with electrically energized components.

[0118] The first regulator 31 is for example an electronic regulator. Similarly, the second regulator 32, the third regulator 33, the fourth regulator 34 may be electronic regulators.

[0119] According to the embodiment of FIG. 1, the thermal conditioning system 100 comprises a third bypass branch D1 connecting a fifth connection point 15-1 arranged on the main loop A between the second expansion valve 32 and the first expansion valve 31 to a sixth connection point 16-1 arranged on the main loop A between the second connection point 12 and the fourth connection point 14. The third branch D1 successively comprises a fifth expansion valve 35 and a fourth heat exchanger 4 configured to exchange heat with the interior air flow Fi.

[0120] The fourth heat exchanger 4 allows the interior air flow Fi to be cooled to the passenger compartment, so as to cool the passenger compartment and ensure the thermal comfort of the passengers.

[0121] In this embodiment, the refrigerant circuit 10 comprises a first one-way valve 43-1 arranged on the main loop A between the sixth connection point 16-1 and the fourth connection point 14. The first one-way valve 43-1 is configured to allow circulation of refrigerant fluid from the sixth connection point 16-1 to the fourth connection point 14. The first one-way valve 43-1 is also configured to prohibit circulation of refrigerant fluid from the fourth connection point 14 to the sixth connection point 16-1. The first one-way valve 43-1 is a check valve in the example shown. A check valve is a passive device that reacts to the pressure difference between its inlet and outlet. No electrical control is required.

[0122] According to an alternative embodiment, illustrated in Figure 3, the thermal conditioning system 100 comprises a third branch D2 connecting a fifth connection point 15-2 arranged on the second branch C between the third connection point 13 and the fourth regulator 34 to a sixth connection point 16-2 arranged on the second bypass branch C between the third exchanger 3 and the fourth connection point 14. The third branch D2 successively comprises a fifth expansion valve 35 and a fourth heat exchanger 4 configured to exchange heat with the interior air flow Fi. In other words, the third branch of derivation can be chosen according to two distinct variants D1 and D2. These two variants are mutually exclusive, that is to say that if the refrigerant circuit 10 comprises a third branch of type D1, no branch of type D2 is present, and vice versa.

[0123] Tank] The fourth exchanger 4 is arranged in the heating, ventilation and / or air conditioning system of the vehicle. The fourth exchanger 4 is arranged upstream of the exchanger ensuring the heating of the interior air flow Fi, which is, depending on the embodiment, the first exchanger 1 or the exchanger 1 B.

[0124] According to this embodiment variant, the refrigerant circuit 10 comprises a first one-way valve 43-2 arranged on the third bypass branch D2 between the fourth exchanger 4 and the sixth connection point 16-2. The first one-way valve 43-2 is configured to allow circulation of refrigerant fluid from the fifth connection point 15-2 to the sixth connection point 16-2 and configured to prohibit circulation of refrigerant fluid from the sixth connection point 16-2 to the fifth connection point 15-2.

[0125] When the first exchanger 1 is traversed by refrigerant fluid, the same direction of circulation is identical in all operating modes. Similarly, the third exchanger 3 and the fourth exchanger 4 are always traversed in the same direction of circulation of the refrigerant fluid, when they are traversed by refrigerant fluid. Depending on certain operating modes, the circulation of refrigerant fluid in each exchanger may be blocked.

[0126] The direction of circulation of the refrigerant fluid in the second exchanger 2 may be reversed depending on the operating modes of the thermal conditioning system. In particular, the direction of operation may be different depending on whether the second exchanger 2 transfers heat to the outside air flow Fe or receives heat from the outside air flow Fe.

[0127] In the same way, the direction of circulation in the first heat exchange section 6a of the internal exchanger 6 can be reversed depending on the operating modes of the thermal conditioning system. In other words, according to certain operating modes the first heat exchange section 6a of the internal exchanger 6 receives the refrigerant coming from the second expansion valve 32, and according to other operating modes the first heat exchange section 6a of the internal exchanger 6 supplies the refrigerant to the second expansion valve 32. The second expansion valve 32 is a bidirectional expansion valve.

[0128] The direction of circulation in the second heat exchange section 6b of the internal exchanger 6 is constant. This means that the direction of circulation of the refrigerant fluid in the second heat exchange section 6b is identical for all operating modes of the thermal conditioning system 100.

[0129] According to one embodiment, illustrated in Figures 4 to 8, the thermal conditioning system 100 comprises a fourth bypass branch E connecting a seventh connection point 17 arranged on the main loop A downstream of the first connection point 11 and upstream of the first exchanger 1 to an eighth connection point 18 arranged on the second bypass branch C downstream of the fourth expansion valve 34 and upstream of the fourth connection point 14. The fourth bypass branch E comprises a sixth expansion valve 36.

[0130] The fourth bypass branch E allows the high pressure and high temperature refrigerant fluid at the outlet of the compressor 7 to return to the inlet 7a of the compressor without passing through the first exchanger 1 or the second exchanger 2. The fourth bypass branch E brings the refrigerant fluid back to high pressure to the inlet of the accumulator 8. The flow circulating in the fourth bypass branch E makes it possible to increase the total flow of refrigerant fluid supplied by the compressor 7 and thus increase the thermal heating power supplied by the refrigerant fluid.

[0131] According to the variants of figures 4 to 7, the eighth connection point 18 is arranged downstream of the third exchanger 3. The refrigerant flowing through the fourth branch E does not pass through the third exchanger 3.

[0132] According to the variant of figure 8, the eighth connection point 18 is arranged upstream of the third exchanger 3. The eighth connection point 18 is thus arranged between the outlet 34b of the fourth expansion valve 34 and the inlet 3a of the third exchanger 3. The refrigerant fluid flowing through the fourth bypass branch E can flow through the third exchanger 3 then join the main loop A at the fourth connection point 14.

[0133] According to another variant embodiment, not shown, the thermal conditioning system 100 comprises a fourth bypass branch E connecting a seventh connection point 17 arranged on the main loop A downstream of the first connection point 11 and upstream of the first exchanger 1 to an eighth connection point 18 arranged on the main loop A downstream of the fourth connection point 14 and upstream of the accumulation device 8. As previously, the fourth bypass branch E comprises a sixth expansion valve 36. In other words, in this variant not shown the eighth connection point 18 is arranged between the fourth connection point 14 and the input of the accumulator 8.

[0134] According to one embodiment, illustrated in particular in Figures 4 to 8, the thermal conditioning system 100 comprises a fifth branch F connecting a ninth connection point 19 arranged on the second branch C downstream of the third exchanger 3 and upstream of the fourth connection point 14 to a tenth connection point 20 arranged on the main loop A between the third connection point 13 and the second regulator 32.

[0135] According to the variants of figures 4 to 7, the tenth connection point 20 is arranged between the first regulator 31 and the internal exchanger 6.

[0136] According to the variant of figure 8, the tenth connection point 20 is arranged between the internal exchanger 6 and the second regulator 32.

[0137] The refrigerant circuit 10 comprises a second one-way valve 44 arranged on the fifth bypass branch F. The second one-way valve 44 is configured to allow circulation of refrigerant from the ninth connection point 19 to the tenth connection point 20 and configured to prohibit circulation of refrigerant from the tenth connection point 20 to the ninth connection point 19.

[0138] The second one-way valve 44 is, for example, a non-return valve.

[0139] The fifth branch F allows the high-pressure or intermediate-pressure refrigerant fluid at the outlet of the third exchanger 3 to join the main loop A, pass through the second expansion valve 32 and the second exchanger 2, then join the inlet 7a of the compressor 7. The seventh expansion valve 37 makes it possible to block the circulation of refrigerant fluid from the ninth connection point 19 to the fourth connection point 14, so that the refrigerant fluid coming from the third exchanger 3 passes through the fifth branch F. The fifth branch F thus allows the refrigerant fluid to supply heat to the element 25 of the electric traction chain at the third exchanger 3, that is to say that this branch makes it possible to heat the element 25 of the electric traction chain.

[0140] In the same way, when the third bypass branch is of type D2, as illustrated in figure 5, the high pressure or intermediate pressure refrigerant fluid at the outlet of the fourth exchanger 4 can join the main loop A by circulating in the fifth bypass branch F. The fourth exchanger 4 can thus heat the interior air flow Fi.

[0141] The ninth connection point 19 can be confused with the sixth connection point 16-2.

[0142] According to the second embodiment of the thermal conditioning system 100, illustrated in particular in FIGS. 4 to 8, the second branch branch C comprises a seventh regulator 37 arranged between the ninth connection point 19 and the fourth connection point 14.

[0143] When the third branch branch is of type D1, as illustrated in Figure 4, the seventh expansion valve 37 allows the refrigerant fluid coming from the third exchanger 3 to be expanded before it mixes with the refrigerant fluid leaving the fourth exchanger 4. The fourth exchanger 4 can therefore operate at a lower pressure than that of the third exchanger 3, therefore at a lower evaporation temperature. The fourth exchanger 4 and the third exchanger 3 can thus each provide cooling, with two different temperature levels.

[0144] In addition, when the third branch branch is of type D2, as illustrated in Figure 5, the seventh expansion valve 37 makes it possible to expand the refrigerant fluid coming from the fourth exchanger 4 before it mixes with the refrigerant fluid at the outlet of the second exchanger 2. As previously, the fourth exchanger 4 can therefore operate at a higher pressure than that of the second exchanger 2, therefore at a higher evaporation temperature. This case is used for example during an operating mode aimed at dehumidifying the air in the passenger compartment, which will be described later.

[0145] When the fourth branch E is present and connected to the second branch C downstream of the third exchanger 3, the seventh regulator 37 is arranged between the ninth connection point 19 and the eighth connection point 18. This configuration is illustrated in Figures 4 to 7.

[0146] The fifth branch of derivation F may include an eighth regulator 38. The eighth regulator 38 is for example a calibrated orifice. The eighth regulator 38 is optional, i.e. it may not be present.

[0147] The eighth expansion valve makes it possible to expand the refrigerant fluid coming from the third exchanger 3 before it enters the first heat exchange section 6a of the internal exchanger 6, and thus to control the heat exchange in the internal exchanger 6.

[0148] According to the first embodiment and its variants, illustrated in Figures 1 to 3, the first regulator 31 is arranged between the first exchanger 1 and the third connection point 13.

[0149] According to the second embodiment, illustrated in Figures 4 to 8, the first regulator 31 is arranged between the tenth connection point 20 and the third connection point 13.

[0150] The refrigerant circuit 10 comprises a third one-way valve 45 arranged on the main loop A between the first exchanger I and the third connection point 13. The third one-way valve 45 is configured to allow circulation of refrigerant fluid from the first exchanger 1 to the third connection point. 13. The third one-way valve 45 is also configured to prohibit circulation of refrigerant fluid from the third connection point 13 to the first exchanger 1. The third one-way valve 45 is for example a non-return valve.

[0151] Each non-return valve 43, 44, 45 can be replaced by an electrically controlled valve controlled so as to ensure the same conditions of circulation of the refrigerant fluid.

[0152] The main loop A comprises a first shut-off valve 41 arranged between the first connection point 11 and the first heat exchanger 1. The first shut-off valve 41 is arranged between the first connection point II and the seventh connection point 17.

[0153] The main loop A comprises a second shut-off valve 42 arranged between the second connection point 12 and the fourth connection point 14. The second shut-off valve 42 is arranged between the second connection point 12 and the sixth connection point 16-1.

[0154] The first shut-off valve 41 is an electrically operated valve. Similarly, the second shut-off valve 42 is an electrically operated valve. The first shut-off valve 41 is a two-way valve. Similarly, the second shut-off valve 42 is a two-way valve.

[0155] Figures 6 and 7 show diagrammatically two variants of the second embodiment in which part of the circuit 10 is formed by a refrigerant fluid distribution module.

[0156] According to the variant of figure 6, the thermal conditioning system 100 comprises a refrigerant fluid distribution module 50 comprising: - a first inlet 11 of refrigerant fluid, - a second refrigerant fluid inlet I2, - a first outlet S1 of refrigerant fluid, - a second S2 refrigerant outlet, - a first channel C1 connecting the first input 11 to the first output S1, - a second channel C2 connecting the second input I2 to a connection point P arranged on the first channel C1 between the first input 11 and the first output S1, - a third channel C3 connecting the second output S2 to the connection point P, - a seventh regulator 37 arranged on the first channel C1 between the connection point P and the first output S1, - a one-way valve 44 arranged on the second channel C2 between the connection point P and the second outlet S. The first channel C1 partly forms the second branch of the C branch. The second channel C2 partly forms the third branch of derivation D2. The third channel C3 partly forms the fifth branch of the F branch.

[0157] The distribution module 50 integrates certain components and forms part of the refrigerant circulation circuit, which facilitates the mechanical integration of the components. The distribution module 50 can be delivered pre-assembled, which reduces the number of components to be assembled on the vehicle. In addition, the overall footprint is reduced.

[0158] The connection point P is here confused with the sixth connection point 16-2 and with the ninth connection point 19.

[0159] The channels C1, C2, C3 of the refrigerant distribution module 50 are formed by internal recesses of a metal block. The distribution module 50 can for example be obtained by casting aluminum and machining.

[0160] The refrigerant fluid distribution module 50 may comprise an eighth expansion valve 38 arranged on the third channel C3. The eighth regulator 38 is for example arranged on the third channel C3 between the connection point P and the one-way valve 44.

[0161] Figure 7 shows a diagram of a 50' distribution module according to another definition.

[0162] In this variant, the 50' refrigerant distribution module comprises: - a first 11' refrigerant fluid inlet, - a second ES2' refrigerant fluid inlet / outlet, - a third ES3' refrigerant fluid inlet / outlet, - a first channel C1' connecting the second input / output ES2' to the third input / output ES3', - a second channel C2' connecting the first input 11' to a connection point P' arranged on the first channel C1' between the second input / output ES2' and the third input / output ES3', - the first regulator 31, - a one-way valve 44 arranged on the second channel C2' between the first inlet 11' and the connection point P'. The first regulator 31 is arranged on the first channel C1' between the third input / output ES3' and the connection point P'. The first channel C1' partly forms the main loop A. The second channel C2' partly forms the fifth branch of derivation F.

[0163] The connection point P' is here confused with the tenth connection point 20.

[0164] As previously, the channels C1', C2' of the refrigerant fluid distribution module 50' are for example formed by internal recesses of a metal block.

[0165] The refrigerant fluid distribution module 50' may comprise an eighth regulator 38 arranged on the second channel C2'. The eighth regulator 38 is for example arranged on the second channel C2' between the first inlet 11' and the one-way valve 44.

[0166] Figures 9 to 14 illustrate several operating modes of the thermal conditioning system 100. These different modes can be selectively activated, for example by the control unit 60, according to the instructions of the occupants of the vehicle and according to the conditions of use.

[0167] Figure 9 illustrates a method of operating a thermal conditioning system 100 according to the first embodiment, in a mode known as passenger compartment dehumidification and battery cooling. In this mode of operation: — a total flow Q1 of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and is divided between: -- a second flow Q2 circulating in the main loop A, successively in the first exchanger 1 where it gives off heat to the interior air flow Fi, in the first expansion valve 31 where it passes to intermediate pressure, -- a third flow Q3 circulating in the first branch of bypass B, successively in the third expansion valve 33 where it passes at intermediate pressure, in the second exchanger 2 where it gives off heat to the external air flow Fe, in the second expansion valve 32, in the internal exchanger 6, and is divided between: — a fourth flow Q4 circulating in the third bypass branch D1, successively in the fifth regulator 35 where it passes at low pressure, in the fourth exchanger 4 where it receives heat from the interior air flow Fi, in the main loop A, — a fifth flow Q5 circulating in the main loop A and joining the second flow Q2, the second flow Q2 and the fifth flow Q5 forming a sixth flow Q6 circulating in the second branch of bypass C, successively in the fourth expander 34 where it passes at low pressure, in the third exchanger 3 where it receives heat, and joins the fourth flow Q4, the sixth flow Q6 and the fourth flow Q4 forming the total flow Q1, the total flow Q1 circulates successively in the accumulation device 8, in the internal exchanger 6, and returns to the compressor 7.

[0168] The value of the “high pressure” type pressure is for example between 80 bars and 120 bars. The so-called "intermediate" pressure value is lower than the high pressure value. For example, intermediate pressure is between 40 bars and 70 bars. The value of the so-called “low pressure” is lower than the value of the intermediate pressure. Low pressure is for example between 1 bar and 50 bars.

[0169] In this operating mode, the indoor air flow Fi is cooled at the fourth exchanger 4, and heated at the first exchanger 1, which makes it possible to dehumidify the indoor air flow Fi. The refrigerant absorbs heat from element 25 of the traction chain at the third exchanger 3, which allows element 25 of the traction chain to be cooled. The third expansion valve 33 makes it possible to control the value of the intermediate pressure in the second exchanger 2, and thus the quantity of heat dissipated in the external air flow Fe. In addition, the control of the intermediate pressure makes it possible to control the quantity of heat exchanged at the level of the internal exchanger 6. The internal exchanger 6 participates in the heat exchanges, since the first heat exchange section 6a and the second heat exchange section 6b are both traversed by the refrigerant fluid. The second shut-off valve 42 is in the closed position, which prevents the circulation of refrigerant fluid in the portion of the main loop A between the second connection point 12 and the sixth connection point 16-1. All other portions of the refrigerant circuit 10 are traversed by fluid refrigerant. The fifth flow rate Q5 can take negative values, i.e. flow from the third connection point 13 to the fifth connection point 15-1. In this case, the fourth flow rate Q4 is greater than the third flow rate Q3. When the fifth flow rate is positive, as is the case in Figure 9, the circulation of refrigerant fluid takes place from the fifth connection point 15-1 to the third connection point 13. The third flow rate Q3 is then greater than the fifth flow rate Q5. The direction of the flow rate Q5 depends on the respective values ​​of the flow rates Q2, Q3 and Q6, which vary according to the conditions of use.

[0170] Figure 10 illustrates a method of operating a thermal conditioning system 100 according to the second embodiment, in a so-called battery heating mode with recovery of energy from the outside air. In this mode of operation: - a total flow Q of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates in the main loop A, in the first exchanger 1, in the second bypass branch C, successively in the fourth expansion valve 34 where it passes at intermediate pressure, in the third heat exchanger 3 where it gives off heat, in the fifth bypass branch F, in the main loop A successively in the internal exchanger 6, in the second expansion valve 32 where it passes at low pressure, in the second exchanger 2 where it receives heat from the outside air flow Fe, in the accumulation device 8, in the internal exchanger 6, and returns to the compressor 7.

[0171] In this operating mode, the total flow rate Q of refrigerant can transfer heat to the indoor air flow Fi at the first exchanger 1. For this, the flow rate of the indoor air flow Fi can be controlled to a non-zero value.

[0172] In this operating mode, the total flow rate Q of refrigerant can also circulate in the first exchanger 1 without giving up heat to the indoor air flow Fi. For this, the flow rate of the indoor air flow Fi is, for example, maintained at a zero value.

[0173] In this mode of operation, the refrigerant transfers heat to element 25 of the traction chain at the level of the third exchanger 3, which allows the element 25 of the traction chain to be heated. The fourth pressure reducer 34 allows the intermediate pressure value to be controlled. The low-pressure refrigerant receives heat from the outside air flow Fe at the second exchanger 2. The direction of circulation of the refrigerant fluid in the second exchanger 2 is reversed compared to the previous operating mode. The internal exchanger 6 participates in heat exchanges. The fourth exchanger 4 is not traversed by the refrigerant fluid. The fifth expansion valve 35 is in the closed position, which blocks the circulation of refrigerant fluid in the third bypass branch D1. The portion of the second branch C between the ninth connection point 19 and the fourth connection point 14 is not traversed by the refrigerant fluid. The portion of main loop A between the third connection point 13 and the tenth connection point 20 is not crossed by the refrigerant fluid, the first expansion valve 31 being in the closed position. Similarly, the first branch of bypass B and the fourth branch of bypass E are not crossed by the refrigerant fluid.

[0174] Figure 11 illustrates a method of operating a thermal conditioning system 100 according to the first variant of the second embodiment, in a mode known as battery heating and passenger compartment heating with recovery of energy from the outside air. In this mode of operation: - a total flow Q1 of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates in the main loop A, in the first exchanger 1 where it gives off heat to the interior air flow Fi, and is divided between: -- a second flow Q2 circulating in the second branch of bypass C, successively in the fourth expansion valve 34 where it passes at intermediate pressure, in the third heat exchanger 3 where it gives off heat, -- a third flow Q3 circulating in the third branch of bypass D2, successively in the fifth expansion valve 35 where it passes at pressure intermediate, in the fourth heat exchanger 4 where it gives up heat to the internal air flow Fi, and joins the second flow Q2, the second flow Q2 and the third flow Q3 forming the total flow Q1, the total flow Q1 formed circulating in the fifth branch of derivation F, in the main loop A successively in the internal exchanger 6, in the second expansion valve 32 where it passes at low pressure, in the second exchanger 2 where it receives heat from the external air flow Fe, in the accumulation device 8, in the internal exchanger 6, and returns to the compressor 7.

[0175] This operating mode differs from the previous mode in that the flow of refrigerant fluid leaving the first exchanger 1 can be divided at the fifth connection point 15-2 and circulate in parallel in the third exchanger 3 and in the fourth exchanger 4. This division is made possible by the particular arrangement of the third branch branch D2. The third exchanger 3 and the fourth exchanger 4 can thus provide heating, respectively, of the element 25 of the powertrain, and of the interior air flow Fi. The interior air flow Fi is thus heated both at the first exchanger 1 and at the fourth exchanger 4, which makes it possible to increase the heating power and the speed at which the temperature of the passenger compartment rises.

[0176] The low-pressure refrigerant receives heat from the outside air flow Fe at the second exchanger 2. The first branch of bypass B and the fourth branch of bypass E are not crossed by the refrigerant fluid. The portion of the second branch C between the ninth connection point 19 and the fourth connection point 14 is not traversed by the refrigerant fluid. The portion of main loop A between the third connection point 13 and the tenth connection point 20 is not crossed by the refrigerant fluid, the first expansion valve 31 being in the closed position. The internal exchanger 6 participates in heat exchanges.

[0177] Figure 12 illustrates a method of operating a thermal conditioning system 100 according to the first variant of the second mode of realization, in a mode called passenger compartment dehumidification with recovery of energy from the outside air. In this mode of operation: - a total flow Q1 of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates in the main loop A, in the first exchanger 1 where it gives off heat to the interior air flow Fi, and is divided between: -- a second flow Q2 circulating in the third bypass branch D2, successively in the fifth expander 35 where it passes at intermediate pressure, in the fourth heat exchanger 4 where it receives heat from the interior air flow Fi, in the main loop A, in the seventh expander 37 where it passes at low pressure, -- a third flow Q3 circulating in the main loop A, successively in the first expander 31, in the internal exchanger 6, in the second expander 32 where it passes at low pressure, in the second heat exchanger 2 where it receives heat from the external air flow Fe, and joins the second flow Q2, the second flow Q2 and the third flow Q3 forming the total flow Q1, the total flow Q1 formed circulating in the main loop A successively in the accumulation device 8, in the internal exchanger 6, and returns to the compressor 7.

[0178] The fourth exchanger 4 and the second exchanger 2 both operate as evaporators. At the fourth exchanger 4, the refrigerant receives heat from the indoor air flow Fi, in order to cool it. At the second exchanger 2, the refrigerant receives heat from the outdoor air flow Fe. This heat contributes to heating the indoor air flow Fi at the first exchanger 1. The pressure in the fourth exchanger 4 may be higher than the pressure in the second exchanger 2, since the refrigerant from the fourth exchanger 4 undergoes expansion by passing through the seventh expansion valve 37 before joining the refrigerant from the second exchanger 2 at the fourth connection point 14. The evaporation temperature in the fourth exchanger 4 may therefore be higher than that in the second exchanger 2.It is therefore possible to recover heat at the level of the second exchanger 2 even by a temperature. negative ambient temperature, i.e. a negative outside air flow temperature Fe, without risking simultaneous icing of the fourth exchanger 4.

[0179] Figure 13 illustrates a method of operating a thermal conditioning system 100 according to the second embodiment, in a mode known as accelerated heating of the passenger compartment and the battery. In this mode of operation: - a total flow Q1 of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, circulates in the main loop A and is divided between: -- a second flow Q2 circulating in the main loop A, in the first exchanger 1 where it gives off heat to the interior air flow Fi, in the second bypass branch C, successively in the fourth expansion valve 34 where it passes to intermediate pressure, in the third heat exchanger 3 where it gives off heat, in the seventh expansion valve 37 where it passes to low pressure, -- a third flow Q3 circulating in the fourth bypass branch E, in the sixth expander 36 where it undergoes expansion, and joins the second flow Q2, the second flow Q2 and the third flow Q3 thus forming the total flow Q1, the total flow Q1 formed circulates in the main loop A, successively in the accumulation device 8, in the internal exchanger 6 and returns to the compressor 7.

[0180] In this operating mode, the interior air flow Fi is heated by the high-pressure refrigerant at the first exchanger 1, which heats the passenger compartment. The intermediate pressure refrigerant transfers heat to element 25 of the traction chain at the third exchanger 3, which allows element 25 of the traction chain to be heated. The flow Q2 of refrigerant fluid, mainly in liquid form at the outlet of the third exchanger 3 and the seventh expansion valve 37, is mixed with the flow Q3 of high-temperature gaseous refrigerant fluid which leaves the sixth expansion valve 36. The third flow Q3 joins the second flow Q2 between the seventh regulator 37 and the fourth connection point 14. The mixture formed, essentially or totally in gaseous form, is re-aspirated by the compressor 7 after passing through the accumulation device 8. The additional flow circulating in the fourth branch of bypass E increases the heating power provided and accelerates the rise in temperature of the passenger compartment. It is therefore not necessary to equip the vehicle's heating system with additional electric heating.

[0181] The second exchanger 2 and the fourth exchanger 4 do not participate in heat exchanges. The internal exchanger 6 does not participate in the heat exchanges, because the flow rate of refrigerant in the first heat exchange section 6a is zero. The first regulator 31, the second regulator 32, the third regulator 33 and the fifth regulator 35 are in the closed position. The first branch of bypass B and the fifth branch of bypass F are not crossed by the refrigerant fluid. The portion of main loop A between the third connection point 13 and the fourth connection point 14 is not crossed by the refrigerant fluid.

[0182] Figure 14 illustrates a method of operating a thermal conditioning system 100 according to the second embodiment, in a mode called passenger compartment heating and energy recovery. According to this mode of operation: - a total flow Q1 of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates in the main loop A, in the first exchanger 1 where it gives off heat to the interior air flow Fi, and is divided between: -- a second flow Q2 circulating in the second bypass branch C, successively in the fourth regulator 34 where it passes to a first intermediate pressure, in the third heat exchanger 3 where it receives heat, in the seventh regulator 37 where it passes to low pressure, -- a third flow Q3 circulating in the main loop A, successively in the first regulator 31 where it passes to a second intermediate pressure greater than or equal to the first intermediate pressure, in the internal exchanger 6, in the second regulator 32 where it passes to low pressure, in the second exchanger 2 where it receives heat from the outside air flow Fe, and joins the second flow Q2, the second flow Q2 and the third flow Q3 thus forming the total flow Q1, the total flow Q1 formed circulates in the main loop A, successively in the accumulation device 8, in the internal exchanger 6 and returns to the compressor 7.

[0183] In this operating mode, the interior air flow Fi is heated at the first exchanger 1, which allows the passenger compartment to be heated. The refrigerant fluid can receive heat from the element 25 of the traction chain at the third exchanger 3, which allows energy recovery. The fourth expansion valve 34 allows the intermediate pressure value to be controlled. The low-pressure refrigerant receives heat from the outside air flow Fe at the second exchanger 2. The heat taken from the outside air flow Fe and the heat recovered from the thermal losses of the electric powertrain both contribute to heating the vehicle interior. The fourth exchanger 4 does not participate in heat exchanges. The internal exchanger 6 participates in heat exchanges. The first branch of bypass B and the third branch of bypass D1 are not crossed by the refrigerant fluid. Likewise, the fifth branch F is not traversed by the refrigerant fluid. Indeed, the second one-way valve 44 prevents the circulation of the refrigerant fluid from the tenth connection point 20 to the ninth connection point 19.

[0184] Many other operating modes, not shown, are also possible.

[0185] For example, according to a mode called passenger compartment cooling and powertrain cooling, the first stop valve 41 is closed so as to prevent the circulation of refrigerant fluid in the first exchanger 1. The high-pressure refrigerant fluid thus circulates in the second exchanger 2 where the heat of the refrigerant fluid is dissipated in the outside air flow, then circulates in parallel in the fourth exchanger 4 and in the third exchanger 3. The fifth expansion valve 35 and the fourth expansion valve 34 expand the refrigerant fluid to a low pressure state. The sixth expansion valve 36 is in the partially open position. Thus, the circuit portion 10 between the first stop valve 41 and the third one-way valve 45, including the first exchanger 1, is maintained in a low pressure state, which is the state of the refrigerant fluid downstream of the seventh expansion valve 37. In this way, the mass of refrigerant included in this portion of the circuit can be minimized, which makes it possible to reduce the quantity of refrigerant required.

[0186] Other refrigerant circuit architectures are feasible.

[0187] In particular, according to variants not shown, the fourth branch branch E may be present without the fifth branch branch F being present. Similarly, the fifth branch branch F may be present while the fourth branch branch E is not present. The fifth branch F may have the definition shown in Figure 8 with a fourth branch E defined as in Figures 4 to 7. Similarly, the fourth branch E may have the definition shown in Figure 8 with a fifth branch F defined as in Figures 4 to 7.

Claims

Claims

1. A 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) comprising successively according to the direction of circulation of the refrigerant fluid: -- a compressor (7), -- a first heat exchanger (1) thermally coupled with an interior air flow (Fi) to a passenger compartment of the vehicle, -- a first regulator (31), -- a second regulator (32), -- a second heat exchanger (2) configured to exchange heat with an external air flow (Fe) to the passenger compartment of the vehicle, -- a refrigerant fluid accumulation device (8), A first bypass branch (B) connecting a first connection point (11) arranged on the main loop (A) downstream of an outlet (7b) of the compressor (7) and upstream of the first exchanger (1) to a second connection point (12) arranged on the main loop (A) downstream of the second heat exchanger (2) and upstream of the accumulation device (8), the first bypass branch (B) comprising a third expansion valve (33), - A second bypass branch (C) connecting a third connection point (13) arranged on the main loop (A) between the first exchanger (1) and the second expansion valve (32) to a fourth connection point (14) arranged on the main loop (A) downstream of the second exchanger (2) and upstream of the accumulation device (8), the second bypass branch (C) successively comprising a fourth expansion valve (34) and a third heat exchanger (3), in which the main loop (A) comprises an internal exchanger (6) configured to allow heat exchange between the refrigerant circulating between the first expansion valve (31) and the second expansion valve (32) and the refrigerant downstream of the accumulation device (8) and upstream of an inlet (7a) of the compressor (7).

2. Thermal conditioning system (100) according to claim 1, wherein the third heat exchanger (3) is thermally coupled with an element (25) of an electric powertrain of a motor vehicle.

3. A thermal conditioning system (100) according to claim 1 or 2, comprising: - A third branch branch (D1) connecting a fifth connection point (15-1) arranged on the main loop (A) between the second expansion valve (32) and the first expansion valve (31) to a sixth connection point (16-1) arranged on the main loop (A) between the second connection point (12) and the fourth connection point (14), the third branch branch (D1) successively comprising a fifth expansion valve (35) and a fourth heat exchanger (4) configured to exchange heat with the interior air flow (Fi).

4. A thermal conditioning system (100) according to claim 1 or 2, comprising: - A third branch branch (D2) connecting a fifth connection point (15-2) arranged on the second branch branch (C) between the third connection point (13) and the fourth expansion valve (34) to a sixth connection point (16-2) arranged on the second branch branch (C) between the third exchanger (3) and the fourth connection point (14), the third branch branch (D2) successively comprising a fifth expansion valve (35) and a fourth heat exchanger (4) configured to exchange heat with the interior air flow (Fi).

5. Thermal conditioning system (100) according to one of the preceding claims, comprising: - A fourth branch branch (E) connecting a seventh connection point (17) arranged on the main loop (A) downstream of the first connection point (11) and upstream of the first exchanger (1) to an eighth connection point (18) arranged on the second branch branch (C) downstream of the fourth regulator (34) and upstream of the fourth connection point (14), the fourth branch branch (E) comprising a sixth regulator (36).

6. Thermal conditioning system (100) according to one of the preceding claims, comprising: - A fifth bypass branch (F) connecting a ninth connection point (19) arranged on the second bypass branch (C) downstream of the third exchanger (3) and upstream of the fourth connection point (14) to a tenth connection point (20) arranged on the main loop (A) between the third connection point (13) and the second expansion valve (32), in which the refrigerant circuit (10) comprises a second one-way valve (44) arranged on the fifth bypass branch (F), the second one-way valve (44) being configured to allow circulation of refrigerant from the ninth connection point (19) to the tenth connection point (20) and configured to prohibit circulation of refrigerant from the tenth connection point (20) to the ninth connection point (19).

7. Thermal conditioning system (100) according to the preceding claim, wherein the second bypass branch (C) comprises a seventh regulator (37) arranged between the ninth connection point (19) and the fourth connection point (14).

8. Thermal conditioning system (100) according to claim 6 or 7, wherein the fifth bypass branch (F) comprises an eighth expansion valve (38).

9. Thermal conditioning system (100) according to one of claims 6 to 8 in combination with claim 7, comprising a refrigerant fluid distribution module (50) comprising: - a first inlet (11) of refrigerant fluid, - a second inlet (I2) for refrigerant fluid, - a first outlet (S1) of refrigerant fluid, - a second outlet (S2) of refrigerant fluid, - a first channel (C1) connecting the first input (11) to the first output (S1), - a second channel (C2) connecting the second input (12) to a connection point (P) arranged on the first channel (C1) between the first input (11) and the first output (S1), - a third channel (C3) connecting the second output (S2) to the connection point (P), - a seventh regulator (37) arranged on the first channel (C1) between the connection point (P) and the first output (S1), - a one-way valve (44) arranged on the second channel (C2) between the connection point (P) and the second outlet (S2), in which: the first channel (C1) partly forms the second branch branch (C), the second channel (C2) partly forms the third branch branch (D2), the third channel (C3) partly forms the fifth branch branch (F).

10. Thermal conditioning system (100) according to one of claims 6 to 8, comprising a refrigerant fluid distribution module (50') comprising: - a first inlet (11') of refrigerant fluid, - a second refrigerant fluid inlet / outlet (ES2'), - a third inlet / outlet (ES3') for refrigerant fluid, - a first channel (C1') connecting the second input / output (ES2') to the third input / output (ES3'), - a second channel (C2') connecting the first input (11') to a connection point (P') arranged on the first channel (C1') between the second input / output (ES2') and the third input / output (ES3'), - the first regulator (31), - a one-way valve (44) arranged on the second channel (C2') between the first inlet (11') and the connection point (P'), in which: the first regulator (31) is arranged on the first channel (C1') between the third inlet / outlet (ES3') and the connection point (P'), the first channel (C1') partly forms the main loop (A), the second channel (C2') partly forms the fifth bypass branch (F).

11. Method of operating a thermal conditioning system (100) according to one of the preceding claims in combination with claim 3, in a mode known as passenger compartment dehumidification and battery cooling in which: — a total flow (Q1) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and is divided between: -- a second flow (Q2) circulating in the main loop (A), successively in the first exchanger (1) where it gives off heat to the interior air flow (Fi), in the first expansion valve (31) where it passes to intermediate pressure, -- a third flow (Q3) circulating in the first bypass branch (B), successively in the third expansion valve (33) where it passes at intermediate pressure, in the second exchanger (2) where it gives off heat to the outside air flow (Fe), in the second expansion valve (32), in the internal exchanger (6), and is divided between: — a fourth flow (Q4) circulating in the third bypass branch (D1), successively in the fifth regulator (35) where it passes at low pressure, in the fourth exchanger (4) where it receives heat from the interior air flow (Fi), in the main loop (A), — a fifth flow (Q5) circulating in the main loop (A) and joining the second flow (Q2), the second flow (Q2) and the fifth flow (Q5) forming a sixth flow (Q6) circulating in the second bypass branch (C), successively in the fourth expansion valve (34) where it passes at low pressure, in the third exchanger (3) where it receives heat, and joins the fourth flow (Q4), the sixth flow (Q6) and the fourth flow (Q4) forming the total flow (Q1), the total flow (Q1) formed circulates in the main loop (A), successively in the accumulation device (8), in the internal exchanger (6), and returns to the compressor (7).

12. Method of operating a thermal conditioning system (100) according to one of the preceding claims in combination with claims 3 and 6, in a so-called battery heating mode with recovery of energy from the outside air in which: - a total flow rate (Q) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates in the main loop (A), in the first exchanger (1), in the second bypass branch (C), successively in the fourth expansion valve (34) where it passes at intermediate pressure, in the third heat exchanger (3) where it gives off heat, in the fifth bypass branch (F), in the main loop (A) successively in the internal exchanger (6), in the second expansion valve (32) where it passes at low pressure, in the second exchanger (2) where it receives heat from the outside air flow (Fe), in the accumulation device (8), in the internal exchanger (6), and returns to the compressor (7).

13. Method of operating a thermal conditioning system (100) according to one of the preceding claims in combination with claims 4 and 6, in a mode known as battery heating and passenger compartment heating with recovery of energy from the outside air in which: - a total flow (Q1) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates in the main loop (A), in the first exchanger (1) where it gives off heat to the interior air flow (Fi), and is divided between: -- a second flow (Q2) circulating in the second bypass branch (C), successively in the fourth expansion valve (34) where it passes at intermediate pressure, in the third heat exchanger (3) where it gives off heat, -- a third flow (Q3) circulating in the third bypass branch (D2), successively in the fifth expansion valve (35) where it passes at intermediate pressure, in the fourth heat exchanger (4) where it gives off heat to the internal air flow (Fi), and joins the second flow (Q2), the second flow (Q2) and the third flow (Q3) forming the total flow (Q1), the total flow (Q1) formed circulating in the fifth bypass branch (F), in the main loop (A) successively in the internal exchanger (6), in the second expansion valve (32) where it passes at low pressure, in the second exchanger (2) where it receives heat from the external air flow (Fe), in the accumulation device (8), in the internal exchanger (6),and returns to the compressor (7).,

14. Method of operating a thermal conditioning system (100) according to one of the preceding claims in combination with claims 4, 6, 7, in a so-called passenger compartment dehumidification mode with energy recovery from outside air in which: - a total flow (Q1) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates in the main loop (A), in the first exchanger (1) where it gives off heat to the interior air flow (Fi), and is divided between: -- a second flow (Q2) circulating in the third bypass branch (D2), successively in the fifth expander (35) where it passes at intermediate pressure, in the fourth heat exchanger (4) where it receives heat from the interior air flow (Fi), in the main loop A, in the seventh expander (37) where it passes at low pressure, -- a third flow (Q3) circulating in the main loop (A), successively in the first expander (31), in the internal exchanger (6), in the second expander (32) where it passes at low pressure, in the second heat exchanger (2) where it receives heat from the outside air flow (Fe), and joins the second flow (Q2), the second flow (Q2) and the third flow (Q3) forming the total flow (Q1), the total flow (Q1) formed circulating in the main loop A successively in the accumulation device (8), in the internal exchanger (6), and returns to the compressor (7).

15. Method of operating a thermal conditioning system (100) according to one of the preceding claims in combination with claims 5 and 7, in a mode known as accelerated heating of the passenger compartment and the battery in which: - a total flow (Q1) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, circulates in the main loop (A) and is divided between: -- a second flow (Q2) circulating in the main loop (A), in the first exchanger (1) where it transfers heat to the interior air flow (Fi), in the second bypass branch (C), successively in the fourth expansion valve (34) where it passes to intermediate pressure, in the third heat exchanger (3) where it transfers heat, in the seventh expansion valve (37) where it passes to low pressure, -- a third flow (Q3) circulating in the fourth bypass branch (E), in the sixth expansion valve (36) where it undergoes expansion, and joins the second flow (Q2), the second flow (Q2) and the third flow (Q3) thus forming the total flow (Q1), the total flow (Q1) formed circulates in the main loop A, successively in the accumulation device (8), in the internal exchanger (6) and returns to the compressor (7).

16. Method of operating a thermal conditioning system (100) according to one of the preceding claims in combination with claims 4 and 7, in a so-called passenger compartment heating and energy recovery mode in which: - a total flow (Q1) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates in the main loop (A), in the first exchanger (1) where it gives off heat to the interior air flow (Fi), and is divided between: -- a second flow (Q2) circulating in the second bypass branch (C), successively in the fourth regulator (34) where it passes to a first intermediate pressure, in the third heat exchanger (3) where it receives heat, in the seventh regulator (37) where it passes to low pressure, -- a third flow (Q3) circulating in the main loop (A), successively in the first expander (31) where it passes to a second intermediate pressure greater than or equal to the first intermediate pressure, in the internal exchanger (6), in the second expander (32) where it passes to low pressure, in the second exchanger (2) where it receives heat from the external air flow (Fe), and joins the second flow (Q2), the second flow (Q2) and the third flow (Q3) thus forming the total flow (Q1), the total flow (Q1) formed circulates in the main loop A, successively in the accumulation device (8), in the internal exchanger (6) and returns to the compressor (7).

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