Thermal conditioning system

Abstract

The invention relates to a thermal conditioning system (100) for a motor vehicle, comprising a refrigerant circuit (10) including: - A main loop (A) comprising successively: - a compressor (7), - a first heat exchanger (1) thermally coupled with an interior airflow (Fi) to a vehicle passenger compartment, - a first expansion valve (31), - a second expansion valve (32), - a second heat exchanger (2) thermally coupled with an exterior airflow (Fe) to the vehicle passenger compartment, - a refrigerant accumulation device (8), - A first branch (B) of the main loop (A), comprising a third expansion valve (33), - A second branch (C) of the main loop (A), comprising successively a fourth expansion valve (34) and a third heat exchanger (3).in which the main loop (A) includes an internal heat 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 storage device (8) and upstream of an inlet (7a) of the compressor (7). Figure 5,

Description

Title of the invention: Thermal conditioning system technical field

[0001] The present invention relates to the field of thermal conditioning systems. Such systems can, for example, be fitted to motor vehicles. These systems ensure thermal regulation of various vehicle components, such as the passenger compartment or an electrical energy storage battery, when the vehicle is electrically powered. Heat exchange is managed primarily by the compression and expansion of a refrigerant circulating in a circuit containing several heat exchangers. A compressor forces the refrigerant into a high-pressure state, allowing its circulation within the circuit. Previous technique

[0002] Chemical refrigerants generally have a high global warming potential (GWP), which is a disadvantage. Carbon dioxide, which by definition has a global warming potential of one, can be used as a refrigerant. The thermodynamic properties of this gas mean that the compressor discharge pressure is generally in the range of 80 to 130 bar, in order for the system to provide sufficient thermal power. The discharge temperature of the refrigerant at this pressure range can, in some applications, be problematic for the compressor because it is too high. Furthermore, this high discharge temperature can also be detrimental to certain components through which the high-pressure, high-temperature refrigerant circulates.

[0003] Furthermore, in the case of an electric vehicle, it may be necessary to be able to heat the battery, particularly to enable rapid charging in cold ambient temperatures, especially below freezing. Dedicated heating devices can be used. Such dedicated devices increase the price and weight of the heating system.

[0004] There is therefore a need for a thermal conditioning system to control the discharge temperature of the refrigerant and to heat the battery. Summary

[0005] To this end, a thermal conditioning system for motor vehicles 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 refrigerant flow: — a compressor, — a first heat exchanger thermally coupled with an airflow inside a vehicle's passenger compartment, — a first expansion valve, — a second expansion valve, — a second heat exchanger configured to exchange heat with an outside airflow to the vehicle's passenger compartment, — a refrigerant fluid accumulation device, - A first branch connecting a first connection point located on the main loop downstream of a compressor outlet and upstream of the first heat exchanger to a second connection point located on the main loop downstream of the second heat exchanger and upstream of the accumulation device, the first branch comprising a third expansion valve, - A second branch connecting a third connection point located on the main loop between the first exchanger and the second expansion valve to a fourth connection point located on the main loop downstream of the second exchanger and upstream of the accumulation device, the second branch comprising successively a fourth expansion valve and a third heat exchanger, in which the main loop includes 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 downstream of the accumulation device and upstream of a compressor inlet.

[0006] According to certain 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.

[0007] According to other modes of operation, the refrigerant fluid circulating between the first expansion valve and the second expansion valve circulates from the second expansion valve to the first expansion valve.

[0008] This refrigerant circuit architecture allows heat to be transferred to the indoor airflow at the first heat exchanger and heat to be selectively absorbed or transferred to the outdoor airflow at the second heat exchanger, by controlling the pressure at the inlet of the second exchanger. The second heat 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. This allows control of the compressor's discharge temperature.

[0009] 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 inside a vehicle passenger compartment.

[0011] According to one 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 airflow inside the vehicle's passenger compartment.

[0012] The internal heat exchanger includes 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 traction chain of a motor vehicle.

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

[0015] According to one embodiment, the element of the vehicle's electric powertrain includes an electrical energy storage battery.

[0016] Alternatively or in addition, the element of the vehicle's electric drive chain includes an electric vehicle traction motor.

[0017] Alternatively or in addition, the element of the vehicle's electric traction chain includes an electronic control unit for the vehicle's electric traction motor.

[0018] According to one embodiment, the third heat exchanger is thermally coupled with the element of the electric traction chain via 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, and the fourth regulator can be electronic regulators.

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

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

[0022] In this embodiment, the refrigerant circuit may include 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 refrigerant flow from the sixth connection point to the fourth connection point and configured to prohibit refrigerant flow from the fourth connection point to the sixth connection point.

[0023] The first one-way valve is, for example, a non-return valve.

[0024] According to another embodiment, the thermal conditioning system comprises: - A third branch connecting a fifth connection point located on the second branch between the third connection point and the fourth pressure regulator to a sixth connection point located on the second branch between the third heat exchanger and the fourth connection point, the third branch of the bypass comprising successively a fifth expansion valve and a fourth heat exchanger configured to exchange heat with the internal airflow.

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

[0026] The fourth exchanger is arranged upstream of the first exchanger according to a direction of flow of the internal airflow.

[0027] In this embodiment, the refrigerant circuit includes a first one-way valve disposed on the third branch between the fourth exchanger and the sixth connection point. The first one-way valve is configured to allow refrigerant flow from the fifth connection point to the sixth connection point and configured to prohibit refrigerant flow from the sixth connection point to the fifth connection point.

[0028] According to one embodiment, the thermal conditioning system comprises: - A fourth branch 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 downstream of the fourth expansion valve and upstream of the fourth connection point, the fourth branch comprising a sixth expansion valve.

[0029] The fourth bypass branch allows the high-pressure, high-temperature refrigerant from the compressor outlet to return to the compressor inlet without passing through the first or second heat 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 refrigerant flow rate supplied by the compressor and thus increases the heating power provided by the refrigerant.

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

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

[0032] According to yet another embodiment, the thermal conditioning system includes a fourth branch 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 main loop downstream of the fourth connection point and upstream of the accumulation device, the fourth branch including a sixth expansion valve.

[0033] According to one embodiment, the thermal conditioning system comprises: - A fifth branch connecting a ninth connection point located on the second branch 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 expansion valve.

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

[0035] According to one 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 includes a second one-way valve arranged on the fifth branch of the branch. The second one-way valve is configured to allow refrigerant flow from the ninth connection point to the tenth connection point and configured to prohibit refrigerant 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 exiting the third heat exchanger to rejoin the main loop and from there to the compressor inlet. The fifth bypass branch thus allows the refrigerant fluid to supply heat to the electric traction element at the third heat exchanger, i.e., it provides heating for the electric traction element.

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

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

[0040] According to one embodiment of the thermal conditioning system, the second branch branch includes a seventh expansion valve disposed between the ninth connection point and the fourth connection point.

[0041] The seventh expansion valve allows the refrigerant from the third heat exchanger to expand before it mixes with the refrigerant at the outlet of the fourth heat exchanger. The fourth heat exchanger can therefore operate at a higher pressure than the third heat exchanger, and thus at a higher temperature.

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

[0043] According to one embodiment of the thermal conditioning system, the fifth branch branch includes an eighth expansion valve.

[0044] The eighth expansion valve allows the refrigerant fluid from the third exchanger to be expanded before entering the first heat exchange section of the internal exchanger, and thus to control the heat exchange in the internal exchanger.

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

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

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

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

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

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

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

[0052] The main loop includes a second shut-off valve disposed 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 including: - a first inlet of refrigerant fluid, - a second refrigerant inlet, - a first refrigerant 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 located 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 positioned on the first channel between the connection point and the first outlet, - a one-way valve located on the second channel between the connection point and the second outlet, in which: the first canal forms part of the second branch of the line The second canal partially forms the third branch of the diversion. the third canal forms part of the fifth branch of the derivation.

[0057] The integration of certain components and part of the refrigerant circulation circuit in the form of a distribution module makes it easier to integrate the mechanical components and to reduce the overall size.

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

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

[0060] According to another embodiment, the thermal conditioning system comprises a refrigerant distribution module including: - a first inlet of refrigerant fluid, - a second refrigerant inlet / outlet, - a third refrigerant 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 located on the first channel between the second input / output and the third input / output, - the first regulator, - a one-way valve located on the second channel between the first inlet and the connection point, in which: The first regulator is positioned on the first channel between the third inlet / outlet and the connection point. The first channel partially forms the main loop. the second canal forms part of the fifth branch of the derivation.

[0061] The channels of the refrigerant distribution module are formed by internal recesses in 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 above, in a so-called passenger compartment dehumidification and battery cooling mode in which: - a total flow of refrigerant circulates in the compressor where it passes under high pressure, and is divided between: — a second flow circulating in the main loop, successively in the first exchanger where it transfers heat to the internal airflow, in the first expansion valve where it passes to an intermediate pressure, — a third flow circulating in the first branch of the bypass, successively in the third expansion valve where it passes to intermediate pressure, in the second exchanger where it transfers heat to the outside air flow, in the second expansion valve, in the internal exchanger, and divides between: — a fourth flow circulating in the third branch, successively in the fifth pressure reducer where it passes at low pressure, in the fourth heat exchanger where it receives heat from the internal airflow, 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 pressure reducer where it passes at low pressure, in the third exchanger where it receives heat, and rejoins 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 value of the low pressure is less than the value of the intermediate pressure.

[0066] The invention also relates to a method of operating a thermal conditioning system as described above, in a so-called battery heating mode with energy recovery from the outside air in which: - a total flow of refrigerant 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 up 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 airflow, 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 internal airflow at the level of the first exchanger.

[0068] In this mode of operation, the total flow of refrigerant can also circulate in the first exchanger without transferring heat to the internal airflow.

[0069] The invention also relates to a method of operating a thermal conditioning system as already described, in a so-called battery heating and passenger compartment heating mode with energy recovery from outside air in which: - a total flow of refrigerant circulates in the compressor where it passes through high pressure, and circulates in the main loop, in the first heat exchanger where it transfers heat to the internal airflow, and is divided between: — a second flow circulating in the second bypass branch, successively in the fourth pressure regulator where it passes to intermediate pressure, in the third heat exchanger where it releases heat, — a third flow circulating in the third branch of the bypass, successively in the fifth pressure regulator where it passes at intermediate pressure, in the fourth heat exchanger where it gives up heat to the internal airflow, 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 to low pressure, in the second exchanger where it receives heat from the outside airflow, in the accumulation device, in 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 so-called passenger compartment dehumidification mode with energy recovery from outside air in which: - a total flow of refrigerant circulates in the compressor where it passes through high pressure, and circulates in the main loop, in the first heat exchanger where it transfers heat to the internal airflow, and is divided between: — a second 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 receives heat from the internal airflow, in the main loop, in the seventh expansion valve 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 rejoins the second flow, the second flow rate and the third flow rate together form the total flow rate, 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] Both the fourth and second heat exchangers operate as evaporators. In the fourth heat exchanger, the refrigerant absorbs heat from the incoming airflow to cool and dehumidify it. In the second heat exchanger, the refrigerant absorbs heat from the outgoing airflow, which contributes to heating the incoming airflow in the first heat exchanger. The pressure in the fourth heat exchanger can be higher than the pressure in the second heat exchanger because the refrigerant from the fourth heat exchanger undergoes expansion as it passes through the seventh expansion valve before joining the refrigerant from the second heat exchanger. Therefore, the evaporation temperature in the fourth heat exchanger can be higher than that in the second heat exchanger.It is therefore possible to recover heat at the second exchanger even in negative ambient temperatures, without risking freezing the fourth exchanger.

[0072] The invention also relates to a method of operating a thermal conditioning system as described above, in a so-called accelerated heating mode of the passenger compartment and the battery in which: - a total flow of refrigerant circulates through the compressor where it is under 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 releases heat to the internal airflow, in the second bypass branch, successively in the fourth expansion valve where it passes to intermediate pressure, in the third heat exchanger where it releases 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 regulator where it undergoes expansion, and rejoins the second flow, the second and third flow rates thus forming the total flow rate, 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 so-called passenger compartment heating and energy recovery mode in which: - a total flow of refrigerant circulates in the compressor where it passes through high pressure, and circulates in the main loop, in the first heat exchanger where it transfers heat to the internal airflow, and is divided between: — a second flow circulating in the second bypass branch, successively in the fourth pressure regulator where it passes to a first intermediate pressure, in the third heat exchanger where it receives heat, in the seventh pressure regulator where it passes to low pressure, — a third flow circulating in the main loop, successively in the first expansion valve 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 to low pressure, in the second exchanger where it receives heat from the outside air flow, and rejoins the second flow, the second and third flow rates thus forming the total flow rate, The total flow produced circulates in the main loop, successively through the accumulation device, the internal heat 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 analysis of the accompanying drawings, on 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 the [Fig.1], operating according to a first mode of operation, called passenger compartment dehumidification and battery cooling mode,

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

[0085] [Fig. 11] is a schematic view of the thermal conditioning system of [Fig. 5], operating according to a third mode of operation, called battery heating and passenger compartment heating mode with energy recovery from outside air,

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

[0087] [Fig. 13] is a schematic view of the thermal conditioning system of the [Fig.4], operating according to 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 the [Fig.4], operating according to an operating mode, called passenger compartment heating and energy recovery mode. Description of the implementation methods

[0089] To facilitate reading the figures, the different elements are not necessarily shown to scale. In these figures, identical elements bear the same reference numerals. Certain elements or parameters may be indexed, i.e. These elements are designated, for example, as first element or second element, or first parameter and second parameter, etc. The purpose of this indexing is to differentiate between similar, but not identical, elements or parameters. This indexing does not imply any priority of one element or parameter over another, and the names can 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 flow, 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 flow, 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 flows successively through the first element, then the second element, without passing through the compression device. In other words, the refrigerant exits the compression device, possibly passes through one or more elements, then passes through the first element, then the second element, and 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 to go 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 that subsystem.

[0093] The thermal conditioning system 100, which will be described below, comprises an electronic control unit 60 that receives information from various sensors measuring, in particular, the characteristics of the refrigerant at various points in the circuit. The electronic control unit 60 also receives instructions from the vehicle occupants, such as the desired temperature inside the passenger compartment. The electronic control unit 60 can also receive instructions from other electronic subsystems, such as the electrical energy storage battery management system. The electronic control unit 60 implements control laws to operate the various actuators, in order to control the thermal conditioning system 100 and ensure compliance with the received instructions.

[0094] A compression device 7, also called a compressor, allows a refrigerant fluid to circulate in a refrigerant circulation circuit 10. The compression device 7 can be an electric compressor, that is to say, a compressor whose moving parts are driven by an electric motor. The compression device The compressor 7 has a low-pressure refrigerant intake side, also called the inlet 7a of the compressor, and a high-pressure refrigerant discharge side, also called the outlet 7b of the compressor. The internal moving parts of the compressor 7 increase the refrigerant pressure from low pressure at the inlet 7a to high pressure at the outlet 7b. After expansion in one or more expansion chambers and circulation through at least part of the circuit, the refrigerant 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 leak-proof when it is in its nominal operating condition, that is, without any faults or leaks. Each connection point of the circuit 10 allows the refrigerant to flow into one or the other of the circuit sections that converge at that connection point. The distribution of the refrigerant between the circuit sections that converge at a connection point is achieved by opening or closing the shut-off valves, check valves, or expansion devices included on each of these sections. In other words, each connection point is a means of redirecting the refrigerant arriving at that connection point.Various shut-off valves and check valves thus allow the refrigerant to be selectively directed 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 R 134a.

[0097] Each refrigerant expansion device, also called an expansion valve, can be an electronic expansion valve. In an electronic expansion valve, the passage area through which the refrigerant flows can be continuously adjusted between a closed position and a maximum open position. To achieve this, an electronic control module drives an electric motor that moves a movable shutter, thus controlling the passage area available to the refrigerant. In the closed position, the circulation of refrigerant is interrupted; that is, the flow of refrigerant through the electronic expansion valve is zero. In the maximum open position, the refrigerant flows through the expansion valve without undergoing any expansion.

[0098] The term "interior airflow Fi" refers to an airflow destined for the passenger compartment of the motor vehicle. This interior airflow Fi may circulate within a heating, ventilation, and / or air conditioning system, frequently referred to by the English term "HVAC," for "Heating, Ventilating, and Air Conditioning." This system does not have not shown in the various figures. A first motor-fan unit, not shown, is installed in the heating, ventilation and / or air conditioning system in order to increase the flow rate of the indoor airflow Fi if necessary.

[0099] The term "external airflow Fe" refers to an airflow that is not directed towards the vehicle's passenger compartment. In other words, this airflow Fe remains outside the vehicle's passenger compartment. A second motor-fan unit, also not shown, can be activated to increase the flow rate of the external airflow Fe if necessary. The airflow provided by both the first and second motor-fan units can be adjusted in real time according to heat exchange requirements, for example, by the electronic control unit 60 of the climate control 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 "storage device" is equivalent to the term "refrigerant storage 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 [Fig.1] shows a thermal conditioning system 100 for a motor vehicle, comprising a refrigerant fluid circuit 10 configured to circulate a refrigerant fluid. The refrigerant circuit 10 comprises: - A main loop A comprising successively, according to the direction of refrigerant flow: — a compressor 7, — a first heat exchanger 1 thermally coupled with an internal airflow Fi to a vehicle passenger compartment, — a first regulator 31, — a second regulator 32, — a second heat exchanger 2 configured to exchange heat with an outside airflow Fe to the vehicle's passenger compartment, — a refrigerant fluid accumulation device 8, - A first branch branch B connecting a first connection point 11 located 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 located on the main loop A downstream of the second heat exchanger 2 and upstream of the accumulation device 8, the first branch branch B comprising a third expansion valve 33, - A second branch C connecting to a third connection point 13 located on the main loop A between the first exchanger 1 and the second expansion valve 32 to a fourth connection point 14 disposed on the main loop A downstream of the second exchanger 2 and upstream of the accumulation device 8, the second branch C comprising successively a fourth expansion valve 34 and a third heat exchanger 3. The main loop A includes 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 storage 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 compensates for variations in the quantity of refrigerant circulating in the circuit 10, depending on operating conditions. The accumulation device 8 also separates the liquid and gaseous phases 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 flows from the first expansion valve 31 to the second expansion valve 32. According to other 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 second expansion valve 32 to the first expansion valve 31.

[0105] This refrigerant circuit architecture allows heat to be transferred to the indoor airflow Fi at the first heat exchanger 1 and heat to be selectively absorbed or transferred to the outdoor airflow Fe at the second heat exchanger 2, while controlling the pressure at the inlet of the second heat exchanger 2. The second heat 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 heat exchanger 6, which allows control of the discharge temperature of the compressor 7. The discharge temperature is understood to be 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 airflow Fi to a vehicle passenger compartment. The thermal coupling between the first heat exchanger 1 and the internal airflow Fi is said to be direct. Indeed, the airflow Fi is in contact with the walls of the heat exchanger through which the refrigerant circulates. In this embodiment, the first heat exchanger 1 is located in the vehicle's heating, ventilation and / or air conditioning system.

[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 includes a heat exchanger IB configured to exchange heat with an interior airflow Fi to the vehicle's passenger compartment. The thermal coupling between the first heat exchanger 1 and the interior airflow Fi is in this case said to be indirect, since it is achieved via a heat transfer fluid which transfers the heat supplied by the refrigerant fluid to the airflow Fi supplying the vehicle's passenger compartment. The heat transfer fluid circulating in circuit 30 is, for example, a mixture of water and glycol. According to this variant, the IB heat exchanger, also called a heater radiator, is placed in the vehicle's heating, ventilation and / or air conditioning system.

[0108] The second heat exchanger 2 is, for example, located in the front of the vehicle so as to directly receive the outside airflow. The second heat exchanger 2 can be located just behind the vehicle's grille. The grille can include a movable flap allowing the cross-section of the outside airflow to be controlled, i.e., varied as needed.

[0109] The internal heat exchanger 6 includes 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 includes 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 chain of a motor vehicle.

[0112] The third heat exchanger 3 allows for the selective cooling or heating of the element 25 of the vehicle's electric powertrain. The element 25 of the vehicle's electric powertrain can thus be maintained, or placed, within a preferred temperature range corresponding to the element's optimal operation.

[0113] Element 25 of the vehicle's electric drive chain here includes an electrical energy storage battery.

[0114] Alternatively or in addition, element 25 of the vehicle's electric drive chain includes an electric vehicle traction motor.

[0115] Alternatively or in addition, element 25 of the vehicle's electric traction chain includes an electronic control unit for the vehicle's electric traction motor.

[0116] According to the illustrated example, the third heat exchanger 3 is thermally coupled with the element 25 of the electric traction chain via a heat transfer fluid circulating in a heat transfer fluid 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 circulating in the third heat exchanger 3 and on the other hand with the element 25 of the vehicle's electric powertrain. The heat transfer fluid thus enables heat transfer between the refrigerant and the element 25 of the electric powertrain. For example, the heat transfer fluid circulates between the battery elements, 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 in circuit 40 does not mix with the heat transfer fluid in circuit 30. The heat transfer fluid in circuit 40 can be a dielectric fluid. When the heat transfer fluid in circuit 40 is a dielectric fluid, it can be in direct contact with electrically live components.

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

[0119] According to the embodiment of [Fig. 1], the thermal conditioning system 100 includes a third branch DI connecting a fifth connection point 15-1 located on the main loop A between the second regulator 32 and the first regulator 31 to a sixth connection point 16-1 located on the main loop A between the second connection point 12 and the fourth connection point 14. The third branch of the DI branch includes successively a fifth expansion valve 35 and a fourth heat exchanger 4 configured to exchange heat with the internal airflow Fi.

[0120] The fourth heat exchanger 4 cools the interior airflow Fi 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 includes a first one-way valve 43-1 disposed on the main loop A between the sixth connection point 16-1 and fourth connection point 14. The first one-way valve 43-1 is configured to allow refrigerant flow 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 refrigerant flow from the fourth connection point 14 to the sixth connection point 16-1. The first one-way valve 43-1 in the illustrated example is a check valve. 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 [Fig.3], the thermal conditioning system 100 includes a third branch branch D2 connecting a fifth connection point 15-2 located 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 located on the second branch branch C between the third heat exchanger 3 and the fourth connection point 14. The third branch of the D2 branch includes successively a fifth expansion valve 35 and a fourth heat exchanger 4 configured to exchange heat with the internal airflow Fi. In other words, the third branch of derivation can be chosen according to two distinct variants DI and D2. These two variants are mutually exclusive, that is to say that if the refrigerant fluid circuit 10 includes a third branch of type D1, no branch of type D2 is present, and vice versa.

[0123] Reservoir] The fourth heat exchanger 4 is located in the vehicle's heating, ventilation and / or air conditioning system. The fourth heat exchanger 4 is located upstream of the heat exchanger providing heating for the interior airflow Fi, which, depending on the embodiment, is the first heat exchanger 1 or the heat exchanger IB.

[0124] According to this embodiment, the refrigerant fluid circuit 10 includes a first one-way valve 43-2 disposed on the third branch 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 refrigerant flow from the fifth connection point 15-2 to the sixth connection point 16-2 and configured to prohibit refrigerant flow from the sixth connection point 16-2 to the fifth connection point 15-2.

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

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

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

[0128] The direction of flow in the second heat exchange section 6b of the internal heat exchanger 6 is constant. This means that the direction of flow of the refrigerant in the second heat exchange section 6b is the same 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 branch E connecting a seventh connection point 17 located on the main loop A downstream of the first connection point 11 and upstream of the first heat exchanger 1 to an eighth connection point 18 located on the second branch C downstream of the fourth expansion valve 34 and upstream of the fourth connection point 14. The fourth branch E comprises a sixth expansion valve 36.

[0130] The fourth bypass branch E allows the high-pressure, high-temperature refrigerant fluid at the outlet of the compressor 7 to return to the compressor inlet 7a without passing through the first heat exchanger 1 or the second heat exchanger 2. The fourth bypass branch E returns the high-pressure refrigerant fluid to the inlet of the accumulator 8. The flow circulating in the fourth bypass branch E increases the total flow rate of refrigerant fluid supplied by the compressor 7 and thus increases the heating power supplied by the refrigerant fluid.

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

[0132] According to the variant of [Fig.8], the eighth connection point 18 is located upstream of the third interchange 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 flowing through the fourth branch E can flow through the third exchanger 3 and then join the main loop A at the fourth connection point 14.

[0133] According to another embodiment, not shown, the thermal conditioning system 100 includes a fourth branch E connecting a seventh connection point 17 located on the main loop A downstream of the first connection point 11 and upstream of the first heat exchanger 1 to an eighth connection point 18 located on the main loop A downstream of the fourth connection point 14 and upstream of the storage device 8. As before, the fourth branch E includes 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 inlet 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 located 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 located on the main loop A between the third connection point 13 and the second expansion valve 32.

[0135] According to the variants in Figures 4 to 7, the tenth connection point 20 is arranged between the first expansion valve 31 and the internal exchanger 6.

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

[0137] The refrigerant circuit 10 includes a second one-way valve 44 disposed on the fifth branch F. The second one-way valve 44 is configured to allow refrigerant flow from the ninth connection point 19 to the tenth connection point 20 and configured to prohibit refrigerant flow 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 exiting the third heat exchanger 3 to rejoin the main loop A, pass through the second expansion valve 32 and the second heat exchanger 2, then joining the inlet 7a of the compressor 7. The seventh expansion valve 37 allows the circulation of refrigerant from the ninth connection point 19 to the fourth connection point 14 to be blocked, so that the refrigerant from the third heat exchanger 3 passes through the fifth branch F. The fifth branch F thus allows the refrigerant to supply heat to the element 25 of the electric traction chain at the level of the third heat exchanger 3, that is to say that this branch allows the element 25 of the electric traction chain to be heated.

[0140] Similarly, when the third branch of the bypass is of type D2, as illustrated in [Fig.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 branch of the bypass F. The fourth exchanger 4 can thus heat the indoor airflow 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 Figures 4 to 8, the second branch of the bypass C includes a seventh expansion valve 37 disposed between the ninth connection point 19 and the fourth connection point 14.

[0143] When the third branch of the bypass is of type Dl, as illustrated in [Fig. 4], the seventh expansion valve 37 allows the refrigerant from the third heat exchanger 3 to expand before it mixes with the refrigerant at the outlet of the fourth heat exchanger 4. The fourth heat exchanger 4 can therefore operate at a lower pressure than the third heat exchanger 3, and thus at a lower evaporation temperature. The fourth heat exchanger 4 and the third heat exchanger 3 can therefore each provide cooling at two different temperature levels.

[0144] Furthermore, when the third branch of the line is of type D2, as illustrated in [Fig. 5], the seventh expansion valve 37 allows the refrigerant from the fourth heat exchanger 4 to expand before it mixes with the refrigerant exiting the second heat exchanger 2. As before, the fourth heat exchanger 4 can therefore operate at a higher pressure than the second heat exchanger 2, and thus at a higher evaporation temperature. This case is used, for example, in an operating mode designed to dehumidify the passenger compartment air, 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 expansion valve 37 is disposed between the ninth connection point 19 and the eighth connection point. chord 18. This configuration is illustrated in figures 4 to 7.

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

[0147] The eighth expansion valve allows the refrigerant from the third heat exchanger 3 to be expanded before entering the first heat exchange section 6a of the internal heat exchanger 6, and thus to control the heat exchange in the internal heat exchanger 6.

[0148] According to the first embodiment and its variants, illustrated in figures 1 to 3, the first expansion valve 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 fluid circuit 10 includes a third one-way valve 45 disposed on the main loop A between the first heat exchanger 1 and the third connection point 13. The third one-way valve 45 is configured to allow refrigerant flow from the first heat exchanger 1 to the third connection point 13. The third one-way valve 45 is also configured to prohibit refrigerant flow from the third connection point 13 to the first heat exchanger 1. The third one-way valve 45 is, for example, a check valve.

[0151] Each check valve 43, 44, 45 can be replaced by an electrically operated valve controlled so as to ensure the same refrigerant circulation conditions.

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

[0153] The main loop A includes a second shut-off valve 42 disposed between the second connection point 12 and the fourth connection point 14. The second shut-off valve 42 is located 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 schematically illustrate two variants of the second embodiment in which part of the circuit 10 is formed by a refrigerant distribution module.

[0156] According to the variant in [Fig. 6], the thermal conditioning system 100 comprises a refrigerant distribution module 50 including: - a first inlet II of refrigerant fluid, - a second refrigerant inlet 12, - a first S1 outlet of refrigerant fluid, - a second refrigerant outlet S2, - a first channel Cl connecting the first input II to the first output SI, - a second channel C2 connecting the second input 12 to a connection point P arranged on the first channel Cl between the first input II and the first output SI, - a third channel C3 connecting the second output S2 to the connection point P, - a seventh regulator 37 arranged on the first channel Cl between the connection point P and the first outlet SI, - a one-way valve 44 arranged on the second channel C2 between the connection point P and the second outlet S. The first channel Cl forms part of the second branch of the derivation C. The second channel C2 forms part of the third branch of the derivation D2. The third channel C3 forms part of the fifth branch of the F branch.

[0157] The distribution module 50 integrates certain components and forms part of the refrigerant circulation circuit, thus facilitating the mechanical integration of the components. The distribution module 50 can be delivered pre-assembled, reducing the number of components to be assembled on the vehicle. Furthermore, the overall size 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 Cl, C2, C3 of the refrigerant distribution module 50 are formed by internal recesses in a metal block. The distribution module 50 can, for example, be obtained by aluminum casting and machining.

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

[0161] Fig. 7 schematically represents a 50' distribution module according to another definition.

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

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

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

[0165] The refrigerant distribution module 50' may include an eighth expansion valve 38 arranged on the second channel C2'. The eighth expansion valve 38 is, for example, arranged on the second channel C2' between the first inlet II' 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 vehicle occupants and according to the conditions of use.

[0167] Figure 9 illustrates a method of operation of a thermal conditioning system 100 according to the first embodiment, in a mode known as passenger compartment dehumidification and battery cooling. In this operating mode: - a total flow rate Q1 of refrigerant circulates in the compressor 7 where it passes under high pressure, and is divided between: — a second flow Q2 circulating in the main loop A, successively in the first exchanger 1 where it transfers heat to the internal 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 the bypass B, successively in the third expansion valve 33 where it passes to intermediate pressure, in the second exchanger 2 where it gives up heat to the outside air flow Fe, in the second expansion valve 32, in the internal exchanger 6, and divides between: — a fourth flow Q4 circulating in the third branch of the bypass Dl, successively in the fifth expansion valve 35 where it passes at low pressure, in the fourth exchanger 4 where it receives heat from the internal 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 expansion valve 34 where it passes at low pressure, in the third exchanger 3 where it receives heat, and rejoins the fourth flow Q4, the sixth flow rate Q6 and the fourth flow rate Q4 forming the total flow rate Q1, The total flow Ql circulates successively through the accumulation device 8, the internal exchanger 6, and returns to the compressor 7.

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

[0169] In this operating mode, the indoor airflow Fi is cooled at the level of the fourth exchanger 4, and heated at the level of the first exchanger 1, which allows the indoor airflow Fi to be dehumidified. The refrigerant absorbs heat from traction chain element 25 at the third exchanger 3, which cools traction chain element 25. The third expansion valve 33 allows control of the intermediate pressure value in the second heat exchanger 2, and thus the amount of heat dissipated in the outside air stream Fe. In addition, controlling the intermediate pressure allows control of the amount of heat exchanged at the internal heat exchanger 6. The internal exchanger 6 participates in the heat exchange, 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 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 filled with refrigerant. The fifth flow rate Q5 can take negative values, that is, flow from third connection point 13 to 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 in [Fig. 9], the refrigerant circulates 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 operating conditions.

[0170] Fig. 10 illustrates a method of operation of a thermal conditioning system 100 according to the second embodiment, in a so-called battery heating mode with energy recovery from outside air. In this operating mode: - a total flow Q of refrigerant 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 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 up heat, in the fifth branch of bypass 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 mode of operation, the total flow rate Q of refrigerant can transfer heat to the internal airflow Fi at the level of the first exchanger 1. For this, the flow rate of the internal airflow 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 heat exchanger 1 without transferring heat to the internal airflow Fi. For this, the flow rate of the internal airflow Fi is, for example, maintained at a value of zero.

[0173] In this operating mode, the refrigerant transfers heat to the traction chain element 25 at the third heat exchanger 3, thereby heating the traction chain element 25. The fourth expansion valve 34 controls the intermediate pressure. The low-pressure refrigerant receives heat from the outside airflow Fe at the second exchanger 2. The direction of refrigerant flow in the second exchanger 2 is reversed compared to the previous operating mode. Internal exchanger 6 participates in heat exchange. The fourth heat exchanger 4 is not receiving refrigerant. The fifth expansion valve 35 is in the closed position, which blocks the circulation of refrigerant. in the third branch of derivation Dl. The portion of the second branch of the bypass C between the ninth connection point 19 and the fourth connection point 14 is not traversed by the refrigerant. The portion of the main loop A between the third connection point 13 and the tenth connection point 20 is not traversed by the refrigerant fluid, the first expansion valve 31 being in the closed position. Similarly, the first branch of the bypass B and the fourth branch of the bypass E are not traversed by the refrigerant fluid.

[0174] Fig. 11 illustrates a method of operation of a thermal conditioning system 100 according to the first variant of the second embodiment, in a so-called battery heating and cabin heating mode with energy recovery from outside air. In this operating mode: - a total flow Q1 of refrigerant circulates in the compressor 7 where it passes through high pressure, and circulates in the main loop A, in the first heat exchanger 1 where it transfers heat to the internal airflow Fi, and is divided between: — a second flow Q2 circulating in the second branch of the bypass C, successively in the fourth expansion valve 34 where it passes at intermediate pressure, in the third heat exchanger 3 where it releases heat, — a third flow Q3 circulating in the third branch of the bypass D2, successively in the fifth expansion valve 35 where it passes to intermediate pressure, in the fourth heat exchanger 4 where it transfers heat to the internal airflow Fi, and rejoins the second flow Q2, the second flow Q2 and the third flow Q3 forming the total flow Ql, the total flow Ql formed circulating in the fifth branch of bypass F, in the main loop A successively in the internal exchanger 6, in the second expansion valve 32 where it passes to 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.

[0175] This operating mode differs from the previous mode in that the refrigerant flow exiting the first heat exchanger 1 can be divided at the fifth connection point 15-2 and circulate in parallel through the third heat exchanger 3 and the fourth heat exchanger 4. This division is made possible by the specific arrangement of the third branch of the bypass D2. The third heat exchanger 3 and the fourth heat exchanger 4 can thus provide heating, respectively, to the traction chain element 25 and the internal airflow Fi. The internal airflow Fi is thus heated both at the first heat exchanger 1 and at the level of the fourth exchanger 4, which allows to increase the heating power and the speed of temperature rise of the passenger compartment.

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

[0177] Fig. 12 illustrates a method of operation of a thermal conditioning system 100 according to the first variant of the second embodiment, in a mode known as passenger compartment dehumidification with energy recovery from outside air. In this operating mode: - a total flow Q1 of refrigerant circulates in the compressor 7 where it passes through high pressure, and circulates in the main loop A, in the first heat exchanger 1 where it transfers heat to the internal airflow Fi, and is divided between: — a second flow Q2 circulating in the third branch of the bypass D2, successively in the fifth expansion valve 35 where it passes at intermediate pressure, in the fourth heat exchanger 4 where it receives heat from the internal air flow Fi, in the main loop A, in the seventh expansion valve 37 where it passes at low pressure, — a third flow Q3 circulating in the main loop A, successively in the first expansion valve 31, in the internal exchanger 6, in the second expansion valve 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 rate Q2 and the third flow rate Q3 forming the total flow rate Q1, The total flow rate Ql formed, circulating in the main loop A, successively passes through the accumulation device 8, the internal heat exchanger 6, and returns to the compressor 7.

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

[0179] Fig. 13 illustrates a method of operation of a thermal conditioning system 100 according to the second embodiment, in a so-called accelerated heating mode of the passenger compartment and the battery. In this operating mode: - a total flow rate Q1 of refrigerant circulates in the compressor 7 where it passes through 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 releases heat to the internal 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 releases heat, in the seventh expansion valve 37 where it passes to low pressure, — a third flow Q3 circulating in the fourth branch of the bypass 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 Ql, the total flow Ql 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 mode of operation, the interior airflow Fi is heated by the high-pressure refrigerant at the level of the first exchanger 1, which makes it possible to heat the passenger compartment. The intermediate pressure refrigerant fluid gives up heat to traction chain element 25 at the third exchanger 3, which allows traction chain element 25 to be heated. The Q2 flow rate of refrigerant, mostly in liquid form at the outlet of the third exchanger 3 and the seventh expansion valve 37, is mixed with the Q3 flow rate of high-temperature gaseous refrigerant that exits 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 drawn back into the compressor 7 after passing through the accumulation device 8. The additional flow circulating in the fourth branch of the E bypass increases the heating power supplied and accelerates the temperature rise of the passenger compartment. Therefore, it is not necessary to equip the vehicle's heating system with an additional electric heater.

[0181] The second exchanger 2 and the fourth exchanger 4 do not participate in heat exchange. The internal exchanger 6 does not participate in heat exchange, because the flow rate of refrigerant fluid 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 the bypass B and the fifth branch of the bypass F are not traversed by the refrigerant fluid. The portion of the main loop A between the third connection point 13 and the fourth connection point 14 is not traversed by the refrigerant.

[0182] Fig. 14 illustrates a method of operation of a thermal conditioning system 100 according to the second embodiment, in a mode known as passenger compartment heating and energy recovery. According to this operating method: - a total flow Q1 of refrigerant circulates in the compressor 7 where it passes through high pressure, and circulates in the main loop A, in the first heat exchanger 1 where it transfers heat to the internal airflow Fi, and is divided between: — a second flow Q2 circulating in the second branch of the bypass C, successively in the fourth expansion valve 34 where it passes to a first intermediate pressure, in the third heat exchanger 3 where it receives heat, in the seventh expansion valve 37 where it passes to low pressure, — a third flow Q3 circulating in the main loop A, successively in the first expansion valve 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 expansion valve 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 Ql, the total flow Ql 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 mode of operation, the inside air flow Fi is heated at the level of the first exchanger 1, which makes it possible to heat the passenger compartment. The refrigerant can receive heat from element 25 of the traction chain at the third heat exchanger 3, thus enabling energy recovery. The fourth expansion valve 34 controls the intermediate pressure. The low-pressure refrigerant receives heat from the outside airflow Fe at the second exchanger 2. The heat taken from the outside airflow Fe and the heat recovered from the thermal losses of the electric drivetrain both contribute to heating the vehicle's passenger compartment. The fourth heat exchanger 4 does not participate in heat exchange. The internal heat exchanger 6 participates in heat exchange. The first branch of the bypass B and the third branch of the bypass DI are not traversed by the refrigerant fluid. Similarly, the fifth branch F does not carry the refrigerant. Indeed, the second one-way valve 44 prevents the refrigerant from flowing from the tenth connection point 20 to the ninth connection point 19.

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

[0185] For example, according to a mode called passenger compartment cooling and powertrain cooling, the first shut-off valve 41 is closed so as to prevent the circulation of refrigerant fluid in the first heat exchanger 1. The high-pressure refrigerant thus circulates in the second heat exchanger 2 where the heat of the refrigerant is dissipated in the outside airflow, then circulates in parallel in the fourth heat exchanger 4 and in the third heat 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 portion of the circuit 10 between the first shut-off valve 41 and the third one-way valve 45, encompassing the first heat exchanger 1, is maintained in a low-pressure state, which is the state of the refrigerant downstream of the seventh expansion valve 37. Thus, the mass of refrigerant contained in this portion of the circuit can be minimized, which reduces the amount of refrigerant required.

[0186] Other refrigerant circuit architectures are feasible.

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

Claims

Demands

1. A motor vehicle thermal conditioning system (100), 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 refrigerant flow: — a compressor (7), — a first heat exchanger (1) thermally coupled with an internal airflow (Fi) to a vehicle passenger compartment, — a first expansion valve (31), — a second expansion valve (32), — a second heat exchanger (2) configured to exchange heat with an external airflow (Fe) to the vehicle passenger compartment, — a refrigerant fluid accumulation device (8), — A first branch (B) connecting a first connection point (11) located on the main loop (A) downstream of an outlet (7b) of the compressor (7) and upstream of the first heat exchanger (1) to a second connection point (12) located on the main loop (A) downstream of the second heat exchanger (2) and upstream of the accumulation device (8), the first branch (B) comprising a third expansion valve (33), - A second branch branch (C) connecting a third connection point (13) located on the main loop (A) between the first exchanger (1) and the second expansion valve (32) to a fourth connection point (14) located on the main loop (A) downstream of the second exchanger (2) and upstream of the storage device (8), the second branch branch (C) comprising successively a fourth expansion valve (34) and a third heat exchanger (3), in which the main loop (A) includes 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 storage 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 traction chain of a motor vehicle.

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

4. Thermal conditioning system (100) according to claim 1 or 2, comprising: - A third branch branch (D2) connecting a fifth connection point (15-2) disposed 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) disposed 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 indoor airflow (Fi).

5. Thermal conditioning system (100) according to any one of the preceding claims, comprising: - A fourth branch (E) connecting a seventh connection point (17) disposed 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) disposed on the second branch (C) downstream of the fourth expansion valve (34) and upstream of the fourth connection point (14), the fourth branch (E) comprising a sixth expansion valve (36).

6. Thermal conditioning system (100) according to any one of the preceding claims, comprising: - A fifth branch (F) connecting a ninth connection point (19) disposed on the second branch (C) downstream of the third heat exchanger (3) and upstream of the fourth connection point (14) to a tenth connection point (20) disposed on the main loop (A) between the third connection point (13) and the second expansion valve (32), in which the refrigerant circuit (10) includes a second one-way valve (44) disposed on the fifth branch (F), the second one-way valve (44) being configured to permit refrigerant flow from the ninth connection point (19) to the tenth connection point (20) and configured to prohibit refrigerant flow 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 branch of bypass (C) comprises a seventh expansion valve (37) disposed 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 branch (F) comprises an eighth expansion valve (38).

9. Thermal conditioning system (100) according to any one of claims 6 to 8 in combination with claim 7, comprising a refrigerant distribution module (50) having: - a first refrigerant inlet (II), - a second refrigerant inlet (12), - a first refrigerant outlet (SI), - a second refrigerant outlet (S2), - a first channel (Cl) connecting the first inlet (II) to the first outlet (SI), - a second channel (C2) connecting the second inlet (12) to a connection point (P) disposed on the first channel (Cl) between the first inlet (II) and the first outlet (SI), - a third channel (C3) connecting the second outlet (S2) to the connection point (P), - a seventh expansion valve (37) disposed on the first channel (Cl) between the connection point (P) and the first outlet (SI),- a one-way valve (44) disposed on the second channel (C2) between the connection point (P) and the second outlet (S2), in which: the first channel (Cl) partly forms the second branch (C), the second channel (C2) partly forms the third branch of the branch (D2), the third channel (C3) forms part of the fifth branch of the derivation (F).

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

11. A method of operating a thermal conditioning system (100) according to any 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 rate (Ql) of refrigerant circulates in the compressor (7) where it passes under high pressure, and is divided between: — a second flow (Q2) circulating in the main loop (A), successively in the first exchanger (1) where it transfers heat to the internal 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 to intermediate pressure, in the second exchanger (2) where it gives up 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 branch of the bypass (Dl), successively in the fifth expansion valve (35) where it passes at low pressure, in the fourth exchanger (4) where it receives heat from the internal 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 the bypass (C), successively in the fourth expansion valve (34) where it passes at low pressure, in the third exchanger (3) where it receives heat, and joining the fourth flow (Q4), the sixth flow rate (Q6) and the fourth flow rate (Q4) forming the total flow rate (QD, 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. A method of operating a thermal conditioning system (100) according to any one of the preceding claims in combination with claims 3 and 6, in a so-called battery heating mode with energy recovery from outside air, in which: - a total flow (Q) of refrigerant 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 up 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. A method of operating a thermal conditioning system (100) according to any one of the preceding claims in combination with claims 4 and 6, in a so-called battery heating and cabin heating mode with energy recovery from outside air, in which: - a total flow rate (Ql) of refrigerant circulates in the compressor (7) where it passes under high pressure, and circulates in the main loop (A), in the first exchanger (1) where it transfers heat to the internal airflow (Fi), and divides between: — a second flow (Q2) circulating in the second bypass branch (C), successively in the fourth pressure regulator (34) where it passes at intermediate pressure, in the third heat exchanger (3) where it releases heat, — a third flow (Q3) circulating in the third bypass branch (D2), successively in the fifth expansion valve (35) where it passes to intermediate pressure, in the fourth heat exchanger (4) where it transfers heat to the internal airflow (Fi), and rejoins the second flow (Q2), the second flow (Q2) and the third flow (Q3) forming the total flow (QD, the total flow (Q1) formed circulating in the fifth branch of bypass (F), in the main loop (A) successively in the internal exchanger (6), in the second expansion valve (32) where it passes to 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).

14. A method of operating a thermal conditioning system (100) according to any 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 rate (Ql) of refrigerant circulates in the compressor (7) where it passes through a high pressure, and circulates in the main loop (A), in the first heat exchanger (1) where it releases heat to the interior airflow (Fi), and is divided between: — a second flow (Q2) 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 receives heat from the internal airflow (Fi), in the main loop A, in the seventh expansion valve (37) where it passes at low pressure, — a third flow (Q3) circulating in the main loop (A), successively in the first expansion valve (31), in the internal heat exchanger (6), in the second expansion valve (32) where it passes at low pressure, in the second heat exchanger (2) where it receives heat from the flow of outside air (Fe), and joins the second flow rate (Q2), the second flow rate (Q2) and the third flow rate (Q3) forming the total flow rate (QD, 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. A method of operating a thermal conditioning system (100) according to any one of the preceding claims in combination with claims 5 and 7, in a so-called accelerated heating mode of the passenger compartment and the battery in which: - a total flow rate (Ql) of refrigerant circulates in the compressor (7) where it passes through 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 releases heat to the internal airflow (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 releases heat, in the seventh expansion valve (37) where it passes to low pressure, — a third flow (Q3) circulating in the fourth branch of the bypass (E), in the sixth regulator (36) where it undergoes a reduction, and rejoins the second flow (Q2), the second flow rate (Q2) and the third flow rate (Q3) thus forming the total flow rate (Q1), The total flow (Ql) 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. A method of operating a thermal conditioning system (100) according to any 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 rate (Ql) of refrigerant circulates in the compressor (7) where it passes through high pressure, and circulates in the main loop (A), in the first heat exchanger (1) where it transfers heat to the internal airflow (Fi), and is divided between: — a second flow (Q2) circulating in the second bypass branch (C), successively in the fourth pressure regulator (34) where it passes to a first intermediate pressure, in the third heat exchanger (3) where it receives heat, in the seventh expansion valve (37) where it passes to low pressure, — a third flow (Q3) circulating in the main loop (A), successively in the first expansion valve (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 expansion valve (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 rate (Q2) and the third flow rate (Q3) thus forming the total flow rate (Q1), the total flow (Q 1 ) 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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