Thermal conditioning system

Abstract

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

Description

Title of the invention: Thermal conditioning system technical field

[0001] The present invention relates to the field of thermal conditioning systems. Such systems can, for example, be fitted to motor vehicles. These systems 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. The refrigerant can absorb or release heat at the various heat exchangers arranged in 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 use of such a refrigerant is therefore advantageous. However, the thermodynamic properties of this gas mean that the nominal operating pressure in the circuit is higher than with traditional refrigerants, such as fluorinated refrigerants. The compressor must therefore be capable of delivering high discharge pressures, making it a more expensive component.

[0003] Furthermore, it is desirable that the thermal conditioning system be able to operate in numerous modes, so as to optimize heat exchange management under various vehicle operating conditions. Known thermal conditioning systems generally exhibit a high degree of complexity and do not allow for all the desired operating modes. It is therefore desirable to have thermal conditioning systems with an optimized architecture, allowing a wider range of operating modes while being simpler to implement, in order to reduce their cost. Summary

[0004] To this end, a thermal conditioning system for a motor vehicle is proposed, comprising a refrigerant circuit configured to circulate a refrigerant, the refrigerant circuit having a main loop comprising successively, according to the direction of refrigerant circulation: - a compressor, - a first heat exchanger thermally coupled with a first airflow, - a first expansion valve, - a second heat exchanger thermally coupled with an element of an electric powertrain of a motor vehicle, - a second expansion valve, - a third heat exchanger configured to exchange heat with an airflow inside a passenger compartment of the vehicle, - a refrigerant accumulation device,the thermal conditioning system comprising a first branch connecting a first connection point located on the main loop downstream of the first heat exchanger and upstream of the second expansion valve to a second connection point located on the main loop downstream of the third heat exchanger and upstream of the storage device, the first branch comprising a fourth heat exchanger thermally coupled with an airflow outside the vehicle's passenger compartment, the first airflow being an airflow inside a vehicle's passenger compartment,characterized in that the thermal conditioning system comprises a second branch connecting a third connection point located on the main loop downstream of the compressor and upstream of the first heat exchanger to a fourth connection point located on the first branch between the fourth heat exchanger and the second connection point.

[0005] This refrigerant circuit architecture allows for a wide range of operating modes in a simple manner. In particular, this architecture makes it possible to cool the passenger compartment of a vehicle while simultaneously heating or cooling the electric powertrain component.

[0006] Adding the first branch off allows additional operating modes to be added to the thermal conditioning system.

[0007] The addition of the second branch of the bypass allows for the addition of further operating modes to the thermal conditioning system.

[0008] According to one embodiment, the element of the vehicle's electric powertrain includes an electrical energy storage battery.

[0009] Alternatively or in addition, the element of the vehicle's electric drive chain includes an electric vehicle traction motor.

[0010] Alternatively or in addition, the element of the vehicle's electric drive chain includes an electronic control unit for the vehicle's electric traction motor.

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

[0012] According to one embodiment, the first branch of the bypass includes a third expansion valve disposed upstream of the fourth heat exchanger.

[0013] According to one embodiment of the thermal conditioning system, the first connection point is located on the main loop downstream of the first exchanger and upstream of the first expansion valve.

[0014] According to one embodiment, the first connection point is located on the main loop downstream of the second exchanger and upstream of the second expansion valve.

[0015] According to one embodiment, the fourth heat exchanger exchanges heat with the outside airflow.

[0016] According to another embodiment, the fourth heat exchanger exchanges heat with a heat transfer fluid from a first heat transfer fluid circuit, the first heat transfer fluid circuit comprising a fifth heat exchanger configured to exchange heat with the outside airflow.

[0017] According to one embodiment, the first heat exchanger exchanges heat with the internal airflow.

[0018] According to another embodiment, the first heat exchanger exchanges heat with a heat transfer fluid from a second heat transfer fluid circuit, the second heat transfer fluid circuit comprising a sixth heat exchanger configured to exchange heat with the internal airflow.

[0019] The second heat transfer fluid circuit may include a heat exchanger configured to exchange heat with the outside airflow. Thus, the first heat exchanger is also thermally coupled with a second airflow, external to a vehicle passenger compartment. The first heat exchanger can thus be thermally coupled with the indoor airflow or with the outdoor airflow. The heat exchanger configured to exchange heat with the outside airflow can be the fifth exchanger. In other words, the first heat exchanger is also thermally coupled to a second external airflow to the vehicle's passenger compartment via a fifth exchanger located on a heat transfer fluid circuit. According to one variant, the second branch connects a third connection point located on the first branch downstream of the fourth exchanger to a fourth connection point located on the main loop downstream of the first connection point and upstream of the first pressure-reducing device.

[0020] According to one embodiment, the thermal conditioning system includes a third branch connecting a fifth connection point located on the main loop downstream of the second heat exchanger and upstream of the second expansion valve to a sixth connection point located on the first branch between the first connection point and the fourth heat exchanger.

[0021] The third branch of the bypass may include a third regulator.

[0022] The addition of the third branch of derivation makes it possible to add operating modes again to the thermal conditioning system.

[0023] The third regulator can be an electronic regulator.

[0024] According to one embodiment of the thermal conditioning system, the main loop includes an internal exchanger configured to allow heat exchange between the refrigerant circulating between the first exchanger and the first expansion valve and the refrigerant circulating downstream of the accumulation device and upstream of a compressor inlet.

[0025] According to another embodiment, the thermal conditioning system includes an internal exchanger configured to allow heat exchange between the refrigerant circulating in the first branch of bypass between the fourth exchanger and the first connection point and the refrigerant circulating in the main loop downstream of the accumulation device and upstream of a compressor inlet.

[0026] The internal exchanger allows for increased heat exchange and thus the thermodynamic performance of the thermal conditioning system.

[0027] According to an example of an embodiment of the thermal conditioning system, the main loop includes a first shut-off valve located downstream of the compressor and upstream of the first expansion valve.

[0028] The first shut-off valve can be arranged between the first connection point and the fourth connection point.

[0029] In another embodiment, the first shut-off valve is arranged between the third connection point and the first heat exchanger.

[0030] According to one embodiment of the thermal conditioning system, the first branch branch includes a second shut-off valve disposed between the second connection point and the third connection point.

[0031] According to one embodiment, the second branch branch includes a third shut-off valve.

[0032] According to one embodiment of the thermal conditioning system, the first branch branch includes a fourth shut-off valve. The fourth shut-off valve is located between the fourth connection point and the sixth connection point.

[0033] The various shut-off valves allow different portions of the refrigerant circuit to be selectively isolated or connected, and thus different operating modes to be achieved.

[0034] The first shut-off valve is, for example, an electrically operated valve.

[0035] Similarly, the second shut-off valve, the third shut-off valve and the fourth Shut-off valves can be electrically operated valves.

[0036] Each shut-off valve is a two-way valve. Each shut-off valve can be a two-position valve.

[0037] According to one embodiment of the thermal conditioning system, the second branch branch includes a first one-way valve configured to allow refrigerant fluid to circulate through the first one-way valve only from the third connection point to the fourth connection point.

[0038] According to another embodiment, the main loop includes a first one-way valve configured to allow refrigerant fluid to circulate through the first one-way valve only from the first exchanger to the first connection point.

[0039] According to one embodiment of the thermal conditioning system, the main loop includes a second one-way valve configured to allow refrigerant flow from the third exchanger to the second connection point and configured to prohibit refrigerant flow from the second connection point to the third exchanger.

[0040] According to one embodiment, the first branch branch includes a third one-way valve configured to allow refrigerant fluid to circulate through the third one-way valve only from the sixth connection point to the first connection point.

[0041] Each one-way valve is, for example, a check valve.

[0042] The various one-way valves contribute to selectively isolating or connecting different portions of the refrigerant circuit in order to achieve different modes of operation.

[0043] According to one variant, the thermal conditioning system comprises a fourth branch connecting a seventh connection point located on the main loop between the fifth connection point and the second expansion valve to an eighth connection point located on the main loop between the third heat exchanger and the second connection point, the fourth branch branch including a fifth shut-off valve.

[0044] The addition of the fourth branch allows for the addition of further operating modes to the thermal conditioning system.

[0045] The seventh connection point can be confused with the fifth connection point.

[0046] The eighth connection point can be confused with the second connection point.

[0047] The invention further relates to a method of operating a thermal conditioning system as described above, in a so-called passenger compartment cooling and battery cooling mode in which: - a total flow of refrigerant circulates in the compressor where it passes at high pressure, and circulates successively in the main loop, in the first exchanger where it gives up heat to the outside airflow, in the first expansion valve where it passes at intermediate pressure, in the second exchanger where it receives heat, in the second expansion valve where it passes at low pressure, in the third exchanger where it receives heat from the inside airflow, in the accumulation device, and returns to the compressor.

[0048] The invention also relates to a method of operating a thermal conditioning system described above, in a so-called passenger compartment cooling and battery cooling mode in which: - a total flow of refrigerant circulates in the compressor where it passes through high pressure, and circulates successively in the main loop, in the first heat exchanger where it releases heat, in the first expansion valve where it passes through intermediate pressure, in the second heat exchanger where it receives heat, in the second expansion valve where it passes through low pressure, in the third heat exchanger where it receives heat from the internal airflow, in the accumulation device, and returns to the compressor, - a flow of heat transfer fluid circulates in the first exchanger where it receives heat, then in the fifth exchanger where it gives up heat to the outside air flow, and returns to the first exchanger.

[0049] The invention further relates to a method of operating a thermal conditioning system as described above, in a so-called battery cooling mode in which: - a total flow of refrigerant circulates in the compressor where it passes under high pressure, and circulates successively in the main loop, in the second bypass branch, in the first bypass branch, in the fourth heat exchanger where it gives up heat to the outside airflow, in the main loop, in the first expansion valve where it goes to low pressure, in the second exchanger where it receives heat, in the fourth bypass branch, in the main loop, in the accumulation device, and returns to the compressor.

[0050] The invention also relates to a method of operating a thermal conditioning system according to other embodiments already described, in the so-called passenger compartment dehumidification and battery heating mode in which: - a flow of refrigerant circulates in the compressor where it passes at high pressure, and circulates successively in the main loop, in the first exchanger where it gives up heat, in the first expansion valve, in the second exchanger where it gives up heat, in the second expansion valve where it passes at low pressure, in the third exchanger where it receives heat from the internal airflow, in the accumulation device, and returns to the compressor.

[0051] The invention also relates to a method of operating a thermal conditioning system according to another embodiment described previously, in the so-called heat pump and battery heating mode in which: - a flow of refrigerant circulates in the compressor where it passes at high pressure, and circulates successively in the main loop, in the first exchanger where it gives up heat to the indoor airflow, in the first expansion valve, in the second exchanger where it gives up heat, in the third bypass branch, in the third expansion valve where it passes at low pressure, in the second bypass branch, in the fourth heat exchanger where it receives heat from the outdoor airflow, in the main loop, in the accumulation device, and returns to the compressor. Brief description of the drawings

[0052] Other features, details and advantages will become apparent upon reading the detailed description below, and upon analysis of the accompanying drawings, on which:

[0053] [Fig-1] is a schematic view of a thermal conditioning system according to a first embodiment of the invention,

[0054] [Fig.2] is a schematic view of a thermal conditioning system according to a variant of the first embodiment of the invention,

[0055] [Fig.3] is a schematic view of a thermal conditioning system according to a second embodiment of the invention,

[0056] [Fig.4] is a schematic view of a thermal conditioning system according to a first variant of the second embodiment of the invention,

[0057] [Fig.5] is a schematic view of a thermal conditioning system according to a second variant of the second embodiment of the invention,

[0058] [Fig.6] is a schematic view of a thermal conditioning system according to a third embodiment of the invention,

[0059] [Fig.7] is a schematic view of a thermal conditioning system according to a fourth embodiment of the invention,

[0060] [Fig.8] is a schematic view of a thermal conditioning system according to a variant of the fourth embodiment of the invention,

[0061] [Fig.9] is a schematic view of the thermal conditioning system of the [Fig.2], operating according to a first mode of operation, called passenger compartment cooling and battery cooling mode,

[0062] [Fig. 10] is a schematic view of the thermal conditioning system of the [Fig.3], operating according to the first operating mode, called passenger compartment cooling and battery cooling mode,

[0063] [Fig. 11] is a schematic view of the thermal conditioning system of the [Fig.8], operating according to a second operating mode, called battery cooling mode,

[0064] [Fig. 12] is a schematic view of the thermal conditioning system of the [Fig.6], operating according to a third mode of operation, called passenger compartment dehumidification and battery heating mode,

[0065] [Fig. 13] is a schematic view of the thermal conditioning system of the [Fig.7], operating according to the third mode of operation, called passenger compartment dehumidification and battery heating mode,

[0066] [Fig. 14] is a schematic view of the thermal conditioning system of the [Fig.5], operating according to a fourth operating mode, called heat pump and battery heating mode,

[0067] [Fig. 15] is a schematic view of the thermal conditioning system of the [Fig.7], operating according to the fourth operating mode, called heat pump and battery heating mode. Description of the implementation methods

[0068] To facilitate reading the figures, the various elements are not necessarily drawn to scale. In these figures, identical elements bear the same reference numerals. Certain elements or parameters may be indexed, that is, designated, for example, as first element or second element, or first parameter and second parameter, etc. This indexing aims to differentiate similar, but not identical, elements or parameters. This indexing does not imply any priority of one element or parameter over another, and the designations may be interchanged.

[0069] 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 a 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.

[0070] The expression "a second element is placed between a first element and a third element" means that the shortest path to go from the first element to the third element passes through the second element.

[0071] When it is specified that a subsystem includes a given element, this does not exclude the presence of other elements in that subsystem.

[0072] The thermal conditioning system 100, which will be described below, includes an electronic control unit (not shown) that receives information from various sensors measuring, in particular, the characteristics of the refrigerant at various points in the circuit. The electronic control unit also receives instructions from the vehicle occupants, such as the desired temperature inside the passenger compartment. The electronic control unit can also receive instructions from other electronic subsystems, such as the battery management system for electrical energy storage. The electronic control unit implements control laws to operate the various actuators in order to control the thermal conditioning system 100 and ensure compliance with the received instructions.

[0073] A compression device 7, also called a compressor, allows a refrigerant to circulate in a refrigerant circulation circuit 10. The compression device 7 can be an electric compressor, that is, a compressor whose moving parts are driven by an electric motor. The compression device 7 has a low-pressure refrigerant intake side, also called the inlet 7a of the compression device, and a high-pressure refrigerant discharge side, also called the outlet 7b of the compression device 7. The internal moving parts of the compressor 7 cause the refrigerant to go from a low pressure at the inlet 7a to a high pressure at the outlet 7b. After expansion in one or more expansion and circulation devices in at least part of the circuit, the refrigerant returns to the inlet 7a of the compressor 7 and begins a new thermodynamic cycle.

[0074] 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.

[0075] The refrigerant used by the refrigerant circuit 10 is a natural refrigerant, such as R744. R290 can also be used. A chemical refrigerant such as R1234yf or R134a can also be used.

[0076] The term "interior airflow Fi" refers to an airflow directed towards the passenger compartment of the motor vehicle. This interior airflow Fi may circulate within a heating, ventilation, and / or air conditioning (HVAC) system. This system is not shown in the various figures. A first motor-fan unit, not shown, is located within the HVAC system to increase the flow rate of the interior airflow Fi if necessary.

[0077] 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 of the climate control system 100.

[0078] 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".

[0079] The heat transfer fluid circuit(s) also form one or more closed and sealed circuits in which a heat transfer fluid can circulate.

[0080] A "loop" is understood to mean a closed circuit of fluid circulation. Starting from any initial point of a loop and following this loop, one returns to this initial point. A branch circuit consists of exactly one input and one output. Each branch circuit is connected at its ends to a portion of the main circuit. Each connection is made at a junction point. A branch can connect two distinct points of the same loop. A branch can also connect a loop to another branch. A branch can also connect two other branch lines.

[0081] Figure 1 schematically represents a first embodiment of a thermal conditioning system 100 for a motor vehicle. The thermal conditioning system 100 comprises a refrigerant circuit 10 configured to circulate a refrigerant. The refrigerant circuit 10 comprises a main loop A including successively, according to the direction of refrigerant flow: - a compressor 7, - a first heat exchanger 1 thermally coupled with a first airflow Fl, - a first regulator 31, - a second heat exchanger 2 thermally coupled with an element 25 of an electric traction chain of a motor vehicle, - a second expansion valve 32, - a third heat exchanger 3 configured to exchange heat with an interior airflow Fi to a vehicle passenger compartment, - a refrigerant fluid accumulation device 9.

[0082] This refrigerant circuit architecture allows for a simple implementation of numerous operating modes. In particular, this architecture makes it possible to cool the passenger compartment of a vehicle while simultaneously heating or cooling the element 25 of the electric powertrain, depending on the level of expansion provided by the first expansion valve 31.

[0083] The third exchanger 3, also called the passenger compartment evaporator, is located in the vehicle's heating, ventilation and / or air conditioning system.

[0084] According to the first embodiment illustrated in [Fig.1] and according to the variant illustrated in [Fig.2], the first airflow Fl is an outside airflow Fe to a passenger compartment of the vehicle.

[0085] According to the example in Figures 1 and 2, the first heat exchanger 1 exchanges heat with the outside airflow Fe. In this case, the first interchange 1 is placed for example at the front of the vehicle, just behind the grille in order to directly receive the airflow resulting from the forward movement of the vehicle.

[0086] According to the examples illustrated in the various figures, element 25 of the vehicle's electric powertrain comprises an electrical energy storage battery. Alternatively, or additionally, element 25 of the vehicle's electric powertrain may comprise a vehicle electric traction motor. Alternatively, or additionally, element 25 of the vehicle's electric powertrain may comprise an electronic control unit for the vehicle's electric traction motor.

[0087] The first regulator 31 is, for example, an electronic regulator. Similarly, the second regulator 32 can be an electronic regulator. In an electronic expansion valve, the passage area allowing the refrigerant to flow can be continuously adjusted between a minimum and maximum opening 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. The minimum opening position can be a closed position, meaning a position in which the flow of refrigerant through the expansion valve is interrupted. The refrigerant flow through the expansion valve is then zero.

[0088] According to the second, third and fourth embodiments and their variants, illustrated in figures 3 to 8, the thermal conditioning system 100 comprises a first branch branch B connecting a first connection point 11,11' located on the main loop A downstream of the first exchanger 1 and upstream of the second expansion valve 32 to a second connection point 12 located on the main loop A downstream of the third heat exchanger 3 and upstream of the storage device 9. The first branch branch B includes a fourth heat exchanger 4 thermally coupled with an outside airflow Fe to the vehicle's passenger compartment.

[0089] According to the embodiments of the thermal conditioning system 100 in Figures 3 to 8, the first airflow Fl is an interior airflow Fi to a passenger compartment of the vehicle. In this case, the first heat exchanger 1 is located in the vehicle's heating, ventilation and / or air conditioning system. The first exchanger 1 is arranged downstream of the third exchanger 3 according to the direction of flow of the indoor air flow Fi.

[0090] According to the second embodiment and its variants, as well as according to the third embodiment, illustrated in figures 3 to 6, the first branch of the bypass B includes a third expansion valve 33 arranged upstream of the fourth heat exchanger 4. The third expansion valve is located between the first connection point 11' and the fourth exchanger 4. Adding the first branch B allows for the addition of operating modes to the thermal conditioning system.

[0091] According to the second embodiment of the thermal conditioning system 100 and according to its first variant, as well as according to the third embodiment and according to the fourth embodiment, illustrated respectively in figures 3, 4, 6 and 7, the first connection point 11 is arranged on the main loop A downstream of the first exchanger 1 and upstream of the first expansion valve 31.

[0092] According to the variant of the second embodiment, illustrated in [Fig.5], the first connection point 11' is arranged on the main loop A downstream of the second exchanger 2 and upstream of the second expansion valve 32.

[0093] The thermal coupling between the fourth heat exchanger 4 and the outside airflow Fe can be of the so-called direct type or of the so-called indirect type.

[0094] According to the second embodiment, the third embodiment, and according to the fourth embodiment and its variant, the fourth heat exchanger 4 exchanges heat with the outside airflow Fe. This configuration is thus illustrated in [Fig. 3] and Figures 6 to 8. The thermal coupling between the fourth heat exchanger 4 and the outside airflow Fe is then said to be direct.

[0095] According to the first variant and the second variant of the second embodiment, the fourth heat exchanger 4 exchanges heat with a heat transfer fluid from a first heat transfer fluid circuit 21, the first heat transfer fluid circuit 21 comprising a fifth heat exchanger 5 configured to exchange heat with the outside air flow Fe. This configuration is illustrated in Figures 4 and 5. The thermal coupling between the fourth heat exchanger 4 and the outside air flow Fe is then said to be indirect, since it is achieved through a heat transfer fluid. The heat transfer fluid is, for example, a mixture of water and glycol. A circulation pump, not shown, circulates the heat transfer fluid in the first circuit 21. The pump is, for example, an electric pump, which allows the flow rate of the heat transfer fluid in the first heat transfer fluid circuit 21 to be varied on demand.

[0096] Similarly, the thermal coupling between the first heat exchanger 1 and the internal airflow Fi can be direct or indirect.

[0097] According to the embodiment examples in Figures 3, 6 and 8, the first heat exchanger 1 exchanges heat with the internal airflow Fi. The thermal coupling between the first heat exchanger 1 and the internal airflow Fi is then said to be direct.

[0098] According to the embodiment examples in Figures 4, 5 and 7, the first heat exchanger 1 exchanges heat with a heat transfer fluid from a second heat transfer fluid circuit 22, the second heat transfer fluid circuit 22 comprising a sixth heat exchanger 6 configured to exchange heat with the internal airflow Fi. The thermal coupling between the first heat exchanger 1 and the internal airflow Fi is then said to be indirect, since it is achieved through a heat transfer fluid. The heat transfer fluid is, for example, a mixture of water and glycol. The sixth heat exchanger 6 is located in the vehicle's heating, ventilation and / or air conditioning system. The sixth heat exchanger 6 plays the same role as the first heat exchanger 1 when the latter is traversed by the interior airflow Fi.

[0099] According to the second variant of the second embodiment, illustrated in [Fig. 5], the first heat exchanger 1 is also thermally coupled with a second airflow Fe external to a vehicle passenger compartment, via a fifth heat exchanger 5 located on a heat transfer fluid circuit 22. More specifically, the second heat transfer fluid circuit 22 includes a heat exchanger configured to exchange heat with the outside airflow Fe. This heat exchanger configured to exchange heat with the outside airflow Fe is here the fifth exchanger 5. The fifth heat exchanger 5 comprises a first heat exchange section located on the first heat transfer fluid circuit 21, and a second heat exchange section located on the second heat transfer fluid circuit 22. Each heat exchange section allows heat exchange between the heat transfer fluid circulating in the corresponding circuit and the outside air flow Fe. According to another variant not shown, the exchanger of the second circuit 22 configured to exchange heat with the outside airflow Fe can be a separate exchanger from the fifth exchanger 5.

[0100] According to the example in [Fig. 5], the second heat transfer fluid circuit 22 includes a circulation pump 23. The second heat transfer fluid circuit 22 also includes a three-way valve 40. The three-way valve 40 allows the flow to be directed heat transfer fluid from the first exchanger 1 to the sixth exchanger 6 or to the fifth exchanger 5. The first exchanger 1 can thus be selectively coupled to the indoor airflow, via the sixth exchanger 6, or to the outdoor airflow, via the fifth exchanger 5, depending on the position of the three-way valve 40 circulation imposed by the three-way valve 40.

[0101] According to the second embodiment, illustrated in [Fig.3], the thermal conditioning system 100 includes a second branch branch C connecting a third connection point 13 located on the first branch branch B downstream of the fourth exchanger 4 to a fourth connection point 14 located on the main loop A downstream of the first connection point 11 and upstream of the first expansion device 31. The second branch of derivation C is not present on the variants of the second embodiment, illustrated in figures 4 and 5.

[0102] According to the third embodiment and according to the fourth embodiment, as well as its variant, illustrated in figures 6 to 8, the thermal conditioning system 100 comprises a second branch branch C' connecting a third connection point 13 located on the main loop A downstream of the compressor 7 and upstream of the first exchanger 1 to a fourth connection point 14 located on the first branch branch B between the fourth exchanger 4 and the second connection point 12.

[0103] The addition of the second branch of derivation C makes it possible to add even more operating modes to the thermal conditioning system. The third connection point 13 is located between the outlet 7b of the compressor 7 and the first heat exchanger 1. The fourth connection point 14 is located between the fourth heat exchanger 4 and the second connection point 12.

[0104] According to the fourth embodiment and its variant, shown schematically in Figures 7 and 8, the thermal conditioning system 100 includes a third branch D connecting a fifth connection point 15 located on the main loop A downstream of the second heat exchanger 2 and upstream of the second expansion valve 32 to a sixth connection point 16 located on the first branch B between the first connection point 11 and the fourth heat exchanger 4.

[0105] The third branch D includes a third regulator 33'. The third regulator 33 may be an electronic regulator.

[0106] The addition of the third branch of derivation D makes it possible to add more operating modes to the thermal conditioning system.

[0107] The fifth connection point 15 is located between the second exchanger 2 and the second expansion valve 32. The sixth connection point 16 is located between the first connection point 11 and the fourth exchanger 4.

[0108] The thermal conditioning system 100 may include an internal exchanger 8, 8'.

[0109] According to the variant of the first embodiment, illustrated in [Fig.2], as well as in the other embodiments illustrated in Figures 3 to 5 and 7 to 8, the main loop A includes an internal exchanger 8 configured to allow heat exchange between the refrigerant circulating between the first exchanger 1 and the first expansion valve 31 and the refrigerant circulating downstream of the accumulation device 9 and upstream of an inlet 7a of the compressor 7.

[0110] The internal exchanger makes it possible to improve the thermal performance of the thermal conditioning system 100 by increasing the enthalpy variation during the thermodynamic cycle carried out by the refrigerant fluid.

[0111] The internal heat exchanger 8 has a first heat exchange section 8a arranged on the main refrigerant loop between the first heat exchanger 1 and the first expansion valve 31. The internal heat exchanger 8 has a second heat exchange section 8b arranged on the main refrigerant loop A between the accumulator 9 and the inlet 7a of the compressor 7. The internal exchanger 8 is configured to allow heat exchange between the low-pressure refrigerant in the second heat exchange section 8b and the high-pressure refrigerant in the first heat exchange section 8a.

[0112] According to the second embodiment, [Fig.3], the first heat exchange section 8a is downstream of the fourth connection point 14. According to the first variant of the second embodiment, [Fig.4], the first heat exchange section 8a is downstream of the first connection point 11.

[0113] According to the third embodiment, corresponding to [Fig.6], the thermal conditioning system 100 includes an internal exchanger 8' configured to allow heat exchange between the refrigerant circulating in the first branch of bypass B between the fourth exchanger 4 and the first connection point 11 and the refrigerant circulating in the main loop A downstream of the accumulation device 9 and upstream of an inlet 7a of the compressor 7.

[0114] The internal heat exchanger 8' includes a first heat exchange section 8a' arranged on the first branch of the bypass B between the first connection point 11 and the third expansion valve 33. The internal heat exchanger 8 includes a second heat exchange section 8b arranged on the main refrigerant loop A between the accumulator 9 and the inlet 7a of the compressor 7. The internal exchanger 8' is configured to allow heat exchange between the low-pressure refrigerant in the second heat exchange section 8b' and the high-pressure refrigerant in the first heat exchange section 8a'.

[0115] According to the illustrated example, an internal heat exchanger is present in all embodiments except the first embodiment, illustrated in [Fig. 1]. However, the presence of the internal heat exchanger is not essential. Variants of the second, third, and fourth embodiments in which the internal heat exchanger is not present may be implemented.

[0116] The thermal conditioning system 100 includes a set of shut-off valves for selectively blocking or allowing the circulation of the refrigerant. The various shut-off valves allow different portions of the refrigerant circuit 10 to be selectively isolated or connected, thus enabling different operating modes of the thermal conditioning system 100.

[0117] According to the second embodiment, as well as the third and fourth embodiments of the thermal conditioning system 100, the main loop A includes a first shut-off valve 41, 41' disposed downstream of the compressor 7 and upstream of the first expansion valve 31.

[0118] The first shut-off valve 41 can be arranged between the first connection point 11 and the fourth connection point 14. This configuration corresponds to the second embodiment, [Fig.3].

[0119] The first shut-off valve 41' can be disposed between the third connection point 13 and the first heat exchanger 1. This is the configuration shown in figures 6 to 8.

[0120] According to the second embodiment, as well as the third and fourth embodiments of the thermal conditioning system 100, the first branch branch B includes a second shut-off valve 42 disposed between the second connection point 12 and the third connection point 13. The first variant of the second embodiment, as well as the second variant, illustrated in figures 4 and 5, do not include a shut-off valve on the first branch of the B branch.

[0121] According to the third and fourth embodiments, the second branch of the bypass C' includes a third shut-off valve 43. The third shut-off valve 43 is located between the third connection point 13 and the fourth connection point 14.

[0122] According to the variant of the fourth embodiment of the thermal conditioning system 100, illustrated in [Fig.8], the first branch of the bypass B includes a fourth shut-off valve 44.

[0123] The fourth shut-off valve 44 is arranged between the fourth connection point 14 and the sixth connection point 16.

[0124] The first shut-off valve 41, 41' is, for example, an electrically operated valve. Similarly, the second shut-off valve 42, the third shut-off valve 43 and the fourth shut-off valve 44 can be electrically operated valves. Each shut-off valve 41, 41', 42, 43, 44 is a two-way valve. In other words, in the illustrated example, each shut-off valve has exactly one inlet and one outlet for refrigerant.

[0125] Each stop valve can be a two-position valve. A two-position valve is a valve with two stable equilibrium positions. In the first position, corresponding to the valve being closed, the fluid passage area is zero and fluid flow through the valve is blocked. According to a second position corresponding to an open state of the valve, the fluid passage area is at its maximum and fluid circulation through the valve is permitted.

[0126] Alternatively, the first stop valve 41' and the third stop valve 43 can be proportional valves. A proportional valve includes a movable disc whose position can vary continuously between a closed position and a fully open position. A proportional valve thus allows not only the selective control of fluid flow, but also the continuous adjustment of the fluid flow rate through the valve.

[0127] In addition to the shut-off valves already described, the thermal conditioning system 100 includes a set of one-way valves. A one-way valve allows fluid to flow through that valve only in one direction. The various one-way valves help to selectively isolate or connect different portions of the refrigerant circuit 10 in order to achieve different operating modes.

[0128] According to the second embodiment, schematically shown in [Fig.3], the second branch of the branch C includes a first one-way valve 47 configured to allow refrigerant fluid to circulate through the first one-way valve 47 only from the third connection point 13 to the fourth connection point 14.

[0129] In other words, the first one-way valve 47 is configured to allow refrigerant fluid to circulate through the first one-way valve 47 from the third connection point 13 to the fourth connection point 14. configured to prohibit refrigerant flow through the first one-way valve 47 from the fourth connection point 14 to the third connection point 13.

[0130] According to the second and third embodiments, the main loop A includes a first one-way valve 47' configured to allow refrigerant fluid to circulate through the first one-way valve 47' only from the first exchanger 1 to the first connection point 11.

[0131] In other words, the main loop A includes a first one-way valve 47' configured to allow refrigerant flow through the first one-way valve 47' from the first exchanger 1 to the first connection point 11 and configured to prohibit refrigerant flow through the first one-way valve 47' from the first connection point 11 to the first exchanger 1.

[0132] According to the third and fourth embodiment, the main loop A includes a second one-way valve 48 configured to allow refrigerant fluid to circulate through the second one-way valve 48 only from the third exchanger 3 to the second connection point 12.

[0133] In other words, the main loop A includes a second one-way valve 48 configured to allow refrigerant flow through the second one-way valve 48 from the third exchanger 3 to the second connection point 12, and configured to prohibit refrigerant flow through the second one-way valve 48 from the second connection point 12 to the third exchanger 3.

[0134] According to the variant of the fourth embodiment, [Fig.8], the second one-way valve 48 is arranged between the third exchanger 3 and the eighth connection point 18.

[0135] According to the fourth embodiment and its variant, the first branch branch B includes a third one-way valve 49 configured to allow refrigerant fluid to circulate through the third one-way valve 49 only from the sixth connection point 16 to the first connection point 11.

[0136] In other words, the first branch branch B includes a third one-way valve 49 configured to permit refrigerant flow through the third one-way valve 49 from the sixth connection point 16 to the first connection point 11 and configured to prohibit refrigerant flow through the third one-way valve 49 from the first connection point 11 to the sixth connection point 16.

[0137] Each one-way valve 47, 48, 49 is for example a non-return valve. A check valve is a passive device that reacts to the pressure difference between its inlet and outlet. No electrical control is required.

[0138] The variant of the fourth embodiment, illustrated in [Fig.8], differs from the fourth embodiment by the presence of an additional branch E and by the presence of an additional shut-off valve 44.

[0139] According to this variant, the thermal conditioning system 100 includes a fourth branch E connecting a seventh connection point 17 located on the main loop A between the fifth connection point 15 and the second expansion valve 32 to an eighth connection point 18 located on the main loop A between the third heat exchanger 3 and the second connection point 12. The fourth branch E includes a fifth shut-off valve 45.

[0140] The addition of the fourth branch E allows the low-pressure refrigerant from the second heat exchanger 2 to return to the accumulator 9 and then to the inlet 7a of the compressor 7 without passing through the second expansion valve 2 or the third heat exchanger 3. The pressure drop of the low-pressure circuit is thus reduced, which makes it possible to improve the thermodynamic performance in cooling mode of the element 25 alone.

[0141] The fifth shut-off valve 45 can be a two-position valve. The fifth shut-off valve 45 can also be a proportional valve. In this case, this valve allows adjustment of the quantity of refrigerant bypassing the third heat exchanger 3.

[0142] In the example shown, the seventh connection point 17 coincides with the fifth connection point 15. Similarly, the eighth connection point 18 is confused with the second connection point 12.

[0143] Figures 9 to 15 illustrate several modes of operation of a thermal conditioning system according to different embodiments. In these figures, the portions of the refrigerant circuit 10 in which a flow of refrigerant circulates are shown in thick solid lines, while the portions in which the refrigerant does not circulate are shown in thin dashed lines.

[0144] Fig. 9 illustrates a method of operation of a thermal conditioning system 100 according to the first embodiment, in a first operating mode called passenger compartment cooling and battery cooling mode.

[0145] According to this mode of operation: - a total flow rate Q of refrigerant circulates in the compressor 7 where it passes through high pressure, and circulates successively in the main loop A, in the first heat exchanger 1 where it transfers heat to the outside air flow Fe, in the first expansion valve 31 where it passes to intermediate pressure, in the second exchanger 2 where it receives heat, in the second expansion valve 32 where it passes to low pressure, in the third exchanger 3 where it receives heat from the internal airflow Fi, in the accumulation device 9, and returns to the compressor 7.

[0146] The high-pressure refrigerant fluid passes through the first exchanger 1 and dissipates heat into the outside airflow Fe. The high-pressure refrigerant then passes through the first heat exchange section 8a of the internal exchanger 8. The cooled refrigerant then undergoes two successive expansions, the first in the first expansion valve 31 and the second in the second expansion valve 32. The intermediate-pressure refrigerant flow after the first expansion receives heat at the second heat exchanger 2, which cools the component 25 of the vehicle's electric powertrain. The low-pressure refrigerant flow after the second expansion receives heat at the third heat exchanger 3, which cools the interior airflow Fi. The traction chain element 25 and the passenger compartment are jointly cooled. The respective expansion level achieved by each of the expansion valves 31, 32 allows the cooling power supplied on the one hand to the electric traction chain element 25 and on the other hand to the vehicle passenger compartment, i.e., the distribution of the cooling power is adjusted. In all operating modes, the intermediate pressure is lower than the high pressure and results from expansion. Similarly, the low pressure is lower than both the high pressure and the intermediate pressure, and also results from expansion. The refrigerant fluid from the accumulator 9 passes through the second heat exchange section 8b of the internal exchanger 8 before being drawn back into the compressor 7.

[0147] Fig. 10 illustrates a method of operation of a thermal conditioning system 100 according to the second variant of the second embodiment, in the first operating mode called passenger compartment cooling mode and battery cooling.

[0148] According to this mode of operation: - a total flow Q of refrigerant circulates in the compressor 7 where it passes at high pressure, and circulates successively in the main loop A, in the first exchanger 1 where it gives up heat, in the first expansion valve 31 where it passes at intermediate pressure, in the second exchanger 2 where it receives heat, in the second expansion valve 32 where it passes at low pressure, in the third exchanger 3 where it receives heat from the internal air flow Fi, in the accumulation device 9, and returns to the compressor 7; - a flow D of heat transfer fluid circulates in the first exchanger 1 where it receives heat, then in the fifth exchanger 5 where it gives up heat to the outside air flow Fe, and returns to the first exchanger 1.

[0149] The high-pressure refrigerant fluid at the outlet of the compressor 7 passes through the first heat exchanger 1 and supplies heat to the heat transfer fluid of the circuit 22. The high-pressure refrigerant fluid is thus cooled. The cooled, high-pressure refrigerant then passes through the first heat exchange section 8a of the internal exchanger 8. As was the case with the first embodiment, in this operating mode the refrigerant undergoes two successive expansions, the first in the first expansion valve 31 and then the second in the second expansion valve 32. The level of expansion achieved by each of the expansion valves 31, 32 allows the cooling power supplied on the one hand to the element 25 of the vehicle's electric traction chain and on the other hand to the vehicle's passenger compartment. The third expansion valve 33 is in the closed position, there is no circulation of refrigerant fluid in the bypass branch B and in the fourth exchanger 4. The refrigerant circulates only in the main loop A. The refrigerant from the third exchanger 3 joins the accumulator 9 then passes through the second heat exchange section 8b of the internal exchanger 8 before joining the inlet 7a of the compressor 7. The heat transferred to the heat transfer fluid in circuit 22 is dissipated into the outside airflow Fe. To achieve this, the three-way valve 40 directs the heat transfer fluid from the first heat exchanger 1 to the fifth heat exchanger 5, and prevents the circulation of heat transfer fluid in the sixth heat exchanger 6. The circulation pump 23 is activated. The arrows marked with the symbol D illustrate the circulation of the heat transfer fluid.

[0150] Fig. 11 illustrates a method of operation of a thermal conditioning system 100 according to the variant of the fourth embodiment, in a second operating mode called battery cooling mode.

[0151] According to this mode of operation: - a total flow Q of refrigerant circulates in the compressor 7 where it passes at high pressure, and circulates successively in the main loop A, in the second branch of bypass C', in the first branch of bypass B, in the fourth heat exchanger 4 where it gives up heat to the outside air flow Fe, in the main loop A, in the first expansion valve 31 where it passes at low pressure, in the second exchanger 2 where it receives heat, in the fourth branch of bypass E, in the main loop A, in the accumulation device 9, and returns to the compressor 7.

[0152] The first shut-off valve 41' is in the closed position, and the third shut-off valve 43 is in the open position. Thus, the high-pressure refrigerant from the compressor 7 is directed to the second bypass branch C'. The refrigerant from the third shut-off valve 43 leaves the second branch C' at the fourth connection point 14 and joins the first branch B. The second shut-off valve 42 is in the closed position, so the refrigerant flows from the fourth connection point 14 to the sixth connection point 16. The high-pressure refrigerant passes through the fourth heat exchanger 4 and dissipates heat into the outside airflow Fe, thus being cooled. The cooled refrigerant then undergoes expansion by passing through the first expansion valve 31 and goes to low pressure. The low-pressure refrigerant flow absorbs heat and evaporates at the second heat exchanger 2, thus cooling the component 25 of the vehicle's electric drive system. The second expansion valve 32 is closed, blocking the flow of refrigerant to the third heat exchanger 3. The fifth shut-off valve 45 is open. The low-pressure refrigerant from the second heat exchanger 2 is therefore directed to the fourth branch line E without passing through the main loop section A extending between the seventh connection point 17 and the eighth connection point 18, which includes the second expansion valve 32 and the third heat exchanger 3. This reduces the pressure drop to the accumulator 9, thereby increasing the cooling capacity that can be provided by the second heat exchanger 2. The second one-way valve 48 prevents the low-pressure refrigerant from flowing from the eighth connection point 18 to the third exchanger 3 and accumulating there. The traffic flow in the internal interchange 8 is the same as before.

[0153] It is also possible to partially open the third expansion valve 33' so that some of the refrigerant from the fourth heat exchanger 4 flows into the third bypass branch D, and therefore does not contribute to the heat exchange in the internal heat exchanger 8. The efficiency of the internal heat exchanger 8 can thus be controlled by adjusting the opening of the third expansion valve 33', thereby adjusting the flow rate of refrigerant circulating in the third bypass branch D and bypassing the internal heat exchanger 8. By reducing the efficiency of the internal heat exchanger 8, the temperature of the gaseous refrigerant at the inlet 7a of the compressor 7 can be limited, which also makes it possible to keep the discharge temperature at the outlet 7b of the compressor 7 below an acceptable upper limit. The thermal stresses on the compressor 7 can thus be limited.

[0154] Figures 12 and 13 illustrate a third operating mode, referred to as the passenger compartment dehumidification and battery heating mode. Figure 12 relates to the third embodiment and Figure 13 relates to the fourth embodiment.

[0155] According to this mode of operation: - a flow Q of refrigerant circulates in the compressor 7 where it passes to high pressure, and circulates successively in the main loop A, in the first exchanger 1 where it gives up heat, in the first expansion valve 31, in the second exchanger 2 where it gives up heat, in the second expansion valve 32 where it passes to low pressure, in the third exchanger 3 where it receives heat from the internal air flow Fi, in the accumulation device 9, and returns to the compressor 7.

[0156] The third shut-off valve 43 is in the closed position and the first shut-off valve 41' is in the open position, so as to direct the flow of refrigerant from the compressor 7 to the first heat exchanger 1, through the main branch. At the third connection point 13, the circulation of refrigerant in the second bypass branch C' is blocked. When the architecture of the refrigerant circuit 10 corresponds to the third embodiment, [Fig.12], the second shut-off valve 42 is in the closed position, and prevents the refrigerant from the first exchanger 1 from circulating in the first branch branch B from the first connection point 11. When the architecture of the refrigerant circuit 10 corresponds to the fourth embodiment, [Fig. 13], the third one-way valve 49 prevents the refrigerant from the first exchanger 1 from circulating in the first branch branch B. The third expansion valve 33' and the second shut-off valve 42 are in the closed position. The high-pressure refrigerant circulates in the first exchanger 1, and heats the heat transfer fluid in the second circuit 22. The heated heat transfer fluid releases heat to the internal airflow Fi at the sixth exchanger 6. The first expansion valve 31 is preferably in the fully open position, and the refrigerant does not undergo any expansion there. The second expansion valve 32 expands the refrigerant to a low-pressure state. The third expansion valve 33 is in the closed position. The third branch of the bypass D is not carrying the refrigerant. It is also possible to cause a partial expansion of the refrigerant at the first expansion valve 31, in order to obtain different condensation pressures in the first exchanger 1 and in the second exchanger 2, and thus different temperature levels. The indoor airflow Fi is heated at the sixth heat exchanger 6 by the heat supplied by the refrigerant at the first heat exchanger 1. The flow The indoor air Fi is also cooled at the third exchanger 3, which allows the indoor air flow Fi to be dehumidified. The heat given off by the refrigerant at the second exchanger 2 is used to heat element 25 of the traction chain. The outside airflow Fe provides the heat necessary for the evaporation of the refrigerant in the fourth exchanger 4.

[0157] Fig. 14 illustrates a method of operation of a thermal conditioning system 100 according to the second variant of the second embodiment, in a fourth mode of operation called heat pump and battery heating mode.

[0158] According to this mode of operation: - a flow Q of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates successively in the main loop A, in the first exchanger 1 where it gives up heat to the internal airflow Fi, in the first expansion valve 31, in the second exchanger 2 where it gives up heat, in the first bypass branch B, in the third expansion valve 33 where it passes at low pressure, in the fourth heat exchanger 4 where it receives heat from the external airflow Fe, in the main loop A, in the accumulation device 9, and returns to the compressor 7.

[0159] As before, the first expansion valve 31 is preferably in the fully open position, and the refrigerant does not undergo expansion. The third expansion valve 33 expands the refrigerant to a low-pressure state. The second expansion valve 32 is in the closed position, and the refrigerant from a second heat exchanger 2 does not circulate through the third expansion valve 3. At the first connection point 11', the refrigerant leaves the main loop A and takes the first branch of the bypass B. The indoor airflow Fi is heated at the level of the sixth exchanger 6 thanks to the heat transmitted by the refrigerant fluid to the heat transfer fluid of the second circuit 22 at the level of the first exchanger 1. The heat given off by the refrigerant at the second exchanger 2 also allows the element 25 of the traction chain to be heated. The outside airflow Fe provides the heat necessary for the evaporation of the refrigerant in the fourth exchanger 4. The total heating power supplied by the thermal conditioning system 100 can be distributed between power supplied to the indoor airflow Fi and power supplied to the element 25. This distribution can be controlled by the respective expansion level of the first expansion valve 31 and the third expansion valve 33, as well as by the control of the indoor airflow Fi. The circulation of the refrigerant fluid in the internal exchanger 8 is the same as that already described. As with the previous operating mode, the first expansion valve 31 can be in a partially open position so as to achieve a partial expansion of the refrigerant at the level of the first expansion valve 31. The condensation pressure in the first heat exchanger 1 can thus be different from the condensation pressure in the second heat exchanger 2, and different temperature levels can be obtained in the first heat exchanger 1 and the second heat exchanger 2.

[0160] Fig. 15 illustrates a method of operation of a thermal conditioning system 100 according to the fourth embodiment, in the fourth operating mode known as heat pump and battery heating mode.

[0161] According to this mode of operation: - a flow Q of refrigerant fluid circulates in the compressor 7 where it passes to high pressure, and circulates successively in the main loop A, in the first exchanger 1 where it gives up heat to the internal airflow Fi, in the first expansion valve 31, in the second exchanger 2 where it gives up heat, in the third bypass branch D, in the third expansion valve 33' where it passes to low pressure, in the second bypass branch B, in the fourth heat exchanger 4 where it receives heat from the external airflow Fe, in the main loop A, in the accumulation device 9, and returns to the compressor 7.

[0162] The heat exchanges take place in the same way when the architecture of the refrigerant circuit 10 corresponds to the fourth embodiment, and are identical to what has been described previously for the second variant of the second embodiment. The refrigerant from the second heat exchanger 2 flows into the third branch line D and is expanded by the third expansion valve 33'. At the fifth connection point 15, the refrigerant leaves the main loop A and is redirected to the third branch line D. At the sixth connection point 16, the refrigerant leaves the third branch line D and joins the first branch line B. At the second connection point 12, the refrigerant from the fourth heat exchanger 4 joins the main loop A. The third one-way valve 49 prevents the high-pressure refrigerant from the first exchanger 1 from flowing into the first branch branch B, because the refrigerant cannot flow from the first connection point 11 to the sixth connection point 16. The second shut-off valve 42 is in the open position, and the third shut-off valve 43 is in the closed position.

Claims

1. Demands Thermal conditioning system (100) for a motor vehicle, comprising a refrigerant circuit (10) configured to circulate a refrigerant, the refrigerant circuit (10) comprising a main loop (A) comprising successively, according to the direction of refrigerant flow: - a compressor (7), - a first heat exchanger (1) thermally coupled with a first airflow (Fl), - a first regulator (31), - a second heat exchanger (2) thermally coupled with an element (25) of an electric drivetrain of a motor vehicle, - a second regulator (32), - a third heat exchanger (3) configured to exchange heat with an interior airflow (Fi) to a vehicle passenger compartment, - a refrigerant fluid accumulation device (9), the thermal conditioning system comprising a first branch (B) connecting a first connection point (11,11') disposed on the main loop (A) downstream of the first heat exchanger (1) and upstream of the second expansion valve (32) to a second connection point (12) disposed on the main loop (A) downstream of the third heat exchanger (3) and upstream of the accumulation device (9), the first branch (B) comprising a fourth heat exchanger (4) thermally coupled with an exterior airflow (Fe) to the vehicle passenger compartment, the first airflow (Fl) being an internal airflow (Fi) to a vehicle's passenger compartment, characterized in that the thermal conditioning system includes a second branch branch (C') connecting a third connection point (13) located on the main loop (A) downstream of the compressor (7) and upstream of the first exchanger (1) to a fourth connection point (14) located on the first branch branch (B) between the fourth exchanger (4) and the second connection point (12).

2. Thermal conditioning system (100) according to claim 1, wherein the first branch of bypass (B) includes a third expansion valve (33) disposed upstream of the fourth heat exchanger (4).

3. Thermal conditioning system (100) according to claim 1 or 2, wherein the first connection point (11) is disposed on the main loop (A) downstream of the first exchanger (1) and upstream of the first expansion valve (31).

4. Thermal conditioning system (100) according to any one of claims 1 to 3, comprising a third branch (D) connecting a fifth connection point (15) disposed on the main loop (A) downstream of the second heat exchanger (2) and upstream of the second expansion valve (32) to a sixth connection point (16) disposed on the first branch (B) between the first connection point (11) and the fourth heat exchanger (4), wherein the third branch (D) comprises a third expansion valve (33').

5. Thermal conditioning system (100) according to any one of claims 1 to 4, wherein the main loop (A) includes an internal exchanger (8) configured to permit heat exchange between the refrigerant circulating between the first exchanger (1) and the first expansion valve (31) and the refrigerant circulating downstream of the storage device (9) and upstream of an inlet (7a) of the compressor (7).

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

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

8. Thermal conditioning system (100) according to any one of the preceding claims in combination with claim 4, comprising a fourth branch (E) connecting a seventh connection point (17) disposed on the main loop (A) between the fifth connection point (15) and the second expansion valve (32) to an eighth connection point (18) disposed on the main loop (A) between the third heat exchanger (3) and the second connection point (12), the fourth branch (E) comprising a fifth shut-off valve (45).

9. Method of operating a thermal conditioning system (100) according to claim 1, in a mode called cabin cooling and battery cooling in which: - a total flow (Q) of refrigerant circulates in the compressor (7) where it passes at high pressure, and circulates successively in the main loop (A), in the first exchanger (1) where it gives up heat to the outside airflow (Fe), in the first expansion valve (31) where it passes at intermediate pressure, in the second exchanger (2) where it receives heat, in the second expansion valve (32) where it passes at low pressure, in the third exchanger (3) where it receives heat from the inside airflow (Fi), in the accumulation device (9), and returns to the compressor (7).

10. A method of operating a thermal conditioning system (100) according to claim 8, in a so-called battery cooling mode in which: - a total flow rate (Q) of refrigerant circulates in the compressor (7) where it is under high pressure, and circulates successively in the main loop (A), in the second bypass branch (C'), in the first bypass branch (B), in the fourth heat exchanger (4) where it transfers heat to the outside airflow (Fe), in the main loop (A), in the first expansion valve (31) where it passes to low pressure, into the second exchanger (2) where it receives heat, into the fourth bypass branch (E), into the main loop (A), into the accumulation device (9), and returns to the compressor (7).

11. Method of operating a thermal conditioning system (100) according to any one of claims 1 to 4, in a mode called passenger compartment dehumidification and battery heating in which: - a flow (Q) of refrigerant fluid circulates in the compressor (7) where it passes to high pressure, and circulates successively in the main loop (A), in the first exchanger (1) where it gives up heat, in the first expansion valve (31), in the second exchanger (2) where it gives up heat, in the second expansion valve (32) where it passes to low pressure, in the third exchanger (3) where it receives heat from the interior airflow (Fi), in the storage device (9), and returns to the compressor (7).

12. Method of operating a thermal conditioning system (100) according to any one of claims 1 to 4, in a so-called heat pump and battery heating mode in which: - a flow (Q) of refrigerant circulates in the compressor (7) where it passes at high pressure, and circulates successively in the main loop (A), in the first exchanger (1) where it gives up heat to the indoor airflow (Fi), in the first expansion valve (31), in the second exchanger (2) where it gives up heat, in the third bypass branch (D), in the third expansion valve (33') where it passes at low pressure, in the second bypass branch (B), in the fourth heat exchanger (4) where it receives heat from the outdoor airflow (Fe), in the main loop (A), in the storage device (9), and returns to the compressor (7).

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