Vehicle thermal management system

Abstract

A thermal management system (1) for a vehicle, comprising: - a main branch (3) comprising a main heat exchanger (34) and extending between a main junction (31) and a main branch point (32); - a first branch (4) and a second branch (5) extending between the main branch point (32) and the main junction (31), the first branch (4) comprising a first heat exchanger (41) and a device (42) for storing refrigerant (FR), the second branch (5) comprising a second heat exchanger (51); - a secondary branch (7) comprising a secondary heat exchanger (73) and extending between a first branch point (71) arranged between a compression device (33) and the main heat exchanger (34) and a first junction point (72) arranged between the main heat exchanger (34) and the main junction (31).

Description

[0001] The field of the invention is that of thermal management systems for vehicles, in particular for hybrid or electric vehicles, comprising at least one refrigerant circuit.

[0002] Motor vehicles are generally equipped with a refrigerant circuit for heating or cooling various areas or various components of the vehicle. It is in particular known that this refrigerant circuit is used to thermally treat the air flow conveyed to the interior of the vehicle equipped with such a circuit. This refrigerant circuit is incorporated into a thermal management system associated with the facilities for heating, ventilating and / or air conditioning the vehicle interior, to thermally manage the air flow outside the vehicle and towards the vehicle interior. In particular, by means of the change of state of the refrigerant, this circuit allows the air flow fed into the heating, ventilation and / or air conditioning facilities to be heated and / or cooled.

[0003] In another application of this circuit, it is known to use the circuit to cool at least one element of the electric powertrain of the vehicle, that is to say, of the powertrain comprising a motor operated at least partially using electrical energy supplied by one or more electrical energy storage devices on board the vehicle. Since all these elements are difficult to withstand excessive temperature variations, it is understood that the thermal management system, and in particular the refrigerant circuit, ensures thermal regulation, more particularly cooling, of these elements. In particular, this element of the powertrain can be an electrical energy storage device for supplying electrical energy, or an electric motor capable of moving the vehicle. The refrigerant circuit is thus designed to cool this electrical energy storage device to a temperature that remains moderate.

[0004] This thermal management system is generally arranged at least partially at the front end of the vehicle. More particularly, these thermal management systems traditionally comprise at least one heat exchanger arranged at this front end. The reduction in size of such a heat exchanger, when it comes to limiting the size of the devices arranged at the front end, is accompanied by a loss of efficiency of the thermal management system, and thus by a loss of its ability to cool the various electrical elements mentioned above.

[0005] This loss of performance is particularly apparent when the electrical energy storage device of the vehicle is used in such a way that it is significantly warmed up, for example during a fast charging phase of the storage device. Fast charging involves charging the electrical energy storage device at high voltage and current, to charge the electrical energy storage device in a short time of a few tens of minutes. This fast charging causes the electrical energy storage device to heat up to a greater extent than that found during normal operation of the storage device, and therefore needs to be managed.

[0006] Moreover, during the charging or fast charging phase, it can be necessary to maintain acceptable thermal comfort levels inside the vehicle, which means that the refrigerant circuit can need to be able to simultaneously thermally manage the interior and thermally manage the storage device. This need means that the performance of the thermal management system requires the system, in particular the heat exchanger arranged at the front, to have a certain size which makes the system somewhat incompatible with the front end size constraints imposed on current motor vehicles, in particular vehicles driven by electric motors.

[0007] The present invention falls within this context and seeks to solve these various drawbacks by proposing a thermal management system intended for a vehicle and comprising at least one circuit for a refrigerant having a main branch extending between a main junction point and a main branching point, and at least one first branch and one second branch extending between the main branching point and the main junction point, in parallel with each other and in series with the main branch:

[0008] - the main branch having at least one compression device and a main heat exchanger configured to implement a heat exchange between the refrigerant and an external air flow of the vehicle interior;

[0009] - the first branch comprising a first heat exchanger and a storage device for the refrigerant arranged between the first heat exchanger and the main junction point;

[0010] - the second branch comprising a second heat exchanger.

[0011] The refrigerant circuit according to the invention further comprises a secondary branch extending between a first branching point arranged on the main branch between the compression device and the main heat exchanger and a first junction point arranged on the main branch between the main heat exchanger and the main branching point, the secondary branch comprising a secondary heat exchanger configured to implement a heat exchange between the refrigerant and an internal air flow sent to the vehicle interior.

[0012] It should be understood that throughout the following description, the qualifiers “main”, “first”, “second” or “primary”, “secondary” have the purpose of distinguishing similar elements of the thermal management system and do not imply any type of hierarchy with respect to the components within said system.

[0013] The refrigerant circuit of the thermal management system according to the application is configured to operate in a heat pump mode for heating the internal air flow before being delivered to the vehicle interior or to operate alternately in an air conditioning mode for cooling the internal air flow before being delivered to the vehicle interior. Depending on the implemented mode of operation, the main heat exchanger and the first or second heat exchanger can be configured to operate as a condenser or as an evaporator with respect to the refrigerant. In other words, the first or second heat exchanger can be installed in a heating, ventilation and / or air conditioning installation.

[0014] Advantageously, the secondary heat exchanger can be configured to implement a direct heat exchange between the refrigerant and the internal air flow. Alternatively, the secondary heat exchanger can be configured to implement a heat exchange between the refrigerant and a heat transfer fluid circulating in an auxiliary loop, which can comprise at least one auxiliary heat exchanger configured to implement a heat exchange between the heat transfer fluid and the internal air flow. In this way, the secondary heat exchanger contributes to implementing an indirect heat exchange between the refrigerant and the internal air flow via the heat transfer fluid circulating in the auxiliary loop.

[0015] The "accumulator device" is understood to be a device that makes it possible to separate the liquid phase from the gaseous phase of the refrigerant and to accumulate the liquid phase of the refrigerant to deliver refrigerant that is substantially gaseous towards the compression device.

[0016] Within the thermal management system, at least the first heat exchanger and / or the main heat exchanger are intended to supply the refrigerant to the accumulator device, while the second heat exchanger provided in the second branch is intended to bypass said accumulator device. In particular, the second heat exchanger is connected downstream of the accumulator device in the direction of circulation of the refrigerant in the circuit, to be able to superheat the fluid that reaches the compression device directly, thus contributing to improving the coefficient of performance of the circuit. The term "directly" means without a bottle or accumulator device between the second heat exchanger and the compression device.

[0017] According to an optional feature of the application, at least one of the first heat exchanger and the second heat exchanger can be thermally coupled to a heat transfer fluid loop comprising at least one element of the electric powertrain of the vehicle, and at least the other of the first heat exchanger and the second heat exchanger can be configured to implement a heat exchange between the refrigerant and an internal air flow of the vehicle interior.

[0018] According to different embodiments of the application, the first heat exchanger or the second heat exchanger can be thermally coupled to one of the elements of the electric powertrain of the vehicle.

[0019] Throughout the following description, the expression "first embodiment" will be used to specifically illustrate a thermal management system in which the first heat exchanger is configured to implement a heat exchange between the refrigerant and the internal air flow, while the second heat exchanger is thermally coupled to at least one element of the powertrain.

[0020] The expression "second embodiment" will be used to specifically describe a thermal management system in which the first heat exchanger is thermally coupled to at least one element of the powertrain, while the second heat exchanger is configured to achieve heat exchange between the refrigerant and the internal air flow.

[0021] The expression "thermally coupled" is understood to mean that the first heat exchanger or the second heat exchanger is configured to allow thermal management, in particular cooling, of said element. In this way, the thermal management system can be configured to dissipate thermal energy generated by at least one of the elements of the powertrain, for example a motor capable of moving the vehicle and operating at least partially on the basis of electrical energy, an electronic control module controlling the motor and / or an electrical energy storage device for supplying energy to the motor.

[0022] According to an aspect of the application, the secondary branch comprises at least one device for regulating the flow rate of the refrigerant and / or a secondary non-return valve.

[0023] The expression "device for regulating the flow rate" refers in this case to a component of the thermal management system configured to interrupt the circulation of the refrigerant in the secondary branch or to regulate the flow rate of the refrigerant, such as a two-way valve or a multi-way valve.

[0024] In the present description, a "non-return valve" refers to a component of the thermal management system configured to limit the circulation of the refrigerant within the branch in question, in this case the secondary branch, to a single direction of circulation.

[0025] According to an optional feature of the application, the thermal management system can comprise at least one tertiary branch extending between a second branching point and a second merging point, the second branching point being provided on the main branch between the main heat exchanger and the first heat exchanger, the second merging point being provided on the main branch between the first branching point and the main heat exchanger.

[0026] As an example, the second branching point can be provided on the first branch. According to one particular embodiment, the second branching point and the main branching point can coincide, so that the first branch, the second branch and the tertiary branch are arranged in parallel with each other and in series with the main branch of the circuit.

[0027] According to an optional feature of the application, the thermal management system can comprise a quaternary branch extending between a third branching point and a third merging point, the third branching point being provided on the main branch between the main heat exchanger and the first merging point, the third merging point being provided on the first branch between the first heat exchanger and the reservoir device, the quaternary branch comprising at least one device for regulating the flow rate of the refrigerant.

[0028] Similarly to what is set forth above with respect to the device for regulating the flow rate, the device for regulating the flow rate of fluid is configured to interrupt the circulation of refrigerant in the fourth branch or to regulate the flow rate of this refrigerant.

[0029] According to an optional feature of the application, the main branch comprises at least one main check valve arranged between the main heat exchanger and the first junction point. In particular, this check valve is configured to limit the circulation of refrigerant within the main branch as a function of the operating mode implemented.

[0030] According to an optional feature of the application, the thermal management system comprises a third branch extending between the main bifurcation point and a fourth junction point arranged on the first branch between the first heat exchanger and the accumulation device, this third branch comprising at least one third heat exchanger.

[0031] In other words, the third heat exchanger is arranged in parallel with the first heat exchanger. Thus, the accumulation device can be supplied by the first heat exchanger and / or by the third heat exchanger and / or by the main heat exchanger.

[0032] Advantageously, the third heat exchanger can be thermally coupled to at least one of the elements of the electric powertrain of the vehicle as set forth above. Advantageously, the first heat exchanger or the second heat exchanger for one portion and the third heat exchanger for another portion can be allocated to the thermal management of the same element of the electric powertrain, to optimize the thermal regulation of this element. As an example, the element of the powertrain can be the electrical energy storage device. Advantageously, the thermal management system is designed to meet a cooling demand that is greater than the cooling demand required during normal operation of the storage device and that can occur, for example, during a fast charging phase or during the thermal management of the vehicle interior simultaneous with the charging of the electrical energy storage device.

[0033] According to an optional feature of the application, the thermal management system can comprise at least one tertiary heat exchanger configured to implement a heat exchange between the refrigerant and an external air flow of the vehicle interior, this tertiary heat exchanger being arranged on the main branch between the main heat exchanger and the main bifurcation point.

[0034] In particular, this tertiary heat exchanger can be arranged upstream of the main heat exchanger in the circulation direction of the external air flow.

[0035] In particular, this tertiary heat exchanger can be arranged directly upstream of the main heat exchanger in the circulation direction of the external air flow, so that the air flow heated by the heat exchange with the tertiary heat exchanger is conveyed directly towards the main heat exchanger. Thus, the main heat exchanger and the tertiary heat exchanger can be arranged at the front end of the vehicle, or alternatively on the roof of the vehicle, in the rear wing, and generally in any zone of the vehicle that can be swept by the external air flow.

[0036] In this arrangement, the refrigerant leaving the main heat exchanger is conveyed towards the tertiary heat exchanger before passing through the main branching point. The tertiary heat exchanger then acts as a subcooling unit for the refrigerant, which means that the tertiary heat exchanger is configured to lower the temperature of the refrigerant below its condensation temperature, thereby helping to optimize the performance of the thermal management system.

[0037] According to an optional feature of the application, the thermal management system comprises at least one circulation management member configured to cause an expansion of the refrigerant and / or to interrupt the circulation of the refrigerant passing through the at least one circulation management member, and the at least one circulation management member is arranged between the first merging point and the main merging point.

[0038] In other words, the circulation management member is configured to implement a function of reducing the pressure of the refrigerant, for example to bring the refrigerant from a high pressure to a lower pressure than this high pressure, or to implement a function of hindering the circulation of the refrigerant. As an example, the circulation management member can be an electronic expansion valve equipped with a stop function.

[0039] According to a first embodiment variant of the thermal management system, the circulation management member is arranged on the main branch, the thermal management system comprising at least one member for controlling the flow rate of the refrigerant, the at least one member being arranged on the first branch and / or on the second branch between the management member and the main merging point.

[0040] In other words, in this first variant, the circulation management member is in particular arranged between the first merging point and the main branching point. Then, when the refrigerant circulates through the main branching point, that is to say, before the refrigerant is distributed to the first branch and / or to the second branch and / or to the third branch and / or to the tertiary branch, the refrigerant is subjected to a low pressure.

[0041] The "member for controlling the flow rate" refers to a component of the thermal management system configured to interrupt the circulation of the refrigerant in the branch in question or to regulate the flow rate of this refrigerant. As an example, the member for controlling the flow rate can comprise a two-way valve or a multi-way valve.

[0042] In particular, the thermal management system can comprise a plurality of members for controlling the flow rate. Advantageously, at least one of these members for controlling the flow rate can be arranged on the third branch and / or on the tertiary branch.

[0043] According to a second variant, the thermal management system can comprise a plurality of members for managing the circulation of the refrigerant, at least one circulation management member, hereafter referred to as a first circulation management member, being arranged in the first branch between the main branching point and the first heat exchanger, a second circulation management member being arranged on the second branch between the main branching point and the second heat exchanger.

[0044] In other words, in this variant, the refrigerant that passes through the main branching point is subjected to high pressure and the expansion of the refrigerant is achieved at least in the first branch and in the second branch, and not in the main branch of the circuit.

[0045] In addition, the thermal management system can comprise a third circulation management member, which is arranged in the third branch between the main branching point and the third heat exchanger.

[0046] In addition, the thermal management system can comprise at least one tertiary member for managing the circulation of the refrigerant, which is arranged on the tertiary branch, that is to say, upstream of the main heat exchanger.

[0047] According to alternative embodiments of the first and second variants of the thermal management system, the thermal management system can comprise a module for distributing the refrigerant, the distribution module having at least one housing delimiting an internal volume, the main branching point and at least one member for managing the circulation of the refrigerant being arranged in the at least one housing.

[0048] In particular, when the thermal management system is implemented according to the first variant, the module for distributing the refrigerant can house at least one of the members for controlling the circulation of the refrigerant. Advantageously, the distribution module can house all of the members for controlling the circulation of the refrigerant.

[0049] Similarly, when the thermal management system is implemented according to the second variant, the module for distributing the refrigerant can house the plurality of members for managing the circulation of the refrigerant. Advantageously, the distribution module can house all of the members for managing the circulation of the refrigerant.

[0050] Such a distribution module in particular relates to the physical grouping together, within the thermal management system, of the circulation management member(s) and / or the member(s) for controlling the circulation, thus simplifying the integration of such a distribution module into a vehicle.

[0051] According to a particular embodiment applicable to the first embodiment, the second embodiment and the different embodiment variants set out above, the thermal management system can comprise at least one internal heat exchanger configured to implement a heat exchange between a first part of the internal heat exchanger, which is included in a first portion of the thermal management system extending between the accumulation device and the compression device, and a second part of the internal heat exchanger, which is included in a second portion of the thermal management system extending between the main heat exchanger and the main branching point.

[0052] In this arrangement, the first part of the internal heat exchanger can thus be provided on the main branch, between the main junction and the compression device, so that at least the refrigerant leaving the first heat exchanger and / or the second heat exchanger is conveyed towards the first part of the internal heat exchanger. Alternatively, the first part of the internal heat exchanger can be provided on the first branch, between the accumulator device and the main junction, so that the refrigerant leaving the second heat exchanger bypasses the first part of the internal heat exchanger.

[0053] According to an optional feature of this particular embodiment, when the first part of the internal heat exchanger is provided between the accumulator device and the main junction, the thermal management system can comprise a bypass branch for the refrigerant, extending between a split point and a connection point, the split point being provided between the second heat exchanger and the main junction, the connection point being provided between the accumulator device and the first part of the internal heat exchanger.

[0054] In other words, this bypass branch is configured to convey at least part of the refrigerant leaving the second heat exchanger towards the first part of the internal heat exchanger.

[0055] According to an alternative of this particular embodiment, when the first part of the internal heat exchanger is provided between the main junction and the compression device, the thermal management system can comprise a bypass branch for the refrigerant, extending between a split point and a connection point, the split point being provided between the second heat exchanger and the main junction, the connection point being provided between the first part of the internal heat exchanger and the compression device.

[0056] In other words, this bypass branch is configured to make at least part of the refrigerant leaving the second heat exchanger bypass the first part of the internal heat exchanger and, if necessary, directly supply the compression device.

[0057] Advantageously, and independently of the positioning of the bypass branch, the circulation of refrigerant in the bypass branch can be regulated, the thermal management system comprising at least one means for regulating the flow of refrigerant, provided on the bypass branch and / or provided on the second branch, between the split point and the main junction.

[0058] As an example, the thermal management system can comprise at least one means for regulating the flow of refrigerant provided on the bypass branch (referred to as a first means for regulating the flow of refrigerant) and at least one second means for regulating the flow of refrigerant provided between the split point and the main junction.

[0059] Alternatively, the means for regulating the flow of refrigerant can comprise a multi-way valve provided at the split point.

[0060] The application also relates to a method for regulating the temperature of the refrigerant leaving the compression device configured with the thermal management system as set out above, the regulation method comprising:

[0061] - a first step of estimating the temperature of the refrigerant leaving the compression device;

[0062] - a second step of comparing the estimated temperature of the refrigerant with at least one temperature threshold;

[0063] - a third step of regulating the heat exchange implemented in the second heat exchanger and / or regulating the circulation of the refrigerant in the second branch, the third step being implemented when the estimated temperature of the refrigerant is greater than or equal to the temperature threshold.

[0064] As an example, the first step can comprise a step of directly measuring the temperature of the refrigerant or measuring the pressure of the refrigerant to derive therefrom the temperature of the refrigerant.

[0065] The expression "regulating the heat exchange" means varying a variable of the thermal management system that varies the heat exchange implemented in the second heat exchanger. For example, when the thermal management system is implemented according to the first embodiment, this variable can be the flow rate of the refrigerant circulating in the second branch and / or the flow rate of the heat transfer fluid circulating in the heat transfer fluid loop, or when the thermal management system is implemented according to the second embodiment, this variable can be the flow rate of the internal air flow.

[0066] The expression "regulating the circulation" means controlling the path of the refrigerant within the second branch, which means, for example, that all or some of the refrigerant circulates along the second branch when the thermal management system comprises an internal heat exchanger and a bypass branch.

[0067] In particular, the third step can comprise at least one sub-step of increasing the flow rate of the refrigerant circulating in the second branch.

[0068] Additionally or alternatively, the second heat exchanger can be thermally coupled to the heat transfer fluid loop, or, in the case where the second heat exchanger is configured to implement a heat exchange between the refrigerant and an internal air flow of the vehicle interior, the third step can comprise at least one sub-step of decreasing the flow rate of the heat transfer fluid or the flow rate of the internal air flow participating in the heat exchange implemented in the second heat exchanger.

[0069] Another subject of the application is a motor vehicle comprising at least one thermal management system as set out above.

[0070] Other features, details and advantages will become more clearly apparent on reading the detailed description provided below, in relation to the various exemplary embodiments illustrated in the following drawings:

[0071] Figure 1is a general schematic view of a thermal management system comprising at least one refrigerant circuit according to the present application;

[0072] Figure 2 is Figure 1 is a schematic view of a first embodiment of a thermal management system;

[0073] Figure 3 is Figure 1 is a schematic view of a second embodiment of a thermal management system;

[0074] Figure 4 is a partial schematic view of a first embodiment variant of a management system as Figures 1 to 3

[0075] Figure 5 is a partial schematic view of a second embodiment variant of a management system as Figures 1 to 3

[0076] schematically illustrates Figure 6 schematically illustrates the operation of a thermal management system as Figure 2

[0077] Figure 7 schematically illustrates the operation of a thermal management system as Figure 2

[0078] Figure 8 schematically illustrates the operation of a thermal management system as Figure 2

[0079] Figure 9 schematically illustrates the operation of a thermal management system as Figure 2

[0080] Figure 10 schematically illustrates the operation of a thermal management system as Figure 2

[0081] Figure 11 is a schematic view of a method for regulating the temperature of a refrigerant circulating in a thermal management system as Figure 1 Figure 2 Figure 3 or​​​​​​​​

[0082] Figure 12 is a schematic view of a particular exemplary embodiment of a thermal management system as Figure 1 , Figure 2 or Figure 3 illustrated;

[0083] Figure 13 is a schematic view of an alternative of a particular exemplary embodiment as Figure 12 illustrated;

[0084] Figure 14 is a schematic view of a method for regulating the temperature of a refrigerant circulating in a thermal management system as Figure 12 illustrated.

[0085] It should first be noted that the drawings explain the application in detail for implementing the application, of course, if necessary, said drawings can be used to better define the application.

[0086] Figure 1 is a general depiction of a thermal management system 1 for a vehicle, comprising at least one circuit 2 of a refrigerant FR, for example a subcritical fluid known with reference to R134A or R1234YF, which is intended in particular for the thermal management of the vehicle interior.

[0087] The terms "upstream" and "downstream" adopted in the following description refer to the direction of circulation of the fluids in question, that is to say, to the direction of circulation S1 of the refrigerant in the circuit 2 or to the direction of circulation S2 of the external air flow FA1 of the vehicle interior.

[0088] In Figures 6 to 10 , the refrigerant is denoted by arrows showing the direction of circulation S1 of the refrigerant in the pipe in question. The solid line shows a portion of the circuit 2 in which the refrigerant circulates, while the dashed line shows that there is no circulation of refrigerant. The high-pressure high-temperature refrigerant is denoted by a thick line. The low-pressure low-temperature refrigerant is denoted by a thin line.

[0089] The designations "main", "first", "second", "primary", etc. are not intended to indicate a hierarchy or an order of the terms they accompany. These designations are used to distinguish the terms they accompany and can be interchanged without narrowing the scope of the application.

[0090] As Figure 1 illustrated, the circuit 2 of the refrigerant FR is a closed circuit 2 that implements a thermodynamic cycle. The circuit 2 comprises at least one main branch 3 extending between a main junction point 31 and a main branching point 32, and on which at least one compression device 33 intended to increase the pressure of the refrigerant is provided, and a main heat exchanger 34 configured to implement a heat exchange between the refrigerant FR and an air flow FA1 of the vehicle from the outside to the inside.

[0091] In particular, the main heat exchanger 34 can be used at least as a condenser. This main heat exchanger can be arranged at the front end of the vehicle, so as to benefit from the supply of the external air flow FA1 during the running phase. It should be noted that the compression device 33 can take the form of an electric compressor, that is to say a compressor comprising a compression mechanism, an electric motor and possibly a controller.

[0092] The circuit 2 also comprises at least one first branch 4 and one second branch 5, which extend between the main diverging point 32 and the main converging point 31, in parallel with each other and in series with the main branch 3. The first branch 4 comprises a first heat exchanger 41 and an accumulator device 42 for the refrigerant, which is arranged between the first heat exchanger 41 and the main converging point 31. Thus, in the direction of circulation S1 of the refrigerant, the accumulator device 42 is arranged upstream of the main converging point 31 and thus upstream of the compression device 33. The accumulator device 42 is configured to separate the liquid phase from the gaseous phase of the refrigerant and to accumulate the liquid phase of the refrigerant, so as to deliver refrigerant that is substantially gaseous towards the compression device 33.

[0093] The second branch 5 comprises at least one second heat exchanger 51. The second branch 5 is connected to the main branch 3, so as to bypass the accumulator device 42. Thus, the accumulator device 42 can be supplied with refrigerant at least by the first heat exchanger 41 and / or the main heat exchanger 34, while the second heat exchanger 51 directly supplies the compression device 33, that is to say without passing through the accumulator device 42.

[0094] According to one exemplary embodiment, the first heat exchanger 41 and the second heat exchanger 51 can be configured to implement a heat exchange between the refrigerant FR and an external air flow FA2 of the vehicle interior. In other words, the first heat exchanger 41 and the second heat exchanger 51 can be configured to operate at least as evaporators. Optionally, one of these heat exchangers, for example the first heat exchanger 41, can be configured to produce a greater power than the other heat exchanger, in this case the second heat exchanger 51. For example, the first heat exchanger 41 can be larger in size than the second heat exchanger 51.

[0095] According to other particular exemplary embodiments of the application, at least one of the first heat exchanger 41 and the second heat exchanger 51 is configured to be thermally coupled to a heat transfer fluid loop 6 of the electric powertrain of the vehicle, comprising at least one element 61 (visible in Figure 2 or Figure 3 ), while at least the other of the first heat exchanger 41 and the second heat exchanger 51 is configured to implement a heat exchange between the refrigerant and an internal air flow FA2 of the vehicle interior.

[0096] Thus, Figure 2 and Figure 3The heat management system 1 is illustrated as Figure 1 Two separate embodiments of the heat management system 1 are illustrated, which differ from each other by the operation of their first 41 and second 51 heat exchangers. Figure 2 A first embodiment of the heat management system 1 is illustrated, in which the first heat exchanger 41 is configured to achieve heat exchange between the refrigerant FR and the internal air flow FA2 of the vehicle interior, while the second heat exchanger 51 is thermally coupled to at least one of the elements 61 of the electric powertrain of the vehicle.

[0097] By contrast, Figure 3 A second embodiment of the heat management system 1 is illustrated, in which the first heat exchanger 41 is thermally coupled to at least one of the elements 61 of the electric powertrain of the vehicle, while the second heat exchanger 51 is configured to achieve heat exchange between the refrigerant and the internal air flow FA2 of the vehicle interior.

[0098] As Figure 2 illustrated, the heat transfer fluid loop 6 is a closed loop 6 comprising at least one main pipe 600 on which at least the second heat exchanger 51, at least one element 61 of the electric powertrain and a device 62 for setting the heat transfer fluid in circulation, such as a pump, are provided. It is noted that the different fluids circulating through the second heat exchanger 51 do not mix and the heat exchange between the two fluids is achieved by conduction.

[0099] The element 61 of the powertrain to be heat managed, in particular to be cooled, can for example comprise an electric motor, a control module for said motor or an electrical energy storage device 63 configured to supply electrical energy to said motor. For the sake of clarity, throughout the following description, the element 61 of the powertrain under discussion will be the electrical energy storage device 63 and the terms "element 61 of the powertrain" and "electrical energy storage device 63" can be used interchangeably.

[0100] It is understood that this description of the heat transfer fluid loop 6 and any description given with reference to said loop 6 extends to the second embodiment of the heat management system 1 as Figure 3 illustrated, with the difference that the heat transfer fluid loop 6 then comprises the first heat exchanger 41 instead of the second heat exchanger 51. This equally applies to the exemplary embodiment in which the first 41 and second 51 heat exchangers are configured to achieve heat exchange between the refrigerant FR and the external air flow FA2 of the vehicle interior, as set out above, the entire description herein being applicable mutatis mutandis.

[0101] As Figures 1 to 3The thermal management system 1 also comprises at least one secondary branch 7 extending between a first diverging point 71 and a first converging point 72. In particular, the first diverging point 71 is provided on the main branch 3 between the compression device 33 and the main heat exchanger 34, while the first converging point 72 is provided on the main branch 3 between the main heat exchanger 34 and the main diverging point 32. In other words, the secondary branch 7 is provided within the thermal management system 1 to be able to bypass the main heat exchanger 34 depending on the operating mode implemented by the circuit 2.

[0102] The secondary branch 7 comprises a secondary heat exchanger 73 configured to implement a heat exchange between the refrigerant and the internal air flow FA2 conveyed to the vehicle interior. Thus, the secondary heat exchanger 73 is configured to operate as a condenser in the heating, ventilation and / or air conditioning installation of the vehicle. Then, the heat exchange between the refrigerant and the internal air flow directly occurs.

[0103] According to an alternative not shown, the secondary heat exchanger 73 can be configured to implement a heat exchange between the refrigerant and a heat transfer fluid circulating in an auxiliary loop. Such an auxiliary loop can comprise at least one auxiliary heat exchanger configured to implement a heat exchange between the heat transfer fluid and the internal air flow FA2. In other words, in this alternative, the secondary heat exchanger 73 contributes to implementing an indirect heat exchange between the refrigerant and the internal air flow FA2 via the heat transfer fluid circulating in the auxiliary loop.

[0104] Furthermore, the secondary branch 7 comprises at least one device 74 for regulating the refrigerant flow, configured to interrupt the circulation of the refrigerant in the secondary branch 7 or to regulate the flow rate of the refrigerant, and / or a secondary non-return valve 75 configured to limit the circulation of the refrigerant within the secondary branch 7 to one circulation direction, in particular configured, in the example illustrated, to prevent the circulation of the refrigerant within the secondary branch 7 from the first converging point 72 to the first diverging point 71.

[0105] In addition, the thermal management system 1 can comprise in the main branch 3 at least one element 35 for regulating the refrigerant flow. Such a regulating element 35 is configured to vary the refrigerant flow and / or to interrupt the circulation of the refrigerant in at least a portion of the main branch 3. The regulating element 35 is provided between the first diverging point 71 and the main heat exchanger 34 to selectively direct the refrigerant either towards the remaining portion of the main branch 3 or towards the secondary branch 7.

[0106] The thermal management system 1 according to the application can be configured to implement different operating modes related to the thermal management of the vehicle interior and / or of at least one element 61 of the electric powertrain. To this end, the thermal management system 1 according to the application can comprise at least one tertiary branch 8 and / or one quaternary branch 9.

[0107] The third branch 8 extends between a second diverging point 81, provided between the main heat exchanger 34 and the first heat exchanger 41, and a second converging point 82, provided on the main branch 3 between the first diverging point 71 and the main heat exchanger 34. According to an alternative not shown, the second diverging point 81 and the main diverging point 32 can coincide.

[0108] As such, the fourth branch 9 extends between a third diverging point 91, provided on the main branch 3 between the main heat exchanger 34 and the first converging point 72, and a third converging point 92, provided on the first branch 4 between the first heat exchanger 41 and the reservoir device 42. The fourth branch 9 comprises at least one device 93 for regulating the flow rate of the refrigerant, configured to interrupt the circulation of the refrigerant in the fourth branch 9 and / or to regulate the flow rate of the refrigerant within the same branch, as a function of the operating mode implemented by the circuit 2.

[0109] In particular, the main branch 3 of the circuit 2 can comprise at least one main non-return valve 36, provided between the main heat exchanger 34 and the first converging point 72 and configured to prevent the circulation of the refrigerant from the first converging point 72 towards the main heat exchanger 34.

[0110] Optionally, the thermal management system 1 can also comprise a third branch 10 extending between the main diverging point 32 and a fourth converging point 101, provided on the first branch 4 between the first heat exchanger 41 and the reservoir device 42. The third branch 10 comprises at least one third heat exchanger 102 thermally coupled to at least one of the elements of the electric powertrain of the vehicle.

[0111] According to an optional feature and depending on the implemented embodiment, the first heat exchanger 41 or the second heat exchanger 51 for one portion and the third heat exchanger 102 for the other portion can be configured to jointly thermally manage the same element 61 of the electric powertrain, for example the electric energy storage device 63. In particular, this arrangement makes it possible to meet cooling needs that are greater than those required during normal operation of the storage device 63 and which can occur, for example, during a fast charging phase or during thermal management of the vehicle interior simultaneous with the charging of the electric energy storage device 63.

[0112] According to an alternative not shown, the first heat exchanger 41 or the second heat exchanger 51 can be configured to be thermally coupled to a first element of the powertrain, while the third heat exchanger 102 can be configured to be thermally coupled to a second element of the powertrain separate from the first element.

[0113] The third heat exchanger 102 is thus arranged in parallel with the first heat exchanger 41 and in parallel with the second heat exchanger 51 and is provided in the circuit 2 so that the accumulation device 42 can be supplied by the first heat exchanger 41 and / or by the third heat exchanger 102 and / or by the main heat exchanger.

[0114] Optionally, the thermal management system 1 according to the application can comprise at least one tertiary heat exchanger 37 configured to implement a heat exchange between the refrigerant FR and an external air flow FA1 of the vehicle interior. The tertiary heat exchanger 37 is provided on the main branch 3 between the main heat exchanger 34 and the main branching point 32 to be able to supercool the refrigerant leaving the main heat exchanger 34 depending on the operating mode implemented.

[0115] Advantageously, the tertiary heat exchanger 37 can be provided upstream of the main heat exchanger 34 along the circulation direction S2 of the external air flow FA1. In other words, the tertiary heat exchanger 37 is arranged to be passed by the external air flow FA1 before it passes through the main heat exchanger 34.

[0116] The thermal management system 1 also comprises at least one member 38 for managing the circulation of the refrigerant, provided between the first merging point 72 and the main merging point 31 and configured to cause an expansion and / or an interruption of the circulation of the refrigerant passing through the member. Figures 1 to 3 Various alternative examples of this management member 38 and its positioning are illustrated in a diamond way and will be referred to below with reference to Figure 4 and Figure 5 Different variants of this management member 38 incorporation are described in detail. As an example, the circulation management member 38 can be an electronic expansion valve equipped with a stop function.

[0117] This circulation management member 38 can be switched to different positions. When the circulation management member is fully open, it does not change the state of the refrigerant and is qualified as not acting. When the circulation management member is partially open, the management member 38 causes an expansion of the refrigerant. Finally, when the circulation management member is closed, the management member 38 implements its stop function and prevents the passage of the refrigerant.

[0118] The circulation management member 38 can be provided within the thermal management system 1 according to different variants, Figure 4 and Figure 5 Particular example embodiments of the thermal management system 1 implemented according to these different variants are illustrated in Figure 1 , Figure 2 , Figure 3 or Figure 12Each of the illustrated embodiments and alternatives of the management system is schematically indicated in the remaining figures by the inset 1000, in combination with one or another variant.

[0119] According to Figure 4 In the first embodiment variant of the thermal management system 1 illustrated in the middle, the circulation management member 38 can be provided on the main branch 3, that is to say, between the first merging point 72 and the main diverging point 32. In this thermal management system 1, the refrigerant is subjected to low pressure when it circulates through the main diverging point 32, that is to say, before it is distributed to the first branch 4 and / or to the second branch 5 and / or to the third branch 10 and / or to the tertiary branch 8.

[0120] In this variant, the thermal management system 1 comprises at least one member 11 for controlling the flow rate of the refrigerant, provided on the first branch 4 and / or on the second branch 5, in particular between the member 38 for managing the circulation of the refrigerant and the main merging point 31, to selectively control the path of the refrigerant fluid in the first branch 4 and / or in the second branch 5.

[0121] The member 11 for controlling the flow rate is a component of the thermal management system 1 configured to interrupt the circulation of the refrigerant in the branch in question or to regulate the flow rate of this refrigerant. By way of example, the member 11 for controlling the flow rate can comprise a two-way valve or a multi-way valve.

[0122] In this case, the first variant of the thermal management system 1 comprises a plurality of members 11 for controlling the flow rate. The member 11 for controlling the flow rate of the refrigerant, hereinafter referred to as first member 111 for controlling the flow rate, is provided on the first branch 4. As illustrated, this first control member 111 can be provided upstream of the first heat exchanger 41, that is to say, between the main diverging point 32 and the first heat exchanger 41, along the circulation direction S1 of the refrigerant, or, according to an alternative not illustrated, downstream of this same first heat exchanger 41, between the first heat exchanger 41 and the main merging point 31.

[0123] Similarly, the thermal management system 1 can comprise a second member 112 for controlling the flow rate of the refrigerant, provided on the second branch 5, upstream or downstream of the second heat exchanger 51, and / or a third member 113 for controlling the flow rate of the refrigerant, provided on the third branch 10, upstream or downstream of the third heat exchanger 102, and / or a tertiary member 114 for controlling the flow rate of the refrigerant, provided on the tertiary branch 8.

[0124] It should be understood that this embodiment variant is by no means limiting and that, according to alternative solutions not shown, the plurality of control members 11 can comprise at least one multi-way valve configured to simultaneously control the circulation of the refrigerant in the different branches of the circuit 2. As an example, such a multi-way valve can be provided at the main branching point 32 to control the circulation of the refrigerant towards the first branch 4 and / or towards the second branch 5 and / or towards the third branch 10.

[0125] It should be understood that the member(s) 11 for controlling the flow of heat transfer fluid thus make it possible to selectively direct the refrigerant subjected to low pressure towards the different branches branching off from the main branching point 32, for example, thereby allowing and preventing the circulation of this refrigerant in one or other of the branches 4, 5, 8 and / or 10.

[0126] According to Figure 5 According to a second variant illustrated in Fig. 2, the thermal management system 1 can comprise a plurality of members 38 for managing the circulation of the refrigerant, i.e. a plurality of components configured to cause the expansion of the refrigerant and / or interrupt the circulation of the refrigerant therethrough.

[0127] In the example shown, a circulation management member 38, hereinafter referred to as first circulation management member 381, is provided in the first branch 4, between the main branching point 32 and the first heat exchanger 41. In particular, as illustrated, the thermal management system 1 can comprise a first circulation management member 381 provided on the first branch 4 between the second branching point 81 of the tertiary branch 8 and the first heat exchanger 41, and a tertiary circulation management member 384 provided on the tertiary branch 8 between the second branching point 81 and the main merging point 31 Figures 1 to 3 As can be seen in Fig. 2, the expansion and / or control of the circulation of the refrigerant conveyed towards the first branch 4 and / or towards the tertiary branch 8 can be implemented by the same circulation management member 38, for example the first management member 381 provided on the first branch 4 between the main branching point 32 and the second branching point 81, according to alternative solutions not shown.

[0128] The thermal management system 1 can also comprise at least one second circulation management member 382, which in this variant is provided on the second branch 5 between the main branching point 32 and the second heat exchanger 51.

[0129] In this variant, the thermal management system 1 can also comprise at least one third circulation management member 383 on the tertiary branch 10, provided between the main branching point 32 and the second heat exchanger 51.

[0130] In other words, in this second variant, the refrigerant that passes through the main branching point 32 is subjected to high pressure and high temperature, and the expansion of the refrigerant is implemented downstream of the main branching point 32, at least in the first branch 4 and in the second branch 5, and not in the main branch 3 of the circuit 2.

[0131] According to one particular exemplary embodiment, the thermal management system 1 implemented according to the first variant or according to the second variant, respectively illustrated in Figure 4 and Figure 5 may comprise a refrigerant distribution module 12. The distribution module 12 has at least one housing 121 delimiting an internal volume 122 in which the main branching point 32 and at least one member 38 for managing the circulation of the refrigerant are arranged. In Figure 4 and Figure 5 , this housing 121 is schematically illustrated by way of a thick dashed line, to indicate the optional nature of this feature inherent to the present particular exemplary embodiment.

[0132] Thus, this distribution module 12 comprises at least one inlet 123 for the refrigerant to enter the distribution module 12, allowing passage through at least a portion of the main branch 3, and a plurality of outlets for the refrigerant to exit the distribution module 12, the number of outlets employed in the operating mode of the thermal management system 1 being equal to the number of heat exchangers 41, 51, 101 and / or 34 supplied with refrigerant.

[0133] Thus, the distribution module 12 illustrated comprises, in a non-limiting manner, a first outlet 124 allowing passage through the first branch 4, and / or a second outlet 125 allowing passage through the second branch 5, and / or a third outlet 126 allowing passage through the third branch 10, and / or a fourth outlet 127 allowing passage through the tertiary branch 8.

[0134] Advantageously, in each of the variants illustrated, the refrigerant circulating through the first outlet 124 and / or the second outlet 125 and / or the third outlet 126 and / or the fourth outlet 127 is subjected to low pressure. Thus, the distribution module 12 is not constrained in terms of sealing and / or strength, and the housing 121 of said distribution module 12 can be made of plastic material.

[0135] Furthermore, according to the example for the first embodiment variant illustrated in Figure 4 , at least one of the members 11 for controlling the circulation of the refrigerant can be arranged in the internal volume 122 delimited by the housing 121. Advantageously, the distribution module 12 can house all of the members 11 for controlling the circulation of the refrigerant in the internal volume 122.

[0136] Similarly, as illustrated in Figure 5As shown, for the second embodiment variant, the distribution module 12 can house, in the internal volume 122 of the casing 121, at least part of the plurality of components 38 for managing the circulation of refrigerant. Advantageously, the distribution module 12 can house, within the casing 121, all of the components 38 for managing the circulation of refrigerant of the thermal management system 1. By way of example, in the example shown, the distribution module 12 houses the first circulation management component 381, the second circulation management component 382, the third circulation management component 383 and the tertiary circulation management component 384.

[0137] In particular, such a distribution module 12 involves physically grouping together, within the thermal management system 1, the circulation management component(s) 38 and / or the component(s) 11 for controlling the flow of refrigerant, thus simplifying the integration of these components into the vehicle.

[0138] Figures 6 to 10 Different operating modes of the thermal management system 1 are illustrated. For the sake of clarity, these different operating modes will be described with respect to the thermal management system 1 implemented according to the first embodiment as described above with reference to Figure 2 and according to the first embodiment variant as shown above with reference to Figure 4 However, it should be understood that all the following description should be extended to different combinations of the embodiments and embodiment variants as set out above.

[0139] Figure 6 A first example of operation of the thermal management system 1 according to the application is illustrated, in which the circuit 2 is configured to operate in air conditioning mode, which means that the circuit is configured to cool the internal air flow FA2 passing through the first heat exchanger 41 before being delivered to the vehicle interior. In particular, such an operating mode can be implemented during the driving phase of the vehicle.

[0140] In the circuit 2, the circulation of refrigerant FR is limited to the main branch 3 and the first branch 4. The refrigerant does not pass through the second branch 5, the third branch 10, the secondary branch 7, the tertiary branch 8 and the quaternary branch 9. In the example shown, the circulation of refrigerant in said branches 5, 10, 7, 8 and 9 is hindered respectively by the closing of the second control component 112, the third control component 113, the means for regulating the flow 74, the tertiary control component 114 and the device for regulating the flow of refrigerant 93.

[0141] The refrigerant leaves the compression device 33 at high pressure, high temperature and substantially gaseous, and proceeds towards the main heat exchanger 34 operating as a condenser. The refrigerant, exhibiting a temperature higher than the temperature of the external air flow FA1, passes through this first main heat exchanger 34 and releases the thermal energy of the refrigerant to the external air flow FA1. The refrigerant thus cooled leaves the main heat exchanger 34 mainly in liquid state and enters the tertiary heat exchanger 37.

[0142] The tertiary heat exchanger 37 operates as a subcooler, meaning that it cools the refrigerant to a temperature at least lower than its condensation temperature by exchanging heat with the colder external air flow FA1. The refrigerant thus leaves the tertiary heat exchanger 37 at a lower temperature than the temperature observed at the outlet of the main heat exchanger 34.

[0143] As shown, advantageously, the tertiary heat exchanger 37 is arranged upstream of the main heat exchanger 34 along the circulation direction S2 of the external air flow FA1. In this way, the external air flow FA1 involved in the heat exchange in the tertiary heat exchanger 37 exhibits a lower temperature than the temperature of the external air flow FA1 involved in the heat exchange in the main heat exchanger 34, which has already been heated. The temperature drop between the refrigerant and the external air flow FA1 dedicated to the main heat exchanger 34 is thus reduced compared to the temperature drop observed in the tertiary heat exchanger 37. This arrangement helps to increase the capacity of the thermal management system 1, in particular by allowing a reduction of the rotation speed of the compression device 33 for providing the same cooling power.

[0144] The refrigerant thus subcooled passes through the main non-return valve 36 up to the first junction point 72 and then circulates towards the main branching point 32. As set out above, in the example shown, the thermal management system 1 combines the first embodiment and the first embodiment variant. The refrigerant management member 38 configured to expand and / or interrupt the circulation of the refrigerant is thus arranged on the main branch 3, between the first junction point 72 and the main branching point 32.

[0145] The refrigerant thus undergoes a reduction of its pressure in the refrigerant management member 38 and passes through the main branching point 32 at low pressure. The refrigerant is conveyed into the first branch 4 since the first control member 111 allows the passage of the refrigerant by being at least partially open while the second control member 112, the third control member 113 and the tertiary control member 114 are closed.

[0146] The refrigerant passes through the first heat exchanger 41 at low pressure and low temperature. In doing so, the refrigerant captures thermal energy from the hotter internal air stream FA2, which is thus cooled before being delivered to the vehicle interior. The refrigerant thus leaves the first heat exchanger 41 in two-phase form and circulates along the first branch 4 until the reservoir device 42. Within the reservoir device 42, the liquid and gaseous phases of the refrigerant are separated, and the refrigerant that is substantially gaseous passes through the main junction 31 before being delivered back to the main branch 3 and the compression device 33.

[0147] Figure 7 A second operating mode of the thermal management system 1 is illustrated, in which the refrigerant circuit 2 simultaneously cools the vehicle interior and thermally manages, in particular cools, at least one element 61 of the powertrain. In this case, the element 61 of the powertrain in question is the electrical energy storage device 63. By way of example, this operating mode allows the simultaneous cooling of the interior of the vehicle and of the electrical energy storage device 63 during the driving phase, that is to say during normal operation of the vehicle.

[0148] In this operating mode, the path of the refrigerant in the circuit 2 is identical to that described above with reference to the first operating mode, with the exception that at least one of the heat exchangers thermally coupled to the electrical energy storage device 63 is supplied with refrigerant. In this case, the thermal management system 1 is implemented according to the first embodiment, and the second heat exchanger 51 is supplied with refrigerant. Figure 6

[0149] Thus, when the refrigerant passes through the main junction 32 at low pressure and low temperature, a first portion of the refrigerant is delivered into the first branch 4, to pass through the first heat exchanger 41 and then through the reservoir device 42, while a second portion of the refrigerant is delivered into the second branch 5, the at least partial opening of the second member 112 for controlling the flow of refrigerant allowing the passage of the refrigerant.

[0150] This second portion of refrigerant exchanges heat with the heat transfer fluid loop 6 within the second heat exchanger 51, to cool the heat transfer fluid. In the heat transfer fluid loop 6, the heat transfer fluid is set in circulation by the means 62 for setting circulation, captures thermal energy from the electrical energy storage device 63, and then releases the thermal energy to the refrigerant within the second heat exchanger 51. Thereby, the cooled heat transfer fluid is delivered towards the electrical energy storage device 63, while the thermal conditions imposed by the element 61 of the electric powertrain allow the refrigerant leaving the second heat exchanger 51 to be superheated, which is then in gaseous form. This superheating corresponds to an increase in the temperature of the refrigerant above its saturation temperature at the same pressure. In this superheated state, the refrigerant reaches the main junction 31 and is then delivered directly back to the compression device 33, without first passing through the bottle or reservoir device 42.

[0151] ​At the main junction 31, the second portion of superheated refrigerant coming from the second branch 5 is mixed with the first portion of refrigerant coming from the first branch 4 and from the accumulator device 42 in a state of near-saturation vapor (for example, vapor content close to 0.95) before reaching the compression device 33 in a state of moderate superheat, this superheat helping to increase the coefficient of performance of the circuit 2.

[0152] Figure 8 A third operating mode of the thermal management system 1 is illustrated, in which the circuit 2 simultaneously cools the vehicle interior (i.e., in air conditioning mode) and the thermal management electric energy storage device 63. This third operating mode is particularly suitable for the operation of the electric energy storage device 63, in which operation the electric energy storage device generates more heat than can be observed during normal operation of the vehicle, for example during fast charging of the electric energy storage device 63. This operating mode is therefore substantially identical to the second operating mode and therefore reference can be made to the description given in relation to the second operating mode, with the necessary modifications. However, this operating mode differs from the aforementioned operating modes in that the third branch 10 is likewise supplied with refrigerant. Figure 7

[0153] As set out above, when the thermal management system 1 is implemented according to the first embodiment, the cooling of the vehicle interior is achieved by the first heat exchanger 41. In this case, the cooling of the electric energy storage device 63 is performed jointly by the second heat exchanger 51 and the third heat exchanger 102, within which heat energy is captured from the heat transfer fluid circulating in the loop 6 to meet the increase in the demand for cooling of the electric energy storage device 63.

[0154] In this thermal management system 1, the heat transfer fluid loop 6 can for example comprise at least a main pipe 600 on which the second heat exchanger 51, the means 62 for setting to circulate and the element 61 of the powertrain to be thermally managed, in this case the electric energy storage device 63, are arranged. Furthermore, the loop 6 can have at least one first pipe 610 comprising the third heat exchanger 102 and connected to the main pipe 600 of the heat transfer fluid loop 6. In a non-limiting manner, this first pipe 610 can be arranged so that the second heat exchanger 51 and the third heat exchanger 102 are arranged in parallel with each other as illustrated in the figures.

[0155] Alternatively, the second heat exchanger 51 and the third heat exchanger 102 can be arranged in series with each other on the same pipe of the heat transfer fluid loop 6.

[0156] ​Thus, at the main branching point 32 of the refrigerant circuit 2, a first portion of refrigerant and a second portion of refrigerant are conveyed respectively towards the first branch 4 and towards the second branch 5 (as set out above), while a third portion of refrigerant is conveyed towards the third branch 10, the at least partial opening of the third member 113 of the control circuit allowing the passage of refrigerant.

[0157] Then, the first portion of refrigerant and the third portion of refrigerant are conveyed towards the accumulator device 42, while the second portion of superheated refrigerant bypasses the accumulator device. Thus, the main junction point 31 receives a mixture of superheated refrigerant and non-superheated refrigerant, which is then conveyed back to the compression device 33.

[0158] Thus, in the second operating mode and in the third operating mode, the second heat exchanger 51 and / or the third heat exchanger 102 are used according to the needs for cooling the elements 61 of the electric powertrain. In the driving phase, the needs for cooling are low, the second heat exchanger 51 or the first heat exchanger 41 can be used in the case of the second embodiment. In the fast charging phase, the second heat exchanger 51 or the first heat exchanger 41 can be used in common with the third heat exchanger 102 to cool the electric energy storage device 63. In each of these operating modes, the second heat exchanger 51 at least partially superheats the refrigerant at the inlet of the compression device 33, thus contributing to improve the operating cycle.

[0159] Figure 9 A fourth operating mode of the thermal management system 1 is illustrated, in which the refrigerant circuit 2 operates in a heating mode for heating the vehicle interior. As set out above, the refrigerant is subjected to high pressure and high temperature in the compression device 33. This refrigerant circulates along the main branch 3 until the first branching point 71, at which, due to the combination of the closing of the element 35 for regulating the flow of refrigerant contained on the main branch 3 and the opening of the regulating device 74 contained in the secondary branch 7, the refrigerant is conveyed to the secondary branch 7.

[0160] Then, the high pressure high temperature refrigerant passes through the secondary heat exchanger 73, which acts as a condenser, in which the high pressure high temperature refrigerant releases thermal energy to the cooler internal air flow FA2 passing through said secondary heat exchanger 73. In doing so, the internal air flow FA2 thus heated is conveyed towards the vehicle interior to heat the vehicle interior, while the at least partially condensed refrigerant is conveyed towards the first junction point 72.

[0161] In the example illustrated, the thermal management system 1 implements a heating mode as referred to with reference to Figure 4The first variant thus described, the management member 38 of the circulation of refrigerant is provided on the main branch 3. The management member 38 thus expands the refrigerant which, before passing again through the main bifurcation point 32 and thus before being distributed at least towards the first branch 4 and / or the second branch 5 and / or the third branch 10 and / or the fourth branch 8, passes from a high pressure and high temperature to a low pressure and low temperature.

[0162] In the fourth operating mode, the refrigerant is only partially supplied to the first branch 4 without being supplied to the second branch 5 or to the third branch 10, the circulation of the refrigerant being hindered by the closing of the first control member 111, of the second control member 112 and of the third control member 113, respectively.

[0163] The fourth control member 114 is at least partially open so that the refrigerant circulates partially along the first branch 4 between the main bifurcation point 32 and the second bifurcation point 81, then along the fourth branch 8 until the second merging point 82 before being transmitted back to the main branch 3.

[0164] The refrigerant then enters the main heat exchanger 34 which operates as an evaporator and the refrigerant captures the thermal energy output by the flow of hotter outside air FA1. Advantageously, it should be noted that the direction of circulation S1 of the refrigerant within the main heat exchanger 34 is reversed compared to the direction of circulation observed in the three first operating modes.

[0165] The refrigerant leaves the main heat exchanger 34 in a substantially gaseous state and passes through the third bifurcation point 91. Since the device 93 for regulating the flow of refrigerant is at least partially open and the main non-return valve 36 is closed, the refrigerant circulates in the fourth branch 9 until the third merging point 92, then reaches the first branch 4 to be transmitted back to the reservoir device 42 and then to the compression device 33.

[0166] In this operating mode, the refrigerant thus bypasses the first heat exchanger 41, the second heat exchanger 51 and the third heat exchanger 102.

[0167] Figure 10 A fifth operating mode of the thermal management system 1 is illustrated, for example implemented during a driving phase, in which the circuit 2 is used simultaneously in a heating mode for heating the vehicle interior and in a cooling mode for cooling the elements 61 of the electric powertrain.

[0168] This operating mode is substantially identical to the fourth operating mode, therefore reference is made to Figure 9 The description given of the thermal management system 1 is transposable and applies, with the necessary modifications, to the present operating mode, apart from the differences mentioned below.

[0169] Therefore, in this case, the heating of the vehicle interior is performed by the secondary heat exchanger 73. In addition and similarly to what is set forth for the second embodiment, where the circuit 2 cools both the vehicle interior and the electrical energy storage device 63, the cooling of the electrical energy storage device 63 is performed by the second heat exchanger 51 or by the first heat exchanger 41, respectively, depending on whether the thermal management system 1 is implemented according to the first embodiment or according to the second embodiment.

[0170] In this case, the second means 112 for controlling the circulation of the refrigerant is open so that, when the refrigerant passes through the main bifurcation point 32 at low pressure and low temperature, a first portion of the refrigerant is conveyed towards the tertiary branch 8 and the main heat exchanger 34, while a second portion of the refrigerant is conveyed into the second branch 5 to feed the second heat exchanger 51.

[0171] In the second heat exchanger 51, the second portion of the refrigerant captures thermal energy from the electrical energy storage device 63 via the heat transfer fluid circulating in the loop 6. As set forth above, the refrigerant leaves the second heat exchanger 51 in a superheated gaseous state, this superheating raising the temperature of the second portion of the refrigerant above its saturation temperature at the same pressure. At the main junction point 31, the superheated second portion of the refrigerant and the first portion of the refrigerant coming from the main heat exchanger 34 are mixed in a moderately superheated state before reaching the compression device 33, this superheating helping to increase the coefficient of performance of the circuit 2.

[0172] When one of the heat exchangers (in this case the second heat exchanger 51) is used as a superheater (for example, as set forth in the second operating mode, third operating mode or fifth operating mode described respectively with reference to Figure 7 , Figure 8 or Figure 10 ), the temperature of the refrigerant can rise to a value liable to reduce the performance of the thermal management system 1 and it can be necessary to reduce this temperature.

[0173] In order to maintain optimal performance of the thermal management system 1 according to the application, as Figure 11 indicated, the thermal management system can be configured to implement a method for regulating the temperature of the refrigerant leaving the compression device 33. It should be understood that this method can be applied to any one of the combinations of embodiments, variants and alternatives set forth above.

[0174] In particular, this regulation method comprises at least:

[0175] - a first step: estimating the temperature of the refrigerant leaving the compression device 33;

[0176] - a second step: comparing the estimated temperature of the refrigerant FR with at least one temperature threshold;

[0177] - a third step is implemented when the estimated temperature of the refrigerant FR is greater than or equal to the temperature threshold: adjusting the heat exchange implemented in the second heat exchanger 51 and / or adjusting the circulation of the refrigerant in the second branch 5.

[0178] As an example, the step of estimating the temperature can be performed by measuring the temperature and / or the pressure of the refrigerant circulating in the circuit 2. In particular, such a measurement can be performed by means of the temperature and / or pressure sensor 39. Advantageously, such a measurement can be performed downstream of the compression device 33, for example on the main branch 3 between the compression device 33 and the first branching point 71, along the circulation direction SI of the refrigerant.

[0179] The measurement performed is transmitted to the control unit 13 of the thermal management system 1, which compares it at least with the temperature threshold. As an example, the temperature threshold of the refrigerant can be approximately 115°C. In the thermal management system 1 shown, such a data transmission is schematically depicted by the thin dotted line 2000.

[0180] The control unit 13 can then implement the third step of the adjustment method, if necessary. In the example shown, the third step is implemented when the estimated temperature of the refrigerant FR is greater than or equal to the temperature threshold. Figure 11 In the example shown, this third step comprises adjusting the heat exchange implemented in the second heat exchanger 51, i.e. the heat exchange implemented in the heat exchanger operating as a superheater and bypassing the reservoir device 42.

[0181] In particular, the adjustment of the heat exchange implemented in the second heat exchanger 51 seeks to increase the proportion of liquid phase in the refrigerant leaving the second heat exchanger 51, for example in order to obtain a vapour content of approximately 0.80, so that when the portion of refrigerant coming from the reservoir device 42 and the second heat exchanger 51 mixes at the main merging point 31, the temperature of this mixture decreases to a value suitable for optimal operation of the thermal management system 1, thus reducing the temperature of the refrigerant measured downstream of the compression device 33. Such an adjustment is controlled by the control unit 13 and is schematically depicted by the thin dotted line 3000.

[0182] In particular, the third step of the adjustment method can comprise a sub-step of increasing the flow rate of the refrigerant circulating in the second branch 5. To this end, when the thermal management system 1 is implemented according to the first embodiment variant, the control unit 13 can increase the flow rate of the refrigerant, for example via the second means for controlling the flow rate of the refrigerant 112, or when the thermal management system 1 is implemented according to the second embodiment variant, the control unit can increase the flow rate of the refrigerant, for example via the second circulation management means 382 visible in Figure 4. Figure 5 In particular, the third step of the adjustment method can comprise a sub-step of increasing the flow rate of the refrigerant circulating in the second branch 5. To this end, when the thermal management system 1 is implemented according to the first embodiment variant, the control unit 13 can increase the flow rate of the refrigerant, for example via the second means for controlling the flow rate of the refrigerant 112, or when the thermal management system 1 is implemented according to the second embodiment variant, the control unit can increase the flow rate of the refrigerant, for example via the second circulation management means 382 visible in Figure 4.

[0183] The third step of the adjustment method can comprise a sub-step of reducing the flow rate of the heat transfer fluid participating in the heat exchange implemented in the second heat exchanger 51 or the flow rate of the internal air flow FA2.

[0184] In other words, when the thermal management system 1 is implemented according to the first embodiment and the second heat exchanger is configured to be thermally coupled to the heat transfer fluid circuit 6 comprising the element 61 of the powertrain, the third step of regulation of the method can be implemented by reducing the flow rate of the heat transfer fluid circulating in the circuit 6, for example via the means 62 for setting the circulation (as Figure 2 illustrated).

[0185] Similarly, when the thermal management system 1 is implemented according to the second embodiment and the second heat exchanger 51 is configured to implement heat exchange between the refrigerant and the internal air flow FA2, the third step of the method for regulating the temperature of the refrigerant can be implemented by reducing the flow rate of this internal air flow FA2 through the second heat exchanger 51, as can be seen in Figure 3 .

[0186] Figure 12 The general depiction of a particular exemplary embodiment of the thermal management system 1 is illustrated, such an alternative being applicable to the different examples and embodiments as described above with reference to Figures 1 to 3 , independently of the embodiment variants set forth in Figure 4 and Figure 5 .

[0187] In the example illustrated, the thermal management system 1 comprises at least one internal heat exchanger 14 configured to implement heat exchange between a first part 141 and a second part 142 of the internal heat exchanger 14.

[0188] In particular, the first part 141 of the internal heat exchanger 14 is provided in a first portion 301 of the thermal management system 1 extending between the reservoir device 42 and the compression device 33, and in which the refrigerant is subjected to low pressure and low temperature. In other words, the first part 141 of the heat exchanger is provided downstream of the reservoir device 42, in the circulation direction S1 of the refrigerant. The second part 142 of the internal heat exchanger 14 is provided in a second portion 302 of the thermal management system 1 in which the refrigerant is subjected to high pressure and high temperature, the second portion extending between the main heat exchanger 34 and the main branching point 32, that is to say, the second portion extends upstream of the circulation management member 38 configured to expand and / or regulate the flow rate of the refrigerant.

[0189] In particular, as illustrated in Figure 12 , the first part 141 of the internal heat exchanger 14 can be provided on the first branch 4, between the reservoir device 42 and the main merging point 31. In this way, when the thermal management system is according to the first embodiment as described above with reference to Figure 7 , Figure 8 or Figure 10When one of the illustrated operating modes is operating, the refrigerant leaving the second heat exchanger 51 bypasses the first part 141 of the internal heat exchanger 14, while the refrigerant leaving the first heat exchanger 41 and / or the third heat exchanger 102 and / or the main heat exchanger 34 is conveyed towards the first part 141 of the internal heat exchanger 14.

[0190] Alternatively, the first part 141 of the internal heat exchanger 14 can be interposed between the main junction point 31 and the compression device 33, this alternative being represented by the first part 141’ of the internal heat exchanger 14, as shown in the figure. In this alternative, the refrigerant leaving the first heat exchanger 41 and / or the second heat exchanger 51 and / or the third heat exchanger 102 and / or the main heat exchanger 34 is conveyed towards the first part 141 of the internal heat exchanger 14. Figure 13

[0191] This internal heat exchanger 14 makes it possible to recover thermal energy from one part of the refrigerant circuit 2, in this case the second high-pressure part 302, to exchange thermal energy with another part of this same circuit 2, in this case the first low-pressure part 301, to reduce the power consumed by the compression device 33 and to improve the performance of the refrigerant circuit 2 overall, in particular when the thermal management system 1 is operating according to any one of the first operating mode, the second operating mode or the third operating mode as described above with reference to Figure 6 , Figure 7 or Figure 8 .

[0192] Since the internal heat exchanger 14 is arranged between two parts 301, 302 of the circuit 2 presenting a temperature difference between each other, it should be understood that this thus allows heat exchange between these two parts 141, 141’, 142 and therefore between the two parts 301, 302 of the refrigerant circuit 2 on which these parts 141, 141’, 142 of the internal heat exchanger 14 are arranged. In the example shown, advantageously, the internal heat exchanger 14 makes it possible to heat the refrigerant upstream of the compression device 33 so that this refrigerant is present only in gaseous form on arrival at the inlet of the compression device 33, and to cool the refrigerant upstream of the means 38 for managing the circulation of the refrigerant, regardless of the variant implemented, so that this means 38 causes a drop in pressure more easily.

[0193] When the thermal management system 1 comprises such a heat exchanger and the second heat exchanger 51 is able to operate as a superheater, for example when the circuit 2 is operating according to reference Figure 7 , Figure 8 or Figure 10 ​When operating in any one of the second, third or fifth operating modes described, it can be necessary to regulate the circulation of the refrigerant as a function of its temperature. In particular, when it is necessary to increase the superheat of the refrigerant, it can be necessary to pass the refrigerant leaving the second heat exchanger 51 through the first portion 141, 141’ of the internal heat exchanger 14, in order to capture the thermal energy of the refrigerant circulating in the second portion 142 of the internal heat exchanger 14. Conversely, when the temperature of the refrigerant rises to values that can reduce the performance of the thermal management system 1, the refrigerant leaving the second heat exchanger 51 must bypass the first portion 141, 141’ of the internal heat exchanger 14.

[0194] Therefore, the thermal management system 1 can be configured to implement the method for regulating the temperature as set out above, with reference to Figure 11 The description of the method for regulating the temperature and of the components of the thermal management system 1 described can be transposed to the alternative embodiments. In particular, the thermal management system 1 comprises at least a temperature and / or pressure sensor 39 and a control unit 13.

[0195] Furthermore, as Figure 12 indicated, when the first portion 141 of the internal heat exchanger 14 is arranged between the reservoir device 42 and the main junction point 31, the thermal management system 1 can comprise at least one bypass branch 15 configured to convey at least a portion of the refrigerant leaving the second heat exchanger 51 towards the first portion 141 of the internal heat exchanger 14.

[0196] Said bypass branch 15 for the refrigerant extends between a split point 151 and a connection point 152. The split point 151 is arranged on the second branch 5 between the second heat exchanger 15 and the main junction point 31, while the connection point 152 is arranged on the first main branch 4 between the reservoir device 42 and the first portion 142 of the internal heat exchanger 14.

[0197] When the thermal management system is operating, the refrigerant leaving the second heat exchanger 51 can then be conveyed towards the split branch 15 and / or continue to circulate on the second branch 5 towards the main junction point 31.

[0198] Alternatively, when the first portion 141’ of the internal heat exchanger 14 is arranged between the main junction point 31 and the compression device 33, according to Figure 13In the alternative shown, the bypass branch 15 for the refrigerant can extend between the branch point 151 (in this case, the branch point is located between the second heat exchanger 51 and the main junction point 31) and the connection point 152 (in this case, the connection point is located in the main branch 3, between the first component 141' of the internal heat exchanger 14 and the compressor 33) to bypass the first component 141' of the internal heat exchanger 14, thereby facilitating the regulation of the refrigerant temperature when necessary.

[0199] Optionally, the circulation of refrigerant leaving the second heat exchanger 51 can be adjusted. For example... Figure 12 and Figure 13 As shown, the thermal management system 1 may therefore include at least one component 153, 154 disposed on the bypass branch 15 and / or between the main junction 31 on the branch point 151 and the second branch 5 for regulating the refrigerant flow.

[0200] For example, such as Figure 12 As shown, the thermal management system 1 may include a component (referred to as a first regulating component 153) disposed on a bypass branch 15 for regulating refrigerant flow, and at least one second component 154 disposed between the bypass point 151 and the main junction point 31 for regulating refrigerant flow. These regulating components 153, 154 are configured to selectively direct refrigerant circulating in the second branch 5 toward the bypass branch 15, then toward the first component 141 of the internal heat exchanger 14, and / or toward the main branch 3. Advantageously, such regulating components 153, 154 may be configured to regulate the refrigerant flow. According to an alternative not shown, the thermal management system 1 may include a single component, such as a multi-way valve, disposed at the branch point 151 for regulating refrigerant flow.

[0201] Similarly, according to an alternative not shown, the thermal management system 1 may not have one or more regulating members 153, 154 as described above. The refrigerant leaving the second heat exchanger 51 then circulates simultaneously in the bypass branch 15 and the second branch 5 towards the main junction 31. In this alternative, the bypass branch may include a pipe with a diameter smaller than that of the pipe used for the second branch 5 and / or the main branch 3 to regulate the distribution of the refrigerant.

[0202] Therefore, when the thermal management system 1 includes the above reference Figure 12 When the internal heat exchanger 14 is arranged as described, the third step of the method for regulating the temperature of the refrigerant can be performed by regulating the heat exchange occurring in the second heat exchanger 51 (as referenced above). Figure 11by adjusting the circulation of the refrigerant in the second branch 5, that is, if necessary, by controlling the path of the refrigerant circulating in the second branch 5, i.e. by controlling the refrigerant circulating in the second branch towards the main branch 3 and the main junction to bypass the accumulation device 42 and the first part 141 of the internal heat exchanger 14, or towards the bypass branch 15 to convey at least a portion of the refrigerant through said first part 141 of the internal heat exchanger 14.

[0203] As an example, in the thermal management system 1 as shown in Figure 14 the control unit 13 can:

[0204] - adjust the flow rate of the refrigerant circulating in the second branch 5, for example according to the variant implemented, by means of the second control member 112 or the second management member 382 (visible in Figure 4 and Figure 5 ; and / or

[0205] - according to the embodiment implemented, adjust the flow rate of the heat transfer fluid or of the internal air flow FA2 involved in the heat exchange occurring in the second heat exchanger 51; and / or

[0206] - adjust the path of the refrigerant in the second branch 5 by means of the first adjustment member 153 and the second adjustment member 154, such control being represented by the thin dotted line 4000.

[0207] As an example, when the estimated temperature of the refrigerant downstream of the compression device 33 is greater than a defined threshold, the control unit 13 can adjust the temperature of the refrigerant downstream of the compression device 33 by increasing the flow rate of the refrigerant circulating in the second heat exchanger 51, thus increasing the liquid portion of a portion of the refrigerant circulating in the second branch 5. The control unit 13 can then, if necessary, also control the path of this same portion of refrigerant by closing the first adjustment member 153 and by opening the second adjustment member 154. This portion of refrigerant coming from the second heat exchanger 51 then bypasses the first part 141 of the internal heat exchanger 14 and does not capture the thermal energy coming from the refrigerant circulating in the second part 142 of said internal heat exchanger 14. At the junction 31, this portion of refrigerant mixes with one or more portions of refrigerant coming from the first heat exchanger 41 and / or from the third heat exchanger and / or from the main heat exchanger 34 and passing through the accumulation device 42 and through the first part 141 of the internal heat exchanger 14, thus reducing the temperature of the mixture of refrigerant upstream of the compression device 33 and thus also making it possible to reduce the temperature of the refrigerant downstream of the compression device 33 towards a value suitable for optimising the performance of the thermal management system 1.

[0208] On the contrary, if it is necessary to superheat the refrigerant and therefore to convey this portion of refrigerant leaving the second heat exchanger 51 through the first component 141 of the internal heat exchanger 14 and therefore into the bypass branch 15, the control unit 13 can control the path of this same portion of refrigerant by opening the first regulating member 153 and by closing the second regulating member 154.

[0209] It should be understood that the features related to the regulating member(s) 153, 154 and the features related to the implementation of the method for regulating the temperature of the refrigerant can be extended, with the necessary modifications, to alternative solutions of the thermal management system 1 shown in Figure 13

[0210] From the foregoing it will be appreciated that the present application relates to a thermal management system comprising a refrigerant circuit which makes it possible to ensure, in a simple manner and without excessive consumption, the thermal management of at least one element of the electric powertrain of a vehicle, such as an electrical energy storage device configured to supply electrical energy to an electric drive motor of the vehicle, and the thermal management of the interior of said vehicle. The coefficient of performance of the thermal management system according to the present application is therefore improved, in particular when the requirements, in particular for cooling, are greater than the usual requirements of the vehicle. The present application also relates to a method for regulating the temperature of the refrigerant circulating in such a management system in order to optimize the performance of the management system.

[0211] However, the present application is in no way limited to the means and configurations described and shown herein, and extends to all equivalent means or configurations and to any technically operable combination of these means. In particular, modifications can be made to the architecture of the refrigerant circuit without departing from the present application, provided that it ultimately implements the functions described in this document.​

Claims

1. A thermal management system (1) intended for a vehicle and comprising at least one circuit (2) for a refrigerant (FR) having a main branch (3) extending between a main junction point (31) and a main branching point (32), and at least one first branch (4) and one second branch (5) extending between the main branching point (32) and the main junction point (31), in parallel with each other and in series with the main branch (3): - the main branch (3) having at least one compression device (33) and a main heat exchanger (34) configured to implement heat exchange between the refrigerant (FR) and an external air flow (FA1) inside the vehicle; - the first branch (4) comprising a first heat exchanger (41) and an accumulator device (42) for the refrigerant (FR), the accumulator device (42) being arranged between the first heat exchanger (41) and the main junction point (31); - the second branch (5) comprising a second heat exchanger (51); the circuit (2) for a refrigerant (FR) comprising a secondary branch (7) extending between a first branching point (71) arranged on the main branch (3) between the compression device (33) and the main heat exchanger (34) and a first junction point (72) arranged on the main branch (3) between the main heat exchanger (34) and the main branching point (32), the secondary branch (7) comprising a secondary heat exchanger (73) configured to implement heat exchange between the refrigerant (FR) and an internal air flow (FA2) conveyed into the vehicle interior; the thermal management system comprising at least: - one tertiary branch (8) extending between a second branching point (81) arranged between the main heat exchanger (34) and the first heat exchanger (41) and a second junction point (82) arranged on the main branch (3) between the first branching point (71) and the main heat exchanger (34); - one quaternary branch (9) extending between a third branching point (91) arranged on the main branch (3) between the main heat exchanger (34) and the first junction point (72) and a third junction point (92) arranged on the first branch (4) between the first heat exchanger (41) and the accumulator device (42), the quaternary branch (9) comprising at least one device (93) for regulating the flow rate of the refrigerant (FR).

2. The thermal management system (1) of claim 1, wherein At least one of said first heat exchanger (41) and said second heat exchanger (51) is thermally coupled to a heat transfer fluid circuit (6) comprising at least one element (61) of an electrically powered driveline of said vehicle, and at least the other of said first heat exchanger (41) and said second heat exchanger (51) is configured to effect heat exchange between said refrigerant (FR) and an internal air flow (FA2) inside said vehicle.

3. The thermal management system (1) of claim 1 or 2, wherein Said secondary branch (7) comprises at least one device (74) for regulating the flow rate of refrigerant (FR) and / or a secondary non-return valve (75).

4. The thermal management system (1) of claim 1, wherein Said primary branch (3) comprises at least one primary non-return valve (36) arranged between said primary heat exchanger (34) and said first junction point (72).

5. The thermal management system (1) of claim 1, comprising a third branch (10) extending between said primary branching point (32) and a fourth junction point (101) arranged on said first branch (4) between said first heat exchanger (41) and said accumulation device (42), said third branch (10) comprising at least one third heat exchanger (102).

6. The thermal management system (1) of claim 1, comprising at least one tertiary heat exchanger (37) configured to effect heat exchange between said refrigerant (FR) and an external air flow (FA1) inside said vehicle, said tertiary heat exchanger (37) being arranged on said primary branch (3) between said primary heat exchanger (34) and said primary branching point (32) and upstream of said primary heat exchanger (34) along a circulation direction (S2) of said external air flow (FA1).

7. The thermal management system (1) of claim 1, comprising at least one circulation management member (38) configured to cause expansion of said refrigerant (FR) and / or to interrupt circulation of refrigerant (FR) through said at least one circulation management member, said at least one circulation management member being arranged between said first junction point (72) and said primary junction point (31).

8. The thermal management system (1) of claim 7, wherein Said circulation management member (38) is arranged on said primary branch (3), said thermal management system (1) comprising at least one member (11) for controlling the flow rate of refrigerant (FR) arranged on said first branch (4) and / or on said second branch (5) between said management member (38) and said primary junction point (31).

9. The thermal management system (1) of claim 7, comprising a plurality of means (38) for managing the circulation of the refrigerant (FR), at least one circulation managing means (38), hereinafter referred to as first circulation managing means (381), being arranged in the first branch (4) between the main branching point (32) and the first heat exchanger (41), a second circulation managing means (382) being arranged on the second branch (5) between the main branching point (32) and the second heat exchanger (51).

10. The thermal management system (1) of one of claims 7 to 9, comprising a module (12) for dispensing refrigerant (FR), the dispensing module (12) having at least one housing (121) delimiting an internal volume (122), the main branching point (32) and at least one means (38) for managing the circulation of the refrigerant (FR) being arranged in the at least one housing.

11. The thermal management system (1) of claim 1, comprising at least one internal heat exchanger (14) configured to achieve heat exchange between a first part (141, 141') and a second part (142) of the internal heat exchanger (14), the first part (141, 141') of the internal heat exchanger (14) being comprised in a first portion (301) of the thermal management system (1) extending between the accumulation device (42) and the compression device (33), and the second part (142) of the internal heat exchanger (14) being comprised in a second portion (302) of the thermal management system (1) extending between the main heat exchanger (34) and the main branching point (32).

12. The thermal management system (1) of claim 11, wherein the first part (141) of the internal heat exchanger (14) being arranged between the accumulation device (42) and the main merging point (31), the thermal management system (1) comprising a bypass branch (15) for the refrigerant (FR) extending between a tapping point (151) arranged between the second heat exchanger (51) and the main merging point (31) and a connection point (152) arranged between the accumulation device (42) and the first part (141) of the internal heat exchanger (14).

13. The thermal management system (1) of claim 11, wherein the first part (141') of the internal heat exchanger (14) being arranged between the main merging point (31) and the compression device (33), the thermal management system (1) comprising a bypass branch (15) for the refrigerant (FR) extending between a tapping point (151) arranged between the second heat exchanger (51) and the main merging point (31) and a connection point (152) arranged between the first part (141') of the internal heat exchanger (14) and the compression device (33).

14. A method for regulating the temperature of the refrigerant (FR) exiting the compression device (33) configured by the thermal management system (1) according to any one of claims 1 to 13, the regulating method comprising: - a first step of estimating the temperature of the refrigerant (FR) exiting the compression device (33); - a second step of comparing the estimated temperature of the refrigerant (FR) with at least one temperature threshold; - a third step of regulating the heat exchange effected in the second heat exchanger (51) and / or regulating the circulation of the refrigerant (FR) in the second branch (5), the third step being effected when the estimated temperature of the refrigerant (FR) is greater than or equal to the temperature threshold.

15. The method of claim 14, wherein, The third step comprises at least one sub-step of increasing the flow rate of the refrigerant (FR) circulating in the second branch (5).

16. The method of claim 14 or 15, wherein, The second heat exchanger (51) is thermally coupled to the heat transfer fluid circuit (6) or the second heat exchanger (51) is configured to effect a heat exchange between the refrigerant (FR) and an internal air flow (FA2) of the vehicle interior, the third step comprising at least one sub-step of reducing the flow rate of the heat transfer fluid or the flow rate of the internal air flow (FA2) involved in the heat exchange effected in the second heat exchanger (51).

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