WO2021170948A1

WO2021170948A1 - Vehicle heat treatment system

Info

Publication number: WO2021170948A1
Application number: PCT/FR2021/050314
Authority: WO
Inventors: Mohamed Yahia
Original assignee: Valeo Systemes Thermiques
Priority date: 2020-02-27
Filing date: 2021-02-24
Publication date: 2021-09-02
Also published as: CN115243908A; EP4110633A1

Abstract

Heat treatment system (1) for a vehicle, comprising: - a main arm (3) comprising a main heat exchanger (34) and extending between a main convergence point (31) and a main divergence point (32); - a first arm (4) and a second arm (5) extending between the main divergence point (32) and the main convergence point (31), the first arm (4) comprising a first heat exchanger (41) and a device (42) for storing cooling fluid (FR), the second arm (5) comprising a second heat exchanger (51), - a secondary arm (7) comprising a secondary heat exchanger (73) and extending between a first divergence point (71) arranged between the compression device (33) and the main heat exchanger (34), and a first convergence point (72) arranged between the main heat exchanger (34) and the main convergence point (31).

Description

VEHICLE HEAT TREATMENT SYSTEM

The field of the present invention is that of heat treatment systems for vehicles, in particular for hybrid or electric motor vehicles, these heat treatment systems comprising at least one coolant circuit.

Motor vehicles are commonly equipped with a refrigerant circuit used to heat or cool different areas or different components of the vehicle. It is in particular known to use this refrigerant circuit to heat treat a flow of air sent into the passenger compartment of the vehicle equipped with such a circuit. Such a refrigerant circuit is integrated into a heat treatment system which is associated with a ventilation, heating and / or air conditioning installation of a vehicle interior so as to heat treat an air flow outside the vehicle. directing towards the cockpit. In fact, such a circuit makes it possible, using changes in the state of the refrigerant fluid, to heat and / or cool an air flow sent inside the ventilation, heating and / or installation. air conditioning.

In another application of this circuit, it is known to use it to cool at least one element of an electric traction chain of the vehicle, that is to say a traction chain comprising an engine operating at least partially at electrical energy supplied by one or more electrical energy storage devices on board the vehicle. As all of these elements cannot withstand excessively large temperature changes, it will be understood that the heat treatment system, and in particular the refrigerant fluid circuit, ensures their thermal regulation, more particularly their cooling. This element of the traction chain can in particular be the electrical energy storage device used to supply electrical energy or else the electric motor capable of setting said vehicle in motion. The refrigerant fluid circuit is thus sized to cool this electrical energy storage device for temperatures which remain moderate. Such heat treatment systems are most often at least partly arranged on the front face of the vehicles. More exactly, these heat treatment systems conventionally comprise at least one heat exchanger which is arranged at this front face. In a context of limitation of the size of the equipment fitted out on the front face, the reduction in the dimensions of such a heat exchanger is accompanied by a loss of efficiency of the heat treatment systems and therefore of its cooling capacity of the various aforementioned electrical elements. Such a loss of performance is particularly noticeable when the electrical storage device of the vehicle is used in a manner which causes the latter to heat up considerably, for example during a phase of rapid charging of the storage device. Fast charging consists of charging the electrical storage device at a high voltage and amperage so as to charge the electrical storage device in a short time of a few tens of minutes. This rapid charging implies a heating of the electrical storage device greater than that observed during the usual operation of the storage device which must therefore be treated.

In addition, during a charging or rapid charging phase, it may be necessary to maintain an acceptable level of thermal comfort inside the passenger compartment, i.e. the refrigerant circuit can be required to simultaneously ensure the heat treatment of the passenger compartment and the heat treatment of the storage device. Such demands imply performance of the treatment system which requires dimensioning of the system, and in particular of the heat exchanger arranged on the front face, which makes it hardly compatible with the dimensioning constraints of motor vehicles, in particular vehicles driven by an engine. electric, current.

The present invention falls within this context and aims to resolve these various drawbacks by proposing a heat treatment system intended for a vehicle and comprising at least one refrigerant circuit which comprises a main branch extending between a main point of convergence. and a main point of divergence, and at least a first branch and a second branch which extend between the main point of divergence and the main point of convergence, in parallel with each other and in series with the main branch : - the main branch comprising at least one compression device and a main heat exchanger configured to implement a heat exchange between the refrigerant fluid and a flow of air outside a passenger compartment of the vehicle; the first branch comprising a first heat exchanger and a device for accumulating the refrigerant fluid, the accumulating device being arranged between the first heat exchanger and the main point of convergence; - the second branch comprising a second heat exchanger;

The refrigerant fluid circuit according to the invention furthermore comprises a secondary branch which extends between a first point of divergence, arranged on the main branch between the compression device and the main heat exchanger, and a first point convergence, arranged on the main branch between the main heat exchanger and the main point of divergence, and the secondary branch comprising a secondary heat exchanger configured to implement a heat exchange between the refrigerant and an air flow interior sent into the vehicle cabin.

It is understood that, throughout the description below, the qualifiers "main", "first", "second" or even "primary", "secondary" are intended to distinguish similar elements of the processing system. thermal and do not confer any hierarchy of components within said system.

The refrigerant circuit of the heat treatment system according to the invention is configured to operate alternately in heat pump mode, so as to heat the interior air flow before sending it into the passenger compartment, or in air conditioning mode, in order to cool the interior air flow before sending it into the passenger compartment. Depending on the operating mode implemented, the main heat exchanger as well as the first heat exchanger or the second heat exchanger can be configured to operate as a condenser or as an evaporator, vis-à-vis the refrigerant. In other words, the first heat exchanger or the second heat exchanger can be installed in a ventilation, heating, and / or air conditioning installation.

The secondary heat exchanger can advantageously be configured to implement a direct heat exchange between the refrigerant fluid and the internal air flow. Alternatively, the secondary heat exchanger can be configured to implement a heat exchange between the refrigerant fluid and a heat transfer fluid circulating in an ancillary loop which may comprise at least at least one annex 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 fluid and the interior air flow via the heat transfer fluid circulating in the ancillary loop.

The term “accumulation device” is understood to mean a device making it possible to separate a liquid phase from a gaseous phase of the refrigerant fluid as well as to accumulate the liquid phase of the refrigerant fluid so as to send an essentially gaseous refrigerant fluid to the compression device. . Within the heat treatment system, at least the first heat exchanger and / or the main heat exchanger are intended to supply the storage device with refrigerant fluid while the second heat exchanger, arranged in the second branch, is intended bypassing said accumulation device. The second heat exchanger is in fact connected downstream of the storage device, in a direction of circulation of the refrigerant fluid in the circuit, so as to be able to generate an overheating of the fluid which directly joins the compression device, thus contributing to raising the temperature. circuit performance coefficient. By "directly" is meant that there is no bottle or storage device between the second heat exchanger and the compression device.

According to an optional characteristic of the invention, at least one of the first heat exchanger and second heat exchanger can be thermally coupled to a heat transfer fluid loop comprising at least one element of an electric traction chain of the vehicle and at least one Another of the first heat exchanger and second heat exchanger can be configured to implement a heat exchange between the coolant and the flow of air inside the passenger compartment.

According to different embodiments of the present invention, the first heat exchanger or the second heat exchanger can be thermally coupled to one of the elements of the electric power train of the vehicle.

Throughout the description below, the heat treatment system in which the first heat exchanger is configured to implement a heat exchange between the fluid will be qualified as a first embodiment. refrigerant and the interior air flow while the second heat exchanger is thermally coupled to the at least one element of the traction chain.

The heat treatment system in which the first heat exchanger is thermally coupled to at least one element of the traction chain while the second heat exchanger is configured to implement a heat exchange between the heat exchanger will be qualified as a second embodiment. refrigerant and indoor air flow.

The term “thermally coupled” is understood to mean the fact that the first heat exchanger or the second heat exchanger is configured to allow the heat treatment, and in particular the cooling of said element. In this way, the heat treatment system can be configured to dissipate the calories generated by at least one of the elements of the traction chain, for example an engine capable of setting said vehicle in motion and operating at least partially at the same time. electrical energy, an electronic control module controlling it and / or an electrical energy storage device used to supply energy to the motor.

According to one aspect of the invention, the secondary branch comprises at least one means for regulating the flow of refrigerant fluid and / or a secondary non-return valve.

The term "flow regulation means" is understood here to mean a component of the heat treatment system configured to interrupt the circulation of the refrigerant fluid in the secondary branch or to regulate the flow rate such as a two-way or multi-way valve.

By “non-return valve” is meant, in the present description, a component of the heat treatment system configured to limit the circulation of the refrigerant fluid within the branch considered, here the secondary branch, to a single direction of circulation.

According to an optional characteristic of the invention, the heat treatment system can comprise at least one tertiary branch which extends between a second point of divergence, arranged between the main heat exchanger and the first heat exchanger, and a second point of convergence, arranged on the main branch between the first point of divergence and the main heat exchanger. By way of example, the second point of divergence can be arranged on the first branch. According to a particular example of embodiment, the second point of divergence and the main point of divergence can be merged, so that the first branch, the second branch and the tertiary branch are arranged in parallel with each other and in series with the branch. main circuit.

According to an optional characteristic of the invention, the heat treatment system can comprise a quaternary branch which extends between a third point of divergence, arranged on the main branch between the main heat exchanger and the first point of convergence, and a third point of convergence, arranged on the first branch between the first heat exchanger and the storage device, the quaternary branch comprising at least one device for regulating the flow of refrigerant fluid.

Similarly to what has been explained with reference to the flow regulating means, the fluid flow regulating device is configured to interrupt the circulation of the refrigerant fluid in the quaternary branch or to regulate the flow thereof.

According to an optional feature of the invention, the main branch comprises at least one main non-return valve, disposed between the main heat exchanger and the first point of convergence. Such a non-return valve is in particular configured to limit the circulation of the refrigerant fluid within the main branch according to the operating mode implemented.

According to an optional characteristic of the invention, the heat treatment system comprises a third branch which extends between the main point of divergence and a fourth point of convergence, arranged on the first branch between the first heat exchanger and the device. accumulation, the third branch comprising at least a third heat exchanger.

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

Advantageously, the third heat exchanger can be thermally coupled to at least one of the elements of the electric traction chain of the vehicle such as than previously exposed. Advantageously, the first heat exchanger or the second heat exchanger on the one hand, and the third heat exchanger on the other hand, can be assigned to the heat treatment of the same element of the electric traction chain so as to optimize its regulation. thermal. By way of example, the element of the traction chain can be the electrical energy storage device. The heat treatment system is advantageously adapted to meet cooling needs greater than those required during normal operation of the storage device, which may for example be observed during a rapid charging phase or during thermal treatment of the passenger compartment. simultaneously with the load of the electric energy storage device.

According to an optional characteristic of the invention, the heat treatment system can comprise at least one tertiary heat exchanger configured to implement a heat exchange between the refrigerant fluid and the air flow outside the vehicle interior, the 'tertiary heat exchanger being disposed on the main branch between the main heat exchanger and the main point of divergence.

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

In particular, the tertiary heat exchanger can be placed directly upstream of the main heat exchanger according to the direction of circulation of the flow of outside air so that the flow of air heated by heat exchange with the heat exchanger tertiary sector is sent directly to the main heat exchanger. The main heat exchanger and the tertiary heat exchanger can thus be arranged on the front face of the vehicle or, alternatively, on a roof of the vehicle, in a rear wing and in general in all areas of the vehicle which can be swept by the flow of outside air.

In such an arrangement, the refrigerant fluid exiting the main heat exchanger is sent to the tertiary heat exchanger before passing through the main point of divergence. The tertiary heat exchanger then functions as a unit for sub-cooling the refrigerant fluid, i.e. the tertiary heat exchanger is configured to lower the temperature of the refrigerant below its condensing temperature, thus helping to optimize performance of the heat treatment system.

According to an optional characteristic of the invention, the heat treatment system comprises at least one circulation management member configured to operate an expansion of the refrigerant fluid and / or to interrupt the circulation of the refrigerant fluid therethrough and arranged between the first point of convergence and the main point of convergence.

In other words, the circulation management unit is configured to implement a function of reducing the pressure of the refrigerant fluid, for example so as to change the refrigerant fluid from a high pressure to a low pressure, lower than the high pressure, or to implement a function of obstructing the circulation of the refrigerant fluid. For example, the traffic management unit may be an electronic expansion valve equipped with a stop function.

According to a first variant embodiment of the heat treatment system, the circulation management member can be arranged on the main branch, the heat treatment system comprising at least one refrigerant fluid flow control member arranged on the first branch and / or on the second branch between the management body and the main point of convergence.

In other words, in this first variant, the traffic management unit is particularly placed between the first point of convergence and the main point of divergence. The refrigerant is then subjected to a low pressure when it circulates at the level of the main point of divergence, that is to say prior to its distribution in the first branch and / or in the second branch and / or in the third branch and / or in the tertiary branch.

The term “flow control member” is understood to mean a component of the heat treatment system configured to interrupt the circulation of the refrigerant fluid in the branch in question or to regulate the flow thereof. For example, the flow control member may consist of a two-way valve or a multi-way valve.

In particular, the heat treatment system can include a plurality of flow control members. Advantageously, at least one of these flow control members can be placed on the third branch and / or on the tertiary branch. According to a second variant, the heat treatment system may comprise a plurality of members for managing the circulation of the refrigerant fluid, at least the member for managing the circulation, hereinafter called the first member for managing the circulation being arranged in the first branch, between the main point of divergence and the first heat exchanger, and a second circulation management member being arranged on the second branch, between the main point of divergence and the second heat exchanger.

In other words, in such a variant, the refrigerant fluid passing at the level of the main point of divergence is subjected to a high pressure and the expansion of the refrigerant fluid is at least implemented in the first branch and second branch, and not in the main branch of the circuit.

Furthermore, the heat treatment system may include a third circulation management member, arranged in the third branch between the main point of divergence and the third heat exchanger. Additionally, the heat treatment system may include at least one tertiary refrigerant circulation management unit, arranged on the tertiary branch, that is to say upstream of the main heat exchanger.

According to an alternative embodiment of the first variant and of the second variant of the heat treatment system, the latter may comprise a refrigerant fluid distribution module, the distribution module comprising at least one housing delimiting an internal volume in which are arranged the main point of divergence and the at least one unit for managing the circulation of the refrigerant fluid.

Particularly, when the heat treatment system is produced according to the first variant, the refrigerant fluid distribution module can house at least one of the refrigerant fluid circulation control members. Advantageously, the distribution module can house all of the refrigerant circulation control devices.

Similarly, when the heat treatment system is produced according to the second variant, the refrigerant fluid distribution module can accommodate a plurality of the refrigerant fluid circulation management members. Advantageously, the distribution module can house all of the components for managing the circulation of the refrigerant fluid. Such a distribution module contributes in particular to physically grouping together, within the heat treatment system, the traffic management unit (s) and / or the traffic control unit (s), thus simplifying their traffic control unit (s). incorporation into the vehicle. According to a particular embodiment, applicable to the first embodiment, to the second embodiment as well as to the various variant embodiments described above, the heat treatment system may comprise at least one internal heat exchanger configured to implement an exchange. heat exchanger between a first part and a second part of the internal heat exchanger, the first part of the internal heat exchanger being included in a first portion of the heat treatment system which extends between the storage device and the storage device. compression, and the second part of the internal heat exchanger being included in a second portion of the heat treatment system which extends between the main heat exchanger and the main point of divergence.

In such an arrangement, the first part of the internal heat exchanger can thus be arranged on the main branch so as to be interposed between the main point of convergence and the compression device so that at least the refrigerant fluid leaving the first heat exchanger and / or the second heat exchanger is fed to the first part of the internal heat exchanger. Alternatively, the first part of the internal heat exchanger can be arranged on the first branch, between the storage device and the main point of convergence, so that the refrigerant fluid leaving the second heat exchanger bypasses the first part of the heat exchanger. the internal heat exchanger. According to an optional characteristic of this particular mode, when the first part of the internal heat exchanger is arranged between the storage device and the main point of convergence, the heat treatment system can include a branch for bypassing the refrigerant fluid which s 'extends between a bypass point, disposed between the second heat exchanger and the main point of convergence, and a connection point, disposed between the storage device and the first part of the internal heat exchanger. In other words, such a bypass branch is configured to send at least part of the refrigerant fluid leaving the second heat exchanger to the first part of the internal heat exchanger.

According to an optional characteristic of an alternative of this particular embodiment, when the first part of the internal heat exchanger is arranged between the main point of convergence and the compression device, the heat treatment system can comprise the bypass branch refrigerant which extends between the bypass point, disposed between the second heat exchanger and the main point of convergence, and the connection point, disposed between the first part of the internal heat exchanger and the compression device.

In other words, such a bypass branch is configured that at least part of the refrigerant fluid leaving the second heat exchanger bypasses the first part of the internal heat exchanger and can, as needed, directly feed the compression device. .

Advantageously, and independently of the positioning of the bypass branch, the circulation of the refrigerant fluid in the bypass branch can be regulated, the heat treatment system comprising at least one member for regulating the flow of refrigerant fluid arranged on the bypass branch and / or between the point of derivation and the main point of convergence on the second branch.

By way of example, the heat treatment system may comprise at least the refrigerant flow rate regulator member, called the first refrigerant fluid flow rate regulator member, arranged on the bypass branch, and at least one second member. for regulating the flow of refrigerant, arranged between the bypass point and the main point of convergence.

Alternatively, the refrigerant flow regulator can consist of a multi-way valve arranged at the bypass point.

The present invention also relates to a method of adjusting a temperature of the refrigerant fluid at the outlet of the compression device equipping a heat treatment system as described above, the adjustment method comprising: - A first step of estimating the temperature of the coolant at the outlet of the compression device;

- A second step of comparing the estimated temperature of the coolant with at least one temperature threshold value;

- A third step of regulating the heat exchange implemented in the second heat exchanger and / or regulating the circulation of the refrigerant fluid in the second branch implemented when the estimated temperature of the refrigerant is greater than or equal to the temperature threshold value.

For example, the first step may include a step of directly measuring the temperature of the refrigerant or measuring the pressure of the refrigerant so as to extract the temperature of the refrigerant.

By "heat exchange regulation" is meant the modification of a variable of the heat treatment system modifying the heat exchange implemented within the second heat exchanger. For example, such a variable may be the flow rate of the refrigerant fluid circulating in the second branch and / or the flow rate of the heat transfer fluid circulating in the heat transfer fluid loop, when the heat treatment system is produced according to the first embodiment, or the flow rate of the interior air flow, when the heat treatment system is produced according to the second embodiment.

By “regulation of the circulation” is meant the control of the flow of the refrigerant fluid within the second branch, that is to say the fact that the refrigerant fluid circulates entirely or not along the second branch, for example when the heat treatment system includes the internal heat exchanger and the bypass branch.

In particular, the third step can include at least one substep for increasing the flow of refrigerant fluid circulating in the second branch.

Additionally or alternatively, the second heat exchanger can be thermally coupled to the heat transfer fluid loop or the second heat exchanger being configured to implement a heat exchange between the coolant and the air flow inside the passenger compartment, the third step may include at least one sub-step of reducing the flow rate of the heat transfer fluid or the flow rate of the interior air flow involved in the heat exchange implemented in the second heat exchanger.

An object of the present invention also relates to a motor vehicle comprising at least one heat treatment system as described above.

Other characteristics, details and advantages will emerge more clearly on reading the detailed description given below as an indication in relation to the various embodiments illustrated in the following figures:

Figure i is a general schematic representation of a heat treatment system according to the invention comprising at least one refrigerant circuit;

Figure 2 is a schematic representation of a first embodiment of the heat treatment system shown in Figure t;

Figure 3 is a schematic representation of a second embodiment of the heat treatment system shown in Figure 1;

Figure 4 is a partial schematic representation of a first alternative embodiment of the processing systems as shown in Figures 1 to 3;

Figure 5 is a partial schematic representation of a second alternative embodiment of the processing systems as shown in Figures 1 to 3;

Figure 6 schematically illustrates a first example of the operation of the heat treatment system shown in Figure 2 in which the refrigerant circuit operates in passenger compartment cooling mode;

FIG. 7 schematically illustrates a second example of the operation of the heat treatment system shown in FIG. 2 in which the refrigerant circuit operates in cooling mode of the passenger compartment and of an element of a traction chain of the vehicle;

FIG. 8 schematically illustrates a third example of operation of the heat treatment system shown in FIG. 2 in which the refrigerant circuit operates in mode for cooling the passenger compartment and at least one element of an electric traction chain of the vehicle. vehicle; FIG. G schematically illustrates a fourth example of the operation of the heat treatment system shown in FIG. 2 in which the refrigerant circuit operates in mode for heating the passenger compartment;

Figure io schematically illustrates a fifth example of the operation of the heat treatment system shown in Figure 2 in which the refrigerant circuit operates in the mode of heating the passenger compartment and cooling of the element of the electric drive chain of the vehicle;

Figure n is a schematic representation of a process for adjusting the temperature of the refrigerant circulating in the heat treatment systems shown in Figures 1, 2 or 3;

Figure 12 is a schematic representation of a particular embodiment of heat treatment systems as shown in Figures 1, 2 or 3;

Figure 13 is a schematic representation of an alternative to the particular embodiment shown in Figure 12;

Figure 14 is a schematic representation of the process for adjusting the temperature of the refrigerant circulating in a heat treatment system as shown in Figure 12;

It should first be noted that the figures set out the invention in detail to implement the invention, said figures can of course be used to better define the invention, if necessary.

FIG. 1 is a general representation of a heat treatment system 1 of a vehicle comprising at least one circuit 2 of refrigerant fluid FR, for example a sub-critical fluid such as that known under the reference R134A or R1234YF, which is in particular intended for the heat treatment of a vehicle interior.

The terms “upstream” and “downstream” used in the following description refer to the direction of circulation of the fluid considered, that is to say to a direction of flow Si of the refrigerant fluid in circuit 2 or to a direction of flow. circulation S2 of an external air flow FAi to the passenger compartment.

In FIGS. 6 to 10, the refrigerant fluid is symbolized by an arrow which illustrates the direction of circulation Si of the latter in the pipe considered. Full lines illustrate a portion of circuit 2 where the refrigerant fluid circulates while the dotted lines show an absence of circulation of the refrigerant fluid. High pressure, high temperature refrigerant is shown by thick lines. Low pressure and low temperature refrigerant fluid is represented by thin lines.

The names "principal", "first", "second", "primary" etc ... are not intended to indicate a level of hierarchy or to organize the terms they accompany. These names make it possible to distinguish the terms which they accompany and can be inverted without reducing the scope of the invention.

As illustrated in Figure 1, the refrigerant fluid circuit 2 FR is a closed circuit 2 which implements a thermodynamic cycle. The circuit 2 comprises at least one main branch 3 which extends between a main point of convergence 31 and a main point of divergence 32 and on which are arranged at least one compression device 33, intended to raise the pressure of the refrigerant fluid, and a main heat exchanger 34 configured to implement a heat exchange between the refrigerant fluid FR and the flow of air FAi outside the vehicle interior.

In particular, the main heat exchanger 34 can at least be used as a condenser. It can be placed on the front of the vehicle to benefit from an external air flow intake FAi during the driving phase. Note that the compression device 33 may take the form of an electric compressor, that is to say a compressor which includes a compression mechanism, an electric motor and possibly a controller.

Circuit 2 further comprises at least a first branch 4 and a second branch 5 which extend between the main point of divergence 32 and the main point of convergence 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 a refrigerant storage device 42 which is arranged between the first heat exchanger 41 and the main point of convergence 31. The storage device 42 is thus arranged. upstream of the main point of convergence 31, and therefore of the compression device 33, according to the direction of flow Si of the refrigerant. The accumulation device 42 is configured to separate a liquid phase from a gas phase of the refrigerant fluid and to accumulate the liquid phase of the refrigerant fluid so in sending an essentially gaseous refrigerant fluid to the compression device 33.

The second branch 5 comprises at least a second heat exchanger 51. The second branch 5 is connected to the main branch 3 so as to bypass the accumulation device 42. Thus, the accumulation device 42 is able to be at less supplied with refrigerant fluid by the first heat exchanger 41 and / or by the main heat exchanger 34, while the second heat exchanger 51 supplies directly, that is to say without going through the storage device 42, the compression device 33.

According to an exemplary embodiment, the first heat exchanger 41 and the second heat exchanger 51 can be configured to implement a heat exchange between the refrigerant fluid FR and a flow of air FA2 outside the vehicle interior. In other words, the first heat exchanger 41 and the second heat exchanger 51 can be configured to at least function as an evaporator. Optionally, one of these heat exchangers, for example the first heat exchanger 41, can be configured to produce a higher power than the other heat exchanger, here the second heat exchanger 51. For example, the first heat exchanger 41 may have dimensions greater than those of the second heat exchanger 51.

According to other particular embodiments of the invention, at least one of the first heat exchanger 41 and second heat exchanger 51 is configured so as to be thermally coupled to a heat transfer fluid loop 6 comprising at least one element 61, visible in Figures 2 or 3, of an electric drive chain of the vehicle while at least the other of the first heat exchanger 41 and second heat exchanger 51 is configured to implement a heat exchange between the coolant and the flow interior air FA2 to the passenger compartment.

Figures 2 and 3 thus illustrate two distinct embodiments of the heat treatment system 1 as shown in Figure 1, these embodiments differing from each other by the function of their first heat exchanger 41 and second heat exchanger 51. FIG. 2 represents a first embodiment of the heat treatment system 1 in which the first heat exchanger 41 is configured to implement a heat exchange between the heat exchanger. refrigerant fluid FR and the flow of air FA2 inside the passenger compartment while the second heat exchanger 51 is thermally coupled to at least one of the elements 61 of the electric drive system of the vehicle.

Conversely, FIG. 3 represents a second embodiment of the heat treatment system 1 in which the first heat exchanger 41 is thermally coupled to at least one of the elements 61 of the electric traction chain of the vehicle while the second heat exchanger 51 is configured to implement a heat exchange between the refrigerant fluid and the flow of air FA2 inside the passenger compartment.

As illustrated in FIG. 2, the heat transfer liquid loop 6 is a closed loop 6 which comprises at least one main pipe 600 on which are at least arranged the second heat exchanger 51, at least one element 61 of the chain. electric traction and a circulation means 62 of the heat transfer fluid, such as a pump. It should be noted that, in the second heat exchanger 51, the various circulating fluids do not mix and that the heat exchange between these two fluids takes place by conduction.

The element 61 of the traction chain to be thermally treated, and in particular to be cooled, may, for example, consist of an electric motor, a control module for said motor, or of an electrical energy storage device 63 configured to supply power. said motor into electrical energy. For the sake of clarity, throughout the description below, the element 61 of the traction chain considered will be the electrical energy storage device 63 and the terms “element 61 of the traction chain” and “Electrical energy storage device 63” can be used without distinction.

It is understood that such a description of the heat transfer fluid loop 6, as well as any description given with reference to said loop 6, extends to the second embodiment of the heat treatment system 1 as illustrated in FIG. 3. , with the difference that the heat transfer fluid loop 6 then comprises the first heat exchanger 41 instead of the second heat exchanger 51. The same applies to the embodiment as described above, in which the first heat exchanger 41 and the second heat exchanger 51 are configured to implement a heat exchange between the refrigerant fluid FR and an air flow exterior FA2 to the passenger compartment, the entire description of this text being able to apply mutatis-mutandis.

The heat treatment system 1 as illustrated in FIGS. 1 to 3 also comprises at least one secondary branch 7 which extends between a first point of divergence 71 and a first point of convergence 72. The first point of divergence 71 is particularly disposed on the main branch 3 between the compression device 33 and the main heat exchanger 34 while the first point of convergence 72 is disposed on the main branch 3 between the main heat exchanger 34 and the main point of divergence 32 In other words, the secondary branch 7 is arranged within the heat treatment system 1 so as to be able to ensure, depending on the operating mode implemented by the circuit 2, the bypass of the main heat exchanger 34. .

The secondary branch 7 comprises a secondary heat exchanger 73 configured to implement a heat exchange between the coolant and the internal air flow FA2 sent into the vehicle cabin. The secondary heat exchanger 73 is thus configured to operate as a condenser in a ventilation, heating, and / or air conditioning installation of the vehicle. The heat exchange between the refrigerant and the indoor air flow then occurs directly.

According to an alternative not shown, the secondary heat exchanger 73 can be configured to implement a heat exchange between the refrigerant fluid and a heat transfer fluid circulating in an ancillary loop. Such an ancillary loop may include at least one ancillary heat exchanger configured to implement a heat exchange between the heat transfer fluid and the internal air flow FA2. In other words, in such an alternative, the secondary heat exchanger 73 contributes to implementing an indirect heat exchange between the refrigerant fluid and the internal air flow FA2 via the heat transfer fluid circulating in the annex loop.

In addition, the secondary branch 7 comprises at least one means 74 for regulating the flow of refrigerant fluid, configured to interrupt the circulation of the refrigerant fluid in the secondary branch 7 or to regulate the flow thereof, and / or a secondary non-return valve 75 configured to limit the circulation of the refrigerant fluid within the secondary branch 7 to a single direction of circulation and in particular, in the example illustrated, preventing the circulation of the refrigerant fluid from the first point of convergence 72 to the first point of divergence 71 within the secondary branch 7.

Additionally, the heat treatment system 1 may comprise, in the main branch 3, at least one element 35 for regulating the flow of refrigerant fluid. Such a regulation element 35 is configured to modify the flow of refrigerant fluid and / or to interrupt the circulation of said refrigerant fluid in at least part of the main branch 3. The regulation element 35 is arranged between the first point of divergence 71 and the main heat exchanger 34 so as to selectively direct the refrigerant to the rest of the main branch 3 or to the secondary branch 7.

The heat treatment system 1 according to the invention can be configured so as to implement different operating modes relating to the heat treatment of the passenger compartment and / or of at least one element 61 of the electric powertrain. To this end, the heat treatment system 1 according to the invention can include at least one tertiary branch 8 and / or a quaternary branch 9.

The tertiary branch 8 extends between a second point of divergence 81, arranged between the main heat exchanger 34 and the first heat exchanger 41, and a second point of convergence 82, arranged on the main branch 3, between the first point of divergence 71 and the main heat exchanger 34. According to an alternative not shown, the second point of divergence 81 and the main point of divergence 32 may be the same.

The quaternary branch 9 for its part extends between a third point of divergence 91, arranged on the main branch 3 between the main heat exchanger 34 and the first point of convergence 72, and a third point of convergence 92 arranged on the first branch 4 between the first heat exchanger 41 and the storage device 42. The quaternary branch 9 comprises at least one device 93 for regulating the flow of refrigerant fluid configured to interrupt, according to the operating mode implemented by the circuit 2 , the circulation of the refrigerant fluid in the quaternary branch 9 and / or regulate the flow of the refrigerant fluid within this same branch.

Particularly, the main branch 3 of the circuit 2 can comprise at least one main non-return valve 36, disposed between the main heat exchanger 34 and the first point of convergence 72, and configured to prevent the refrigerant fluid from flow from the first point of convergence 72 to the main heat exchanger 34.

The heat treatment system 1 can also optionally comprise at least a third branch 10 which extends between the main point of divergence 32 and a fourth point of convergence 101, arranged on the first branch 4 between the first heat exchanger 41 and the storage device 42. The third branch 10 comprises at least a third heat exchanger 102 thermally coupled to at least one of the elements of the electric traction chain of the vehicle.

According to an optional characteristic and according to the embodiment implemented, the first heat exchanger 41 or the second heat exchanger 51 on the one hand and the third heat exchanger 102 on the other hand can be configured to jointly heat treat the same element 61. of the electric traction chain, for example the electric energy storage device 63. Such an arrangement makes it possible, in particular, to meet cooling needs greater than those required during normal operation of the storage device 63, which may for example be observed during a rapid charging phase or during thermal treatment of the storage device. the passenger compartment simultaneously with the load of the storage device 63 of electrical energy.

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 traction chain while the third heat exchanger 102 can be configured to be thermally coupled to a second element of the traction chain, distinct from the first element.

Thus, the third heat exchanger 102 is arranged in parallel with the first heat exchanger 41 and the second heat exchanger 51 and is arranged in the circuit 2 so that the storage 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.

The heat treatment system 1 according to the invention can, optionally, comprise at least one tertiary heat exchanger 37 configured to implement a heat exchange between the refrigerant fluid FR and the flow of outside air. FAi to the vehicle interior. The tertiary heat exchanger 37 is arranged on the main branch 3 between the main heat exchanger 34 and the main point of divergence 32 so as to be able to ensure, depending on the operating mode implemented, the sub-cooling of the fluid. refrigerant leaving the main heat exchanger 34.

Advantageously, the tertiary heat exchanger 37 can be arranged upstream of the main heat exchanger 34 according to the direction of circulation S2 of the external air flow FAi. In other words, the tertiary heat exchanger 37 is arranged so that the outside air flow FAi passes through it before the latter passes through the main heat exchanger 34.

The heat treatment system 1 also comprises at least one member 38 for managing the circulation of the refrigerant fluid which is arranged between the first point of convergence 72 and the main point of convergence 31 and configured to operate an expansion of the refrigerant fluid and / or to interrupt the circulation of the refrigerant fluid through it. This management member 38 and different alternative examples of its positioning are shown in Figures 1 to 3 by a diamond, different integration variants of such a management member 38 will be detailed below with reference to Figures 4 and 5. By way of example, the traffic management unit 38 may be an electronic expansion valve equipped with a stop function.

Such a traffic management unit 38 can be tilted to different positions. When fully open, it does not change the state of the refrigerant and is qualified as inoperative. When it is partially open, the management unit 38 performs the expansion of the refrigerant fluid. Finally, when it is closed, the management unit 38 implements its stop function and obstructs the passage of the refrigerant fluid therethrough.

The circulation management unit 38 can be arranged within the heat treatment system 1 according to different variants, examples of partial representations of the heat treatment system 1 produced according to these different variants being illustrated in Figures 4 and 5. It is understood that each of these variants can be integrated into each of the embodiments and alternatives of the processing system as set out in Figures 1, 2, 3 or 12, the integration of one or the other of the variants being schematically represented by an insert 1000 in the rest of the figures. According to a first variant embodiment of the heat treatment system 1, illustrated in FIG. 4, the traffic management member 38 can be arranged on the main branch 3, that is to say between the first point of convergence 72 and the main point of divergence 32. In such a heat treatment system 1, the refrigerant is then subjected to a low pressure when it circulates at the level of the main point of divergence 32, that is to say prior to its distribution to the first branch 4 and / or towards the second branch 5 and / or towards the third branch

10 and / or to the tertiary branch 8.

In such a variant, the heat treatment system 1 comprises at least one member 11 for controlling the flow of refrigerant fluid arranged on the first branch 4 and / or on the second branch 5, in particular between the member 38 for managing the circulation. refrigerant and the main point of convergence 31, so as to selectively control the path of the refrigerant in the first branch 4 and / or in the second branch 5.

The flow control member 11 is a component of the heat treatment system 1 configured to interrupt the circulation of the refrigerant fluid in the branch in question or to regulate the flow. For example, the supervisory body

The flow rate may consist of a two-way valve or a multi-way valve.

In this case, the first variant of the heat treatment system 1 comprises a plurality of flow control members 11. The refrigerant fluid flow control member 11, hereinafter called the first flow control member 111, is disposed on the first branch 4. As illustrated, such a first control member 111 can be disposed upstream of the first heat exchanger 41 according to the direction of circulation Si of the refrigerant fluid, that is to say between the main point of divergence 32 and the first heat exchanger 41, or, according to an alternative not shown, downstream of this same first heat exchanger 41 , between the first heat exchanger 41 and the main point of convergence 31.

Similarly, the heat treatment system 1 may comprise a second control member 112 of the flow of refrigerant fluid, arranged on the second branch 5 upstream or downstream of the second heat exchanger 51, and / or a third control member 113 the flow of refrigerant fluid, disposed upstream or downstream of the third heat exchanger 102 on the third branch 10, and / or a tertiary control unit 114 of the flow of refrigerant, arranged on the tertiary branch 8.

It is understood that such an alternative embodiment is in no way limiting and that the plurality of control members 11 may, according to an alternative not shown, comprise at least one multi-way valve configured to simultaneously control the circulation of the refrigerant fluid in different branches of circuit 2. By way of example, such a multi-way valve can be fitted at the level of the main point of divergence 32 so as to control the circulation of the refrigerant fluid towards the first branch 4 and / or towards the second branch 5 and / or to the third branch 10.

It is understood that the control member (s) 11 of the coolant flow rate thus make it possible to selectively direct the coolant, subjected to a low pressure, towards the various branches emerging for example from the main point of divergence 32 in authorizing and prohibiting the circulation of this refrigerant fluid in one or the other of these branches 4, 5, 8 and / or 10.

According to a second variant, illustrated in FIG. 5, the heat treatment system 1 can comprise a plurality of members 38 for managing the circulation of the refrigerant fluid, that is to say a plurality of components configured to operate an expansion. of the refrigerant fluid and / or to interrupt the circulation of the refrigerant fluid therethrough.

In the example illustrated, the traffic management unit 38, hereinafter called the first traffic management unit 381, is arranged in the first branch 4, between the main point of divergence 32 and the first heat exchanger 41 In particular, the heat treatment system 1 can include, as illustrated, the first traffic management member 381, arranged on the first branch 4 between the second point of divergence 81 of the tertiary branch 8 and the first heat exchanger. 41, and a tertiary traffic management body 384, arranged on the tertiary branch 8 between the second point of divergence 81 and the main point of convergence 31, visible in Figures 1 to 3. According to an alternative not shown, the trigger and / or the control of the circulation of the refrigerant fluid sent to the first branch 4 and / or to the tertiary branch 8 can be implemented by the same management member 38 of the circulation, for example the pre mier organ management 381, arranged on the first branch 4, between the main point of divergence 32 and the second point of divergence 81.

The heat treatment system 1 can also include at least one second circulation management member 382, here arranged on the second branch 5 between the main point of divergence 32 and the second heat exchanger 51.

In such a variant, the heat treatment system 1 can also include, on the third branch 10, at least one third traffic management member 383, arranged between the main point of divergence 32 and the second heat exchanger 51.

In other words, in this second variant, the refrigerant fluid passing at the level of the main point of divergence 32 is subjected to a high pressure and a high temperature and the expansion of the refrigerant fluid is carried out downstream of the main point of divergence 32, at least in the first branch 4 and second branch 5, and not in the main branch 3 of circuit 2.

According to a particular exemplary embodiment, the heat treatment system 1 produced according to the first variant or according to the second variant, respectively represented in FIGS. 4 and 5, can comprise a distribution module 12 of the refrigerant fluid. The distribution module 12 comprises at least one housing 121 delimiting an internal volume 122 in which are formed the main point of divergence 32 and at least one member 38 for managing the circulation of the refrigerant fluid. In Figures 4 and 5, such a housing 121 is schematically represented by thick dotted lines so as to indicate the optional character, specific to the present particular embodiments, of such a characteristic.

Such a distribution module 12 thus comprises at least one inlet 123 for the refrigerant fluid in the distribution module 12, allowing at least part of the main branch 3 to pass, and a plurality of outlets for the refrigerant fluid outside the distribution module 12, the number of outputs implemented in an operating mode of the heat treatment system 1 being equal to the number of heat exchanger (s) 41, 51, 101 and / or heat exchanger 34, supplied with refrigerant fluid.

The illustrated distribution module 12 thus comprises, in a nonlimiting manner, a first outlet 124, allowing the first branch 4 to pass, and / or a second outlet. 125, allowing the second branch 5 to pass, and / or a third outlet 126, allowing the third branch 10 to pass, and / or a fourth outlet 127, allowing the tertiary branch 8 to pass.

Advantageously, in each of the illustrated variants, the refrigerant fluid circulating at the level of 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 a low pressure. Also, the distribution module 12 is not subject to sealing and / or strength constraints and the housing 121 of said distribution module 12 can be made of a plastic material. Moreover, according to the example illustrated in FIG. 4 for the first variant embodiment, at least one of the control members 11 of the circulation of the refrigerant fluid can be arranged in the internal volume 122 delimited by the housing 121. Advantageously , the distribution module 12 can house, in the internal volume 122, all of the control members 11 for the circulation of the refrigerant fluid. Similarly, as illustrated in FIG. 5 for the second variant embodiment, the distribution module 12 can accommodate at least part of the plurality of management members 38 for the circulation of the refrigerant fluid in the internal volume 122 of the housing. 121. Advantageously, the distribution module 12 can house all of the management members 38 for the circulation of the refrigerant fluid from the heat treatment system 1 within the housing 121. By way of example, in the example illustrated, the module distribution 12 houses the first traffic management unit 381, the second traffic management unit 382, the third traffic management unit 383 and the tertiary traffic management unit 384.

Such a distribution module 12 participates in particular in physically grouping together, within the heat treatment system 1, the traffic management unit (s) 38 and / or the control unit (s) 11 of the flow rate. coolant, thus simplifying their incorporation into the vehicle.

FIGS. 6 to 10 illustrate different modes of operation of the heat treatment system 1. For the sake of clarity, these different modes of operation will be described for a heat treatment system 1 produced according to the first embodiment, in which the second exchanger thermal 51 is thermally coupled to at least one element 61 of the traction chain such as previously described with reference to FIG. 2, and according to the first variant embodiment as shown in FIG. 4. It is nevertheless understood that the whole of the following description extends to the various combinations of the embodiments and of the embodiments. variant embodiments as previously described. FIG. 6 illustrates a first example of the operation of the heat treatment system 1 according to the invention, in which the circuit 2 is configured to operate in air conditioning mode, that is to say that it is configured to cool the flow of interior air FA2, passing through the first heat exchanger 41, before the latter is sent into the passenger compartment of the vehicle. Such an operating mode can in particular be implemented during a phase of rolling of the vehicle.

In circuit 2, the circulation of the refrigerant fluid FR is limited to the main branch 3 and to the first branch 4. The second branch 5, the third branch 10, the secondary branch 7, the tertiary branch 8 and the quaternary branch 9 do not are not traversed by the refrigerant. In the example illustrated, the circulation of the refrigerant fluid in said branches 5, 10, 7, 8 and 9 is respectively hampered by the closing of the second control member 112, of the third control member 113, of the flow regulation means 74. , of the tertiary control member 114 and of the device 93 for regulating the flow of refrigerant fluid.

The refrigerant fluid leaves the compression device 33 under high pressure, high temperature and in a predominantly gaseous state to the main heat exchanger 34 which functions as a condenser. The refrigerant having a temperature higher than that of the external air flow FAi passes through this first main heat exchanger 34 and transfers its calories to the external air flow FAi. The refrigerant thus cooled leaves the main heat exchanger 34 mainly in the liquid state and enters the tertiary heat exchanger 37.

The tertiary heat exchanger 37 operates as a sub-cooler, that is to say that it ensures the cooling of the refrigerant fluid to a temperature at least below its condensation temperature by heat exchange with the air flow. outside FAi, colder. The refrigerant thus leaves the tertiary heat exchanger 37 at a temperature lower than that observed at the outlet of the main heat exchanger 34. As illustrated, the tertiary heat exchanger 37 is advantageously arranged upstream of the main heat exchanger 34 in the direction of circulation S2 of the external air flow FAi. In this way, the outside air flow FAi involved in the heat exchange at the level of the tertiary heat exchanger 37 has a temperature lower than that of the outside air flow FAi involved in the heat exchange at the level of the 'main heat exchanger 34, which has been preheated. The temperature pinch between the coolant and the outside air flow FAi specific to the main heat exchanger 34 is thus reduced compared to the temperature pinch observed at the tertiary heat exchanger 37. Such an arrangement contributes to increase the capacity of the heat treatment system 1, in particular by allowing, for the supply of the same cold power, a reduction in the speed of rotation of the compression device 33.

The refrigerant thus sub-cooled passes through the main non-return valve 36 to the first point of convergence 72, then circulates towards the main point of divergence 32. As previously explained, in the example illustrated, the heat treatment system 1 combines the first embodiment and the first variant embodiment. Also, the refrigerant fluid management member 38, configured to ensure the expansion and / or to interrupt the circulation of the refrigerant fluid, is arranged on the main branch 3, between the first point of convergence 72 and the main point of divergence 32. .

The refrigerant thus undergoes a decrease in its pressure in the refrigerant fluid management member 38 and passes, at low pressure, at the level of the main point of divergence 32. The second control member 112, the third control member 113 and the tertiary control member 114 being closed and the first control member 111 allowing the passage of the refrigerant fluid while being at least partially open, the refrigerant fluid is sent to the first branch 4.

The refrigerant fluid passes through the first heat exchanger 41 at low pressure and at low temperature. In doing so, the coolant captures calories from the warmer interior air flow FA2, which is thus cooled before being sent to the passenger compartment. The refrigerant thus leaves the first heat exchanger 41 in two-phase form and circulates along the first branch 4 as far as the accumulation device 42. Within the accumulation device 42, the liquid phase and the gaseous phase of the refrigerant fluid are separated and refrigerant essentially gaseous passes the main point of convergence 31 in order to be returned to the main branch 3 and to the compression device 33.

FIG. 7 illustrates a second mode of operation of the heat treatment system 1 in which the refrigerant circuit 2 simultaneously ensures the cooling of the passenger compartment and the heat treatment, in particular the cooling, of at least one element 61 of the traction chain. In this case, the element 61 of the powertrain under consideration is the electrical energy storage device 63. This operating mode allows, by way of example, simultaneous cooling of the passenger compartment of the vehicle and of the electrical energy storage device 63 during a driving phase, that is to say during a normal operation of the vehicle.

In such an operating mode, the path of the refrigerant fluid in circuit 2 is substantially identical to what was previously explained for the first operating mode, with reference to FIG. 6, with the difference that at least one of the heat exchangers thermally coupled to the storage device 63 of electrical energy is supplied with refrigerant fluid. In this case, the heat treatment system 1 being produced according to the first embodiment, it is the second heat exchanger 51 which is supplied with coolant.

Also, when the refrigerant fluid passes the main point of divergence 32, at low pressure and at low temperature, a first fraction of the refrigerant fluid is sent into the first branch 4 so as to pass through the first heat exchanger 41, then the device. accumulation 42, while a second fraction of refrigerant fluid is sent into the second branch 5, the at least partial opening of the second control member 112 of the flow rate of the refrigerant allowing its passage.

This second refrigerant fraction performs a heat exchange with the heat transfer fluid loop 6 within the second heat exchanger 51 so as to cool the heat transfer fluid. In the heat transfer fluid loop 6, the heat transfer fluid is circulated by the circulation means 62, it captures calories from the electrical energy storage device 63 which it then transfers to the refrigerant fluid within the second exchanger. thermal 51. The coolant thus cooled is returned to the electrical energy storage device 63 while the thermal conditions imposed by the element 61 of the traction chain electrical allow overheating of the refrigerant fluid leaving the second heat exchanger 51 which is then in the gaseous state. This overheating corresponds to an increase in the temperature of the refrigerant fluid above its saturation temperature at the same pressure. It is in this superheated state that the refrigerant fluid reaches the main point of convergence 31 and is then returned directly to the compression device 33 without first passing through a bottle or the accumulation device 42.

At the main point of convergence 31, the second fraction of superheated refrigerant fluid, resulting from the second branch 5, and the first fraction of refrigerating fluid close to the vapor saturating state (vapor content close to 0.95 for example), resulting from the first branch 4 and the accumulation device 42, mix before joining the compression device 33 with moderate overheating, such overheating contributing to raising the coefficient of performance of circuit 2. FIG. 8 illustrates a third mode of operation of the heat treatment system 1 in which the circuit 2 simultaneously implements the cooling of the passenger compartment, that is to say the air conditioning mode, and a heat treatment of the storage device 63 of electrical energy. This third operating mode is particularly suited to an operation of the electric energy storage device 63 generating a higher heating than that which can be observed during the usual operation of the vehicle, for example during a rapid charging of the storage device 63 d. 'electric energy. The present mode of operation is thus substantially identical to the second mode of operation, so reference may be made to the description given in relation to FIG. 7 which applies mutatis mutandis. The present mode of operation nevertheless differs from the previous one in that the third branch 10 is also supplied with coolant.

As previously explained, the cooling of the passenger compartment is implemented by the first heat exchanger 41 when the heat treatment system 1 is produced according to the first embodiment. The cooling of the electrical storage device 63 is here carried out jointly by the second heat exchanger 51 and by the third heat exchanger 102 within which the refrigerant fluid collects calories from the heat transfer fluid circulating in the loop 6, so to meet the increased need for cooling the electrical energy storage device 63.

In such a heat treatment system 1, the heat transfer fluid loop 6 can, for example, comprise at least the main pipe 600 on which are arranged the second heat exchanger 51, the circulation means 62 and the element 61 of the traction chain to be heat treated, here the storage device 63 of the electrical energy. Furthermore, the loop 6 may include at least a first pipe 610 which comprises the third heat exchanger 102 and is connected to the main pipe 600 of the loop 6 of heat transfer fluid. In a non-limiting manner, such a first pipe 610 can be arranged so that the second heat exchanger 51 and the third heat exchanger 102 are arranged, as illustrated, in parallel with one another.

Alternatively, the second heat exchanger 51 and the third heat exchanger 102 can be arranged in series with one another, on the same pipe of the heat transfer fluid loop 6.

Thus, at the level of the main point of divergence 32 of the refrigerant circuit 2, the first fraction of refrigerant and the second fraction of refrigerant are, as previously explained, respectively sent to the first branch 4 and to the second branch 5 while a third fraction of the refrigerant fluid is sent to the third branch 10, the at least partial opening of the third control member 113 of the circulation allowing the passage of the refrigerant fluid therein.

The first fraction and third fraction of refrigerant are then sent to the accumulation device 42, while the second fraction of refrigerant, superheated, bypasses it. The main point of convergence 31 thus receives a mixture of superheated and non-superheated refrigerant fluid which is then returned to the compression device 33.

Thus, in the second and third operating modes, the second heat exchanger 51 and / or the third heat exchanger 102 are operated according to the cooling demand of the element 61 of the electric traction chain. In the rolling phase, the cooling demand is low and the second heat exchanger 51, or the first heat exchanger 41 in the case of the second embodiment, can be used. In the rapid charge phase, the second heat exchanger 51, or the first heat exchanger 41, as well as the third heat exchanger 102, can jointly ensure the cooling of the storage device 63 of electrical energy. In each of these operating modes, the second heat exchanger 51 ensures at least partial superheating of the refrigerant fluid at the inlet of the compression device 33, thus contributing to an improvement in the operating cycle.

FIG. 9 represents a fourth mode of operation of the heat treatment system 1, in which the refrigerant fluid circuit 2 operates in passenger compartment heating mode. As previously explained, the refrigerant fluid is subjected to a high pressure and a high temperature in the compression device 33. It circulates along the main branch 3 up to the first point of divergence 71 at which, by virtue of the combination of the closing of the regulating element 35 of the flow of refrigerant included on the main branch 3 and the opening of the regulating means 74 included in the secondary branch 7, it is sent to the secondary branch 7.

The high pressure and high temperature refrigerant then passes through the secondary heat exchanger 73, used as a condenser, in which it transfers calories to the interior air flow FA2, colder, passing through said secondary heat exchanger 73. In doing so, the internal air flow FA2 thus heated is sent to the passenger compartment so as to ensure its heating while the refrigerant fluid, at least partially condensed, is sent to the first point of convergence 72.

In the example illustrated, the heat treatment system 1 implements the first variant as explained with reference to FIG. 4, also the management member 38 for the circulation of the refrigerant fluid is arranged on the main branch 3. The management unit 38 thus operates an expansion of the refrigerant fluid, which passes from high pressure and high temperature to low pressure and low temperature, prior to its passage at the level of the main point of divergence 32 and therefore prior to its distribution to at least the first branch 4 and / or the second branch and / or the third branch 10 and / or the tertiary branch 8. In the fourth operating mode, the refrigerant only partially supplies the first branch 4 and does not supply not the second branch 5 or the third branch 10, its circulation being hampered by the closing of the first control organ reads, second control organ 112 and third control organ 113 respectively.

The tertiary control member 114 is at least partially open so that the refrigerant fluid circulates in part on the first branch 4, between the main point of divergence 32 and the second point of divergence 81, then on the tertiary branch 8 up to at the second point of convergence 82 before being returned to the main branch 3.

The coolant then enters the main heat exchanger 34, functioning as an evaporator, and the coolant captures calories from the warmer outdoor air stream FAi. Advantageously, it will be noted that the direction of flow Si of the refrigerant within the main heat exchanger 34 is reversed with respect to the direction of flow observed in the first three operating modes.

The refrigerant fluid leaves the main heat exchanger 34 in the essentially gaseous state and passes the third point of divergence 91. The regulating device 93 of the flow rate of refrigerant fluid being at least partially open and the main check valve 36 being closed, the refrigerant circulates in the quaternary branch 9 to the third point of convergence 92 then joins the first branch 4 in order to be returned to the accumulation device 42 then to the compression device 33.

In such an operating mode, the refrigerant thus bypasses the first heat exchanger 41, the second heat exchanger 51 and the third heat exchanger 102.

FIG. 10 illustrates a fifth operating mode of the heat treatment system 1, for example implemented during the taxiing phase, in which the circuit 2 is simultaneously operated in the passenger compartment heating mode and in the cooling mode of the vehicle. element 61 of the electric traction chain.

Such an operating mode is substantially identical to the fourth operating mode also the description of the heat treatment system 1 made with reference to FIG. 9 is transposable and applies mutatis-mutandis to the present operating mode except for the differences mentioned above. after. Thus, the heating of the passenger compartment is here carried out by the secondary heat exchanger 73. Additionally and similarly to what has been explained for the second operating mode, in which the circuit 2 jointly ensures the cooling of the passenger compartment and of the electrical energy storage device 63, the cooling of the electrical storage device 63 is performed by the second heat exchanger 51 or by the first heat exchanger 41, depending on whether the heat treatment system 1 is produced according to the first embodiment or the second embodiment respectively.

In this case, the second control member 112 of the circulation of the refrigerant fluid is open, so that, when the refrigerant passes the main point of divergence 32 at low pressure and at low temperature, a first fraction of the refrigerant fluid is sent to the tertiary branch 8 and the main heat exchanger 34 while a second fraction of refrigerant fluid is sent to the second branch 5 in order to supply the second heat exchanger 51. In the second heat exchanger 51, the second fraction of refrigerant fluid collects calories from the electrical energy storage device 63 via the heat transfer fluid circulating in the loop 6. As previously explained, the refrigerant fluid leaves the second heat exchanger 51 overheated and in the gaseous state, such overheating raising the temperature of the second refrigerant fraction above its saturation temperature at the same pressure. At the main point of convergence 31, the second fraction of refrigerant, superheated, and the first fraction of refrigerant, coming from the main heat exchanger 34, mix before joining the compression device 33 with moderate overheating , such overheating contributing to raising the coefficient of performance of circuit 2.

When one of the heat exchangers, in this case the second heat exchanger 51, is used as a superheater such as has, for example, been explained in the second operating mode, the third operating mode or even the fifth operating mode. operation, respectively described with reference to FIGS. 7, 8 or 10, the temperature of the refrigerant fluid can be raised to values liable to reduce the performance of the heat treatment system 1 and a reduction in this temperature may be required. In order to ensure the maintenance of optimal performance of the heat treatment system 1 according to the invention, that can, as illustrated in FIG. 11, be configured in order to implement a method of adjusting a temperature of the fluid. refrigerant at the outlet of the compression device 33. It is understood that such a method can be applied to any one of the combinations of the embodiments, variants and alternatives described above.

Such an adjustment method comprises in particular at least: a first step of estimating the temperature of the refrigerant fluid at the outlet of the compression device 33; a second step of comparing the estimated temperature of the refrigerant fluid (FR) with at least one threshold temperature value; a third step of regulating the heat exchange implemented in the second heat exchanger 51 and / or regulating the circulation of the refrigerant fluid in the second branch 5 implemented when the estimated temperature of the refrigerant fluid (FR) is higher or equal to the temperature threshold value.

The temperature estimation step can, by way of example, be carried out by measuring the temperature and / or the pressure of the refrigerant fluid circulating in circuit 2. In particular, such a measurement can be carried out by a sensor. 39 temperature and / or pressure. Advantageously, such a measurement can be carried out downstream of the compression device 33 in the direction of circulation Si of the refrigerant fluid, for example on the main branch 3 between the compression device 33 and the first point of divergence 71.

The measurement taken is transmitted to a control unit 13 of the heat treatment system 1, which compares it with at least the temperature threshold value. For example, a coolant temperature threshold value could be of the order of H5 ° C. In the heat treatment system 1 illustrated, such data transmission is schematically represented by the thin dotted line 2000.

The control unit 13 can then, as required, implement the third step of the adjustment method. In the example illustrated in FIG. 11, this third step consists in regulating the heat exchange implemented in the second heat exchanger 51, that is to say in the heat exchanger operating as a superheater and bypassing the heat exchanger. accumulation device 42. The regulation of the heat exchange implemented within the second heat exchanger 51 aims in particular to increase the proportion of liquid phase of the refrigerant fluid leaving the second heat exchanger 51, for example in order to obtain a vapor content of the order of 0.80, so that, when the refrigerant fractions coming from the storage device 42 and from the second heat exchanger 51 mix at the level of the main point of convergence 31, the temperature of this mixture is lowered to values suitable for optimal operation of the heat treatment system 1, thus reducing the temperature of the refrigerant fluid measured downstream of the compression device 33. Such regulation is controlled by the control unit 13 and schematically represented by the thin dotted line 3000.

In particular, the third step of the adjustment method can comprise a sub-step of increasing the flow of refrigerant fluid circulating in the second branch 5. To this end, the control unit 13 can, by way of example, increase the flow of refrigerant fluid through the second control member 112 of the flow rate of refrigerant fluid, when the heat treatment system 1 is produced according to the first variant embodiment, or through the second management member 382 of the circulation, visible in FIG. 5 when the heat treatment system 1 is produced according to the second variant embodiment.

The third step of the adjustment process may include a sub-step of reducing the flow rate of the coolant or the flow rate of the internal air flow FA2 involved in the heat exchange implemented in the second heat exchanger 51.

In other words, when the heat treatment system 1 is produced according to the first embodiment and the second heat exchange is configured to be thermally coupled to the heat transfer fluid loop 6 comprising the element 61 of the traction chain , the third step of regulating the process can be implemented by reducing the flow rate of the heat transfer fluid circulating in the loop 6, for example by means of the circulation means 62, shown in FIG. 2.

Similarly, when the heat treatment system 1 is produced according to the second embodiment and the second heat exchanger 51 is configured to implement a heat exchange between the refrigerant fluid and the internal air flow FA2, the third step the temperature adjustment process refrigerant can be implemented by reducing the flow rate of this internal air flow FA2 through the second heat exchanger 51, as shown in Figure 3.

FIG. 12 illustrates a general representation of a particular example of an embodiment of the heat treatment system 1, such an alternative being able to be applied to the various examples and embodiment as previously described with reference to FIGS. 1 to 3, and this independently of the variant embodiment, shown in Figures 4 and 5, which it incorporates.

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

The first part 141 of the internal heat exchanger 14 is particularly fitted in a first portion 301 of the heat treatment system 1 which extends between the storage device 42 and the compression device 33 and in which the refrigerant fluid is subjected to low pressure and low temperature. In other words, the first part 141 of the heat exchanger is disposed downstream of the accumulation device 42 according to the direction of flow Si of the refrigerant fluid. The second part 142 of the internal heat exchanger 14 is arranged in a second portion 302 of the heat treatment system 1, in which the refrigerant fluid is subjected to a high pressure and a high temperature, which extends between the heat exchanger. main heat 34 and the main point of divergence 32, that is to say upstream of the circulation management member 38 configured to ensure the expansion and / or to regulate the flow of the refrigerant fluid.

In particular, the first part 141 of the internal heat exchanger 14 can be arranged on the first branch 4, between the storage device 42 and the main point of convergence 31, as shown in FIG. 12. In this way, when the heat treatment system operates according to one of the operating modes as previously explained with reference to Figures 7, 8 or 10, the refrigerant fluid leaving the second heat exchanger 51 bypasses the first part 141 of the internal heat exchanger 14 while than the fluid refrigerant leaving the first heat exchanger 41 and / or the third heat exchanger 102 and / or the main heat exchanger 34 is fed to the first part 141 of the internal heat exchanger 14.

Alternatively, the first part 141 of the internal heat exchanger 14 can be interposed between the main point of convergence 31 and the compression device 33, such an alternative being represented by the first part 141 'of the internal heat exchanger 14 , shown in Figure 13. In such an alternative, the refrigerant fluid 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 fed to the first part 141 of the internal heat exchanger 14.

Such an internal heat exchanger 14 allows the recovery of calories from a portion of the refrigerant circuit 2, here the second portion 302, high pressure, to exchange them with another portion of this same circuit 2, here the first portion 301, low pressure, so as to reduce the power consumed by the compression device 33 and overall increase the performance of the refrigerant fluid circuit 2, in particular when the heat treatment system 1 operates according to any one of the first, second or third modes of operation as previously described with reference to Figures 6, 7 or 8.

The internal heat exchanger 14 being disposed between two portions 301, 302 of circuit 2 having a temperature differential between them, it is understood that it thus allows heat exchange between its two parts 141, 141 ', 142 and therefore between the two portions 301, 302 of the refrigerant fluid circuit 2 on which these parts 141, 141 ', 142 of the internal heat exchanger 14 are arranged. In the example illustrated, the internal heat exchanger 14 advantageously allows, on the one hand, the heating of the refrigerant fluid upstream of the compression device 33 so that this refrigerant fluid is exclusively in gaseous form when it reaches the inlet of the compression device 33 and on the other hand to cool the refrigerant fluid upstream of the 'member 38 for managing the circulation of the refrigerant, and this independently of the variant implemented, so that the pressure drop operated by this member 38 is facilitated. When the heat treatment system 1 comprises such a heat exchanger and the second heat exchanger 51 is capable of operating as a superheater, for example when the circuit 2 operates according to any one of the second, third or fifth operating modes as described with reference to FIGS. 7, 8 or 10, it may be necessary to ensure the regulation of the circulation of the refrigerant fluid as a function of the temperature of the refrigerant fluid. In particular, when it is necessary to increase the superheating of the refrigerant fluid, it may be necessary to send the refrigerant fluid leaving the second heat exchanger 51 through the first part 141, 141 'of the internal heat exchanger 14 in order to that it captures the calories of the refrigerant fluid circulating in the second part 142 of the internal heat exchanger 14. Conversely, when the temperature of the refrigerant fluid rises to values liable to reduce the performance of the cooling system. heat treatment 1, it is necessary for the refrigerant fluid leaving the second heat exchanger 51 to bypass the first part 141, 141 'of the internal heat exchanger 14.

The heat treatment system 1 can then be configured so as to implement the temperature adjustment method as previously explained, the description of the temperature adjustment method as well as the components of the heat treatment system 1 described. with reference to FIG. 11 which can be transposed to the present alternative embodiment. In particular, the heat treatment system 1 comprises at least the temperature and / or pressure sensor 39 as well as the control unit 13.

Furthermore, as illustrated in FIG. 12, when the first part 141 of the internal heat exchanger 14 is arranged between the storage device 42 and the main point of convergence 31, the heat treatment system 1 may comprise at at least one bypass branch 15, configured to send at least part of the refrigerant fluid leaving the second heat exchanger 51 to the first part 141 of the internal heat exchanger 14.

Said branch 15 of the refrigerant fluid extends between a branch point 151 and a connection point 152. The branch point 151 is disposed on the second branch 5, between the second heat exchanger 51 and the main point of convergence 31 , while the connection point 152 is arranged on the first main branch 4, between the storage device 42 and the first part 142 of the internal heat exchanger 14.

When the heat treatment system is in operation, the refrigerant fluid leaving the second heat exchanger 51 can thus be sent to the bypass branch 15 and / or continue to circulate on the second branch 5, to the main point of convergence 31.

Alternatively, when the first part 141 ′ of the internal heat exchanger 14 is arranged between the main point of convergence 31 and the compression device 33, according to the alternative illustrated in FIG. 13, the bypass branch 15 of the refrigerant fluid can extend between the bypass point 151, here disposed between the second heat exchanger 51 and the main point of convergence 31, and the connection point 152, here disposed in the main branch 3, between the first part 141 'of the internal heat exchanger 14 and the compression device 33 so as to bypass the first part 141 'of said internal heat exchanger 14 and thus contribute to the regulation of the temperature of the refrigerant fluid if necessary.

Optionally, the circulation of the refrigerant fluid leaving the second heat exchanger 51 can be regulated. As illustrated in FIGS. 12 and 13, the heat treatment system 1 can thus comprise at least one regulator 153, 154 of the flow of refrigerant fluid arranged on the bypass branch 15 and / or between the bypass point 151 and the main point of convergence 31 on the second branch 5.

For example, as illustrated in FIG. 12, the heat treatment system 1 can comprise the member for regulating the flow of refrigerant fluid, called the first regulator member 153, arranged on the bypass branch 15, and at least one second regulator 154 of the flow of refrigerant fluid, disposed between the bypass point 151 and the main point of convergence 31, these regulators 153, 154 being configured to selectively direct the refrigerant circulating in the second branch 5 towards the bypass branch 15 then to the first part 141 of the internal heat exchanger 14 and / or to the main branch 3. Advantageously, such regulators 153, 154 can be configured to regulate the flow of the refrigerant fluid. According to an alternative not shown, the heat treatment system 1 could include a single refrigerant fluid flow regulator, for example a multi-way valve, arranged at the bypass point 151.

Also, according to an alternative not shown, the heat treatment system 1 can be devoid of the regulating member (s) 153, 154 as described above. The refrigerant fluid leaving the second heat exchanger 51 then circulates simultaneously in the bypass branch 15 and in the second branch 5 in the direction of the main point of convergence 31. In such an alternative, the bypass branch can comprise a pipe with a diameter less than that of a pipe used for the second branch 5 and / or for the main branch 3 so as to regulate the distribution of the coolant.

Thus, when the heat treatment system 1 comprises the internal heat exchanger 14 arranged as previously explained with reference to FIG. 12, the third step of the process for adjusting the temperature of the refrigerant fluid can be carried out by regulating the temperature. heat exchange carried out in the second heat exchanger 51, as previously described with reference to FIG. 11, and / or by regulating the circulation of the refrigerant fluid in the second branch 5, that is to say by controlling , as needed, the path of the refrigerant circulating in the second branch 5 either towards the main branch 3 and the main point of convergence so as to bypass the storage device 42 and the first part 141 of the internal heat exchanger 14 , or to the bypass branch 15 so as to send at least part of the refrigerant fluid through said first part 141 of the internal heat exchanger 14.

By way of example, in the heat treatment system 1 as illustrated in FIG. 14, the control unit 13 can regulate: the flow of the refrigerant fluid circulating in the second branch 5, for example by means of the second control member 112 or second management member 382, visible in Figures 4 and 5, depending on the variant implemented, and / or;

- The flow rate of the heat transfer fluid or of the internal air flow FA2, depending on the embodiment used, involved in the heat exchange taking place in the second heat exchanger 51 and / or;

- the flow of the refrigerant fluid in the second branch 5, through the first regulator 153 and the second control member regulation 154, such a control being represented by the thin dotted line 4000.

By way of example, when the temperature of the refrigerant fluid estimated downstream of the compression device 33 is greater than the defined threshold value, the control unit 13 can adjust the temperature of the refrigerant fluid downstream of the compression device 33 by increasing the flow rate of the refrigerant fluid circulating in the second heat exchanger 51, thus increasing the portion of the liquid phase of the fraction of refrigerant fluid circulating in the second secondary branch 5. The control unit 13 can then, according to need, also control the flow of this same fraction of refrigerant fluid by closing the first regulator 153 and by opening the second regulator 154. The refrigerant fraction from the second heat exchanger 51 then bypasses the first part 141 of the internal heat exchanger 14 and does not capture calories from the refrigerant circulating in the second part 142 of said internal heat exchanger 14. At the point of convergence 31, this fraction of refrigerant fluid mixes with the refrigerant fraction (s) from the first heat exchanger 41 and / or the third heat exchange and / or the main heat exchanger 34 passing through the storage device 42 and through the first part 141 of the internal heat exchanger 14, thus lowering the temperature of the refrigerant mixture upstream of the compression device 33 and thus allowing also to lower the temperature of the coolant downstream of the compression device 33 to values suitable for optimizing the performance of the heat treatment system 1.

Conversely, if it is necessary to superheat the refrigerant fluid, and therefore to send the fraction of refrigerant fluid leaving the second heat exchanger 51 through the first part 141 of the internal heat exchanger 14, and therefore in the bypass branch 15, the control unit 13 can then control the flow of this same fraction of refrigerant fluid by opening the first regulating member 153 and closing the second regulating member 154.

It is understood that the characteristics relating to the regulator (s) 153, 154 as well as to the implementation of the method for adjusting the temperature of the refrigerant fluid may extend mutatis mutandis to the alternative of the system. of heat treatment 1 illustrated in Figure 13. It will be understood from the foregoing that the present invention relates to a heat treatment system comprising a refrigerant fluid circuit making it possible to ensure simply and without excess consumption the heat treatment of at least one element of an electric power train. a vehicle, such as an electrical energy storage device configured to supply electrical energy to an electric drive motor of the vehicle, as well as the heat treatment of a passenger compartment of said vehicle. The coefficient of performance of the heat treatment system according to the invention is thus improved, in particular when the requirements, in particular for cooling, are greater than the usual requirements of the vehicle. The invention also relates to a method for adjusting the temperature of the refrigerant fluid circulating in such a treatment system so as to optimize its performance.

The invention cannot, however, be limited to the means and configurations described and illustrated here, and it also extends to all equivalent means or configurations and to any technically operative combination of such means. In particular, the architecture of the refrigerant circuit can be modified without harming the invention insofar as it ultimately fulfills the functions described in this document.

Claims

1. Heat treatment system (î) intended for a vehicle and comprising at least one circuit (2) of refrigerant fluid (FR) which comprises a main branch (3) extending between a main point of convergence (31) and a main point of divergence (32), and at least a first branch (4) and a second branch (5) which extend between the main point of divergence (32) and the main point of convergence (31), in parallel l 'one from the other and in series with the main branch (3): the main branch (3) comprising at least one compression device (33) and a main heat exchanger (34) configured to implement a heat exchange between the coolant (FR) and a flow of air (FAi) outside a vehicle interior; the first branch (4) comprising a first heat exchanger (41) and a device (42) for accumulating the refrigerant fluid (FR), the accumulating device (42) being arranged between the first heat exchanger (41) and the main point of convergence (31); the second branch (5) comprising a second heat exchanger (51); the circuit (2) of refrigerant fluid (FR) comprising a secondary branch (7) which extends between a first point of divergence (71), arranged on the main branch (3) between the compression device (33) and the 'main heat exchanger (34), and a first point of convergence (72), disposed on the main branch (3) between the main heat exchanger (34) and the main point of divergence (32), and the branch secondary (7) comprising a secondary heat exchanger (73) configured to implement a heat exchange between the refrigerant fluid (FR) and an interior air flow (FA2) sent into the vehicle cabin.

2. Heat treatment system (1) according to the preceding claim, wherein at least one of the first heat exchanger (41) and second heat exchanger (51) is thermally coupled to a loop (6) of heat transfer fluid comprising at least an element (61) of an electric traction chain of the vehicle and at least the other of the first heat exchanger (41) and second heat exchanger (51) is configured to implement a heat exchange between the refrigerant fluid (FR) and an interior air flow (FA2) to the passenger compartment.

3. Heat treatment system (I) according to claim i or 2, wherein the secondary branch (7) comprises at least one regulating means (74) of the flow of refrigerant fluid (FR) and / or a non-return valve. secondary (75).

4. Heat treatment system (1) according to one of the preceding claims, comprising at least: a tertiary branch (8) which extends between a second point of divergence (81), disposed between the main heat exchanger ( 34) and the first heat exchanger (41), and a second point of convergence (82), disposed on the main branch (3) between the first point of divergence (71) and the main heat exchanger (34); a quaternary branch (9) which extends between a third point of divergence (91), disposed on the main branch (3) between the main heat exchanger (34) and the first point of convergence (72), and a third point of convergence (92), arranged on the first branch (4) between the first heat exchanger (41) and the storage device (42), the quaternary branch (9) comprising at least one regulating device (93) of the refrigerant fluid flow (FR).

5. Heat treatment system (1) according to one of the preceding claims, wherein the main branch (3) comprises at least one main non-return valve (36), arranged between the main heat exchanger (34) and the first point of convergence (72).

6. Heat treatment system (1) according to one of the preceding claims, comprising a third branch (10) which extends between the main point of divergence (32) and a fourth point of convergence (101), arranged on the first branch (4) between the first heat exchanger (41) and the storage device (42), the third branch (10) comprising at least a third heat exchanger (102).

7. Heat treatment system (1) according to one of the preceding claims, comprising at least one tertiary heat exchanger (37) configured to implement a heat exchange between the refrigerant fluid (FR) and the outside air flow. (FA2) to the passenger compartment of the vehicle, the tertiary heat exchanger (37) being arranged on the main branch (3) between the main heat exchanger (34) and the main point of divergence (32) and the tertiary heat exchanger (37) being arranged upstream of the main heat exchanger (34) in the direction of circulation (S2) of the flow of outside air (FAi).

8. Heat treatment system (1) according to any one of the preceding claims comprising at least one management member (38) of the circulation configured to operate an expansion of the refrigerant fluid (FR) and / or to interrupt the circulation of the fluid. refrigerant (FR) therethrough and disposed between the first point of convergence (72) and the main point of convergence (31).

9. Heat treatment system (1) according to the preceding claim, wherein the management member (38) of the circulation is arranged on the main branch (3), the heat treatment system (1) comprising at least one member. control (11) of the flow of refrigerant fluid (FR) disposed on the first branch (4) and / or on the second branch (5) between the management member (38) and the main point of convergence (31).

10. Heat treatment system (1) according to claim 8, comprising a plurality of management members (38) of the circulation of the refrigerant fluid (FR), at least the management member (38) of the circulation, called. hereinafter the first management unit (381) of the circulation being arranged in the first branch (4), between the main point of divergence (32) and the first heat exchanger (41), and a second management unit (382) the circulation being disposed on the second branch (5), between the main point of divergence (32) and the second heat exchanger (51).

11. Heat treatment system (1) according to one of claims 8 to 10, comprising a distribution module (12) of the refrigerant fluid (FR), the distribution module (12) comprising at least one housing (121) delimiting an internal volume (122) in which are arranged the main point of divergence (32) and at least one management member (38) of the circulation of the refrigerant fluid (FR).

12. Heat treatment system (1) according to any one of the preceding claims, comprising at least one internal heat exchanger (14) configured to implement a 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 included in a first portion (301) of the heat treatment system (1) which s 'extends between the device accumulator (42) and the compression device (33), and the second part (142) of the internal heat exchanger (14) being included in a second portion (302) of the heat treatment system (1) which s 'extends between the main heat exchanger (34) and the main point of divergence (32).

13. Heat treatment system (1) according to the preceding claim, wherein the first part (141) of the internal heat exchanger (14) is disposed between the storage device (42) and the main point of convergence (31). ), the heat treatment system (1) comprising a bypass branch (15) of the refrigerant fluid (FR) which extends between a bypass point (151), arranged between the second heat exchanger (51) and the main point convergence (31), and a connection point (152), arranged between the storage device (42) and the first part (141) of the internal heat exchanger (14).

14. Heat treatment system (1) according to claim 12, wherein the first part (141 ') of the internal heat exchanger (14) is arranged between the main point of convergence (31) and the compression device (33). ), the heat treatment system (1) comprising a bypass branch (15) of the refrigerant fluid (FR) which extends between a bypass point (151), arranged between the second heat exchanger (51) and the main point convergence point (31), and a connection point (152), arranged between the first part (141 ') of the internal heat exchanger (14) and the compression device (33).

15. A method of adjusting a temperature of the refrigerant fluid (FR) at the outlet of the compression device (33) equipping a heat treatment system (1) according to any one of the preceding claims, the adjustment method comprising:

A first step of estimating the temperature of the refrigerant fluid (FR) at the outlet of the compression device (33);

A second step of comparing the estimated temperature of the refrigerant fluid (FR) with at least one threshold temperature value;

A third step of regulating the heat exchange implemented in the second heat exchanger (51) and / or regulating the circulation of the refrigerant fluid (FR) in the second branch (5) implemented when the estimated temperature of the refrigerant (FR) is greater than or equal to the temperature threshold value.

16. Adjustment method according to the preceding claim, wherein the third step comprises at least one sub-step of increasing the flow of refrigerant fluid (FR) circulating in the second branch (5).

17. The adjustment method according to claim 15 or 16, wherein the second heat exchanger (51) is thermally coupled to the heat transfer fluid loop (6) or the second heat exchanger (51) is configured to implement an exchange. thermal between the coolant (FR) and the flow of air inside (FA2) in the passenger compartment, the third stage comprising at least one substep of reducing the flow rate of the heat transfer fluid or the flow rate of the flow of interior air ( FA2) involved in the heat exchange implemented in the second heat exchanger (51).