FR3080329A1 - REFRIGERANT FLUID CIRCUIT FOR VEHICLE, ADAPTED TO A QUICK CHARGE OF AN ELECTRIC STORAGE DEVICE - Google Patents

Abstract

The invention relates to a refrigerant circuit (3) comprising a main pipe (5) comprising a first heat exchanger (9) arranged to be traversed by an external air flow (FE) to a passenger compartment, a first branch (13) comprising a second heat exchanger (18) configured to thermally treat an air flow (FA) sent into the passenger compartment, a second branch (14) comprising a heat exchanger (21) thermally coupled to a cooling device electrical storage (2), a third limb (6) comprising a first compression device (7), a fourth limb (35) comprising a second compression device (37), and a refrigerant distribution device (22) ( FR) having a first port (29) connected to an input (34) of the first compression device (7) and a second port (30) connected to an output (38) of the second compression device (37). Application to motor vehicles.

Description

The field of the present invention is that of refrigerant circuits for vehicles, in particular for motor vehicles.

Motor vehicles are commonly equipped with a refrigerant circuit used to heat or cool different areas or components of the vehicle. It is particularly known to use this refrigerant circuit to thermally treat an air flow sent into the passenger compartment of the vehicle equipped with such a circuit.

In another application of this circuit, it is known to use it to cool an electrical storage device of the vehicle, the latter being used to supply energy to an electric motor capable of setting the vehicle in motion. The refrigerant circuit thus provides the energy capable of cooling the electrical storage device during its use in taxiing phases. The refrigerant circuit is thus dimensioned to cool this electrical storage device.

When this refrigerant circuit simultaneously performs heat treatment of the passenger compartment and heat treatment of the storage device, it is subjected to very high stresses which bring the circuit to the limits of its capacities. This is particularly the case when the electrical storage device is used in a way which causes it to heat up considerably. An example of this situation is in particular a rapid charging phase of the storage device. It consists in charging the electrical storage device under 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 charge involves heating of the electrical storage device which must be treated. Furthermore, consideration must be given to the possibility of maintaining an acceptable level of thermal comfort inside the passenger compartment, either because the occupants of the vehicle remain inside the vehicle all or part of the charging time mentioned above, either to anticipate the return of these occupants and to avoid any thermal inconvenience. It is also necessary to heat treat the passenger compartment during this rapid charge to maintain acceptable conditions of comfort, especially when the temperature outside the vehicle exceeds 30 ° C. These two requests for cooling imply a dimensioning of the system which makes it not very compatible with the constraints of current motor vehicles, in particular vehicles powered by an electric motor. The technical problem therefore resides in the capacity on the one hand to dissipate the calories generated by the electrical storage device during rapid charging, and on the other hand to cool the passenger compartment, by limiting consumption and / or space and / or the noise pollution of a system capable of simultaneously fulfilling these two functions.

The invention falls within this context and proposes a technical solution which contributes to the achievement of this double objective, that is to say to keep the electrical storage device below a threshold temperature during rapid charging. and cool the passenger compartment of the vehicle, by means of a coolant circuit cleverly designed to operate with two compression devices, implementing them one or the other, or alternatively or simultaneously in circuit configurations refrigerant making them work in parallel or in series.

The invention therefore relates to a refrigerant circuit of a vehicle comprising at least one main pipe comprising a first portion and a second portion, the main pipe being arranged in series with a first branch and a second branch, the first branch and the second branch being in parallel and arranged between the first portion and the second portion, the first portion of the main pipe comprising a first heat exchanger arranged to be traversed by a flow of air outside a passenger compartment of the vehicle, the first branch comprising a first expansion member and a second heat exchanger configured to heat treat a flow of air sent into the passenger compartment of the vehicle, the second branch comprising a second expansion member and a heat exchanger thermally coupled to a device vehicle electrical storage system, the refrigerant circuit comprising a third branch which comprises a first compression device and a fourth branch which comprises a second compression device, characterized in that the refrigerant circuit comprises a five-way refrigerant distribution device, a first port of the refrigeration device distribution being connected to an input of the first compression device, a second port of the distribution device being connected to an output of the second compression device.

It is thus possible to operate the first compression device and the second compression device, simultaneously or alternately, according to thermal needs. This configuration notably meets the high thermal requirements. For example, the thermal requirements are high when the refrigerant circuit operates in cabin cooling mode and in rapid charge mode while the occupants remain in the vehicle and it is then necessary to cool the cabin. Thermal requirements are also high when it is necessary to quickly reduce the temperature of the passenger compartment, when pre-conditioning the passenger compartment, or to maintain air conditioning in the passenger compartment when the outside temperatures are high. The invention also makes it possible to put the first compression device and the second compression device into operation when a rapid charge phase of the electrical storage device is activated.

The second compression device is independent of the first compression device in the sense that one of the compression devices can be active while the other compression device is inactive, or else simultaneously rotate at different rotational speeds. Thus, the first compression device and the second compression device are configured to induce equal or distinct compression levels of the refrigerant.

This organization avoids sizing components, in particular the compression device, for use phases known as rapid charge ultimately short compared to the use phases known as rolling, where the energy requirement is lower.

This organization of the refrigerant circuit also makes it possible to limit the noise nuisance, by operating the first compression device and the second compression device at speeds below an acceptable acoustic threshold, which would not be the case with a single device. compression which would then impose a very high speed of rotation during rapid charging, and consequently an acoustic nuisance for the occupants remaining in the vehicle.

The first compression device and the second compression device are for example compressors, and the invention finds a very particular application when the compressors are electric compressors with fixed displacement and variable speed. It is thus possible to control the thermal power of the refrigerant circuit according to the invention.

The five-way coolant distribution device is configured to pass through the coolant. The five-way coolant distribution device includes one or more inlets and one or more outlets corresponding to ports specific to the distribution device. The first port, when open, is an output from the dispatch device. The distribution device thus supplies refrigerant to the third branch via the first port. The second port, when open, is an input to the dispatcher. The distribution device is then supplied with refrigerant by the fourth branch via the second port. The distribution device is for example a five-way valve. This five-way valve is for example with rotary valves.

Within the distribution device coexist five channels configured to be used by the refrigerant. These channels, internal to the distribution device, are open or closed, so as to allow or prevent the circulation of the refrigerant. Each channel extends between at least two ports of the distribution device. The opening of these channels causes the refrigerant to be directed from one or more inlets to one or more outlets from the distribution device.

The refrigerant is for example a subcritical fluid, such as that known under the reference R134A or R1234YL. Alternatively, the fluid can be super-critical, such as carbon dioxide whose reference is R744.

The refrigerant circuit according to the invention is a closed circuit which implements a thermodynamic cycle. The first branch is in parallel with the second branch, seen from the refrigerant.

The first heat exchanger can be installed on the front of the vehicle. This first heat exchanger can thus be used as a condenser, or gas-cooled in the case of a super-critical fluid.

The heat exchanger is configured to heat treat an electrical storage device in the vehicle. It is therefore specially dedicated to this electrical storage device and does not have the function of cooling another component. The first heat exchanger exchanges calories between the coolant and the vehicle's electrical storage device, either directly, i.e. by convection between the first exchanger and the electrical storage device, or indirectly via a fluid loop coolant, the latter being intended to transport the calories from the electrical storage device to a third heat exchanger. It is therefore understood that the cooling of the electrical storage device can be indirect. Alternatively, the first heat exchanger can be in contact with the electrical storage device. In such a case, the cooling of the electrical storage device is direct.

According to one aspect of the invention, the refrigerant circuit comprises a first connection point and a second connection point between which the first branch and the second branch extend, a third port of the distribution device being connected to the second point connection by the second portion of the main pipe.

The first connection point is the area of the refrigerant circuit where the first portion of the main pipe separates in two, forming the first branch and the second branch. The first connection point therefore connects the first portion of the main pipe to the first branch and to the second branch. Viewed from the refrigerant, the first connection point allows the refrigerant circuit to diverge.

The second connection point is the area of the refrigerant circuit where the first branch and the second branch join, to form the second portion of the main pipe. The second connection point therefore connects the first branch, the second branch and the second portion of the main pipe. Seen from the refrigerant, the second connection point allows the refrigerant circuit to converge.

The second portion of the main pipe extends between the second connection point and the third port of the distribution device. The third port, when open, is an input to the dispatcher. The distribution device is then supplied with refrigerant by the second portion of the main pipe via the third port.

According to one aspect of the invention, a fifth branch extends between a fourth port of the distribution device and a third connection point, the third connection point connecting the first portion of the main pipe, the third branch and the fifth branch .

The fifth branch is in parallel with the third branch between the distribution device and the third connection point.

The third connection point is the area of the refrigerant circuit where the third branch and the fifth branch join, to join the first portion of the main pipe. Viewed from the refrigerant, the third connection point allows the refrigerant circuit to converge.

The fourth port, when open, is an output from the splitter. The distribution device then supplies refrigerant to the fifth branch via the fourth port.

According to one aspect of the invention, a sixth branch is included between the fourth branch and a fifth port of the distribution device.

The fifth port, when open, is an input to the dispatcher. When the fifth port is an inlet, the sixth branch and the fourth branch are in parallel from the point of view of the refrigerant. The distribution device is then supplied with refrigerant by the sixth branch via the fifth port.

Alternatively, the fifth port, when open, is an output from the distribution device. When the fifth port is an outlet, the sixth branch and the fourth branch are in series from the point of view of the refrigerant. The distribution device then supplies refrigerant to the sixth branch via the fifth port.

According to one aspect of the invention, the distribution device comprises a first channel which extends between the first port of the distribution device and the second port of the distribution device.

The first channel is configured to supply the first compression device. The first route connects the third branch to the fourth branch. Thus, the third branch, the first channel and the fourth branch are in series. When the first port and the second port are open, the first compression device is in series with respect to the second compression device using this first channel.

According to one aspect of the invention, the distribution device comprises a second channel which extends between the second port of the distribution device and the fourth port of the distribution device.

The second route connects the fourth branch and the fifth branch. Thus, the fourth branch, the second track and the fifth branch are in series. When the second port and the fourth port are open, the second compression device is in parallel with the first compression device by this second channel.

When the first channel is open, the second channel is closed, and vice versa. The first channel and the second channel can be closed at the same time, but are not opened simultaneously.

According to one aspect of the invention, the distribution device comprises a third channel which extends between the third port of the distribution device and the first port of the distribution device.

The third channel is configured to supply the first compression device. The third track connects the second portion of the main pipe to the third branch. Thus, the second portion of the main pipe, the third track and the third branch are in series. When the third port and the first port are open, the first compression device is in parallel with the second compression device using this third channel.

When the first channel is open, the third channel is closed, and vice versa. The first channel and the third channel can be closed at the same time, but are not opened simultaneously.

The second channel and the third channel can be opened simultaneously. The third channel can be opened while the second channel is closed. The second channel is closed when the third channel is closed.

According to one aspect of the invention, the distribution device comprises a fourth channel which extends between the third port of the distribution device and the fifth port of the distribution device.

The fourth channel is configured to supply the second compression device. The fourth track connects the second portion of the main pipe to the sixth branch. In this configuration, the fifth port is an output of the distribution device. Thus, the second portion of the main pipe, the fourth track and the sixth branch are in series. When the third port and the fifth port are open, the first compression device is alternately in series or in parallel with the second compression device using this fourth channel, depending on the state of opening of the other channels.

The first channel and the fourth channel can be opened simultaneously. Alternatively, the first channel can be opened while the fourth channel is closed.

The second channel and the fourth channel can be opened simultaneously. Alternatively, the fourth channel can be opened while the second channel is closed. The second channel is closed when the fourth channel is closed. Alternatively, when the second channel is open, the fourth channel is open.

The third channel and the fourth channel can be opened simultaneously. Alternatively, the fourth channel can be opened while the third channel is closed.

According to one aspect of the invention, the distribution device comprises a fifth channel which extends between the fifth port of the distribution device and the first port of the distribution device.

The fifth channel is configured to supply the first compression device. The fifth track connects the second portion of the main pipe to the third branch. In this configuration, the fifth port is an input of the distribution device. Thus, the second portion of the main pipe, the fifth track and the third branch are in series. When the fifth port and the first port are open, the first compression device is in parallel with the second compression device using this fifth channel.

When the first channel is open, the fifth channel is closed, and vice versa. The first channel and the fifth channel can be closed at the same time, but are not opened simultaneously.

When the second channel is open, the fifth channel is closed, and vice versa. The second lane and the fifth lane can be closed at the same time, but are not opened simultaneously.

When the fourth channel is open, the fifth channel is closed, and vice versa. The fourth lane and the fifth lane can be closed at the same time, but are not opened simultaneously.

The fifth lane and the third lane can be opened simultaneously. The third channel can be opened while the fifth channel is closed. When the third lane is closed, so is the fifth.

According to one aspect of the invention, the third branch comprises a first non-return valve configured to allow the circulation of the coolant from the first compression device to the first heat exchanger.

During the implementation of the invention, the first non-return valve imposes on the refrigerant a direction of flow in the third branch. Thanks to the first non-return valve, the refrigerant flows from the first port of the distribution device to the third connection point. Reverse traffic, i.e. from the third connection point to the first compression device, is blocked.

According to one aspect of the invention, the fifth branch comprises a second non-return valve configured to allow the circulation of the coolant from the fourth port of the distribution device to the first heat exchanger.

During the implementation of the invention, the second non-return valve imposes on the refrigerant a direction of circulation in the fifth branch. Thanks to the second non-return valve, the refrigerant flows from the fourth port of the distribution device to the third connection point. Reverse traffic, i.e. to the fourth port of the dispatcher, is blocked.

According to one aspect of the invention, the first branch comprises a third check valve located downstream of the second heat exchanger and configured to allow the circulation of the coolant from the second heat exchanger to the third port of the distribution device.

During the implementation of the invention, the third check valve imposes on the refrigerant a direction of flow in the first branch. Thanks to the third non-return valve, the fluid circulates from the second heat exchanger to the second portion of the main pipe. Reverse traffic, i.e. from the second portion of the main line to the second heat exchanger, is blocked.

According to one aspect of the invention, the refrigerant circuit comprises an internal heat exchanger with two passes, a first pass being located between the first connection point and the first expansion member and a second pass being located between the exchanger and the second connection point.

The internal heat exchanger includes two passes making up the refrigerant circuit. When the refrigerant circulates in each of the passes, that is to say when the refrigerant circulates in the first branch and in the second branch, a thermal transfer takes place between the refrigerant present in one and the other pass . Under these conditions, the refrigerant present in the first pass is at high pressure and at high temperature, while the refrigerant present in the second pass is at low pressure and at low temperature.

According to one aspect of the invention, the internal heat exchanger is a first internal heat exchanger, the refrigerant circuit comprising a second internal heat exchanger with two layers, the first layer being located on the first branch between the first connection point and the first pass, and the second ply being located on the second branch between the second expansion member and the heat exchanger.

The two layers of the second internal heat exchanger constitute the refrigerant circuit. The second internal heat exchanger also implements a heat exchange between the refrigerant circulating in the first branch and that of the second branch. Under these conditions, the refrigerant present in the first sheet is at high pressure and at high temperature, while the refrigerant present in the second sheet is at low pressure and at low temperature.

Seen from the refrigerant, the second internal heat exchanger is upstream of the first internal heat exchanger. The first pass and the first layer are arranged so that the refrigerant circulates first in the first layer and then in the first pass. The second pass and the second layer are arranged so that the refrigerant circulates first in the second layer and then in the second pass. It will be noted that the first ply and the first pass are arranged in series in the first branch, and the second ply and the second pass are arranged in series in the second branch.

The presence of two internal heat exchangers implements successive heat exchanges. These exchanges take place between the first branch and the second branch and make it possible to optimize the thermal distribution of the refrigerant fluid circuit, between these two parallel branches serving respectively the second heat exchanger and the heat exchanger.

The invention also relates to a vehicle heat treatment system comprising the refrigerant circuit as described above and a circulation loop of heat transfer fluid comprising a third heat exchanger configured to heat exchange with at least one electrical storage device for the vehicle, the heat exchanger being configured to be traversed by the refrigerant and by the heat transfer fluid.

Other characteristics, details and advantages of the invention will emerge more clearly on reading the description given below by way of indication in relation to the drawings in which:

- Figure 1 is a schematic view of the refrigerant circuit according to the invention, in a first embodiment,

FIG. 2 is a schematic view of the refrigerant circuit according to the invention, in a second embodiment,

FIGS. 3 to 5 schematically illustrate the refrigerant circuit shown in FIG. 2, operated according to different operating modes consisting in cooling the passenger compartment and the electrical storage device,

FIGS. 6 and 7 schematically illustrate the refrigerant circuit shown in FIG. 2, operated according to different operating modes consisting in cooling the passenger compartment without thermally treating the electrical storage device,

- Figures 8 and 9 schematically illustrate the refrigerant circuit shown in Figure 2, operated in different modes of operation consisting of cooling the electrical storage device without heat treating the passenger compartment.

It should first be noted that the figures show the invention in detail to implement the invention, said figures can of course be used to better define the invention if necessary. These figures are schematic representations which illustrate how the refrigerant circuit is made, what makes it up and how the refrigerant circulates within it. In particular, the refrigerant circuit according to the invention mainly comprises two refrigerant compression devices, a five-way refrigerant distribution device, heat exchangers, expansion members, pipes connecting each of these components, and optionally valves or flap.

The terms upstream and downstream used in the following description refer to the direction of circulation of the fluid considered, that is to say the refrigerant, an air flow sent to a passenger compartment of the vehicle or an external air flow to a passenger compartment of the vehicle.

For FIGS. 3 to 9, in the coolant circuit and in the heat transfer fluid circulation loop, lines symbolizing pipes connecting the components are full when they illustrate the circulating fluid, while dotted lines show an absence of circulation of said fluid. In the refrigerant circuit represented in FIGS. 3 to 9, the refrigerant is symbolized by a long arrow which illustrates a direction of circulation of the latter in the pipe considered. Thick lines and a solid arrow are used to symbolize a refrigerant in a state of high pressure and high temperature. Thin lines and a hollow arrow correspond to a fluid in a state of low pressure and low temperature.

In the heat transfer fluid circulation loop illustrated in FIGS. 3 to 9, the heat transfer fluid is symbolized by a short arrow which illustrates its direction of circulation in the pipe considered.

The different components are explained below according to a direction of circulation of the fluid considered, that is to say the refrigerant fluid or the heat transfer fluid. In addition, the designations "first", "second", "third", ... have no hierarchical value or vis-à-vis their succession. These designations are only intended to distinguish the components of the refrigerant circuit.

Referring first to Figure 1, there is shown a heat treatment system 1 according to the invention, in a first embodiment. This heat treatment system 1 is capable of operating in a mode making it possible to ventilate and air condition a passenger compartment of a vehicle in parallel with a heat treatment of an electrical storage device 2 of the vehicle in a fast charge situation. This is for example the case when the occupants of the vehicle remain in the passenger compartment for the time of rapid charging.

The heat treatment system 1 consists of a circuit 3 of coolant with two compression devices and a circulation loop 4 of heat transfer fluid.

The refrigerant circuit 3 is a closed circuit which comprises a network of pipes connecting the components of the refrigerant circuit 3. The pipeline network is constructed so that some components are arranged in series and others in parallel. The pipeline network thus comprises a main pipeline 5 and detailed branches elsewhere. Branch connection points but also certain components are used to connect the branches together.

The coolant circuit 3 comprises, on a third branch 6, a first compression device 7 for the coolant. It will be noted that the first compression device 7 for the refrigerant fluid can take the form of an electric compressor, that is to say a compressor which comprises a compression mechanism, an electric motor and a control and monitoring unit. electrical conversion. The compression mechanism of the first compression device 7 is rotated by the electric motor.

A first non-return valve 8 is placed downstream of the first compression device 7 on the third branch 6.

A first heat exchanger 9 is located downstream of the first non-return valve 8. The first non-return valve 8 is configured to allow the circulation of the coolant from the first compression device 7 to the first heat exchanger 9, and blocks the circulation reverse. This first heat exchanger 9 is positioned on the main pipe 5 of the refrigerant fluid circuit 3, and more precisely on a first portion 10 of this main pipe 5. The first heat exchanger 9 is configured to be traversed by an external air flow to the vehicle and operate as a condenser to remove heat from the refrigerant. A third connection point 11 connects the third branch 6 to the first portion 10 of the main pipe 5. This third connection point 11 is thus positioned between the first non-return valve 8 and the first heat exchanger 9.

The first portion 10 of the main pipe 5 is divided into a first connection point 12 into two parallel branches. The first portion 10 of the main pipe 5 therefore extends between the third connection point 11 and the first connection point 12. From this first connection point 12, the refrigerant circuit 3 diverges into a first branch 13 and a second branch 14, which join each other at a second connection point 15. Thus, the first branch 13 extends between the first connection point 12 and the second connection point 15, just as the second branch 14. This second connection point 15 links the first branch 13 and the second branch 14 to a second portion 16 of the main pipe 5.

A first expansion member 17 is positioned on the first branch 13 downstream of the first connection point 12. A second heat exchanger 18 is disposed between the first expansion member 17 and the second connection point 15. This second heat exchanger 18 is configured to be traversed by an interior air flow intended for the passenger compartment of the vehicle, the second heat exchanger 18 operating as an evaporator in order to cool this air flow. A third non-return valve 19 is located downstream of the second heat exchanger 18. The third non-return valve 19 is configured to allow the circulation of the coolant from the second heat exchanger 18 to the second connection point 15, and blocks the circulation reverse.

A second expansion member 20 is positioned on the second branch 14 downstream of the first connection point 12. A heat exchanger 21 is disposed between the second expansion member 20 and the second connection point 15. This heat exchanger 21 is configured to be thermally coupled to the electrical storage device 2. In this case, the heat exchanger 21 is configured to heat treat the electrical storage device 2 indirectly. The electrical storage device 2 exchanges its calories not directly by convection with the heat exchanger 21, but indirectly via the circulation loop 4 of heat transfer fluid. The circulation loop 4 of heat transfer fluid is in fact intended to transport to the heat exchanger 21 the calories that the electrical storage device 2 has exchanged with a third heat exchanger 46.

The function of the electrical storage device 2 is to supply electrical energy to one or more electric motors which set the vehicle in motion. Such an electrical storage device 2 accumulates or restores this electrical energy with a view to setting the vehicle in motion, via the dedicated electric motor. This is for example a battery pack grouping together several electric cells which store electric current.

The second portion 16 of the main pipe 5 is between the second connection point 15 and a distribution device 22 of five-way refrigerant 24, 25, 26, 27, 28. The distribution device 22 comprises a body 23 at within which there is a first channel 24, a second channel 25, a third channel 26, a fourth channel 27 and a fifth channel 28.

These channels 24, 25, 26, 27, 28 are in communication with the branches of the refrigerant circuit 3 via ports 29, 30, 31, 32, 33. The first channel 24 extends between a first port 29 and a second port 30. The second channel 25 extends between the second port 30 and a fourth port 31. The third channel 26 extends between a third port 32 and the first port 29. The fourth channel 27 extends between the third port 32 and a fifth port 33. The fifth channel 28 extends between the first port 29 and the fifth port 33. Depending on the operation of the refrigerant circuit 3, the ports of the distribution device 22 operate at the input and / or at the exit. They are alternately either open or closed, depending on the implementation of the coolant circuit 3, as will be described in Figures 3 to 9. In this case, the first port 29 and the fourth port 31, when they are open, are outputs of the distribution device 22. The second port 30 and the third port 32, when open, are inputs of the distribution device 22. The fifth port 33, when open, is alternately a entry or exit.

The first port 29 links the first channel 24, the third channel 26 and the fifth channel 28 of the distribution device 22 to the third branch 6 of the coolant circuit 3. Thus, the third branch 6 extends between the first port 29 and the third connection point 11. On the third branch 6, the first compression device 7 is positioned so that an inlet 34 of this first device compression 7 is connected to the first port 29.

The second port 30 links the first channel 24 and the second channel 25 to a fourth branch 35 of the coolant circuit 3. This fourth branch 35 extends between the second port 30 and a fourth connection point 36. A second compression device 37 is positioned on this fourth branch 35 so that an outlet 38 from this second compression device 37 is connected to the second port 30.

It will be noted that the second compression device 37 for the coolant can take the form of an electric compressor, that is to say a compressor which includes a compression mechanism, an electric motor and a control and monitoring unit. electrical conversion. The compression mechanism of the second compression device 37 is rotated by the electric motor.

The third port 32 links the second portion 16 of the main pipe 5 to the third track 26 and to the fourth track 27. The second portion 16 of the main pipe 5 therefore extends from the second connection point 15 to the third port 32.

The fourth port 31 links the second channel 25 to a fifth branch 39 of the refrigerant circuit 3. The fifth branch 39 extends between the fourth port 31 and the third connection point 11. Thus, seen from the refrigerant, the third connection point 11 allows the third branch 6 and the fifth branch 39 to converge towards the first portion 10 of the main pipe 5. A second non-return valve 40 is positioned on the fifth branch 39. It is configured to allow the circulation of the coolant from the fourth port 31 to the third connection point 11, and blocks circulation in the direction reverse.

The fifth port 33 links the fourth channel 27 and the fifth channel 28 to a sixth branch 41 of the refrigerant circuit 3. The sixth branch 41 extends between the fifth port 33 and the fourth connection point 36. The fifth port 33 being able to operate at input or at output, this sixth branch 41 is bidirectional from the point of view of the refrigerant.

This configuration means that the fourth branch 35, the first channel 24 and the third branch 6 are in series. The fourth branch 35, the second track 25 and the fifth branch 39 are in series. The second portion 16 of the main pipe 5, the third track 26 and the third branch 6 are in series. The second portion 16 of the main pipe 5, the fourth track 27 and the sixth branch 41 are in series. The sixth branch 41, the fifth track 28 and the third branch 6 are in series. Thus, the first compression device 7 and the second compression device 37 are in parallel or in series between the third port 32 and the third connection point 11, depending on the opening and closing clearance of the channels 24, 25, 26 , 27, 28, whether or not used by the refrigerant.

The refrigerant circuit 3 also comprises a seventh branch 42. The latter extends between the fourth connection point 36 and a fifth connection point 43. The fifth connection point 43 is positioned on the first branch 13, between the second heat exchanger 18 and the third non-return valve 19.

When the coolant flows from the fifth port 33 to the fourth connection point 36, the sixth branch 41 and the fourth branch 35 are in series. Seen from the refrigerant, the fourth connection point 36 is then a point of convergence between the seventh branch 42 and the sixth branch 41.

When the refrigerant flows from the fourth connection point 36 to the fifth port 33, the sixth branch 41 and the fourth branch 35 are in parallel. Seen from the refrigerant, the fourth connection point 36 is a point of divergence between the sixth branch 41 and the fourth branch 35.

The circulation loop 4 of heat transfer fluid is a closed circuit which comprises a pipe 44 so that the components which it connects are arranged in series with respect to each other.

The circulation loop 4 of heat transfer fluid comprises a means 45 for circulating heat transfer fluid, such as a pump. The means 45 for circulating heat transfer fluid is disposed upstream of the heat exchanger 21, according to the direction of circulation of the heat transfer fluid in the pipe 44. The third heat exchanger 46 is placed downstream of the heat exchanger 21. This third heat exchanger 46 is placed upstream of the means 45 for circulating heat transfer fluid. The third heat exchanger 46 is in physical contact with the electrical storage device 2 to heat treat it, for example to capture the calories it dissipates. Thus, the heat exchanger 21 thermally treats the electrical storage device 2 via the third heat exchanger 46.

Figure 2 shows the heat treatment system 1 according to the invention, in a second embodiment. This second embodiment corresponds to the first embodiment described in FIG. 1 to which a first internal heat exchanger 47 and / or a second internal heat exchanger 48 has been added. The heat treatment system 1 according to the invention is in fact configured to operate with two internal heat exchangers 47, 48 as shown in FIG. 2, or without internal heat exchanger as shown in FIG. 1, but these examples are nonlimiting, since the circuit 3 of refrigerant fluid according to the invention can also include a single internal heat exchanger 47, 48.

Thus, the thermal treatment system 1 of FIG. 2 is like that described in FIG. 1 except for the presence of the two internal heat exchangers 47, 48. Therefore, only the positioning of these two heat exchangers internal 47, 48 within the refrigerant circuit 3 is described below, and reference will be made to the description above for the implementation of the components common to these two embodiments.

The first internal heat exchanger 47 comprises two passes 49, 50 constituting the refrigerant fluid circuit 3. The second internal heat exchanger 48 comprises two layers 51, 52 constituting the refrigerant fluid circuit 3.

A first ply 51 and a first pass 49 are in series on the first branch 13. The first ply 51 is positioned between the first connection point 12 and the first pass 49. The first pass 49 is located between the first ply 51 and the first trigger 17.

A second ply 52 and a second pass 50 are in series on the second branch 14. The second ply 52 is positioned between the second expansion member 20 and the heat exchanger 21. The second pass 50 is located between the heat exchanger heat and the second connection point 15.

The operating modes of FIGS. 3 to 9 apply mutatis mutandis to the refrigerant circuit 3 according to the first embodiment as described in FIG. 1, with the exception of the interactions relating to the internal heat exchangers 47, 48.

FIG. 3 illustrates the heat treatment system 1 according to the invention presented in FIG. 2. This operating mode allows the electrical storage device 2 and the passenger compartment of the vehicle to be cooled simultaneously. The first compression device 7 and the second compression device 37 operate in parallel and simultaneously. The first compression device 7 is dedicated to the comfort of the passenger compartment and the second compression device 37 is dedicated to cooling the electrical storage device 2. This configuration allows the heat exchanger 21 and the second heat exchanger 18 to operate at different low pressure levels.

In this operating example, at the level of the device 22 for distributing refrigerant FR, the first port 29, the fourth port 31, the second port 30, and the third port 32 are open. The fifth port 33 is closed. Thus, the refrigerant FR circulates in the third channel 26 and in the second channel 25, and does not circulate in the first channel 24, in the fourth channel 27 and in the fifth channel 28.

In the fourth branch 35, the refrigerant FR passes from a low pressure and a low temperature to a high pressure and a high temperature thanks to the second compression device 37. The refrigerant FR passes through the distribution device thanks to the second channel 25, joining the fifth branch 39, which it travels to the third connection point 11, via the second non-return valve 40 passing through.

In the third branch 6, the refrigerant FR passes from a low pressure and from a second low temperature to a high pressure and a high temperature thanks to the first compression device 7. It passes through the first non-return valve 8 which is passing before joining the third connection point 11.

The two portions of the refrigerant fluids FR, mix at the third connection point 11. The mixture then travels through the first portion 10 of the main pipe 5 to the first connection point 12. By traversing the first portion 10 of the main pipe 5 , it passes through the first heat exchanger 9 operating as a condenser. A heat exchange takes place there between the refrigerant FR and the air flow outside FE to the vehicle.

The refrigerant FR, at the first connection point 12, is distributed between the first branch 13 and the second branch 14.

In the first branch 13, the refrigerant FR integrates the first layer 51 of the second internal heat exchanger 48. A heat exchange with the refrigerant FR of the first pass 49 takes place there so that the calories pass from the fluid FR refrigerant from the first layer 51 to the FR refrigerant the second layer 52. Then the FR refrigerant integrates the first pass 49 of the first internal heat exchanger 47. Another heat exchange with the FR refrigerant, FR refrigerant in the second pass 50 this time, takes place there: the calories pass from the refrigerating fluid FR the first pass 49 to the refrigerating fluid FR the second pass 50. Then, the refrigerating fluid FR passes through the first expansion member 17, undergoing a lowering of his pressure. It goes there from a state of high pressure and high temperature to a state of low pressure and low temperature before entering the second heat exchanger 18.

A heat exchange between the refrigerant FR and the air flow FA intended for the passenger compartment of the vehicle takes place at the level of the second heat exchanger 18, the latter operating as an evaporator. The FA air flow sent to the passenger compartment is thus cooled.

The third non-return valve 19 is blocking and prevents the refrigerant fluid FR from flowing between the second connection point 15 and the fifth connection point 43, the pressure at the second connection point 15 being greater than the pressure at the fifth connection point 43. The closing of the fifth port 33 prevents the circulation of the refrigerating fluid FR in the sixth branch 41. Consequently, the refrigerating fluid FR circulates from the second heat exchanger 18 to the second compression device 37, successively crossing the fifth point of connection 43, the seventh branch 42, the fourth connection point 36, before entering the fourth branch 35 to complete a thermodynamic cycle.

In the second branch 14, the refrigerant FR undergoes expansion by passing through the second expansion member 20. It passes from a state of high pressure and high temperature to a state of low pressure and low temperature before d 'integrate the second layer 52 of the second internal heat exchanger 48 where the heat transfer takes place as described above. Then, the refrigerant FR circulates through the heat exchanger 21 to carry out a heat exchange with the heat transfer fluid FC of the heat transfer fluid loop FC, the heat transfer fluid FC circulating in the heat exchanger 21, within the circulation loop 4 of the heat transfer fluid FC. Fe refrigerant fluid FR captures the calories of the heat transfer fluid FC, in order to cool the electrical storage device 2, via the third heat exchanger 46 of the circulation loop 4 of the heat transfer fluid FC, the heat exchanger 21 then operating as an evaporator.

After the heat exchanger 21, the refrigerant FR passes through the second pass 50 and operates a heat exchange with the refrigerant FR of the first pass 49 as mentioned above. Downstream of the second pass 50, after the second connection point 15, the refrigerating fluid FR circulates in the second portion 16 of the main pipe 5, entering the distribution device 22 via the third port 32. Using the third channel 26, the refrigerant FR joins the third branch 6 via the first port 29, then the first compression device 7 to complete a thermodynamic cycle.

Thus in the operating mode described in FIG. 3, the first compression device 7 and the second compression device 37 are in parallel between the first connection point 12, diverging, and the third connection point 11, converging, from the point of view of the refrigerant FR. They are both supplied with a refrigerant having a different low pressure.

Figures 4 and 5 illustrate the heat treatment system 1 according to the invention presented in Figure 2. Figure 4 and Figure 5 can illustrate two independent operating modes, dissociated. FIG. 4 and FIG. 5 can also illustrate the same sequential operating mode, divided into two sequences, a first sequence being illustrated in FIG. 4 and followed by a second sequence illustrated in FIG. 5. The two independent operating modes, like the sequential mode, allow the simultaneous cooling of the electrical storage device 2 and the passenger compartment of the vehicle by operating only one compressor.

In the independent operating modes, either the first compression device 7 or the second compression device 37 is responsible for cooling the electrical storage device 2 and the passenger compartment of the vehicle. The two compression devices 7, 37 do not operate at the same time. FIG. 4 shows a first independent operating mode where only the first compression device 7 is operating. FIG. 5 shows a second independent operating mode where only the second compression device 37 is operating.

In the sequential operating mode, the first compression device 7 and the second compression device 37 operate alternately: in the first sequence described in FIG. 4, only the first compression device 7 is operational; in the second sequence described in FIG. 5, only the second compression device 37 is operating. The first sequence illustrated in FIG. 4 and the second sequence illustrated in FIG. 5 succeed one another, by the alternating opening and closing of the ports 29, 30, 31, 32, 33 of the distribution device 22, so that any the compression function is carried alternately by one or other of the compression devices 7, 37, avoiding simultaneous operation of the latter at too low speeds of rotation. Thus, either the first compression device 7 or the second compression device 37 is responsible for cooling the electrical storage device 2 and the passenger compartment of the vehicle. In both sequences, the low pressures and the high pressures are identical.

In the examples referred to in FIGS. 4 and 5, the coolant LR circulates as previously described in FIG. 3 from the third connection point 11 to the third port 32 on the one hand, and to the fourth connection point 36 d 'somewhere else.

At the level of the coolant distribution device 22 FR, for the first independent operating mode as well as for the first sequence of the sequential operating mode, illustrated in FIG. 4, the first port 29, the third port 32 and the fifth port 33 are open. The second port 30 and the fourth port 31 are closed. Thus, the refrigerant FR circulates in the third channel 26 and the fifth channel 28, and does not circulate in the first channel 24, the second channel 25 and the fourth channel 27. Furthermore, the third non-return valve 19 and the second non-return valve 40 are blocking, respectively preventing the circulation of the refrigerant fluid FR on the first branch 13 between the fifth connection point 43 and the second connection point 15, and in the fifth branch 39. The first non-return valve 8 is in turn, thus allowing the circulation of the coolant in the third branch 6.

In FIG. 4, the refrigerant FR enters the distribution device 22 through the fifth port 33 which serves as an inlet, and also through the third port 32, after having traversed the sixth channel 41 from the fourth connection point 36. The refrigerant FR which crosses the fifth channel 28 and that which crosses the third channel 26 converge to exit the compression device at the same port, the first port 29. From this first port 29, the refrigerant FR undergoes compression at level of the first compression device 7 before joining the third connection point 11.

The refrigerant FR does not circulate between the fifth connection point 43 and the second connection point 15, nor in the fourth branch 35 and the fifth branch 39. The second compression device 37 is stopped, not aspirating the refrigerant FR in the fourth branch 35.

At the level of the coolant distribution device 22 FR, and this for the second independent operating mode as well as for the second sequence of the sequential operating mode, illustrated in FIG. 5, the second port 30, the fourth port 31, the third port 32 and the fifth port 33 are open. The first port 29 is closed. Thus, the refrigerant FR circulates in the fourth channel 27 and the second channel

25, and does not circulate in the first channel 24, in the third channel 26 and the fifth channel 28. Furthermore, the third non-return valve 19 and the first non-return valve 8 are blocking, respectively preventing the circulation of the fluid FR refrigerant on the first branch 13 between the fifth connection point 43 and the second connection point 15, and in the third branch 6. The second non-return valve 40 is open allowing circulation of the refrigerant in the fifth branch 39.

The LR refrigerant circulates from the third port 32 to the fourth connection point 36 via the fourth channel 27 and the fifth port 33. The LR refrigerant circulates in the opposite direction in the sixth branch 41 with respect to what has been described in Figure 4. At the fourth connection point 36 also converge the refrigerant LR from the seventh branch 42 in addition to that from the sixth branch 41. From the fourth connection point 36, the refrigerant LR circulates in the fourth branch 35 to join the second compression device 37 where it undergoes compression. The refrigerant then joins the third connection point 11, via the second channel 25 and the fifth branch 39.

The LR refrigerant does not circulate between the fifth connection point 43 and the second connection point 15, nor in the third branch 6. The first compression device 7 is thus stopped.

FIG. 6 illustrates the heat treatment system 1 according to the invention presented in FIG. 2. This operating mode allows dedicated cooling for the passenger compartment of the vehicle. The first compression device 7 and the second compression device 37 operate therein in parallel and simultaneously, at the same compression ratio. This configuration enables significant cooling of the LA air flow intended for the passenger compartment to be generated in a short time, for example for accelerated preconditioning of the passenger compartment.

In the example of Figure 6, the LR refrigerant circulates as previously described in Figure 3, except for the following. The second expansion member 20 is closed to block the circulation of the heat transfer fluid in the second branch 14, rendering the heat exchanger 21 inoperative, just like the first internal heat exchanger 47 and the second internal heat exchanger 48. The third non-return valve is in turn: the refrigerant FR diverges at the fifth connection point 43, sucked in by the first compression device 7 and the second compression device 37. The refrigerant thus passes through the entire first branch 13, joining the second connection point 15. Thus, the first compression device 7 and the second compression device 37 are supplied in parallel by the refrigerant FR from the second heat exchanger 18 which operates as an evaporator.

In the operating mode described in FIG. 6, the first compression device 7 and the second compression device 37 are in parallel between the fifth connection point 43, diverging, and the third connection point 11, converging, from the point of view FR refrigerant.

FIG. 7 illustrates the heat treatment system 1 according to the invention presented in FIG. 2. This operating mode allows dedicated cooling for the passenger compartment of the vehicle. The first compression device 7 and the second compression device 37 operate therein in series, to sequentially compress the refrigerant fluid FR passing through them successively. This configuration enables significant cooling of the FA air flow intended for the passenger compartment to be generated in a short time, in particular when the vehicle is stationary or idling. This configuration therefore allows the heat treatment system 1 to operate at operating points with a high compression ratio, low pressure low and very high pressure. This operating case can prove to be very useful in the case of the use of the refrigerant FR R744 because it makes it possible to limit the discharge temperature at the outlet of the second compressor ?. One can also imagine cooling by an external device the discharge of the compressor 37 to limit the consumption of the compressor 7.

In this operating example, at the level of the device 22 for distributing refrigerant FR, the first port 29 and the second port 30 are open. The third port 32, the fourth port 31 and fifth port 33 are closed. Thus, the refrigerant FR circulates in the first channel 24, and does not circulate in the second channel 25, the third channel 26, in the fourth channel 27 and the fifth channel 28.

Furthermore, the second non-return valve 40 and the third non-return valve 19 are blocking, and the second expansion member 20 is closed. The first non-return valve 8 is in turn. As a result, the heat exchanger 21 is inoperative, just like the first internal heat exchanger 47 and the second internal heat exchanger 48. The second heat exchanger 18 operates as an evaporator.

In the example of FIG. 7, the refrigerating fluid LR circulates as previously described in FIG. 6 from the third connection point 11 to the fifth connection point 43. The loop 4 for circulation of heat transfer fluid LC is as described in figure 6.

At the fifth connection point 43, the refrigerant LR only borrows the seventh branch 42, sucked in by the second compression device 37. It then crosses the fourth connection point 36 to end up in the fourth branch 35. The refrigerant LR passes through the second compression device 37, and undergoes a first expansion. It then passes through the distribution device 22 via the first channel 24. The refrigerant LR then joins the third branch 6. It then undergoes a second expansion therein passing through the first compression device 7. The high pressure is thus gradually reached.

Thanks to the first channel 24, the second compression device 37 is arranged in series with the first compression device 7, from the point of view of the refrigerating fluid LR. Therefore, the LR refrigerant is brought to a first high pressure level by means of the second compression device 37. Then, this LR refrigerant is raised to a second high pressure level, more important than the first high pressure level. thanks to the first compression device 7. The high pressure obtained sequentially allows high pressure to be obtained with less effort and with a lower level of noise than with a single compression device.

FIG. 8 illustrates the heat treatment system 1 according to the invention presented in FIG. 2. This operating mode allows dedicated cooling to the electrical storage device 2. The passenger compartment is not treated during the operation of this mode.

The first compression device 7 and the second compression device 37 operate therein in parallel, at the same compression rate. This configuration makes it possible to reduce the speed of rotation of the compression devices 7, 37 compared to a single compression device.

In this operating example, at the level of the device 22 for distributing refrigerant FR, the first port 29, the second port 30, the third port 32, the fourth port 31, and the third port 32 are open. No ports are closed. Thus, the refrigerant FR circulates in each port. Furthermore, the first expansion member 17 is closed and the third non-return valve 19 is blocking. Therefore, the second heat exchanger 18 is inoperative, just like the first internal heat exchanger 47 and the second internal heat exchanger 48. The heat exchanger 21 operates as an evaporator.

In the example of FIG. 8, the refrigerating fluid FR circulates as previously described in FIG. 3 from each of the compression devices 7, 37 to the first connection point 12. From this first connection point 12, the refrigerant only borrows the second branch 14. The refrigerant FR passes through the second expansion member 20 where it undergoes relaxation, passes the second thermodynamically neutral sheet 52, and the heat exchanger 21 where it indirectly operates the heat treatment of the electrical storage device 2. The refrigerant FR passes through the second pass 50 before joining the third port 32 via the second portion 16 of the main pipe 5. From the third port 32, the refrigerant FR diverges. On one side it joins the first compression device 7 after having passed the third track 26. On the other side, it takes the fourth track 27, the sixth branch 41 to the fourth point of convergence 36. From the fourth point of convergence 36, the refrigerant FR joins the second compression device 37.

Thus in the operating mode described in FIG. 8, the first compression device 7 and the second compression device 37 are in parallel between the third port 32, where the refrigerant FR diverges, and the third connection point 11, converging, from the FR refrigerant point of view.

FIG. 9 illustrates the heat treatment system 1 according to the invention presented in FIG. 2. This mode of operation allows cooling dedicated to the electrical storage device 2, without heat treatment of the passenger compartment. The first compression device 7 and the second compression device 37 operate therein in series, to sequentially compress the refrigerant FR passing through them successively. This configuration makes it possible to reduce the speed of rotation of the first compression device and second compression device 37 compared to a single compression device, while providing significant cooling of the electrical storage device 2, necessary for example when the ambient temperature is high. .

In this operating example, at the level of the device 22 for distributing refrigerant FR, the first port 29, the second port 30, the third port 32 and the fifth port 33 are open. The fourth port 31 is closed. Thus, the refrigerant FR circulates in the first channel 24 and the fourth channel 27, and does not circulate in the second channel 25, the third channel 26 and the fifth channel 28.

In the example of FIG. 9, the refrigerating fluid FR circulates as previously described in FIG. 8 from the third connection point 11 and up to the third port 32. Reference will be made to the description of FIG. 8 for setting up work of this part of the circuit. This embodiment is particularly suitable for low ambient temperatures, even negative temperatures, for the so-called heating function. The suction point of the compressor 37 is then close to 1 bar and the discharge pressure of 7 is close to 20 bars.

At the third port 32, the refrigerant FR crosses the fourth channel 27 and the fifth port 33. After the fifth port 33, the refrigerant FR follows the sixth branch 41 and the fourth connection point 36 before arriving in the fourth branch 35. It then undergoes compression by means of the second compression device 37. Then, being of high pressure and high temperature, it crosses the first channel 24 and the third branch 6 via the first compression device 7 before joining the third connection point 11.

Thanks to the first channel 24, the second compression device 37 is arranged in series with the first compression device 7, from the point of view of the refrigerant fluid FR. This has the effect of gradually obtaining the high pressure as described in FIG. 7.

It will be understood from reading the above that the present invention provides a refrigerant circuit configured to implement compression of the refrigerant adapted to the desired operation with a view to cooling a passenger compartment and / or an electrical storage device. This refrigerant circuit, moreover compatible with the rapid charging of the vehicle, is in fact capable of delivering strong cooling while minimizing the noise nuisance due to the compression device. The efficiency of this cooling circuit finds its utility when the cooling circuit is requested to cool quickly and in a minimum of time both the passenger compartment of the vehicle and the electrical storage device.

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

Claims (10)

1, Refrigerant fluid circuit (3) of a vehicle comprising at least one main line (5) comprising a first portion (10) and a second portion (16), the main line (5) being arranged in series a first branch (13) and a second branch (14), the first branch (13) and the second branch (14) being in parallel and arranged between the first portion (10) and the second portion (16) , the first portion (10) of the main pipe (5) comprising a first heat exchanger (9) arranged to be traversed by an external air flow (FE) to a passenger compartment of the vehicle, the first branch (13) comprising a first expansion member (17) and a second heat exchanger (18) configured to thermally treat an air flow (FA) sent into the passenger compartment of the vehicle, the second branch (14) comprising a second expansion member (20) and a heat exchanger (21) thermally coupled to a dis positive electrical storage (2) of the vehicle, the circuit (3) of refrigerant fluid (FR) comprising a third branch (6) which comprises a first compression device (7) and a fourth branch (35) which comprises a second device compression (37), characterized in that the refrigerant (FR) circuit (3) comprises a five-way distributor (22) of the refrigerant (FR) (24, 25, 26, 27, 28), a first port (29) of the distribution device (22) being connected to an inlet (34) of the first compression device (7), a second port (30) of the distribution device (22) being connected to an outlet (38 ) of the second compression device (37). 2, the refrigerant fluid circuit (3) according to claim 1, comprising a first connection point (12) and a second connection point (15) between which the first branch (13) and the second branch extend. (14), a third port (32) of the distribution device (22) being connected to the second connection point (15) by the second portion (16) of the main pipe (5). 3, circuit (3) of refrigerant fluid (FR) according to the preceding claim, wherein a fifth branch (39) extends between a fourth port (31) of the distribution device (22) and a third connection point (11 ), the third connection point (11) connecting the first portion (10) of the main pipe (5), the third branch (6) and the fifth branch (39). 4. Circuit (3) of refrigerant fluid (FR) according to the preceding claim, wherein a sixth branch (41) is between the fourth branch (35) and a fifth port (33) of the distribution device (22). 5. Refrigerant fluid circuit (3) according to any one of the preceding claims, in which the distribution device (22) comprises a first channel (24) which extends between the first port (29) of the device distribution (22) and the second port (30) of the distribution device (22). 6. Circuit (3) of refrigerant fluid (FR) according to claims 3 to 5, wherein the distribution device (22) comprises a second channel (25) which extends between the second port (30) of the distribution device (22) and the fourth port (31) of the distribution device (22). 7. A circuit (3) of refrigerant fluid (FR) according to claims 2 to 6, wherein the distribution device (22) comprises a third channel (26) which extends between the third port (32) of the distribution device (22) and the first port (29) of the distribution device (22). 8. A circuit (3) of refrigerant fluid (FR) according to claims 5 to 7, wherein the distribution device (22) comprises a fourth channel (27) which extends between the third port (32) of the distribution device (22) and the fifth port (33) of the distribution device (22). 9. A circuit (3) of refrigerant fluid (FR) according to claims 4 to 8, wherein the distribution device (22) comprises a fifth channel (28) which extends between the fifth port (33) of the distribution device (22) and the first port (29) of the distribution device (22). 10. A heat treatment system (1) of a vehicle comprising the circuit (3) of refrigerant fluid (FR) according to any one of the preceding claims and a circulation loop (4) of heat transfer fluid (FC) comprising a third heat exchanger (46) configured to heat exchange with at least one electrical storage device (2) of the vehicle, the heat exchanger (21) being configured to be traversed by the coolant (FR) and by the heat transfer fluid (FC ).