HEAT TREATMENT SYSTEM FOR A MOTOR VEHICLE

Description

[0001] The present invention relates to the field of heat transfer fluid loops operating with a refrigerant circuit. The invention concerns a heat treatment system comprising at least one heat transfer fluid loop and a refrigerant circuit. Such a heat treatment system is known from US patent 2014 / 124159 A1.

[0002] A refrigerant circuit is typically associated with a vehicle's ventilation, heating, and / or air conditioning system to thermally treat an outside airflow entering the passenger compartment. This circuit uses changes in the refrigerant's state to heat and / or cool the airflow directed into the ventilation, heating, and / or air conditioning system.

[0003] Such thermal management systems are generally integrated into vehicles with an electric powertrain, meaning one that includes a motor powered at least partially by electricity supplied by one or more onboard electrical storage devices. Since all these components are sensitive to significant temperature changes, it is understandable that the thermal management system ensures their temperature regulation, and more specifically, their cooling.

[0004] These heat treatment systems are most often, at least partially, located at the front of vehicles. More precisely, these heat treatment systems typically include at least one heat exchanger positioned at the front. Given the need to limit the size of front-facing equipment, reducing the dimensions of such a heat exchanger results in a loss of efficiency for the heat treatment systems and, consequently, a decrease in their cooling capacity for the aforementioned electrical components.

[0005] To optimize the performance of the refrigerant circuit, it is known to integrate at least one heat exchanger configured to subcool the refrigerant by exchanging heat with the heat transfer fluid circulating in the heat transfer fluid loop. Typical architectures of such a loop include a radiator located at the front of the vehicle, downstream of the heat exchanger, aligned with the direction of airflow through the heat exchanger.

[0006] However, it may be necessary to reverse this architecture so that the radiator is positioned upstream of the heat exchanger, following the direction of airflow from outside the passenger compartment through the radiator and heat exchanger. A drawback of this architecture is that the heat exchanger is unable to subcool the refrigerant after its condensation phase, thus further reducing the performance of the heating and cooling system.

[0007] Such a performance loss is particularly noticeable when the vehicle's electrical storage system is used in a way that causes significant heating, for example, during a rapid charging phase. Rapid charging involves charging the electrical storage system at high voltage and amperage to fully charge it in a short period of a few tens of minutes. This rapid charging results in greater heating of the electrical storage system than that observed during normal operation, and therefore requires attention.

[0008] Furthermore, during rapid charging, it may be necessary to maintain an acceptable level of thermal comfort inside the passenger compartment. This means that the refrigerant circuit may have to simultaneously provide thermal treatment for both the passenger compartment and the storage device. Such demands require a high level of performance from the treatment system, necessitating a specific system design, particularly for the heat exchanger located at the front of the vehicle, which makes it poorly suited to the design constraints of the front ends of current motor vehicles, especially those powered by electric motors.

[0009] The present invention falls within this context and aims to resolve these various drawbacks by proposing a heat treatment system for a vehicle comprising at least one refrigerant circuit and at least one heat transfer fluid loop: the refrigerant circuit comprising at least one compression device, one expansion device, a first heat exchanger configured to implement heat exchange between the refrigerant and an outside airflow to a vehicle passenger compartment, a second heat exchanger configured to implement heat exchange between the refrigerant and the heat transfer fluid circulating in the loop and a fourth heat exchanger configured to implement heat exchange between the refrigerant and an inside airflow to the passenger compartment; the heat transfer fluid loop comprising, on a main line, the second heat exchanger and at least one primary radiator configured to implement heat exchange between the outside airflow to the vehicle passenger compartment and the heat transfer fluid;

[0010] The treatment system is characterized in that the refrigerant circuit includes a third heat exchanger configured to implement heat exchange between the refrigerant and the outside airflow or between the refrigerant and the heat transfer fluid and in that the first heat exchanger, the second heat exchanger and the third heat exchanger are arranged in the refrigerant circuit between an outlet of the compression device and an inlet of the expansion means, the primary radiator being disposed upstream of the first heat exchanger in a direction of circulation of the outside airflow.

[0011] 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 an interior airflow before sending it into the passenger compartment, or in air conditioning mode, in order to cool the interior airflow before sending it into the passenger compartment.

[0012] Depending on the operating mode of the heat treatment system circuit, the first heat exchanger and the fourth heat exchanger can thus be configured to operate as a condenser or as an evaporator, with respect to the refrigerant.

[0013] Also, to optimize the efficiency of the heat treatment system, at least one of the heat exchangers can be configured to subcool the liquid refrigerant. "Subcooling" refers to lowering the temperature of the refrigerant below its condensation temperature.

[0014] Advantageously, in the present invention, at least the second heat exchanger and / or the third heat exchanger are configured to ensure the subcooling of the refrigerant circulating in the circuit.

[0015] According to a particular embodiment of the invention, the second heat exchanger and the primary radiator are arranged in the main line of the heat transfer fluid loop so that the primary radiator discharges calories captured by the second heat exchanger into the outside airflow.

[0016] In other words, in the heat transfer fluid loop, the second heat exchanger is positioned downstream of the primary radiator according to a direction of heat transfer fluid circulation in the heat transfer fluid loop.

[0017] Thus, the calories captured by the heat transfer fluid at the level of the second heat exchanger are discharged into the outside airflow via the primary radiator, which ensures a return of the heat transfer fluid at a temperature significantly lower than the temperature of the refrigerant entering the second heat exchanger.

[0018] According to the invention, the primary radiator is arranged upstream of the first heat exchanger in a direction of circulation of the outside air flow.

[0019] In particular, the primary radiator of the heat transfer fluid loop is positioned directly upstream of the first heat exchanger of the refrigerant circuit according to the direction of the flow of outside air entering the front of the vehicle so that the airflow heated by heat exchange with the primary radiator is sent directly to the first heat exchanger.

[0020] According to a particular embodiment of the invention, the heat transfer fluid loop is thermally coupled to at least one element of the vehicle's electric drivetrain.

[0021] According to another aspect of the invention, the refrigerant circuit is a closed circuit comprising at least one main branch on which are successively arranged at least the compression device, the first heat exchanger, the second heat exchanger, the third heat exchanger, the expansion member, hereinafter referred to as the first expansion member, and the fourth heat exchanger, the refrigerant circuit comprising a second branch which extends from a divergence point, disposed between an outlet of the third heat exchanger and an inlet of the fourth heat exchanger, and a convergence point, disposed between an outlet of the fourth heat exchanger and an inlet of the compression device, the second branch comprising at least one expansion member, referred to as the second expansion member, and a fifth heat exchanger thermally coupled to an electrical storage device of the vehicle.The term "thermally coupled" refers to a fifth heat exchanger configured to provide direct or indirect cooling of the electrical storage device. For example, the fifth heat exchanger can be configured to facilitate heat exchange between the refrigerant and the electrical storage device, with the latter being placed in contact with the fifth heat exchanger. Alternatively, the fifth heat exchanger can be configured to facilitate heat exchange between the refrigerant and a heat transfer fluid within a second loop of the heat treatment system, this second loop including the electrical storage device.

[0022] In this way, the heat treatment system can be configured to dissipate the calories generated by at least one of the elements of the powertrain, such as a motor operating at least partially on electrical power or an electronic control module controlling it, and / or by the electrical storage device.

[0023] It is understood that the terms "first", "second" are intended to distinguish similar elements of said system and do not confer any hierarchy of the components of the heat treatment system.

[0024] According to a feature of a particular embodiment of the invention, the refrigerant circuit may include a third branch extending between a divergence point, hereinafter referred to as the second divergence point, located between the outlet of the compression device and an inlet of the first heat exchanger, and a convergence point, hereinafter referred to as the second convergence point, located between the outlet of the third heat exchanger and the inlet of the fourth heat exchanger, the third branch comprising at least one heat exchanger used as a condenser.

[0025] Specifically, the heat exchanger can be configured to implement heat exchange between the refrigerant and a heat transfer fluid circulating in a second, additional heat transfer fluid loop. Alternatively, the heat exchanger can be configured to implement heat exchange between the refrigerant and an interior airflow intended for distribution into the vehicle's passenger compartment, thereby enabling the thermal treatment of said interior airflow.

[0026] According to the invention, the refrigerant circuit may include a fourth branch extending between a divergence point, hereinafter referred to as the third divergence point, located between the outlet of the third heat exchanger and the inlet of the fourth heat exchanger, and a convergence point, hereinafter referred to as the third convergence point, located between the outlet of the compression device and the inlet of the first heat exchanger, the fourth branch comprising at least one expansion member referred to as the third expansion member.

[0027] According to an optional feature of the invention, the refrigerant circuit may include a fifth branch extending between a divergence point, hereinafter referred to as the fourth divergence point, disposed between an outlet of the second heat exchanger and an inlet of the third heat exchanger, and a convergence point, hereinafter referred to as the fourth convergence point, disposed between the outlet of the fourth heat exchanger and the inlet of the compression device.

[0028] According to a particular embodiment of the invention, the heat treatment system may, in addition, include an internal heat exchanger arranged between two distinct portions of the refrigerant circuit, in particular a first portion, comprising between the outlet of the compression device and the inlet of the first expansion member, at which the refrigerant is subjected to a high pressure, and a second portion of the refrigerant circuit, comprising between an outlet of the first expansion member and the inlet of the compression device, in which the refrigerant is subjected to a low pressure, lower than the high pressure.

[0029] According to a first, second and third embodiment, the third heat exchanger is configured to implement heat exchange between the refrigerant fluid and the outside airflow to the passenger compartment.

[0030] According to one aspect of these embodiments, the third heat exchanger is arranged upstream of the first heat exchanger in a direction S3 of the flow of air outside the passenger compartment.

[0031] In particular, the third heat exchanger is positioned directly upstream of the first heat exchanger according to the direction of the flow of outside air entering the front of the vehicle so that the airflow heated by heat exchange with the third heat exchanger is sent directly to the first heat exchanger.

[0032] According to one aspect of the first embodiment, the refrigerant circuit may include at least one receiver placed between the first and second heat exchangers. Such a receiver ensures that only a liquid fraction of the refrigerant exiting the first heat exchanger is directed to the second heat exchanger. Thus, when the first heat exchanger is used as a condenser, the second and third heat exchangers can be used as subcoolers for the refrigerant, thereby optimizing the coefficient of performance of the heat treatment system.

[0033] According to one aspect of the second embodiment, the refrigerant circuit may include at least one receiver integrated into the first heat exchanger. Thus, when the first heat exchanger operates as a condenser, at least one terminal section of said heat exchanger, supplied only with liquid refrigerant, can be used as a refrigerant subcooler. As a result, the heat treatment system implements three successive refrigerant subcoolings: one at the terminal section of the first heat exchanger, one in the second heat exchanger, and one in the third heat exchanger, further optimizing system performance without increasing the size of the various heat exchangers located at the front of the vehicle.

[0034] According to the third embodiment, the heat transfer fluid loop may include a second line extending in parallel with the main line between a branch point, located between an outlet of the circulation element and an inlet of the primary radiator, and a connection point, located between an outlet of the primary radiator and an inlet of the second heat exchanger, the second line comprising at least one heat transfer fluid flow control device.

[0035] For example, the heat transfer fluid flow control device can be a three-way valve integrated at the branch point. It is understood that the heat transfer fluid flow control device allows the heat transfer fluid to be selectively directed to the main line or to the secondary line by permitting or preventing the circulation of this heat transfer fluid in one or the other of these lines.

[0036] Alternatively, the heat transfer fluid loop may include a plurality of flow control devices, for example two two-way valves, one being installed in the main line and the other being installed in the second line.

[0037] According to fourth and fifth embodiments, the third heat exchanger is configured to implement heat exchange between the refrigerant and the heat transfer fluid.

[0038] According to one aspect of these fourth and fifth embodiments, the heat transfer fluid loop includes a bypass line comprising at least the third heat exchanger and a secondary radiator configured to implement heat exchange between the heat transfer fluid and the outside airflow, the secondary radiator being arranged upstream of the primary radiator in the S3 direction of flow of the outside airflow to the passenger compartment.

[0039] In other words, in the heat transfer fluid loop according to these embodiments, the second heat exchanger and the third heat exchanger are arranged in parallel with each other.

[0040] In particular, the secondary radiator of the heat transfer fluid loop is positioned directly upstream of the primary radiator in the direction of flow S3 of the outside air entering the front of the vehicle so that the airflow heated by heat exchange with the secondary radiator is sent directly to the primary radiator and then to the first heat exchanger.

[0041] According to one aspect of the fourth embodiment, the bypass line extends between a separation point, located between the outlet of the heat transfer fluid circulation element and the inlet of the primary radiator, and a junction point, located between the outlet of the second heat exchanger and an inlet of the circulation element.

[0042] Put another way, according to the fourth embodiment, part of the heat transfer fluid is sent to the primary radiator while the other part is sent to the secondary radiator, the heat transfer fluid then circulating in parallel, and in the same direction of circulation, in the primary radiator and in the secondary radiator.

[0043] According to one aspect of the fourth embodiment and similarly to the third embodiment, the heat transfer fluid loop may include the second line extending in bypass of the main line between the bypass point, located between the outlet of the circulation element and the inlet of the primary radiator, and the connection point, located between the outlet of the primary radiator and the inlet of the second heat exchanger, the second line including at least the heat transfer fluid flow control device.

[0044] According to a feature of the fifth embodiment, the bypass line can extend between the separation point, located between the outlet of the primary radiator and the inlet of the second heat exchanger, and the junction point, located between the outlet of the second heat exchanger and the inlet of the circulation element.

[0045] In other words, the fifth embodiment, unlike the fourth embodiment, ensures that a portion of the heat transfer fluid circulates successively in the primary radiator and then in the secondary radiator, so as to further cool said heat transfer fluid and thus optimize the performance of the heat treatment system.

[0046] An object of the present invention also relates to a motor vehicle comprising at least one heat treatment system as previously described.

[0047] Other features, details and advantages will become clearer upon reading the detailed description given below for guidance purposes in relation to the various implementation examples illustrated in the following figures: There figure 1 is a schematic representation of a heat treatment system according to a first and a second embodiment, this heat treatment system comprising at least one refrigerant circuit and one heat transfer fluid loop; The figure 2 schematically illustrates a first example of the operation of the heat treatment system shown on the figure 1 in which the refrigerant circuit operates in passenger compartment cooling mode; The figure 3 schematically illustrates a second example of the operation of the heat treatment system shown on the figure 1 in which the refrigerant circuit operates in cooling mode for an electrical storage device in the vehicle; The figure 4 schematically illustrates the heat treatment system according to a third embodiment; The figure 5 illustrates the heat treatment system according to the figure 4 , when it implements the first operating mode, that is, the cooling of the passenger compartment; The figure 6 illustrates the heat treatment system according to the figure 4 , when it implements a third operating mode and the refrigerant circuit is operating in passenger compartment heating mode; The figure 7 schematically illustrates the heat treatment system according to a fourth embodiment; The figure 8 schematically illustrates the heat treatment system shown on the figure 7 when operating in cabin cooling mode; The figure 9 schematically illustrates the heat treatment system shown on the figure 7 when the refrigerant circuit is operating in passenger compartment heating mode; The figure 10 schematically illustrates the heat treatment system according to a fifth embodiment; The figure 11 schematically illustrates a first example of the operation of the heat treatment system shown on the figure 10 in which the refrigerant circuit operates in passenger compartment cooling mode;

[0048] There figure 1 This schematically illustrates a thermal treatment system 1 for several functions of a motor vehicle, including at least one ventilation, heating and / or air conditioning system 10 for the passenger compartment, an electrical storage device 11, and at least one element 12 of the vehicle's electric powertrain. The thermal treatment system 1 comprises a heat transfer fluid loop 2, for example glycol water, and a refrigerant circuit 3 intended, in particular, for the thermal treatment of the vehicle's passenger compartment.

[0049] Throughout the description, the terms "upstream", "downstream", "inlet" and "outlet" refer to a flow direction S1 of the heat transfer fluid in the heat transfer fluid loop 2 or a flow direction S2 of the refrigerant in the refrigerant circuit 3 or a flow direction S3 of an outside airflow FA1 to the passenger compartment.

[0050] The refrigerant circuit 3 consists of a closed circuit which includes at least one main branch 300 on which are arranged at least one compression device 31, intended to raise the pressure of the refrigerant and an expansion device 32, called the first expansion device 32, intended to lower the pressure of the refrigerant.The refrigerant circuit 3 further comprises at least one first heat exchanger 33 configured to implement heat exchange between the refrigerant and the outside airflow FA1 to the passenger compartment, at least one second heat exchanger 34 configured to implement heat exchange between the refrigerant and the heat transfer fluid circulating in the loop 2, a third heat exchanger 35 configured to implement heat exchange between the refrigerant and the outside airflow FA1 or between the refrigerant and the heat transfer fluid and a fourth heat exchanger 36 configured to implement heat exchange between the refrigerant and an inside airflow FA2 to the passenger compartment.

[0051] In particular, according to the present invention, the first heat exchanger 33, the second heat exchanger 34, and the third heat exchanger 35 are arranged in the refrigerant circuit 3 between an outlet of the compression device 31 and an inlet of the first expansion device 32. In the first embodiment as illustrated in the figure 1 , the third heat exchanger 35 is configured to implement heat exchange between the refrigerant fluid and the outside airflow FA1 and it is positioned upstream of the first heat exchanger 33 according to the direction of flow S3 of the outside airflow FA1 to the passenger compartment.

[0052] The heat transfer fluid loop 2 consists of a closed loop comprising a main line 200 on which are arranged a heat transfer fluid circulation element 21, such as a pump, at least one second heat exchanger 34, and at least one primary radiator 22 configured to implement heat exchange between the outside airflow FA1 to the passenger compartment and the heat transfer fluid. It should be noted that, in the second heat exchanger 34, the different circulating fluids do not mix and that the heat exchange between these two fluids occurs by conduction.

[0053] Also, the heat transfer fluid loop 2 is thermally coupled to at least one element 12 of the vehicle's electric drive chain, for example at least one electric motor or a control module of said motor, so as to be able to provide its heat treatment, in particular cooling.

[0054] Thus, within the heat treatment system 1, the primary radiator 22 of the heat transfer fluid loop 2 and the first heat exchanger 33 of the refrigerant circuit 3 are exposed to the outside airflow FA1, the primary radiator 22 being, according to the invention, positioned upstream of the first heat exchanger 33 in the direction of flow S3 of the outside airflow FA1. Advantageously, the primary radiator 22 and the first heat exchanger 33 are located at the front of the vehicle. Alternatively, they could also be installed on the roof of the vehicle, in a rear fender, and generally in any area of ​​the vehicle that can be swept by the outside airflow FA1.

[0055] The refrigerant circuit 3 thus comprises the main branch 300 on which are successively arranged, according to the direction of circulation S2 of the refrigerant, the compression device 31, the first heat exchanger 33, the second heat exchanger 34, the third heat exchanger 35, the first expansion member 32, and the fourth heat exchanger 36. The refrigerant circulating in a first portion 301 of the refrigerant circuit 3, between the outlet of the compression device 31 and the inlet of the first expansion member 32, is subjected to a high pressure while the refrigerant circulating in a second portion 302 of the circuit, between an outlet of the first expansion member 32 and an inlet of the compression device 31, is subjected to a low pressure, lower than the high pressure.

[0056] Advantageously, the refrigerant circuit 3 may include, between an outlet of the first heat exchanger 33 and an inlet of the second heat exchanger 34, at least one bottle 4. Such a bottle 4 ensures that only a liquid fraction of the refrigerant exiting the first heat exchanger 33 is brought to the second heat exchanger 34 so that, when the first heat exchanger 33 is used as a condenser, the second heat exchanger 34 and / or the third heat exchanger 35 can be used as a sub-cooler for the refrigerant.

[0057] Advantageously, the refrigerant circuit 3 of the heat treatment system 1 includes an internal heat exchanger 37. This internal heat exchanger 37 allows the recovery of heat from a portion of the refrigerant circuit 3, here the first portion 301, to exchange it with another portion of the same circuit, here the second portion 302, so as to reduce the power consumed by the compression device 31 and overall increase the performance of the refrigerant circuit 3.

[0058] A first line 3010, comprising the first section 301, is used to conduct the refrigerant under high pressure and high temperature. A second line 3020, included in the second section 302, is used to conduct the refrigerant under low pressure and low temperature. In the illustrated example, the first line 3010 and the second line 3020 comprise, respectively, a first section 371 and a second section 372 of the internal heat exchanger 37.

[0059] Since the internal heat exchanger 37 is arranged between two pipes 3010, 3020 which have a temperature differential between them, it is understood that it allows heat exchange between its two parts 371, 372 and therefore between the two pipes 3010, 3020 of the refrigerant circuit 3 on which these parts 371, 372 are arranged.In the illustrated example, the first part 371 of the internal heat exchanger 37 is located between an outlet of the third heat exchanger 35 and the inlet of the first expansion valve 32, and the second part 372 of this internal heat exchanger 37 is located between an outlet of the fourth heat exchanger 36 and the inlet of the compression device 31. This allows, on the one hand, the refrigerant to be heated upstream of the compression device 31 so that it is exclusively in gaseous form when it reaches the inlet of the compression device 31, and on the other hand, the refrigerant to be cooled upstream of the first expansion valve 32 so that the pressure drop achieved by this expansion valve 32 is facilitated. The overall efficiency of the refrigerant circuit 3 is thus improved by the presence of this internal heat exchanger 37.

[0060] The refrigerant circuit 3 includes a second branch 310 which diverges from the main branch 300 and extends between a point of divergence, called the first point of divergence 311, located between the outlet of the third heat exchanger 35 and an inlet of the fourth heat exchanger 36, and a point of convergence, called the first point of convergence 312, located between the outlet of the fourth heat exchanger 36 and the inlet of the compression device 31.

[0061] The second branch 310 comprises, successively, according to the direction of flow S2 of the refrigerant, an expansion valve, referred to as the second expansion valve 313, and a fifth heat exchanger 314 thermally coupled to the vehicle's electrical storage device 11, configured to at least electrically power the component 12 of the vehicle's electric drivetrain. The fifth heat exchanger 314 is thus arranged in parallel with the fourth heat exchanger 36 from the perspective of the refrigerant.

[0062] It is understood that the electrical storage device 11 is arranged near, or advantageously in thermal contact with, the fifth heat exchanger 314, and that the latter is configured to implement a heat exchange between the refrigerant circulating in the second branch 310 and a second heat transfer fluid loop 5 comprising the electrical storage device 11 and configured to provide its cooling. For example, the heat transfer fluid in this second loop can be circulated by a circulator 51.

[0063] There figure 1 The diagram also shows the ventilation, heating, and / or air conditioning system 10, which includes a housing 101 defining an internal volume. The interior airflow FA2 is channeled through this housing 101 before being sent into the vehicle's passenger compartment. The housing 101 notably contains the fourth heat exchanger 36 and may, for example, accommodate at least one heat exchanger configured to thermally treat an interior airflow sent to the passenger compartment. The ventilation, heating, and / or air conditioning system 10 also includes a fan 102 responsible for moving the interior airflow FA2 within the housing 101, as well as mixing or distribution flaps 103, generally designated by the reference numeral.

[0064] THE figures 2 And 3These figures describe examples of distinct operating modes of the heat treatment system 1 as previously described, i.e., implemented according to the first embodiment. In these figures, solid lines represent pipes of the heat treatment system 1 in which the refrigerant or heat transfer fluid circulates, while dashed lines represent pipes of the heat treatment system 1 in which neither the refrigerant nor the heat transfer fluid circulates. The outside airflow FA1 and its direction of flow S3, the inside airflow FA2, the direction of flow S1 of the heat transfer fluid in the heat transfer fluid loop 2, and the direction of flow S2 of the refrigerant in the refrigerant circuit 3 are also schematically represented on the various figures. figures 1 à 11 Organs or devices for regulating the flow of different fluids are illustrated as solid when they block the circulation of the fluid concerned, and as hollow when they allow said circulation.

[0065] There figure 2 represents a first example of operation of the heat treatment system 1 according to the first embodiment, in which the refrigerant circuit 3 is configured to operate in air conditioning mode, i.e. it is configured to cool the interior airflow FA2 before it is sent into the passenger compartment of the vehicle.

[0066] In the refrigerant circuit 3, the refrigerant flow is limited to the main branch 300. The second branch 310 does not carry the refrigerant. For example, the refrigerant flow may be restricted in these branches by at least the second expansion valve 313 and / or by a refrigerant flow control device such as a two-way or three-way valve.

[0067] The refrigerant leaves the compression unit 31 under high pressure, at high temperature, and in a gaseous state, heading towards the first heat exchanger 33, which functions as a condenser. Since the refrigerant's temperature is higher than that of the outside air flow FA1 passing through the first heat exchanger 33, it releases its heat to the outside air flow FA1. The cooled refrigerant leaves the first heat exchanger 33 primarily in a liquid state and enters the receiver 4, which is configured to send only a liquid portion of the refrigerant to the second heat exchanger 34.Due to the presence of the bottle 4, the second heat exchanger 34 functions as a sub-cooler, that is to say, it ensures the cooling of the refrigerant circulating in a first pass 341 of the second heat exchanger 34 to a temperature at least lower than its condensation temperature by heat exchange with the colder heat transfer fluid circulating in a second pass 342 of the second heat exchanger 34.

[0068] In particular, it should be noted that the heat transfer fluid circulating in the second pass 342 of the second heat exchanger 34 comes from the primary radiator 22 which is first crossed by the outside air flow FA1, so that the temperature of the heat transfer fluid is lowered to a temperature close to that of the outside air flow FA1, thus ensuring a first efficient subcooling of the refrigerant circulating in the second heat exchanger 34 before sending it to the third heat exchanger 35 for a second subcooling.

[0069] In the third heat exchanger 35, the cooled refrigerant, which is warmer than the outside airflow, gives up heat to the latter and exits the third heat exchanger 35 at a temperature lower than that observed at the outlet of the second heat exchanger 34.

[0070] In this embodiment, the third heat exchanger 35 is advantageously positioned upstream of the first heat exchanger 33 along the S3 direction of the outside air flow. Consequently, the outside air flow FA1 involved in the heat exchange at the third heat exchanger 35 has a lower temperature than the outside air flow FA1 involved in the heat exchange at the first heat exchanger 33, which has been preheated. The temperature difference between the refrigerant and the outside air flow FA1 at the first heat exchanger 33 is thus reduced compared to the temperature difference observed at the third heat exchanger 35.Such an arrangement contributes to increasing the capacity of the thermal treatment system 1, in particular by allowing, for the supply of the same cooling power, a reduction in the rotation speed of the compression device 31 which is accompanied by a decrease in the electrical consumption of said device 31 as well as a reduction of possible noises in the passenger compartment which may result from a high rotation speed of the compressor.

[0071] The subcooled refrigerant is then sent into the first part 371 of the internal heat exchanger 37 where, as previously explained, it gives up heat to the colder refrigerant circulating in the second part 372 of the internal heat exchanger 37. The cooled refrigerant then flows into the first expansion member 32 where it undergoes a reduction in pressure.

[0072] The low-pressure refrigerant enters the fourth heat exchanger 36, which acts as an evaporator, where it evaporates by absorbing heat from the interior airflow FA2. The cooled interior airflow FA2 is then sent to the vehicle's passenger compartment, while the refrigerant leaves the fourth heat exchanger 36 warmed and at least partially in a gaseous state. The refrigerant then enters the second section 372 of the internal heat exchanger 37, where it absorbs heat from the refrigerant circulating in the first section 371 of the internal heat exchanger 37, before being returned to the compression unit 31.

[0073] Alternatively, the refrigerant circuit 3 may include, between the outlet of the fourth heat exchanger 36 and an inlet of the second part 372 of the internal heat exchanger 37, an accumulation device, not shown, in which the liquid phase and the gaseous phase are separated so that only the gaseous phase is subsequently sent to the second part 372 of the internal heat exchanger 37 and then, again, to the compression device 31.

[0074] In the heat transfer fluid loop 2, the heat transfer fluid is put into circulation by the circulation element 21, it captures heat from at least one of the elements 12 of the electric vehicle's powertrain and then discharges this heat into the outside airflow at the primary radiator 22. The cooled heat transfer fluid then enters the second heat exchanger 34 in which, as explained above, it captures heat from the refrigerant circulating in the first pass 341 of the second heat exchanger 34.

[0075] The heat transfer fluid exiting the second heat exchanger 34 is then returned to the circulation element 21, the second heat exchanger 34 and the primary radiator 22 being thus arranged in the heat transfer fluid loop 2 so that, from one cycle to another, the primary radiator 22 discharges into the outside airflow FA1 calories captured by the second heat exchanger 34 but also by the element 12 of the electric traction chain.

[0076] There figure 3 illustrates a second example of the operation of the heat treatment system 1. This second example of operation is substantially similar to the one described previously in that the refrigerant circuit 3 operates in an air conditioning mode and the description of these elements is based on the figure 2 is therefore applicable to the present operating example. This second operating example differs from the first operating example in that the heat treatment system 1 is configured to provide heat treatment for the electrical storage device 11 simultaneously with the heat treatment of the passenger compartment. To this end, the second branch 310 of the refrigerant circuit 3 also carries the refrigerant. In other words, the second secondary expansion valve 313 allows the refrigerant to circulate in said second branch 310.

[0077] Thus, when the refrigerant reaches the first divergence point 311, a portion of the refrigerant is directed towards the first expansion valve 32 and towards the fourth heat exchanger 36, as described with reference to the figure 2 and another part of this refrigerant is directed to the second expansion member 313 of the second branch 310, in which its pressure is lowered, before joining the fifth heat exchanger 314. In the fifth heat exchanger 314, the refrigerant, circulating in a first pass 3141 of the fifth heat exchanger 314, captures heat from the heat transfer fluid circulating in a second pass 3142 of the fifth heat exchanger 314, which is hotter than the refrigerant.

[0078] The refrigerant leaves the fifth heat exchanger 314 and joins the first convergence point 312 in order to be directed to the compression device 31. At the same time, the heat transfer fluid which has been cooled in the fifth heat exchanger 314 circulates in the second heat transfer fluid loop 5 so as to cool the electrical storage device 11.

[0079] Such a mode of operation can in particular be implemented during a rapid charging phase of the electrical storage device 11 so as to reduce its heating, the thermal treatment system 1 thus simultaneously ensuring the thermal treatment of said electrical storage device 11 and the maintenance of an acceptable level of thermal comfort inside the passenger compartment.

[0080] According to a second embodiment, substantially identical to the first embodiment as described with reference to figures 1 à 3 The heat treatment system 1 can be configured so that the bottle is integrated into the first heat exchanger 33 and not positioned between the outlet of the first heat exchanger 33 and the inlet of the second heat exchanger 34. This alternative is shown in the figures 1 à 3 by bottle 4', illustrated in dotted lines in the first heat exchanger 33.

[0081] By virtue of this arrangement, a terminal section 38 of the first heat exchanger 33, comprising the outlet of the first heat exchanger 33, is supplied solely with refrigerant in liquid form from the cylinder 4'. It follows from such an architecture that, when the refrigerant circuit 3 of the heat treatment system 1 operates in an air conditioning mode, substantially identical to that previously described with reference to the figure 2 , or according to an air conditioning and thermal treatment mode of an electrical storage device 11, as described above with reference to the figure 3 The first heat exchanger 33 functions partially as a subcooler. In particular, a first section of the first heat exchanger 33 functions, as previously described, as a condenser, while the terminal section 38 functions as a subcooler.

[0082] The refrigerant circulating in the heat treatment system 1 is thus subjected to three successive subcoolings, respectively in the first heat exchanger 33, in the second heat exchanger 34 and in the third heat exchanger 35, and the thermal requirements of the heat treatment system 1 can be reduced.

[0083] THE figures 4 à 6 illustrate a third embodiment of the heat treatment system 1. In the heat treatment system 1 as illustrated in the figure 6 The main branch 300 and second branch 310 of the refrigerant circuit 3, as well as the various components they comprise, are identical to those detailed with reference to figures 1 à 3 the difference being that refrigerant circuit 3 is without bottle 4.

[0084] Similar to what has been previously described, the refrigerant circuit 3 may include, between the outlet of the fourth heat exchanger 36 and the inlet of the second part 372 of the internal heat exchanger 37, an accumulation device, not shown, in which the liquid phase and the gaseous phase are separated so that only the gaseous phase is subsequently sent to the second part 372 of the internal heat exchanger 37 and then, again, to the compression device 31.

[0085] The refrigerant circuit 3 includes a third branch 320 extending between a divergence point, hereinafter referred to as the second divergence point 321, located between the outlet of the compressor 31 and an inlet of the first heat exchanger 33, and a convergence point, hereinafter referred to as the second convergence point 322, located between the outlet of the third heat exchanger 35 and the inlet of the fourth heat exchanger 36. The third branch 320 includes at least one heat exchanger 323 configured to be used at least as a condenser. By way of example, the heat exchanger 323 may implement heat exchange between the refrigerant and a heat transfer fluid or between the refrigerant and an airflow intended to be sent to the passenger compartment.

[0086] The third branch 320 allows, in particular, the bypassing of the fourth heat exchanger 36. Such a bypass can be implemented, for example, when the circuit is operating in heating mode in order to send a flow of hot air into the vehicle's passenger compartment. To this end, the third branch 320 may include a refrigerant flow control device 324, for example, a two-way valve, configured to direct the refrigerant to the main branch 300 or to the third branch 320.

[0087] The refrigerant circuit 3 also includes a fourth branch 330 which extends between a divergence point, hereinafter referred to as the third divergence point 331, located between the outlet of the third heat exchanger 35 and the inlet of the fourth heat exchanger 36, and a convergence point, hereinafter referred to as the third convergence point 332, located between the outlet of the compression device 31 and the inlet of the first heat exchanger 33. The fourth branch 330 includes at least one expansion member, referred to as the third expansion member 333.

[0088] Finally, the refrigerant circuit 3 includes a fifth branch 360 extending between a divergence point, hereafter referred to as the fourth divergence point 361, located between an outlet of the second heat exchanger 34 and an inlet of the third heat exchanger 35, and a convergence point, hereafter referred to as the fourth convergence point 362, located between the outlet of the fourth heat exchanger 36 and the inlet of the compressor device 31. The fifth branch 360 also contributes to bypassing the fourth heat exchanger 36, particularly when the refrigerant circuit 3 is operating in heating mode, as described below. Specifically, the fifth branch 360 may include at least one refrigerant flow control device 363, for example, a two-way valve, configured to direct the refrigerant to the main branch 300 or to the fifth branch 360.

[0089] The heat transfer fluid loop 2 of the present heat treatment system 1 differs from the first and second embodiments in that it comprises, in addition to the main line 200, a second line 210 branching off from said main line 200. The second line 210 extends between a branch point 201, located between an outlet of the circulation element 21 and an inlet of the primary radiator 22, and a connection point 202, located between an outlet of the primary radiator 22 and the inlet of the second heat exchanger 34. The second line 210 comprises at least one heat transfer fluid flow control device 23 configured to selectively direct the heat transfer fluid to the main line 200 and / or to the second line 210. In the illustrated example, the control device 23 is a three-way valve located at the branch point 201.Alternatively, the heat transfer fluid loop 2 may include two heat transfer fluid flow control devices 23, for example two two-way valves, arranged in the main line 200 and in the second line 210.

[0090] There figure 5 represents the third embodiment when operating according to the first operating mode of the heat treatment system 1, that is, when the refrigerant circuit 3 is configured to operate in air conditioning mode. In such an operating mode, the circulation of the refrigerant in the refrigerant circuit 3 is identical to that of the first and second operating modes, the description given with reference to the figure 2 is thus transposable to the present embodiment and the circulation of the refrigerant is limited to the main branch 300. The second branch 310, the third branch 320, the fourth branch and the fifth branch are not traversed by the refrigerant, the circulation of the refrigerant in the said branches being able to be hindered by at least one of the expansion members 313, 333 and / or one of the regulating members or devices 324, 353 of the flow of the refrigerant circuit 3 included in the corresponding branches.

[0091] For example, when the refrigerant reaches the second divergence point 321, the combined effect of closing the third control valve 324 of the third branch 320 and opening a control valve 39 of the main branch 300 prevents the refrigerant from circulating in the third branch 320. As a result, the refrigerant flows in the main branch 300 towards the first heat exchanger 33, which functions as a condenser. Similarly, when the liquid refrigerant exiting the second heat exchanger 34 passes the fourth divergence point 361, closing the flow control valve 353 of the fifth branch 360 ensures that the refrigerant is sent to the third heat exchanger 35.The same applies to the refrigerant fluid exiting the third heat exchanger 35 which, when it passes the third divergence point 331, remains on the main branch due to the closure of the third expansion device 333.

[0092] In the heat transfer fluid loop 2, the control device 23 restricts the flow of the heat transfer fluid in the second line 210 so that the heat transfer fluid flows in the main line 200 along a path identical to that previously described with reference to the figure 2 .

[0093] It is understood that this embodiment can also implement the second operating mode ensuring the simultaneous heat treatment of the passenger compartment and the electrical storage device 11, the description given previously with reference to the figure 3 being transposable to the present alternative.

[0094] There figure 6 illustrates a third operating mode of the heat treatment system 1 according to the third embodiment as illustrated in the figure 4 , in which the refrigerant circuit 3 operates in passenger compartment heating mode.

[0095] In this third example of operation, the second branch 310 of the refrigerant circuit 3, thermally coupled to the electrical storage device 11, is not traversed by the refrigerant.

[0096] The refrigerant leaves the compression device 31 in a gaseous state, at high pressure and high temperature, and flows towards the second divergence point 321. The control valve 39 of the main branch 300 is closed, while the control valve 324, located in the third branch 320, is open. The compressed refrigerant is thus diverted from the main branch 300 and sent to the third branch 320, bypassing the first heat exchanger 33.

[0097] The refrigerant is then returned to the main branch 300 at the second convergence point 322, and then passes through the first part 371 of the internal heat exchanger 37, the operation of which is identical to that described previously. The refrigerant leaves the internal heat exchanger 37 in at least a partially liquid state and flows along the main branch 300 to the third divergence point 331, where, through the opening of the third expansion valve 333, it is sent to the fourth branch 330.

[0098] Advantageously, the main branch 300 may also include at least one check valve 391, disposed between the outlet of the third heat exchanger 35 and the third divergence point 331 and configured to impede the circulation of the refrigerant in the main branch 300 when it is sent towards the fourth branch 330.

[0099] The refrigerant passes through the third expansion valve 333, where it undergoes expansion, and emerges in a two-phase state. This expanded refrigerant then passes through the third convergence point 332 and enters the first heat exchanger 33, which is used as an evaporator and configured to facilitate heat exchange between the refrigerant and the outside airflow FA1 to the passenger compartment.

[0100] For example, the refrigerant entering the first heat exchanger 33 may have a temperature of around -30°C, while the outside air flow FA1 has a higher temperature, for example, around -20 to -5°C. Also, since the primary radiator 22 is off when the refrigerant circuit 3 is operating in heating mode, the outside air flow FA1 involved in the heat exchange in the first heat exchanger 33 is not preheated by passing through the primary radiator 22. The outside air flow FA1 thus transfers its heat to the colder refrigerant circulating in the first heat exchanger 33, thereby evaporating it.

[0101] It should also be noted that, when the outside airflow FA1 has such temperatures, it can directly ensure the cooling of the electrical storage device 11 and / or at least one element 12 of the electric traction chain.

[0102] The refrigerant exits the first heat exchanger 33 in at least a partially gaseous state and is sent to the second heat exchanger where it undergoes a second evaporation. Indeed, according to the third operating mode, the second heat exchanger can be configured to function as a second evaporator. Thus, the heat transfer fluid circulating in the second pass 342 of the second heat exchanger 34 transfers heat to the refrigerant circulating in the first pass 341 of the second heat exchanger. The latter thus exits heated and in an essentially gaseous state and then circulates to the fourth divergence point 361 of the refrigerant circuit 3.With the refrigerant flow control device 363 of the fifth branch 360 open, the refrigerant bypasses the third heat exchanger 35 and is sent to the fifth branch 360, towards the fourth convergence point 362 and the second part 372 of the internal heat exchanger 37.

[0103] In the heat transfer fluid loop, the primary radiator 22 is inactive. The heat transfer fluid circulates in loop 2 to the control device 23 located at the branch point 201. This device is selectively opened to impede the circulation of the heat transfer fluid towards the primary radiator 22 and to allow its circulation on the second line 210. At the connection point 202, the heat transfer fluid is returned to the main line 200 towards the second heat exchanger 34, which, as previously explained, is used as an evaporator for the refrigerant circulating in circuit 3. The heat transfer fluid circulating in the second pass 342 of the second heat exchanger 34, being cooler than the refrigerant, transfers heat to the latter.The cooled heat transfer fluid is returned to the circulation element 21 and then to at least one element 12 of the traction chain, which it can thus advantageously cool.

[0104] Advantageously, the first and second embodiments as described with reference to figures 1 à 4 may also include the third branch and / or the fourth branch and / or the fifth branch as described in reference to figures 4 à 6 the characteristics and elements relating to these branches can, according to alternative embodiments, be transposed to the first and second embodiments.

[0105] THE figures 7 à 11 These two embodiments of the heat treatment system 1 illustrate how the third heat exchanger 35 facilitates heat exchange between the refrigerant circulating in circuit 3 and the heat transfer fluid circulating in loop 2. Unlike the third heat exchanger 35 described previously, which facilitates heat exchange between the outside airflow FA1 and the refrigerant, the positioning of the third heat exchanger 35 in these embodiments is not required in an area where the outside airflow FA1 circulates, for example, at the front. Therefore, such a third heat exchanger 35 can advantageously be located away from the first heat exchanger 33, thus facilitating its installation within the vehicle and reducing the space required by the heat treatment system 1 at the front of the vehicle.Furthermore, such a third heat exchanger 35 can have smaller dimensions than the third heat exchanger 35 as described in reference to the first three embodiments while maintaining similar cooling capacities.

[0106] There figure 7 represents a fourth embodiment of the present invention, the refrigerant circuit 3 of which is substantially identical to that previously described for the third embodiment. The description relating to said circuit, made with reference to figures 4 à 6 , is thus transposable to the present embodiment.

[0107] As previously explained, the refrigerant circuit 3 may include, between the outlet of the fourth heat exchanger 36 and the inlet of the second part 372 of the internal heat exchanger 37, the accumulation device 6.

[0108] Loop 2 of the heat transfer fluid, similarly to what has been described for the third embodiment with reference to figures 4 à 6 , includes the main line 200 on which are arranged the heat transfer fluid circulation element 21, the primary radiator 22 and the second heat exchanger 34. The heat transfer fluid loop 2 includes the second line 210 which extends in a branch off from the main line 200 between the branch point 201 as previously described and the connection point 202. This second line 210 may include at least the heat transfer fluid flow control device 23.

[0109] Also, according to this embodiment, the heat transfer fluid loop 2 includes a bypass line 220 which comprises at least the third heat exchanger 35 and a secondary radiator 24 configured to implement heat exchange between the heat transfer fluid and the outside airflow FA1 to the passenger compartment. The secondary radiator 24 is particularly positioned upstream of the primary radiator 22 along the direction S3 of the outside airflow FA1 to the passenger compartment, so that, at the front of the vehicle, the following sequence is found, along the direction S3 of the outside airflow: the secondary radiator 24, then the primary radiator 22, and then the first heat exchanger 33.

[0110] The bypass line 220 extends between a separation point 221, located between an outlet of the heat transfer fluid circulation element 21 and the inlet of the primary radiator 22, and a junction point 222, located between the outlet of the second heat exchanger 34 and an inlet of the circulation element 21. The bypass line 220 advantageously allows the simultaneous, parallel circulation of the heat transfer fluid in the primary radiator 22 and then the second heat exchanger 34 on the one hand and in the secondary radiator 24 and the third heat exchanger 35 on the other hand.

[0111] There figure 8 represents the heat treatment system 1 according to the fourth embodiment when it operates according to the first operating mode, that is to say when the refrigerant circuit 3 is configured to operate in air conditioning mode.

[0112] In the refrigerant circuit 3, the circulation of the refrigerant is limited to the main branch 300 of the circuit 3, the path of the refrigerant thus being substantially identical to that previously described for the first embodiments. The description given with reference to the figure 2 or in reference to the figure 5 is thus transposable to the present embodiment with the difference that, in the present embodiment, the heat treatment system may be without a bottle or, alternatively, the bottle 4 may be disposed between the outlet of the second heat exchanger 34 and the inlet of the third heat exchanger 35, for example downstream of the fourth divergence point 361 according to the direction of circulation of the refrigerant in the circuit 3. It follows from such an architecture that only the third heat exchanger 35 functions as a sub-cooler instead of at least the second heat exchanger 34 and the third heat exchanger 35 as previously described.

[0113] It is understood that this embodiment may also implement the second mode of operation, as previously described with reference to the figure 3 , in order to simultaneously ensure the thermal treatment of the passenger compartment and the thermal treatment of the electrical storage device 11, the description of the refrigerant flow path in the second branch 310 made with reference to the figure 3 being transposable to the present embodiment.

[0114] In the heat transfer fluid loop 2, the heat transfer fluid is circulated along the main line 200 to the control valve 23 located at the branch point 201. This valve is selectively opened to prevent the flow of heat transfer fluid to the second line 210 and to direct the heat transfer fluid towards the primary radiator 22. At the separation point 221, the heat transfer fluid is divided into two portions. A first portion 301 of the heat transfer fluid is sent along the branch line 220 to the secondary radiator 24, while a second portion remains on the main line 200 and circulates towards the primary radiator 22.

[0115] On the main line 200, the heat transfer fluid enters the primary radiator 22 and discharges heat into the outside air stream. Advantageously, the primary radiator 22 is positioned in the loop 2 so as to discharge heat absorbed from at least one element 12 of the traction chain into the outside air stream FA1. The heat transfer fluid then flows through the second pass 342 of the second heat exchanger 34, where it absorbs heat from the warmer refrigerant flowing through the first pass 341 of the second heat exchanger 34. The heat transfer fluid is then returned to the circulation element 21.

[0116] In the bypass line 220, the heat transfer fluid circulating in the secondary radiator 24, being warmer than the outside airflow FA1, transfers heat to the latter. The secondary radiator 24 is positioned in the loop so as to discharge heat absorbed from at least one element 12 of the traction chain into the outside airflow FA1. The secondary radiator 24 is advantageously arranged to allow heat exchange between the heat transfer fluid and the entire outside airflow FA1; it therefore exhibits good heat exchange efficiency, and the temperature of the heat transfer fluid can be lowered to a temperature close to that of the outside airflow FA1. The cooled heat transfer fluid is then sent to the third heat exchanger 35, used as a subcooler, while the heated outside airflow FA1 circulates through the primary radiator 22 as previously described.The heat transfer fluid circulating in a second pass 352 of the third heat exchanger 35 captures the heat from the cooler refrigerant circulating in a first pass 351 of the third heat exchanger 35, which comes from the second heat exchanger 34 and lowers the temperature of the latter to a temperature close to that of the outside airflow FA1 arriving at the front of the vehicle.

[0117] The heat transfer fluid from the secondary radiator 24 is thus advantageously lowered to a temperature close to that of the outside airflow. This design of the heat treatment system 1 therefore advantageously reduces the temperature drop in the third heat exchanger 35, thereby improving the thermal capacity of the system.

[0118] There figure 9 represents the heat treatment system 1 according to the fourth embodiment when it implements the third operating mode, that is, when the refrigerant circuit 3 is configured to operate in heating mode. The path of the refrigerant in the circuit is similar to that previously described for the third embodiment, the description given with reference to the figure 6 thus being transposable to the present embodiment.

[0119] In loop 2 of the heat transfer fluid, similarly to what was described in reference to the figure 6 The control device 23 obstructs the circulation of the heat transfer fluid to the primary radiator 22. In the present embodiment, this results in the circulation to the secondary radiator 24 also being prevented, with the primary radiator 22 and the secondary radiator 24 thus being inactive.

[0120] Thus, at the branch point 201, the heat transfer fluid is sent to the second line 210 and then returned to the main line 200 upstream of the second heat exchanger 34, following the direction of flow S1 of the heat transfer fluid in the loop. As previously explained, the heat transfer fluid, being warmer than the refrigerant circulating in the first pass 341 of the second heat exchanger 34, transfers heat to the latter, causing it to evaporate. The heat transfer fluid thus exits the second heat exchanger 34 cooled and is then returned to the circulation element 21 and at least one element 12 of the traction chain to allow for its cooling.

[0121] There figure 10 represents a fifth embodiment of the present invention in which the third heat exchanger 35 implements heat exchange between the refrigerant circulating in the circuit and the heat transfer fluid circulating in the loop. In this embodiment, the refrigerant circuit 3 is substantially identical to that previously described with reference to the third and fourth embodiments. The description of said circuit, given with reference to the figure in figures 4 And 7 This is therefore applicable to the present embodiment. The present embodiment further reduces the temperature difference between the heat transfer fluid at the outlet of the secondary radiator 24 and the outside air flow FA1, thus improving the thermal performance of the heat treatment system 1.

[0122] Similar to the fourth embodiment, the heat treatment system may be without a bottle, as shown herein, or may include the bottle 4, disposed between the outlet of the second heat exchanger 34 and the inlet of the third heat exchanger 35. The same applies to the accumulator as previously mentioned, disposed upstream of the second part 372 of the internal heat exchanger 37 according to the direction of circulation S2 of the refrigerant in the circuit 3.

[0123] Also, the fifth embodiment differs from the third embodiment by the absence of the second line 210 and by a different arrangement of the bypass line 220 in the heat transfer fluid loop 2. In this fifth embodiment, the bypass line 220 extends between the separation point 221, this time located between the outlet of the primary radiator and the inlet of the second heat exchanger, and the junction point 222, located, as previously described, between the outlet of the second heat exchanger 34 and the inlet of the circulation element 21.Similar to the fourth embodiment, the bypass line 220 includes at least the third heat exchanger 35 and the secondary radiator 24 configured to facilitate heat exchange between the heat transfer fluid and the outside airflow. The secondary radiator 24 is located upstream of the primary radiator 22 in the direction S3 of the outside airflow to the passenger compartment. Similar to what was previously described with reference to the fourth embodiment, the secondary radiator 24 is advantageously positioned to allow heat exchange between the heat transfer fluid and the entire outside airflow rate FA1. It thus exhibits good heat exchange efficiency and allows the temperature of the heat transfer fluid to be lowered to a temperature close to that of the outside airflow FA1.

[0124] There figure 11 represents the heat treatment system 1 according to the fifth embodiment when it implements the first mode of operation, that is to say in which the refrigerant circuit 3 is configured to operate in air conditioning mode.

[0125] In the refrigerant circuit 3, the circulation of the refrigerant is limited to the main branch 300, the path of the refrigerant being substantially identical to that previously described for the third or fourth embodiments, so that the description given therein with reference to the figures 5 And 8 is transposable to the present method, with the exception of the presence or positioning of the bottle.

[0126] It is understood that this embodiment may also implement the second operating mode as previously described so as to simultaneously ensure the thermal treatment of the passenger compartment and the thermal treatment of the electrical storage device 11, the description of the refrigerant flow path being made with reference to the figure 3 can therefore also be applied to the present embodiment.

[0127] In the heat transfer fluid loop 2, the heat transfer fluid is circulated through the main line 200 to the primary radiator 22, where it releases heat into the cooler outside air stream. The cooled heat transfer fluid exits the primary radiator 22 and circulates through the main line 200 to the separation point 221. There, a first portion of the heat transfer fluid is sent to the second heat exchanger 34, while a second portion is sent through the bypass line 220 to the secondary radiator 24 for further cooling.

[0128] As previously explained with reference to the figure 8 , in the second heat exchanger 34, the heat transfer fluid captures heat from the warmer refrigerant circulating in the first pass 341 of the second heat exchanger 34. This heat transfer fluid is then returned to the circulation element 21, for example so as to allow the cooling of at least one element 12 of the traction chain.

[0129] In the bypass line 220, the second portion of heat transfer fluid, previously cooled in the primary radiator 22, enters the secondary radiator 24. The heat transfer fluid transfers heat to the cooler outside air stream and exits the secondary radiator 24 at a temperature lower than that observed at the outlet of the primary radiator 22 and close to the temperature of the outside air stream FA1. This heat transfer fluid is then sent to the second pass 352 of the third heat exchanger 35, which is used as a subcooler, where it absorbs heat from the warmer refrigerant fluid exiting the second heat exchanger 34. The temperature of the refrigerant circulating in the first pass 351 of the third heat exchanger 35 is thus lowered to a temperature close to that of the outside air stream FA1.The heat transfer fluid then circulates on the main line 200 so as to allow, in particular, the cooling of at least one element 12 of the electric traction chain.

[0130] Such an architecture of the heat treatment system 1 ensures two successive coolings of the second fraction of heat transfer fluid so as to lower its temperature further, thereby optimizing the subcooling of the refrigerant at the third heat exchanger 35. Indeed, at the inlet of the secondary radiator 24, the second fraction of heat transfer fluid has a lower temperature than that which could be observed at the same point in the fourth embodiment as previously described with reference to the figure 7The temperature difference between the heat transfer fluid and the outside airflow FA1 in the secondary radiator 24 is thus reduced compared to the fourth embodiment. The flow path of the second portion of heat transfer fluid is therefore comparable to the circulation of a fluid in a heat exchanger comprising two counter-current layers, which is thermally more efficient.

[0131] The present invention thus proposes a vehicle heat treatment system comprising at least one refrigerant circuit in which a first, second, and third heat exchanger are arranged between a compression device and an expansion device of said circuit, at least the second and / or third heat exchanger being configured to operate as a subcooler so as to subcool the refrigerant in order to improve the coefficient of performance of the system as a whole. The heat treatment system also comprises at least one heat transfer fluid loop having at least one primary radiator located at the front of the vehicle, upstream of the first heat exchanger of the circuit in the direction of airflow from outside the vehicle's passenger compartment.

[0132] The present invention is not limited to the means and configurations described and illustrated herein, and also extends to any system falling within the scope defined by the claims. In particular, the architecture of the heat transfer fluid circulation loop and the architecture of the refrigerant circuit may be modified without prejudice to the invention, provided that such modifications fall within the scope defined by the claims.

Claims

1. Thermal treatment system (1) intended for a vehicle comprising at least one refrigerant circuit (3) and at least one heat transfer fluid loop (2): - the refrigerant circuit (3) comprising at least one compression device (31), one expansion member (32), one first heat exchanger (33) configured to exchange heat between the refrigerant and an air flow (FA1) external to an interior of the vehicle, one second heat exchanger (34) configured to exchange heat between the refrigerant and the heat transfer fluid circulating in the loop (2) and one fourth heat exchanger (36) configured to exchange heat between the refrigerant and an air flow (FA2) internal to the interior; - the heat transfer fluid loop (2) comprising, on a main line (200), the second heat exchanger (34) and at least one primary radiator (22) configured to exchange heat between the air flow (FA1) external to the interior of the vehicle and the heat transfer fluid; characterized in that the refrigerant circuit (3) comprises a third heat exchanger (35) configured to exchange heat between the refrigerant and the external air flow (FA1) or between the refrigerant and the heat transfer fluid and in that the first heat exchanger (33), the second heat exchanger (34) and the third heat exchanger (35) are disposed in the refrigerant circuit (3) between an outlet of the compression device (31) and an inlet of the expansion means (32), the primary radiator (22) being disposed upstream of the first heat exchanger (33) according to a direction of circulation (S3) of the external air flow (FA1).

2. Thermal treatment system (1) according to the preceding claim, wherein the second heat exchanger (34) and the primary radiator (22) are disposed in the main line (200) of the heat transfer fluid loop (2) such that the primary radiator (22) discharges heat energy captured by the second heat exchanger (34) into the external air flow (FA1).

3. Treatment system according to any one of the preceding claims, wherein the heat transfer fluid loop (2) is thermally coupled to at least one element (12) of an electric powertrain of the vehicle.

4. Thermal treatment system (1) according to any one of the preceding claims, wherein the refrigerant circuit (3) is a closed circuit comprising at least one main leg (300) on which at least the compression device (31), the first heat exchanger (33), the second heat exchanger (34), the third heat exchanger (35), the expansion member (32), referred to as the first expansion member (32), and the fourth heat exchanger (36) are successively arranged, the refrigerant circuit (3) comprising a second leg (310) which extends from a point of divergence (311), disposed between an outlet of the third heat exchanger (35) and an inlet of the fourth heat exchanger (36), and a point of convergence (312), disposed between an outlet of the fourth heat exchanger (36) and an inlet of the compression device (31), the second leg (310) comprising at least one expansion member, referred to as the second expansion member (313), and one fifth heat exchanger (314) thermally coupled to an electrical storage device (11) of the vehicle.

5. Thermal treatment system (1) according to the preceding claim, wherein the refrigerant circuit (3) comprises a third leg (320) which extends between a point of divergence, referred to as the second point of divergence (321), disposed between the outlet of the compression device (31) and an inlet of the first heat exchanger (33), and a point of convergence, referred to as the second point of convergence (322), disposed between the outlet of the third heat exchanger (35) and the inlet of the fourth heat exchanger (36), the third leg (320) comprising at least one heat exchanger (323) used as a condenser, the refrigerant circuit (3) comprising a fourth leg (330) which extends between a point of divergence, referred to as the third point of divergence (331), disposed between the outlet of the third heat exchanger (35) and the inlet of the fourth heat exchanger (36), and a point of convergence, referred to as the third point of convergence (332), disposed between the outlet of the compression device (31) and the inlet of the first heat exchanger (33), the fourth leg (330) comprising at least one expansion member referred to as the third expansion member (333).

6. Thermal treatment system (1) according to any one of the preceding claims, wherein the refrigerant circuit (3) comprises a fifth leg (360) which extends between a point of divergence, referred to as the fourth point of divergence (361), disposed between an outlet of the second heat exchanger (34) and an inlet of the third heat exchanger (35), and a point of convergence, referred to as the fourth point of convergence (362), disposed between the outlet of the fourth heat exchanger (36) and the inlet of the compression device (31).

7. Thermal treatment system (1) according to any one of the preceding claims, wherein the third heat exchanger (35) is configured to exchange heat between the refrigerant and the air flow (FA1) external to the interior, and wherein the third heat exchanger (35) is disposed upstream of the first heat exchanger (33) according to the direction of circulation (S3) of the air flow (FA1) external to the interior.

8. Thermal treatment system (1) according to the preceding claim, wherein the heat transfer fluid loop (2) comprises a second line (210) which branches off from the main line (200) between a branch point (201), disposed between an outlet of the circulation element (21) and an inlet of the primary radiator (22), and a connection point (202), disposed between an outlet of the primary radiator (22) and the inlet of the second heat exchanger (34), the second line (210) comprising at least one member (23) for controlling the heat transfer fluid flow.

9. Thermal treatment system (1) according to any one of Claims 1 to 6, wherein the third heat exchanger (35) is configured to exchange heat between the refrigerant and the heat transfer fluid.

10. Thermal treatment system (1) according to the preceding claim, wherein the heat transfer fluid loop (2) comprises a branch line (220) which has at least the third heat exchanger (35) and a secondary radiator (24) configured to exchange heat between the heat transfer fluid and the external air flow (FA1), the secondary radiator (24) being disposed upstream of the primary radiator (22) according to the direction of circulation (S3) of the air flow (FA1) external to the interior.

11. Thermal treatment system (1) according to the preceding claim, wherein the branch line (220) extends between a separation point (221), disposed between the outlet of the element (21) for circulating the heat transfer fluid and the inlet of the primary radiator (22), and a joining point (222), disposed between an outlet of the second heat exchanger (34) and an inlet of the circulation element (21).

12. Thermal treatment system (1) according to Claim 10 or 11, wherein the heat transfer fluid loop (2) comprises a second line (210) which branches off from the main line (200) between a branch point (201), disposed between an outlet of the circulation element (21) and an inlet of the primary radiator (22), and a connection point (202), disposed between an outlet of the primary radiator (22) and the inlet of the second heat exchanger (34), the second line (210) comprising at least one member (23) for controlling the heat transfer fluid flow.

13. Thermal treatment system (1) according to Claim 10, wherein the branch line (220) extends between a separation point (221), disposed between the outlet of the primary radiator (22) and the inlet of the second heat exchanger (34), and a joining point (222), disposed between the outlet of the second heat exchanger (34) and the inlet of the circulation element (21).