Propane thermal management system for vehicles, particularly electric-powered ones.

Abstract

The invention relates to a thermal management device for a vehicle, wherein the thermal management device comprises a phase-change fluid circuit (1), of the propane type, the circuit (1) being connected via a first heat exchanger (14) to a first heat exchanger circuit (2), said first heat exchanger (14) being, in particular, a cooler (14), the circuit (1) being connected via a second heat exchanger (11) to a second heat exchanger circuit (3), said second exchanger (11) being, in particular, a condenser (11), each of the first and second heat exchanger circuits (2, 3) comprising a means for controlling the flow rate of a heat transfer fluid, such that said first and second heat exchangers (11, 14) are of the propane / water type. The invention also relates to a vehicle having such a device, as well as a cooling method. Figure for the abstract: 1

Description

Title of the invention: Propane thermal management device for vehicles, in particular electric-powered vehicles.

[0001] The invention relates to the field of vehicles, particularly automobiles, which include thermal management devices. The vehicle is preferably of the electric propulsion type.

[0002] Various types of refrigerants are known for regulating the temperature of the passenger compartment or battery of an electric vehicle. Each refrigerant is assigned a greenhouse effect coefficient, and it is well established that refrigerant 1234yf® has a significantly lower greenhouse effect coefficient than the previous refrigerant 134a®. However, this important improvement faces other obstacles to its continued commercialization, notably the fact that it contains a fluorinated substance considered hazardous to public health.

[0003] Other types of natural refrigerant exist, such as propane, so the replacement of 1234yf® refrigerant in air conditioning circuits is to be considered in the near future. The major drawback of using carbon dioxide as a refrigerant is that it requires an air conditioning loop with high pressure resistance, on the order of 125 bar for example, as well as resistance to operating temperatures of around 150°C. Due to these pressure and temperature parameters, the risk of leaks is a significant obstacle to its widespread adoption, particularly in mass production within the automotive sector. Using propane as a refrigerant is less demanding because the air conditioning system can be fully operational with an operating pressure of approximately 25 bar and an operating temperature of around 100°C. Therefore, a propane-based air conditioning system tends to be similar to a traditional system using 1234yf® refrigerant, making it possible to consider switching refrigerants without requiring significant modifications to existing air conditioning circuits. However, it is essential to adhere to the safety requirements specific to the nature of propane, and to design a compact air conditioning loop to simplify leak management.

[0004] Replacing the 1234yf® refrigerant with propane can be easily done, taking into account another factor that has a significant impact on the use of propane as a refrigerant, namely its very high degree of flammability, which classifies it as a highly hazardous gas. To overcome this problem, the amount of propane that can be carried on a vehicle must be limited, in particular by developing an ultra-compact air conditioning loop.

[0005] It is within this framework that the present invention falls. The invention relates to a thermal management device for a vehicle, in particular an electric vehicle comprising at least one element of the powertrain and a vehicle interior to be thermally regulated, characterized in that the thermal management device comprises a phase change fluid circuit of the propane type, in that the circuit is connected by a first heat exchanger to a first heat exchange circuit, said first heat exchanger being in particular a cooler, in that the circuit is connected by a second heat exchanger to a second heat exchange circuit, said second exchanger being in particular a condenser, each of the first and second heat exchange circuits comprising a means for controlling the flow of a heat transfer fluid, in particular water, such that said first and second heat exchangers are of the propane / water type.

[0006] The device that is the subject of the invention may further comprise the following characteristics, taken separately or in combination with each other: - the phase change fluid is propane, the mass content of which is between 100g and 200g, preferably 150g, - The phase-change fluid circuit comprises a compressor, condenser, expansion valve, and cooler, in that order, within a main fluid loop circulating when the compressor is activated. - The phase-change fluid circuit is housed in a hermetically sealed enclosure with a volume between 5 and 20 liters, particularly between 10 and 15 liters, preferably 10 liters. - the second heat exchange circuit includes a thermal loop in which are included at least the condenser, a radiator and a water pump arranged respectively in that order when the water pump is started up, the thermal loop of the second heat exchange circuit being in particular a third thermal loop of the device, - the second heat exchange circuit further includes at least one first component of an electric traction chain located at a branch connecting the condenser to the radiator, and / or a degassing tank located at a branch connecting the radiator to the water pump, - The first heat exchange circuit comprises a first thermal regulation loop and a second thermal regulation loop connected to each other by means of an interconnection device having branches such that one of the branches is a supply line to the second thermal regulation loop, and that the other of the branches is a drain pipe for the second thermal regulation loop, - it includes a means of controlling the flow rate from the first thermal regulation loop to the second thermal regulation loop, - the first thermal regulation loop includes an air exchanger designed to be cooled by a flow of air for the vehicle's passenger compartment, - the second thermal regulation loop includes a second component of an electric traction chain, in particular an electric battery, or a dielectric fluid cooler intended for cooling the second component of the electric traction chain, in particular the cells of an electric battery, - said flow control means is a regulating valve located at the connection branch or at a junction between the supply line of the second thermal regulation loop and the first thermal regulation loop, said junction being located at the outlet of the air exchanger of the first thermal regulation loop, - The first thermal regulation loop includes the phase-change fluid circuit cooler, a pump, and the air exchanger, in that order when the pump is started. - the first thermal regulation loop includes a degassing chamber, - the second thermal regulation loop includes a pump, the second component to be cooled in the electric traction chain, a radiator, a radiator bypass branch, and a bypass valve located at the junction between the branch containing the radiator and the bypass branch, - the bypass branch includes two junctions with said interconnection means, one with the supply line, the other for the discharge line, - it includes a control unit for the water pumps, compressor, expansion valve, as well as at least one temperature sensor connected to the control unit.

[0007] The invention also relates to a vehicle, in particular of the electric propulsion type, characterized in that it includes the thermal management device having at least one of the aforementioned characteristics.

[0008] The invention also relates to a method for cooling at least one element of the powertrain and / or a passenger compartment of a vehicle according to the preceding claim, characterized in that it comprises the steps of implementing the following thermal regulations: - of the phase-change fluid circuit, such that, when passenger compartment cooling is required, the coolant temperature at the cooler outlet is approximately zero degrees Celsius, by controlling the operation of the compressor and / or the expansion valve and / or the condenser, - of the second heat exchange circuit by controlling the operation of the water pump, - of the first loop of the first heat exchange circuit such that the temperature of the heat transfer fluid at the outlet of the air exchanger is between 0 and 5 degrees Celsius when cooling of the passenger compartment is requested, by a control of the operation of the water pump and / or the positioning of flaps regulating the airflow through the cooler and / or a cooler bypass valve, - of the second loop of the first heat exchange circuit such that the temperature of the coolant at the level of the second component to be cooled is greater than or equal to the temperature of the heat transfer fluid at the outlet of the air exchanger, while being between 10 and 30 degrees Celsius, preferably 18 degrees Celsius, by a control of the operation of the water pump and / or a bypass valve.

[0009] The method of the invention may further comprise the following features: - when the temperature of the heat transfer fluid at the outlet of the exhaust pipe is higher than the ambient air temperature, the bypass valve is partially closed in order to cool the heat transfer fluid by heat exchange with the ambient air in the radiator, - the step of implementing the thermal regulation of the first heat exchange circuit, in particular of the first and / or second thermal regulation loop, is carried out by said flow control means, which may be a three-way valve or a two-way valve located in one of the branches of said interconnection means, - the step of implementing the thermal regulation of the first heat exchange circuit, in particular of the first and / or second thermal regulation loop, is carried out by at least one adjustment means located at the level of the first heat exchange circuit, in particular at the level of a branch connecting the coolers together, and / or of the second heat exchange circuit, in particular at the level of a bypass branch, which tends to control the flow of heat transfer fluid circulating respectively at the level of the first and second thermal regulation loops.

[0010] The attached drawings represent, by way of example, a thermal management device for a vehicle, according to the invention. Fig. 1 schematically represents a thermal management device comprising a propane-type phase-change fluid circuit, intended in particular for automotive use, according to the invention; [Fig.2] represents a variant of the thermal management device of [Fig.1], [Fig.3] schematically represents a means of regulating the heat exchange between a heat transfer fluid and the air destined for the passenger compartment, of the thermal management device of the invention, [Fig.4] schematically represents a means of regulating the heat exchange between a heat transfer fluid and the air destined for the passenger compartment, of the thermal management device of the invention.

[0011] Fig. 1 represents a thermal management device comprising three distinct parts.

[0012] The first part relates to a phase-change fluid circuit 1 whose particularity lies in the use of propane as the phase-change fluid. The circuit in which the propane circulates is arranged inside a hermetically sealed enclosure, in that it is airtight so that any propane leakage cannot be dispersed into the ambient air.

[0013] Inside the enclosure are arranged a compressor 10, a second heat exchanger 11 of the condenser type, a reservoir 12, an expansion valve 13 and a first heat exchanger 14, of the cooler type, taken in that order according to the direction of fluid flow during the operation of the compressor. A main loop of the thermal management system consists of the compressor 10, the first and second heat exchangers 14 and 11, and the expansion valve 13, connected in series, each with inlet and outlet pipes for the fluid. The degassing system is not through-flow, meaning it includes a degassing tank connected to the main loop by a single pipe. This pipe connects between the first and second heat exchangers, specifically between the second heat exchanger 11 and the expansion valve 13, which is located upstream of the first heat exchanger 14. The degassing system includes a reservoir for separating the liquid from the vapor of the refrigerant, creating a reserve volume of refrigerant to compensate for volume variations in the air conditioning circuit.

[0014] According to an alternative embodiment not shown, the degassing device could be through-hole, in the sense that the tank would include separate inlet and outlet pipes.

[0015] The mass content of propane in the phase change fluid circuit 1 is less than 200g. It can be, for example, 150g. The first and second heat exchangers 14, 11 allow energy transfer between propane and a heat transfer fluid circulating respectively in first and second heat exchange circuits 2, 3.

[0016] The fluidic connection between the phase change circuit 1 and the first and second heat exchange circuits 2, 3 is made through the enclosure in which the circuit 1 is located, via in particular connectors. The heat exchange between the propane in circuit 1 and the heat transfer fluid in the first heat exchange circuit 2 takes place inside the enclosure. The heat exchange between the propane in circuit 1 and the heat transfer fluid in the second heat exchange circuit 3 takes place inside the enclosure. The volume of the enclosure is approximately 10 liters, so that all the components of the main loop of the thermal management device are constrained in terms of arrangement, which makes the thermal management device compact.

[0017] The first heat exchange circuit 2 will now be detailed. It includes a pump 20 whose operation will generate the circulation of a heat transfer fluid, such as glycol water. The first heat exchange circuit 2 includes a first thermal regulation loop L2. The first thermal regulation loop comprises, in series, the cooler 14, the pump 20, and an air heater 21, in that order during pump operation. A degassing device 22 is located between the air heater 21 and the cooler 14. The degassing device includes a non-through degassing vessel connected to the branch linking the air heater 21 to the cooler 14 by a connecting branch.

[0018] The arrangement of the jar in the first heat exchange loop L2, near the second heat exchange loop L4 also allows degassing of the second loop, without adding another degassing jar.

[0019] According to one embodiment, the degassing jar can be through-hole, which is more efficient in terms of degassing, but which also generates more volume of circulating water, thus increasing the thermal inertia of the loop.

[0020] Preferably, the air at the outlet of the air heater 21 is between 0°C and 10°C, preferably 4°C.

[0021] The first heat exchange circuit 2 includes a second thermal regulation loop L4, which, according to one embodiment, could include the degassing vessel 22. Regardless of the location of the degassing vessel 22, whether directly at the first or second thermal regulation loop L2, L4, its presence is essential to ensure proper operation. of the thermal management system, and also for any after-sales service, which required draining of the first heat exchange circuit 2. The second thermal regulation loop L4 includes a pump 40, a component to be cooled, a radiator 47, a bypass branch 46 of the radiator 47, and a bypass valve 48 located at the junction between the branch including the radiator 47 and the bypass branch. The component to be cooled is the second component 41 of the electric traction chain, namely a power electric battery. The control of the bypass valve 48 allows the flow of heat transfer fluid circulating through the radiator 47 to be regulated so that the thermal regulation of the second component 41 can be carried out by regulation on the ambient air according to the need for cooling and the temperature outside the vehicle.

[0022] Preferably, the regulation temperature of the second component 41 is between 15°C and 25°C, preferably 18°C.

[0023] The first heat exchange circuit 2 includes a means for interconnecting the first and second loops L2 and L4, fluidly linking the loops together. This interconnection means includes a branch 44, which is a supply line to the second thermal regulation loop L4, and a branch 45, which is a discharge line to the second thermal regulation loop L4.

[0024] The regulation temperature of the component to be cooled, respectively the cabin air and the power battery, is lower in the second thermal regulation loop L4 compared to the first thermal regulation loop L2.

[0025] The first circuit 2 further includes a means for controlling the flow 42 circulating from the first thermal regulation loop L2 to the second thermal regulation loop L4.

[0026] According to an embodiment illustrated in [Fig. 1], said flow control means 42 is a proportional three-way control valve 42a. The valve 42a is located at a junction between the supply line 44 of the second thermal control loop L4 and the first thermal control loop L2, said junction being located at the outlet of the air exchanger 21 of the first thermal control loop L2. The three-way valve 42a comprises one inlet and two outlets, one of the outlets being connected to the inlet of the cooler 14, the other of the outlets being connected to the supply branch 44 of said interconnection means for the first and second thermal control loops L2, L4.

[0027] According to an alternative embodiment shown in [Fig. 2], said flow control means 42 is a proportional two-way control valve 42b. The valve 42b is located at the level of the supply line 44 connecting the first thermal regulation loop L2 to the second thermal regulation loop L4.

[0028] According to the embodiment of [Fig.2], the bypass branch 46 comprises two junction nodes 43, each being in fluidic relationship with the interconnection means of the first and second loops L2, L4, respectively with the discharge line 45 and the supply line 44. To assist the regulation of the exchange flow rate Q5 between the two loops L2 and L4 by the two-way valve 42b, by the two lines 44 and 45, a flow adjustment means 49 is disposed between these two lines at the level of the second control loop L4, in particular between the two junction nodes 43, and at the level of the first control loop L2, in particular at the level of the branch connecting the air heater 21 to the cooler 14.

[0029] Upon exiting the heat exchanger 21, the flow Q2 can go to branch 44 or to the cooler 14, circulating through the branch comprising the junction with the degassing device 22. The flow rate is adjusted by a control means 49 located at the branch containing the reservoir 22. This means that the permeability of this branch is reduced in order to direct a portion of the flow Q2 towards branch 44 of the interconnecting means. The same principle is applied to the flow Q4 of the bypass branch 46: upon reaching the first node 43, the reduction in cross-sectional area achieved by the adjustment means 49, located between the nodes 43, promotes fluid circulation towards the discharge pipe 45, which creates the exchange flow Q5 between the first and second thermal control loops L2 and L4.Depending on the pressure distribution in the two loops L2 and L4, at least one of the adjustment means 49 assists the 2-way valve in regulating the target exchange flow rate Q5.

[0030] The use of a 3-way valve, as shown in [Fig. 1], does not require the use of an adjustment means, since the 3-way valve includes a means for restricting the flow to the branch where the degassing device 22 is located. The thermal management device also includes a second heat exchange circuit 3 which is in direct thermal relationship with the condenser 11 of the phase-change fluid circuit 1. This heat exchange link between the propane in gaseous form exiting the compressor 10 under pressure and the second heat exchange circuit 3 is intended to condense the propane into a high-pressure liquid. Upon exiting the condenser as a high-pressure liquid, the propane passes through the expansion valve 13 and then enters the heat exchanger 14, where it evaporates, cooling the fluid in the first circuit 2.

[0031] The second heat exchange circuit 3 can be a thermal loop L3 which includes in series a pump 30, the condenser 11 of the phase-change fluid circuit 1, the first component 32 to be cooled of the traction chain 32 and the Radiator 31 cools the air of the heat transfer fluid, in this order during the operation of the water pump 30. Upstream of the pump 30, a branch of the thermal loop L3 allows connection to a non-through degassing device, comprising a degassing jar 33. The nominal regulation temperature of the first component of the traction chain, which is preferably of the type of an electric traction motor of the vehicle, is higher than that of the second component 41 located in the second loop L4 of the first heat exchange circuit 2.

[0032] In [Fig. 3], the thermal management device includes an air-based temperature control system for the outlet temperature of the air heater 21. The four diagrams illustrate the different operating modes of this system according to different cabin cooling requirements. The system includes a fan 212 and hinged flaps 211, the latter being able to partially or completely block the airflow through the air heater 21 due to their positioning within the air heater 21's beam. The flaps can be positioned between the fan 212 and the air heater 21, depending on the airflow direction. Depending on the cabin cooling requirement, which can be expressed as a ventilation power requirement, the fan speed and the positioning of the movable flaps are modified.Thus, depending on the cooling power requirement P for the passenger compartment, which is between a minimum power Pmin and a maximum power Pmax, the flaps can be placed at the bypass openings of the heater and / or at the heater beam so that the airflow to the passenger compartment passes completely through the heater bypass openings, the heater beam, or partially through the heater bypass openings and the heater beam 21. The assembly consisting of the fan, the flaps and the air heater is preferably located in an air conditioning unit.

[0033] In [Fig. 4], the thermal management device may include an alternative embodiment of the temperature control system at the outlet of the air heater 21. The three diagrams illustrate the different operating modes of this system depending on the cooling capacity of the passenger compartment. In this case, the system includes a bypass valve 21a located upstream of the air heater 21, as well as a bypass branch 21b of the air heater 21. Depending on the passenger compartment cooling requirement, which can be expressed by a temperature of the heat transfer fluid at the outlet of the air heater 21, the bypass valve 21a is controlled. Depending on the power requirement, which ranges from minimum to maximum, the bypass valve 21a allows the quantity of heat transfer fluid circulating in the air heater 21 to be adjusted according to a total flow, a partial flow, or an interruption of the flow. heat transfer fluid within the air heater 21. Total flow means a cessation of flow in the bypass branch 21b. Partial flow means a flow of the heat transfer fluid both in the bypass branch 21b and within the air heater 21. Interruption of flow means a complete flow of the heat transfer fluid in the bypass branch 21b.

[0034] The assembly consisting of the bypass valve 21a and the bypass branch 21b can then be located outside the air conditioning unit, which makes it compact, in particular more compact than in the embodiment of [Fig.3].

[0035] The thermal management device of the invention further comprises software means, for example a computer 50 containing control laws to enable the operation of the pumps 20, 30, 40, the bypass valves 48, and the flow control means 42 to be performed according to at least one measured temperature T4 upstream of the second component 41 to be cooled in the electric traction chain. A temperature sensor 51 performs the measurement of the temperature T4. Pumps 20, 30 and 40 generate flow rates Q2, Q3 and Q4 of cooling fluid respectively.

[0036] The operating method of the thermal management device will now be detailed. The main loop L1 can be considered an ultra-compact refrigeration unit, in which the high-pressure liquid refrigerant enters the expansion valve 13, causing its pressure to drop. Upon entering the cooler 14, which can be considered an evaporator, the propane absorbs heat from the heat transfer fluid in the first thermal control loop L2. During this heat exchange, the propane evaporates and becomes a gas. Exiting the cooler 14, it passes through the expansion valve 13 again, but via a downstream section, known as the expansion valve outlet, which is separate from the upstream section through which the propane flows before passing through the cooler. Because the propane flows through the upstream and downstream sections of the expansion valve at different fluid pressures, the temperature is measured to allow for more precise control of the expansion valve 13.The gas is then drawn into the compressor 10 where it is compressed to increase its pressure. This compression also increases the gas temperature. The high-pressure gas passes into the condenser 11 where it is cooled by the heat transfer fluid of the thermal loop L3 of the second heat exchange circuit, before being transformed into a liquid. The heat recovered by the fluid in the thermal loop L3 can be used to heat the electric motor 32, or another component requiring heating, in winter, or released into the ambient air in summer if this heat is not needed, via the radiator 31. The high-pressure liquid refrigerant enters the reservoir 12 which... It also includes a filter. The propane is then filtered of any impurities and moisture before being directed to the regulator 13 and thus continuing the thermodynamic cycle.

[0037] The first control loop L2 is in direct contact with the cooler 14 of the phase-change fluid circuit 1. The temperature of the first control loop L2 is between 0 and 5°C to ensure cooling of the passenger compartment by the heat exchanger 21. The pump 20 is controlled by the control unit 50 to ensure a sufficient flow rate Q2 according to the passenger compartment's air conditioning demand, which depends on at least one other parameter chosen from among the ambient temperature, the degree of sunlight, and the passenger compartment volume, among others. The control valve 42a, controlled by the control unit 50, allows a constant flow rate Q2 in the heat exchanger 2, except at the branch of the circuit connecting the valve 42a and the degassing chamber 22. This difference in flow rate will be detailed below.

[0038] The thermal loop L3's main role is to cool the condenser 11 of the phase-change fluid circuit 1, via water circulating within the second heat exchange circuit 3. The radiator 31 also cools the other components of the electric drive system 32, such as the electric motor, power electronics, etc. In winter, the thermal loop L3 can also heat the passenger compartment and the traction battery via the first heat exchange circuit 2.

[0039] The second loop L4 of the first heat exchange circuit 2 provides cooling for battery 4L. Battery 41 can be cooled either by a water plate or by a dielectric fluid in which the battery is immersed. The temperature T4 of the water at the inlet of battery 41 is precisely regulated by the device of the invention. In this loop, there is a second pump 40 which provides a flow rate Q4 to the second component 41 of the powertrain to be cooled, namely battery 41, as well as a bypass valve 48, in particular a three-way type, which allows selection of the branch containing a radiator 47 designed to cool the battery without air conditioning in order to reduce energy consumption.This selection can take place for example in winter or when the ambient temperature is quite low, or simply when the battery temperature is quite high and the water cooled by the radiator is sufficient to maintain optimal battery operating conditions, for example while driving on the motorway where the air speed is high to allocate the required performance to the radiator to cool the 4L battery.

[0040] The bypass valve 48 allows the branch 46 to be selected in order to bypass the radiator and to connect the first and second control loops together so that the heat transfer fluid draws the cooling from the level of the Cooler 14. During the cooling of coil 41 by the heat transfer fluid circulating through the first thermal regulation loop L2, the flow control means 42 allows the transfer of a portion of the flow Q2 at a very low temperature T2 to the junction 43 where this very cold water mixes with the relatively hot water exiting the coil. The temperature T4 of the water destined for coil 41 is a mixture of the temperature T5 of the water exiting coil 41 and the temperature T2 of the water exiting the air heater 21. The exact value of the temperature T4 also depends on the flow rate Q5 in branch 44 of said interconnection means, and on the flow rate Q4: _ r5 *W4 -<25)+t ; -Q, 4

[0041] In this formula, the flow rate Q4 and the temperature T5 of the second thermal regulation loop L4 depend mainly on the battery cooling demand 41 imposed by the battery cooling specification. It follows that the control means 50 is capable of regulating a flow rate Q5 by the flow control means 42 in order to obtain precisely, and without temperature oscillation, a battery cooling temperature T4 using the measured temperature values ​​T2 and T5.

Claims

Demands

1. Thermal management device for an electric vehicle comprising at least one powertrain element and a vehicle passenger compartment to be thermally regulated, the thermal management device comprising a phase-change fluid circuit (1) of the propane type, the circuit (1) being connected by a first heat exchanger (14) to a first heat exchange circuit (2), said first heat exchanger (14) being a cooler (14), the circuit (1) being connected by a second heat exchanger (11) to a second heat exchange circuit (3), said second heat exchanger (11) being a condenser (11), each of the first and second heat exchange circuits (2, 3) comprising a means for controlling the flow of a water-type heat transfer fluid, such that said first and second heat exchangers (11, 14) are of the propane / water type,characterized in that the first heat exchange circuit (2) comprises a first thermal regulation loop (L2) and a second thermal regulation loop (L4) connected to each other via an interconnection means comprising branches (44, 45) such that one of the branches (44, 45) is a supply line to the second thermal regulation loop (L4), and the other of the branches (44, 45) is a discharge line to the second thermal regulation loop (L4).

2. Device according to the preceding claim, characterized in that the phase change fluid is propane, the mass content of which is between 100g and 200g, preferably 150g.

3. Device according to claim 1 or 2, characterized in that the phase-change fluid circuit (1) comprises a compressor (10), the condenser (11), an expansion valve (13), the cooler (14) taken in that order within a main loop (L1) of fluid circulating by the operation of the compressor (10).

4. Device according to any one of the preceding claims, characterized in that the phase-change fluid circuit (1) is disposed in a hermetically sealed enclosure having a volume between 5 and 20 litres, in particular between 10 and 15 litres, preferably 10 litres.

5. Device according to any one of the preceding claims, characterized in that the second heat exchange circuit (3) comprises a thermal loop (L3) in which are included at least the condenser (11), a radiator (31) and a water pump (30) arranged respectively in that order when the water pump (30) is started up, the thermal loop (L3) of the second heat exchange circuit (3) being in particular a third thermal loop of the device (1).

6. Device according to any one of the preceding claims, characterized in that it comprises a flow control means (42) circulating from the first thermal regulation loop (L2) to the second thermal regulation loop (L4).

7. Device according to any one of the preceding claims, characterized in that said flow control means (42) is a control valve (42a, 42b) located at the connection branch (44) or at a junction between the supply line of the second thermal control loop (L4) and the first thermal control loop (L2), said junction being located at the outlet of the air exchanger (21) of the first thermal control loop (L2).

8. Device according to any one of the preceding claims, characterized in that the first thermal regulation loop (L2) comprises the cooler (14) of the phase change fluid circuit (1), a pump (20), the air exchanger (21) taken in that order when the pump (20) is started up.

9. Device according to any one of the preceding claims, characterized in that the second thermal regulation loop (L4) comprises a pump (40), the second component (41) to be cooled of the electric traction chain, a radiator (47), a bypass branch (46) of the radiator (47), and a bypass valve (48) located at the junction between the branch comprising the radiator (47) and the bypass branch (46).

10. Device according to any one of the preceding claims, characterized in that it comprises a control unit (50) of the water pumps (20, 30, 40), of the compressor (10), of the expansion valve (13), as well as at least one temperature sensor (Tb T2, T3, T4, T5) connected to the control unit (50).

11. Vehicle, in particular of the electrically powered type, characterized in that it comprises the thermal management device (1) according to any one of claims 1 to 10.

12. A method for cooling at least one element of the powertrain and a passenger compartment of a vehicle according to the preceding claim, characterized in that it comprises the steps of implementing the following thermal controls: - of the phase-change fluid circuit (1), such that, when passenger compartment cooling is required, the temperature (TJ) of the coolant at the outlet of the cooler (14) is approximately on the order of zero degrees Celsius, by controlling the operation of the compressor (10) and / or the expansion valve (13) and / or the condenser (11) - of the second heat exchange circuit (3) by a control of the operation of the water pump (30) - of the first loop (L2) of the first heat exchange circuit such that the temperature (T2) of the heat transfer fluid at the outlet of the air exchanger (21) is between 0 and 5 degrees Celsius when cooling of the passenger compartment is requested, by a control of the operation of the water pump (20) and / or positioning of flaps (211) for adjusting an air flow through the cooler (21) and / or a bypass valve (21b) of the cooler (21) - of the second loop (L4) of the first heat exchange circuit such that the temperature (T4) of the coolant at the level of the second component (41) to be cooled is greater than or equal to the temperature (T2) of the heat transfer fluid at the outlet of the air exchanger (21), while being between 10 and 30 degrees Celsius, preferably 18 degrees Celsius, by a control of the operation of the water pump (40) and / or a bypass valve (48).

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