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 a vehicle, in particular with electric propulsion.

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

[0002] Different types of refrigerant are known for carrying out thermal regulation of the passenger compartment or the battery of an electric vehicle. Each refrigerant is assigned a greenhouse effect coefficient, so that it is well established that refrigerant 1234yf® has a much lower greenhouse effect coefficient than the previous refrigerant 134a®. This significant progress, however, encounters other obstacles to its continued commercialization, in particular because it contains a fluorinated substance which is considered dangerous to public health.

[0003] Other types of natural refrigerant fluid exist, such as propane, so that the replacement of 1234yf® refrigerant fluid in air conditioning circuits is to be considered in the near future. The use of carbon dioxide refrigerant fluid has the major disadvantage that it requires an air conditioning loop with resistance to high pressures, of the order of 125 bars for example, but also resistance to operating temperatures of the order of 150°C. Due to the pressure and temperature parameters, the risk of leaks is a disadvantage to its widespread use, particularly in large series in the automotive sector. The use of propane as a refrigerant is less restrictive because the air conditioning circuit can be fully operational with an operating pressure of approximately 25 bars and an operating temperature of approximately 100°C, so that an air conditioning system with propane tends to be closer to a traditional air conditioning system with the refrigerant 1234yf®, which makes it possible to consider a change of fluid without causing too many modifications to the current air conditioning circuits. However, it is necessary to respect the safety requirements relating to the very nature of the propane fluid, by creating a compact air conditioning loop, so that leak management can be simplified.

[0004] Replacing the 1234yf® refrigerant with propane can be done easily by taking into account another factor that has a strong impact on the use of propane as a refrigerant, namely its very high degree of combustibility, which classifies it in the category of highly dangerous gases. To overcome this problem, the quantity 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 as well as a passenger compartment of the vehicle 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 rate 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 which 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 propane mass content of which is between 100g and 200g, preferably 150g, - the phase change fluid circuit comprises a compressor, the condenser, an expansion valve, the cooler taken in this order within a main loop of fluid circulating by the operation of the compressor, - the phase change fluid circuit is arranged in a hermetic enclosure having a volume of between 5 and 20 liters, in particular between 10 and 15 liters, preferably 10 liters, - the second heat exchange circuit comprises a thermal loop in which are included at least the condenser, a radiator and a water pump arranged respectively in this order when the water pump is put into operation, 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 comprises at least a 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 means comprising branches such that one of the branches is a supply pipe of the second thermal regulation loop, and the other of the branches is a pipe evacuation of the second thermal regulation loop, - it comprises a means for controlling the flow rate circulating from the first thermal regulation loop to the second thermal regulation loop, - the first thermal regulation loop includes an air exchanger intended to be crossed by a flow of air to be cooled for the passenger compartment of the vehicle, - the second thermal regulation loop comprises a second component of an electric traction chain, in particular an electric battery, or a cooler of the dielectric fluid which is 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 pipe 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 control loop includes the cooler of the phase change fluid circuit, a pump, the air exchanger taken in this order when the pump is put into operation, - the first thermal regulation loop includes a degassing jar, - the second thermal regulation loop comprises a pump, the second component to be cooled of the electric drive train, a radiator, a bypass branch of the radiator, and a bypass valve located at the junction between the branch comprising the radiator and the bypass branch, - the bypass branch comprises two junctions with said interconnection means, one with the supply pipe, the other for the discharge pipe, - it includes a control unit for the water pumps, the compressor, the 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 comprises 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 cooling of the passenger compartment is necessary, the temperature of the coolant at the outlet of the cooler is approximately of the order of 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 the cooling of the passenger compartment is requested, by controlling the operation of the water pump and / or positioning of flaps for adjusting an air flow 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 controlling the operation of the water pump and / or a bypass valve.

[0009] The method of the invention may further comprise the following characteristics: - when the temperature of the heat transfer fluid at the outlet of the discharge pipe is higher than the temperature of the ambient air, 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 a 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 rate 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.l] 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 the [Fig.l], [Fig.3] schematically represents a means of regulating on the air the heat exchange between a heat transfer fluid and the air intended for the passenger compartment, of the thermal management device of the invention, [Fig.4] schematically represents a means of regulating on the water the heat exchange between a heat transfer fluid and the air intended for the passenger compartment, of the thermal management device of the invention.

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

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

[0013] Inside the enclosure, there are arranged a compressor 10, a second heat exchanger 11 of the condenser type, a reserve 12, an expansion valve 13 and a first heat exchanger 14, of the cooler type, taken in this order according to the direction of circulation of the fluid during operation of the compressor. A main loop of the thermal management device consists of the compressor 10, the first and second heat exchangers 14, 11 and the expansion valve 13 assembled in series, such that each comprises fluid inlet and outlet pipes. The degassing device is not a through pipe, in the sense that it comprises a degassing tank which is connected to the main loop by a single conduit whose junction is made between the first and second heat exchangers, more particularly between the second heat exchanger 11 and the expansion valve 13 located upstream of the first heat exchanger 14. The degassing device comprises a reservoir intended to separate the liquid from the vapor of the refrigerant fluid, to create a volume reserve of refrigerant fluid in order to compensate for the volume variation of the fluid in the air conditioning circuit.

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

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

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

[0017] The first heat exchange circuit 2 will now be detailed. It includes a pump 20, the operation of which will cause the circulation of a heat transfer fluid, such as, for example, glycolated water. The first heat exchange circuit 2 comprises a first thermal regulation loop L2. The first thermal control loop comprises in series the cooler 14, the pump 20, an air heater 21, taken in this order during operation of the pump. A degassing device 22 is arranged between the air heater 21 and the cooler 14. The degassing device comprises a non-through degassing jar, connected to the branch connecting the air heater 21 to the cooler 14 by a junction tapping.

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

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

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

[0021] The first heat exchange circuit 2 comprises a second thermal regulation loop L4, which according to an alternative embodiment could well comprise the degassing tank 22. Whatever the location of the degassing tank 22 directly at the level of the first or second thermal regulation loop L2, L4, its presence is essential to ensure the proper functioning of the thermal management device, and also for any after-sales service, having required emptying of the first heat exchange circuit 2. The second thermal control loop L4 comprises 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 comprising the radiator 47 and the bypass branch. The component to be cooled is the second component 41 of the electric drive train, in particular an electric power battery. The control of the bypass valve 48 makes it possible to regulate the flow of heat transfer fluid circulating through the radiator 47 so that the thermal regulation of the second component 41 can be carried out by regulation on the ambient air according to the cooling requirement 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 comprises a means for interconnecting the first and second loops L2 and L4 fluidly connecting the loops together. Said interconnection means comprises a branch 44 which is a supply line for the second thermal regulation loop L4, as well as a branch 45 which is an evacuation line for the second thermal regulation loop L4.

[0024] The regulation temperature of the organ to be cooled, respectively the air in the passenger compartment 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 comprises a means for controlling the flow rate 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 an 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 interconnecting means of 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 supply line 44 connecting the first thermal control loop L2 to the second thermal control loop L4.

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

[0029] Leaving the exchanger 21, the flow Q2 can go to the branch 44 or to the cooler 14, circulating through the branch comprising the junction with the degassing device 22. The adjustment of the flow is carried out by a regulation means 49 located at the branch comprising the jar 22, aims to reduce the permeability of this branch, in order to direct a part of the flow Q2 towards the branch 44 of the interconnection means. The same principle is applied for the flow Q4 of the bypass branch 46: arriving at the first node 43, the reduction in the passage section operated by the adjustment means 49, located between the nodes 43, promotes a circulation of the fluid towards the evacuation pipe 45, which creates the exchange flow Q5 between the first and second thermal regulation 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.l] does not require the use of an adjustment means, because the 3-way valve comprises a means for restricting flow towards the branch where the degassing device 22 is located. The thermal management device also comprises a second heat exchange circuit 3 which is in direct thermal relation with the condenser 11 of the phase change fluid circuit 1. Such a heat exchange link between the propane in gaseous state leaving the compressor 10 under pressure and the second heat exchange circuit 3 aims to condense the propane into high pressure liquid. On leaving the condenser in liquid state under high pressure, the propane passes into the expansion valve 13 and then enters the exchanger 14, where it evaporates while cooling the fluid of the first circuit 2.

[0031] The second heat exchange circuit 3 may be a thermal loop L3 which comprises 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 for cooling on the air of the heat transfer fluid, taken in this order during operation of the water pump 30. Upstream of the pump 30, a tapping of the thermal loop L3 allows a 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 comprises a re air regulation of the temperature at the outlet of the air heater 21. The four diagrams illustrate the different operating modes of this system according to different cooling requirements of the passenger compartment. The system comprises a fan 212 as well as articulated flaps 211, the latter being able to block all or part of the flow of air passing through the air heater 21 due to their positioning in line with the beam of the air heater 21. The flaps can be positioned between the fan 212 and the air heater 21, depending on the direction of air flow. Depending on the cooling requirement of the passenger compartment, which can be translated by a ventilation power, the rotation speed of the fan and the positioning of the movable flaps are modified.Thus, depending on the power requirement P for cooling the passenger compartment between a minimum power Pmin and a maximum power Pmax, the flaps can be placed in line with the bypass openings of the air heater and / or in line with the bundle of the air heater so that the air flow to the passenger compartment passes completely through the bypass openings of the air heater, the bundle of the air heater, or partially through the bypass openings of the air heater and the bundle of the air heater 21. . The assembly consisting of the fan, the shutters and the air heater are preferably located in an air conditioning box.

[0033] In [Fig.4], the thermal management device may comprise a variant of embodiment of the temperature regulation system at the outlet of the air heater 21. The three diagrams illustrate the different operating modes of this system depending on the cooling power of the passenger compartment. The system comprises in this case a bypass valve 21a arranged upstream of the air heater 21, as well as a bypass branch 21b of the air heater 21. Depending on the cooling requirement of the passenger compartment, which can be translated 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 between minimum and maximum, the bypass valve 21a makes it possible to adapt the quantity of heat transfer fluid circulating in the air heater 21 according to a total flow, a partial flow or an interruption of the flow of the heat transfer fluid within the air heater 21. By total flow, we mean a stoppage of the flow in the bypass branch 21b.Partial flow means a flow of the heat transfer fluid both in the bypass branch 21b and inside the air heater 21. The term flow interruption means a total flow of the heat transfer fluid in the bypass branch 21b.

[0034] The assembly consisting of the bypass valve 21a and the branch of Bypass 21b can then be located outside the air conditioning housing, 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 comprising the control laws in order to make the operation of the pumps 20, 30, 40, the bypass valves 48 and the flow control means 42 suitable according to at least one measured temperature T4 upstream of the second component 41 to be cooled of the electric traction chain. A temperature sensor 51 measures the measured temperature T4. Pumps 20, 30 and 40 generate flow rates Q2, Q3 and Q4 of coolant respectively.

[0036] The operating method of the thermal management device will now be detailed. The main loop L1 can be likened to an ultra-compact cold production module, in which the high-pressure liquid refrigerant enters the expansion valve 13 such that its pressure drops. Subsequently entering the cooler 14, which can be likened to an evaporator, the propane captures the calories from the heat transfer fluid of the first thermal regulation loop L2. During the heat exchange, the propane evaporates and becomes in the gaseous state. Leaving the cooler 14, it passes back through the expansion valve 13, but through a downstream portion called the outlet portion of the expansion valve, which is distinct from an upstream portion of the expansion valve through which the propane circulates before circulating through the cooler. Since the propane circulates through the upstream and downstream portions of the expansion valve with different fluid pressures, the temperature is captured in order to more precisely control the expansion valve 13.The gas is then sucked in by the compressor 10 where it is compressed to increase its pressure. This compression also increases the temperature of the gas. 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, to then be transformed into liquid. The heat recovered by the fluid of the thermal loop L3 can be used to heat the electric motor 32, or another component to be heated, in winter or rejected into the ambient air in summer if this heat is not useful, via the radiator 31. The high-pressure liquid refrigerant enters the reserve 12 which also includes a filter. The propane is then filtered of any impurities and moisture to be directed to the expansion valve 13 and thus continue 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 so as to ensure the cooling of the passenger compartment by the exchanger 21. The pump 20 is controlled by the computer 50 for ensure a sufficient flow rate Q2 according to the passenger compartment air conditioning demand, which depends on at least one other parameter chosen from the ambient temperature, the degree of sunshine, and the volume of the passenger compartment in particular. The regulating valve 42a controlled by the computer 50 allows a constant flow rate in the heat exchange 2 constant Q2, except at the level of the branch of the circuit connecting the valve 42a and the degassing tank 22. This difference in flow rate will be detailed below.

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

[0039] The second loop L4 of the first heat exchange circuit 2 ensures the cooling of battery 4L. The 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 the battery 41 is precisely regulated by the device which is the subject of the invention. In this loop we have a second pump 40 which ensures a flow rate Q4 at the level of the second component 41 of the powertrain to be cooled, in particular the battery 41, as well as a bypass valve 48, in particular of the three-way type, which makes it possible to select the branch where there is a radiator 47 provided for cooling the battery without air conditioning in order to reduce the energy used.This selection can take place for example in winter or when the ambient temperature is low enough, or simply when the battery temperature is high enough and the water cooled by the radiator is sufficient to maintain the optimal operating conditions of the battery, for example during driving on the highway where the air speed is high to allocate to the radiator the performance required for cooling the 4L battery.

[0040] The bypass valve 48 makes it possible to select the branch 46 in order to bypass the radiator and to connect the first and second control loops together so that the heat transfer fluid draws the frigories at the cooler 14. During the cooling of the battery 41 by the heat transfer fluid circulating through the first thermal control loop L2, the flow control means 42 authorizes the transfer of a portion of the flow Q2 at very low temperature T2 to the junction 43 where this very cold water mixes with the relatively hot water leaving the battery. The temperature T4 of the water destined for the battery 41 is a mixture of the temperature T5 of the water leaving the battery 41 and the temperature T2 of the water leaving the air heater 21. The exact value of the temperature T4 further depends on the flow rate Q5 in the branch 44 of said interconnection means, and on the flow rate Q4: _ T, *(Q4-Q^+T., *Q s 4 Q.

[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 specifications. It follows that the control means 50 is capable of adjusting a flow rate Q5 by the flow rate control means 42 in order to obtain precisely, and without temperature oscillation, a temperature T4 for cooling the battery using the value of the measured temperatures T2 and T5.

Claims

Claims

1. Thermal management device for a vehicle, in particular an electric vehicle comprising at least one element of the powertrain as well as a passenger compartment of the vehicle to be thermally regulated, characterized in that the thermal management device comprises a phase change fluid circuit (1), in particular of the propane type in that the circuit (1) is connected by a first heat exchanger (14) to a first heat exchange circuit (2), said first heat exchanger (14) being in particular a cooler (14), in that the circuit (1) is connected by a second heat exchanger (11) to a second heat exchange circuit (3), said second exchanger (11) being in particular a condenser (11), each of the first and second heat exchange circuits (2, 3) comprising a means for controlling the flow rate of a heat transfer fluid, in particular water, such that said first and second heat exchangers (11,14) are of the propane / water type.,

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 this order within a main loop (Ll) 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 arranged in a hermetic enclosure having a volume of between 5 and 20 liters, in particular between 10 and 15 liters, preferably 10 liters.

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 this order when the water pump (30) is put into operation, 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 the first heat exchange circuit (2) comprises a first thermal regulation loop (L2) and a second thermal regulation loop (L4) connected to each other by means of an interconnection means comprising branches (44, 45) such that one of the branches (44, 45) is a supply pipe for the second thermal regulation loop (L4), and the other of the branches (44, 45) is an evacuation pipe for the second thermal regulation loop (L4).

7. Device according to the preceding claim, characterized in that it comprises a means for controlling the flow rate (42) circulating from the first thermal regulation loop (L2) to the second thermal regulation loop (L4).

8. Device according to claim 6 or 7, characterized in that said flow control means (42) is a regulating valve (42a, 42b) located at the connection branch (44) or at a junction between the supply pipe of the second thermal regulation loop (L4) and the first thermal regulation loop (L2), said junction being located at the outlet of the air exchanger (21) of the first thermal regulation loop (L2).

9. Device according to any one of claims 6 to 8, 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 this order when the pump (20) is put into operation.

10. Device according to any one of claims 6 to 9, 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).

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

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

13. 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 (1), such that, when cooling of the passenger compartment is necessary, the temperature (Ti) of the coolant at the outlet of the cooler (14) is approximately of 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 controlling 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 the cooling of the passenger compartment is requested, by controlling 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 controlling the operation of the water pump (40) and / or a bypass valve (48).

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