FR3081123A1 - THERMAL MANAGEMENT CIRCUIT FOR HYBRID OR ELECTRIC VEHICLE - Google Patents

Abstract

The present invention relates to a thermal management circuit (1) for a hybrid or electric vehicle comprising a first reversible air-conditioning loop (A) comprising a bifluid heat exchanger (7) arranged jointly on a second circulation loop (B), the second circulation loop (B) comprising: • a main loop (B1) comprising a first pump (3), a first heat exchanger (5) and the bifluid heat exchanger (7), and • a secondary loop (B2) comprising a second pump (9), a second heat exchanger (11) and a radiator (13), the main loop (B1) and the secondary loop (B2) being connected to each other by: • a device of redirection (X) of the coolant so that the coolant from the first heat exchanger (5) can flow to the bifluid heat exchanger (7) or to the radiator (13), and the heat transfer fluid from the second exchange heat generator (11) can flow to the radiator (13) or the two-fluid heat exchanger (7), and • a first branch branch (B3) connecting a first junction point (21) disposed on the secondary loop ( B2) downstream of the radiator (13) and a second junction point (22) disposed on the main branch (B1) downstream of the bifluid heat exchanger (7).

Description

The invention relates to the field of motor vehicles and more particularly to a thermal management circuit for a hybrid or electric motor vehicle.

In electric and hybrid vehicles, thermal management of the passenger compartment is generally managed by an invertible air conditioning loop. By invertible, it is meant that this air conditioning loop can operate in a cooling mode in order to cool the air intended for the passenger compartment and in a heat pump mode in order to heat the air intended for the passenger compartment. This reversible air conditioning loop can also include a bypass to manage the temperature of the batteries of the electric or hybrid vehicle as well as the electric motor. It is thus possible to heat or cool the batteries and / or the electric motor thanks to the reversible air conditioning loop. However, it is not possible to at least partially manage the temperature of the batteries and / or the electric motor without using the reversible air conditioning loop. So, for example when the passenger compartment does not need to be heated or cooled, it is still necessary to fully operate the reversible air conditioning loop to heat or cool the batteries and / or the electric motor. This leads to an electrical consumption which can be too high and therefore can impact the autonomy of the electric or hybrid vehicle.

A known solution is to use a second circulation loop separate from the air conditioning loop and inside which a heat transfer fluid circulates. The air conditioning loop and the second circulation loop are connected to each other by a two-fluid heat exchanger to allow heat exchange between the two loops. In order to dissociate the thermal management of the batteries and the electric motor, these elements can be arranged on branches parallel to one another of the second circulation loop. However, the connection between the air conditioning loop and the second circulation loop and its branches can be complex and require numerous valves, for example of the three-way valve type or even four-way valve which are expensive.

One of the aims of the present invention is therefore to at least partially remedy the drawbacks of the prior art and to propose an improved thermal management circuit.

The present invention therefore relates to a thermal management circuit for a hybrid or electric vehicle, said thermal management circuit comprising a first reversible air conditioning loop in which a refrigerant circulates and comprising a two-fluid heat exchanger arranged jointly on a second circulation loop d '' a heat transfer fluid, the second circulation loop of a heat transfer fluid comprising:

• a main loop comprising a first pump, a first heat exchanger and the two-fluid heat exchanger, and • a secondary loop comprising a second pump, a second heat exchanger and a radiator intended to be traversed by an air flow external, the main loop and the secondary loop being connected to each other by:

• a device for redirection of the heat transfer fluid so that the heat transfer fluid from the first heat exchanger can flow to the dual-fluid heat exchanger or to the radiator of the secondary loop, and the heat transfer fluid from the second heat exchanger can circulate towards the radiator or the dual-fluid heat exchanger of the main loop, and • a first branch branch connecting a first junction point arranged on the secondary loop downstream of the radiator, between said radiator and the second heat exchanger and a second junction point arranged on the main branch downstream of the two-fluid heat exchanger, between said two-fluid heat exchanger and the first heat exchanger.

According to one aspect of the invention, the redirection device comprises:

• a second branch branch connecting a third junction point arranged on the main loop downstream of the first heat exchanger, between said first heat exchanger and the dual-fluid heat exchanger, to a fourth junction point arranged on the secondary loop upstream of the radiator, between said radiator and the second heat exchanger, • a third branch branch connecting a fifth junction point arranged on the secondary loop downstream of the second heat exchanger, between said second heat exchanger and the fourth point junction, at a sixth junction point arranged on the main loop downstream of the first heat exchanger, between said first heat exchanger and the third junction point, and • a first and a second three-way valve.

According to another aspect of the invention, the first three-way valve is arranged at the third junction point and that the second three-way valve is arranged at the fifth junction point.

According to another aspect of the invention, the first three-way valve is arranged at the sixth junction point and that the second three-way valve is arranged at the fourth junction point.

According to another aspect of the invention, the redirection device comprises:

• a fourth branch branch connecting a seventh junction point arranged on the main loop downstream of the first heat exchanger, between said first heat exchanger and the two-fluid heat exchanger, to an eighth junction point arranged on the secondary loop upstream of the radiator, between said radiator and the second heat exchanger, • a first shut-off valve disposed on the main loop downstream of the seventh junction point, between said seventh junction point and the second junction point, • a second stop valve placed on the secondary loop downstream of the eighth junction point, between said eighth junction point and the first junction point, • a third stop valve placed on the fourth branch branch.

According to another aspect of the invention, the main loop includes an electric heating device for the heat transfer fluid disposed upstream of the first heat exchanger.

According to another aspect of the invention, the thermal management circuit is configured to operate according to a first cooling mode in which the redirection device is configured to decouple the main loop from the secondary loop so that the heat transfer fluid circulates independently in said main loop and in said secondary loop.

According to another aspect of the invention, the thermal management circuit is configured to operate according to a second cooling mode in which the redirection device is configured to redirect the heat transfer fluid at the outlet of the first and second heat exchangers to the radiator and prevent circulation of the heat transfer fluid in the two-fluid heat exchanger.

According to another aspect of the invention, the thermal management circuit is configured to operate according to a heat recovery mode in which the redirection device is configured to redirect the heat transfer fluid at the outlet of the first and second heat exchangers to the dual fluid heat exchanger and prevent circulation of the heat transfer fluid in the radiator.

The invention also relates to a motor vehicle comprising such a thermal management circuit.

Other characteristics and advantages of the invention will appear more clearly on reading the following description, given by way of illustrative and nonlimiting example, and of the appended drawings among which:

• Figure 1 shows a schematic representation of a thermal management circuit according to a first embodiment, • Figures 2a to 2c show the thermal management circuit of Figure 1 according to different operating modes, • Figure 3 shows a schematic representation of a thermal management circuit according to a second embodiment, • Figures 4a to 4c show the thermal management circuit of Figure 3 according to different operating modes, • Figure 5 shows a schematic representation of a circuit thermal management according to a second embodiment, • Figures 6a to 6c show the thermal management circuit of Figure 5 according to different modes of operation.

In the various figures, identical elements have the same reference numbers.

The following embodiments are examples. Although the description refers to one or more embodiments, this does not necessarily mean that each reference relates to the same embodiment, or that the characteristics apply only to a single embodiment. Simple features of different embodiments can also be combined and / or interchanged to provide other embodiments.

In the present description, it is possible to index certain elements or parameters, such as for example first element or second element as well as first parameter and second parameter or even first criterion and second criterion etc. In this case, it is a simple indexing to differentiate and name elements or parameters or criteria that are similar but not identical. This indexing does not imply a priority of an element, parameter or criterion over another and one can easily interchange such names without departing from the scope of this description. This indexing does not imply an order in time for example to assess this or that criterion.

In the present description, the term "upstream" means that one element is placed before another with respect to the direction of circulation of a fluid. Conversely, by "downstream" is meant that one element is placed after another with respect to the direction of circulation of the fluid.

Figures 1, 3 and 5 show a thermal management circuit 1 of a hybrid or electric vehicle. This thermal management circuit 1 (partially shown) comprises a first reversible air conditioning loop A in which a refrigerant fluid circulates and comprising a two-fluid heat exchanger 7 arranged jointly on a second circulation loop B of a heat transfer fluid. By invertible, it is meant that this air conditioning loop can operate in a cooling mode in order to cool the air intended for the passenger compartment and in a heat pump mode in order to heat the air intended for the passenger compartment. This first reversible air conditioning loop A can be of any type known to those skilled in the art.

The first reversible air conditioning loop A may in particular include downstream of the two-fluid heat exchanger 7 an expansion device 17. This expansion device 17 can allow a loss of pressure of the refrigerant fluid in order to cool the heat transfer fluid of the second loop circulation B at the two-fluid heat exchanger 7. This expansion device 17 can also be bypassed where the coolant can pass without loss of pressure in order to heat the heat transfer fluid of the second circulation loop B at the level of the two-fluid heat exchanger 7.

The second circulation loop B more particularly comprises a main loop B1 and a secondary loop B2 connected in parallel with one another.

The main loop B1 notably includes a first pump 3, a first heat exchanger 5 and the two-fluid heat exchanger 7. The first heat exchanger 5 can more particularly be a heat exchanger allowing the exchange of heat energy with the batteries .

The secondary loop B2 for its part comprises a second pump 9, a second heat exchanger 11 and a radiator 13 intended to be traversed by an external air flow 100. The second heat exchanger 11 can more particularly be a heat exchanger allowing the exchange of heat energy with the electric motor.

The main loop B1 and the secondary loop B2 are connected to each other by a redirection device X and a first branch branch B3.

The heat transfer fluid redirection device X allows in particular that the heat transfer fluid coming from the first heat exchanger 5 can circulate towards the two-fluid heat exchanger 7 or towards the radiator 13 of the secondary loop B2. In addition, the redirection device X allows the heat transfer fluid coming from the second heat exchanger 11 to be able to circulate towards the radiator 13 or the two-fluid heat exchanger 7 of the main loop B1.

The first branch branch B 3 connects in turn a first junction point 21 and a second junction point 22. The first junction point 21 is disposed on the secondary loop B2 downstream of the radiator 13, between said radiator 13 and the second heat exchanger 11. The second junction point 22 is for its part disposed on the main branch B1 downstream of the two-fluid heat exchanger 7, between said two-fluid heat exchanger 7 and the first heat exchanger 5.

In the example of FIGS. 1, 3 and 5, the first pump 3 is disposed upstream of the first heat exchanger 5, between said first heat exchanger 5 and the second junction point 22. It is however quite possible to 'imagine another positioning of this first pump 3 for example downstream of the first heat exchanger 5, between said first heat exchanger 5 and the redirection device X.

Similarly, in the example of FIGS. 1, 3 and 5, the second pump 9 is arranged upstream of the second heat exchanger 11, between said second heat exchanger 11 and the first junction point 21. However, it is entirely made it possible to imagine another positioning of this second pump 9, for example downstream of the second heat exchanger 11, between said second heat exchanger 11 and the redirection device X.

According to a first embodiment illustrated in Figures 1 and 3, the redirection device X comprises a second branch branch B4, a third branch branch B5 as well as a first 32 and a second 33 three-way valve.

The second branch branch B4 more particularly connects a third junction point 23 and a fourth junction point 24. The third junction point 23 is disposed on the main loop B1 downstream of the first heat exchanger 5, between said first heat exchanger heat 5 and the two-fluid heat exchanger 7. The fourth junction point 24 is arranged on the secondary loop B2 upstream of the radiator 13, between said radiator 13 and the second heat exchanger 11.

The third branch branch B 5 more particularly connects a fifth junction point 25 and a sixth junction point 26. The fifth junction point 25 is disposed on the secondary loop B2 downstream of the second heat exchanger 11, between said second exchanger 11 and the fourth junction point 24. The sixth junction point 26 is in turn disposed on the main loop B1 downstream of the first heat exchanger 5, between said first heat exchanger 5 and the third junction point 23 .

According to a first variant of the first embodiment illustrated in FIG. 1, the first three-way valve 32 is arranged at the third junction point 23 and the second three-way valve 33 is arranged at the fifth junction point 25 The first three-way valve 32 here makes it possible to redirect the heat transfer fluid arriving at it towards the two-fluid heat exchanger 7 or towards the secondary loop B2 via the second branch branch B4. The second three-way valve 33 here makes it possible to redirect the heat transfer fluid arriving to the radiator 13 or to the main loop B1 via the third branch branch B5.

According to a second variant of the first embodiment illustrated in FIG. 3, the first three-way valve 32 is arranged at the sixth junction point 26 and the second three-way valve 33 is arranged at the fourth junction point 24 The first three-way valve 32 here makes it possible to redirect the heat transfer fluid arriving to the two-fluid heat exchanger 7 or to the secondary loop B2 via the third branch branch B5. The second three-way valve 33 here makes it possible to redirect the heat transfer fluid arriving to the radiator 13 or to the main loop B1 via the second branch branch B4.

The first and second variants are symmetrical and allow the same operating modes.

According to a second embodiment illustrated in FIG. 5, the redirection device X comprises a fourth branch branch B6, instead of a second B4 and a third B5 branch branch, and three stop valves 34a, 34b and 34c.

The fourth branch branch B6 connects a seventh junction point 27 and an eighth junction point 28. The seventh junction point 27 is arranged on the main loop B1 downstream of the first heat exchanger 5, between said first heat exchanger 5 and the two-fluid heat exchanger 7. The eighth junction point 28 is for its part disposed on the secondary loop B2 upstream of the radiator 13, between said radiator 13 and the second heat exchanger 11.

A first stop valve 34a is disposed on the main loop B1 downstream of the seventh junction point 27, between the seventh junction point 27 and the second junction point 22. This first stop valve 34a allows to pass or no the heat transfer fluid in the two-fluid heat exchanger 7.

A second stop valve 34b is disposed on the secondary loop B2 downstream of the eighth junction point 28, between said eighth junction point 28 and the first junction point 21. This second stop valve 34b allows to pass or not the heat transfer fluid in the radiator 13.

A third stop valve 34c is arranged on the fourth branch branch B6. This third stop valve 34c allows the heat transfer fluid to pass or not to pass through the fourth branch branch B6 so that the latter can circulate between the primary loop B1 and the secondary loop B2 in one direction or the other.

The thermal management circuit 1 can in particular operate according to different operating modes illustrated in FIGS. 2a to 2c, 4a, to 4c and 6a to 6c. In these figures, only the elements in which the heat transfer fluid circulates are shown. In addition, arrows indicate the direction of circulation of the heat transfer fluid.

a) First cooling mode:

The thermal management circuit 1 can in particular be configured to operate according to a first cooling mode illustrated in FIGS. 2a, 4a and 6a.

In this first cooling mode, the redirection device X is configured to decouple the main loop B1 from the secondary loop B2 so that the heat transfer fluid flows independently in said main loop B1 and in said secondary loop B2.

Within the main loop B1, the heat transfer fluid set in motion by the first pump 3 circulates in the first heat exchanger 5 and in the two-fluid heat exchanger 7. At the level of the first heat exchanger 5, the heat transfer fluid recovers heat energy by cooling the batteries, for example. At the two-fluid heat exchanger 7, the heat transfer fluid transfers this heat energy to the refrigerant of the first reversible air conditioning loop A.

Within the secondary loop B2, the heat transfer fluid set in motion by the second pump 9 circulates in the second heat exchanger 11 and in the radiator 13. At the second heat exchanger 11 the heat transfer fluid recovers heat energy by cooling, for example, the electric motor. At the radiator 13, the heat transfer fluid transfers this heat energy to the external air flow 100.

According to the first variant of the first embodiment illustrated in Figure 2a, this is possible when the first three-way valve 32 allows the circulation of the heat transfer fluid from the first heat exchanger 5 to the dual-fluid heat exchanger 7 and blocks traffic to the second branch branch B4. The second three-way valve 33 allows the circulation of the heat transfer fluid from the second heat exchanger 11 to the radiator 13 and blocks the circulation to the third branch branch B5.

According to the second variant of the first embodiment illustrated in FIG. 4a, this is possible when the first three-way valve 32 allows the circulation of the heat-transfer fluid coming from the first heat exchanger 5 towards the two-fluid heat exchanger 7 and blocks traffic to the third branch branch B5. The second three-way valve 33 allows the circulation of the heat transfer fluid from the second heat exchanger 11 to the radiator 13 and blocks the circulation to the second branch branch B4.

According to the second embodiment illustrated in FIG. 6a, this is possible when the first stop valve 34a is open to allow the circulation of the heat-transfer fluid coming from the first heat exchanger 5 towards the two-fluid heat exchanger 7 and when the second stop valve 34b is open to allow the circulation of the coolant coming from the second heat exchanger 11 to the radiator 13. The third stop valve 34c is closed in order to block the circulation of the coolant in the fourth branch branch B6.

This first cooling mode allows for example to independently cool the batteries at the first heat exchanger 5 and the electric motor at the second heat exchanger 11. The main loop B1 and the secondary loop B2 remain independent of one another. 'other. The heat energy from the batteries is transferred to the first air conditioning loop A and that from the electric motor to the radiator 13. The first air conditioning loop A can operate either in heat pump mode or in air conditioning mode.

b) Second cooling mode:

The thermal management circuit 1 can also be configured to operate according to a second cooling mode illustrated in FIGS. 2b, 4b and 6b.

In this second cooling mode, the redirection device X is configured to redirect the heat transfer fluid at the outlet of the first 5 and second 11 heat exchangers to the radiator 13 and prevent the circulation of the heat transfer fluid in the two-fluid heat exchanger 7.

Within the main loop B1, the heat transfer fluid set in motion by the first pump 3 circulates in the first heat exchanger 5 and is redirected to the radiator 13 of the secondary loop B2. At the first heat exchanger 5, the heat transfer fluid recovers heat energy by cooling the batteries, for example.

Within the secondary loop B2, the heat transfer fluid set in motion by the second pump 9 circulates in the second heat exchanger 11 and in the radiator 13. At the second heat exchanger 11 the heat transfer fluid recovers heat energy by cooling, for example, the electric motor.

At the radiator 13, the heat transfer fluid from both the first 5 and the second 11 heat exchanger transfers heat energy to the external air flow 100.

At the outlet of the radiator 13, part of the heat transfer fluid returns to the main loop B1 via the first branch branch B3.

According to the first variant of the first embodiment illustrated in FIG. 2b, this is possible when the first three-way valve 32 allows the circulation of the heat transfer fluid coming from the first heat exchanger 5 to the secondary loop B2 via the second branch of B4 bypass and blocks circulation to the two-fluid heat exchanger 7. The second three-way valve 33 allows the circulation of the heat transfer fluid from the second heat exchanger 11 to the radiator 13 and blocks the circulation to the third branch branch B5.

According to the second variant of the first embodiment illustrated in FIG. 4b, this is possible when the first three-way valve 32 allows the circulation of the heat-transfer fluid coming from the first heat exchanger 5 to the secondary loop B2 via the third branch of B5 bypass and blocks circulation to the two-fluid heat exchanger 7. The second three-way valve 33 allows the circulation of the heat-transfer fluid coming from the second heat exchanger 11 and the third branch of branch B 5 to the radiator 13 and blocks circulation to the second branch branch B4.

According to the second embodiment illustrated in FIG. 6b, this is possible when the first stop valve 34a is closed to prevent the circulation of the heat-transfer fluid coming from the first heat exchanger 5 towards the two-fluid heat exchanger 7. The third stop valve 34c is in turn open to allow the circulation of the coolant in the fourth branch branch B6. The second stop valve 34b is open to allow the circulation of the heat-transfer fluid coming from the second heat exchanger 11 and from the fourth branch branch B 6 towards the radiator 13.

This second cooling mode makes it possible, for example, to jointly cool the batteries at the level of the first heat exchanger 5 and the electric motor at the level of the second heat exchanger 11. The heat energy of the batteries and of the electric motor is transferred in full to the radiator 13. As for the first air conditioning loop A, it can be switched off or can operate in heat pump mode or in air conditioning mode independently of the second circulation loop B.

c) Heat recovery mode:

The thermal management circuit 1 can also be configured to operate according to a heat recovery mode illustrated in FIGS. 2c, 4c and 6c.

In this heat recovery mode, the redirection device X is configured to redirect the heat transfer fluid at the outlet of the first 5 and second 11 heat exchangers to the dual-fluid heat exchanger 7 and prevent the circulation of the heat transfer fluid in the radiator 13 .

Within the main loop B1, the heat transfer fluid set in motion by the first pump 3 circulates in the first heat exchanger 5 and is redirected towards the two-fluid heat exchanger 7. At the level of the first heat exchanger 5, the fluid coolant recovers heat energy by cooling the batteries, for example.

Within the secondary loop B2, the heat transfer fluid set in motion by the second pump 9 circulates in the second heat exchanger 11 and is redirected to the dual-fluid heat exchanger 7. At the second heat exchanger 11 the heat transfer fluid recovers heat energy by cooling for example the electric motor.

At the two-fluid heat exchanger 7, the heat transfer fluid coming from both the first 5 and the second 11 heat exchanger transfers heat energy to the first air conditioning loop A.

At the outlet of the two-fluid heat exchanger 7, part of the heat transfer fluid returns to the secondary loop B2 via the first branch branch B3.

According to the first variant of the first embodiment illustrated in Figure 2c, this is possible when the second three-way valve 33 blocks the circulation of the heat transfer fluid from the second heat exchanger 11 to the radiator 13 and allows circulation to the main loop B1 via the third branch branch B5. The first three-way valve 32 allows the circulation of the heat transfer fluid coming from the first heat exchanger 5 and from the third branch branch B5 to the dual-fluid heat exchanger 7.

According to the second variant of the first embodiment illustrated in FIG. 4c, this is possible when the first three-way valve 32 allows the circulation of the heat-transfer fluid coming from the first heat exchanger 5 towards the two-fluid heat exchanger 7 and blocks traffic to the third branch branch B5. The second three-way valve 33 allows the circulation of the heat transfer fluid coming from the second heat exchanger 11 to the main loop B1 via the second branch branch B4 and blocks the circulation to the radiator 13.

According to the second embodiment illustrated in FIG. 6c, this is possible when the first stop valve 34a is open to allow the circulation of the heat-transfer fluid coming from the first heat exchanger 5 towards the two-fluid heat exchanger 7. The third stop valve 34c is in turn open to allow the circulation of the coolant in the fourth branch branch B6. The second stop valve 34b is closed to prevent the circulation of the heat transfer fluid coming from the second heat exchanger 11 to the radiator 13.

This heat recovery mode makes it possible, for example, to jointly cool the batteries at the level of the first heat exchanger 5 and the electric motor at the level of the second heat exchanger 11. The heat energy of the batteries and of the electric motor is transferred in full to the two-fluid heat exchanger 7 so as to be transmitted to the first air conditioning loop A. The first air conditioning loop A operates in heat pump mode in order to use the heat energy recovered from the second circulation loop B to warm the passenger compartment.

As shown in Figures 3 to 6c, the main loop B1 can also include an electric heating device 15 of the heat transfer fluid. This electric heating device 15, for example a resistance with a positive temperature coefficient, is arranged upstream of the first heat exchanger 5, between the first heat exchanger 5 and the heat exchanger 7. In the example illustrated in the figures 3 to 6c, the electric heating device 15 is arranged between the second junction point 22 and the first heat exchanger 5. This electric heating device 15 can for example be used in order to heat the heat transfer fluid upstream of the first heat exchanger heat 5 in order for example to allow the batteries to reach their optimal operating temperature, in particular in the case of use in cold weather.

Thus, it can be seen that due to its particular architecture, the thermal management circuit 1 allows operation according to different operating modes, a decoupling of thermal management between the main loop B1 and the secondary loop B2 of the second circulation loop B In addition, these different operating modes can be implemented by means of a limited number of valves, whether stop valves or three-way valves, which makes it possible to limit production costs.

Claims (9)

1. Thermal management circuit (1) for a hybrid or electric vehicle, said thermal management circuit (1) comprising a first reversible air conditioning loop (A) in which a refrigerant circulates and comprising a dual-fluid heat exchanger (7) arranged jointly on a second circulation loop (B) of a heat transfer fluid, the second circulation loop (B) of a heat transfer fluid comprising: • a main loop (B1) comprising a first pump (3), a first heat exchanger (5) and the dual-fluid heat exchanger (7), and • a secondary loop (B2) comprising a second pump (9), a second heat exchanger (11) and a radiator (13) intended to be traversed by an external air flow (100), the main loop (Bl) and the secondary loop (B2) being connected one to the other by: • a device for redirection (X) of the heat transfer fluid so that the heat transfer fluid from the first heat exchanger (5) can flow to the dual-fluid heat exchanger (7) or to the radiator (13) of the secondary loop (B2), and the heat transfer fluid coming from the second heat exchanger (11) can circulate towards the radiator (13) or the dual-fluid heat exchanger (7) of the main loop (B1), and • a first branch of bypass (B3) connecting a first junction point (21) disposed on the secondary loop (B2) downstream of the radiator (13), between said radiator (13) and the second heat exchanger (11) and a second junction point (22) disposed on the main branch (B1) downstream of the two-fluid heat exchanger (7), between said two-fluid heat exchanger (7) and the first heat exchanger (5). 2. Thermal management circuit (1) according to claim 1, characterized in that the redirection device (X) comprises: • a second branch branch (B4) connecting a third junction point (23) disposed on the main loop (Bl) downstream of the first heat exchanger (5), between said first heat exchanger (5) and the exchanger dual fluid heat (7), at a fourth junction point (24) disposed on the secondary loop (B2) upstream of the radiator (13), between said radiator (13) and the second heat exchanger (11), • a third branch branch (B5) connecting a fifth junction point (25) disposed on the secondary loop (B2) downstream of the second heat exchanger (11), between said second heat exchanger (11) and the fourth junction point (24), at a sixth junction point (26) arranged on the main loop (B1) downstream of the first heat exchanger (5), between said first heat exchanger (5) and the third junction point (23) , and • a first (32) and a second (33) three-way valve. 3. Thermal management circuit (1) according to claim 2, characterized in that the first three-way valve (32) is arranged at the third junction point (23) and that the second three-way valve (33) is arranged at the fifth junction point (25). 4. Thermal management circuit (1) according to claim 2, characterized in that the first three-way valve (32) is arranged at the sixth junction point (26) and that the second three-way valve (33) is arranged at the fourth junction point (24). 5. Thermal management circuit (1) according to claim 1, characterized in that the redirection device (X) comprises: • a fourth branch branch (B6) connecting a seventh junction point (27) disposed on the main loop (Bl) downstream of the first heat exchanger (5), between said first heat exchanger (5) and the exchanger dual fluid heat (7), at an eighth junction point (28) disposed on the secondary loop (B2) upstream of the radiator (13), between said radiator (13) and the second heat exchanger (11), • a first stop valve (34a) arranged on the main loop (B1) downstream of the seventh junction point (27), between said seventh junction point (27) and the second junction point (22), • a second valve stop (34b) disposed on the secondary loop (B2) downstream of the eighth junction point (28), between said eighth junction point (28) and the first junction point (21), • a third valve stop (34c) disposed on the fourth branch branch (B6). 6. thermal management circuit (1) according to one of the preceding claims, characterized in that the main loop (Bl) comprises an electric heating device (15) of the heat transfer fluid disposed upstream of the first heat exchanger (5) . 7. thermal management circuit (1) according to one of claims 1 to 6, characterized in that it is configured to operate according to a first cooling mode in which the redirection device (X) is configured to decouple the loop main (Bl) of the secondary loop (B2) so that the heat transfer fluid flows independently in said main loop (Bl) and in said secondary loop (B2). 8. Thermal management circuit (1) according to one of claims 1 to 6, characterized in that it is configured to operate according to a second cooling mode in which the redirection device (X) is configured to redirect the fluid heat transfer fluid at the outlet of the first (5) and second (11) heat exchangers to the radiator (13) and prevent the circulation of the heat transfer fluid in the two-fluid heat exchanger (7). 9. Thermal management circuit (1) according to one of claims 1 to 6, characterized in 5 that it is configured to operate according to a heat recovery mode in which the redirection device (X) is configured to redirect the heat transfer fluid at the outlet of the first (5) and second (11) heat exchangers towards the dual fluid heat exchanger (7) and prevent circulation of the heat transfer fluid in the radiator (13).