阅读说明：本技术 用于电动或混合动力机动车辆的热管理的装置 (Device for thermal management of an electric or hybrid motor vehicle ) 是由 J.贝努阿利 于 2020-01-22 设计创作，主要内容包括：本发明涉及一种包括用于机动车辆的间接空调回路(1)的热管理装置,包括：-第一制冷剂流体回路(A),其包括压缩机(3)、双流体热交换器(5)、第一膨胀装置(7)、蒸发器(9)、第二膨胀装置(11)、蒸发器/冷凝器(13),以及-包括第一截止阀(33)的第一旁通管线(30),-第一内部热交换器(19),-第二内部热交换器(19’),-包括布置在冷却器(15)上游的第三膨胀装置(17)的第二旁通管线(40),-包括第一外部散热器(84)的分流支路(80),-传热流体用于在其中流动的第二传热流体回路(B),双流体热交换器(5)共同地一方面布置在压缩机(3)下游的第一制冷剂流体回路(A)上,在所述压缩机(3)和第一膨胀装置(7)之间,另一方面布置在第二传热流体回路(B)上。(The invention relates to a thermal management device comprising an indirect air-conditioning circuit (1) for a motor vehicle, comprising: -a first refrigerant fluid circuit (a) comprising a compressor (3), a two-fluid heat exchanger (5), a first expansion device (7), an evaporator (9), a second expansion device (11), an evaporator/condenser (13), and-a first bypass line (30) comprising a first shut-off valve (33), -a first internal heat exchanger (19), -a second internal heat exchanger (19'), -a second bypass line (40) comprising a third expansion device (17) arranged upstream of the cooler (15), -a branching branch (80) comprising a first external radiator (84), -a second heat transfer fluid circuit (B) for flowing therein of a heat transfer fluid, the two-fluid heat exchangers (5) being jointly arranged on the one hand on the first refrigerant fluid circuit (a) downstream of the compressor (3), between the compressor (3) and the first expansion device (7), on the other hand on the second heat transfer fluid circuit (B).)

1. A thermal management device comprising an indirect air-conditioning circuit (1) for a motor vehicle, comprising:

-a first circuit (a) for a refrigerant fluid for circulation therein, said first circuit (a) for a refrigerant fluid comprising, in the direction of circulation thereof, a compressor (3), a two-fluid heat exchanger (5), a first expansion device (7), an evaporator (9), a second expansion device (11) and an evaporator/condenser (13), and

-a first bypass (30) bypassing the evaporator/condenser (13) and comprising a first shut-off valve (33),

-a first internal heat exchanger (19) allowing heat exchange between a high pressure refrigerant fluid leaving the two-fluid heat exchanger (5) and a low pressure refrigerant fluid leaving the evaporator/condenser (13) or leaving the first bypass (30),

-a second internal heat exchanger (19') allowing heat exchange between the high pressure refrigerant fluid leaving the first internal heat exchanger (19) and the low pressure refrigerant fluid circulating in the first bypass line (30),

-a second bypass pipe (40) bypassing the first expansion device (7) and the evaporator (9), said second bypass pipe (40) comprising a third expansion device (17) upstream of the cooler (15),

-a branching circuit (80) connecting a first branch (81) downstream of the two-fluid heat exchanger (5) between the two-fluid heat exchanger (5) and the first internal heat exchanger (19) to a second branch (82) upstream of the first internal heat exchanger (19) between the first internal heat exchanger (19) and the first branch (81), the branching circuit (80) comprising a first external radiator (84),

-a second circuit (B) for a heat transfer fluid for circulation in the second circuit,

the two-fluid heat exchanger (5) is arranged jointly on the one hand on the first circuit (A) for the refrigerant fluid downstream of the compressor (3), between the compressor (3) and the first expansion device (7), and on the other hand on the second circuit (B) for the heat transfer fluid.

2. Thermal management device according to the preceding claim, characterized in that said indirect air-conditioning circuit (1) comprises means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger (5) directly towards the first internal heat exchanger (19) and/or towards the branching branch (80).

3. The thermal management device according to claim 2, characterized in that said means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger (5) comprise:

-a first shut-off valve (82a) arranged on the main circuit (a) downstream of the first branch (81), between the first branch (81) and the second branch (82), and

-a second shut-off valve (82b) arranged on the branch (80) downstream of the first branch (81), between the first branch (81) and the first external radiator (84).

4. The thermal management device according to claim 2, characterized in that said means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger (5) comprise a three-way valve arranged at the first branch (81).

5. Thermal management device according to any of the preceding claims, characterized in that said branch (80) comprises a check valve (83) arranged downstream of a first external radiator (84), between said first external radiator (84) and a second branch (82), to block the refrigerant flow coming from said second branch (82).

6. A thermal management device according to any one of the preceding claims, characterized in that the second circuit (B) for the heat transfer fluid comprises:

-a two-fluid heat exchanger (5),

-a first heat transfer fluid flow pipe (50) comprising an internal radiator (54) for the passage therethrough of an air flow (100) inside the motor vehicle and connecting a first junction point (61) located downstream of the two-fluid heat exchanger (5) and a second junction point (62) located upstream of said two-fluid heat exchanger (5),

-a second heat transfer fluid circulation pipe (60) comprising a second external radiator (64) for the passage therethrough of an air flow (200) external to the motor vehicle and connecting a first junction point (61) downstream of the two-fluid heat exchanger (5) and a second junction point (62) upstream of said two-fluid heat exchanger (5), and

-a pump (18) located downstream or upstream of the two-fluid heat exchanger (5), between the first junction point (61) and the second junction point (62).

7. The thermal management device according to claim 6, characterized in that it is configured to operate in a cooling mode in which a refrigerant fluid circulates in a first circuit (A) for a refrigerant fluid, in turn in:

-a compressor (3) wherein the refrigerant fluid is converted to a high pressure,

-a two-fluid heat exchanger (5),

-a first external radiator (84) via a shunt branch (80),

-a first internal heat exchanger (19),

-a second internal heat exchanger (19'),

-a first portion of the refrigerant fluid enters the second bypass line (40), enters the third expansion device (17), the refrigerant fluid undergoes a pressure drop in the third expansion device (17) and is transformed to a low pressure, said low pressure refrigerant fluid then circulates in the cooler (15),

-a second portion of the refrigerant fluid enters the first expansion device (7), the evaporator (9) and the first bypass line (30), the refrigerant fluid being subjected to a pressure drop in the first expansion device (7) and being converted to a low pressure,

the two portions of refrigerant fluid are joined together upstream of the first internal heat exchanger (19), the refrigerant fluid then passing through at least the first internal heat exchanger (19) before returning to the compressor (3),

and wherein in the second circuit (B) for the heat transfer fluid, the heat transfer fluid leaving the two-fluid heat exchanger (5) circulates in the second external radiator (64) of the second flow duct (60).

8. The thermal management device according to claim 6, characterized in that it is configured to operate in a dehumidification mode in which a refrigerant fluid circulates in a first circuit (A) for a refrigerant fluid, in turn in:

-a compressor (3) wherein the refrigerant fluid is converted to a high pressure,

-a two-fluid heat exchanger (5),

-a first external radiator (84) via a shunt branch (80),

-a first internal heat exchanger (19),

-a second internal heat exchanger (19'),

-a first portion of the refrigerant fluid enters the second bypass line (40), enters the third expansion device (17), the refrigerant fluid undergoes a pressure drop in the third expansion device (17) and is transformed to a low pressure, said low pressure refrigerant fluid then circulates in the cooler (15),

-a second part of the refrigerant fluid enters the first expansion device (7), the evaporator (9), the second expansion device (11) and the evaporator/condenser (13), the refrigerant fluid undergoes a pressure drop in the first expansion device (7) and is converted to a low pressure, the refrigerant fluid passes the second expansion device (11) without a pressure drop,

the two portions of refrigerant fluid are joined together upstream of the first internal heat exchanger (19), and the refrigerant fluid then passes through the first internal heat exchanger (19) before returning to the compressor (3),

and wherein, in the second circuit (B) for the heat transfer fluid, the heat transfer fluid leaving the two-fluid heat exchanger (5) flows in the internal radiator (54) and releases thermal energy.

9. The thermal management device according to claim 6, characterized in that it is configured to operate in a further dehumidification mode in which a refrigerant fluid circulates in the first circuit (A) for a refrigerant fluid, in turn in:

-a compressor (3) wherein the refrigerant fluid is converted to a high pressure,

-a two-fluid heat exchanger (5),

-a portion of the refrigerant fluid passes through the first external radiator (84) via the tapping branch (80), another portion flows directly towards the first internal heat exchanger (19),

-a first internal heat exchanger (19),

-a second internal heat exchanger (19'),

-a first portion of the refrigerant fluid enters the second bypass line (40), enters the third expansion device (17), the refrigerant fluid undergoes a pressure drop in the third expansion device (17) and is transformed to a low pressure, said low pressure refrigerant fluid then circulates in the cooler (15),

-a second part of the refrigerant fluid enters the first expansion device (7), the evaporator (9), the second expansion device (11) and the evaporator/condenser (13), the refrigerant fluid undergoes a pressure drop in the first expansion device (7) and is converted to a low pressure, the refrigerant fluid passes the second expansion device (11) without a pressure drop,

the first and second portions of refrigerant fluid are joined together upstream of the first internal heat exchanger (19), the refrigerant fluid then passing through the first internal heat exchanger (19) before returning to the compressor (3),

and wherein, in the second circuit (B) for the heat transfer fluid, the heat transfer fluid leaving the two-fluid heat exchanger (5) flows in the internal radiator (54) and releases thermal energy.

Technical Field

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

Background

Motor vehicles nowadays increasingly comprise thermal management devices with air conditioning circuits. Generally speaking, in a "conventional" air-conditioning circuit, a refrigerant fluid passes, in sequence, through a compressor, a first heat exchanger (called condenser) in contact with the air flow outside the motor vehicle to release heat, an expansion device, and a second heat exchanger (called evaporator) in contact with the air flow inside the motor vehicle to cool it.

There is also a more complex air-conditioning circuit architecture, which makes it possible to obtain a reversible air-conditioning circuit, which means that it can absorb thermal energy from the outside air at a first heat exchanger, then called evaporator/condenser, and release it to the vehicle interior, in particular through a dedicated third heat exchanger.

This can be achieved in particular by using an indirect air conditioning circuit. By indirect is meant here that the air conditioning circuit comprises two circuits for the circulation of two different fluids, such as a refrigerant fluid and glycol-water, for various heat exchanges.

The air-conditioning circuit therefore comprises a first circuit for a refrigerant fluid in which a refrigerant fluid circulates, a second circuit for a heat-transfer fluid in which a heat-transfer fluid circulates, and a two-fluid heat exchanger which is jointly arranged on the first circuit for the refrigerant fluid and on the second circuit for the heat-transfer fluid, so as to allow heat exchange between said circuits.

Such an air conditioning circuit may be used in various operating modes, although in the case of electric or hybrid vehicles, a secondary thermal management circuit is used to perform thermal management of elements such as batteries and electronic components. However, this architecture may prove insufficient to remove the heat accumulated in the refrigerant fluid in certain modes, particularly when the battery requires a large amount of cooling power, such as during rapid discharge or charging.

Disclosure of Invention

It is therefore an object of the present invention to at least partly overcome the drawbacks of the prior art and to propose an improved thermal management device which allows thermal management of components such as batteries, in particular when a large amount of cooling power is required.

The present invention therefore relates to a thermal management device comprising an indirect air-conditioning circuit for a motor vehicle, comprising:

-a first circuit for a refrigerant fluid for circulation therein, said first circuit for a refrigerant fluid comprising, in the direction of circulation of the refrigerant fluid, a compressor, a two-fluid heat exchanger, a first expansion device, an evaporator, a second expansion device and an evaporator/condenser, and

-a first bypass pipe bypassing the evaporator/condenser and comprising a first shut-off valve,

a first internal heat exchanger allowing heat exchange between a high pressure refrigerant fluid leaving the two-fluid heat exchanger and a low pressure refrigerant fluid leaving the evaporator/condenser or leaving the first bypass pipe,

-a second internal heat exchanger allowing heat exchange between a high pressure refrigerant fluid leaving the first internal heat exchanger and a low pressure refrigerant fluid circulating in the first bypass pipe,

a second bypass line bypassing the first expansion device and the evaporator, said second bypass line comprising a third expansion device upstream of the cooler,

-a branching circuit connecting a first branch downstream of the two-fluid heat exchanger between the two-fluid heat exchanger and the first internal heat exchanger to a second branch upstream of the first internal heat exchanger between the first internal heat exchanger and the first branch, the branching circuit comprising a first external radiator,

-a second circuit for a heat transfer fluid for circulation in the second circuit,

the two-fluid heat exchangers are commonly arranged on the one hand on a first circuit for the refrigerant fluid downstream of the compressor, between said compressor and the first expansion device, and on the other hand on a second circuit for the heat transfer fluid.

According to an aspect of the invention, the indirect air conditioning circuit comprises means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger directly towards the first internal heat exchanger and/or towards the tapping branch.

According to another aspect of the invention, an apparatus for redirecting refrigerant fluid exiting a two-fluid heat exchanger comprises:

-a first shut-off valve arranged on the main circuit downstream of the first branch, between the first branch and the second branch, and

a second shut-off valve arranged on the branching path downstream of the first branch, between the first branch and the first external radiator.

According to another aspect of the invention, the means for redirecting refrigerant fluid exiting the two-fluid heat exchanger comprises a three-way valve disposed at the first branch.

According to another aspect of the invention, the flow dividing branch comprises a check valve arranged downstream of the first external radiator, between said first external radiator and the second branch, so as to block the refrigerant flow coming from said second branch.

According to another aspect of the invention, a second circuit for a heat transfer fluid comprises:

-a two-fluid heat exchanger,

a first heat transfer fluid flow pipe comprising an internal radiator for the air flow inside the motor vehicle passing through it and connecting a first junction point located downstream of the two-fluid heat exchanger and a second junction point located upstream of said two-fluid heat exchanger,

-a second heat-transfer fluid circulation pipe comprising a second external radiator for the passage therethrough of an air flow external to the motor vehicle and connecting a first junction point located downstream of the two-fluid heat exchanger and a second junction point located upstream of said two-fluid heat exchanger, and

-a pump located downstream or upstream of the two-fluid heat exchanger, between the first junction point and the second junction point.

According to another aspect of the invention, a thermal management device is configured to operate in a cooling mode in which a refrigerant fluid circulates in a first circuit for the refrigerant fluid, in turn in:

-a compressor, wherein the refrigerant fluid is converted to a high pressure,

-a two-fluid heat exchanger,

-a first external heat sink via the shunt branch,

-a first internal heat exchanger having a first heat exchanger,

-a second internal heat exchanger having a first heat exchanger,

a first portion of the refrigerant fluid enters the second bypass line, enters the third expansion device, in which it undergoes a pressure drop and transforms to a low pressure, which then circulates in the cooler,

a second portion of the refrigerant fluid enters the first expansion device, the evaporator and the first bypass line, the refrigerant fluid being subjected to a pressure drop in the first expansion device and being converted to a low pressure,

the two portions of refrigerant fluid are combined upstream of the first internal heat exchanger, and then the refrigerant fluid passes through at least the first internal heat exchanger before returning to the compressor,

and wherein in the second circuit for the heat transfer fluid, the heat transfer fluid leaving the two-fluid heat exchanger circulates in the second external heat sink of the second flow pipe.

According to another aspect of the invention, the thermal management device is configured to operate in a dehumidification mode in which the refrigerant fluid circulates in a first circuit for the refrigerant fluid, in turn in:

-a compressor, wherein the refrigerant fluid is converted to a high pressure,

-a two-fluid heat exchanger,

-a first external heat sink via the shunt branch,

-a first internal heat exchanger having a first heat exchanger,

-a second internal heat exchanger having a first heat exchanger,

a first portion of the refrigerant fluid enters the second bypass line, enters the third expansion device, in which it undergoes a pressure drop and transforms to a low pressure, which then circulates in the cooler,

a second portion of the refrigerant fluid enters the first expansion device, the evaporator, the second expansion device and the evaporator/condenser, the refrigerant fluid undergoes a pressure drop in the first expansion device and is converted to a low pressure, the refrigerant fluid passes through the second expansion device without a pressure drop,

the two portions of refrigerant fluid are combined upstream of the first internal heat exchanger, and the refrigerant fluid then passes through the first internal heat exchanger before returning to the compressor,

and wherein, in the second circuit for the heat transfer fluid, the heat transfer fluid leaving the two-fluid heat exchanger circulates in the internal radiator and releases thermal energy.

According to another aspect of the invention, the thermal management device is configured to operate in a further dehumidification mode in which the refrigerant fluid circulates in the first circuit for the refrigerant fluid, in turn in:

-a compressor, wherein the refrigerant fluid is converted to a high pressure,

-a two-fluid heat exchanger,

a part of the refrigerant fluid passes through the first external radiator via the branch, and another part flows directly to the first internal heat exchanger,

-a first internal heat exchanger having a first heat exchanger,

-a second internal heat exchanger having a first heat exchanger,

a first portion of the refrigerant fluid enters the second bypass line, enters the third expansion device, in which it undergoes a pressure drop and transforms to a low pressure, which then circulates in the cooler,

a second portion of the refrigerant fluid enters the first expansion device, the evaporator, the second expansion device and the evaporator/condenser, the refrigerant fluid undergoes a pressure drop in the first expansion device and is converted to a low pressure, the refrigerant fluid passes through the second expansion device without a pressure drop,

the first and second portions of the refrigerant fluid are combined upstream of the first internal heat exchanger, and the refrigerant fluid then passes through the first internal heat exchanger before returning to the compressor,

and wherein, in the second circuit for the heat transfer fluid, the heat transfer fluid leaving the two-fluid heat exchanger circulates in the internal radiator and releases thermal energy.

Drawings

Other characteristics and advantages of the present invention will become clearer from reading the following description, given by way of illustrative and non-limiting example, and of the accompanying drawings, in which:

figure 1 is a schematic view of a thermal management device according to a first embodiment,

figure 2 is a schematic view of a thermal management device according to a second embodiment,

figure 3 is a schematic view of a thermal management device according to a third embodiment,

figure 4 is a schematic view of a thermal management device according to a fourth embodiment,

figure 5 shows an expansion device according to an alternative embodiment,

figure 6 is a schematic view of a second circuit for a heat transfer fluid of the thermal management device of figures 1 to 4 according to an alternative embodiment,

figure 7a is a schematic view of the thermal management device of figure 2 according to a first cooling mode,

figure 7b is a schematic view of the thermal management device of figure 2 according to a second cooling mode,

figure 8a is a schematic view of the thermal management device of figure 2 according to a third cooling mode,

figure 8b is a schematic view of the thermal management device of figure 2 according to a fourth cooling mode,

figure 9a is a schematic view of the thermal management device of figure 2 according to a fifth cooling mode,

figure 9b is a schematic view of the thermal management device of figure 2 according to a sixth cooling mode,

figure 10a is a schematic view of the thermal management device of figure 2 according to a first dehumidification mode,

FIG. 10b is a schematic view of the thermal management device of FIG. 2 according to a second dehumidification mode,

FIG. 10c is a schematic view of the thermal management device of FIG. 2 according to a third dehumidification mode,

figure 11a is a schematic view of the thermal management device of figure 2 according to a fourth dehumidification mode,

figure 11b is a schematic view of the thermal management device of figure 2 according to a fifth dehumidification mode,

fig. 11c is a schematic view of the thermal management device of fig. 2 according to a sixth dehumidification mode.

Like elements have like reference numerals throughout the various figures.

Detailed Description

The following embodiments are examples. Although the description refers to one or more embodiments, this does not necessarily mean that each reference refers to the same embodiment, or that a feature only applies to one embodiment. Individual features of different embodiments may also be combined and/or interchanged to create other embodiments.

In this specification, some elements or parameters may be indexed, such as a first element or a second element, and a first parameter and a second parameter or even a first criterion and a second criterion, etc. In this case, this is a simple index used to distinguish and represent similar but not identical elements or parameters or criteria. Such indexing does not imply that one element, parameter or criteria takes precedence over another element, parameter or criteria and such names may be readily interchanged without departing from the scope of the present specification. Moreover, such indexing does not imply any chronological order, such as when evaluating any given criteria.

In the present description, "upstream" means that one element is located before the other element with respect to the direction of fluid communication. Conversely, "positioned downstream" means that one element is positioned after another element, relative to the direction of fluid flow.

Fig. 1 shows a thermal management device comprising an indirect air conditioning circuit 1 for a motor vehicle. The indirect air-conditioning circuit 1 comprises in particular:

a first circuit A for a refrigerant fluid intended to circulate in the first circuit,

-a second circuit B for a heat transfer fluid for circulation in the second circuit, and

a two-fluid heat exchanger 5, commonly arranged on a first circuit a for refrigerant fluid and a second circuit B for heat transfer fluid, allowing heat exchange between said first circuit a for refrigerant fluid and said second circuit B for heat transfer fluid.

More particularly, the first circuit a for refrigerant fluid comprises, in the direction of circulation of the refrigerant fluid:

-a compressor 3 for compressing the refrigerant in the compressor,

a two-fluid heat exchanger 5, located downstream of the compressor 3,

-a first expansion device 7 for expanding the gas,

an evaporator 9 for the passage therethrough of an air flow 100 inside the motor vehicle,

-a second expansion device 11 for expanding the gas,

an evaporator/condenser 13 for the passage therethrough of an air flow 200 external to the motor vehicle, and

a first bypass 30 bypassing the evaporator/condenser 13.

As used herein, a "radiator" refers to a heat exchanger whose primary function is to dissipate thermal energy, in this case into the interior air stream 100 or the exterior air stream 200.

As used herein, the term "evaporator" refers to a heat exchanger whose primary function is to absorb thermal energy, in this case into the internal air flow 100. Within the "evaporator", the refrigerant fluid typically transitions from a liquid phase to a vapor phase or a two-phase mixture.

The term "two-fluid heat exchanger" as used herein refers to a heat exchanger in which a refrigerant fluid from a first circuit a for a refrigerant fluid and a heat transfer fluid from a second circuit B for a heat transfer fluid flow simultaneously. Here, the main function of the two-fluid heat exchanger is to dissipate the thermal energy, in this case by supplying it to the heat transfer fluid of the second circuit B. Within the two-fluid heat exchanger, the refrigerant fluid transitions from a vapor phase to a liquid phase.

As used herein, the term "evaporator/condenser" refers to a heat exchanger that is also capable of dissipating or absorbing heat energy, in this case with respect to the flow of outside air 200.

The internal airflow 100 referred to herein is the airflow for the interior compartment of the motor vehicle. Thus, the evaporator 9 can be arranged within a heating, ventilating and air conditioning unit. The external air flow 200 refers to an air flow originating from outside the motor vehicle. The evaporator/condenser 13 can thus be arranged on the front side of the motor vehicle.

The first bypass 30 may more specifically connect the first connection point 31 and the second connection point 32.

The first connection point 31 is preferably positioned downstream of the evaporator 9, in the direction of refrigerant fluid circulation, between said evaporator 9 and the evaporator/condenser 13. More specifically, as shown in fig. 1, the first connection point 31 is located between the evaporator 9 and the second expansion device 11. However, it is fully contemplated that the first connection point 31 is located between the second expansion device 11 and the evaporator/condenser 13, as long as it is possible for the refrigerant fluid to bypass or pass through the second expansion device 11 without experiencing a pressure drop.

The second connection point 32 is itself preferably located downstream of the evaporator/condenser 13, between said heat exchanger 13 and the compressor 3.

To control whether the refrigerant fluid passes within the first bypass pipe 30, the first bypass pipe 30 includes a first shut-off valve 33. In order to keep the refrigerant fluid from passing through the evaporator/condenser 13, the second expansion device 11 may in particular comprise a shut-off function, i.e. the ability to stop the refrigerant fluid flow when it is shut off. An alternative may be to position a shut-off valve between the second expansion means 11 and the first connection point 31.

Another alternative (not shown) would be to install a three-way valve at the first connection point 31.

The first circuit a for the refrigerant fluid may also comprise a non-return valve 23 downstream of the evaporator/condenser 13, between said evaporator/condenser 13 and the second connection point 32, to prevent any backflow of the refrigerant fluid from the first bypass 30 towards the evaporator/condenser 13.

The term stop valve, check valve, three-way valve or expansion device with a closing function as used herein refers to a mechanical or electromechanical element which is automatically adjusted or operated by an electronic control unit carried on the motor vehicle.

The first circuit a for the refrigerant fluid also comprises a first internal heat exchanger 19 (or IHX) which allows the heat exchange between the high pressure refrigerant fluid leaving the two-fluid heat exchanger 5 and the low pressure refrigerant fluid leaving the evaporator/condenser 13 or leaving the first bypass 30. The first internal heat exchanger 19 comprises in particular an inlet and an outlet for a low pressure refrigerant fluid from the second connection point 32 and an inlet and an outlet for a high pressure refrigerant fluid from the two-fluid heat exchanger 5.

By high pressure refrigerant fluid is meant refrigerant fluid that has experienced a pressure increase at the compressor 3 and has not experienced a pressure drop due to one of the expansion devices. By low pressure refrigerant fluid is meant refrigerant fluid that experiences a pressure drop and is at a pressure close to the pressure at the inlet of the compressor 3.

The first circuit a for refrigerant fluid also comprises a second internal heat exchanger 19' (or IHX) allowing heat exchange between the high pressure refrigerant fluid leaving the first internal heat exchanger 19 and the low pressure refrigerant fluid circulating in the first bypass 30. This second internal heat exchanger 19' comprises in particular an inlet and an outlet for the low-pressure refrigerant fluid coming from the first connection point 31, and an inlet and an outlet for the high-pressure refrigerant fluid coming from the first internal heat exchanger 19. As shown in fig. 1, the second internal heat exchanger 19' may be located downstream of the first shut-off valve 33.

At least one of the first internal heat exchanger 19 and the second internal heat exchanger 19' may be a coaxial heat exchanger, which means that one heat exchanger comprises two coaxial tubes and heat exchange takes place between these two tubes.

Preferably, the first internal heat exchanger 19 may be a coaxial internal heat exchanger of a length between 50 and 120mm, while the second internal heat exchanger 19' may be a coaxial internal heat exchanger of a length between 200 and 700 mm.

The first circuit a for refrigerant fluid may also comprise a desiccant bottle 14 located downstream of the two-fluid heat exchanger 5, more particularly between said two-fluid heat exchanger 5 and a first internal heat exchanger 19. Such desiccant bottles, which are located on the high pressure side of the air-conditioning circuit (i.e. downstream of the two-fluid heat exchanger 5 and upstream of the expansion device), are less bulky and less costly than other phase separation solutions, such as an accumulator located on the low pressure side of the air-conditioning circuit (i.e. upstream of the compressor 3, in particular upstream of the first internal heat exchanger 19).

The first expansion means 7 and the second expansion means 11 may be electronic expansion valves, i.e. expansion valves that: the outlet refrigerant fluid pressure is controlled by an actuator that fixes the open cross-section of the expansion device, thereby fixing the fluid pressure at the outlet. Such an electronic expansion valve is particularly capable of allowing refrigerant fluid to pass therethrough without a pressure drop when the expansion device is fully open.

According to a preferred embodiment, the first expansion means 7 is an electronic expansion valve, which may be controlled by a control unit incorporated in the vehicle, and the second expansion means 11 is a thermostatic expansion valve.

The second expansion device 11 may in particular be a thermostatic expansion valve incorporating a shut-off function. In this case, as shown in fig. 5, the first and second expansion means 7, 11 can be bypassed by a shunt tube a', which comprises in particular a shut-off valve 25. The shunt tube a' allows refrigerant fluid to bypass the first and second expansion devices 7, 11 without experiencing a pressure drop. Preferably, at least the second expansion device 11 is a thermostatic expansion valve comprising a shunt tube a'. The first expansion device 7 may also comprise a shut-off function or, downstream thereof, a shut-off valve so as to block or unblock the passage of refrigerant fluid.

The first circuit a for the refrigerant fluid also comprises a second bypass line 40 which bypasses the first expansion device 7 and the evaporator 9. The second bypass line 40 includes the third expansion device 17 upstream of the cooler 15. The coolers 15 may be arranged jointly on the secondary heat management circuit. More particularly, the secondary thermal management circuit may be a circuit in which a heat transfer fluid circulates, connected to a heat exchanger or cold plate in the area of the battery and/or the electronic components. The cooler 15 may also be a heat exchanger in direct contact with the element to be cooled, such as a battery.

The third expansion device 17 may also include a shut-off function to allow or disallow refrigerant fluid to pass through the second bypass line 40. An alternative is to locate a shut-off valve on the second bypass line 40 upstream of the third expansion device 17.

The second bypass line 40 is connected on the one hand upstream of the first expansion device 7. This connection is made at a third connection point 41, located upstream of the first expansion device 7, between the second internal heat exchanger 19' and said first expansion device 7.

According to the first embodiment shown in fig. 1, on the other hand, the second bypass pipe 40 is connected to the first bypass pipe 30 upstream of the first shut-off valve 33 and the second internal heat exchanger 19'. When the first shut-off valve 33 is located upstream of the second internal heat exchanger 19', as shown in fig. 1, this connection is made at a fourth connection point 42 located between the first connection point 31 and the first shut-off valve 33.

According to the second embodiment shown in fig. 2, on the other hand, a second bypass pipe 40 is connected to the first bypass pipe 30 upstream of the second internal heat exchanger 19' and downstream of the first shut-off valve 33. As shown in fig. 2, when the first shut-off valve 33 is located upstream of the second internal heat exchanger 19 ', the fourth connection point 42 is located between the first shut-off valve 33 and the second internal heat exchanger 19'.

Fig. 3 shows a third embodiment, in which a second bypass line 40 is connected on the one hand upstream of the first expansion device 7 and on the other hand downstream of the second expansion device 19 ', between said second expansion device 19' and the first internal heat exchanger 19. The third connection point 41 is therefore also located upstream of the first expansion device 7, between the second internal heat exchanger 19' and said first expansion device 7.

In the example of fig. 3, the fourth connection point 42 is located downstream of the first bypass 30, between the second connection point 32 and the first internal heat exchanger 19. However, it is also fully conceivable that the fourth connection point 42 is located on the first bypass pipe 30, downstream of the first shut-off valve 33 and the second internal heat exchanger 19'.

Fig. 4 shows a fourth embodiment identical to that of fig. 3, except that the first circuit a for the refrigerant fluid comprises a shunt tube 70, which shunt tube 70 is connected on the one hand to the first bypass 30, upstream of the first shut-off valve 33 and the second internal heat exchanger 19'. When the first shut-off valve 33 is located upstream of the second internal heat exchanger 19', as shown in fig. 4, the connection is realized through a fifth connection point 71 between the first connection point 31 and the first shut-off valve 33.

On the other hand, the shunt tube 70 is connected to the second bypass line 40 upstream of the third expansion device 17 between the third expansion device 17 and the second stop valve 73. The second shut-off valve 73 is located between the third connection point 41 and the third expansion device 17. Thus, the connection of the shunt tube 70 is made at the fifth connection point 72 located downstream of the second shut-off valve 73. The bypass tube 70 includes a third shut-off valve 74 to allow or disallow refrigerant fluid to pass therethrough.

The first circuit a for refrigerant fluid also comprises a branch line 80 connecting the first branch 81 to the second branch 82. The first branch 81 is located downstream of the two-fluid heat exchanger, between said two-fluid heat exchanger 5 and the first internal heat exchanger 19. The second branch 82 is itself located upstream of the first internal heat exchanger 19, between said first internal heat exchanger 19 and the first branch 81.

Shunt loop 80 includes a first external radiator 84. The first external heat sink 84 is used to pass an external air flow 200 through it. The first external radiator 84 may in particular be located on the front face of the motor vehicle, upstream of the evaporator/condenser 13. The first external radiator 84 also has the function of subcooling the refrigerant fluid. Therefore, the first radiator 84 is sometimes also referred to as a subcooler.

The indirect air-conditioning circuit 1, more particularly the first circuit a for the refrigerant fluid, comprises means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger 5 directly towards the first internal heat exchanger 19 and/or the branching 80.

According to a first variant illustrated in fig. 1 to 4, the means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger 5 may comprise:

a first shut-off valve 82a arranged on the main circuit a downstream of the first branch 81, between the first branch 81 and the second branch 82, and

a second shut-off valve 82b arranged on the branch 80 downstream of the first branch 81, between the first branch 81 and the first external radiator 84.

According to a second variant, not shown, the means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger 5 comprise a three-way valve arranged at the first branch 81.

The shunt branch 80 may also include a check valve 83 downstream of the first external radiator 84 between the first external radiator 84 and the second branch 82. The check valve 83 is positioned to block refrigerant flow from the second branch 82.

The second circuit B for the heat transfer fluid may itself comprise:

-a two-fluid heat exchanger 5,

a first heat transfer fluid flow pipe 50 comprising an internal radiator 54 for the passage therethrough of an air flow 100 inside the motor vehicle and connecting a first junction point 61 downstream of the two-fluid heat exchanger 5 and a second junction point 62 upstream of said two-fluid heat exchanger 5,

a second heat-transfer fluid circulation duct 60 comprising a second external radiator 64 for the passage therethrough of an air flow 200 external to the motor vehicle and connecting a first junction point 61 downstream of the two-fluid heat exchanger 5 and a second junction point 62 upstream of said two-fluid heat exchanger 5, and

a pump 18, located downstream or upstream of the two-fluid heat exchanger 5, between the first junction point 61 and the second junction point 62.

Thus, the interior radiator 54 may be disposed within the hvac unit. Preferably, the radiator 54 is located downstream of the evaporator in the direction of circulation of the internal air flow 100. The second external radiator 64 may itself be located at the front of the motor vehicle, for example upstream of the evaporator/condenser 13, more particularly between the first external radiator 84 and the evaporator/condenser 13, in the direction of circulation of the external air flow 200.

The indirectly reversible air-conditioning circuit 1 comprises, within the second circuit B for the heat transfer fluid, means for redirecting the heat transfer fluid coming from the two-fluid heat exchanger 5 towards the first through duct 50 and/or the second through duct 60.

As shown in fig. 1 to 4, said means for redirecting the heat transfer fluid coming from the two-fluid heat exchanger 5 may in particular comprise a fourth shut-off valve 63 on the second flow duct 60, so as to block or unblock the heat transfer fluid and prevent it from circulating in said second flow duct 60.

In a hvac unit, the thermal management device may also include a baffle 310 for blocking the flow of internal air 100 through the internal heat sink 54.

This embodiment makes it possible in particular to limit the number of valves in the second circuit B for the heat transfer fluid, thus making it possible to limit the production costs.

According to an alternative embodiment shown in fig. 6, the means for redirecting the heat transfer fluid coming from the two-fluid heat exchanger 5 may comprise in particular:

a fourth shut-off valve 63 located on the second flow duct 60 so as to block or unblock the heat transfer fluid and prevent it from circulating in said second flow duct 60, an

A fifth shut-off valve 53, which is located on the first through duct 50 so as to block or unblock the heat transfer fluid and prevent it from circulating in said first through duct 50.

The second circuit B for the heat transfer fluid may also comprise an electric heating element 55 for heating the heat transfer fluid. The electric heating element 55 is positioned, in particular in the direction of circulation of the heat transfer fluid, downstream of the two-fluid heat exchanger 5, between said two-fluid heat exchanger 5 and the first junction point 61.

The invention also relates to a set of methods for operating a thermal management device according to the various operating modes shown in fig. 7a to 11 c. In these fig. 7a to 11c, only the elements in which the refrigerant fluid and/or the heat transfer fluid circulate are depicted. The direction of circulation of the refrigerant fluid and/or the heat transfer fluid is indicated by arrows. The examples shown in fig. 7a to 11c all show a first circuit a for refrigerant fluid, more specifically the connection of the second bypass pipe 40 according to the embodiment of fig. 2. However, the modes of operation described below are fully contemplated for the embodiments of fig. 1, 3 and 4.

1. A first cooling mode:

fig. 7a shows a first cooling mode, in which, in the first circuit a for the refrigerant fluid, the refrigerant fluid circulates in the following order:

a compressor 3, in which the refrigerant fluid is converted to a high pressure,

a two-fluid heat exchanger 5, in which the refrigerant fluid releases thermal energy to the heat transfer fluid of the second circuit B for heat transfer fluid,

a first internal heat exchanger 19 for the heat exchange,

a second internal heat exchanger 19',

a first expansion device 7, in which the refrigerant fluid undergoes a pressure drop and transforms to a low pressure,

an evaporator 9, in which the refrigerant fluid absorbs thermal energy from the internal air flow 100, cooling the internal air flow 100,

a first bypass 30, in which the refrigerant fluid enters the second internal heat exchanger 19', and

a first internal heat exchanger 19 and then back to the compressor 3.

In the second circuit B for the heat transfer fluid, the heat transfer fluid leaving the two-fluid heat exchanger 5 circulates in the second external radiator 64 of the second circulation pipe 60.

As shown in the example of fig. 7a, a portion of the heat transfer fluid leaving the two-fluid heat exchanger 5 circulates in the inner radiator 54 of the first flow tube 50 and another portion of the heat transfer fluid leaving the two-fluid heat exchanger 5 circulates in the second outer radiator 64 of the second flow tube 60. The baffle 310 is closed to prevent the flow of the internal air stream 100 through the internal heat sink 54.

The refrigerant fluid entering the compressor 3 is in the vapor phase. The refrigerant fluid undergoes compression as it passes through the compressor 3. The refrigerant fluid is then said to be at a high pressure.

The high pressure refrigerant fluid passes through the two-fluid heat exchanger 5 and experiences a drop in thermal energy due to its transformation into the liquid phase and due to the transfer of this thermal energy to the heat transfer fluid of the second circuit B for the heat transfer fluid. The high pressure refrigerant fluid loses heat energy while maintaining a constant pressure.

The high pressure refrigerant fluid does not enter the tap branch 80 because the means for redirecting the refrigerant fluid exiting the two-fluid heat exchanger 5 redirects the refrigerant fluid directly toward the first heat exchanger 19. To this end, in the example shown in fig. 7a, the first shut-off valve 82a of the device is open, while the second shut-off valve 82b of the device is closed.

The high pressure refrigerant fluid then enters the first internal heat exchanger 19 where it loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid from the first bypass line 30.

The high pressure refrigerant fluid then enters the second internal heat exchanger 19' where it again loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid passing through the first bypass line 30.

On leaving the second internal heat exchanger 19', the refrigerant fluid does not circulate in the second bypass line 40, since the third expansion device 17 is closed.

The refrigerant fluid then passes through a first expansion device 7, where the refrigerant fluid undergoes a pressure drop and transitions to a low pressure in the first expansion device 7.

The low pressure refrigerant fluid then enters the evaporator 9 where it picks up heat energy while cooling the internal air stream 100. The refrigerant fluid is converted back to the gaseous state. On leaving the evaporator 9, the refrigerant fluid is redirected towards the first bypass 30. The second expansion device 11 is closed so that refrigerant fluid does not enter the evaporator/condenser 13.

The low pressure refrigerant fluid then enters the second interior heat exchanger 19 'where it picks up heat energy from the high pressure refrigerant fluid passing through the second interior heat exchanger 19'.

The low pressure refrigerant fluid then enters the first interior heat exchanger 19 where it again obtains thermal energy from the high pressure refrigerant fluid passing through the first interior heat exchanger 19. The low pressure refrigerant fluid then returns to the compressor 3.

This first cooling mode is useful for cooling the internal airflow 100.

In this first cooling mode, the two internal heat exchangers 19 and 19' are active and their effects combine. The use of the internal heat exchangers 19 and 19' one after the other makes it possible to reduce the enthalpy of the refrigerant fluid entering the first expansion means 7. The liquid refrigerant fluid leaving the two-fluid heat exchanger 5 is cooled by the gaseous low-pressure refrigerant fluid leaving the evaporator 9. The enthalpy difference across the evaporator 9 is significantly increased, which increases the available cooling power at said evaporator 9 of the cooling air flow 100, thereby increasing the coefficient of performance (COP).

Furthermore, the addition of thermal energy to the low-pressure refrigerant fluid at the first and second internal heat exchangers 19, 19' makes it possible to limit the proportion of refrigerant fluid in the liquid phase before it enters the compressor 3, in particular when the air-conditioning circuit 1 comprises a desiccant bottle 14 located downstream of the two-fluid heat exchanger 5.

In the second circuit B for the heat transfer fluid, the heat transfer fluid obtains thermal energy from the refrigerant fluid at the two-fluid heat exchanger 5.

As shown in fig. 7a, a portion of the heat transfer fluid circulates in the first flow tube 50 and passes through the internal radiator 54. However, the heat transfer fluid does not lose thermal energy because the baffle 310 closes and blocks the internal airflow 100 so that it does not pass through the internal heat sink 54.

Another portion of the heat transfer fluid circulates in the second flow tube 60 and passes through the second external radiator 64. The heat transfer fluid loses thermal energy at the second external heat sink 64 by releasing it into the external air stream 200. The fourth shutoff valve 63 is opened to allow the heat transfer fluid to pass therethrough.

An alternative (not shown) for preventing the heat transfer fluid from exchanging with the internal air flow 100 at the internal radiator 54 is to equip the first through-flow duct 50 with a fifth shut-off valve 53 as shown in fig. 6 and to close this valve to prevent the heat transfer fluid from circulating in said first through-flow duct 50.

2. A second cooling mode:

fig. 7b shows a second cooling mode. This second cooling mode is the same as the first cooling mode of fig. 7a, except that upon exiting the two-fluid heat exchanger 5, the refrigerant fluid passes through the tap branch 80 and the first external radiator 84. To this end, the means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger 5 redirects the refrigerant fluid directly towards the first external heat sink 84 and not towards the first internal heat exchanger 19. For this purpose, in the example shown in fig. 7b, the first shut-off valve 82a of the device is closed, while the second shut-off valve 82b of the device is open.

In the first external heat sink 84, the refrigerant fluid releases thermal energy to the external air flow 200. This allows more heat to be removed than can be removed by the third heat sink 64 alone. This is particularly advantageous when the need for cooling by the evaporator 9 is high. The first external heat sink 84 also provides additional surface area for exchange with the external air stream 200. This allows the refrigerant fluid to reduce its temperature (and therefore its enthalpy) before entering the first internal heat exchanger 19, in order to increase the cooling performance of the system.

3. A third cooling mode:

fig. 8a shows a third cooling mode, in which, in the first circuit a for the refrigerant fluid, the refrigerant fluid circulates in the following order:

a compressor 3, in which the refrigerant fluid is converted to a high pressure,

a two-fluid heat exchanger 5, in which the refrigerant fluid releases thermal energy to the heat transfer fluid of the second circuit B for heat transfer fluid,

a first internal heat exchanger 19 for the heat exchange,

a second internal heat exchanger 19',

a first portion of the refrigerant fluid enters the second bypass line 40, enters the third expansion device 17, undergoes a pressure drop in the third expansion device 17 and is transformed to a low pressure, which is then circulated in the cooler 15,

a second portion of the refrigerant fluid enters the first expansion device 7, the evaporator 9 and enters the first bypass 30, the refrigerant fluid undergoing a pressure drop in the first expansion device 7 and being converted to a low pressure, heat energy being obtained in the evaporator 9 from the internal air flow 100 cooling the latter.

Then, in the example of fig. 8a, the two portions of refrigerant fluid are merged together at the first bypass pipe 30 upstream of the second inner heat exchanger 19'. The refrigerant fluid then enters the second internal heat exchanger 19' and the first internal heat exchanger 19 before returning to the compressor 3.

Regardless of the connection embodiment of the second bypass line 40 shown in fig. 1 to 4, the two portions of refrigerant fluid are again joined together upstream of the first internal heat exchanger 19. The refrigerant fluid therefore passes at least through the first internal heat exchanger 19 before reaching the compressor 3.

In the second circuit B for the heat transfer fluid, the heat transfer fluid leaving the two-fluid heat exchanger 5 circulates in the second external radiator 64 of the second circulation pipe 50.

As shown in fig. 8a, a portion of the heat transfer fluid exiting the two-fluid heat exchanger 5 circulates through the internal radiator 54 of the first circulation tube 50, while another portion of the heat transfer fluid exiting the two-fluid heat exchanger 5 circulates through the second external radiator 64 of the second circulation tube 50. The baffle 310 is closed to prevent the flow of the internal air stream 100 through the internal heat sink 54.

The refrigerant fluid entering the compressor 3 is in the vapor phase. The refrigerant fluid undergoes compression as it passes through the compressor 3. The refrigerant fluid is then said to be at a high pressure.

The high pressure refrigerant fluid passes through the two-fluid heat exchanger 5 and experiences a drop in thermal energy due to its transformation into the liquid phase and due to the transfer of this thermal energy to the heat transfer fluid of the second circuit B for the heat transfer fluid. The high pressure refrigerant fluid loses heat energy while maintaining a constant pressure.

The high pressure refrigerant fluid does not enter the tap branch 80 because the means for redirecting the refrigerant fluid exiting the two-fluid heat exchanger 5 redirects the refrigerant fluid directly toward the first heat exchanger 19. To this end, in the example shown in fig. 7a, the first shut-off valve 82a of the device is open, while the second shut-off valve 82b of the device is closed.

The high pressure refrigerant fluid then enters the first internal heat exchanger 19 where it loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid from the first bypass line 30.

The high pressure refrigerant fluid then enters the second internal heat exchanger 19' where it again loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid passing through the first bypass line 30.

On leaving the second internal heat exchanger 19', a first portion of the refrigerant fluid enters the second bypass line 40 and a second portion of the refrigerant fluid flows to the first expansion device 7.

A first portion of the refrigerant fluid enters the third expansion device 17. The high pressure refrigerant fluid undergoes an isenthalpic pressure drop and changes state to a two-phase mixture. The refrigerant fluid is now said to be at a low pressure.

The low pressure refrigerant fluid then enters cooler 15, which picks up thermal energy at cooler 15. The refrigerant fluid is converted back to the gaseous state. Upon exiting the cooler 15, the refrigerant fluid reaches the first bypass 30. In the example shown in fig. 8a, the refrigerant fluid reaches the first bypass pipe 30 upstream of the first shut-off valve 33 and the second internal heat exchanger 19'.

On leaving the second internal heat exchanger 19', a second portion of the high pressure refrigerant fluid enters the first expansion device 7. The high pressure refrigerant fluid undergoes an isenthalpic pressure drop and changes state to a two-phase mixture. The refrigerant fluid is now said to be at a low pressure.

The low pressure refrigerant fluid then enters the evaporator 9 where it picks up heat energy while cooling the internal air stream 100. The refrigerant fluid is converted back to the gaseous state. On leaving the evaporator 9, the refrigerant fluid is redirected towards the first bypass 30. The second expansion device 11 is closed so that refrigerant fluid does not enter the evaporator/condenser 13.

The low pressure refrigerant fluid from the evaporator 9 and the second bypass line 40 then enters the second internal heat exchanger 19 ', where it picks up thermal energy from the high pressure refrigerant fluid passing through the second internal heat exchanger 19'.

The low pressure refrigerant fluid then enters the first interior heat exchanger 19 where it again obtains thermal energy from the high pressure refrigerant fluid passing through the first interior heat exchanger 19. The low pressure refrigerant fluid then returns to the compressor 3.

This third cooling mode facilitates cooling of the internal airflow 100 and cooling of components, such as batteries and/or electronic components, that are directly or indirectly cooled by the cooler 15.

In this third cooling mode, the two internal heat exchangers 19 and 19' are active both on the refrigerant flow coming from the evaporator 9 and on the refrigerant flow passing through the second bypass line 40, and their effects are combined. The use of the internal heat exchangers 19 and 19' one after the other makes it possible to reduce the thermal energy of the refrigerant fluid entering the first expansion means 7. The liquid refrigerant fluid leaving the two-fluid heat exchanger 5 is cooled by the gaseous low-pressure refrigerant fluid leaving the evaporator 9 and the cooler 15. The thermal energy difference between the ends of the two heat exchangers is significantly increased, allowing an increase in the cooling power available at the evaporator 9 and the cooler 15, which in turn increases the coefficient of performance (COP).

Furthermore, the addition of thermal energy to the low-pressure refrigerant fluid at the first and second internal heat exchangers 19, 19' makes it possible to limit the proportion of refrigerant fluid in the liquid phase before it enters the compressor 3, in particular when the air-conditioning circuit 1 comprises a desiccant bottle 14 located downstream of the two-fluid heat exchanger 5.

In the second circuit B for the heat transfer fluid, the heat transfer fluid obtains thermal energy from the refrigerant fluid at the two-fluid heat exchanger 5.

As shown in the example of fig. 8a, a portion of the heat transfer fluid circulates in the first flow tube 50 and passes through the internal radiator 54. However, the heat transfer fluid does not lose thermal energy because the baffle 310 closes and blocks the internal airflow 100 so that it does not pass through the internal heat sink 54.

Another portion of the heat transfer fluid circulates in the second flow tube 60 and passes through the second external radiator 64. The heat transfer fluid loses enthalpy at the second external heat sink 64 by releasing into the external air flow 200. The fourth shutoff valve 63 is opened to allow the heat transfer fluid to pass therethrough.

An alternative (not shown) for preventing the heat transfer fluid from exchanging with the internal air flow 100 at the internal radiator 54 is to equip the first through-flow duct 50 with a fifth shut-off valve 53 as shown in fig. 6 and to close this valve to prevent the heat transfer fluid from circulating in said first through-flow duct 50.

4. A fourth cooling mode:

fig. 8b shows a fourth cooling mode. This fourth cooling mode is the same as the third cooling mode of fig. 8a, except that on leaving the two-fluid heat exchanger 5, the refrigerant fluid passes through the tap branch 80 and the first external radiator 84. To this end, the means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger 5 redirects the refrigerant fluid directly towards the first external heat sink 84 and not towards the first internal heat exchanger 19. For this purpose, in the example shown in fig. 8b, the first shut-off valve 82a of the device is closed, while the second shut-off valve 82b of the device is open.

In the first external heat sink 84, the refrigerant fluid releases thermal energy to the external air flow 200. This allows more heat to be removed than can be removed by the third heat sink 64 alone. This is particularly beneficial when the outside temperature is high and the cooling requirements are high, especially when a large amount of thermal energy is absorbed at the cooler 15 and it would not be sufficient to simply remove the thermal energy using the second radiator 64, for example during rapid discharge or charging of the battery of an electric or hybrid vehicle, while keeping the inside airflow 100 cool for comfort.

5. A fifth cooling mode:

fig. 9a shows a fifth cooling mode, in which, in the first circuit for the refrigerant fluid, the refrigerant fluid circulates in the following order:

a compressor 3, in which the refrigerant fluid is converted to a high pressure,

a two-fluid heat exchanger 5, in which the refrigerant fluid releases thermal energy to the heat transfer fluid of the second circuit B for heat transfer fluid,

a first internal heat exchanger 19 for the heat exchange,

a second internal heat exchanger 19',

a second bypass line 40, in which the refrigerant fluid enters the third expansion device 17, where it undergoes a pressure drop and transforms to a low pressure, which is then circulated in the cooler 15,

at least a first internal heat exchanger 19 and then back to the compressor 3. .

In the example of fig. 9a, the second bypass pipe 40 is connected to the first bypass pipe 30 upstream of the second internal heat exchanger 19'. The refrigerant fluid enters the second internal heat exchanger 19' before returning to the compressor 3 and then enters the first internal heat exchanger 19.

In the second circuit B for the heat transfer fluid, the heat transfer fluid leaving the two-fluid heat exchanger 5 circulates in the second external radiator 64 of the second circulation pipe 50.

As shown in fig. 9a, a portion of the heat transfer fluid leaving the two-fluid heat exchanger 5 circulates in the inner radiator 54 of the first flow tube 50 and another portion of the heat transfer fluid leaving the two-fluid heat exchanger 5 circulates in the second outer radiator 64 of the second flow tube 50. The baffle 310 is closed to prevent the flow of the internal air stream 100 through the internal heat sink 54.

The refrigerant fluid entering the compressor 3 is in the vapor phase. The refrigerant fluid undergoes compression as it passes through the compressor 3. The refrigerant fluid is then said to be at a high pressure.

The high pressure refrigerant fluid passes through the two-fluid heat exchanger 5 and experiences a drop in thermal energy due to its transformation into the liquid phase and due to the transfer of this thermal energy to the heat transfer fluid of the second circuit B for the heat transfer fluid. The high pressure refrigerant fluid loses heat energy while maintaining a constant pressure.

The high pressure refrigerant fluid does not enter the tap branch 80 because the means for redirecting the refrigerant fluid exiting the two-fluid heat exchanger 5 redirects the refrigerant fluid directly toward the first heat exchanger 19. To this end, in the example shown in fig. 7a, the first shut-off valve 82a of the device is open, while the second shut-off valve 82b of the device is closed.

The high pressure refrigerant fluid then enters the first internal heat exchanger 19 where it loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid from the first bypass line 30.

The high pressure refrigerant fluid then enters the second internal heat exchanger 19' where it again loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid passing through the first bypass line 30.

On leaving the second internal heat exchanger 19', the refrigerant fluid does not reach the evaporator 9, since the first expansion device 7 is closed. The refrigerant fluid enters the second bypass tube 40.

The refrigerant fluid enters the third expansion device 17. The high pressure refrigerant fluid undergoes an isenthalpic pressure drop and changes state to a two-phase mixture. The refrigerant fluid is now said to be at a low pressure.

The low pressure refrigerant fluid then enters cooler 15, which picks up thermal energy at cooler 15. The refrigerant fluid is converted back to the gaseous state. Upon exiting the cooler 15, the refrigerant fluid reaches the first bypass 30. In the example shown in fig. 9a, the refrigerant fluid reaches the first bypass pipe 30 upstream of the first shut-off valve 33 and the second internal heat exchanger 19'. In order to prevent refrigerant fluid from entering the evaporator/condenser 13, the second expansion device 11 or the first shut-off valve 33 is closed according to an embodiment of the second bypass line 40.

The low pressure refrigerant fluid then enters the second interior heat exchanger 19 'where it gains thermal energy from the high pressure refrigerant fluid passing through the second interior heat exchanger 19'.

The low pressure refrigerant fluid then enters the first interior heat exchanger 19 where it again obtains thermal energy from the high pressure refrigerant fluid passing through the first interior heat exchanger 19. The low pressure refrigerant fluid then returns to the compressor 3.

This cooling mode facilitates cooling of components, such as batteries and/or electronic components, that are directly or indirectly cooled by cooler 15.

In this fifth cooling mode, the two internal heat exchangers 19 and 19' are active both on the refrigerant flow coming from the evaporator 9 and on the refrigerant flow passing through the second bypass line 40, and their effects are combined. The use of the internal heat exchangers 19 and 19' one after the other makes it possible to reduce the thermal energy of the refrigerant fluid entering the first expansion means 7. The liquid refrigerant fluid leaving the two-fluid heat exchanger 5 is cooled by the gaseous low-pressure refrigerant fluid leaving the evaporator 9 and the cooler 15. The thermal energy difference between the ends of the two heat exchangers is significantly increased, allowing an increase in the cooling power available at the evaporator 9 and the cooler 15, which in turn increases the coefficient of performance (COP).

Furthermore, the addition of thermal energy to the low-pressure refrigerant fluid at the first internal heat exchanger 19 and the second internal heat exchanger 19' makes it possible to limit the proportion of refrigerant fluid in the liquid phase before it enters the compressor 3, in particular when the air-conditioning circuit 1 comprises a desiccant bottle 14 located downstream of the two-fluid heat exchanger 5.

In the second circuit B for the heat transfer fluid, the heat transfer fluid obtains thermal energy from the refrigerant fluid at the two-fluid heat exchanger 5.

As shown in the example of fig. 9a, a portion of the heat transfer fluid circulates in the first flow tube 50 and passes through the internal radiator 54. However, the heat transfer fluid does not lose thermal energy because the baffle 310 closes and blocks the internal airflow 100 so that it does not pass through the internal heat sink 54.

Another portion of the heat transfer fluid circulates in the second flow tube 60 and passes through the second external radiator 64. The heat transfer fluid loses enthalpy at the second external heat sink 64 by releasing into the external air flow 200. The fourth shutoff valve 63 is opened to allow the heat transfer fluid to pass therethrough.

An alternative (not shown) for preventing the heat transfer fluid from exchanging with the internal air flow 100 at the internal radiator 54 is to equip the first through-flow duct 50 with a fifth shut-off valve 53 as shown in fig. 6 and to close this valve to prevent the heat transfer fluid from circulating in said first through-flow duct 50.

6. Sixth cooling mode:

fig. 9b shows a sixth cooling mode. This sixth cooling mode is the same as the fifth cooling mode of fig. 9a, except that upon exiting the two-fluid heat exchanger 5, the refrigerant fluid passes through the tap branch 80 and the first external radiator 84. To this end, the means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger 5 redirects the refrigerant fluid directly towards the first external heat sink 84 and not towards the first internal heat exchanger 19. For this purpose, in the example shown in fig. 9b, the first shut-off valve 82a of the device is closed, while the second shut-off valve 82b of the device is open.

In the first external heat sink 84, the refrigerant fluid releases thermal energy to the external air flow 200. This allows more heat to be removed than can be removed by the third heat sink 64 alone. This is particularly beneficial when a large amount of thermal energy is absorbed at the cooler 15 and it will not be sufficient to simply remove the thermal energy using the second radiator 64, for example during rapid discharge or charging of the battery of an electric or hybrid vehicle.

7. The first dehumidification mode:

fig. 10a shows a first dehumidification mode, in which, in a first circuit for a refrigerant fluid, the refrigerant fluid circulates in the following order:

a compressor 3, in which the refrigerant fluid is converted to a high pressure,

a two-fluid heat exchanger 5, in which the refrigerant fluid releases thermal energy to the heat transfer fluid of the second circuit B for heat transfer fluid,

a first internal heat exchanger 19 for the heat exchange,

a second internal heat exchanger 19',

a first expansion device 7, in which the refrigerant fluid undergoes a pressure drop and transforms to a low pressure,

an evaporator 9, in which the refrigerant fluid absorbs thermal energy from the internal air flow 100, cooling the internal air flow 100,

a second expansion device 11 through which expansion device 11 the refrigerant fluid passes without a pressure drop,

an evaporator/condenser 13, in which the refrigerant fluid absorbs thermal energy from the external air flow 200, an

A first internal heat exchanger 19 and then back to the compressor 3.

In the second circuit B for the heat transfer fluid, the heat transfer fluid circulates in the internal radiator 54 and releases thermal energy to the internal air flow 100.

The refrigerant fluid entering the compressor 3 is in the vapor phase. The refrigerant fluid undergoes compression as it passes through the compressor 3. The refrigerant fluid is then said to be at a high pressure.

The high pressure refrigerant fluid passes through the two-fluid heat exchanger 5 and experiences a drop in thermal energy due to its transition to the liquid phase and due to the transfer of enthalpy to the heat transfer fluid of the second circuit B for the heat transfer fluid. The high pressure refrigerant fluid loses heat energy while maintaining a constant pressure.

The high pressure refrigerant fluid then enters the first internal heat exchanger 19 where it loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid from the evaporator/condenser 13.

The high pressure refrigerant fluid then enters the second internal heat exchanger 19 ', where it does not lose thermal energy, since there is no circulation of the low pressure refrigerant fluid in said second internal heat exchanger 19'.

As shown in fig. 10a, on leaving the second internal heat exchanger 19', the refrigerant fluid does not circulate in the second bypass line 40, since the third expansion device 17 is closed.

The high pressure refrigerant fluid enters the first expansion device 7. The high pressure refrigerant fluid undergoes an isenthalpic pressure drop and changes state to a two-phase mixture. The refrigerant fluid is now said to be at a low pressure.

The refrigerant fluid then passes through the evaporator 9, which absorbs thermal energy in the evaporator 9 while cooling the internal air flow 100.

On leaving the evaporator 9, the refrigerant fluid is redirected towards the evaporator/condenser 13. For this purpose, the first shut-off valve 33 of the first bypass is closed. Before reaching the evaporator/condenser 13, the refrigerant fluid enters the first expansion device 11, and the refrigerant fluid passes through the first expansion device 11 without a pressure drop.

The low pressure refrigerant fluid then passes through the evaporator/condenser 13 where it absorbs heat energy from the outside air stream 200. The refrigerant fluid is thus converted back to the gaseous state.

The low pressure refrigerant fluid then enters the first interior heat exchanger 19 where it again obtains thermal energy from the high pressure refrigerant fluid passing through the first interior heat exchanger 19. The low pressure refrigerant fluid then returns to the compressor 3.

In this first dehumidification mode, only the first internal heat exchanger 19 is active. Since the thermal energy of the low pressure refrigerant fluid entering the compressor 3 is higher, the thermal energy of the high pressure refrigerant fluid leaving the compressor 3 will also be higher than the thermal energy of the refrigerant fluid when there is no internal heat exchanger.

Furthermore, the addition of thermal energy to the low-pressure refrigerant fluid at the first internal heat exchanger 19 makes it possible to limit the proportion of refrigerant fluid in the liquid phase before it enters the compressor 3, in particular when the air-conditioning circuit 1 comprises a desiccant bottle 14 located downstream of the two-fluid heat exchanger 5. The effectiveness of the first internal heat exchanger 19 is limited because its length is between 50 and 120 mm. Such dimensions make it possible to limit the heat exchange between the high pressure refrigerant fluid and the low pressure refrigerant fluid, so that the thermal energy exchanged makes it possible to limit the proportion of refrigerant fluid in the liquid phase before it enters the compressor 3, without compromising the efficiency of the heat pump mode. In particular, the purpose of this heat pump mode is to release as much thermal energy as possible into the internal air flow 100 in order to heat it at the evaporator 9. In the first dehumidification mode, the thermal energy comes from the external air flow 200 through the evaporator/condenser 13.

In the second circuit B for the heat transfer fluid, the heat transfer fluid obtains thermal energy from the refrigerant fluid at the two-fluid heat exchanger 5.

As shown in fig. 10a, the heat transfer fluid circulates in the first flow tube 50 and passes through the internal radiator 54. The heat transfer fluid loses heat energy by heating the internal airflow 100. For this purpose, the flap 310 is opened and/or the fifth shut-off valve 53 is opened. The fourth shut-off valve 63 itself is closed to prevent the heat transfer fluid from flowing into the second flow tube 60.

This first dehumidification mode facilitates dehumidification of the internal air flow 100 with cooling at the evaporator 9, which allows moisture to condense and then dehumidify by heating the internal air flow 100 at the internal heat sink 54.

Furthermore, the electrical heating element 55 may be operated to provide an additional supply of thermal energy to the heat transfer fluid to heat the internal air flow 100.

8. The second dehumidification mode:

fig. 10b shows a second dehumidification mode. This second dehumidification mode is identical to the first dehumidification mode of fig. 10a, except that on leaving the two-fluid heat exchanger 5, the refrigerant fluid passes through the bypass branch 80 and the first external radiator 84. To this end, the means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger 5 redirects the refrigerant fluid directly towards the first external heat sink 84 and not towards the first internal heat exchanger 19. For this purpose, in the example shown in fig. 10b, the first shut-off valve 82a of the device is closed, while the second shut-off valve 82b of the device is open.

In the first external heat sink 84, the refrigerant fluid releases thermal energy to the external air flow 200. This allows more heat to be removed than can be removed by internal heat sink 54 alone. This is particularly beneficial when a large amount of thermal energy is absorbed at the evaporator 9 and evaporator/condenser 13 and it is not sufficient to remove the thermal energy using the internal heat sink 54.

9. The third dehumidification mode:

fig. 10c shows a third dehumidification mode. This third dehumidification mode is identical to the first dehumidification mode of fig. 10a, except that on leaving the two-fluid heat exchanger 5, a first portion of the refrigerant fluid passes through the tapping branch 80 and the first external radiator 84, and a second portion of the refrigerant fluid passes directly to the first internal heat exchanger 19. To this end, the means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger 5 redirects the refrigerant fluid towards the first internal heat exchanger 19 and the first external heat sink 84. For this purpose, in the example shown in fig. 10c, the first shut-off valve 82a of the device is open and the second shut-off valve 82b of the device is open.

In the first external heat sink 84, the refrigerant fluid releases thermal energy to the external air flow 200. This allows more heat to be removed than can be removed by internal heat sink 54 alone. This is particularly beneficial when a large amount of thermal energy is absorbed at the evaporator 9 and evaporator/condenser 13 and it is not sufficient to remove the thermal energy using the internal heat sink 54.

10. The fourth dehumidification mode:

fig. 11a shows a second dehumidification mode, in which, in the first circuit of refrigerant fluids, the refrigerant fluids circulate in the following order:

a compressor 3, in which the refrigerant fluid is converted to a high pressure,

a two-fluid heat exchanger 5, in which the refrigerant fluid releases thermal energy to the heat transfer fluid of the second circuit B for heat transfer fluid,

a first internal heat exchanger 19 for the heat exchange,

a second internal heat exchanger 19',

a first portion of the refrigerant fluid enters the second bypass line 40, enters the third expansion device 17, undergoes a pressure drop therein and is transformed to a low pressure, which is then circulated in the cooler 15,

a second portion of the refrigerant fluid enters the first expansion device 7, where it undergoes a pressure drop and changes to a low pressure, enters the evaporator 9, where it obtains thermal energy from the internal air stream 100, cools the internal air stream, enters the second expansion device 11, through which the refrigerant fluid passes without a pressure drop, enters the evaporator/condenser 13, where the refrigerant fluid obtains thermal energy from the external air stream 200.

The two portions of refrigerant fluid join together upstream of the first internal heat exchanger 19. In the example of fig. 11a, the refrigerant fluid leaving the cooler 15 passes through the second bypass pipe 30 and enters the second internal heat exchanger 19'.

The refrigerant fluid then enters the first internal heat exchanger 19 before returning to the compressor 3.

Regardless of the connection embodiment of the second bypass pipe 40 shown in fig. 1 to 4, the two portions of refrigerant fluid are joined together upstream of the first internal heat exchanger 19.

In the second circuit B for the heat transfer fluid, the heat transfer fluid circulates in the internal radiator 54 and releases thermal energy to the internal air flow 100.

The refrigerant fluid entering the compressor 3 is in the vapor phase. The refrigerant fluid undergoes compression as it passes through the compressor 3. The refrigerant fluid is then said to be at a high pressure.

The high pressure refrigerant fluid passes through the two-fluid heat exchanger 5 and experiences a drop in thermal energy due to its transition to the liquid phase and due to the transfer of enthalpy to the heat transfer fluid of the second circuit B for the heat transfer fluid. The high pressure refrigerant fluid loses heat energy while maintaining a constant pressure.

The high pressure refrigerant fluid then enters the first internal heat exchanger 19 where it loses heat energy. This heat energy is transferred to the low pressure refrigerant fluid from the evaporator/condenser 13.

The high pressure refrigerant fluid then enters the second internal heat exchanger 19 ', where it does not lose thermal energy, since there is no circulation of the low pressure refrigerant fluid in said second internal heat exchanger 19'.

As shown in fig. 11a, on leaving the second internal heat exchanger 19', the refrigerant fluid circulates in the second bypass pipe 40 and flows towards the evaporator 9.

A first portion of the high pressure refrigerant fluid enters the third expansion device 17. The high pressure refrigerant fluid undergoes an isenthalpic pressure drop and changes state to a two-phase mixture. The refrigerant fluid is now said to be at a low pressure.

The low pressure refrigerant fluid then enters cooler 15, which picks up thermal energy at cooler 15. The refrigerant fluid is converted back to the gaseous state. Upon exiting the cooler 15, the refrigerant fluid reaches the first bypass 30. In the example shown in fig. 11a, the refrigerant fluid reaches the first bypass pipe 30 upstream of the first shut-off valve 33 and the second internal heat exchanger 19'. In order to prevent refrigerant fluid from entering the evaporator/condenser 13, the second expansion device 11 or the first shut-off valve 33 is closed according to an embodiment of the second bypass line 40.

The low pressure refrigerant fluid then enters the second interior heat exchanger 19 'where it picks up heat energy from the high pressure refrigerant fluid passing through the second interior heat exchanger 19'.

A second portion of the high pressure refrigerant fluid enters the first expansion device 7. The high pressure refrigerant fluid undergoes an isenthalpic pressure drop and changes state to a two-phase mixture. The refrigerant fluid is now said to be at a low pressure.

The refrigerant fluid then passes through the evaporator 9 where it absorbs thermal energy while cooling the internal air flow 100.

On leaving the evaporator 9, the refrigerant fluid is redirected towards the evaporator/condenser 13. For this purpose, the first shut-off valve 33 of the first bypass is closed. Before reaching the evaporator/condenser 13, the refrigerant fluid enters the first expansion device 11, and the refrigerant fluid passes through the first expansion device 11 without a pressure drop.

The low pressure refrigerant fluid then passes through the evaporator/condenser 13 where it absorbs heat energy from the outside air stream 200. The refrigerant fluid is thus converted back to the gaseous state.

The two portions of low pressure refrigerant fluid are joined together upstream of the first internal heat exchanger 19. The refrigerant fluid then enters the first interior heat exchanger 19 where it again obtains thermal energy from the high pressure refrigerant fluid passing through the first interior heat exchanger 19. The low pressure refrigerant fluid then returns to the compressor 3.

In the fourth dehumidification mode, shown in fig. 11a, the two internal heat exchangers 19 and 19' are active both on the refrigerant fluid coming from the evaporator 9 and on the refrigerant fluid passing through the second bypass line 40, and their effects are combined. The use of the internal heat exchangers 19 and 19' one after the other makes it possible to reduce the thermal energy of the refrigerant fluid entering the first expansion means 7. The liquid refrigerant fluid leaving the two-fluid heat exchanger 5 is cooled by the gaseous low-pressure refrigerant fluid leaving the evaporator 9 and the cooler 15. The thermal energy difference between the ends of the two heat exchangers is significantly increased, allowing an increase in the cooling power available at the evaporator 9 and the cooler 15, which in turn increases the coefficient of performance (COP).

Furthermore, the addition of thermal energy to the low-pressure refrigerant fluid at the first internal heat exchanger 19 and the second internal heat exchanger 19' makes it possible to limit the proportion of refrigerant fluid in the liquid phase before it enters the compressor 3, in particular when the air-conditioning circuit 1 comprises a desiccant bottle 14 located downstream of the two-fluid heat exchanger 5.

However, the second internal heat exchanger 19 'may not be effective if a second bypass pipe 40 is connected downstream of said second internal heat exchanger 19' as in the embodiment of fig. 3 and 4.

In the second circuit B for the heat transfer fluid, the heat transfer fluid obtains thermal energy from the refrigerant fluid at the two-fluid heat exchanger 5.

As shown in fig. 11a, the heat transfer fluid circulates in the first flow tube 50 and passes through the internal radiator 54. The heat transfer fluid loses heat energy by heating the internal airflow 100. For this purpose, the flap 310 is opened and/or the fifth shut-off valve 53 is opened. The fourth shut-off valve 63 itself is closed to prevent the heat transfer fluid from flowing into the second flow tube 60.

This fourth dehumidification mode facilitates dehumidification of the internal air flow 100 with cooling at the evaporator 9, which allows moisture to condense and then dehumidify by heating the internal air flow 100 at the internal heat sink 54. Thermal energy is also recovered at the cooler 15 to heat the internal air flow 100 using the internal heat sink 54.

Furthermore, the electrical heating element 55 may be operated to provide an additional supply of thermal energy to the heat transfer fluid to heat the internal air flow 100.

11. A fifth dehumidification mode:

fig. 11b shows a fifth dehumidification mode. This fifth dehumidification mode is identical to the fourth dehumidification mode of fig. 11a, except that on leaving the two-fluid heat exchanger 5, the refrigerant fluid passes through the tap branch 80 and the first external radiator 84. To this end, the means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger 5 redirects the refrigerant fluid directly towards the first external heat sink 84 and not towards the first internal heat exchanger 19. For this purpose, in the example shown in fig. 11b, the first shut-off valve 82a of the device is closed, while the second shut-off valve 82b of the device is open.

In the first external heat sink 84, the refrigerant fluid releases thermal energy to the external air flow 200. This allows more heat to be removed than can be removed by internal heat sink 54 alone. This is particularly beneficial when a large amount of thermal energy is absorbed at the evaporator 9, evaporator/condenser 13 and cooler 15 and it is not sufficient to remove the thermal energy using the internal heat sink 54.

12. Sixth dehumidification mode:

fig. 11c shows a sixth dehumidification mode. This sixth dehumidification mode is identical to the fourth dehumidification mode of fig. 11a, except that on leaving the two-fluid heat exchanger 5, a first portion of the refrigerant fluid passes through the tapping branch 80 and the first external radiator 84, and a second portion of the refrigerant fluid passes directly to the first internal heat exchanger 19. To this end, the means for redirecting the refrigerant fluid leaving the two-fluid heat exchanger 5 redirects the refrigerant fluid towards the first internal heat exchanger 19 and the first external heat sink 84. For this purpose, in the example shown in fig. 10b, the first shut-off valve 82a of the device is open and the second shut-off valve 82b of the device is open.

In the first external heat sink 84, the refrigerant fluid releases thermal energy to the external air flow 200. This allows more heat to be removed than can be removed by internal heat sink 54 alone. This is particularly beneficial when a large amount of thermal energy is absorbed at the evaporator 9, evaporator/condenser 13 and cooler 15 and it is not sufficient to remove the thermal energy using the internal heat sink 54.

Other modes of operation, such as a heat pump mode, and modes for de-icing or recovering heat from the cooler 15 are also contemplated for this architecture of the thermal management device.

It can therefore be clearly seen that the thermal management device is able to dissipate more thermal energy due to its architecture, in particular due to the presence of the shunt branch 80 and the first external heat sink 84. This is particularly beneficial when the cooler 15 requires a large amount of cooling power, for example during rapid discharge or charging of the battery of an electric or hybrid vehicle.