FR3099554A1 - Thermal management device comprising an attached magnetocaloric device - Google Patents

Abstract

The present invention relates to a thermal management device (1) for a motor vehicle comprising a thermal management circuit internal to the motor vehicle, comprising a main loop (A) in which a refrigerant fluid is intended to circulate, said main loop (A) comprising, in the direction of circulation of the refrigerant fluid, a compressor (3), a first heat exchanger (5), a first expansion device (7) and a second heat exchanger (11), said thermal management device (1) comprising a magnetocaloric system attached to the motor vehicle, said magnetocaloric system comprising: - a magnetocaloric branch (M) comprising a third heat exchanger (53), - a magnetocaloric device (50), - a first bypass pipe (55) including one end comprises a first connection member (55a), - a second branch pipe (56) one end of which has a second connection member (56a), the circuit d e thermal management further comprising: - a fourth heat exchanger (54) configured to exchange heat energy with a fluid of said thermal management circuit, - a third bypass pipe (57), one end of which comprises a third control member connection (55a) configured to connect to the first connection member (55a), and - a fourth branch pipe (58), one end of which includes a fourth connection member (58a) configured to connect to the second connection member (56a ). Figure for the abstract: Fig. 3

Description

Thermal management device comprising an attached magnetocaloric device

The present invention relates to a thermal management device for a motor vehicle. This thermal management device itself comprising a magnetocaloric device.

More specifically, the invention relates to a thermal management device of the air conditioning, heat pump or reversible air conditioning type in order to regulate the temperature of an internal air flow intended for the passenger compartment and/or in order to regulate internal elements to the vehicle such as for example batteries for an electric or hybrid vehicle.

As a general rule, heat exchangers for thermal management devices are sized to exchange enough heat to meet the specifications requested by manufacturers under the most extreme external conditions in terms of thermal power to be evacuated and ambient conditions. These heat exchangers are therefore generally oversized in most real driving conditions. In the extreme conditions for which they are designed, they are a source of nuisance and overconsumption. Indeed, to exchange a lot of heat at the front face, for example during rapid charging of a battery which requires a lot of thermal power to be evacuated, the compressor of the thermal management device as well as the fan arranged on the front face produce a lot of noise and consume a lot of energy. Moreover, for high powers, the ratio between the thermal power of a heat exchanger and its mass decreases. Larger and heavier exchangers are therefore needed to achieve the thermal power required.
In addition, additional cooling power may be requested from time to time, for example when an electric or hybrid motor vehicle is being fast charged. During this fast charge, the batteries tend to heat up excessively and it is therefore necessary to cool them more than normal.

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 device in which the oversizing of the heat exchangers is limited.

The present invention therefore relates to a thermal management device for a motor vehicle comprising a thermal management circuit internal to the motor vehicle, comprising a main loop in which a coolant is intended to circulate, said main loop comprising, in the direction of circulation of the coolant , a compressor, a first heat exchanger, a first expansion device and a second heat exchanger,
said thermal management device comprising a magnetocaloric system attached to the motor vehicle in which a heat transfer fluid is intended to circulate, said magnetocaloric system comprising:
- a magnetocaloric branch comprising a third heat exchanger,
- a magnetocaloric device,
- a first branch line, a first end of which is connected downstream of the magnetocaloric device and a second end of which comprises a first connection member, and
- a second branch line, a first end of which is connected upstream of the magnetocaloric device and a second end of which comprises a second connection member,
the magnetocaloric device being arranged jointly on the magnetocaloric branch and the first and second branch lines,
the thermal management circuit further comprising:
- a fourth heat exchanger configured to exchange heat energy with a fluid of said thermal management circuit,
- a third branch line, a first end of which is connected to a coolant inlet of the fourth heat exchanger and a second end of which includes a third connection member configured to connect to the first connection member, and
- A fourth branch pipe, a first end of which is connected to a coolant outlet of the fourth heat exchanger and a second end of which comprises a fourth connection member configured to connect to the second connection member.

According to one aspect of the invention, the magnetocaloric system attached to the motor vehicle is arranged within a thermal management module attached to the exterior of said vehicle, said thermal management module being electrically connected to said motor vehicle so as to supply electricity the magnetocaloric system.

According to one aspect of the invention, the thermal management module attached to the outside of the motor vehicle is mobile so as to supply electricity to the magnetocaloric system when said vehicle is in motion.

According to another aspect of the invention, the third and fourth branch pipes each comprise a flexible portion, said flexible portions comprising respectively the third and fourth connection members.

According to another aspect of the invention, the fourth heat exchanger is a two-fluid heat exchanger connected on the one hand to the third and fourth branch pipes and on the other hand to a first branch branch of the thermal management circuit, said first bypass branch being arranged upstream of one of the heat exchangers of the thermal management circuit.

According to another aspect of the invention:
- the main loop comprises a second bypass branch arranged in parallel with the first expansion device and the second heat exchanger, said second bypass branch comprising a second expansion device and a fifth heat exchanger arranged downstream of the second expansion device , and,
- the thermal management circuit comprises a secondary loop inside which a heat transfer fluid is intended to circulate and comprising a pump and a sixth heat exchanger,
the fifth heat exchanger being arranged jointly on the second bypass branch and the secondary loop so as to allow heat energy exchanges between the refrigerant of the main loop and the heat transfer fluid of the secondary loop.

According to another aspect of the invention, the first bypass branch comprises a fluid inlet point arranged on the secondary loop upstream of the fifth heat exchanger and a fluid outlet point arranged downstream of the fifth heat exchanger.

According to another aspect of the invention, the first bypass branch comprises a fluid inlet point and a fluid outlet point both arranged downstream or upstream of the fifth heat exchanger.

According to another aspect of the invention, the secondary loop comprises a third bypass branch comprising a seventh heat exchanger, said third bypass branch comprising a fluid entry point arranged on the secondary loop downstream of the pump and a fluid outlet point arranged upstream of the sixth heat exchanger.

According to another aspect of the invention, the thermal management device is a reversible air conditioning device and in that the first heat exchanger is a water condenser arranged jointly on the main loop and on the third bypass branch, the first heat exchanger being disposed upstream of the seventh heat exchanger.

The present invention also relates to a thermal management module comprising a magnetocaloric system in which a heat transfer fluid is intended to circulate, said magnetocaloric system comprising:
- a magnetocaloric branch comprising a third heat exchanger,
- a magnetocaloric device,
- a first branch line, a first end of which is connected downstream of the magnetocaloric device and a second end of which comprises a first connection member, and
- a second branch line, a first end of which is connected upstream of the magnetocaloric device and a second end of which comprises a second connection member,
the magnetocaloric device being arranged jointly on the magnetocaloric branch and the first and second branch lines.

Other characteristics and advantages of the present invention will appear more clearly on reading the following description, provided by way of illustration and not limitation, and the appended drawings in which:

FIG. 1 shows a schematic representation of a thermal management device according to a first embodiment,

FIG. 2 shows a schematic representation of a thermal management device according to a second embodiment,

FIG. 3 shows a schematic representation of a thermal management device according to a third embodiment,

FIG. 4 shows a schematic representation of a thermal management device according to a fourth embodiment,

FIG. 5 shows a schematic representation of a thermal management device according to a fifth embodiment,

FIG. 6 shows shows a schematic representation of a thermal management device according to a sixth embodiment,

FIG. 7 shows shows a schematic representation of a thermal management device according to a seventh embodiment,

FIG. 8 shows shows a schematic representation of a thermal management device according to an eighth embodiment.

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

The following achievements are examples. Although the description refers to one or more embodiments, this does not necessarily mean that each reference is to the same embodiment, or that the features apply only to a single embodiment. Single features of different embodiments may 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 else 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 close, but not identical. This indexing does not imply a priority of one element, parameter or criterion over another and it is easy to interchange such denominations without departing from the scope of the present description. Nor does this indexing imply an order in time, for example, to assess such and such a criterion.

In the present description, “placed upstream” means that one element is placed before another with respect to the direction of circulation of a fluid. Conversely, “placed downstream” means that one element is placed after another in relation to the direction of fluid circulation.

In order to facilitate understanding, in the various figures, the pipes through which a refrigerant fluid passes are shown in solid lines and those through which another heat transfer fluid passes in dotted lines.

Figures 1 to 4 show a schematic representation of a thermal management device 1 for a motor vehicle according to a simple embodiment. The thermal management device 1 comprises a thermal management circuit comprising a main loop A in which a refrigerant fluid is intended to circulate. This main loop A comprises, in the direction of circulation of the refrigerant fluid, a compressor 3, a first heat exchanger 5, a first expansion device 7 and a second heat exchanger 11.
The main loop A can also include a phase separation device 60 arranged upstream of the compressor 3.

This thermal management device 1 can for example be an air conditioning circuit as illustrated in FIGS. 1 and 2. In this case, the first heat exchanger 5 is a condenser, for example placed on the front face of the motor vehicle. The first heat exchanger 5 is thus intended to be crossed by an external air flow 100.
The second heat exchanger 11 is itself an evaporator, for example placed within a heating, ventilation and air conditioning device (also called HVAC for the acronym for Heating, Ventilation and Air Conditioning). The second heat exchanger 11 is thus intended to be traversed by an internal air flow 200 going in the direction of the passenger compartment of the motor vehicle.

The thermal management device 1 may on the contrary be a heat pump as illustrated in FIGS. 3 and 4. In this case, the first heat exchanger 5 is still a condenser but for example disposed within the heating, ventilation and air conditioner. The first heat exchanger is then intended to be traversed by the internal air flow 200 going in the direction of the passenger compartment of the motor vehicle.
The second heat exchanger 11 is for its part still an evaporator but for example arranged on the front face of the motor vehicle. The second heat exchanger 11 is then intended to be crossed by an external air flow 100.

By condenser and evaporator is meant here a heat exchanger defined by its function. A condenser has the function of heating the element with which it exchanges heat energy and an evaporator has the function of cooling the element with which it exchanges heat energy.

The thermal management device 1 further comprises a magnetocaloric system attached to the motor vehicle in which a heat transfer fluid is intended to circulate. This magnetocaloric system comprises a magnetocaloric device 50 and a third heat exchanger 53.
The magnetocaloric system more particularly comprises a magnetocaloric branch M comprising the third heat exchanger 53. The magnetocaloric system also comprises:
- a first branch line 55, a first end of which is connected downstream of the magnetocaloric device 50 and a second end of which comprises a first connection member 55a, and
- A second branch line 56, a first end of which is connected upstream of the magnetocaloric device 50 and a second end of which comprises a second connection member 56a.
The magnetocaloric device 50 is in particular arranged jointly on the magnetocaloric branch M and on the first 55 and second 56 branch pipes.

The connection members 55a, 56a, 57a and 58a are fluidic connection members allowing the circulation of a heat transfer fluid. These connection members 55a, 56a, 57a and 58a can for example be of the quick coupling type.

By magnetocaloric system attached to the motor vehicle, it is meant here that the magnetocaloric system is arranged within a thermal management thermal management module X.
This thermal management module X can for example be a thermal management module external to the motor vehicle attached to the latter. For example, this thermal management module X can be hung on the roof of the motor vehicle, on a hitch hooked to the rear of the motor vehicle or even on a dedicated trailer hooked to said motor vehicle.
It is also possible to imagine that the thermal management module X is arranged for example within a charging terminal for an electric or hybrid vehicle. The magnetocaloric system will then be used during rapid recharging of the motor vehicle to increase the cooling power of the batteries. The connection members 55a, 56a, 57a and 58a can in this case be placed at the level of the hatch and the charging connector of the motor vehicle to allow simultaneous connection both electrically and fluidically when connecting to the terminal.
Another possibility is also that the thermal management module X can be inserted into a dedicated housing within the motor vehicle, for example in the trunk, when its presence is necessary.

The thermal management module X can in particular be electrically connected to said motor vehicle so as to supply electricity to the magnetocaloric system. This electrical connection can in particular be made by means of a male/female connector (not shown) arranged close to the connection members 55a, 56a, 57a, 58a. This thermal management module X may also include a fan (not shown) in order to generate an air flow at the level of the third heat exchanger 53.

The thermal management circuit, arranged within the motor vehicle itself, comprises a fourth heat exchanger 54 configured to exchange heat energy with a fluid of said thermal management circuit. By fluid of the thermal management circuit, is meant here a fluid playing a role in the thermal management of the motor vehicle. This may in particular be an internal air flow 100, an external air flow 200, the refrigerant from the main loop A or even a heat transfer fluid from a secondary loop D (visible in FIGS. 5 to 8).
The thermal management circuit further comprises:
- a third branch pipe 57, a first end of which is connected to a coolant inlet of the fourth heat exchanger 54 and a second end of which includes a third connection member 55a configured to connect to the first connection member 55a, and
- A fourth branch line 58, a first end of which is connected to a coolant outlet of the fourth heat exchanger 54 and a second end of which includes a fourth connection member 58a configured to connect to the second connection member 56a.

The fact that the magnetocaloric system is attached to the motor vehicle allows it to be installed and used only when its use is necessary, in particular when the cooling requirements are greater, for example when the batteries of an electric vehicle or hybrids are fast charging. This may also be the case for rapidly warming up elements of the thermal management circuit.
In addition, the fact that the connection between the magnetocaloric system and the thermal management circuit is made via a fourth heat exchanger 54 on which the connections are made, makes it possible to limit the risks of entry of air in the thermal management circuit and therefore loss of efficiency.

The third 57a and the fourth 58a connection members are preferably arranged at the body of the motor vehicle in order to be able to make the connections with the first 55a and second 56a connection members. In order to compensate for any deformations in the event of impact and also to facilitate assembly, the third 57 and fourth 58 branch pipes each comprise a flexible portion 57', 58', as illustrated in FIG. 2. These flexible portions 57', 58' respectively comprise at one of their ends the third 57a and fourth 58a connection members. The other end of these flexible portions 57', 58' is for its part connected by means of a connection member 57b, 58b to another portion of the third 57 and fourth 58 branch pipes making the connection with the fourth heat exchanger. heat 54.

By magnetocaloric device 50 is meant here a device comprising a material capable of a magnetocaloric effect, that is to say which heats up when it is subjected to a magnetic field, for example by means of an electromagnetic coil , and which cools when this magnetic field is extinguished. A synchronous redirection of one or more fluids with its heating or cooling phases makes it possible to heat or cool an element.

Thus, when the magnetocaloric device 50 is subjected to a magnetic field, it heats up and transmits calorific energy to the heat transfer fluid intended for the magnetocaloric branch M. This heat transfer fluid then passes through the third heat exchanger 53 for example to dissipate this heat energy. When the magnetocaloric device 50 is no longer subject to this magnetic field, it cools and absorbs calorific energy from the fluid of the thermal management circuit in order to cool it. This cooled heat transfer fluid then passes through the first branch line 55 to join the fourth heat exchanger 54. The reverse is also possible, that is to say that the magnetocaloric device 50 cools the heat transfer fluid intended for the third heat exchanger 53 and heats the heat transfer fluid destined for the first branch pipe 55 and the fourth heat exchanger 54.

As described above, the magnetocaloric branch M as well as the first 55 and second 56 branch pipes are all three connected to the magnetocaloric device 50. The magnetocaloric branch M is in fluid communication with the first 55 and second 56 branch pipes via the device. magnetocaloric device 50. The first end of the second branch line 56 is thus connected to a first coolant inlet of the magnetocaloric device 50 which is connected to a first coolant fluid outlet of the magnetocaloric device 50 connected to the magnetocaloric branch M. A Conversely, the first end of the first bypass line 55 is connected to a second heat transfer fluid outlet of the magnetocaloric device 50 which is connected to a second heat transfer fluid inlet of the magnetocaloric device 50 connected to the magnetocaloric branch M.

This magnetocaloric system thus makes it possible to improve the efficiency of the thermal management circuit, in particular of the heat exchangers of the thermal management circuit, one of the fluids of which exchanges calorific energy directly or indirectly with the magnetocaloric device 50.

The magnetocaloric system may comprise a pump or else, as illustrated in FIGS. 1 to 4, the magnetocaloric device 50 may itself be configured to set the calorific fluid in motion in the magnetocaloric system.

According to a first embodiment illustrated in Figures 1 and 2, the fourth heat exchanger 54 is arranged in the air flow 100, 200 upstream or downstream of a heat exchanger of the thermal management circuit.

According to the example of FIG. 1 in which the thermal management device is an air conditioning circuit, the fourth heat exchanger 54 is arranged in the internal air flow 200 in parallel with the second heat exchanger 11. The redirection of the fluid The coolant is then set so that it passes through the fourth heat exchanger 54 after the magnetocaloric device 50 absorbs heat energy. The internal air flow 200 is thus cooled both by the second heat exchanger 11 and by the fourth heat exchanger 54. The efficiency of the second heat exchanger 11 is thus improved by the presence of the magnetocaloric system. The dimensioning of the second heat exchanger 11 can thus be reduced compared to what it would have been without the presence of the magnetocaloric system.

According to the example of FIG. 2 in which the thermal management device is a heat pump, the fourth heat exchanger 54 is arranged in the internal air flow 200 in parallel with the first heat exchanger 5. The redirection of the fluid The coolant is then set so that it passes through the fourth heat exchanger 54 after the magnetocaloric device 50 releases heat energy. The internal air flow 200 is thus heated both by the first heat exchanger 5 and by the fourth heat exchanger 54. The efficiency of the first heat exchanger 5 is thus improved by the presence of the magnetocaloric system. The dimensioning of the first heat exchanger 5 can thus be reduced compared to what it would have been without the presence of the magnetocaloric system.

According to a variant not shown, the fourth heat exchanger 54 can be arranged in the external air flow 100 upstream of the first 5 or second 11 heat exchanger. Depending on whether it is an air conditioning circuit or a heat pump, the magnetocaloric system will respectively cool or heat the external air flow 100 before the latter passes through the second 11 or first 5 heat exchanger. heat in order to improve their efficiency.

In order to limit the costs and also the size, the fourth heat exchanger 54 and the heat exchanger of the thermal management circuit intended to be crossed by an air flow 100, 200 can be grouped together in a single heat exchanger tri-fluid. By tri-fluid is meant here that the heat exchanger is crossed by the air flow 100, 200 but also that it comprises tubes in which circulates the fluid of the thermal management circuit, here the refrigerant of the loop main A, and the heat transfer fluid of the magnetocaloric system.

In a second embodiment illustrated in FIGS. 3 and 4, the fourth heat exchanger 54 is a two-fluid heat exchanger arranged jointly on a first bypass branch B of the thermal management circuit. This first bypass branch B is arranged upstream of one of the heat exchangers of the thermal management circuit, here the heat exchanger intended to be crossed by the internal air flow 200.

In the example of Figure 3, the thermal management device 1 is an air conditioning circuit like the example of Figure 1. In this example of Figure 3, the main loop A is identical to that of the example of Figure 1 and the first bypass branch B is directly connected to said main loop A. The first bypass branch B comprises a fluid inlet point 31 and a fluid outlet point 32 both arranged in upstream of the second heat exchanger 11. The fluid inlet point 31 is arranged upstream of the fluid outlet point 32, between the first expansion device 7 and said fluid outlet point 32. The fluid outlet point 32 is arranged between the fluid entry point 31 and the second heat exchanger 11.
In order to redirect at least part of the coolant flow alternately to the fourth heat exchanger 54, the first bypass branch B includes a redirection device 52, for example a three-way valve. This redirection device 52 is in particular arranged at the level of the fluid entry point 31.
Thus, at least a portion of the refrigerant fluid is cooled at the level of the fourth heat exchanger 54, when it is connected to the magnetocaloric system, which makes it possible to improve the efficiency of the second heat exchanger 11. The dimensioning of the second exchanger heat 11 can thus be reduced compared to what it would have been without the presence of the magnetocaloric system.

In the example of Figure 4, the thermal management device 1 is a heat pump like the example of Figure 2. In this example of Figure 4, the main loop A is identical to that of the example of FIG. 2 and the first bypass branch B is directly connected to said main loop A. The first bypass branch B comprises a fluid inlet point 31 and a fluid outlet point 32 both arranged in upstream of the first heat exchanger 5. The fluid inlet point 31 is arranged upstream of the fluid outlet point 32, between the compressor 3 and said fluid outlet point 32. The fluid outlet point 32 is as to him disposed between the fluid entry point 31 and the first heat exchanger 5.
In order to redirect at least part of the flow of refrigerant fluid to the fourth heat exchanger 54, the first bypass branch B includes a redirection device 52, for example a three-way valve. This redirection device 52 is in particular arranged at the level of the fluid entry point 31.
Thus, at least a portion of the refrigerant fluid is heated at the level of the fourth heat exchanger 54 via the magnetocaloric device 50 which makes it possible to improve the efficiency of the first heat exchanger 5, when said fourth heat exchanger 54 is connected to the magnetocaloric system. The dimensioning of the first heat exchanger 5 can thus be reduced compared to what it would have been without the presence of the magnetocaloric system.

According to a variant not shown, the first bypass branch B can be arranged upstream of one of the heat exchangers of the thermal management circuit intended to be crossed by the external air flow 100. Depending on whether it is a an air conditioning circuit or a heat pump, the magnetocaloric system will respectively cool or heat the refrigerant in order to improve the efficiency of the second 11 or first 5 heat exchanger.

As illustrated in FIGS. 5 and 6, the main loop A can also comprise a second bypass branch C arranged in parallel with the first expansion device 7 and the second heat exchanger 11. This second bypass branch C more precisely connects a point coolant inlet 33 and a coolant outlet point 34 both arranged on the main loop A. The coolant fluid inlet point 33 is in particular arranged upstream of the first expansion device 7, between the first heat exchanger heat exchanger 5 and said first expansion device 7. The refrigerant fluid outlet point 34 is disposed downstream of the second heat exchanger 11, between said second heat exchanger 11 and the compressor 3.
The second bypass branch C comprises a second expansion device 13 and a fifth heat exchanger 15 disposed downstream of the second expansion device 13.

In order to determine whether the refrigerant fluid passes through the second 11 and/or the fifth 15 heat exchanger, the first 7 and second 13 expansion devices may include a stop function, that is to say they are configured to be able to block the flow of refrigerant fluid.

Still according to FIGS. 5 and 6, the thermal management circuit further comprises a secondary loop D inside which a heat transfer fluid is intended to circulate. This secondary loop D comprises in particular a pump 17 and a sixth heat exchanger 19. This sixth heat exchanger 19 can for example be one or more plates intended for the thermal management of elements such as the batteries of an electric or hybrid vehicle. .
The fifth heat exchanger 15 is for its part arranged jointly on the second bypass branch C and the secondary loop D so as to allow the exchange of heat energy between the refrigerant fluid of the main loop A and the heat transfer fluid of the loop secondary d.

Like the embodiments illustrated in FIGS. 3 and 4, the fourth heat exchanger 54 is a two-fluid heat exchanger arranged jointly on the first bypass branch B of the thermal management circuit connected to the secondary loop D. The first bypass branch B is arranged upstream of one of the heat exchangers of the thermal management circuit, here the sixth heat exchanger 19. This positioning of the fourth heat exchanger 54, when it is connected to the magnetocaloric system, makes it possible to improve the efficiency of the sixth heat exchanger 19, for example when the cooling requirements are high, in particular during rapid charging of the batteries.

In order to redirect at least part of the heat transfer fluid flow towards the fourth heat exchanger 54, the first bypass branch B comprises a redirection device 52, for example a three-way valve.

According to the first variant illustrated in FIG. 5, the first bypass branch B comprises a fluid inlet point 31 arranged on the secondary loop D upstream of the fifth heat exchanger 15 and a fluid outlet point 32 arranged downstream of the fifth heat exchanger 15. This first variant allows the heat transfer fluid passing through the first bypass branch B to bypass the fifth heat exchanger 15.

According to the second variant illustrated in FIG. 6, the first bypass branch B comprises a fluid inlet point 31 and a fluid outlet point 32 both arranged downstream of the fifth heat exchanger 15. This second variant allows the heat transfer fluid passing through the first bypass branch B must first pass through the fifth heat exchanger 15.

As illustrated in FIG. 7, the secondary loop D may also include a third bypass branch E. This third bypass branch E connects more particularly an inlet point 35 and an outlet point 36 of the coolant fluid. The heat transfer fluid entry point 35 is in particular arranged upstream of the fifth heat exchanger 15, between the sixth 19 and the fifth 15 heat exchanger in the direction of circulation of the heat transfer fluid. The heat transfer fluid outlet point 36 is arranged upstream of the sixth heat exchanger 19, between the fifth 15 and the sixth 19 heat exchanger in the direction of circulation of the heat transfer fluid. The third bypass branch E comprises a seventh heat exchanger 21, for example arranged on the front face of the motor vehicle and intended to be crossed by the external air flow 100.
The heat transfer fluid entry point 35 is arranged on the secondary loop D downstream of the pump 17. This makes it possible, for example, to evacuate calorific energy from the sixth heat exchanger 19 via the seventh heat exchanger that the refrigerant is forced to pass through the fifth heat exchanger 15.

In order to redirect at least part of the heat transfer fluid flow towards the third bypass branch E and/or towards the fifth heat exchanger 15, the third bypass branch E comprises a redirection device 20, for example a three-way valve .

According to the example of Figure 7, the first bypass branch B may include a fluid inlet point 31 and a fluid outlet point 32 arranged on said third bypass branch E both downstream of the seventh heat exchanger 21. The magnetocaloric system can thus allow a better evacuation of the calorific energy of the refrigerant fluid circulating in the third bypass branch E, for example to improve the efficiency of the sixth heat exchanger 19.

The thermal management device 1 can also be a reversible air conditioning device as shown in FIG. 8. The first heat exchanger 5 is then a water condenser arranged jointly on the main loop A and on the third bypass branch E in order to allow heat energy to be exchanged between the refrigerant of the main loop A and the heat transfer fluid flowing in the third bypass branch E. On said third bypass branch E, the first heat exchanger 5 is in particular arranged upstream of the seventh heat exchanger 21.

The third bypass branch E may further comprise a fourth bypass branch F bypassing the first heat exchanger 5 in order, for example, to evacuate calorific energy from the sixth heat exchanger 19 via the seventh heat exchanger 21 without that the refrigerant fluid is not obliged to pass through the first heat exchanger 5. This fourth bypass branch F connects in particular a fluid inlet point 37 disposed upstream of the first heat exchanger 5 and an outlet point of the heat transfer fluid 38 disposed downstream of the first heat exchanger 5, between said first heat exchanger 5 and the seventh heat exchanger 21. This fourth bypass branch F may in particular comprise a device for redirecting the heat transfer fluid to control the flow of heat transfer fluid, for example a shut-off valve 28 or a three-way valve arranged at the level of the coolant fluid entry point 37.

The third bypass branch E can also comprise a fifth bypass branch G. This fifth bypass branch G comprises in particular an eighth heat exchanger 30, for example a radiator intended to be crossed by the internal air flow 200 and to heat it. . This fifth bypass branch G more precisely connects a heat transfer fluid entry point 39 and a heat transfer fluid exit point 40. The heat transfer fluid entry point 39 is arranged upstream of the seventh heat exchanger 21, between the first heat exchanger 5 and said seventh heat exchanger 21. The heat transfer fluid outlet point 40 is for its part disposed downstream of the seventh heat exchanger 21. This fifth bypass branch G may in particular comprise a fluid redirection device heat transfer fluid to control the flow of heat transfer fluid, for example a three-way valve 29 arranged at the level of the heat transfer fluid entry point 39.

Still according to the reversible air conditioning device 1 of FIG. 8, the main loop A can itself comprise a sixth bypass branch H. This sixth bypass branch H connects a refrigerant fluid inlet point 41 disposed downstream of the first heat exchanger 5 and a coolant fluid outlet point 42 disposed downstream of the coolant fluid inlet point 41, between said coolant fluid inlet point 41 and the first expansion device 7, more precisely upstream of the coolant fluid outlet point coolant inlet 33 of the second bypass branch C. This sixth bypass branch H comprises in particular a third expansion device 23 arranged upstream of a ninth heat exchanger 25. This ninth heat exchanger 25 can in particular be arranged on the front face of the motor vehicle and intended to be traversed by the external air flow 100 in order to absorb the calorific energy. The sixth bypass branch H may further include a non-return valve 26 disposed downstream of the ninth heat exchanger 25. In order to control the flow of refrigerant fluid, the third expansion device 23 may include a stop function and the main loop A include a shut-off valve 27 arranged between the entry point 41 and the exit point 42 of the refrigerant fluid from the sixth bypass branch H.

The first bypass branch B can itself be connected to the third bypass branch E, upstream of the first heat exchanger 5. The first bypass branch B can then comprise a fluid inlet point 31 and a fluid outlet 32 both arranged upstream of the first heat exchanger 5 on the third bypass branch E. the fourth heat exchanger 54 can thus, when it is connected to the magnetocaloric system, for example help to heat the refrigerant fluid to reheat the internal air flow 200 via the eighth heat exchanger 30 or to cool the refrigerant fluid in order to facilitate the dissipation of heat energy in the external air flow 100 via the seventh heat exchanger 21.

Thus, it is clearly seen that due to the presence of the magnetocaloric system, it is possible, depending on its positioning, to improve the efficiency of the heat exchangers within the thermal management device.

Claims (9)

Thermal management device (1) for a motor vehicle comprising a thermal management circuit internal to the motor vehicle, comprising a main loop (A) in which a refrigerant fluid is intended to circulate, said main loop (A) comprising, in the direction of circulation refrigerant fluid, a compressor (3), a first heat exchanger (5), a first expansion device (7) and a second heat exchanger (11),
characterized in that said thermal management device (1) comprises a magnetocaloric system attached to the motor vehicle in which a heat transfer fluid is intended to circulate, said magnetocaloric system comprising:
a magnetocaloric branch (M) including a third heat exchanger (53),
- a magnetocaloric device (50),
- a first branch line (55), a first end of which is connected downstream of the magnetocaloric device (50) and a second end of which includes a first connection member (55a), and
- a second branch pipe (56), a first end of which is connected upstream of the magnetocaloric device (50) and a second end of which comprises a second connection member (56a),
the magnetocaloric device (50) being arranged jointly on the magnetocaloric branch (M) and the first (55) and second (56) branch pipes,
the thermal management circuit further comprising:
- a fourth heat exchanger (54) configured to exchange heat energy with a fluid of said thermal management circuit,
- a third branch line (57) whose first end is connected to a coolant inlet of the fourth heat exchanger (54) and whose second end comprises a third connection member (55a) configured to connect to the first member connection (55a), and
- a fourth branch line (58) whose first end is connected to a coolant outlet of the fourth heat exchanger (54) and whose second end comprises a fourth connection member (58a) configured to connect to the second member connection (56a). Thermal management device (1) according to Claim 1, characterized in that the magnetocaloric system attached to the motor vehicle is arranged within a thermal management module (X), in particular a mobile thermal management module (X), attached outside of said vehicle, said thermal management module being electrically connected to said motor vehicle so as to supply electricity to the magnetocaloric system. Thermal management device (1) according to any one of the preceding claims, characterized in that the third (57) and fourth (58) branch pipes each comprise a flexible portion (57', 58'), the said flexible portions ( 57', 58') respectively comprising the third (57a) and fourth (58a) connection members. Thermal management device (1) according to Claim 1, characterized in that the fourth heat exchanger (54) is a two-fluid heat exchanger connected on the one hand to the third (57) and fourth (58) branch lines and on the other hand to a first bypass branch (B) of the thermal management circuit, said first bypass branch (B) being arranged upstream of one of the heat exchangers of the thermal management circuit. Thermal management device (1) according to any one of Claims 1 to 3, characterized in that:
- the main loop (A) comprises a second bypass branch (C) arranged in parallel with the first expansion device (7) and the second heat exchanger (11), said second bypass branch (C) comprising a second expansion (13) and a fifth heat exchanger (15) arranged downstream of the second expansion device (13), and that,
- the thermal management circuit comprises a secondary loop (D) inside which a heat transfer fluid is intended to circulate and comprising a pump (17) and a sixth heat exchanger (19),
the fifth heat exchanger (15) being arranged jointly on the second bypass branch (C) and the secondary loop (D) so as to allow heat energy exchanges between the refrigerant of the main loop (A) and the secondary loop heat transfer fluid (D). Thermal management device (1) according to Claim 5 in combination with Claim 4, characterized in that the first bypass branch (B) comprises a fluid entry point (31) arranged on the secondary loop (D) in upstream of the fifth heat exchanger (15) and a fluid outlet point (32) disposed downstream of the fifth heat exchanger (15). Thermal management device (1) according to Claim 5 in combination with Claim 4, characterized in that the first bypass branch (B) has a fluid entry point (31) and a fluid exit point (32 ) both arranged downstream or upstream of the fifth heat exchanger (15). Thermal management device (1) according to Claim 5, characterized in that the secondary loop (D) comprises a third bypass branch (E) comprising a seventh heat exchanger (21), the said third bypass branch (E) comprising a fluid inlet point (35) arranged on the secondary loop (D) downstream of the pump (17) and a fluid outlet point (36) arranged upstream of the sixth heat exchanger (19). Thermal management device (1) according to Claim 5, characterized in that the thermal management device (1) is a reversible air conditioning device and in that the first heat exchanger (5) is a water condenser arranged jointly on the main loop (A) and on the third bypass branch (E), the first heat exchanger (5) being arranged upstream of the seventh heat exchanger (21).