CN116829383A

CN116829383A - Thermal management device for electric or hybrid motor vehicle

Info

Publication number: CN116829383A
Application number: CN202180092056.2A
Authority: CN
Inventors: M·亚希亚; S·卡尔
Original assignee: Valeo Systemes Thermiques SAS
Current assignee: Valeo Systemes Thermiques SAS
Priority date: 2020-12-02
Filing date: 2021-11-18
Publication date: 2023-09-29
Also published as: FR3116764B1; FR3116764A1; WO2022117360A1; EP4255745A1

Abstract

A thermal management device (1) for an electric or hybrid motor vehicle, comprising a refrigerant circuit comprising: -a main loop (a) comprising a first heat exchanger (101), a first expansion device (5), a second heat exchanger (102), a second expansion device (7) and a third heat exchanger (103), -a first bypass branch (A1), -a second bypass branch (A2), -a third bypass branch (A3) comprising a fourth heat exchanger (104), -a first system for redirecting refrigerant to the second expansion device (7) or to the compressor (3) via the first bypass branch (A1), -a second system for redirecting refrigerant to the first expansion device (5) or to the second heat exchanger (102) via the second bypass branch (A2), -a third system for redirecting refrigerant to the second heat exchanger (102) and/or to the fourth heat exchanger (104) via the third bypass branch (A3).

Description

Thermal management device for electric or hybrid motor vehicle

The present invention relates to the field of electric or hybrid motor vehicles and more particularly to a device for thermal management of the battery and the power electronics and/or the electric machine of said electric vehicle.

Today's electric or hybrid motor vehicles increasingly include heat transfer fluid circuits for thermal management of the batteries and power electronics and/or motors of the electric vehicle. In order for these elements to be as efficient as possible, they need to be kept at an optimal operating temperature. Therefore, it is necessary to cool these elements during use to ensure that they do not excessively exceed the optimal operating temperature. Also, for example in cold weather, it may be desirable to heat the elements so that they reach the optimum operating temperature in the shortest possible time. Furthermore, these elements may have different optimal operating temperatures, which requires different thermal management of each of these elements.

Thus, it is known that the heat transfer fluid circuit comprises a complex architecture that allows thermal management of both the battery and the power electronics and/or the motor of the electric vehicle. In this case, the heat transfer fluid circuit typically includes a dedicated heat exchanger and a dedicated expansion device for each of these elements, as well as various circulation branches and bypass branches, in order to ensure satisfactory thermal management of these elements at different temperatures. However, these architectures are often complex and costly.

It is therefore an object of the present invention to at least partly overcome the drawbacks of the prior art and to propose a simpler, less costly thermal management device that is capable of operating in different modes of operation for thermal management of the battery and the power electronics and/or the motor of an electric vehicle.

The present invention therefore relates to a thermal management device for an electric or hybrid motor vehicle, said thermal management device comprising a refrigerant circuit inside which a refrigerant is intended to circulate, the refrigerant circuit comprising:

a main loop comprising a compressor, a first heat exchanger, a first expansion device, a second heat exchanger, a second expansion device and a third heat exchanger in the direction of circulation of the refrigerant,

a first bypass branch connecting a first connection point positioned upstream of the second expansion device, between the second heat exchanger and said second expansion device, and a second connection point positioned downstream of the third heat exchanger, between said third heat exchanger and the compressor,

a second bypass branch connecting a third connection point positioned on the main branch downstream of the compressor between said compressor and the first expansion device and a fourth connection point positioned on the main branch downstream of the first expansion device between said first expansion device and the second heat exchanger,

A third bypass branch connecting a fifth connection point positioned on the main branch downstream of the first expansion device, between said first expansion device and the second heat exchanger, and a sixth connection point positioned upstream of the compressor, said third bypass branch comprising a fourth heat exchanger,

a first system for redirecting the refrigerant arriving at the first connection point to the second expansion device or to the compressor via the first bypass branch,

a second system for redirecting the refrigerant arriving at the third connection point to the first expansion device or to the second heat exchanger via the second bypass branch,

-a third system for redirecting the refrigerant arriving at the fifth connection point to the second heat exchanger and/or to the fourth heat exchanger via a third bypass branch.

According to one aspect of the invention, the first expansion device is a bore tube.

According to another aspect of the invention, the first redirecting system includes a first shut-off valve positioned on the first bypass branch.

According to another aspect of the invention, the second expansion device comprises a shut-off valve function.

According to another aspect of the invention, the second redirecting system includes a second shut-off valve positioned on the second bypass branch.

According to another aspect of the invention, the third redirecting system includes a third shut-off valve positioned on the third bypass branch.

According to another aspect of the invention, a third shut-off valve is positioned on the third bypass branch upstream of the fourth heat exchanger.

According to another aspect of the invention, the third stop valve is a solenoid valve that can be controlled by pulse width modulation.

According to another aspect of the invention, the fifth junction of the third bypass branch is positioned on the main branch upstream of the fourth junction of the second bypass branch.

According to another aspect of the invention, a fourth shut-off valve is positioned on the main branch downstream of said fifth connection point, between the fifth connection point and the fourth connection point.

According to another aspect of the invention, the fourth shut-off valve is a solenoid valve that can be controlled by pulse width modulation.

According to another aspect of the invention:

the first heat exchanger is an internal condenser configured to be passed by an internal air flow,

the second heat exchanger is an evaporator-condenser configured to be passed by an external air stream,

the third heat exchanger is a cooler configured for thermal management of the battery,

The fourth heat exchanger is a cooler configured for thermally managing the power electronics and/or the electric machine of the motor vehicle.

According to another aspect of the invention, the thermal management device comprises a fourth bypass branch connecting a seventh connection point positioned downstream of the second heat exchanger and an eighth connection point positioned upstream of the compressor, said fourth bypass branch comprising a fifth heat exchanger and a third expansion device positioned upstream of said fifth heat exchanger.

According to another aspect of the invention, the third expansion device comprises a shut-off valve function.

According to another aspect of the invention, the fifth heat exchanger is an evaporator configured to be passed by an internal air stream.

According to another aspect of the invention, the third connection point of the second bypass branch is positioned on the main branch downstream of the first heat exchanger, between said first heat exchanger and the first expansion device.

According to another aspect of the invention, the third connection point of the second bypass branch is positioned on the main branch upstream of the first heat exchanger, between the compressor and said first heat exchanger.

Further features and advantages of the invention will become more apparent from reading the following description, provided by way of non-limiting illustration, and from the accompanying drawings, in which:

Figure 1 is a schematic depiction of a thermal management apparatus according to a first embodiment,

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

figure 3 is a schematic depiction of the thermal management device of figure 1 in a first heat pump mode,

figure 4 is a schematic depiction of the thermal management device of figure 1 in a second heat pump mode,

figure 5 is a schematic depiction of the thermal management device of figure 1 in a first dehumidification mode,

figure 6 is a schematic depiction of the thermal management device of figure 1 in a second dehumidification mode,

figure 7 is a schematic depiction of the thermal management device of figure 1 in a first cooling mode,

figure 8 is a schematic depiction of the thermal management device of figure 1 in a second cooling mode,

figure 9 is a schematic depiction of the thermal management device of figure 1 in a third cooling mode,

figure 10 is a schematic depiction of the thermal management device of figure 1 in a fourth cooling mode,

figure 11 is a schematic depiction of the thermal management device of figure 1 in a fifth cooling mode,

FIG. 12 is a schematic depiction of the thermal management device of FIG. 1 in a sixth cooling mode.

Like elements are denoted by like reference numerals throughout the various figures.

The following embodiments are examples. While the specification relates to one or more embodiments, this does not necessarily mean that each reference numeral relates to the same embodiment, or that the features apply to only one embodiment. Individual features of the different embodiments may also be combined and/or interchanged to provide other embodiments.

In this specification, certain elements or parameters may be assigned ordinal numbers such as, for example, a first element or a second element, and a first parameter and a second parameter, or a first criterion and a second criterion, etc. In this case, ordinal numbers are merely intended to distinguish and represent similar but not identical elements, or parameters, or criteria. Such ordinal numbers do not mean that one element, parameter, or criterion is prioritized over another element, parameter, or criterion, and such numbers may be readily interchanged without departing from the scope of the present description. Also, such ordinal numbers do not imply any temporal order, for example, in evaluating any given criteria.

In this specification, "placed upstream" is understood to mean that one element is placed before another element with respect to the circulation direction of the fluid. In contrast, "downstream" is understood to mean that one element is placed after another element with respect to the direction of circulation of the fluid.

Fig. 1 shows a schematic depiction of a thermal management device 1 for an electric or hybrid motor vehicle. The thermal management device 1 comprises a refrigerant circuit in which the refrigerant is intended to circulate. The refrigerant circuit comprises a main branch a, a first bypass branch A1, a second bypass branch A2 and a third bypass branch A3.

The main branch a, shown in bold in fig. 1, comprises, in the direction of circulation of the refrigerant, a compressor 3, a first heat exchanger 101, a first expansion device 5, a second heat exchanger 102, a second expansion device 7 and a third heat exchanger 103. The main branch a may also comprise a phase separation device 11, such as a reservoir, upstream of the compressor 3. More specifically, this reservoir 11 may be positioned between the third heat exchanger 103 and the compressor 3.

The first bypass branch A1 is connected to the main branch a such that the first bypass branch bypasses the second expansion device 7 and the third heat exchanger 103. Thus, the first bypass branch A1 connects the first connection point 41 and the second connection point 42. The first connection point 41 is positioned on the main branch a upstream of the second expansion device 7, between the second heat exchanger 102 and said second expansion device 7. The second connection point 42 is positioned on the main branch a downstream of the third heat exchanger 103, between said third heat exchanger 103 and the compressor 3. More specifically, the second connection point 42 is positioned upstream of the reservoir 11.

The thermal management device 1 further comprises a first system for redirecting the refrigerant arriving at the first connection point 41 in order to redirect the refrigerant coming from the second heat exchanger 102 to the second expansion device 7 or to the compressor 3 via the first bypass branch A1. This first redirecting system may in particular comprise a first shut-off valve 31 positioned on the first bypass branch A1. The second expansion device 7 may comprise a shut-off function such that when said expansion device is fully closed, the refrigerant cannot pass through the expansion device and then through the third heat exchanger 103. Thus, by controlling the opening and closing of the first shut-off valve 31 and the second expansion device 7, it is possible to control the circulation of the refrigerant and define its path within the refrigerant circuit. The second expansion device 7 may be, for example, an expansion valve.

An alternative (not shown) to the first redirecting system may be: in addition to the first shut-off valve 31, the main branch a comprises a further shut-off valve positioned between the first connection point 41 and the second connection point 42. This further shut-off valve replaces the shut-off function of the second expansion device 7. Another alternative (not shown) may also be, for example, to use a three-way valve positioned at the first connection point 41.

The second bypass branch A2 connects the third connection point 43 and the fourth connection point 44. A third connection point 43 is positioned on the main branch a downstream of the compressor 3, between said compressor 3 and the first expansion device 5. The fourth connection point 44 is positioned on the main branch a downstream of the first expansion device 5, between said first expansion device 5 and the second heat exchanger 102. The second bypass branch A2 is thus connected to the main branch a such that the second bypass branch can bypass the first expansion device 5.

According to a first variant, illustrated in fig. 1, the third connection point 43 is more particularly positioned downstream of the first heat exchanger 101, between said first heat exchanger 101 and the first expansion device 5. According to this first variant, the second bypass branch A2 may bypass only the first expansion device 5.

According to a second variant, illustrated in fig. 2, the third connection point 43 is more specifically positioned upstream of the first heat exchanger 101, between the compressor 3 and said first heat exchanger 101. According to this second variant, the second bypass branch A2 may bypass the first heat exchanger 101 and the first expansion device 5. This second variant may be advantageous for the different modes of operation described below, so that the refrigerant does not enter the first heat exchanger 101.

The third bypass branch A3 may bypass the second heat exchanger 102, the second expansion device 7 and the third heat exchanger 103. The third bypass branch A3 comprises a fourth heat exchanger 104.

This third bypass branch A3 connects more specifically the fifth connection point 45 and the sixth connection point 46. A fifth connection point 45 is positioned on the main branch a downstream of the first expansion device 5, between said first expansion device 5 and the second heat exchanger 102. In the example illustrated in fig. 1, the fifth connection point 45 is positioned more specifically upstream of the fourth connection point 44 of the second bypass branch A2, between the first expansion device 5 and said fourth connection point 44.

The sixth connection point 46 is positioned upstream of the compressor 3. As illustrated in fig. 1, the sixth connection point 46 may be positioned on the main branch a downstream of the second connection point 42 of the first bypass branch A1, between said second connection point 42 and the compressor 3. More specifically, the sixth connection point may be located upstream of the reservoir 11. A variant (not shown) may be to position the sixth connection point 46 still on the main branch a, but downstream of the third heat exchanger 103, between said third heat exchanger 103 and the second connection point 42. Another variant (not shown) may locate the sixth connection point 46 on the first bypass branch A1 upstream of the second connection point 42, between the first shut-off valve 31 and said second connection point 42.

The thermal management device 1 further comprises a second system for redirecting the refrigerant arriving at the third connection point 43 to the first expansion device 5 or to the second heat exchanger 102 via the second bypass branch A2. This second redirecting system may in particular comprise a second shut-off valve 32 positioned on the second bypass branch A2.

The thermal management system 1 further comprises a third system for redirecting the refrigerant arriving at the fifth connection point 45 to the second heat exchanger 102 and/or via the third bypass branch A3 to the fourth heat exchanger 104. This third redirecting system may in particular comprise a third shut-off valve 33 positioned on the third bypass branch A3. The third shut-off valve 33 may be positioned in particular on the third bypass branch A3 upstream of the fourth heat exchanger 104, so as to limit the pressure of the refrigerant inside said fourth heat exchanger 104 when the third shut-off valve 33 is closed. To control the flow rate and the flow of the refrigerant through the third bypass branch A3 and through the fourth heat exchanger 104, the third shut-off valve 33 may be a solenoid valve controllable by pulse width modulation.

As in the example illustrated in fig. 1, when the fifth connection point 45 of the third bypass branch A3 is positioned on the main branch a upstream of the fourth connection point 44 of the second bypass branch A2, the thermal management device 1 may comprise a fourth shut-off valve 34 positioned on the main branch a downstream of said fifth connection point 45, between the fifth connection point 45 and the fourth connection point 44. This particular configuration has the advantage of sharing the fourth shut-off valve 34 between the second and third refrigerant redirecting systems. In order to control the flow rate and the flow of the refrigerant having passed through the first expansion device 5 to the second heat exchanger 102, the fourth shut-off valve 34 may be a solenoid valve controllable by pulse width modulation.

An alternative solution (not shown) is to use two separate shut-off valves for the second and third refrigerant redirecting systems instead of the fourth shut-off valve 44, for example when the fourth connection point 44 of the second bypass branch A2 is on the main branch a upstream of the fifth connection point 45 of the third bypass branch A3. A shut-off valve dedicated to the second refrigerant redirecting system is then positioned on the main branch a between the third connection point 43 and the fourth connection point 44. A shut-off valve dedicated to the third refrigerant redirecting system is positioned on the main branch a between the fifth connection point 45 and the second heat exchanger 102.

Another alternative solution (not shown) for these second and third refrigerant redirecting systems may also be to position three-way valves at the third and fifth connection points 43 and 45, respectively.

The first heat exchanger 101 may in particular be an internal condenser configured to be passed by the internal air flow 200. This first heat exchanger 101 may be more specifically located within a hvac device. In this case, the interior air flow 200 is an air flow intended for the passenger compartment of a motor vehicle. As illustrated in fig. 1, when the third connection point 43 of the second bypass branch A2 is downstream of the first heat exchanger 101, the thermal management device 1 may in particular comprise a shut-off device 13, so as to prevent the internal air flow 200 from passing through the first heat exchanger 101 and to prevent heat energy from being exchanged between the internal air flow 200 and the refrigerant when the refrigerant passes through the second bypass branch A2. This shut-off device 13 may be unnecessary when the third connection point 43 is upstream of the first heat exchanger 101, as illustrated in fig. 2. In this case, when the refrigerant passes through the second bypass branch A2, the refrigerant does not pass through the first heat exchanger 101.

The second heat exchanger 102 may be an evaporator-condenser configured to be passed by the external air stream 300. The second heat exchanger 102 may be more specifically positioned on the front face of the motor vehicle. The external air flow 300 is an air flow from outside the motor vehicle.

The third heat exchanger 103 may be a cooler configured for thermal management of the battery. This third heat exchanger 103 may be, for example, one or more cold plates in direct contact with the battery, or a two-fluid exchanger exchanging thermal energy with a heat transfer fluid circuit dedicated to the thermal management of the battery.

The fourth heat exchanger 104 may be a cooler configured for thermally managing power electronics and/or an electric machine of the motor vehicle. This fourth heat exchanger 104 may be, for example, one or more cold plates in direct contact with the power electronics and/or the motor, or a two-fluid exchanger that exchanges thermal energy with a heat transfer fluid circuit dedicated to the thermal management of the power electronics and/or the motor.

The first expansion means 5 may in particular be a perforated tube. Using a perforated tube as the first expansion device 5 may perform a calibrated first expansion of the refrigerant intended for the second heat exchanger 102 and/or the fourth heat exchanger 104. The orifice tube is more cost effective than other expansion devices such as expansion valves. In addition, because the first expansion is calibrated, there is no need to use a pressure/temperature sensor at the outlet of the second heat exchanger 102 to control the thermal management device 1, but only a more cost effective temperature sensor.

As again illustrated in fig. 1, the thermal management device 1 may further comprise a fourth bypass branch A4. This fourth bypass branch A4 comprises a fifth heat exchanger 105 and a third expansion device 9 positioned upstream of the fifth heat exchanger 105, and connects the seventh connection point 47 and the eighth connection point 48.

The seventh connection point 47 is more specifically positioned downstream of the second heat exchanger 102. The seventh connection point 47 may be positioned on the main branch a upstream of the second expansion means 7. As illustrated in fig. 1, the seventh connection point 47 may be positioned downstream of the first connection point 41 of the first bypass branch A1, between said first connection point 41 and the second expansion device 7. The seventh connection point 47 may also be still positioned on the main branch a upstream of the first connection point 41, between the second heat exchanger 102 and said first connection point 41. The seventh connection point 47 may alternatively be positioned on the first bypass branch A1 upstream of the first shut-off valve 31, between the first connection point 41 and said first shut-off valve 31.

The eighth connection point 48 is positioned upstream of the compressor 3, more specifically upstream of the reservoir 11. As illustrated in fig. 1, the eighth connection point 48 may be positioned on the third bypass branch A3 downstream of the fourth heat exchanger 104 between the fourth heat exchanger 104 and the sixth connection point 46 of the third bypass branch A3. According to a variant (not shown), the eighth connection point 48 may be positioned on the main branch a downstream of the third heat exchanger 103. Thus, the eighth connection point 48 may also be arranged upstream of the reservoir 11 between the third heat exchanger 103 and the second connection point 42 of the first bypass branch A1, between the second connection point 42 and the sixth connection point 46 or between the sixth connection point 46 and the compressor 3. According to a further variant (not shown), the eighth connection point 48 may be positioned on the first bypass branch A1 downstream of the first shut-off valve 31, between said first shut-off valve 31 and the second connection point 42.

In order to allow or prevent refrigerant to enter the fifth heat exchanger 105, the third expansion device 9 may comprise a shut-off function similar to the second expansion device 7. A variant may also be that the fourth bypass branch comprises a shut-off valve, or that the thermal management device 1 comprises a three-way valve at the seventh connection point 47. The third expansion device 9 may also be an expansion valve.

The fifth heat exchanger 105 may in particular be an evaporator configured to be passed by the internal air flow 200. Accordingly, the fifth heat exchanger 105 may be positioned in a hvac device in the same manner as the first heat exchanger 101. The fifth heat exchanger 105 may be positioned in the internal air flow 200, in particular upstream of the first heat exchanger 101.

Thus, the thermal management device 1 may operate in the different modes of operation illustrated in fig. 3-12. In fig. 3 to 12, a portion in which the refrigerant circulates is shown in solid lines, and a portion in which the refrigerant does not circulate is shown in broken lines. The modes of operation described below are not limiting. Other modes of operation are also contemplated and applied in the described architecture.

1) First heat pump mode:

fig. 3 shows the thermal management device 1 of fig. 1 in a first heat pump operation mode.

In this first heat pump mode, the refrigerant enters the compressor 3, where it undergoes a pressure increase and transitions to a so-called high pressure. The refrigerant then passes through the first heat exchanger 101 where it undergoes enthalpy drop, in particular by heating the internal air stream 200. For this purpose, the shut-off device 13 (if present) is opened, as shown in fig. 3.

The refrigerant then passes through the first expansion device 5, where it undergoes a pressure drop and is converted to a so-called low pressure. Here, the second refrigerant redirecting system is configured such that refrigerant does not enter the second bypass branch A2. Thus, the second shut-off valve 32 is closed.

The refrigerant then passes through the second heat exchanger 102, where it undergoes an enthalpy increase by absorbing heat energy from the external air stream 300. Here, the third refrigerant redirecting system is configured such that refrigerant does not enter the third bypass branch A3. Thus, the third shut-off valve 33 is closed, and the fourth shut-off valve 34 is open.

The refrigerant then enters the first bypass branch A1 to reach the compressor 3. Here, the first refrigerant redirecting system is configured such that the refrigerant does not pass through the second expansion device 7 or the third heat exchanger 103. Thus, the first shut-off valve 31 is open and the second expansion device 7 is closed.

Also, if the heat management device 1 includes the fourth bypass branch A4, the refrigerant does not pass through the fourth bypass branch. For this purpose, the third expansion device 9 may also be closed.

Thus, the first heat pump mode may recover thermal energy from the external air stream 300 in the second heat exchanger 102 to heat the internal air stream 200 with the thermal energy.

2) Second heat pump mode:

fig. 4 shows the thermal management device 1 of fig. 1 in a second heat pump operation mode.

In this second heat pump mode, the refrigerant follows the same path as in the first heat pump mode in fig. 3, except at a fifth connection point 45:

a first portion of the refrigerant is redirected to the second heat exchanger 102 and then via the first bypass branch A1 to the compressor 3, as in the first heat pump mode of fig. 3, and

the second portion of refrigerant is redirected into the third bypass branch A3 and reaches the compressor 3 after passing through the fourth heat exchanger 104.

To this end, the third refrigerant redirecting system is configured such that at the fifth connection point 45, the refrigerant enters the second heat exchanger 102 and also passes through the third bypass branch A3. Therefore, the third shut-off valve 33 and the fourth shut-off valve 34 may be opened.

The second portion of the refrigerant, when passing through the fourth heat exchanger 104, recovers heat energy, for example, by cooling the power electronics and/or the electric machine of the motor vehicle.

Here, the first portion of refrigerant and the second portion of refrigerant are joined at a sixth connection point 46 before being returned to the compressor 3.

Thus, this second heat pump mode may be performed in the second heat exchanger 102 by recovering heat energy from the external air stream 300 and by cooling the power electronics and/or the electric machine of the motor vehicle in order to heat the internal air stream 200 with this heat energy.

This second heat pump mode may be particularly used when the external temperature is very low, and the recovery of thermal energy from the external air stream 300 would require a significant amount of power consumption, thereby reducing the coefficient of performance of the thermal management device 1.

3) First dehumidification mode:

fig. 5 shows the thermal management device 1 of fig. 1 in a first dehumidification mode of operation.

In this first dehumidification mode, the refrigerant enters the compressor 3, where it undergoes a pressure increase and transitions to a so-called high pressure. The refrigerant then passes through the first heat exchanger 101 where it undergoes enthalpy drop, in particular by heating the internal air stream 200. For this purpose, the shut-off device 13 (if present) is opened, as shown in fig. 5.

The refrigerant then passes through a first expansion device 5, in which the refrigerant undergoes a first pressure drop and is converted to a so-called intermediate pressure. Here, the second refrigerant redirecting system is configured such that refrigerant does not enter the second bypass branch A2. Thus, the second shut-off valve 32 is closed.

The refrigerant then enters the fourth bypass branch A4 to reach the third expansion device 9. Here, the first refrigerant redirecting system is configured such that the refrigerant does not pass through the second expansion device 7, the third heat exchanger 103, or the first bypass branch A1. Therefore, both the first shut-off valve 31 and the second expansion device 7 are closed.

As the refrigerant passes through the third expansion device 9, the refrigerant undergoes a second pressure drop and transitions from a so-called intermediate pressure to a so-called low pressure. The refrigerant then passes through a fifth heat exchanger 105 where it recovers heat energy, for example by cooling the internal air stream 200.

Accordingly, the first dehumidification mode may cool the internal air stream 200 in the fifth heat exchanger 105 to condense moisture therein, and then heat the internal air stream 200 in the first heat exchanger 101 to enhance comfort. Thus, after the internal air flow has passed through the fifth heat exchanger 105, the thermal energy recovered from the internal air flow 100 in the fifth heat exchanger 105 is dissipated into the external air flow 300 in the second heat exchanger 102 and into the internal air flow 200 in the first heat exchanger 101.

4) Second dehumidification mode:

fig. 6 shows the thermal management device 1 of fig. 1 in a second dehumidification mode of operation.

In this second dehumidification mode, the refrigerant follows the same path as in the first dehumidification mode in fig. 5, except at a fifth connection point 45:

a first portion of the refrigerant is redirected to the second heat exchanger 102 and then via the first bypass branch A1 to the compressor 3, as in the first dehumidification mode of fig. 5, and

Here, the first portion of refrigerant and the second portion of refrigerant are joined at an eighth connection point 48 before being returned to the compressor 3.

Thus, this second dehumidification mode may recover thermal energy in the fifth heat exchanger 105 by cooling the interior air stream 200 and thermal energy in the fourth heat exchanger 104 by cooling the power electronics and/or the electric machine of the motor vehicle. The recovered heat energy is dissipated into the external air flow 300 in the second heat exchanger 102 and into the internal air flow 200 in the first heat exchanger 101 in order to dehumidify it.

This second dehumidification mode may be particularly used when the external temperature is very low, and the recovery of thermal energy from the external air stream 300 would require a significant amount of power consumption, thereby reducing the coefficient of performance of the thermal management device 1.

5) First cooling mode:

fig. 7 shows the thermal management device 1 of fig. 1 in a first cooling mode of operation.

In this first cooling mode, the refrigerant enters the compressor 3, where it undergoes a pressure increase and transitions to a so-called high pressure. The refrigerant then passes through the second bypass branch A2 to reach the second heat exchanger 102, bypassing the first expansion device 5.

Here, the second refrigerant redirecting system is configured such that refrigerant enters the second bypass branch A2. Thus, the second shut-off valve 32 is open.

Here, the third refrigerant redirecting system is configured such that the refrigerant does not enter the third bypass branch A3 and does not pass through the first expansion device 5. Therefore, the third shut-off valve 33 and the fourth shut-off valve 34 are closed.

As illustrated in fig. 7, if the third connection point 43 is downstream of the first heat exchanger 101, the refrigerant passes through said first heat exchanger 101 before entering the second bypass branch A2. However, since the shut-off device 13 is closed such that no internal air flow passes through the first heat exchanger 101, the refrigerant experiences little or no thermal energy loss when passing through the first heat exchanger 101.

If the third connection point 43 is upstream of the first heat exchanger 101 (see fig. 2), the refrigerant enters the second bypass branch A2 upstream of the first heat exchanger 101 and bypasses the first heat exchanger.

The refrigerant then passes through the second heat exchanger 102 where it dissipates heat energy into the external air stream 300.

The refrigerant then passes through the second expansion device 7 and not through the first bypass branch A1. Here, the first refrigerant redirecting system is configured such that the refrigerant passes through the second expansion device 7 and the third heat exchanger 103 without passing through the first bypass branch A1. The first shut-off valve 31 is closed and the second expansion device 7 is opened to allow the refrigerant to pass.

As the refrigerant passes through the second expansion device 7, the refrigerant undergoes a pressure drop and transitions from a so-called high pressure to a so-called low pressure. The refrigerant then passes through a third heat exchanger 103 where it recovers heat energy, for example by cooling a battery of the motor vehicle.

Here, if the heat management device 1 includes the fourth bypass branch A4, the refrigerant does not pass through the fourth bypass branch. For this purpose, the third expansion device 9 is closed.

Thus, the first cooling mode may cool the battery in the third heat exchanger 103. The heat energy recovered from the battery in the third heat exchanger 103 is dissipated into the external air flow 300 in the second heat exchanger 102.

6) Second cooling mode:

fig. 8 shows the thermal management device 1 of fig. 1 in a second cooling mode of operation.

In this second cooling mode, the refrigerant follows the same path as in the first cooling mode in fig. 7, except at the third connection point 43:

the first portion of refrigerant is redirected to the second bypass branch A2, as in the first cooling mode of fig. 7, and

the second portion of refrigerant is redirected to the first expansion device 5 and the third bypass branch A3 and reaches the compressor 3 after passing through the fourth heat exchanger 104.

To this end, the third refrigerant redirecting system is configured such that at the fifth connection point 45, the refrigerant passes through the third bypass branch A3. Thus, the third shut-off valve is open, while the fourth shut-off valve 34 is still closed.

In this second cooling mode, the refrigerant passes through the first heat exchanger 101 when the third connection point 43 is positioned upstream or downstream of the first heat exchanger 101. The shut-off device 13 is closed such that the refrigerant passing through the first heat exchanger 101 experiences little or no heat energy loss.

The second portion of the refrigerant undergoes a pressure drop and is converted to a so-called low pressure when passing through the first expansion device 5. The second portion of the refrigerant then passes through a fourth heat exchanger 104 where it recovers heat energy, for example, by cooling the power electronics and/or the electric machine of the motor vehicle.

Thus, the second cooling mode may cool the battery in the third heat exchanger 103 and the power electronics and/or the motor vehicle in the fourth heat exchanger 104. Both the thermal energy recovered from the battery in the third heat exchanger 103 and the thermal energy recovered from the power electronics and/or the motor of the motor vehicle in the fourth heat exchanger 104 are dissipated into the external air flow 300 in the second heat exchanger 102.

7) Third cooling mode:

fig. 9 shows the thermal management device 1 of fig. 1 in a third cooling mode of operation.

In this third cooling mode, the refrigerant follows the same path as in the first cooling mode in fig. 7, except at a seventh connection point 47:

a first portion of the refrigerant is redirected to a second expansion device 7, as in the first cooling mode of fig. 7, and

the second portion of refrigerant is redirected to the third expansion device 9 and the fourth bypass branch A4 and reaches the compressor 3 after passing through said third expansion device 9 and the fifth heat exchanger 105. For this purpose, the third expansion device 9 is open.

The second portion of the refrigerant undergoes a pressure drop and is converted to a so-called low pressure when passing through the third expansion device 7. The second portion of the refrigerant then passes through a fifth heat exchanger 105 where it recovers heat energy, for example, by cooling the internal air stream 200.

Thus, this third cooling mode may cool the battery in the third heat exchanger 103 and cool the internal air stream 200 in the fifth heat exchanger 105. Both the thermal energy recovered from the battery in the third heat exchanger 103 and the thermal energy recovered from the internal air stream 200 in the fifth heat exchanger 105 are dissipated into the external air stream 300 in the second heat exchanger 102.

8) Fourth cooling mode:

FIG. 10 illustrates the thermal management device of FIG. 1 in a fourth cooling mode of operation.

This fourth cooling mode corresponds more specifically to the combination of the second cooling mode and the third cooling mode in fig. 8 and 9.

Thus, this fourth cooling mode is similar to the third cooling mode, with the first portion of refrigerant passing through the second bypass branch A2 and through the second heat exchanger 102 combining the cooling of the battery in the third heat exchanger 103 and the cooling of the internal air stream in the fifth heat exchanger 105. The first portion of refrigerant undergoes a pressure drop as it passes through the second expansion device 7 or the third expansion device 9 before passing through the third heat exchanger 103 or the fifth heat exchanger 105, respectively.

In addition, similar to the second cooling mode, the second portion of refrigerant passes through the first heat exchanger 5 instead of through the second bypass branch A2. The second portion of refrigerant experiences a pressure drop as it passes through the first expansion device 5 and into the third bypass branch A3. The second portion of the refrigerant then cools the power electronics and/or the motor of the motor vehicle as a result of passing through the fourth heat exchanger 104.

9) Fifth cooling mode:

fig. 11 shows the thermal management device 1 of fig. 1 in a fifth cooling mode of operation.

In this fifth cooling mode, the refrigerant enters the compressor 3, where it undergoes a pressure increase and transitions to a so-called high pressure. The refrigerant then passes through the second bypass branch A2 to reach the second heat exchanger 102, bypassing the first expansion device 5.

As illustrated in fig. 11, if the third connection point 43 is downstream of the first heat exchanger 101, the refrigerant passes through said first heat exchanger 101 before entering the second bypass branch A2. However, since the shut-off device 13 is closed such that no internal air flow passes through the first heat exchanger 101, the refrigerant experiences little or no thermal energy loss when passing through the first heat exchanger 101.

The refrigerant then passes through the third expansion device 9, but not through the first bypass branch A1 or the second expansion device 7. Here, the first refrigerant redirecting system is configured such that the refrigerant does not pass through the second expansion device 7 or the third heat exchanger 103 and also does not pass through the first bypass branch A1. The first shut-off valve 31 and the second expansion device 7 are closed to prevent the refrigerant from passing. The third expansion means 9 is open.

As the refrigerant passes through the third expansion device 9, the refrigerant undergoes a pressure drop and transitions from a so-called high pressure to a so-called low pressure. The refrigerant then passes through a fifth heat exchanger 105 where it recovers heat energy, for example by cooling the internal air stream 200.

Thus, the first cooling mode may cool the internal air flow 200 in the fifth heat exchanger 105. The heat energy recovered from the inner air stream 200 in the fifth heat exchanger 105 is dissipated into the outer air stream 300 in the second heat exchanger 102.

10 Sixth cooling mode:

FIG. 12 illustrates the thermal management device of FIG. 1 in a sixth cooling mode of operation.

In this sixth cooling mode, the refrigerant follows the same path as in the fifth cooling mode in fig. 11, except at the third connection point 43:

the first portion of refrigerant is redirected to the second bypass branch A2, as in the fifth cooling mode of fig. 11, and

To this end, the third refrigerant redirecting system is configured such that at the fifth connection point 45, the refrigerant passes through the third bypass branch A3. Thus, the third shut-off valve 33 is open, while the fourth shut-off valve 34 is still closed.

In this sixth cooling mode, refrigerant passes through the first heat exchanger 101 when the third connection point 43 is positioned upstream or downstream of the first heat exchanger 101. The shut-off device 13 is closed such that the refrigerant passing through the first heat exchanger 101 experiences little or no heat energy loss.

Thus, this sixth cooling mode may cool the internal air flow 200 in the fifth heat exchanger 105 and the power electronics and/or the electric machine of the motor vehicle in the fourth heat exchanger 104. Both the thermal energy recovered from the internal air flow 200 in the fifth heat exchanger 105 and the thermal energy recovered from the power electronics and/or the electric machine of the motor vehicle in the fourth heat exchanger 104 are dissipated into the external air flow 300 in the second heat exchanger 102.

It can thus be seen that the inventive architecture of the thermal management device 1 allows operation in different modes of operation, but still remains easy to implement and cost effective.

Claims

1. A thermal management device (1) for an electric or hybrid motor vehicle, comprising a refrigerant circuit, the refrigerant being intended to circulate inside the refrigerant circuit, the refrigerant circuit comprising:

-a main loop (a) comprising, in the direction of circulation of the refrigerant, a compressor (3), a first heat exchanger (101), a first expansion device (5), a second heat exchanger (102), a second expansion device (7) and a third heat exchanger (103),

-a first bypass branch (A1) connecting a first connection point (41) positioned upstream of the second expansion device (7), between the second heat exchanger (102) and the second expansion device (7), and a second connection point (42) positioned downstream of the third heat exchanger (103), between the third heat exchanger (103) and the compressor (3),

-a second bypass branch (A2) connecting a third connection point (43) positioned on the main branch (a) downstream of the compressor (3) between the compressor (3) and the first expansion device (5) and a fourth connection point (44) positioned on the main branch (a) downstream of the first expansion device (5) between the first expansion device (5) and the second heat exchanger (102),

-a third bypass branch (A3) connecting a fifth connection point (45) positioned on the main branch (a) downstream of the first expansion means (5) between the first expansion means (5) and the second heat exchanger (102), and a sixth connection point (46) positioned upstream of the compressor (3), the third bypass branch (A3) comprising a fourth heat exchanger (104),

-a first system for redirecting the refrigerant reaching the first connection point (41), to the second expansion device (7) or to the compressor (3) via the first bypass branch (A1),

-a second system for redirecting the refrigerant arriving at the third connection point (43) to the first expansion device (5) or to the second heat exchanger (102) via the second bypass branch (A2),

-a third system for redirecting the refrigerant reaching the fifth connection point (45), redirecting the refrigerant to the second heat exchanger (102) and/or redirecting the fourth heat exchanger (104) via the third bypass branch (A3).

2. A thermal management device (1) according to claim 1, wherein said first expansion means (5) is a perforated tube.

3. The thermal management device (1) according to any one of the preceding claims, wherein said second redirecting system comprises a second shut-off valve (32) positioned on said second bypass branch (A2).

4. The thermal management device (1) according to any one of the preceding claims, wherein said third redirecting system comprises a third shut-off valve (33) positioned on said third bypass branch (A3).

5. The thermal management device (1) according to the preceding claim, wherein the third shut-off valve (33) is positioned on the third bypass branch (A3) upstream of the fourth heat exchanger (104).

6. The thermal management device (1) according to any one of the preceding claims, wherein a fifth connection point (45) of the third bypass branch (A3) is positioned on the main branch (a) upstream of a fourth connection point (44) of the second bypass branch (A2).

7. Thermal management device (1) according to the preceding claim, wherein a fourth shut-off valve (34) is positioned on said main branch (a), downstream of said fifth connection point (45), between said fifth connection point (45) and said fourth connection point (44).

8. The thermal management device (1) according to any one of the preceding claims, wherein:

the first heat exchanger (101) is an internal condenser configured to be passed by an internal air flow (200),

the second heat exchanger (102) is an evaporator-condenser configured to be passed by an external air flow (300),

the third heat exchanger (103) is a cooler configured for thermal management of the battery,

-the fourth heat exchanger (104) is a cooler configured for thermal management of power electronics and/or an electric machine of the motor vehicle.

9. The thermal management device (1) according to any one of the preceding claims, characterized in that it comprises a fourth bypass branch (A4) connecting a seventh connection point (47) positioned downstream of the second heat exchanger (102) and an eighth connection point (48) positioned upstream of the compressor (3), the fourth bypass branch (A4) comprising a fifth heat exchanger (105) and a third expansion device (9) positioned upstream of the fifth heat exchanger (105).

10. The thermal management device (1) according to claim 9, wherein the fifth heat exchanger (105) is an evaporator configured to be passed by an internal air flow (200).