EP4255745A1

EP4255745A1 - Thermal management device for an electric or hybrid motor vehicle

Info

Publication number: EP4255745A1
Application number: EP21814779.1A
Authority: EP
Inventors: Mohamed Yahia; Stefan Karl
Original assignee: Valeo Systemes Thermiques SAS
Current assignee: Valeo Systemes Thermiques SAS
Priority date: 2020-12-02
Filing date: 2021-11-18
Publication date: 2023-10-11
Also published as: FR3116764A1; WO2022117360A1; CN116829383A; FR3116764B1

Abstract

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

Description

THERMAL MANAGEMENT DEVICE OF AN ELECTRIC OR HYBRID MOTOR VEHICLE

[1]The present invention relates to the field of electric or hybrid motor vehicles and more particularly to a thermal management device for batteries, as well as power electronics and/or the electric motor of said electric vehicle.

[2]Current electric or hybrid motor vehicles increasingly include a heat transfer fluid circuit in order to thermally manage the batteries as well as the power electronics and/or the electric motor of said electric vehicle. Indeed, in order for these elements to be as efficient as possible, they must remain at an optimum operating temperature. It is therefore necessary to cool them during use so that they do not excessively exceed this optimum operating temperature. Similarly, it may also be necessary to heat them, for example in cold weather, so that they reach this optimum operating temperature as quickly as possible. In addition, these elements may have different optimum operating temperatures, which implies a differentiation in thermal management for each of these elements.

[3]I1 is thus known that the heat transfer fluid circuit comprises a complex architecture allowing both the thermal management of the batteries and of the power electronics and/or of the electric motor of said electric vehicle. The heat transfer fluid circuit then generally comprises a heat exchanger as well as a dedicated expansion device for each of these elements as well as various circulation and bypass branches in order to ensure good thermal management of these elements at different temperatures. However, these architectures are generally complex and expensive.

[4] One of the aims of the present invention is therefore to at least partially remedy the drawbacks of the prior art and to propose a simpler, less expensive thermal management device that can operate according to different operating modes for the thermal management of batteries as well as power electronics and/or the electric motor of an electric vehicle. [5] 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 in which a refrigerant fluid is intended to circulate and comprising:

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

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

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

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

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

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

[6]According to one aspect of the invention, the first expansion device is a tube orifice.

[7]According to another aspect of the invention, the first redirection system comprises a first shut-off valve arranged on the first bypass branch.

[8]According to another aspect of the invention, the second trigger device includes a stop function.

[9]According to another aspect of the invention, the second redirection system comprises a second shut-off valve arranged on the second bypass branch.

[10]According to another aspect of the invention, the third redirection system comprises a third shut-off valve arranged on the third bypass branch.

[1 l]According to another aspect of the invention, the third shut-off valve is arranged on the third bypass branch upstream of the fourth heat exchanger.

[12]According to another aspect of the invention, the third shut-off valve is a solenoid valve controllable by pulse width modulation.

[13]According to another aspect of the invention, the fifth connection point of the third branch branch is arranged on the main branch upstream of the fourth connection point of the second branch branch.

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

[15]According to another aspect of the invention, the fourth shut-off valve is a solenoid valve controllable by pulse width modulation.

[16]According to another aspect of the invention:

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

- the second heat exchanger is an evapo-condenser configured to be crossed by an external air flow,

- the third heat exchanger is a chiller configured for the thermal management of the batteries,

- the fourth heat exchanger is a chiller configured for the thermal management of 1 power electronics and/or of the electric motor of the motor vehicle.

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

[18]According to another aspect of the invention, the third trigger device includes a stop function.

[19]According to another aspect of the invention, the fifth heat exchanger is an evaporator configured to be crossed by an internal air flow.

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

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

[22]Other characteristics and advantages of the present invention will appear more clearly on reading the following description, provided for illustrative and non-limiting purposes, and the appended drawings in which:

[23] Figure 1 is a schematic representation of a thermal management device according to a first embodiment,

[24] Figure 2 is a schematic representation of a thermal management device according to a second embodiment,

[25] Figure 3 is a schematic representation of the thermal management device of Figure 1 according to a first heat pump mode,

[26] Figure 4 is a schematic representation of the thermal management device of Figure 1 according to a second heat pump mode,

[27] Figure 5 is a schematic representation of the thermal management device of Figure 1 according to a first dehumidification mode, [28] Figure 6 is a schematic representation of the thermal management device of Figure 1 according to a second mode of dehumidification,

[29] Figure 7 is a schematic representation of the thermal management device of Figure 1 according to a first cooling mode,

[30] Figure 8 is a schematic representation of the thermal management device of Figure 1 according to a second cooling mode,

[31] Figure 9 is a schematic representation of the thermal management device of Figure 1 according to a third mode of cooling,

[32] Figure 10 is a schematic representation of the thermal management device of Figure 1 according to a fourth cooling mode,

[33] Figure 11 is a schematic representation of the thermal management device of Figure 1 according to a fifth cooling mode,

[34] Figure 12 is a schematic representation of the thermal management device of Figure 1 according to a sixth mode of cooling.

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

[36]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. Simple features of different embodiments may also be combined and/or interchanged to provide other embodiments.

[37]In the present description, certain elements or parameters can be indexed, such as for example first element or second element as well as first parameter and second parameter or even first criterion and second criterion, etc. In this case, it is a simple indexing to differentiate and name elements or parameters or criteria that are close, but not identical. This indexing does not imply a priority of one element, parameter or criterion over another and such denominations can easily be interchanged 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.

[38] In the present description, the term “placed upstream” means that one element is placed before another with respect to the direction of circulation of a fluid. Conversely, “place downstream” means that one element is placed after another with respect to the direction of flow of the fluid.

[39] Figure 1 shows a schematic representation of a thermal management device 1 of an electric or hybrid motor vehicle. The thermal management device 1 comprises a refrigerant circuit in which a refrigerant fluid is intended to circulate. This refrigerant circuit comprises a main branch A, a first bypass branch Al, a second bypass branch A2 and a third bypass branch A3.

[40] The main branch A, shown in extra thickness in Figure 1, comprises, in the direction of circulation of the refrigerant fluid, 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 can also include, upstream of the compressor 3, a phase separation device 11 such as an accumulator. More precisely, this accumulator 11 can be arranged between the third heat exchanger 103 and the compressor 3.

[41] The first bypass branch Al is connected to the main branch A so as to bypass the second expansion device 7 and the third heat exchanger 103. The first bypass branch Al thus connects a first connection point 41 to a second connection point 42. The first connection point 41 is arranged 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 arranged 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 arranged upstream of the accumulator 11.

[42] The thermal management device 1 further comprises a first system for redirecting the refrigerant fluid arriving at the first connection point 41 in order to redirect the refrigerant fluid coming from the second heat exchanger 102 to the compressor 3 via the first branch of diversion Al or to the second expansion device 7. This first redirection system may in particular comprise a first shut-off valve 31 arranged on the first bypass branch AL The second expansion device 7 may for its part include a shut-off function so that, when the latter is completely closed, the refrigerant fluid cannot pass through it and then pass through the third heat exchanger 103. By controlling the opening and closing of the first shut-off valve 31 and the second expansion device 7, it is thus possible to control the circulation of the refrigerant fluid and to define its path within the refrigerant circuit. The second expansion device 7 may for example be an expansion valve.

[43]An alternative, not shown, of the first redirection system can be that in addition to the first shut-off valve 31, the main branch A comprises another shut-off valve arranged between the first 41 and the second 42 point connection. This other stop valve replacing the stop function of the second expansion device 7. Yet another alternative not shown can also be the use of a three-way valve arranged at the level of the first connection point 41 for example.

[44] The second bypass branch A2 connects a third connection point 43 to a fourth connection point 44. The third connection point 43 is arranged 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 arranged 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 so as to allow bypassing of the first expansion device 5.

[45] According to a first variant illustrated in Figure 1, the third connection point 43 is more precisely disposed downstream of the first heat exchanger 101, between said first heat exchanger 101 and the first expansion device 5. According to this first alternatively, the second bypass branch A2 allows bypassing only the first expansion device 5.

[46] According to a second variant illustrated in Figure 2, the third connection point 43 is more precisely arranged upstream of the first heat exchanger 101, between compressor 3 and said first heat exchanger 101. According to this second variant, the second bypass branch A2 allows both the bypass of the first heat exchanger 101 and the bypass of the first expansion device 5. This second variant can be advantageous for different modes of operation, described later in the description, so that the refrigerant fluid does not pass through the first heat exchanger 101.

[47] The third bypass branch A3 allows the bypass of 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.

[48] This third bypass branch A3 more precisely connects a fifth connection point 45 to a sixth connection point 46. The fifth connection point 45 is arranged 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 more precisely arranged 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.

[49] The sixth connection point 46 is arranged upstream of the compressor 3. As illustrated in Figure 1, the sixth connection point 46 can be arranged on the main branch A downstream of the second connection point 42 of the first bypass branch Al, between said second connection point 42 and the compressor 3. More specifically, upstream of the accumulator 11. A variant not shown may be to arrange 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. Yet another variant, not shown, may be to arrange the sixth connection point 46 on the first bypass branch Al, in upstream of the second connection point 42, between the first shut-off valve 31 and said second connection point 42.

[50] The thermal management device 1 also comprises a second system for redirecting the refrigerant fluid arriving at the third connection point 43, redirecting the refrigerant fluid to the second heat exchanger 102 via the second bypass branch A2 or to the first device of relaxation 5. This second redirection system may in particular comprise a second shut-off valve 32 disposed on the second bypass branch A2.

[51] The thermal management device 1 also comprises a third system for redirecting the refrigerant fluid arriving at the fifth connection point 45, redirecting the refrigerant fluid to the second heat exchanger 102 and/or to the fourth heat exchanger 104 via the third bypass branch A3. This third redirection system may in particular comprise a third shut-off valve 33 arranged on the third bypass branch A3. The third shut-off valve 33 can in particular be arranged on the third bypass branch A3 upstream of the fourth heat exchanger 104 in order to limit the pressure of the refrigerant fluid within said fourth heat exchanger 104 when the third shut-off valve 33 is closed. In order to control the flow rate and quantity of refrigerant passing through the third bypass branch A3 and passing through the fourth heat exchanger 104, the third shut-off valve 33 can be a solenoid valve controllable by pulse width modulation.

[52] When, as in the example illustrated in Figure 1, the fifth connection point 45 of the third branch branch A3 is arranged on the main branch A upstream of the fourth connection point 44 of the second branch branch A2, the thermal management device 1 may include a fourth shut-off valve 34 arranged on the main branch A downstream of said fifth connection point 45, between the fifth 45 and the fourth 44 connection point. This particular configuration has the advantage of pooling the fourth shut-off valve 34 both for the second and the third refrigerant fluid redirection system. In order to control the flow rate and the quantity of refrigerant fluid having passed through the first expansion device 5 towards the second heat exchanger 102, the fourth shut-off valve 34 can be a solenoid valve controllable by pulse width modulation.

[53]An alternative solution (not shown), for example when the fourth connection point 44 of the second bypass branch A2 is upstream of the fifth connection point 45 of the third bypass branch A3 on the main branch A, remains the use of two separate shut-off valves for the second and third refrigerant redirection system in replacement of the fourth shut-off valve 44. The shut-off valve dedicated to the second refrigerant fluid redirection system would then be placed on the main branch A between the third 43 and the fourth 44 connection point. The shut-off valve dedicated to the third refrigerant fluid redirection system would be arranged on the main branch A between the fifth connection point 45 and the second heat exchanger 102.

[54] Yet another alternative solution (not shown) for these second and third refrigerant fluid redirection systems can also be to arrange a three-way valve respectively at the level of the third 43 and the fifth 45 connection point.

[55] The first heat exchanger 101 can in particular be an internal condenser configured to be crossed by an internal air flow 200. This first heat exchanger 101 can more particularly be arranged within one of a heating device , ventilation and air conditioning. The internal air flow 200 is then an air flow intended for the passenger compartment of the motor vehicle. When the third connection point 43 of the second bypass branch A2 is downstream of the first heat exchanger 101, as illustrated in FIG. that the internal air flow 200 passes through the first heat exchanger 101 and that there is an exchange of calorific energy between the internal air flow 200 and the refrigerant fluid when the refrigerant fluid passes through the second bypass branch A2. This closure device 13 may not be necessary when the third connection point 43 is upstream of the first heat exchanger 101 as illustrated in FIG. 2. Indeed, in this case, when the refrigerant fluid passes through the second bypass branch A2, the refrigerant fluid does not pass through the first heat exchanger 101.

[56] The second heat exchanger 102 can be an evapo-condenser configured to be crossed by an external air flow 300. The second heat exchanger 102 can more particularly be placed on the front of the motor vehicle. The external air flow 300 is a flow of air coming from outside the motor vehicle.

[57] The third heat exchanger 103 can be a chiller configured for battery thermal management. This third heat exchanger 103 can be for example one or more cold plates directly in contact with the batteries or even a two-fluid heat exchanger exchanging heat energy with a heat transfer fluid circuit dedicated to the thermal management of the batteries.

[58] The fourth heat exchanger 104 can be a cooler configured for the thermal management of the power electronics and/or the electric motor of the motor vehicle. This fourth heat exchanger 104 may for example be one or more cold plates directly in contact with the power electronics and/or the electric motor or even a two-fluid heat exchanger exchanging heat energy with a heat transfer fluid circuit dedicated to the thermal management of the power electronics and/or the electric motor.

[59] The first expansion device 5 may in particular be a tube orifice. The use of a tube orifice as the first expansion device 5 makes it possible to perform a first calibrated expansion of the refrigerant fluid intended for the second heat exchanger 102 and/or the fourth heat exchanger 104. A tube orifice is more economical another expansion device such as an expansion valve. In addition, the fact that the first expansion is calibrated, it is not necessary to use a pressure/temperature sensor at the outlet of the second heat exchanger 102 for controlling the thermal management device 1 but simply a sensor more economical temperature.

[60] Still as shown in Figure 1, the thermal management device 1 may also include a fourth bypass branch A4. This fourth bypass branch A4 comprises a fifth heat exchanger 105 and a third expansion device 9 arranged upstream of the fifth heat exchanger 105 and connects a seventh connection point 47 to an eighth connection point 48.

[61] The seventh connection point 47 is more particularly arranged downstream of the second heat exchanger 102. The seventh connection point 47 can be arranged on the main branch A upstream of the second expansion device 7. The seventh connection point 47 can be arranged, as shown in Figure 1, downstream of the first connection point 41 of the first branch Al branch, between said first connection point 41 and the second expansion device 7. The seventh connection point 47 can also be arranged, still 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 can be arranged alternately on the first branch diversion Al upstream of the first shut-off valve 31, between the first connection point

41 and said first shut-off valve 31.

[62] The eighth connection point 48 is arranged upstream of the compressor 3, more precisely upstream of the accumulator 11. The eighth connection point 48 can be, as illustrated in FIG. 1, arranged on the third bypass branch A3, downstream of the fourth heat exchanger 104, between said 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 can be arranged on the main branch A, downstream of the third heat exchanger 103. The eighth connection point 48 can thus also be arranged between the third heat exchanger 103 and the second connection point 42 of the first bypass branch Al, between the second connection point

42 and the sixth connection point 46 or between the sixth connection point 46 and the compressor 3, upstream of the accumulator 11. According to yet another variant (not shown), the eighth connection point 48 can be arranged on the first bypass branch Al, downstream of the first shut-off valve 31, between said first shut-off valve 31 and the second connection point 42.

[63] In order to allow or not the passage of the refrigerant fluid in the fifth heat exchanger 105, the third expansion device 9 may comprise, like the second expansion device 7, a stop function. A variant can 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 level of the seventh connection point 47. The third expansion device 9 can also be an expansion valve.

[64] The fifth heat exchanger 105 can in particular be an evaporator configured to be crossed by an internal air flow 200. The fifth heat exchanger 105 can thus be placed in a heating, ventilation and air conditioning device in the same way than the first heat exchanger 101. The fifth heat exchanger 105 can in particular be placed upstream of the first heat exchanger 101 in the internal air flow 200.

[65] The thermal management device 1 can thus operate according to different operating modes illustrated in FIGS. 3 to 12. In FIGS. the coolant does not circulate are shown in dotted lines. The operating modes described below are not limiting. Other operating modes can also be imagined and applied with the architecture described.

[6611) first heat pump mode:

[67] Figure 3 shows the thermal management device 1 of Figure 1 according to a first mode of heat pump operation.

[68] In this first heat pump mode, the refrigerant passes through the compressor 3 where it undergoes a pressure increase and passes to a so-called high pressure. The refrigerant fluid then passes through the first heat exchanger 101 at the level of which it undergoes a loss of enthalpy, in particular by heating the internal air flow 200. For this, the shutter device 13 is open if it is present as in figure 3.

[69] The coolant then passes through the first expansion device 5 at which it undergoes a loss of pressure and goes to a so-called low pressure. The second refrigerant fluid redirection system is here configured so that the refrigerant fluid does not pass into the second bypass branch A2. The second shut-off valve 32 is thus closed.

[70] The refrigerant then passes through the second heat exchanger 102 at which it undergoes an enthalpy increase by absorbing heat energy from the external air flow 300. The third refrigerant fluid redirection system is configured here so that the refrigerant fluid does not pass into the third bypass branch A3. The third stop valve 33 is thus closed and the fourth stop valve 34 is open.

[71] The refrigerant fluid then passes through the first bypass branch Al to join the compressor 3. The first refrigerant fluid redirection system is here configured so that the refrigerant fluid does not pass through the second expansion device 7 nor the third exchanger heat 103. The first stop valve 31 is thus open and the second expansion device 7 is closed.

[72]Similarly, if the thermal management device 1 comprises a fourth bypass branch A4, the refrigerant fluid does not pass through the latter. For this, the third expansion device 9 can also be closed.

[73] This first heat pump mode thus makes it possible to recover heat energy in the external air flow 300 at the level of the second heat exchanger 102 in order to heat the internal air flow 200 with this heat energy.

[74129 second heat pump mode:

[75] Figure 4 shows the thermal management device 1 of Figure 1 according to a second mode of heat pump operation.

[76] In this second heat pump mode, the refrigerant fluid follows the same path as in the first heat pump mode of Figure 3, except that at the level of the fifth connection point 45:

- a first portion of refrigerant fluid is redirected to the second heat exchanger 102 and then joins the compressor 3 via the first bypass branch Al as in the first heat pump mode of Figure 3, and

- a second portion of the refrigerant fluid is redirected in the third bypass branch A3 and joins the compressor 3 after having passed through the fourth heat exchanger 104.

[77] For this, the third refrigerant fluid redirection system is configured so that at the level of the fifth connection point 45 the refrigerant fluid goes both to the second heat exchanger 102 and crosses the third bypass branch A3. The third 33 and fourth 34 shut-off valves can thus be opened.

[78]By crossing the fourth heat exchanger 104, the second portion of refrigerant fluid recovers heat energy, for example by cooling the power electronics and/or the electric motor of the motor vehicle.

[79] The first and the second portion of refrigerant fluid join here at the level of the sixth connection point 46 before returning to the compressor 3. [80] This second heat pump mode thus makes it possible to recover heat energy in the external air flow 300 at the level of the second heat exchanger 102 and by cooling the power electronics and/or the electric motor of the motor vehicle in order to heat the internal air flow 200 with this calorific energy.

[81] This second heat pump mode can in particular be used when the outside temperature is very low and for which the recovery of heat energy in the external air flow 300 would require a high consumption of electrical energy, reducing the coefficient of thermal management device performance 1.

[82131 first dehumidification mode:

[83] Figure 5 shows the thermal management device 1 of Figure 1 according to a first mode of dehumidification operation.

[84] In this first mode of dehumidification, the refrigerant fluid passes into the compressor 3 at which it undergoes an increase in pressure and passes to a so-called high pressure. The refrigerant fluid then passes through the first heat exchanger 101 at the level of which it undergoes a loss of enthalpy, in particular by heating the internal air flow 200. For this, the shutter device 13 is open if it is present as in Figure 5.

[85] The coolant then passes through the first expansion device 5 at which it undergoes a first loss of pressure and passes to a so-called intermediate pressure. The second refrigerant fluid redirection system is here configured so that the refrigerant fluid does not pass into the second bypass branch A2. The second shut-off valve 32 is thus closed.

[86] The refrigerant then passes through the second heat exchanger 102 at which it undergoes an enthalpy increase by absorbing heat energy from the external air flow 300. The third refrigerant fluid redirection system is configured here so that the refrigerant fluid does not pass into the third bypass branch A3. The third stop valve 33 is thus closed and the fourth stop valve 34 is open.

[87]The refrigerant fluid then passes through the fourth bypass branch A4 to reach the third expansion device 9. The first refrigerant fluid redirection system is here configured so that the refrigerant fluid does not pass through the second expansion device 7, the third interchange heat 103 or even passes through the first bypass branch Al. The first shut-off valve 31 is closed as well as the second expansion device 7.

[88]While passing through the third expansion device 9, the refrigerant undergoes a second loss of pressure and goes from a so-called intermediate pressure to a so-called low pressure. The refrigerant then passes through the fifth heat exchanger 105 at which it recovers heat energy, for example by cooling the internal air flow 200.

[89] This first dehumidification mode thus makes it possible to subject the internal air flow 200 to cooling at the level of the fifth heat exchanger 105 in order to condense its humidity and then to heat the internal air flow 200 at the level of the first heat exchanger 101 for better comfort. The calorific energy recovered in the internal air flow 100 at the level of the fifth heat exchanger 105 is thus dissipated both in the external air flow 300 at the level of the second heat exchanger 102 and of the first heat exchanger 101 in the internal air flow 200 having previously passed through the fifth heat exchanger 105.

[9014) second dehumidification mode:

[91] Figure 6 shows the thermal management device 1 of Figure 1 according to a second mode of dehumidification operation.

[92] In this second dehumidification mode, the refrigerant fluid follows the same path as in the first dehumidification mode of Figure 5, except that at the fifth connection point 45:

- a first portion of refrigerant fluid is redirected to the second heat exchanger 102 and then joins the compressor 3 via the first bypass branch Al as in the first dehumidification mode of Figure 5, and

[93] For this, the third refrigerant fluid redirection system is configured so that at the level of the fifth connection point 45 the refrigerant fluid goes both to the second heat exchanger 102 and crosses the third branch branch A3. The third 33 and fourth 34 stop valves can thus be opened.

[94]By crossing the fourth heat exchanger 104, the second portion of refrigerant fluid recovers heat energy, for example by cooling the power electronics and/or the electric motor of the motor vehicle.

[95] The first and the second portion of refrigerant fluid meet here at the level of the eighth connection point 48 before returning to the compressor 3.

[96] This second dehumidification mode thus makes it possible to recover heat energy at the level of the fifth heat exchanger 105 by cooling the internal air flow 200 and at the level of the fourth heat exchanger 104 and cooling the power electronics and/or the electric motor of the motor vehicle, the heat energy recovered is dissipated both at the level of the second heat exchanger 102 in the external air flow 300 and at the level of the first heat exchanger 101 in the flow of internal air 200 for its dehumidification.

[97] This second dehumidification mode can in particular be used when the outside temperature is very low and for which the recovery of heat energy in the external air flow 300 would require a significant consumption of electrical energy, reducing the coefficient of performance of the thermal management device 1.

[9815) first cooling mode:

[99] Figure 7 shows the thermal management device 1 of Figure 1 in a first mode of cooling operation.

[100] In this first cooling mode, the refrigerant fluid passes through the compressor 3 at which it undergoes a pressure increase and passes to a so-called high pressure. The refrigerant fluid then passes through the second bypass branch A2 to join the second heat exchanger 102 bypassing the first expansion device 5.

[101] The second refrigerant fluid redirection system is here configured so that the refrigerant passes into the second bypass branch A2. The second shut-off valve 32 is thus opened.

[102] The third refrigerant fluid redirection system is here configured so that the refrigerant fluid does not pass into the third bypass branch A3 and does not pass through the first expansion device 5 either. The third 33 and fourth 34 shut-off valves are thus closed.

[103] In the case illustrated in Figure 7 where the third connection point 43 is downstream of the first heat exchanger 101, the refrigerant passes through said first heat exchanger 101 before passing into the second bypass branch A2. However, the refrigerant fluid does not undergo any or little heat energy loss while crossing the first heat exchanger 101 because the shutter device 13 is closed so that an internal air flow does not cross the first heat exchanger. 101.

[104] In the case where the third connection point 43 is upstream of the first heat exchanger 101 (see figure 2), the refrigerant passes into the second bypass branch A2 upstream of the first heat exchanger 101 and bypasses this last.

[105] The refrigerant then passes through the second heat exchanger 102 where it dissipates heat energy into the external air flow 300.

[106] The refrigerant fluid then passes through the second expansion device 7 without passing through the first bypass branch Al. The first refrigerant fluid redirection system is here configured so that the refrigerant fluid passes through the second expansion device 7, the third heat exchanger heat 103 and does not pass through the first bypass branch AL The first shut-off valve 31 is closed and the second expansion device 7 is open to allow the coolant to pass.

[107]While passing through the second expansion device 7, the refrigerant undergoes a loss of pressure and goes from a so-called high pressure to a so-called low pressure. The refrigerant then passes through the third heat exchanger 103 at which it recovers heat energy, for example by cooling the batteries of the motor vehicle.

[108] In the case where the thermal management device 1 comprises a fourth bypass branch A4, the refrigerant fluid does not pass here through the latter. For this, the third expansion device 9 is closed.

[109] This first cooling mode thus makes it possible to cool the batteries at the level of the third heat exchanger 103. The heat energy recovered from the batteries at the level of the third heat exchanger 103 is dissipated in the external air flow 300 at the level of the second heat exchanger 102. [ 11016) second cooling mode:

[11 l] Figure 8 shows the thermal management device 1 of Figure 1 according to a second mode of cooling operation.

[112] In this second cooling mode, the coolant follows the same path as in the first cooling mode of Figure 7, except that at the third connection point 43:

- a first portion of refrigerant fluid is redirected into the second bypass branch A2 as in the first cooling mode of Figure 7, and

- a second portion of the refrigerant fluid is redirected to the first expansion device 5 and the third bypass branch A3 before joining the compressor 3 after having passed through the fourth heat exchanger 104.

[113] For this, the third refrigerant fluid redirection system is configured so that at the level of the fifth connection point 45 the refrigerant fluid passes through the third bypass branch A3. The third shut-off valve is thus open and the fourth shut-off valve 34 is always closed.

[114] In this second cooling mode, coolant passes through the first heat exchanger 101 both when the third connection point 43 is arranged upstream or downstream of said first heat exchanger 101. In order for the coolant passing through the first heat exchanger 101 suffers little or no loss of heat energy, the shutter device 13 is closed.

[115] Passing through the first expansion device 5, the second portion of refrigerant undergoes a loss of pressure and goes to a so-called low pressure. The second portion of refrigerant then passes through the fourth heat exchanger 104, at which it recovers heat energy, for example by cooling the power electronics and/or the electric motor of the motor vehicle.

[116] This second cooling mode thus makes it possible to cool the batteries at the level of the third heat exchanger 103 as well as the power electronics and/or of the electric motor of the motor vehicle at the level of the fourth heat exchanger 104. The energy heat recovered, both from the batteries at the level of the third heat exchanger 103 and from 1 power electronics and / or electric motor of the motor vehicle at the level of the fourth heat exchanger 104, is dissipated in the external air flow 300 at the level of the second heat exchanger 102.

[ 11717) third cooling mode:

[118] Figure 9 shows the thermal management device 1 of Figure 1 according to a third mode of cooling operation.

[119] In this third cooling mode, the refrigerant fluid follows the same path as in the first cooling mode of Figure 7, except that at the level of the seventh connection point 47:

- a first portion of coolant is redirected to the second expansion device 7 as in the first cooling mode of Figure 7, and

- a second portion of the refrigerant fluid is redirected to the third expansion device 9 and the fourth bypass branch A4 before joining the compressor 3 after having passed through said third expansion device 9 and the fifth heat exchanger 105. For this, the third expansion device 9 is open.

[120] Passing through the third expansion device 7, the second portion of refrigerant undergoes a loss of pressure and goes to a so-called low pressure. The second portion of refrigerant then passes through the fifth heat exchanger 105, at which it recovers heat energy, for example by cooling the internal air flow 200.

[121] This third cooling mode thus makes it possible to cool the batteries at the level of the third heat exchanger 103 as well as the internal air flow 200 at the level of the fifth heat exchanger 105. The heat energy recovered, both from the batteries at the level of the third heat exchanger 103 that of the internal air flow 200 at the level of the fifth heat exchanger 105, is dissipated in the external air flow 300 at the level of the second heat exchanger 102.

[ 12218) fourth cooling mode:

[123] Figure 10 shows the thermal management device of Figure 1 according to a fourth mode of cooling operation. [124] This fourth cooling mode corresponds more particularly to the combination of the second and third cooling modes of Figures 8 and 9.

[125] This fourth cooling mode thus combines, like the third cooling mode, cooling of the batteries at the level of the third heat exchanger 103 and cooling of the internal air flow at the level of the fifth heat exchanger 105 by a first portion of refrigerant fluid passing through the second bypass branch A2 and crossing the second heat exchanger 102. This first portion of refrigerant fluid undergoes a loss of pressure while passing through the second 7 or the third 9 expansion device before passing through respectively the third 103 or the fifth 105 heat exchanger.

[126]Furthermore, like the second mode of cooling, a second portion of refrigerant passes through the first heat exchanger 5 instead of passing through the second bypass branch A2. This second portion of refrigerant undergoes a loss of pressure while passing through the first expansion device 5 and passes into the third bypass branch A3. This second portion of coolant then cools the power electronics and/or the electric motor of the motor vehicle by crossing the fourth heat exchanger 104.

[ 12719) fifth cooling mode:

[128] Figure 11 shows the thermal management device 1 of Figure 1 in a fifth mode of cooling operation.

[129] In this fifth mode of cooling, the refrigerant passes through the compressor 3 at which it undergoes a pressure increase and passes to a so-called high pressure. The refrigerant fluid then passes through the second bypass branch A2 to join the second heat exchanger 102 bypassing the first expansion device 5.

[130] The second refrigerant fluid redirection system is here configured so that the refrigerant passes into the second bypass branch A2. The second shut-off valve 32 is thus opened.

[131]The third refrigerant fluid redirection system is here configured so that the refrigerant fluid does not pass into the third bypass branch A3 and does not pass through the first expansion device 5 either. The third 33 and fourth 34 shut-off valves are thus closed.

[132] In the case illustrated in Figure 11 where the third connection point 43 is downstream of the first heat exchanger 101, the refrigerant passes through said first heat exchanger 101 before passing into the second bypass branch A2. However, the refrigerant fluid does not undergo any or little heat energy loss while crossing the first heat exchanger 101 because the shutter device 13 is closed so that an internal air flow does not cross the first heat exchanger. 101.

[133] In the case where the third connection point 43 is upstream of the first heat exchanger 101 (see figure 2), the refrigerant fluid passes into the second bypass branch A2 upstream of the first heat exchanger 101 and bypasses this last.

[134] The refrigerant then passes through the second heat exchanger 102 where it dissipates heat energy into the external air flow 300.

[135] The refrigerant fluid then passes through the third expansion device 9 without passing through the first bypass branch Al or through the second expansion device 7. The first refrigerant fluid redirection system is here configured so that the refrigerant fluid does not pass through the second expansion device 7, the third heat exchanger 103 and does not cross the first bypass branch AL either. The first shut-off valve 31 and the second expansion device 7 are closed in order to block the refrigerant fluid. The third expansion device 9 is itself open.

[136] When passing through the third expansion device 9, the refrigerant undergoes a loss of pressure and goes from a so-called high pressure to a so-called low pressure. The refrigerant then passes through the fifth heat exchanger 105 at which it recovers heat energy, for example by cooling the internal air flow 200.

[137] This first mode of cooling thus makes it possible to cool the internal air flow 200 at the level of the fifth heat exchanger 105. The heat energy recovered from the internal air flow 200 at the level of the fifth heat exchanger 105 is dissipated in the external air flow 300 at the level of the second heat exchanger 102.

[ 138110) sixth cooling mode: [139] Figure 12 shows the thermal management device of Figure 1 according to a sixth mode of cooling operation.

[140] In this sixth cooling mode, the coolant follows the same path as in the fifth cooling mode of Figure 11, except that at the third connection point 43:

- a first portion of refrigerant fluid is redirected into the second bypass branch A2 as in the fifth cooling mode of Figure 11, and

[141] For this, the third refrigerant fluid redirection system is configured so that at the level of the fifth connection point 45 the refrigerant fluid passes through the third bypass branch A3. The third shut-off valve 33 is thus open and the fourth shut-off valve 34 is still closed.

[142] In this sixth mode of cooling, coolant passes through the first heat exchanger 101 both when the third connection point 43 is arranged upstream or downstream of said first heat exchanger 101. In order for the coolant passing through the first heat exchanger 101 suffers little or no loss of heat energy, the shutter device 13 is closed.

[143] Passing through the first expansion device 5, the second portion of refrigerant undergoes a loss of pressure and goes to a so-called low pressure. The second portion of refrigerant then passes through the fourth heat exchanger 104, at which it recovers heat energy, for example by cooling the power electronics and/or the electric motor of the motor vehicle.

[144] This sixth cooling mode thus makes it possible to cool the internal air flow 200 at the level of the fifth heat exchanger 105 as well as the power electronics and/or the electric motor of the motor vehicle at the level of the fourth heat exchanger 104. The heat energy recovered, both from the internal air flow 200 at the level of the fifth heat exchanger 105 and from the power electronics and/or the electric motor of the motor vehicle at the level of the fourth heat exchanger 104, is dissipated in the external air flow 300 at the level of the second heat exchanger 102.

[145] Thus, it is clear that the present architecture of the thermal management device 1 allows operation according to different operating modes but also remains simple to implement and economical.

Claims

1. Thermal management device (1) of an electric or hybrid motor vehicle, said thermal management device comprising a refrigerant circuit in which a refrigerant fluid is intended to circulate and comprising:

- a main loop (A) comprising, in the direction of circulation of the refrigerant fluid, 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 (Al) connecting a first connection point (41) arranged upstream of the second expansion device (7), between the second heat exchanger (102) and said second expansion device (7), to a second connection point (42) disposed downstream of the third heat exchanger (103), between said third heat exchanger (103) and the compressor (3),

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

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

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

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

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

2. Thermal management device (1) according to claim 1, characterized in that the first expansion device (5) is a tube orifice.

3. Thermal management device (1) according to any one of the preceding claims, characterized in that the second redirection system comprises a second shut-off valve (32) arranged on the second bypass branch (A2).

4. Thermal management device (1) according to any one of the preceding claims, characterized in that the third redirection system comprises a third shut-off valve (33) arranged on the third bypass branch (A3).

5. Thermal management device (1) according to the preceding claim, characterized in that the third shut-off valve (33) is arranged on the third bypass branch (A3) upstream of the fourth heat exchanger (104).

6. Thermal management device (1) according to any one of the preceding claims, characterized in that the fifth connection point (45) of the third bypass branch (A3) is arranged on the main branch (A) upstream of the fourth connection point (44) of the second branch branch (A2).

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

8. Thermal management device (1) according to any one of the preceding claims, characterized in that:

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

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

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

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

9. 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) disposed downstream of the second heat exchanger (102), at an eighth connection point (48) arranged upstream of the compressor (3), said fourth bypass branch (A4) comprising a fifth heat exchanger (105) and a third expansion device (9) arranged in upstream of said fifth heat exchanger (105).

10. Thermal management device (1) according to claim 9, characterized in that the fifth heat exchanger (105) is an evaporator configured to be traversed by an internal air flow (200).