Device for thermal management of an electric or hybrid motor vehicle, comprising a refrigerant circuit

Abstract

The invention relates to a device for thermal management of an electric or hybrid motor vehicle, the thermal management device comprising a refrigerant circuit (A) inside which a refrigerant is intended to circulate, the refrigerant circuit (A) comprising, in the direction of circulation of the refrigerant: - a compressor (1), - a condenser (2, 3) intended for absorbing heat energy from the refrigerant, - a pre-expansion device (4, 5) arranged directly upstream of a tank bottle (6), - a main expansion device (7, 8), and - an evaporator (9, 10) intended for transmitting heat energy to the refrigerant.

Description

Description Title of the invention: THERMAL MANAGEMENT DEVICE FOR A MOTOR VEHICLE ELECTRIC OR HYBRID INCLUDING A REFRIGERANT FLUID CIRCUIT

[0001] The invention relates to the field of electric or hybrid motor vehicles and more particularly to a thermal management device within such a vehicle.

[0002] Today's electric and hybrid vehicles increasingly include a heat transfer fluid circuit to thermally manage the batteries. Indeed, to be as efficient as possible, these batteries must remain at an optimal operating temperature. It is therefore necessary to cool them during use so that they do not exceed this optimal operating temperature excessively. Similarly, it may also be necessary to heat these batteries, for example in cold weather, so that they reach this optimal operating temperature as quickly as possible.

[0003] It is also known that electric or hybrid motor vehicles include a refrigerant circuit that contributes to the thermal management of the batteries, the cabin, and other vehicle components. In particularly hot weather, it may be necessary to significantly cool the temperature of the batteries to keep them at their optimal operating temperature. Under these conditions, the refrigerant must be able to store as much heat energy as possible from the batteries. However, this objective is difficult to achieve with current thermal management devices.

[0004] One of the aims of the present invention is therefore to at least partially remedy the drawbacks of the prior art and to propose an improved thermal management device.

[0005] The 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 in the direction of circulation of the refrigerant: a compressor, a condenser intended to absorb heat energy from the refrigerant, a pre-expansion device arranged directly upstream of a reservoir bottle, a main expansion device, and an evaporator intended to transmit heat energy to the refrigerant.

[0006] Thanks to the provision of a pre-expansion device directly upstream of the reservoir bottle, the thermal management device according to the invention advantageously makes it possible to obtain a greater reduction in temperature upstream of the reservoir bottle and therefore a greater enthalpic energy delta allowing greater absorption of heat energy at the evaporator.

[0007] By "directly upstream", it is understood in the invention that no other device having an effect on the pressure and / or temperature of the refrigerant fluid is arranged on the path of the refrigerant fluid between the two elements concerned, in this case the pre-expansion device and the reservoir bottle.

[0008] According to one embodiment of the invention, the condenser comprises an additional heat exchanger intended to be crossed by both the refrigerant fluid and an auxiliary fluid, the pre-expansion device comprising a first pre-expansion device and where the thermal management device comprises in the direction of circulation of the refrigerant fluid a main loop comprising in the direction of the refrigerant fluid the compressor, the additional heat exchanger, the first pre-expansion device arranged directly upstream of the reservoir bottle, the main expansion device and the evaporator.

[0009] According to one aspect of the invention, the main loop is a first main loop, wherein the condenser further comprises a first condenser intended to allow the heating of an additional fluid and arranged on the first main loop in the direction of circulation of the refrigerant fluid between the compressor and the additional heat exchanger.

[0010] In particular, the pre-expansion device comprises a second pre-expansion device, the thermal management device comprises a first bypass pipe connecting a first connection point, arranged on the first main loop downstream of the first condenser, to a second connection point, arranged on the first main loop between the first pre-expansion device and the reservoir bottle, and the second pre-expansion device is arranged between the first condenser and the reservoir bottle.

[0011] According to another aspect of the invention, the thermal management device further comprises: a fourth bypass pipe connecting a seventh connection point, arranged on the first main loop downstream of the reservoir bottle, to an eighth connection point, arranged on the first main loop between the first pre-expansion device and the reservoir bottle, and a fifth bypass pipe connecting a ninth connection point, arranged on the first main loop downstream of the additional heat exchanger, to a tenth connection point, arranged on the first main loop downstream of the evaporator.

[0012] In particular, the thermal management device according to the invention further comprises a sixth bypass pipe connecting an eleventh connection point, arranged on the first main loop downstream of the compressor, to a twelfth connection point, arranged on the first main loop upstream of the additional heat exchanger.

[0013] In particular, the thermal management device further comprises a third bypass pipe connecting a fifth connection point, arranged on the first main loop downstream of the first condenser, to a sixth connection point, arranged on the first main loop between the additional heat exchanger and the first pre-expansion device.

[0014] According to another aspect of the invention, the main loop is a second main loop, the condenser further comprises a first condenser intended to transmit heat energy to an internal air flow, and the thermal management device comprises in the direction of circulation of the refrigerant fluid a first bypass branch connecting a first junction point, arranged on the second main loop downstream of the compressor, to a second junction point, arranged on the second main loop upstream of the first pre-expansion device, said first bypass branch comprising the first condenser.

[0015] In particular, the thermal management device of the invention further comprises a second bypass branch connecting a third junction point, arranged on the second main loop downstream of the first condenser, to a fourth junction point, arranged on the second main loop upstream of the additional heat exchanger, said second bypass pipe comprising a secondary expansion device.

[0016] 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:

[0017] Figure 1 is a schematic representation of a thermal management device according to a first general embodiment.

[0018] Figure 2 is a schematic representation of the thermal management device of Figure 1 in a general mode of operation.

[0019] Figure 3 is a schematic representation of a thermal management device according to a second embodiment.

[0020] Figure 4 is a schematic representation of the thermal management device of Figure 3 according to a first mode and a second mode of operation.

[0021] Figure 5 is a schematic representation of the thermal management device of Figure 3 according to a third mode of operation.

[0022] Figure 6 is a schematic representation of the thermal management device of Figure 3 according to a fourth mode of operation.

[0023] Figure 7 is a schematic representation of the thermal management device of Figure 3 according to a fifth mode of operation.

[0024] Figure 8 is a schematic representation of the thermal management device of Figure 3 according to a sixth mode of operation.

[0025] Figure 9 is a schematic representation of a thermal management device according to a third embodiment.

[0026] Figure 10 is a schematic representation of a thermal management device according to a fourth embodiment.

[0027] Figure 11 is a schematic representation of the thermal management device of Figure 10 according to a seventh mode of operation.

[0028] Figure 12 is a schematic representation of the thermal management device of Figure 10 in an eighth mode of operation.

[0029] Figure 13 is a schematic representation of a thermal management device according to a fifth embodiment.

[0030] Figure 14A and Figure 14B represent two schematic representations of a thermal management device according to two variants of a sixth embodiment.

[0031] Figure 15 is a schematic representation of the thermal management device of Figures 14A, 14B according to a ninth mode of operation.

[0032] Figure 16 is a schematic representation of the thermal management device of Figures 14A, 14B according to a tenth mode of operation.

[0033] Figure 17 is a schematic representation of the thermal management device of Figures 14A, 14B according to an eleventh mode of operation.

[0034] Figure 18 is a schematic representation of a thermal management device according to a seventh embodiment.

[0035] In the different figures, identical elements bear the same reference numbers.

[0036] The following embodiments are examples. Although the description refers to one or more embodiments, this does not necessarily mean that each reference relates to the same embodiment. embodiment, or that the features apply only to a single embodiment. Single features of different embodiments may also be combined and / or interchanged to provide other embodiments.

[0037] In this description, certain elements or parameters may be indexed, such as first element or second element, as well as first parameter and second parameter, or 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 names can easily be interchanged without departing from the scope of this description. This indexing also does not imply an order in time, for example, to assess this or that criterion.

[0038] In this description, "placed upstream" means that one element is placed before another in relation to the direction of circulation of a fluid. Conversely, "placed downstream" means that one element is placed after another in relation to the direction of circulation of the fluid.

[0039] First embodiment:

[0040] Figure 1 shows a thermal management device 1 of an electric or hybrid motor vehicle according to a first embodiment. This thermal management device 1 comprises a refrigerant circuit A inside which a refrigerant is intended to circulate.

[0041] This refrigerant circuit comprises a first main loop A1 comprising, in the direction of circulation of the refrigerant, a compressor 1, a condenser 2, 3 intended to absorb heat energy from the refrigerant, a pre-expansion device 4, 5 arranged directly upstream of a reservoir bottle 6, a main expansion device 7, 8 and an evaporator 9, 10 intended to transmit heat energy to the refrigerant.

[0042] By condenser and evaporator, we mean that the heat exchangers are defined by their function and their positioning in the first main loop A1 according to the direction of circulation of the refrigerant fluid. Thus, a condenser will be positioned, in the direction of circulation of the refrigerant, in a so-called high-pressure portion of the refrigerant circuit A, in order to absorb heat energy from the refrigerant and transmit it to an auxiliary fluid, for example an air flow passing through it or another heat transfer fluid. The refrigerant is generally in the gas phase at high pressure at the inlet of the condenser and in the liquid phase or liquid-gas mixture still at high pressure at the outlet of the condenser. An evaporator will be positioned, in the direction of circulation of the refrigerant, in a so-called low-pressure portion of the refrigerant circuit A, in order to absorb heat energy from an auxiliary fluid, for example an air flow passing through it or from another heat transfer fluid, and transmit it to the refrigerant.The refrigerant fluid is generally in liquid phase or liquid-gas mixture at low pressure gas phase at the inlet of the evaporator and in gas phase still at low pressure at the outlet of the evaporator.

[0043] The reservoir bottle 6 is installed between the condenser 2, 3 and the main expansion device 7, 8 to temporarily store the refrigerant conveyed from the condenser 2, 3 to the evaporator 9, 10, so that a sufficient quantity of refrigerant is supplied to the evaporator 9, 10. The reservoir bottle 6 can in particular make it possible to eliminate the humidity and foreign substances contained in the refrigerant, and to supply the refrigerant in a completely liquid state to the expansion valve. The presence of such a reservoir bottle therefore makes it possible to improve the heat absorption efficiency at the evaporator 9, 10.

[0044] The presence of a pre-expansion device 4, 5 directly upstream of the reservoir bottle 6 makes it possible to increase the subcooling before it enters the evaporator 9, 10 and therefore to obtain a greater enthalpic energy delta between the inlet of the condenser 2, 3 and the outlet of the reservoir bottle 6. Thus, the refrigerant fluid can recover more calories during its passage through the evaporator 9, 10. As will be seen later in the description, the evaporator 10 can in particular be arranged at the level of the vehicle's batteries.

[0045] General operating mode

[0046] Figure 2 shows a general mode of operation of the thermal management device 1 of the invention shown in Figure 1.

[0047] The refrigerant is first compressed at the compressor 1, it is then in a gaseous state called high pressure and high temperature. Then the refrigerant passes into the condenser 2, 3 at which it is condensed and undergoes a loss of heat energy, and therefore of temperature, to the benefit of a first auxiliary flow (described in detail later). At the outlet of the condenser 2, 3, the refrigerant is in a state of gas / liquid mixture at high pressure. The refrigerant then passes through the pre-expansion device 4, 5 where it will undergo a first loss of pressure which causes the refrigerant to pass to a so-called intermediate pressure. This first loss of pressure makes it possible to cause a change of phase to the gaseous phase of a portion of the liquid part of the refrigerant within the reservoir bottle 6.This phase change involves a withdrawal of a portion of the heat energy from the refrigerant fluid and therefore a drop in the liquid phase enthalpy. The pressure loss is less significant here than at the main expansion device 7, 8. The refrigerant fluid then passes into the reservoir bottle 6 where it will be purified and where a phase separation is carried out so that the refrigerant fluid at the outlet of the reservoir bottle 6 is in the liquid phase. At the outlet of the reservoir bottle 6, the subcooling of the refrigerant fluid is thus increased compared to that at the outlet of the condenser 2, 3. The refrigerant fluid then passes through a main expansion device 7, 8 at which it undergoes a second pressure loss and causes the refrigerant fluid to pass from the so-called intermediate pressure to a so-called low pressure.The refrigerant then passes into the evaporator 9, 10 where it absorbs heat energy from a second auxiliary flow (described in detail later), which increases its enthalpy and causes it to pass into a gaseous state. The refrigerant finally returns to the compressor 1.

[0048] Second embodiment:

[0049] Figure 3 shows a second embodiment of the thermal management device of the invention in which the first main loop A1 is represented in thick lines.

[0050] In this second embodiment, as well as in the third and fourth embodiments illustrated in Figures 9 and 10, the condenser 2, 3 can in particular be formed of two separate heat exchangers arranged in series on the first main loop A1. These heat exchangers can thus be a first condenser 2 and an additional heat exchanger 3 configured to play the role of a second condenser.

[0051] The first condenser 2 is intended to be crossed by an auxiliary fluid and to transmit heat energy from the refrigerant fluid to this auxiliary fluid.

[0052] In the embodiments and operating modes illustrated in Figures 3 to 18, the auxiliary fluid intended to pass through the first condenser 2 is an internal air flow 100. The first condenser 2 can then be, for example, a so-called internal condenser, arranged within a heating, ventilation and air conditioning device (also called HVAC). The internal air flow 100 is sent into the passenger compartment of the vehicle.

[0053] The auxiliary fluid with which the first condenser 2 can exchange heat energy may also be a heat transfer fluid circulating within an auxiliary thermal management circuit (not shown). The first condenser may thus be, for example, a double-fluid heat exchanger. It is thus entirely possible to imagine that, in the embodiments and operating modes described below, the internal air flow 100 is replaced by a heat transfer fluid circulating within an auxiliary thermal management circuit.

[0054] Depending on the operating modes, the first condenser 2 may be a through condenser, i.e. it is not crossed by this auxiliary fluid so that the refrigerant fluid passing through it does not undergo or only slightly heat exchange with this auxiliary fluid. In the case where this auxiliary fluid is an internal air flow 100, the arrival of the latter to the first condenser 2 may be cut off, for example by a shutter or the internal air flow 100 may bypass the first condenser 2. In the case where this auxiliary fluid is a heat transfer fluid of an auxiliary thermal management circuit, the circulation of the fluid heat transfer fluid within the first condenser 2 can be stopped by stopping the additional thermal management circuit or by bypassing the first condenser 2.

[0055] Likewise, the additional heat exchanger 3 is intended to be crossed by both the refrigerant fluid and an auxiliary fluid. Depending on the operating modes, the additional heat exchanger 3 may in particular be configured to transfer heat energy from the auxiliary fluid to the refrigerant fluid, thus heating the refrigerant fluid, it then plays the role of an evaporator. The additional heat exchanger 3 may also be configured to transfer heat energy from the refrigerant fluid to the auxiliary fluid, thus cooling the refrigerant fluid, it then plays the role of a second condenser. This auxiliary fluid may in particular be of the same nature or distinct from the auxiliary fluid passing through the first condenser 2.

[0056] In the embodiments and operating modes illustrated in Figures 3 to 18, the auxiliary fluid intended to pass through the additional heat exchanger 3 is a first heat transfer fluid circulating within a first heat transfer fluid circuit B1. The additional heat exchanger 3 can thus be a double-fluid heat exchanger arranged jointly on the refrigerant circuit A and on a first heat transfer fluid circuit B1 in which a first heat transfer fluid circulates. This first heat transfer fluid can be water or glycolated water. The first heat transfer fluid circuit B1 can in particular comprise one or more parallel circuits or circuits joining at the additional heat exchanger 3 and arranged at the front of the vehicle and / or at the vehicle batteries and / or at an electric motor and / or at the power electronics.The first heat transfer fluid circuit B1 may in particular also comprise at least one radiator arranged on the front of the motor vehicle in order to evacuate heat energy with the external air.

[0057] The auxiliary fluid with which the additional heat exchanger can exchange heat energy can also be an air flow passing through the latter. This variant is not shown in Figures 3 to 18. It is thus entirely possible to imagine that, in the embodiments and operation described below, the first heat transfer fluid circulating within the first heat transfer fluid circuit B1, is replaced by an air flow.

[0058] So that a pre-expansion device 4, 5 is always arranged directly upstream of the reservoir bottle 6 regardless of the operating mode, the thermal management device, and more particularly its main loop A1, may comprise a first pre-expansion device 4 arranged between the additional heat exchanger 3 and the reservoir bottle 6 and a second expansion device 5 arranged between the first condenser 2 and the reservoir bottle 6, as described in detail below.

[0059] The pre-expansion device 4, 5 may be an expansion device with a variable opening diameter allowing the passage of the refrigerant fluid without loss of pressure when it is open to its maximum diameter. Thus, in particular, when the internal condenser 2 does not exchange or exchanges little heat energy with the auxiliary fluid, the second pre-expansion device 5 does not impact the state of the fluid before its arrival at the additional heat exchanger 3. An alternative not shown may also be that this pre-expansion device 4, 5 can be bypassed.

[0060] As shown in this figure 3, the refrigerant circuit A may in particular be an air conditioning circuit where the evaporator 9, 10 comprises a first heat exchanger 9 intended to be crossed by the internal air flow 100. The first heat exchanger 9 may be arranged within the heating, ventilation and air conditioning device 110, for example upstream of the first condenser 2 in the direction of the internal air flow 100. In this case, the second auxiliary fluid corresponds to the internal air flow 100. Upstream of the first heat exchanger 9 is arranged a first main expansion device 7.

[0061] The refrigerant circuit A can thus comprise a first main loop A1 comprising, in the direction of circulation of the refrigerant, the compressor 1, the first condenser 2, the additional heat exchanger 3, the first pre-expansion device 4, the reservoir bottle 6, the first main expansion device 7, and the first heat exchanger 9.

[0062] In particular, the first main loop A1 may include an interchange internal heat exchanger 11 arranged jointly on a first portion 21 and a second portion 22 of the first main loop A1 in order to obtain an exchange of calories between these two portions. The first portion 21 is arranged between the reservoir bottle 6 and the main expansion device 7, 8, and the second portion 22 is arranged between the evaporator 9, 10 and the compressor 1. This exchange of calories makes it possible to improve the coefficient of performance of the refrigerant circuit A.

[0063] In order to be a reversible air conditioning circuit, the refrigerant circuit A may also comprise a first bypass line c1, shown in thin lines, connecting a first connection point 31, arranged on the first main loop A1 downstream of the first condenser 2, to a second connection point 32, arranged on the first main loop A1 between the first pre-expansion device 4 and the reservoir bottle 6. This first bypass line c1 allows the refrigerant A1 to bypass the additional heat exchanger 3 and to connect the first condenser 2 and the reservoir bottle 6 together. The second pre-expansion device 5 may be arranged at the level of the first main loop A1 upstream of the first connection point 31, as shown, or within the first bypass line c1.Thus, depending on the operating mode, whether the refrigerant arrives at the reservoir bottle 6 from the first condenser 2 or from the additional heat exchanger 3, it always passes through a pre-expansion device 4, 5 arranged directly upstream of the reservoir bottle 6.

[0064] By reversible, it is meant that the refrigerant circuit A1 is capable of being able to cool the internal air flow 100 or heat it as required. The internal air flow 100 is notably cooled via the first heat exchanger 9 in a cooling mode of the thermal management device of the invention.

[0065] As shown in Figure 3, the refrigerant circuit A1 may comprise a first device for controlling the circulation of the refrigerant fluid from the first main loop A1 to the first bypass pipe c1 at the first connection point 31. As shown, this first control device may in particular be a three-way valve 51 arranged at the first connection point 31. Alternatively, the first control device may comprise two shut-off valves each arranged downstream of the first connection point 31 on the first main loop A1 and on the first bypass pipe c1, respectively.

[0066] As also shown in Figure 3, the refrigerant circuit A1 may comprise a second device for controlling the circulation of the refrigerant fluid from the first bypass line c1 to the first main loop A1 at the second connection point 32. As shown, the second control device may be a non-return valve 62 arranged on the first main loop A1 downstream of the first pre-expansion device 4, and more precisely between the second connection point 32 and the first pre-expansion device 4. This non-return valve 62 makes it possible to prevent the refrigerant fluid passing through the first bypass line c1 from being directed to the first pre-expansion device 4. Alternatively, the second control device may be a shut-off valve.

[0067] In order for the refrigerant circuit A to be reversible and to allow several operating modes, the evaporator 9, 10 may comprise a second heat exchanger 10. This second heat exchanger 10 may in particular allow thermal management and more particularly the cooling of the batteries of the electric or hybrid motor vehicle. Like the additional heat exchanger 3, the second heat exchanger may also be arranged jointly on the refrigerant circuit A and a second heat transfer fluid circuit B2 within which a second heat transfer fluid is intended to circulate in order to allow heat exchange between them.The second heat fluid circuit B2 may in particular comprise one or more parallel circuits or circuits joining at the level of the additional heat exchanger 3 and arranged at the level of the front face of the vehicle and / or at the level of the electric motor and / or at the level of the power electronics.

[0068] As shown in Figure 3, the second heat exchanger 10 can be arranged on a second bypass line c2 of the refrigerant circuit A, shown in thin lines. The second bypass line c2 connects a third connection point 33, arranged on the first main loop A1 between the reservoir bottle 6 and the first expansion device main 7, to a fourth connection point 34, arranged on the first main loop A1 downstream of the first heat exchanger 9. The second bypass line c2 comprises, in the direction of circulation of the refrigerant fluid, a second main expansion device 8 arranged upstream of the second heat exchanger 10.

[0069] In particular, and as shown in FIG. 3, the third connection point 33 is arranged between the internal heat exchanger 11 and the first main expansion device 7, and the fourth connection point 34 is arranged between the first non-return valve 61 and the first heat exchanger 9.

[0070] As shown in Figure 3, the refrigerant circuit may comprise a third device for controlling the circulation of the refrigerant fluid from the first main loop A1 to the second bypass line c2. This third control device may in particular be a three-way valve arranged at the third connection point 33. Alternatively, and as shown, the third control device may comprise two shut-off valves 53, 54, each arranged downstream of the third connection point 33 on the first main loop A1 and on the second bypass line c2, respectively. Alternatively, the third control device may correspond to the main expansion device 7, 8, the opening of which may be adjustable so as to allow or prevent the refrigerant fluid from passing through them.

[0071] In particular, the first main loop A1 may comprise a first non-return valve 61 arranged downstream of the first heat exchanger 9 and the second bypass pipe c2 may comprise a second non-return valve 63 arranged downstream of the second heat exchanger 10. More specifically, the first non-return valve 61 is arranged upstream of the fourth connection point 34 and makes it possible to prevent the refrigerant fluid leaving the second heat exchanger 10 from rising into the first exchanger 9. Furthermore, the second non-return valve 63 may be arranged between the second heat exchanger 10 and the fourth connection point 34. This second non-return valve 63 makes it possible to prevent the refrigerant fluid leaving the first heat exchanger 9 from reaching the second heat exchanger 10.

[0072] First mode of operation

[0073] In the various representations of the operating modes of the thermal management device of the invention, the portions of the refrigerant circuit A1 in which the refrigerant does not circulate are represented in dotted lines.

[0074] Figure 4 illustrates an operating mode in which the refrigerant circuit A is in a mode of cooling only the internal air flow 100 via the first heat exchanger 9.

[0075] In this operating mode, the first control device, here the three-way valve 51, is configured to close access to the first bypass line c1 so that the refrigerant circulates directly from the first condenser 2 to the dual-fluid heat exchanger 3. The third control device is configured to close access to the second bypass line c2 so that all the refrigerant coming from the reservoir bottle 6 passes through the first heat exchanger 9.

[0076] In this operating mode, the refrigerant fluid leaves the compressor 1 at high pressure and passes successively through the first condenser 2, optionally the second subcooling expansion device 5 if it is arranged on the first main loop A1, and the first connection point 31 where it is directed towards the additional heat exchanger 3 where it always arrives at high pressure and without having exchanged heat energy by passing through the first condenser 2. For this purpose, the first condenser 2 is a pass-through, that is to say that it is not crossed by the internal air flow 100 so that the refrigerant fluid passing through it does not undergo or only little heat exchange with the internal air flow 100. The second pre-expansion device 5 has a maximum opening in the case where the latter is placed on the first main loop A1.

[0077] By passing through the additional heat exchanger 3, the refrigerant undergoes a loss of heat energy to the benefit of the first heat transfer fluid of the first heat transfer fluid circuit B1. The heat energy absorbed by the first heat transfer fluid of the first heat transfer fluid circuit B1 can be released into the outside air, for example by means of a radiator arranged within the first heat fluid circuit B1 placed on the front of the motor vehicle. The refrigerant then passes through the first pre-expansion device 4 where it undergoes a first pressure loss so as to reach a so-called intermediate pressure. The refrigerant then joins the reservoir bottle 6 via the second connection point 32. At the outlet of the reservoir bottle 6, the refrigerant passes through the first portion 21 of the internal heat exchanger 11 where it will undergo a third loss of heat energy to the benefit of the refrigerant passing through the second portion 22. The refrigerant continues towards the third connection point 33 where it is directed towards the first main expansion device 7 at which it undergoes a second pressure loss, greater than the first, in order to reach low pressure.The refrigerant then passes into the first heat exchanger 9 where it absorbs heat energy from the internal air flow 100. The internal air flow 100 is thus cooled. At the outlet of the first heat exchanger 9, the refrigerant reaches the fourth connection point 34. The refrigerant then continues to the second portion 22 of the internal heat exchanger 11 where it absorbs heat energy from the first portion 21. The refrigerant then returns to the compressor 1.

[0078] Second mode of operation

[0079] Figure 4 also illustrates a second mode of operation in which the refrigerant circuit A is in a serial defogging mode of the internal air flow 100.

[0080] As for the first mode of operation, the first control device is configured to close access to the first bypass line c1, and the third control device is configured to close access to the second bypass line c2.

[0081] In order to obtain demisting of the internal air flow 100, the latter is first cooled in order to condense the humidity present within it, then it is heated before reaching the passenger compartment and in particular the windshield.

[0082] For this purpose, in this operating mode, the internal condenser 2 and the first heat exchanger 9 are both crossed by internal air flow 100. Thus, the refrigerant fluid leaving the compressor 1 and passing through the first condenser 2 undergoes a first heat loss to the benefit of the internal air flow 100. The internal air flow 100 is thus reheated before reaching the passenger compartment. The refrigerant continues towards the additional heat exchanger 3. In the case, as shown, the second pre-expansion device 5 is arranged on the first main loop A1, the latter causes the refrigerant to undergo a first pressure loss. In the additional heat exchanger 3, the refrigerant absorbs heat energy from the first heat transfer fluid of the first heat transfer fluid circuit B1 because it has already given up heat energy via the first condenser 2 and has undergone a first pressure loss by passing through the second pre-expansion device 5. The refrigerant then passes through the first pre-expansion device 4 where it possibly undergoes a second pressure loss before joining the reservoir bottle 6.The rest of this mode of operation is identical to that of the first mode of operation.

[0083] Thus, this second mode of operation uses the additional heat exchanger 3 as an evaporator.

[0084] Third mode of operation

[0085] Figure 5 illustrates a third operating mode in which the refrigerant circuit A is in a mode of cooling only the batteries or the second heat transfer fluid via the second heat exchanger 10.

[0086] In this operating mode, the first device is configured to close access to the first bypass line c1, and the third control device is configured to open access to the second bypass line c2 and close access to the first heat exchanger 9.

[0087] In this operating mode, the refrigerant reaches the additional heat exchanger 3 without loss of pressure or temperature. For this purpose, the first condenser 2 is a pass-through condenser, i.e. it is not crossed by the internal air flow 100 so that the refrigerant passing through it undergoes little or no heat exchange with the internal air flow 100. The second pre-expansion device 5 has a maximum opening in the case where the latter is placed on the first main loop A1.

[0088] This mode of operation is identical to the first mode of operation except between the third connection point 33 and the fourth connection point 34. Here, the refrigerant fluid is directed from the third connection point 33 to the second main expansion device 8 where it will undergo a second pressure loss, greater than the first. It then passes into the second heat exchanger 10 where it will absorb heat energy released by the batteries or the second heat transfer fluid. At the outlet of the second heat exchanger 10, the refrigerant fluid passes through the non-return valve 63, and joins the internal heat exchanger 11 via the fourth connection point 34.

[0089] Fourth mode of operation

[0090] Figure 6 illustrates a fourth operating mode corresponding to the combination of the first and third operating modes, where the refrigerant circuit A is in a mode of cooling both the internal air flow 100 via the first heat exchanger 9 and both the batteries or the second heat transfer fluid via the second heat exchanger 10.

[0091] As a result, the refrigerant circulates in parallel: - in the first heat exchanger 9 in order to absorb heat energy from the internal air flow 100, and - in the second bypass line c2 in order to cool the batteries.

[0092] For this purpose, the second control device is configured to allow the refrigerant to pass through the first 9 and the second 10 heat exchanger.

[0093] Thus this mode of operation is identical to the first and third embodiments for the portions of the refrigerant circuit A where the refrigerant circulates, respectively.

[0094] Fifth mode of operation

[0095] Figure 7 illustrates a fifth reverse operating mode, in which the refrigerant circuit A is in a mode of heating the internal air flow 100 via the first condenser 2 and recovering heat from the batteries or the second heat transfer fluid via the second heat exchanger 10.

[0096] In this mode of operation, the first control device is configured to close access to the additional heat exchanger 3 and open access to the first bypass line c1, and the third control device is configured to open access to the second bypass line c2 and close access to the first heat exchanger 9.

[0097] In this operating mode, the refrigerant fluid leaving the compressor 1 passes through the first condenser 2 and there undergoes a heat loss to the benefit of the internal air flow 100. The internal air flow 100 is thus reheated before reaching the passenger compartment. The refrigerant fluid continues towards the second pre-expansion device 5 at which it undergoes a first pressure loss. At the connection point 31, the refrigerant fluid is directed towards the first bypass line c1, then reaches the reservoir bottle 6 via the second connection point 32. At the outlet of the reservoir bottle 6, the refrigerant fluid in the subcooled liquid phase passes through the internal heat exchanger 11 at the first portion 21 where it will undergo a second loss of heat energy to the benefit of the refrigerant fluid passing through the second portion 22.The refrigerant fluid continues towards the third connection point 33 where it is directed towards the second main expansion device 8 where it will undergo a second pressure loss, greater than the first. It then passes into the second heat exchanger 10 where it will absorb heat energy from the batteries or from the second heat transfer fluid and pass into the gas phase. At the outlet of the second heat exchanger 10, the refrigerant fluid joins the internal heat exchanger 11 via the fourth connection point 34. At the second portion 22 of the internal heat exchanger 11, the refrigerant fluid absorbs heat energy from the first portion 21. The refrigerant fluid then returns to the compressor 1.

[0098] Sixth mode of operation

[0099] Figure 8 illustrates a sixth mode of operation in which the refrigerant circuit A is in a demisting mode in parallel with the internal air flow 100.

[0100] In this embodiment, the first control device is configured to close access to the additional heat exchanger 3 and open access to the first bypass pipe c1, and the second control device control is configured to allow refrigerant to pass through the first and second heat exchangers.

[0101] This operating mode is identical to the fifth operating mode except that the refrigerant circulates in parallel: - in the first heat exchanger 9 in order to absorb heat energy from the internal air flow 100, and - in the second bypass line c2 in order to recover heat from the batteries or from the second heat fluid circuit B2 by the second heat exchanger 10.

[0102] Like the second operating mode, the passage through the first heat exchanger 9 makes it possible to absorb heat energy from the internal air flow 100 in order to condense the humidity upstream of its heating by the first condenser 2.

[0103] Third embodiment

[0104] Figure 9 shows a third embodiment of the thermal management device of the invention.

[0105] In this third embodiment we find a first main loop A1, in thick lines, identical to that of the second embodiment of figures 3 to 8.

[0106] The first bypass line c1 of the second embodiment is here replaced by a third bypass line c3 connecting a fifth connection point 35, arranged on the first main loop A1 downstream of the first condenser 2, to a sixth connection point 36, arranged on the first main loop A1 upstream of the first pre-expansion device 4, and more precisely between the additional heat exchanger 3 and the first pre-expansion device 4. Thus in this embodiment, it is not necessary to provide the second pre-expansion device 5 when the refrigerant does not pass through the additional heat exchanger 3.

[0107] A secondary expansion device 12 can be arranged on the main loop A1 upstream of the additional heat exchanger 3, and more precisely between the fifth connection point 35 and the heat exchanger additional heat 3. This secondary expansion device 12 may be an expansion device with a variable opening diameter allowing the passage of the refrigerant fluid without loss of pressure when it is open to its maximum diameter. An alternative may also be that this secondary expansion device 12 can be bypassed.

[0108] The main loop A1 may comprise a non-return valve 65 arranged between the first condenser 2 and the ninth connection point 39, and making it possible to prevent a reflux of the refrigerant fluid towards the first condenser 2.

[0109] The main loop A1 may comprise a fourth device for controlling the circulation of the refrigerant fluid from the first main loop A1 to the third bypass pipe c3 at the fifth connection point 35. This fourth control device may in particular be a stop valve (not shown) arranged on the main branch A1 downstream of the fifth connection point 35. Alternatively, it is the secondary expansion device 12 which comprises a flow stopping function, like the main expansion devices 7, 8.

[0110] The first main loop A1 may here comprise a fifth device for controlling the circulation of the refrigerant fluid from the first main loop A1 to the third bypass pipe c3 at the sixth connection point 36. This fifth control device may in particular be a three-way valve 60 arranged, as shown, at the sixth connection point 36. Alternatively, the fifth control device may comprise two shut-off valves each arranged upstream of the sixth connection point 36 on the first main loop A1 and on the third bypass pipe c3, respectively.

[0111] The six modes of operation described in relation to the second embodiment apply similarly to the third embodiment, except that: - for the first four operating modes, the fourth control device is configured to open access to the additional heat exchanger 3 and the fifth control device is configured to close access to the third bypass line c3 and open access to the first pre-expansion device 4 and to the additional heat exchanger 3, - for the first, second and third operating modes, the secondary expansion device 12 is through, that is to say that it has a maximum opening so as to be crossed by the refrigerant fluid with a minimal pressure loss, like the second pre-expansion device 5 in certain operating modes of the second embodiment, - for the fifth and sixth operating modes, the refrigerant flow passes through the third bypass line c3. For this purpose, the fifth control device is configured to open access to the third bypass line c3 and close access to the additional heat exchanger 3 so that the refrigerant flows directly from the first condenser 2 to the first subcooling expansion device 4.

[0112] Fourth embodiment

[0113] Figure 10 shows a fourth embodiment of the thermal management device of the invention.

[0114] This fourth embodiment can be used for the different embodiments described in relation to the second embodiment and allows new operating modes where the additional heat exchanger 3 acts as an evaporator. For this purpose, this embodiment takes up the portions of the refrigerant circuit A of the second embodiment and further comprises a fourth and a fifth bypass line c4, c5, in thin line.

[0115] The fourth bypass line c4 connects a seventh connection point 37, arranged on the first main loop A1 downstream of the reservoir bottle 6, to an eighth connection point 38, arranged on the first main loop A1 between the first pre-expansion device 4 and the reservoir bottle 6. In particular, the third bypass point 33 is arranged downstream of the internal heat exchanger 11, and upstream of the first 7 and the second 8 main expansion devices. Alternatively, the seventh connection point 37 is the same as the third connection point 33. In particular, the eighth connection point 38 is located upstream of the connection point 32 and more particularly upstream of the non-return valve 62.

[0116] The fourth bypass line c4 may comprise a non-return valve 64 making it possible to prevent the refrigerant fluid coming from the first pre-expansion device 4 from bypassing the reservoir bottle 6 by passing through the fourth bypass line c4.

[0117] The fifth bypass line c5 connects a ninth connection point 39, arranged on the first main loop A1 downstream of the additional heat exchanger 3, to a tenth connection point 40, arranged on the first main loop A1 downstream of the evaporator 9, 10. In particular, the tenth connection point 40 is arranged between the evaporator 9, 10 and the internal heat exchanger 11. In particular again, the tenth connection point 40 is arranged between the fourth connection point 34 and the internal heat exchanger 11.

[0118] The third control device may comprise a stop valve 55 arranged on the fourth bypass line c4 downstream of the seventh connection point 37 in order to allow or not the circulation of the refrigerant fluid in the fourth bypass line c4. Alternatively, the first pre-expansion device 4 may be configured to be able to stop a flow going up towards the additional heat exchanger 3.

[0119] The fifth bypass line c5 may comprise a shut-off valve 58 in order to prevent the refrigerant fluid leaving the evaporator 9, 10 from flowing back up to the double-fluid exchanger 3 in the first six embodiments.

[0120] Seventh mode of operation

[0121] Figure 11 illustrates a seventh mode of operation (for the fourth embodiment of Figure 10) in which the refrigerant circuit A is in a mode of heating the internal air flow 100 via the first condenser 2 and recovering heat from the first heat fluid circuit B1 via the additional heat exchanger 3.

[0122] Thus, in this operating mode, the additional heat exchanger 3 is not crossed by the refrigerant upstream of the reservoir bottle 6, but downstream. The first pre-expansion device 4 therefore does not have the role of causing the refrigerant to undergo a pressure loss. upstream of the reservoir bottle 6, but to expand the refrigerant fluid so that it passes under low pressure before passing through the additional heat exchanger 3 and so that it does not absorb heat energy coming from the first heat fluid of the first heat transfer fluid circuit B1.

[0123] To this end, - the first control device is configured to redirect the refrigerant fluid from the first condenser 2 to the first bypass line c1 and close access to the additional heat exchanger 3 to the refrigerant fluid from the first condenser 2, and - the third control device is configured on the one hand to allow the refrigerant fluid from the reservoir bottle 6 to pass into the fourth bypass line c4 and on the other hand to block the refrigerant fluid so that it does not circulate towards the first heat exchanger 9 and through the second bypass line c2.

[0124] In this operating mode, the refrigerant leaving the compressor 1 passes through the first condenser 2 and there undergoes a first loss of heat energy to the benefit of the internal air flow 100. The internal air flow 100 is thus heated before reaching the passenger compartment. The refrigerant continues towards the second pre-expansion device 5 at which it undergoes a first pressure loss. At the connection point 31, the refrigerant is directed towards the first bypass line c1, then reaches the reservoir bottle 6 via the second connection point 32. At the outlet of the reservoir bottle 6, the refrigerant is entirely in liquid form and passes through the internal heat exchanger 11 at the first portion 21 where it will undergo a second loss of heat energy to the benefit of the refrigerant passing through the second portion 22.The refrigerant continues to the seventh connection point 37 where it is directed to the fourth bypass line c4. The refrigerant goes to the first pre-expansion device 4. The refrigerant is prevented from returning to the reservoir bottle 6 at the non-return valve 62 by the higher pressure exerted there by the refrigerant arriving from the first bypass line c1. At the first pre-expansion device 4, the refrigerant undergoes a second pressure loss. The refrigerant then passes into the additional heat exchanger 3 where it will absorb. the heat energy from the first heat fluid of the first heat transfer fluid circuit B1. The refrigerant fluid leaving the additional heat exchanger 3 arrives at the ninth connection point 39 where it is directed to the fifth bypass line c5 since the first control device closes access to the exchanger 3. The refrigerant fluid then joins the first main loop A1 at the tenth connection point 40, then is directed to the internal heat exchanger 11 by the action of the non-return valves 61, 63 which prevent it from rising to the first 9 and the second 10 heat exchanger. At the second portion 22, it absorbs heat energy from the first portion 21. The refrigerant fluid then returns to the compressor 1.

[0125] Eighth mode of operation

[0126] Figure 12 illustrates an eighth operating mode (for the fourth embodiment of Figure 10) in which the refrigerant circuit A is in a demisting mode in parallel with the internal air flow 100. This operating mode therefore represents an alternative to the sixth operating mode of Figure 8.

[0127] Here, instead of the second heat exchanger 10 recovering heat energy in parallel with the first heat exchanger 9, it is the additional heat exchanger 3 which plays this role.

[0128] For this purpose, the refrigerant circulates in parallel: - in the first heat exchanger 9 in order to absorb heat energy from the internal air flow 100, and - in the fourth c4 and fifth c5 bypass columns in order to recover heat from the first heat transfer fluid of the first heat transfer fluid circuit B1 by the additional heat exchanger 3.

[0129] Thus, this mode of operation is similar to the seventh mode of operation with the difference that the refrigerant fluid at the seventh connection point 37 is split into two parts where a first part is directed towards the fourth bypass line c4 and a second part is directed towards the third connection point 33 in the direction of the first main expansion device 7 and the first heat exchanger 9. The two parts of the refrigerant fluid then join at the tenth connection point 40, then pass through the internal heat exchanger 11 and return to compressor 1.

[0130] In this mode of operation: - the first control device is configured to redirect the refrigerant fluid from the first condenser 2 to the first bypass line c1 and close access to the additional heat exchanger 3 to the refrigerant fluid from the first condenser 2, and - the second control device is configured on the one hand to allow the refrigerant fluid from the reservoir bottle 6 to pass into the fourth bypass line c4 and towards the first heat exchanger 9 and on the other hand to block the refrigerant fluid so that it does not circulate through the second bypass line c2.

[0131] Fifth embodiment

[0132] Figure 13 illustrates the fifth embodiment.

[0133] This fifth embodiment corresponds to a variant of the fourth embodiment of figure 10 comprising a sixth bypass pipe making it possible to bypass the first condenser 2 for the cooling operating modes (first, third and fourth operating mode).

[0134] This fifth embodiment therefore comprises a sixth bypass pipe c6 connecting an eleventh connection point 81, arranged on the first main loop A1 downstream of the compressor 1, to a twelfth connection point 82, arranged on the first main loop A1 upstream of the additional heat exchanger 3. More precisely, the eleventh connection point 81 is arranged between the compressor 1 and the first condenser 2, and the twelfth connection point 82 is arranged between the first connection point 31 and the dual-fluid exchanger 3. In particular, the twelfth connection point is arranged upstream or downstream of the ninth connection point 39. In an alternative, the twelfth connection point is arranged on the third bypass pipe c5, in particular upstream of the shutoff valve 58.

[0135] As shown in Figure 13, the refrigerant circuit may include a sixth device for controlling the circulation of the refrigerant fluid from the first main loop A1 to the sixth bypass line c6 at the eleventh connection point 81. This sixth control device may in particular be a three-way valve arranged at the eleventh connection point 81. Alternatively, and as shown, the sixth control device may comprise two shut-off valves 56, 57, each arranged downstream of the eleventh connection point 81 on the first main loop A1 and on the sixth bypass line, respectively. The shut-off valves 56, 57 may have an electronically controlled variable opening.

[0136] Regarding the cooling embodiments, the refrigerant leaving the compressor 1 arrives at the eleventh connection point 81 where it is directed to the sixth bypass line c6. The refrigerant then reaches the additional heat exchanger 3 via the twelfth connection point 82. The rest of the respective implementation of these operating modes is identical to that described in connection with the second embodiment.

[0137] Furthermore, this fifth mode of realizing the second mode of operation, and the fifth to the eighth embodiments in a manner identical to that described above.

[0138] Sixth embodiment

[0139] A sixth and a seventh embodiment are shown in Figures 14A to 18 and comprise a second main loop A2, in thick line, which directly connects the compressor 1 to the additional heat exchanger 3.

[0140] The second main loop A2 comprises, in the direction of circulation of the refrigerant fluid, the compressor 1, the additional heat exchanger 3, the first pre-expansion device 4, the reservoir bottle 6 and the evaporator 9, 10. In particular, the second main loop A2 may also comprise the internal heat exchanger 11.

[0141] Figures 14A, 14B represent two variants (A and B) of the sixth embodiment where the second main loop A2 comprises, downstream of the reservoir bottle 6, the first main expansion device 7 and the first heat exchanger 9. The two variants differ in terms of the elements used for the first pre-expansion device 4.

[0142] In a first variant, shown in Figure 14A, the pre-expansion device 4 is identical to that used in the first five embodiments.

[0143] Here, and as shown in this figure 14A, the refrigerant circuit A may comprise a first bypass branch d1 connecting a first junction point 41, arranged on the second main loop A2 downstream of the compressor 1, to a second junction point 42, arranged on the second main loop A2 between the additional heat exchanger 3 and the first pre-expansion device 4.

[0144] As shown in Figure 14A, the refrigerant circuit may comprise a seventh device for controlling the circulation of the refrigerant fluid from the second main loop A2 to the first bypass branch d1 at the first junction point 41. This seventh control device may in particular be a three-way valve arranged at the first junction point 41. Alternatively, and as shown, the seventh control device may comprise two shutoff valves 96, 97, each arranged downstream of the first junction point 41 on the second main loop A2 and on the first bypass branch d1, respectively. The shutoff valves 96, 97 may have an electronically controlled variable opening.

[0145] As also shown, the refrigerant circuit may comprise an eighth device for controlling the circulation of the refrigerant fluid from the second main loop A2 to the first bypass branch d1 at the second junction point 42. In the first variant of this sixth embodiment, this eighth control device may in particular be a three-way valve 59, as shown in FIG. 14A, arranged at the second junction point 42. Alternatively, the eighth control device may comprise two shutoff valves, one arranged downstream of the second junction point 42 on the second main loop A2 and the other arranged upstream of the second junction point 42 on the first bypass branch d1, respectively.

[0146] According to the second variant of the sixth embodiment shown in Figure 14B, the pre-expansion device 4 is formed by two non-return valves preprogrammed 71, 72, arranged upstream of the second junction point 42 on the first branch d1 and on the second main loop A2, respectively.

[0147] Thus, here the eighth control device can correspond to the two pre-programmed non-return valves with expansion 71, 72.

[0148] The other elements described in relation to the first variant are identical in the second variant.

[0149] As shown in Figures 14A and 14B, the refrigerant circuit A may comprise the second bypass line c2 comprising the second main expansion device 8 and the second heat exchanger 10.

[0150] The mode of parallel defogging of the internal air flow 100 (sixth operating mode) and the mode of heating the internal air flow 100 via the first condenser 2 and recovering the heat from the second heat transfer fluid (fifth operating mode) described in relation to the third embodiment apply in a similar manner to the first variant of this sixth embodiment.

[0151] Briefly, for the mode of heating the internal air flow 100 via the first condenser 2 and recovering the heat from the second heat transfer fluid, the refrigerant fluid leaving the compressor 1 first arrives at the first junction point 41 where it is directed towards the internal exchanger 2 which it passes through and there undergoes a heat loss to the benefit of the internal air flow 100. The internal air flow 100 is thus heated before reaching the passenger compartment. The refrigerant fluid continues towards the second junction point 42 where it is directed towards the first pre-expansion device 4 at which it undergoes a first pressure loss. Then the refrigerant fluid reaches the reservoir bottle 6.At the outlet of the reservoir bottle 6, the refrigerant in the subcooled liquid phase passes through the internal heat exchanger 11 at the level of the first portion 21 where it will undergo a second loss of heat energy to the benefit of the refrigerant passing through the second portion 22. The refrigerant continues towards the third connection point 33 where it is directed towards the second main expansion device 8 where it will undergo a second pressure loss, greater than the first. It then passes into the second exchanger. heat exchanger 10 where it will absorb heat energy from the batteries or from the second heat transfer fluid and pass into the gas phase. At the outlet of the second heat exchanger 10, the refrigerant fluid joins the internal heat exchanger 11 via the fourth connection point 34. At the second portion 22 of the internal heat exchanger 11, the refrigerant fluid absorbs heat energy from the first portion 21. The refrigerant fluid then returns to the compressor 1.

[0152] Briefly, for the parallel defogging mode of the internal air flow 100, the latter is identical to the heating mode of the internal air flow 100 described above with the difference that the refrigerant fluid circulates in parallel: - in the first heat exchanger 9 in order to absorb heat energy from the internal air flow 100, and - in the second bypass line c2 in order to recover heat from the batteries or from the second heat fluid circuit B2 by the second heat exchanger 10.

[0153] Concerning the second variant of the sixth embodiment, the different operating modes described in relation to the first variant are identical with the difference that the first expansion is ensured by one of the stop valves 71, 72 upstream of the second junction point 42, depending on the operating mode.

[0154] Ninth mode of operation

[0155] Figure 15 illustrates an operating mode (for the sixth operating mode of Figures 14A and 14B) in which the refrigerant circuit A is in a mode of cooling only the internal air flow 100 via the first heat exchanger 9.

[0156] In this mode of operation, the fifth and eighth control devices are configured to close access to the first branch d1.

[0157] In this operating mode, the refrigerant fluid first arrives at the first junction point 41 where it is directed to the additional heat exchanger 3. At the additional heat exchanger 3, it transfers heat energy to the first heat fluid of the first heat transfer fluid circuit B1. It then joins the first pre-expansion device 4 via the second junction point 42. At the first pre-expansion device 4 it undergoes a first pressure loss. The refrigerant then joins the reservoir bottle 6. At the outlet of the reservoir bottle 6, the refrigerant passes through the first portion 21 of the internal heat exchanger 11 where it will undergo a third loss of heat energy to the benefit of the refrigerant passing through the second portion 22. The refrigerant continues towards the third connection point 33 where it is directed towards the first main expansion device 7 at which it undergoes a second pressure loss, greater than the first, in order to arrive at low pressure. The refrigerant then passes into the first heat exchanger 9 where it absorbs heat energy from the internal air flow 100. The internal air flow 100 is thus cooled.At the outlet of the first heat exchanger 9, the refrigerant fluid reaches the fourth connection point 34. The refrigerant fluid then continues towards the second portion 22 of the internal heat exchanger 11 where it absorbs heat energy from the first portion 21. The refrigerant fluid then returns to the compressor 1.

[0158] Tenth mode of operation

[0159] Figure 16 illustrates a tenth operating mode (for the sixth operating mode of Figures 14A and 14B) in which the refrigerant circuit A is in a mode of cooling only the batteries via the second heat exchanger 9.

[0160] This operating mode is identical to the ninth operating mode except between the third connection point 33 and the fourth connection point 34. Here, the refrigerant is directed from the third connection point 33 to the second main expansion device 8 where it will undergo a second pressure loss, greater than the first. It then passes into the second heat exchanger 10 where it will absorb heat energy released by the batteries. At the outlet of the second heat exchanger 10, the refrigerant joins the internal heat exchanger 11 via the fourth connection point 34 before returning to the compressor 1.

[0161] Eleventh mode of operation

[0162] Figure 17 illustrates an eleventh operating mode (for the sixth operating mode of Figures 14A and 14B) corresponding to the combination of the ninth and tenth operating modes, where the refrigerant circuit A is in a mode of cooling both the internal air flow 100 and both the batteries.

[0163] As a result, the refrigerant circulates in parallel: - in the first heat exchanger 9 in order to absorb heat energy from the internal air flow 100, and - in the second bypass line c2 in order to cool the batteries.

[0164] For this purpose, the second control device is configured to allow the refrigerant to pass through the first and second heat exchangers 9, 10.

[0165] Seventh embodiment

[0166] Figure 18 illustrates a seventh embodiment of the invention.

[0167] This seventh embodiment is a variant of the sixth embodiment and therefore incorporates the elements thereof to which is added a second branch d2 connecting a third junction point 43, arranged on the first branch d1 downstream of the first condenser 2, to a fourth junction point 44, arranged on the second main loop A2 upstream of the additional heat exchanger 3.

[0168] In this embodiment, the first bypass branch d1 may comprise the non-return valve 65 arranged here between the first condenser 2 and the third connection point 33. Furthermore, the second bypass branch d2 may comprise the secondary expansion device 12.

[0169] All of the operating modes described in relation to the sixth embodiment apply to this seventh embodiment. Furthermore, this seventh embodiment allows an operating mode in which the refrigerant circuit A is in a serial defogging mode of the internal air flow 100.

[0170] Here, the refrigerant fluid leaving the compressor 1 first arrives at the first junction point 41 where it is directed towards the first condenser 2 which it passes through and there undergoes a heat loss to the benefit of the internal air flow 100. The internal air flow 100 is thus heated before reaching the passenger compartment. The refrigerant fluid continues towards the second junction point 42 where it is directed towards the secondary expansion device 12 within which it undergoes a first pressure loss. The refrigerant fluid continues towards the additional heat exchanger 3. Within the additional heat exchanger 3, the refrigerant fluid absorbs heat energy from the first heat transfer fluid of the first heat transfer fluid circuit B1 because it has already released heat energy via the first condenser 2 and has undergone a first pressure loss by passing through the secondary expansion device 12. The refrigerant fluid then arrives at the second junction point 42 where it is directed towards the first pre-expansion device 4.The refrigerant fluid then passes through the first pre-expansion device 4 where it possibly undergoes a second pressure loss before reaching the reservoir bottle 6. The rest of this operating mode is identical to that of the ninth operating mode.

Claims

Claims 1. Thermal management device for an electric or hybrid motor vehicle, said thermal management device comprising a refrigerant circuit (A) inside which a refrigerant is intended to circulate, the refrigerant circuit (A) comprising in the direction of circulation of the refrigerant: a compressor (1), a condenser (2, 3) intended to absorb heat energy from the refrigerant, a pre-expansion device (4, 5) arranged directly upstream of a reservoir bottle (6), a main expansion device (7, 8), and an evaporator (9, 10) intended to transmit heat energy to the refrigerant.

2. Thermal management device according to claim 1, where the condenser (2, 3) comprises an additional heat exchanger (3) intended to be crossed by both the refrigerant fluid and an auxiliary fluid., the pre-expansion device (4, 5) comprising a first pre-expansion device (4) and where the thermal management device comprising in the direction of circulation of the refrigerant fluid a main loop (A1, A2) comprising in the direction of the refrigerant fluid the compressor (1), the additional heat exchanger (3), the first pre-expansion device (4) arranged directly upstream of the reservoir bottle (6), the main expansion device (7, 8) and the evaporator (9, 10).

3. Thermal management device according to claim 2, wherein the main loop (A1, A2) is a first main loop (A1), where the condenser (2, 3) further comprises a first condenser (2) intended to transmit heat energy to an auxiliary fluid and arranged on the first main loop (A1) in the direction of circulation of the refrigerant fluid between the compressor (1) and the additional heat exchanger (3).

4. Thermal management device according to claim 3, wherein the pre-expansion device (4, 5) comprises a second pre-expansion device (5), wherein the thermal management device comprises a first bypass line (c1) connecting a first connection point (31), arranged on the first main loop (A1) downstream of the first condenser (2), to a second connection point (32), arranged on the first main loop (A1) between the first pre-expansion device (4) and the reservoir bottle (6), and wherein the second pre-expansion device (5) is arranged between the first condenser (2) and the reservoir bottle (6).

5. Thermal management device according to claim 4, further comprising a fourth bypass line (c4) connecting a seventh connection point (37), arranged on the first main loop (A1) downstream of the reservoir bottle (6), to an eighth connection point (38), arranged on the first main loop (A1) between the first pre-expansion device (4) and the reservoir bottle (6), and a fifth bypass line (c5) connecting a ninth connection point (39), arranged on the first main loop (A1) downstream of the additional heat exchanger (3), to a tenth connection point (40), arranged on the first main loop (A1) downstream of the evaporator (9, 10).

6. Thermal management device according to any one of claims 3 to 5, further comprising a sixth bypass line (c6) connecting an eleventh connection point (81), arranged on the first main loop (A1) downstream of the compressor (1), to a twelfth connection point connection (82), arranged on the first main loop (A1) upstream of the additional heat exchanger (3).

7. Thermal management device according to claim 3, further comprising a third bypass pipe (c3) connecting a fifth connection point (35), arranged on the first main loop (A1) downstream of the first condenser (2), to a sixth connection point (36), arranged on the first main loop (A1) between the additional heat exchanger (3) and the first pre-expansion device (4).

8. Thermal management device according to claim 2, wherein the main loop (A1, A2) is a second main loop (A2), wherein the condenser (2, 3) further comprises a first condenser (2) intended to transmit heat energy to an internal air flow (100), and wherein the thermal management device comprises in the direction of circulation of the refrigerant fluid a first bypass branch (d1) connecting a first junction point (41), arranged on the second main loop (A2) downstream of the compressor (1), to a second junction point (42), arranged on the second main loop (A2) upstream of the first pre-expansion device (4), said first bypass branch (d1) comprising the first condenser (2).

9. Thermal management device according to claim 9, further comprising a second bypass branch (d2) connecting a third junction point (43), arranged on the second main loop (A2) downstream of the first condenser (2), to a fourth junction point (44), arranged on the second main loop (A2) upstream of the additional heat exchanger (3), said second bypass pipe comprising a secondary expansion device (12).

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