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

Abstract

The invention relates to a device for thermal management of an electric or hybrid motor vehicle, comprising a refrigerant circuit (A) within which the 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) for absorbing thermal energy from the refrigerant,-a pre-expansion device (4, 5) for pre-expanding the refrigerant in the direction of circulation of the refrigerant, the invention relates to a heat exchanger (1) comprising a storage cylinder (6) arranged directly upstream of the storage cylinder (6), a main expansion device (7, 8), and an evaporator (9, 10) intended for transferring heat energy to a refrigerant.

Description

Technical Field

[0001] The present invention relates to the field of electric or hybrid motor vehicles and more particularly to an apparatus for thermal management within such a vehicle. Background Art

[0002] Today's electric or hybrid motor vehicles more and more often include heat transfer fluid circuits for thermal management of the batteries. In particular, in order for these batteries to be as efficient as possible, they need to be kept at an optimal operating temperature. It is therefore necessary to cool them during use to ensure that they do not exceed this optimal operating temperature to a large extent. Likewise, it may also be necessary to heat these batteries, for example in cold weather, so that they reach this optimal operating temperature in the shortest possible time. Summary of the invention

[0003] It is also known that electric or hybrid motor vehicles include a refrigerant circuit that contributes to the thermal management of the battery, the passenger compartment, and other components of the vehicle. When the weather is particularly hot, it may be necessary to cool the temperature of the battery substantially so that the battery remains at its optimal operating temperature. Under these conditions, the refrigerant must be able to store as much thermal energy from the battery as possible. However, this objective is difficult to achieve with today's thermal management devices.

[0004] Therefore, one of the objects of the present invention is to at least partially overcome the disadvantages 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, comprising a refrigerant circuit in which a refrigerant is intended to circulate, the refrigerant circuit comprising the following components in the direction of circulation of the refrigerant:

[0006] -compressor,

[0007] - a condenser for absorbing thermal energy from the refrigerant,

[0008] - a pre-expansion device, which is arranged directly upstream of the storage cylinder,

[0009] - main expansion device, and

[0010] -Evaporator, used to transfer heat energy to the refrigerant.

[0011] Arranging the preexpansion device directly upstream of the storage cylinder allows the thermal management device according to the invention to advantageously obtain a greater reduction in the temperature upstream of the storage cylinder and therefore a greater enthalpy difference, making it possible to absorb more thermal energy at the evaporator.

[0012] In the present invention, "directly upstream" is understood to mean that no other equipment having an influence on the pressure and / or temperature of the refrigerant is arranged on the path taken by the refrigerant between the two elements in question, in the present case the pre-expansion device and the storage cylinder.

[0013] According to one embodiment of the invention, the condenser comprises an additional heat exchanger through which both the refrigerant and the auxiliary fluid are intended to flow, the preexpansion device comprises a first preexpansion device, and wherein the thermal management device comprises, in the direction of circulation of the refrigerant, a main circuit comprising, in the direction of the refrigerant, a compressor, an additional heat exchanger, a first preexpansion device arranged directly upstream of the storage cylinder, a main expansion device and an evaporator.

[0014] According to one aspect of the invention, the primary circuit is a first primary circuit, wherein the condenser further comprises a first condenser intended to heat the auxiliary fluid and arranged on the first primary circuit in the circulation direction of the refrigerant between the compressor and the additional heat exchanger.

[0015] In particular, the preexpansion device includes a second preexpansion device, the heat management device includes a first bypass pipe, the first bypass pipe connects a first connection point on the first main circuit arranged downstream of the first condenser to a second connection point on the first main circuit arranged between the first preexpansion device and the storage cylinder, and the second preexpansion device is arranged between the first condenser and the storage cylinder.

[0016] According to another aspect of the present invention, the thermal management device further comprises:

[0017] a fourth bypass conduit connecting a seventh connection point on the first main circuit arranged downstream of the storage cylinder to an eighth connection point on the first main circuit arranged between the first pre-expansion device and the storage cylinder, and

[0018] a fifth bypass pipe connecting a ninth connection point disposed on the first main circuit downstream of the additional heat exchanger to a tenth connection point disposed on the first main circuit downstream of the evaporator.

[0019] It is worth noting that the heat management device according to the present invention further comprises a sixth bypass pipe, which connects the eleventh connection point on the first main circuit downstream of the compressor to the twelfth connection point on the first main circuit upstream of the additional heat exchanger.

[0020] It is worth noting that the heat management device further comprises a third bypass pipe, which connects a fifth connection point on the first main circuit downstream of the first condenser to a sixth connection point on the first main circuit between the additional heat exchanger and the first pre-expansion device.

[0021] According to another aspect of the present invention, the main circuit is a second main circuit, the condenser further comprises a first condenser for transferring heat energy to an internal air flow, and the heat management device comprises a first bypass branch in a circulation direction of the refrigerant, the first bypass branch connecting a first junction point on the second main circuit arranged downstream of the compressor to a second junction point on the second main circuit arranged upstream of the first preexpansion device, the first bypass branch comprising the first condenser.

[0022] In particular, the thermal management device of the present invention also includes a second bypass branch, which connects the third junction point to the fourth junction point, the third junction point is arranged on the second main circuit downstream of the first condenser, and the fourth junction point is arranged on the second main circuit upstream of the additional heat exchanger, and the second bypass pipe includes a secondary expansion device. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] Other characteristics and advantages of the invention will become more apparent on reading the following description given by way of non-limiting illustration and with reference to the accompanying drawings, in which:

[0024] Figure 1 is a schematic diagram of a thermal management device according to a first general embodiment.

[0025] Figure 2 According to the general operating mode Figure 1 Schematic diagram of the thermal management device in.

[0026] Figure 3 is a schematic diagram of a heat management device according to a second embodiment.

[0027] Figure 4 According to the first operating mode and the second operating mode Figure 3 Schematic diagram of the thermal management device in.

[0028] Figure 5 According to the third operating mode Figure 3 Schematic diagram of the thermal management device in.

[0029] Figure 6 According to the fourth operating mode Figure 3 Schematic diagram of the thermal management device in.

[0030] Figure 7 According to the fifth operating mode Figure 3 Schematic diagram of the thermal management device in.

[0031] Figure 8 According to the sixth operating mode Figure 3 Schematic diagram of the thermal management device in.

[0032] Fig. 9is a schematic diagram of a heat management device according to a third embodiment.

[0033] Fig.10 is a schematic diagram of a heat management device according to a fourth embodiment.

[0034] Fig.11 According to the seventh operating mode Fig.10 Schematic diagram of the thermal management device in.

[0035] Fig.12 According to the eighth operating mode Fig.10 Schematic diagram of the thermal management device in .

[0036] Fig.13 is a schematic diagram of a heat management device according to a fifth embodiment.

[0037] Fig.14A and Fig. 14B Two schematic diagrams of a heat management device according to two variants of a sixth embodiment are shown.

[0038] Fig.15 According to the ninth operating mode Fig.14A , Fig. 14B Schematic diagram of the thermal management device in.

[0039] Fig.16 According to the tenth operating mode Fig.14A , Fig. 14B Schematic diagram of the thermal management device in.

[0040] Fig.17 According to the eleventh operating mode Fig.14A , Fig. 14B Schematic diagram of the thermal management device in .

[0041] Fig.18 is a schematic diagram of a heat management device according to a seventh embodiment.

[0042] In the various figures, the same elements have the same reference numerals. DETAILED DESCRIPTION

[0043] The following embodiments are examples. Although the description relates to one or more embodiments, this does not necessarily mean that each reference numeral refers to the same embodiment, or that a feature applies to only one embodiment. Individual features of different embodiments may also be combined and / or interchanged to provide other embodiments.

[0044] In this specification, some elements or parameters may be indexed, such as the first element or the second element, and the first parameter and the second parameter, or the first standard and the second standard, etc. In this case, the index is only used to distinguish and represent similar but not identical elements or parameters or standards. The index does not mean to give priority to one element, parameter or standard over another element, parameter or standard, and such designations can be easily interchanged without departing from the scope of this specification. The index also does not mean any temporal order, such as when evaluating any given standard.

[0045] In this specification, "positioned upstream" is understood to mean that one element is positioned before another element relative to the circulation direction of the fluid. In contrast, "positioned downstream" is intended to mean that one element is positioned after another element relative to the circulation direction of the fluid.

[0046] First embodiment:

[0047] Figure 1 A heat management device 1 for an electric or hybrid motor vehicle is shown according to a first embodiment. The heat management device 1 comprises a refrigerant circuit A in which a refrigerant is intended to circulate.

[0048] The refrigerant circuit comprises a first main circuit A1 which, in the circulation direction of the refrigerant, comprises a compressor 1, condensers 2, 3 for absorbing heat energy from the refrigerant, pre-expansion devices 4, 5 arranged directly upstream of a storage cylinder 6, main expansion devices 7, 8 and evaporators 9, 10 for transferring heat energy to the refrigerant.

[0049] The terms "condenser" and "evaporator" are understood to mean a heat exchanger defined by its function and positioning in the first main circuit A1 according to the direction of circulation of the refrigerant. Thus, the condenser will be positioned in the "high-pressure" part of the refrigerant circuit A in the direction of circulation of the refrigerant, so as to absorb thermal energy from the refrigerant and transfer it to an auxiliary fluid, such as an air flow passing through it or another heat transfer fluid. The refrigerant is usually in the high-pressure gas phase at the condenser inlet and in the liquid phase at the condenser outlet, or in the form of a liquid-gas mixture, still at high pressure. The evaporator will be positioned in the "low-pressure" part of the refrigerant circuit A in the direction of circulation of the refrigerant, so as to absorb thermal energy from an auxiliary fluid, such as an air flow passing through it, or from another heat transfer fluid, and transfer it to the refrigerant. The refrigerant is usually in the liquid phase or in the form of a liquid-gas mixture, in the gas phase at the evaporator inlet and in the gas phase at the evaporator outlet, still at low pressure.

[0050] The storage cylinder 6 is installed between the condensers 2, 3 and the main expansion devices 7, 8 to temporarily store the refrigerant delivered from the condensers 2, 3 to the evaporators 9, 10 so that sufficient refrigerant is supplied to the evaporators 9, 10. The storage cylinder 6 can significantly make it possible to eliminate moisture and foreign matter present in the refrigerant, and to supply the refrigerant in a completely liquid state to the expansion valve. Therefore, the presence of such a storage cylinder makes it possible to improve the heat absorption efficiency at the evaporators 9, 10.

[0051] The presence of the pre-expansion devices 4, 5 directly upstream of the storage cylinder 6 makes it possible to increase the subcooling of the refrigerant before it enters the evaporators 9, 10 and thus obtain a greater enthalpy difference between the inlet of the condensers 2, 3 and the outlet of the storage cylinder 6. This allows the refrigerant to recover more thermal energy when it enters the evaporators 9, 10. As will be seen later in the description, the evaporator 10 can in particular be arranged at the location where the battery of the vehicle is located.

[0052] Normal operation mode

[0053] Figure 2 Shows Figure 1 The general mode of operation of the heat management device 1 of the invention is shown.

[0054] The refrigerant is first compressed at the compressor 1 and is therefore in a "high pressure and high temperature" gaseous state. The refrigerant then enters the condensers 2, 3, where it condenses and undergoes a loss of heat energy, and thus a temperature loss, becoming a first auxiliary flow (described in detail later). At the outlet of the condensers 2, 3, the refrigerant is in the form of a gas / liquid mixture at high pressure. The refrigerant then passes through the pre-expansion devices 4, 5, where the refrigerant will experience a first pressure drop, which will transform the refrigerant to an "intermediate" pressure. This first pressure drop makes it possible to change some of the liquid portion of the refrigerant in the storage cylinder 6 into a gas phase. This phase change involves extracting some heat energy from the refrigerant, thereby reducing the enthalpy of the liquid phase. The pressure drop is not as significant here as at the main expansion devices 7, 8. The refrigerant then enters the storage cylinder 6, where it will be purified and a phase separation is achieved, so that the refrigerant at the outlet of the storage cylinder 6 is in a liquid phase. Therefore, at the outlet of the storage cylinder 6, the subcooling of the refrigerant is increased relative to the subcooling at the outlet of the condensers 2, 3. The refrigerant then flows through the main expansion device 7, 8, where it undergoes a second pressure drop and is transformed from the "intermediate" pressure to the "low" pressure. The refrigerant then enters the evaporator 9, 10, where it absorbs heat energy from the second auxiliary flow (described in detail later), thereby increasing its enthalpy and transforming it into a gaseous state. The refrigerant finally returns to the compressor 1.

[0055] Second embodiment:

[0056] Figure 3A second embodiment of the heat management device of the invention is shown, wherein the first main circuit A1 is depicted in bold.

[0057] In this second embodiment, and in Fig. 9 and Fig.10 In the third and fourth embodiments shown, the condensers 2, 3 may in particular be formed by two separate heat exchangers arranged in series on the first main circuit A1. These heat exchangers may thus be a first condenser 2 and an additional heat exchanger 3 configured to act as a second condenser.

[0058] The first condenser 2 is intended to have an auxiliary fluid flow through it and to transfer thermal energy from the refrigerant to the auxiliary fluid.

[0059] exist Figures 3 to 18 In the embodiment and operating mode shown, the secondary fluid intended to flow through the first condenser 2 is an interior air flow 100. The first condenser 2 can then be an "interior" condenser, for example, arranged in a heating, ventilation and air conditioning (also known as HVAC) device. The interior air flow 100 is delivered to the vehicle interior.

[0060] The auxiliary fluid with which the first condenser 2 can exchange thermal energy can also be a heat transfer fluid circulating in an auxiliary thermal management loop (not shown). Thus, the first condenser can be, for example, a two-fluid heat exchanger. Thus, in the embodiments and operating modes described below, it is entirely conceivable to replace the internal air flow 100 with a heat transfer fluid circulating in an auxiliary thermal management loop.

[0061] Depending on the operating mode, the first condenser 2 can be skipped, i.e. the auxiliary fluid does not flow through the first condenser 2, so that the refrigerant flowing through the first condenser 2 does not undergo heat exchange with the auxiliary fluid, or only undergoes very little heat exchange with the auxiliary fluid. If the auxiliary fluid is the internal air flow 100, when the internal air flow 100 reaches the first condenser 2, the internal air flow 100 can be cut off, for example by closing a damper, or the internal air flow 100 can bypass the first condenser 2. If the auxiliary fluid is a heat transfer fluid in an auxiliary thermal management loop, the circulation of the heat transfer fluid within the first condenser 2 can be stopped by interruption of the auxiliary thermal management loop or by a bypass around the first condenser 2.

[0062] Similarly, the additional heat exchanger 3 is intended to have the refrigerant and the auxiliary fluid flowing through it. Depending on the operating mode, the additional heat exchanger 3 can be configured in particular to transfer heat energy from the auxiliary fluid to the refrigerant, thereby heating the refrigerant, and in this case, the heat exchanger acts as an evaporator. The additional heat exchanger 3 can also be configured to transfer heat energy from the refrigerant to the auxiliary fluid, thereby cooling the refrigerant, and in this case, the heat exchanger acts as a second condenser. The auxiliary fluid can in particular be of the same type or of a different type than the auxiliary fluid flowing through the first condenser 2.

[0063] exist Figures 3 to 18 In the illustrated embodiment and operating mode, the auxiliary fluid intended to flow through the additional heat exchanger 3 is the first heat transfer fluid circulating in the first heat transfer loop B1. Therefore, the additional heat exchanger 3 can be a dual-fluid heat exchanger jointly arranged on the refrigerant loop A and on the first heat transfer fluid loop B1, and the first heat transfer fluid circulates in the first heat transfer fluid loop B1. The first heat transfer fluid can be water or ethylene glycol water. The first heat transfer fluid loop B1 can in particular include one or more loops, one or more loops are parallel or meet at the additional heat exchanger 3, and are arranged at the location of the front face of the vehicle and / or the location of the battery of the vehicle and / or the location of the electric motor and / or the location of the power electronic device. The first heat transfer fluid loop B1 can also include at least one radiator arranged in the front of the motor vehicle in order to discharge heat energy to the outside air.

[0064] The auxiliary fluid with which the additional heat exchanger can exchange thermal energy can also be an air flow passing through the latter. Figures 3 to 18 Thus, in the embodiments and operating modes described below, it is perfectly conceivable to replace the first heat transfer fluid circulating in the first heat transfer fluid circuit B1 with an air flow.

[0065] In order that the pre-expansion devices 4, 5 are always arranged directly upstream of the storage cylinder 6, regardless of the operating mode, the thermal management device, more specifically its main circuit A1, may comprise a first pre-expansion device 4 arranged between the additional heat exchanger 3 and the storage cylinder 6 and a second expansion device 5 arranged between the first condenser 2 and the storage cylinder 6, as described in detail later.

[0066] The pre-expansion devices 4, 5 may be expansion devices with a variable diameter opening that allows the refrigerant to pass without a pressure drop when opened to its maximum diameter. It is therefore worth noting that, when the internal condenser 2 does not exchange heat energy or very little heat energy with the auxiliary fluid, the second pre-expansion device 5 does not affect the state of the fluid before it reaches the additional heat exchanger 3. An alternative not shown is also the possibility of bypassing the pre-expansion devices 4, 5.

[0067] If the Figure 3 , the refrigerant circuit A can in particular be an air-conditioning circuit, wherein the evaporators 9, 10 comprise a first heat exchanger 9 intended to be traversed by an internal air flow 100. The first heat exchanger 9 can be arranged in a heating, ventilation and air-conditioning device 110, for example upstream of the first condenser 2 in the flow direction of the internal air flow 100. In this case, the second auxiliary fluid corresponds to the internal air flow 100. The first main expansion device 7 is arranged upstream of the first heat exchanger 9.

[0068] The refrigerant circuit A may thus comprise a first main circuit A1 which comprises, in the circulation direction of the refrigerant, a compressor 1 , a first condenser 2 , an additional heat exchanger 3 , a first pre-expansion device 4 , an accumulator cylinder 6 , a first main expansion device 7 and a first heat exchanger 9 .

[0069] It is worth noting that the first main circuit A1 may include an internal heat exchanger 11 arranged jointly on a first portion 21 and a second portion 22 of the first main circuit A1, so as to obtain an exchange of thermal energy between these two portions. The first portion 21 is arranged between the storage cylinder 6 and the main expansion devices 7, 8, and the second portion 22 is arranged between the evaporators 9, 10 and the compressor 1. This exchange of thermal energy makes it possible to improve the coefficient of performance of the refrigerant circuit A.

[0070] In order to be a reversible air conditioning circuit, the refrigerant circuit A may also include a first bypass pipe c1 shown in a thin line, which connects a first connection point 31 on the first main circuit A1 disposed downstream of the first condenser 2 to a second connection point 32 on the first main circuit A1 disposed between the first pre-expansion device 4 and the storage cylinder 6. This first bypass pipe c1 allows the refrigerant A1 to bypass the additional heat exchanger 3 and makes it possible to connect the first condenser 2 and the storage cylinder 6 to each other. The second pre-expansion device 5 may be disposed on the first main circuit A1 upstream of the first connection point 31, as shown, or in the first bypass pipe c1. Therefore, depending on the operating mode, whether the refrigerant reaches the storage cylinder 6 from the first condenser 2 or from the additional heat exchanger 3, the refrigerant still flows through the pre-expansion devices 4, 5 disposed directly upstream of the storage cylinder 6.

[0071] Reversible means that the refrigerant circuit A1 is able to cool or heat the internal air flow 100 as required. In the cooling mode of the thermal management device of the invention, the internal air flow 100 is significantly cooled via the first heat exchanger 9 .

[0072] like Figure 3As shown, the refrigerant circuit A1 may include a first device for controlling the circulation of the refrigerant from the first main circuit A1 toward the first bypass pipe c1 at the first connection point 31. As shown in the figure, the first control device may be a three-way valve 51 arranged at the first connection point 31. As an alternative, the first control device may include two stop valves, each of which is arranged downstream of the first connection point 31, one stop valve on the first main circuit A1, and one stop valve on the first bypass pipe c1.

[0073] Also like Figure 3 As shown, the refrigerant circuit A1 may include a second device for controlling the circulation of the refrigerant from the first bypass pipe c1 toward the first main circuit A1 at the second connection point 32. As depicted, the second control device may be a check valve 62, which is provided on the first main circuit A1 downstream of the first pre-expansion device 4, and more specifically, between the second connection point 32 and the first pre-expansion device 4. The check valve 62 makes it possible to prevent the refrigerant passing through the first bypass pipe c1 from being directed to the first pre-expansion device 4. As an alternative, the second control device may be a shut-off valve.

[0074] In order to make the refrigerant circuit A reversible and to enable several operating modes, the evaporators 9, 10 may comprise a second heat exchanger 10. This second heat exchanger 10 may in particular enable thermal management and more in particular cooling of the battery of an electric or hybrid motor vehicle. Similar to the additional heat exchanger 3, the second heat exchanger may also be arranged jointly on the refrigerant circuit A and on the second heat transfer fluid circuit B2, the second heat transfer fluid being intended to circulate within the second heat transfer fluid circuit B2 so as to allow heat exchange between these fluids. The second heat transfer fluid circuit B2 may in particular comprise one or more circuits which are parallel or meet at the additional heat exchanger 3 and which are arranged at the location where the front face of the vehicle is located and / or where the electric motor is located and / or where the power electronics are located.

[0075] like Figure 3 As shown, the second heat exchanger 10 may be disposed on a second bypass pipe c2 shown in a thin line of the refrigerant circuit A. The second bypass pipe c2 connects a third connection point 33 on the first main circuit A1 disposed between the storage cylinder 6 and the first main expansion device 7 to a fourth connection point 34 on the first main circuit A1 disposed downstream of the first heat exchanger 9. The second bypass pipe c2 includes a second main expansion device 8 disposed upstream of the second heat exchanger 10 in the circulation direction of the refrigerant.

[0076] It is worth noting that, and Figure 3 As shown, the third connection point 33 is provided between the internal heat exchanger 11 and the first main expansion device 7 , and the fourth connection point 34 is provided between the first non-return valve 61 and the first heat exchanger 9 .

[0077] like Figure 3 As shown, the refrigerant circuit may include a third device for controlling the circulation of the refrigerant from the first main circuit A1 toward the second bypass pipe c2. The third control device may in particular be a three-way valve arranged at the third connection point 33. As an alternative, and as shown in the figure, the third control device may include two stop valves 53, 54, each stop valve 53, 54 being arranged downstream of the third connection point 33, one stop valve being located on the first main circuit A1 and one stop valve being located on the second bypass pipe c2. As an alternative, the third control device may correspond to the main expansion devices 7, 8, the openings of which may be adjusted to allow the refrigerant to flow through them or to prevent the refrigerant from flowing through them.

[0078] It is also worth noting that the first main circuit A1 may include a first check valve 61 disposed downstream of the first heat exchanger 9, and the second bypass pipe c2 may include a second check valve 63 disposed downstream of the second heat exchanger 10. More specifically, the first check valve 61 is disposed upstream of the fourth branch point 34, and makes it possible to prevent the refrigerant leaving the second heat exchanger 10 from returning to the first exchanger 9. In addition, the second check valve 63 may be disposed between the second heat exchanger 10 and the fourth connection point 34. The second check valve 63 makes it possible to prevent the refrigerant leaving the first heat exchanger 9 from reaching the second heat exchanger 10.

[0079] First operating mode

[0080] In the various depictions of the operating modes of the heat management device of the invention, the portion of the refrigerant circuit A1 in which the refrigerant does not circulate is depicted in dotted lines.

[0081] Figure 4 An operating mode is shown, in which the refrigerant circuit A is in a mode in which only the internal air flow 100 is cooled via the first heat exchanger 9 .

[0082] In this operating mode, the first control device (in this case the three-way valve 51) is configured to close the passage to the first bypass line c1, so that the refrigerant circulates directly from the first condenser 2 towards the two-fluid heat exchanger 3. The third control device, for its part, is configured to close the passage to the second bypass line c2, so that all the refrigerant from the storage cylinder 6 passes through the first heat exchanger 9.

[0083] In this operating mode, the refrigerant leaves the compressor 1 at high pressure and passes successively through the first condenser 2, optionally, if arranged on the first main circuit A1, through the second subcooling expansion device 5, and the first connection point 31 where it is directed towards the additional heat exchanger 3 and arrives still at high pressure and without exchanging thermal energy through the first condenser 2. To this end, the first condenser 2 is skipped, i.e. the internal air flow 100 does not flow through it, so that the refrigerant flowing through it does not undergo a heat exchange with the internal air flow 100, or undergoes only a very small heat exchange with the internal air flow 100. If the second pre-expansion device 5 is positioned on the first main circuit A1, it has a maximum opening.

[0084] When the refrigerant flows through the additional heat exchanger 3, the refrigerant experiences a loss of heat energy to the first heat transfer fluid in the first heat transfer fluid circuit B1. The heat energy absorbed by the first heat transfer fluid in the first heat transfer fluid circuit B1 can be released to the outside air, for example, by a radiator arranged in the first heat transfer fluid circuit B1 located in the front of the motor vehicle. The refrigerant then passes through the first pre-expansion device 4, in which the refrigerant experiences a first pressure drop, so that the refrigerant reaches an "intermediate" pressure. The refrigerant then reaches the storage cylinder 6 via the second connection point 32. At the outlet of the storage cylinder 6, the refrigerant flows through the first portion 21 of the internal heat exchanger 11, where it will experience a third loss of heat energy to the refrigerant flowing in the second portion 22. The refrigerant continues to the third connection point 33, where the refrigerant is directed to the first main expansion device 7, and there experiences a second pressure drop greater than the first pressure drop, so that the refrigerant reaches a low pressure. The refrigerant then enters the first heat exchanger 9, in which the refrigerant absorbs heat energy from the internal air flow 100. The internal air flow 100 is thereby cooled. At the outlet of the first heat exchanger 9, the refrigerant goes to the fourth connection point 34. The refrigerant then continues towards the second portion 22 of the internal heat exchanger 11 where it absorbs thermal energy from the first portion 21. The refrigerant then returns to the compressor 1.

[0085] Second operating mode

[0086] Figure 4 A second operating mode is also shown, in which the refrigerant circuit A is in a series demisting mode, in which the interior air flow 100 is dehumidified.

[0087] Just as in the first operating mode, the first control device is configured to close access to the first bypass duct c1 , and the third control device is configured to close access to the second bypass duct c2 .

[0088] In order to dehumidify the interior air flow 100 for demisting purposes, the interior air flow is first cooled to condense the moisture present therein and then heated before it reaches the vehicle interior and in particular the windshield.

[0089] To this end, in this operating mode, the internal air flow 100 flows through both the internal condenser 2 and the first heat exchanger 9. Therefore, the refrigerant leaving the compressor 1 and flowing through the first condenser 2 experiences a first loss of thermal energy to the internal air flow 100. The internal air flow 100 is then heated before it reaches the vehicle interior. The refrigerant continues towards the additional heat exchanger 3. In this case, as depicted, the second pre-expansion device 5 is arranged on the first main circuit A1 and subjects the refrigerant to a first pressure drop. In the additional heat exchanger 3, the refrigerant absorbs thermal energy from the first heat transfer fluid in the first heat transfer fluid circuit B1, because it has released thermal energy via the first condenser 2, and it has undergone a first pressure drop by flowing through the second pre-expansion device 5. The refrigerant then flows through the first pre-expansion device 4, in which the refrigerant may undergo a second pressure drop before reaching the storage cylinder 6. The rest of this operating mode is the same as the first operating mode.

[0090] This second operating mode therefore uses the additional heat exchanger 3 as an evaporator.

[0091] Third operating mode

[0092] Figure 5 A third operating mode is shown, in which the refrigerant circuit A is in a mode for cooling only the battery or for cooling the second heat transfer fluid via the second heat exchanger 10 .

[0093] In this operating mode, the first device is configured to close the passage to the first bypass pipe c1 , and the third control device is configured to open the passage to the second bypass pipe c2 and close the passage to the first heat exchanger 9 .

[0094] In this operating mode, the refrigerant reaches the additional heat exchanger 3 without experiencing a pressure or temperature drop. For this purpose, the first condenser 2 is skipped, i.e. the internal air flow 100 does not flow through it, so that the refrigerant flowing through it does not experience a heat exchange with the internal air flow 100, or only a very small heat exchange with the internal air flow 100. If the second pre-expansion device 5 is positioned on the first main circuit A1, the second pre-expansion device 5 has a maximum opening.

[0095] This operating mode is the same as the first 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 toward the second main expansion device 8, where it will experience a second pressure drop greater than the first pressure drop. It then enters the second heat exchanger 10, where it will absorb the thermal energy emitted by the battery or the second heat transfer fluid. At the outlet of the second heat exchanger 10, the refrigerant passes through the check valve 63 and reaches the internal heat exchanger 11 via the fourth connection point 34.

[0096] Fourth operating mode

[0097] Figure 6 A fourth operating mode is shown corresponding to a combination of the first and third operating modes, wherein the refrigerant circuit A is in a mode of cooling the internal air flow 100 via the first heat exchanger 9 and cooling the battery or the second heat transfer fluid via the second heat exchanger 10 .

[0098] Thus, the refrigerants circulate in parallel:

[0099] - absorbs thermal energy from the internal air flow 100 in the first heat exchanger 9, and

[0100] - Cooling of the battery in the second bypass line c2.

[0101] To this end, the second control device is configured to allow the refrigerant to enter the first heat exchanger 9 and the second heat exchanger 10 .

[0102] Therefore, for the portion of the refrigerant circuit A in which the refrigerant circulates, the operation mode is the same as the first operation mode and the third operation mode, respectively.

[0103] Fifth operating mode

[0104] Figure 7 A fifth reverse operating mode is shown, 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 battery or the second heat transfer fluid via the second heat exchanger 10 .

[0105] In this operating mode, 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 .

[0106] In this operating mode, the refrigerant leaving the compressor 1 flows through the first condenser 2 and there experiences a loss of heat energy to the internal air flow 100. The internal air flow 100 is then heated before it reaches the vehicle interior. The refrigerant continues towards the second pre-expansion device 5, where it experiences a first pressure drop. At the connection point 31, the refrigerant is directed towards the first bypass pipe c1 and then reaches the storage cylinder 6 via the second connection point 32. At the outlet of the storage cylinder 6, the refrigerant in the subcooled liquid phase flows through the internal heat exchanger 11 in the first part 21, where it will experience a second loss of heat energy to the refrigerant flowing in the second part 22. The refrigerant continues towards the third connection point 33, where it is directed towards the second main expansion device 8, and there the refrigerant will experience a second pressure drop greater than the first pressure drop. It then enters the second heat exchanger 10, where it will absorb heat energy from the battery or the second heat transfer fluid and transform into a gas phase. At the outlet of the second heat exchanger 10, the refrigerant goes to the internal heat exchanger 11 via the fourth connection point 34. In the second portion 22 of the internal heat exchanger 11, the refrigerant absorbs thermal energy from the first portion 21. The refrigerant then returns to the compressor 1.

[0107] Sixth operating mode

[0108] Figure 8 A sixth operating mode is shown, in which the refrigerant circuit A is in a parallel demisting mode, in which the interior air flow 100 is dehumidified.

[0109] In this embodiment, the first control device is configured to close the passage to the additional heat exchanger 3 and open the passage to the first bypass pipe c1, and the second control device is configured to allow the refrigerant to flow in the first and second heat exchangers.

[0110] This operation mode is the same as the fifth operation mode except that the refrigerants circulate in parallel:

[0111] - absorbs thermal energy from the internal air flow 100 in the first heat exchanger 9, and

[0112] - in the second bypass c2 , to recover heat from the battery or from the second heat transfer fluid circuit B2 via the second heat exchanger 10 .

[0113] As in the second operating mode, entry into the first heat exchanger 9 makes it possible to absorb thermal energy from the internal air flow 100 in order to condense moisture upstream of the air heated by the first condenser 2 .

[0114] Third embodiment

[0115] Fig. 9 A third embodiment of the heat management device of the present invention is shown.

[0116] This third embodiment comprises a first main loop A1 of thick wire, which is connected to Figures 3 to 8 The first main circuit of the second embodiment is the same.

[0117] The first bypass pipe c1 of the second embodiment is replaced here by a third bypass pipe c3, which connects the fifth connection point 35 on the first main circuit A1 disposed downstream of the first condenser 2 to the sixth connection point 36 on the first main circuit A1 disposed upstream of the first pre-expansion device 4, more specifically, between the additional heat exchanger 3 and the first pre-expansion device 4. Thus, in this embodiment, when the refrigerant does not pass through the additional heat exchanger 3, the second pre-expansion device 5 does not need to be provided.

[0118] The secondary expansion device 12 may be arranged on the main circuit A1 upstream of the additional heat exchanger 3, and more specifically between the fifth connection point 35 and the additional heat exchanger 3. The secondary expansion device 12 may be an expansion device with a variable diameter opening that allows the refrigerant to pass without a pressure drop when opened to its maximum diameter. Alternatively, the secondary expansion device 12 may be bypassed.

[0119] The main circuit A1 may include a check valve 65 which is provided between the first condenser 2 and the ninth connection point 39 and makes it possible to prevent the refrigerant from flowing back toward the first condenser 2 .

[0120] The main circuit A1 may include a fourth device for controlling the circulation of the refrigerant from the first main circuit A1 toward the first bypass pipe c3 at the fifth connection point 35. The fourth control device may in particular be a shut-off valve (not shown) arranged on the main branch A1 downstream of the fifth connection point 35. As an alternative, similar to the main expansion devices 7 and 8, the secondary expansion device 12 includes a flow stop function.

[0121] In this case, the first main circuit A1 may include a fifth device for controlling the circulation of the refrigerant from the first main circuit A1 toward the first bypass pipe c3 at the sixth connection point 36. The fifth control device may in particular be a three-way valve 60 arranged at the sixth connection point 36 as shown in the figure. As an alternative, the fifth control device may include two stop valves, each of which is arranged upstream of the sixth connection point 36, one stop valve on the first main circuit A1 and one stop valve on the third bypass pipe c3.

[0122] The six embodiments described with respect to the second embodiment are similarly applicable to the third embodiment, except that:

[0123] - for the four first operating modes, the fourth control device is configured to open the passage to the additional heat exchanger 3, the fifth control device is configured to close the passage to the third bypass pipe c3 and to open the passage to the first preexpansion device 4 and the additional heat exchanger 3,

[0124] - for the first, second and third operating modes, the secondary expansion device 12 has a flow through it, i.e. the secondary expansion device 12 has a maximum opening so that the refrigerant can flow through the secondary expansion device 12 with a minimum pressure drop, similar to the second pre-expansion device 5 in some operating modes of the second embodiment,

[0125] - For the fifth and sixth operating modes, the refrigerant enters the third bypass pipe c3. To this end, the fifth control device is arranged to open the passage to the third bypass pipe c3 and close the passage to the additional heat exchanger 3, so that the refrigerant circulates directly from the first condenser 2 to the first subcooling expansion device 4.

[0126] Fourth embodiment

[0127] Fig.10 A fourth embodiment of the heat management device of the present invention is shown.

[0128] This fourth embodiment can be used for various embodiments described with respect to the second embodiment, and realizes a new operation mode, in which the additional heat exchanger 3 is similar to an evaporator. To this end, this embodiment repeats part of the refrigerant circuit A of the second embodiment, and also includes a fourth bypass pipe c4 and a fifth bypass pipe c5 of a thin line.

[0129] The fourth bypass pipe c4 connects the seventh connection point 37 on the first main circuit A1 disposed downstream of the storage cylinder 6 to the eighth connection point 38 on the first main circuit A1 disposed between the first pre-expansion device 4 and the storage cylinder 6. It is noteworthy that the third bypass point 33 is disposed downstream of the internal heat exchanger 11 and upstream of the first main expansion device 7 and the second main expansion device 8. Alternatively, the seventh connection point 37 is combined with the third connection point 33. It is noteworthy that the eighth connection point 38 is upstream of the connection point 32, and more particularly upstream of the check valve 62.

[0130] The fourth bypass line c4 may include a check valve 64 for preventing the refrigerant from the first preexpansion device 4 from bypassing the storage cylinder 6 by passing through the fourth bypass line c4.

[0131] The fifth bypass pipe c5 connects the ninth connection point 39 on the first main circuit A1 downstream of the additional heat exchanger 3 to the tenth connection point 40 on the first main circuit A1 downstream of the evaporators 9 and 10. It is worth noting that the tenth connection point 40 is provided between the evaporators 9 and 10 and the internal heat exchanger 11. It is again worth noting that the tenth connection point 40 is provided between the fourth connection point 34 and the internal heat exchanger 11.

[0132] The third control device may include a shutoff valve 55 disposed on the fourth bypass pipe c4 downstream of the seventh connection point 37 to allow or not allow the refrigerant to circulate in the fourth bypass pipe c4. Alternatively, the first preexpansion device 4 may be configured to be able to block the flow back to the additional heat exchanger 3.

[0133] In the six first embodiments, the fifth bypass pipe c5 may include a shutoff valve 58 to prevent the refrigerant leaving the evaporators 9 , 10 from returning to the two-fluid heat exchanger 3 .

[0134] Seventh operating mode

[0135] Fig.11 The seventh operating mode is shown (for Fig.10 ), in which the refrigerant circuit A is in a mode for heating the internal air flow 100 via the first condenser 2 and recovering heat from the first heat transfer fluid circuit B1 via the additional heat exchanger 3.

[0136] Therefore, in this operating mode, the refrigerant flows through the additional heat exchanger 3 not upstream but downstream of the storage cylinder 6. Therefore, in this case, the first pre-expansion device 4 is designed not to subject the refrigerant to a pressure drop upstream of the storage cylinder 6, but to expand the refrigerant so that it is converted to a low pressure before flowing through the additional heat exchanger 3 and it does not absorb thermal energy from the first heat transfer fluid in the first heat transfer fluid circuit B1.

[0137] to this end,

[0138] - a first control device is arranged to redirect the refrigerant from the first condenser 2 to the first bypass pipe c1 and to close the passage of the refrigerant from the first condenser 2 to the additional heat exchanger 3, and

[0139] - The third control device is configured to allow the refrigerant from the storage cylinder 6 to enter the fourth bypass pipe c4 on the one hand and to prevent the refrigerant from circulating towards the first heat exchanger 9 and passing through the second bypass pipe c2 on the other hand.

[0140] In this operating mode, the refrigerant leaving the compressor 1 flows through the first condenser 2 and there experiences a first loss of thermal energy to the internal air flow 100. The internal air flow 100 is thus heated before it reaches the vehicle interior. The refrigerant continues towards the second pre-expansion device 5, where it experiences a first pressure drop. At the connection point 31, the refrigerant is towards the first bypass duct c1 and then reaches the storage cylinder 6 via the second connection point 32. At the outlet of the storage cylinder 6, the refrigerant is completely in liquid form and flows through the internal heat exchanger 11 in the first portion 21, where it will experience a second loss of thermal energy of the refrigerant flowing in the second portion 22. The refrigerant continues towards the seventh connection point 37, where it is directed towards the fourth bypass duct c4. The refrigerant is directed towards the first pre-expansion device 4. The refrigerant is prevented from returning to the storage cylinder 6 at the non-return valve 62 by the greater pressure exerted at the non-return valve 62 by the refrigerant from the first bypass duct c1. At the first pre-expansion device 4, the refrigerant experiences a second pressure drop. The refrigerant then enters the additional heat exchanger 3, where it will absorb thermal energy from the first heat transfer fluid in the first heat transfer fluid circuit B1. The refrigerant leaving the additional heat exchanger 3 reaches the ninth connection point 39, where it is directed towards the fifth bypass pipe c5, as long as the first control device closes the passage to the heat exchanger 3. The refrigerant then enters the first main circuit A1 at the tenth connection point 40 and is then directed towards the internal heat exchanger 11 by the action of the non-return valves 61, 63, which prevent the refrigerant from returning to the first heat exchanger 9 and the second heat exchanger 10. In the second part 22, the refrigerant absorbs thermal energy from the first part 21. The refrigerant then returns to the compressor 1.

[0141] Eighth operating mode

[0142] Fig.12 The eighth operating mode is shown (for Fig.10 ), in which the refrigerant circuit A is in parallel demisting mode, in which the interior air flow 100 is dehumidified. Therefore, this operating mode represents Figure 8 An alternative to the sixth operating mode in.

[0143] In this case, instead of the second heat exchanger 10 recovering thermal energy in parallel with the first heat exchanger 9 , the additional heat exchanger 3 does this.

[0144] To this end, the refrigerants circulate in parallel:

[0145] - absorbs thermal energy from the internal air flow 100 in the first heat exchanger 9, and

[0146] - in the fourth bypass column c4 and the fifth bypass column c5 in order to recover heat from the first heat transfer fluid in the first heat transfer fluid loop B1 via the additional heat exchanger 3 .

[0147] This operating mode is thus similar to the seventh operating mode, except that the refrigerant at the seventh connection point 37 is divided into two parts, a first part being directed towards the fourth bypass pipe c4 and a second part 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 then meet at the tenth connection point 40, then pass through the internal heat exchanger 11 and return to the compressor 1.

[0148] In this operating mode:

[0149] - a first control device is arranged to redirect the refrigerant from the first condenser 2 to the first bypass pipe c1 and to close the passage of the refrigerant from the first condenser 2 to the additional heat exchanger 3, and

[0150] - The second control device is configured to allow the refrigerant from the storage cylinder 6 to enter the fourth bypass pipe c4 and flow to the first heat exchanger 9 on the one hand, and to prevent the refrigerant from circulating through the second bypass pipe c2 on the other hand.

[0151] Fifth embodiment

[0152] Fig.13 A fifth embodiment is shown.

[0153] The fifth embodiment corresponds to Fig.10 A variation of the fourth embodiment in , which comprises a sixth bypass line, which makes it possible to bypass the first condenser 2 for the cooling operating modes (the first, third and fourth operating modes).

[0154] Therefore, the fifth embodiment includes a sixth bypass pipe c6, which connects the eleventh connection point 81 on the first main circuit A1 downstream of the compressor 1 to the twelfth connection point 82 on the first main circuit A1 upstream of the additional heat exchanger 3. More specifically, the eleventh connection point 81 is configured between the compressor 1 and the first condenser 2, and the twelfth connection point 82 is configured between the first connection point 31 and the second fluid exchanger 3. It is worth noting that the twelfth connection point is set upstream or downstream of the ninth connection point 39. In an alternative solution, the twelfth connection point is set on the third bypass pipe c5, especially upstream of the stop valve 58.

[0155] like Fig.13As shown, the refrigerant circuit may include a sixth device for controlling the circulation of the refrigerant from the first main circuit A1 toward the sixth bypass pipe c6 at the eleventh connection point 81. The sixth control device may in particular be a three-way valve arranged at the eleventh connection point 81. As an alternative, and as shown in the figure, the sixth control device may include two stop valves 56, 57, each stop valve 56, 57 being arranged downstream of the eleventh connection point 81, one stop valve 56, 57 on the first main circuit A1 and one stop valve 56, 57 on the sixth bypass pipe. The stop valves 56, 57 may have an electronically controlled variable opening.

[0156] With regard to the cooling embodiment, the refrigerant leaving the compressor 1 reaches the eleventh connection point 81, where it is directed to the sixth bypass pipe c6. The refrigerant then reaches the additional heat exchanger 3 via the twelfth connection point 82. The rest of the corresponding implementation of these operating modes is the same as described with regard to the second embodiment.

[0157] Furthermore, the fifth manner of executing the second operation mode and the fifth to eighth embodiments are the same as those described above.

[0158] Sixth embodiment

[0159] The sixth and seventh embodiments are FIG. 14A to FIG. 18 , and comprising a second main circuit A2 in bold, which connects the compressor 1 directly to the additional heat exchanger 3 .

[0160] The second main circuit A2 comprises, in the circulation direction of the refrigerant, a compressor 1, an additional heat exchanger 3, a first pre-expansion device 4, a storage cylinder 6 and evaporators 9, 10. It is worth noting that the second main circuit A2 may also comprise an internal heat exchanger 11.

[0161] Fig.14A , 14B Two variants (A and B) of the sixth embodiment are depicted in which the second primary circuit A2 comprises, downstream of the storage cylinder 6, a first primary expansion device 7 and a first heat exchanger 9. These two variants differ in the elements used for the first pre-expansion device 4.

[0162] exist Fig.14A In the first variant depicted in FIG. 4 , the pre-expansion device 4 is identical to the pre-expansion device used in the five first embodiments.

[0163] In this case, if Fig.14A As shown, the refrigerant circuit A may include a first bypass branch d1 which connects a first junction point 41 on the second main circuit A2 arranged downstream of the compressor 1 to a second junction point 42 arranged on the second main circuit A2, the second junction point 42 being located between the additional heat exchanger 3 and the first pre-expansion device 4.

[0164] like Fig.14A As shown, the refrigerant circuit may include a seventh device for controlling the circulation of the refrigerant from the second main circuit A2 toward the first bypass branch d1 at the first junction 41. The seventh control device may in particular be a three-way valve arranged at the first junction 41. As an alternative, and as shown in the figure, the seventh control device may include two shut-off valves 96, 97, each of which is arranged downstream of the first junction 41, one shut-off valve on the second main circuit A2 and one shut-off valve on the first bypass branch d1. The shut-off valves 96, 97 may have an electronically controlled variable opening.

[0165] As also depicted, the refrigerant circuit may include an eighth device for controlling the circulation of the refrigerant from the second main circuit A2 toward the first bypass branch d1 at the second junction 42. In a first variant of this sixth embodiment, the eighth control device may in particular be a three-way valve 59 arranged at the second junction 42, such as Fig.14A As an alternative, the eighth control device may include two shutoff valves, one disposed downstream of the second junction 42 on the second main circuit A2 and the other disposed upstream of the second junction 42 on the first bypass branch d1 .

[0166] according to Fig. 14B In the second variant of the sixth embodiment depicted in , the pre-expansion device 4 is formed by two pre-programmed non-return valves 71 , 72 arranged upstream of the second junction 42 on the first bypass branch d1 and the second main circuit A2 , respectively.

[0167] Thus, in this case, the eighth control device may correspond to two preprogrammed check expansion valves 71 , 72 .

[0168] The other elements described with respect to the first variant are the same in the second variant.

[0169] like Fig.14A and 14B As shown, the refrigerant circuit A may include a second bypass line c2 including a second main expansion device 8 and a second heat exchanger 10 .

[0170] The parallel demisting mode (sixth operation mode) in which the internal air flow 100 is dehumidified and the mode (fifth operation mode) in which the internal air flow 100 is heated via the first condenser 2 and heat is recovered from the second heat transfer fluid described with respect to the third embodiment are similarly applicable to the first variation of this sixth embodiment.

[0171] In short, for the mode of heating the interior air flow 100 via the first condenser 2 and recovering heat from the second heat transfer fluid, the refrigerant leaving the compressor 1 first reaches the first junction 41, where the refrigerant is directed towards the interior exchanger 2, through which it passes, and where it experiences a loss of thermal energy to the interior air flow 100. The interior air flow 100 is thus heated before it reaches the vehicle interior. The refrigerant continues towards the second junction 42, where it is directed towards the first pre-expansion device 4, and there experiences a first pressure drop. The refrigerant then reaches the storage cylinder 6. At the outlet of the storage cylinder 6, the refrigerant in the subcooled liquid phase flows through the interior heat exchanger 11 in the first portion 21, where it will experience a second loss of thermal energy to the refrigerant flowing in the second portion 22. The refrigerant continues towards the third junction 33, where it is directed towards the second main expansion device 8, and there the refrigerant will experience a second pressure drop greater than the first pressure drop. It then enters the second heat exchanger 10, where it absorbs thermal energy from the battery or the second heat transfer fluid and changes into a gas phase. At the outlet of the second heat exchanger 10, the refrigerant goes to the internal heat exchanger 11 via the fourth connection point 34. In the second part 22 of the internal heat exchanger 11, the refrigerant absorbs thermal energy from the first part 21. The refrigerant then returns to the compressor 1.

[0172] In short, for the parallel demisting mode in which the internal air flow 100 is dehumidified, the mode is the same as the above-mentioned mode for heating the internal air flow 100, except that the refrigerants circulate in parallel:

[0173] - absorbs thermal energy from the internal air flow 100 in the first heat exchanger 9, and

[0174] - in the second bypass c2 , to recover heat from the battery or from the second heat transfer fluid circuit B2 via the second heat exchanger 10 .

[0175] With regard to the second variant of the sixth embodiment, the various operating modes described with regard to the first variant are the same, except that the first expansion is performed by one of the stop valves 71 , 72 upstream of the second junction 42 , depending on the operating mode.

[0176] Ninth operating mode

[0177] Fig.15 shows one mode of operation (for Fig.14A and 14B ), in which the refrigerant circuit A is in a mode in which only the internal air flow 100 is cooled via the first heat exchanger 9.

[0178] In this operating mode, the fifth and eighth control devices are configured to close access to the first bypass branch d1 .

[0179] In this embodiment, the refrigerant first reaches the first junction 41, where it is directed to the additional heat exchanger 3. At the additional heat exchanger 3, it releases heat energy to the first heat transfer fluid in the first heat transfer fluid circuit B1. Then, it reaches the first pre-expansion device 4 via the second junction 42. At the first pre-expansion device 4, the refrigerant experiences a first pressure drop. The refrigerant then reaches the storage cylinder 6. At the outlet of the storage cylinder 6, the refrigerant flows through the first portion 21 of the internal heat exchanger 11, where it will experience a third loss of heat energy to the refrigerant flowing in the second portion 22. The refrigerant continues to the third connection point 33, where the refrigerant is directed to the first main expansion device 7, and there experiences a second pressure drop greater than the first pressure drop, so that the refrigerant reaches a low pressure. The refrigerant then enters the first heat exchanger 9, where the refrigerant absorbs heat energy from the internal air flow 100. The internal air flow 100 is thereby cooled. At the outlet of the first heat exchanger 9, the refrigerant goes to the fourth connection point 34. The refrigerant then continues towards the second portion 22 of the internal heat exchanger 11 where it absorbs thermal energy from the first portion 21. The refrigerant then returns to the compressor 1.

[0180] Tenth operating mode

[0181] Fig.16 A tenth operating mode is shown (for Fig.14A and 14B ), in which the refrigerant circuit A is in a mode for cooling only the battery via the second heat exchanger 9.

[0182] 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 towards the second main expansion device 8, where it will experience a second pressure drop greater than the first pressure drop. It then enters the second heat exchanger 10, where it will absorb the heat energy emitted by the battery. At the outlet of the second heat exchanger 10, the refrigerant goes to the internal heat exchanger 11 via the fourth connection point 34 before returning to the compressor 1.

[0183] Eleventh Operation Mode

[0184] Fig.17 An eleventh operating mode corresponding to a combination of the ninth and tenth operating modes is shown (for Fig.14A and 14B ), in which the refrigerant circuit A is in a mode for cooling both the internal air flow 100 and the battery.

[0185] Thus, the refrigerant circulates in parallel:

[0186] - absorbs thermal energy from the internal air flow 100 in the first heat exchanger 9, and

[0187] - Cooling of the battery in the second bypass line c2.

[0188] To this end, the second control device is configured to allow the refrigerant to enter the first heat exchanger 9 and the second heat exchanger 10 .

[0189] Seventh embodiment

[0190] Fig.18 A seventh embodiment of the present invention is shown.

[0191] This seventh embodiment is a variation of the sixth embodiment and therefore comprises an element with the addition of a second bypass branch d2 which connects a third junction point 43 on the first bypass branch d1 arranged downstream of the first condenser 2 to a fourth junction point 44 on the second main circuit A2 arranged upstream of the additional heat exchanger 3.

[0192] In this embodiment, the first bypass branch d1 may include a check valve 65, in which case the check valve 65 is disposed between the first condenser 2 and the third connection point 33. Furthermore, the second bypass branch d2 may include a secondary expansion device 12.

[0193] All the operation modes described with respect to the sixth embodiment are applicable to the seventh embodiment. In addition, the seventh embodiment can realize an operation mode in which the refrigerant circuit A is in a series demisting mode for dehumidifying the internal air flow 100.

[0194] In this case, the refrigerant leaving the compressor 1 first reaches the first junction 41 where it is directed towards the first condenser 2, where it passes through the first condenser 2 and where it experiences a loss of heat energy to the interior air flow 100. The interior air flow 100 is thus heated before it reaches the vehicle interior. The refrigerant continues towards the second junction 42 where it is directed towards the secondary expansion device 12, where it experiences a first pressure drop. The refrigerant continues towards the additional heat exchanger 3. Within the additional heat exchanger 3, the refrigerant absorbs heat energy from the first heat transfer fluid in the first heat transfer fluid circuit B1, since it has released heat energy via the first condenser 2 and it has experienced a first pressure drop by flowing through the secondary expansion device 12. The refrigerant then reaches the second junction 42 where it is directed towards the first pre-expansion device 4. The refrigerant then flows through the first pre-expansion device 4, where it may experience a second pressure drop before reaching the storage cylinder 6. The rest of this operation mode is the same as the ninth operation mode.

Claims

1. A thermal management device for an electric or hybrid motor vehicle, the thermal management device comprising a refrigerant circuit (A), in which a refrigerant circulates, the refrigerant circuit (A) comprising, in the circulation direction of the refrigerant: - compressor (1), - a condenser (2, 3) for absorbing heat energy from the refrigerant, - a pre-expansion device (4, 5), arranged directly upstream of the storage cylinder (6), - a main expansion device (7, 8), and - Evaporator (9, 10) for transferring heat energy to the refrigerant.

2. The thermal management device according to claim 1, wherein: The condenser (2, 3) comprises an additional heat exchanger (3) through which both the refrigerant and the auxiliary fluid are intended to flow, The pre-expansion device (4, 5) comprises a first pre-expansion device (4), and The thermal management device comprises a main circuit (A1, A2) in the circulation direction of the refrigerant, and the main circuit comprises the compressor (1), the additional heat exchanger (3), a first pre-expansion device (4) arranged directly upstream of the storage cylinder (6), the main expansion device (7, 8) and the evaporator (9, 10) in the direction of the refrigerant.

3. A thermal management device according to claim 2, wherein the main circuit (A1, A2) is a first main circuit (A1), wherein the condenser (2, 3) further comprises a first condenser (2), the first condenser (2) being used to transfer heat energy to an auxiliary fluid and being arranged on the first main circuit (A1) in the circulation direction of the refrigerant between the compressor (1) and the additional heat exchanger (3).

4. A heat management device according to claim 3, wherein the pre-expansion device (4, 5) comprises a second pre-expansion device (5), wherein the heat management device comprises a first bypass pipe (c1), the first bypass pipe (c1) connecting a first connection point (31) on the first main circuit (A1) arranged downstream of the first condenser (2) to a second connection point (32) on the first main circuit (A1) arranged between the first pre-expansion device (4) and the storage cylinder (6), and wherein the second pre-expansion device (5) is arranged between the first condenser (2) and the storage cylinder (6).

5. The thermal management device according to claim 4, further comprising: - a fourth bypass pipe (c4) connecting the seventh connection point (37) on the first main circuit (A1) arranged downstream of the storage cylinder (6) to the eighth connection point (38) on the first main circuit (A1) arranged between the first pre-expansion device (4) and the storage cylinder (6), and - a fifth bypass pipe (c5) connecting a ninth connection point (39) to a tenth connection point (40), wherein the ninth connection point (39) is arranged on the first main circuit (A1) downstream of the additional heat exchanger (3), and the tenth connection point (40) is arranged on the first main circuit (A1) downstream of the evaporator (9, 10).

6. The thermal management device according to any one of claims 3 to 5, further comprising a sixth bypass pipe (c6), which connects an eleventh connection point (81) on the first main circuit (A1) downstream of the compressor (1) to a twelfth connection point (82) on the first main circuit (A1) upstream of the additional heat exchanger (3).

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

8. The heat management device according to claim 2, wherein the primary circuit (A1, A2) is a second primary circuit (A2), wherein the condenser (2, 3) further comprises a first condenser (2) for transferring thermal energy to the internal airflow (100), And wherein the heat management device includes a first bypass branch (d1) in the circulation direction of the refrigerant, the first bypass branch (d1) connects a first junction point (41) on the second main circuit (A2) arranged downstream of the compressor (1) to a second junction point (42) on the second main circuit (A2) arranged upstream of the first pre-expansion device (4), and the first bypass branch (d1) includes the first condenser (2).

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

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