Thermal conditioning system for a vehicle, particularly a motor vehicle

Abstract

Disclosed is a thermal conditioning system comprising a refrigerant circuit having at least one of a first configuration comprising a first heat exchanger and a compressor and of a second configuration comprising a first heat exchanger (54) and a second heat exchanger (50) wherein, in the first configuration, a duct connects an outlet of the first heat exchanger with an inlet of the compressor, the outlet orifice of the first heat exchanger being aligned with the inlet orifice of the compressor, and in the second configuration, a duct connects the outlet of the second heat exchanger (50) with an inlet (226) of the first heat exchanger (54), the inlet orifice of the first heat exchanger (54) being aligned with the outlet orifice of the second heat exchanger (50).

Description

[0001] DESCRIPTION

[0002] Title: THERMAL CONDITIONING SYSTEM FOR A VEHICLE, PARTICULARLY AN AUTOMOBILE

[0003] The present invention relates to the field of thermal conditioning systems. These systems can in particular equip a motor vehicle. Such systems make it possible to achieve thermal regulation of different parts of the vehicle, such as for example the passenger compartment or an electrical energy storage battery, in the case of an electrically powered vehicle. Heat exchanges are managed mainly by the compression and expansion of a refrigerant fluid within different heat exchangers making it possible to ensure heating or cooling of different parts.

[0004] Thermal conditioning systems commonly use a refrigerant loop and a heat transfer fluid loop that exchange heat with the refrigerant. Such systems are therefore called indirect systems. The refrigerant loop is designed so that the refrigerant transfers heat to a heat transfer fluid in a first heat exchanger. The heat transferred to the heat transfer fluid can then be dissipated in an airflow intended for the passenger compartment to heat it. The heat transfer fluid circuit also allows for the cooling of heat-dissipating elements of the vehicle's powertrain, such as the vehicle's electric traction motor or the power electronics controlling the electric motor. To achieve this, another heat exchanger allows for a heat exchange between the heat transfer fluid and the refrigerant to cool the heat transfer fluid.

[0005] There is therefore a need to have thermal conditioning systems that can offer different modes of cooling and / or heating the battery or different elements of the vehicle's powertrain, in particular without requiring the circulation of pressurized refrigerant fluid.

[0006] Thermal conditioning systems include thermal management components such as pumps, valves, heat exchangers, and temperature control components. Components such as conduits are also provided to guide a fluid and fluidically connect the thermal management components to each other.

[0007] The development of electric vehicles has increased the need for optimized thermal conditioning systems with simplified and economical manufacturing processes while creating a demand for efficient systems, with a reduced footprint, light weight, simple to manufacture and easy to integrate into the environment of a motor vehicle. Documents LIS2019 / 047373, US2004 / 112073 and EP1354735 disclose different types of connection between a compressor and a heat exchanger or between two heat exchangers.

[0008] The invention aims to propose a solution to improve the situation.

[0009] To this end, the present invention relates to a thermal conditioning system comprising: a refrigerant circuit comprising at least one of a first configuration comprising a first heat exchanger and a compressor and a second configuration comprising a first heat exchanger and a second heat exchanger, wherein: for the first configuration, a conduit connects an outlet of the first heat exchanger with an inlet of the compressor, the outlet of the first heat exchanger being aligned with the inlet of the compressor, for the second configuration, a conduit connects the outlet of the second heat exchanger with an inlet of the first heat exchanger, the inlet of the first heat exchanger being aligned with the outlet of the second exchanger.

[0010] In this way, the refrigerant circulating at low pressure at the outlet of the first heat exchanger undergoes only a small pressure drop before entering the compressor compared to the prior art where the pipe was bent. The same is true when the outlet of the second heat exchanger is aligned with the inlet of the first heat exchanger. The circulation of refrigerant is then easier.

[0011] Advantageously, the conduit is straight.

[0012] The duct may have a length of less than 60 mm, for example between 20 and 50 mm, in particular between 30 and 40 mm.

[0013] A support can carry the first exchanger on a first face and the compressor or the second exchanger on a second opposite face.

[0014] The support may have a generally substantially flat shape.

[0015] The support may include a window and the conduit may pass through said support from the first face to the second face through this window. The system may include a refrigerant circulation unit which includes at least one channel.

[0016] The fluid circulation unit may comprise a block, for example made of aluminum, in which the channel is obtained by drilling or obtained during the molding of the block.

[0017] The channel may be formed by a first flat wall element and a second wall element shaped so as to delimit a cavity which is closed by the first wall element,

[0018] Advantageously, the support is formed in a separate part from said at least one channel and comprises a flat receiving area on which is applied one face of said at least one first wall element of said at least one channel.

[0019] Advantageously, the support carrying the channel(s) comprises a flat area for receiving said first flat wall element(s) of said channel(s). A receiving surface is thus provided directly on the support or frame which may have a generally flat shape so as to support the channels of the circulation unit.

[0020] Each first wall element may have a substantially planar general shape. It may comprise a first substantially planar face and a second substantially planar opposite face. The first face and the second face may be parallel to each other. In practice, the first face is applied to the planar receiving area and the second face receives the second wall element.

[0021] The support may be formed from a material less dense than the material of said at least one channel.

[0022] The support may include a compressor receiving portion, this portion being formed on a face of the support opposite that on which the flat receiving area is formed. Thus positioned, the compressor provides additional rigidity to the assembly and prevents twisting of the support.

[0023] Alternatively, the circulation unit forms the support.

[0024] In other words, the circulation unit can carry the first heat exchanger on a first face and the compressor or the second heat exchanger on a second opposite face.

[0025] The circulation unit may comprise a plurality of channels each connecting two components of a refrigerant circuit, at least two channels of the plurality of channels being such that the first wall elements are formed by the same part and the second wall elements are formed in separate parts.

[0026] All channels can have their first wall elements formed in the same piece.

[0027] Said first wall elements of the first channels can be formed in the same substantially planar part, such as a flat plate.

[0028] Spaces may be provided between all or part of said first wall elements and / or second wall elements so as to reduce heat transfer between said wall elements.

[0029] The second wall elements of said at least two channels may have different thicknesses. This is made possible by the fact that the second wall elements are formed in different pieces, unlike the prior art in which all the second wall elements are formed in the same piece and all have a wall of the same thickness.

[0030] The second wall elements of said at least two channels may be formed from different materials.

[0031] At least two channels can have their second wall element formed by the same part.

[0032] Each second wall element may include a boss defining a groove, which may be surrounded by a peripheral edge which may be applied to a corresponding peripheral edge of a first wall element.

[0033] The peripheral edge of a first wall element is welded or brazed with a peripheral edge of a second wall element.

[0034] In other words, the invention relates to a thermal conditioning system comprising a refrigerant circuit comprising a first heat exchanger, for example an internal heat exchanger, and at least one of a compressor and a second heat exchanger; in which a conduit connects an outlet of the first heat exchanger with an inlet of the compressor or an inlet of the first heat exchanger with an outlet of the second heat exchanger, the conditioning system being arranged so that the outlet of the first heat exchanger is aligned with the inlet of the compressor or the inlet of the first exchanger is aligned with the outlet of the second heat exchanger. The conduit is thus preferably straight.In other words, the invention relates to a thermal conditioning system comprising a refrigerant circuit comprising a first heat exchanger, for example an internal heat exchanger, a conduit connecting the first exchanger to an upstream member such as a second exchanger or a downstream member such as a compressor, the conduit being rectilinear and aligned either with the outlet orifice of the upstream component and with the inlet orifice of the first heat exchanger, or with the inlet orifice of the downstream component and with the outlet orifice of the first heat exchanger. The length of the conduit is preferably less than 60 mm.

[0035] One of a compressor and a second heat exchanger wherein a conduit connects an outlet of the first heat exchanger with an inlet of one of the compressor and the first heat exchanger, the outlet of the first heat exchanger being aligned with the inlet of said one of the compressor and the first heat exchanger.

[0036] The invention also relates to a thermal conditioning system for heating and / or cooling electrical and / or electronic elements of an electric or hybrid motor vehicle, and, preferably, the passenger compartment of said vehicle comprising an assembly according to one of the preceding claims.

[0037] According to one aspect of the invention, the second exchanger is a water cooler type evaporator. This water cooler type evaporator allows a heat exchange between the refrigerant fluid and a heat transfer liquid, such as for example glycolated water.

[0038] According to one aspect of the invention, the refrigerant circuit may comprise a water condenser (or "WCDS" for "Water Condenser" in its English name). The water condenser also allows a heat exchange between the refrigerant and a heat transfer liquid, for example glycolated water.

[0039] In an embodiment illustrated in the figures, the first heat exchanger is an exchanger called an internal heat exchanger (or “IHX” for “Internal Heat Exchanger” in its English name). The first heat exchanger of the internal heat exchanger type allows a heat exchange between the refrigerant fluid circulating at high pressure and the refrigerant fluid circulating at low pressure.

[0040] According to another embodiment, the support may carry a bottle such as a desiccant bottle, having the function of separating the liquid refrigerant fluid and the gaseous refrigerant fluid, at high pressure, and of allowing storage and capturing the humidity of the refrigerant fluid passing through it. The bottle, or desiccant bottle, could be placed on the second face of the support. Other advantages and characteristics of the present invention will appear more clearly on reading the following description, given for illustrative and non-limiting purposes, and the appended drawings in which:

[0041] [Fig.1] is a simplified perspective view of a circulation unit for a fluid management module for a vehicle, particularly an automobile.

[0042] [Fig.2] is a side view of the circulation unit of Figure 1.

[0043] [Fig.3] is a simplified bottom view of one face of the circulation unit of Figure 1; this face showing the circulation channels and part of the elements arranged on this face.

[0044] [Fig.4] is a simplified top view of the opposite face of the circulation unit.

[0045] [Fig.5] is a schematic view of the refrigerant circuit associated with the circulation unit of Figure 1, operating according to a first mode of operation.

[0046] [Fig.6] is a schematic view of the refrigerant circuit associated with the circulation unit of Figure 1, operating according to a second mode of operation.

[0047] [Fig.7] is a simplified perspective view of the opposite face of Figure 4, this opposite face showing part of the elements arranged on this second face.

[0048] [Fig.8] is a simplified perspective view of the fluid management module comprising the unit of Figure 1.

[0049] [Fig.9] is a bottom view of the module of Figure 8.

[0050] [Fig.10] is a top view of the fluid management module.

[0051] [Fig.11] is a schematic view of a first embodiment of the invention in which a refrigerant circulation unit support is shown along a first face in part A and along a second opposite face in part B, the support being insulated.

[0052] [Fig.12] is a schematic view of the refrigerant circulation unit support of Figure 11, along a first face in part A and along a second opposite face in part B, the support carrying the refrigerant circulation unit as well as components such as heat exchangers (part A) and a compressor (part B).

[0053] [Fig.13] is a schematic perspective view of a support with a part of a refrigerant circulation unit in part A and a schematic perspective view of the support without the fluid circulation unit in part B. [Fig.14] is a schematic perspective view of the ducts of a refrigerant circulation unit in part A and only the first wall elements of said ducts in part B.

[0054] [Fig.15] is a schematic perspective view illustrating the cooperation between first wall elements formed from a single piece and second wall elements.

[0055] [Fig.16] represents a schematic diagram of an example assembly of a support with first and second wall elements.

[0056] [Fig.17] is a schematic perspective view of a part of the module associated with the first embodiment, in the same orientation in part A and part B, the first heat exchanger (“internal heat exchanger”) having been removed on part B, part C showing a sectional view taken along a fluid connection duct from the compressor to the first heat exchanger.

[0057] [Fig.18] is a schematic view illustrating the alignment of an outlet of a second heat exchanger with the first heat exchanger, associated with a module according to an alternative embodiment.

[0058] The invention relates to a thermal conditioning system 1 for heating and / or cooling electrical and / or electronic elements of an electric or hybrid motor vehicle, and, preferably, the passenger compartment of said vehicle, comprising: a heat transfer fluid circuit for heating and / or cooling the electrical and / or electronic elements, and, preferably, the passenger compartment of the vehicle, a refrigerant circuit 2 comprising a condenser 52, a compressor 20, a first evaporator 48 for cooling the passenger compartment of the vehicle, a second evaporator 50 for cooling the electrical and / or electronic elements, such that the second evaporator 50 is thermally coupled to the heat transfer fluid circuit, a fluid management module, characterized in that the fluid management module comprises: a support 10 having a first face 40 and a second face 42, the first face 40 being opposite the second face 42, and, at least one channel 60, 62,64 for the refrigerant circuit 2, the first face 40 of the support 10 supporting at least the second evaporator and the second face 42 of the support 10 supporting at least one valve 72-2 or 72-3.,

[0059] The refrigerant used by refrigerant circuit 2 is a chemical fluid such as R1234yf. Other refrigerants could be used, such as R134a or R290.

[0060] "High pressure refrigerant" means a refrigerant at a pressure of around 20 bars, and "low pressure refrigerant" means a refrigerant at a pressure of around 3 bars. First, the fluid management module of the thermal management system will be described using figures 1 to 4. The thermal conditioning system as a whole will then be detailed using figures 5 and 6.

[0061] In the particular embodiment of the fluid management module of the thermal conditioning system 1 illustrated in particular in figures 1 to 4, the support 10 is formed of at least a first circulation zone 12 of the refrigerant fluid and intended for the circulation of the refrigerant fluid at high pressure and a second circulation zone 14 of the refrigerant fluid and intended at least for the circulation of the refrigerant fluid at high pressure and / or at low pressure.

[0062] This support 10 is also called a central platform (or "hub" in its English name). The support 10 is intended to be part of a thermal conditioning system 1 of a motor vehicle in which the refrigerant fluid circulates, in particular in an air conditioning and / or heat pump circuit.

[0063] In other words, the support 10 comprises a refrigerant fluid circulation unit.

[0064] According to the embodiment illustrated here, the support 10 is formed of two plates secured to each other. In such a case, the channels for the circuit of a refrigerant fluid 2 are formed by at least one deformation of one of the two plates.

[0065] In other words, and in this particular embodiment, the support 10 integrates the channels for the circuit of a refrigerant fluid 2.

[0066] According to this embodiment, the plates forming the support 10 each comprise one or more flat regions 15 between the channels 60, 64.

[0067] According to this embodiment again, the thickness of the plates forming the support is substantially uniform both at the level of the flat regions and at the level of the channels 60, 64.

[0068] A particular embodiment illustrated here proposes that the support 10 comprises at least a first plate, called transfer plate 80, shaped to form at least one channel or undulation for the circulation of the fluid. In other words, the curvatures of the transfer plate 80 constitute passages which form the channels.

[0069] Still in this particular embodiment, the support 10 comprises at least a second plate called support plate 82. The support plate 82 is configured to provide the interface between the support 10 and elements secured to the support 10.

[0070] The support plate 82 may be flat to be in contact with a portion of the elements secured to the support 10. In other words, in this embodiment, the support plate 82 partly defines the conduits for the refrigerant fluid.

[0071] In the embodiment illustrated in Figure 3, the support 10 comprises at least one first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0072] The first channel 60, intended for the circulation of the high-pressure refrigerant fluid, comprises in the embodiment illustrated here a substantially Y-shaped shape, with a main branch 60-1 and two branches called first (60-2) and second (60-3) branches.

[0073] In a particular embodiment, at least one valve support block is inserted on a branch of the first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0074] In the particular embodiment illustrated in Figures 3 and 4, two valve support blocks 70-2 and 70-3 are each inserted on a branch 60-2 or 60-3 of the first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0075] Here, the valve support blocks 70-2 and 70-3 are each capable of receiving a valve, in particular a stop valve 72-2 or 72-3 visible in figure 7.

[0076] Alternative embodiments not shown propose that the support 10 comprises valves such as progressive valves, EXV (for "electronic expansion valve" in English) or TXV (for "thermostatic expansion valve" in English). These valves will preferably be secured to the support 10 via a valve support block common to several valves and / or an individual support block specific for each valve.

[0077] Thus, the support 10 comprises at least one valve support block 70-2 or 70-3 which can be seen as a distribution block for the refrigerant fluid in the support 10.

[0078] In other words, a stop valve 72-2 or 72-3 is placed in fluid communication with the first channel 60 intended for the circulation of the high-pressure refrigerant fluid via, in this particular embodiment, the valve support block 70-2 or 70-3.

[0079] More particularly, here, the fluid communication is carried out at the level of each respective branch 60-2 or 60-3 of the first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0080] A temperature sensor 74 (visible for example in figure 7) is provided at the level of the first channel 60 intended for the circulation of the high pressure refrigerant fluid.

[0081] In the embodiment illustrated here, the temperature sensor 74 is arranged on one of the two branches of the first channel 60 intended for the circulation of the high-pressure refrigerant fluid (here the second branch 60-2). More particularly, the temperature sensor 74 is arranged near the junction between the main branch 60-1 and the two branches 60-2 and 60-3 of the first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0082] As indicated above, the first channel 60 is intended for the circulation of the high-pressure refrigerant fluid.

[0083] In this embodiment, the main branch 60-1 of the first channel 60 is intended to ensure communication between a first flange 101, fluidly connected to a compressor 20, and the first (60-2) and second (60-3) branches.

[0084] The first branch 60-2 is intended to ensure communication between the main branch 60-1 and a condenser 52.

[0085] The condenser 52 is configured to carry out an exchange of calories between the high-pressure refrigerant fluid and a heat transfer liquid.

[0086] The second branch 60-3 is intended to ensure communication between the main branch 60-1 and a second flange 102, fluidly connected to an internal condenser 46, not shown here.

[0087] This internal condenser 46 is a heat exchanger for regulating the passenger compartment of the vehicle, arranged for example in the passenger compartment of said vehicle. Said internal condenser 46 is intended to heat a flow of air passing through it.

[0088] The support 10 also comprises at least one second channel 62 intended for the circulation of the high-pressure refrigerant fluid.

[0089] In the particular embodiment illustrated in FIG. 3, the support 10 comprises five second channels 62-1, 62-2, 62-3, 62-4 and 62-5 intended for the circulation of the high-pressure refrigerant fluid.

[0090] In this same embodiment, one of the second channels, hereinafter referenced 62-1, is intended to ensure communication between the condenser 52 and another heat exchanger, hereinafter referred to as the first heat exchanger 54.

[0091] According to the embodiment illustrated in Figure 9, the first heat exchanger 54 is an internal heat exchanger, said internal heat exchanger making it possible to carry out a transfer of calories between a low pressure portion of the refrigerant circuit 2 and a high pressure portion of said refrigerant circuit 2. Such an exchange of calories makes it possible to optimize the thermodynamic properties of the refrigerant circuit 2. Still in this same embodiment illustrated here, one of the second channels, hereinafter referenced 62-2, is intended to ensure communication between the first heat exchanger 54 and a branch, said branch being divided into one of the second channels, hereinafter referenced 62-3 and another of the second channels, hereinafter referenced 62-4.

[0092] The second channel 62-3 is intended to ensure communication between the second channel 62-2 and a valve, preferably an expansion valve. In the remainder of the description, this expansion valve will be referred to as the second expansion valve 28.

[0093] Still in this same embodiment illustrated here, the second channel 62-4 is intended to ensure communication between the second channel 62-2 and another valve, preferably an expansion valve. In the remainder of the description, this expansion valve will be called the first expansion valve 26.

[0094] Each of the expansion valves 26, 28, also called expansion valves, may be an electronic expansion valve, or EXV, a thermostatic expansion valve, or TXV, or a calibrated orifice. In the case of an electronic expansion valve, the passage section allowing the refrigerant to pass can be continuously adjusted between a closed position and a maximum open position. For this, an electronic controller controls an electric motor which moves a movable shutter controlling the passage section offered to the refrigerant.

[0095] The first expansion valve 26 is here directly connected to a third flange 103, itself fluidically connected to a first evaporator 48, not shown.

[0096] This first evaporator 48 is a heat exchanger for regulating the passenger compartment of the vehicle, arranged for example in the passenger compartment of said vehicle. Said first evaporator 48 is intended to cool a flow of air passing through it.

[0097] According to this same embodiment, one of the second channels, hereinafter referenced 62-5, is intended to ensure communication between the second channel 62-2 and a fourth flange 104, fluidly connected to the internal condenser 46.

[0098] The support 10 also comprises at least one third channel 64, intended for the circulation of the refrigerant fluid at low pressure.

[0099] In the particular embodiment illustrated in Figure 3, the support 10 comprises three third channels 64-1, 64-2 and 64-3 intended for the circulation of the refrigerant fluid at low pressure. According to this same embodiment, one of the third channels, hereinafter referenced 64-1, is intended to ensure communication between the second expansion valve 28 and the second evaporator 50.

[0100] According to this embodiment, the second evaporator 50 is of the stacked plate water cooler type (or “chiller” in its English name). This second evaporator is configured to carry out an exchange of calories between the low-pressure refrigerant fluid and a heat transfer liquid.

[0101] Still in this same embodiment illustrated here, one of the third channels, hereinafter referenced 64-2, is intended to ensure communication between the second evaporator 50 and a fifth flange 105, fluidly connected to a bottle 56.

[0102] According to this embodiment, the bottle 56 is an accumulator, configured to contain the refrigerant fluid at low pressure.

[0103] According to this embodiment, the bottle 56 could be provided with a refrigerant fluid charging valve 156.

[0104] According to another embodiment, not shown, the bottle 56 may be a desiccant bottle configured to contain the high-pressure refrigerant and capture moisture from the refrigerant passing through it. According to this other embodiment, the bottle 56, or desiccant bottle, would be placed on a high-pressure portion of the circuit.

[0105] In this same embodiment illustrated here, one of the third channels, hereinafter referenced 64-3, is intended to ensure communication between a sixth flange 106, fluidly connected to the bottle 56, and the first heat exchanger 54.

[0106] Furthermore, the support 10 comprises a seventh flange 107, fluidly connected to the first evaporator 48.

[0107] The two expansion valves 26, 28 make it possible to control the supply of refrigerant to the first evaporator 48 and the second evaporator 50. Thus, depending on the position of the expansion valves 26, 28, the first evaporator 48 and / or the second evaporator 50 can be supplied with refrigerant.

[0108] According to one embodiment, the first heat exchanger (54), the second evaporator (50) and the condenser (52) are fluidically connected to the first, second and third channels 60, 62, 64, by means of flanges. More precisely, the first heat exchanger 54 is connected by means of an eighth, ninth and tenth flange, respectively to the second channel 62-1, to the second channels 62-2, to the third channel 64-3, the second evaporator 50 is connected by means of an eleventh and twelfth flange, respectively to the third channel 64-1 and to the third channel 64-2, the condenser 52 is connected by means of a thirteenth flange and a fourteenth flange respectively to the first branch 60-2 of the first channel 60 and to the second channel 62-1.

[0109] In the embodiment illustrated in particular in figures 3 and following, the at least first channel 60 intended for the circulation of the high-pressure refrigerant fluid is arranged on the first circulation zone 12 of the refrigerant fluid and intended for the circulation of the high-pressure refrigerant fluid, while the at least third channel 64 intended for the circulation of the low-pressure refrigerant fluid is arranged on a second circulation zone 14 of the refrigerant fluid intended for the circulation of the low-pressure refrigerant fluid.

[0110] In this embodiment, the first circulation zone 12 of the refrigerant fluid extends substantially along a first plane P1 and the second circulation zone 14 of the refrigerant fluid extends substantially along a second plane P2 and in which the first plane P1 of the first circulation zone 12 of the refrigerant fluid and the second plane P2 of the second circulation zone 14 of the refrigerant fluid are different.

[0111] In this embodiment, the first circulation zone 12 of the refrigerant fluid and the second circulation zone 14 of the refrigerant fluid are connected by a first common edge 16.

[0112] In this embodiment, the support 10 comprises a third zone 18 capable of receiving at least part of the compressor 20, the third zone 18 being distinct from the first circulation zone 12 of the refrigerant fluid and from the second circulation zone 14 of the refrigerant fluid.

[0113] In this embodiment, the third zone 18 extends substantially along a third plane P3, the third plane P3 being different from the first plane P1 of the first circulation zone 12 of the refrigerant fluid and from the second plane P2 of the second circulation zone 14 of the refrigerant fluid. In this embodiment, the first plane P1 of the first circulation zone 12 of the refrigerant fluid, the second plane P2 of the second circulation zone 14 of the refrigerant fluid and the third plane P3 of the third zone 18 are parallel planes.

[0114] In this embodiment, the third zone 18 and the second circulation zone 14 of the refrigerant fluid are connected by a second common edge 22.

[0115] In this embodiment, the support 10 comprises a first opening 32 extending at least over the third zone 18 capable of receiving at least in part the compressor 20.

[0116] This first opening 22 can be seen as a cutout making it possible to lighten the support 10 and making it possible to define two fixing lugs for the compressor 20. In this embodiment, the first opening 32 also extends over the second common edge 22 to the third zone 18 and the second circulation zone 14 of the refrigerant fluid.

[0117] In the embodiment shown in particular in Figure 8, the support 10 comprises a second opening 24, the second opening 24 receiving at least in part a fifteenth flange 115.

[0118] This fifteenth flange 115 ensures fluid communication between the first heat exchanger 54 and the compressor 20.

[0119] According to another aspect of the invention, not shown here, the fifteenth flange 115 could belong to the support 10.

[0120] In the embodiment shown in particular in figures 8 and 10, the second face 42 of the support 10 further comprises a compressor 20.

[0121] In this embodiment, the compressor 20 is secured to the second face 42 of the support 10 by any means such as, for example, screws.

[0122] In the embodiment shown in particular in figures 8 and 10, the second face 42 of the support 10 further comprises a bottle 56.

[0123] In other words, in this embodiment, the bottle 56 is secured to the second face 42 of the support 10.

[0124] According to an embodiment shown in Figure 9, the first heat exchanger 54, the second evaporator 50 and the condenser 52 each have a length and a width, the length of each of the first heat exchanger 54, second evaporator 50 and condenser 52 defining a longitudinal extension direction L1, L2 and L3 respectively and in which the longitudinal extension directions L2 and L3 of the second evaporator 50 and the condenser 52 are parallel and in which the longitudinal extension direction L1 of the first heat exchanger 54 is perpendicular to the longitudinal extension directions L2 and L3 of the second evaporator 50 and the condenser 52.

[0125] Such a distribution also contributes to improving the efficiency of heat exchange through the module by participating in the creation of a thermal gradient.

[0126] Still according to this embodiment, the condenser 52 is arranged on a first circulation zone 12 of the refrigerant fluid of the support 10 and intended for the circulation of the refrigerant fluid at high pressure, the second evaporator 50 and the first heat exchanger 54 are arranged on a second circulation zone 14 of the refrigerant fluid of the support 10 and intended for the circulation of the refrigerant fluid at high pressure and / or for the circulation of the refrigerant fluid at low pressure. According to an embodiment shown in FIG. 10, the compressor 20 and the bottle 56 each comprise a longitudinal extension direction L4 and L5 respectively and in which the longitudinal extension direction L4 of the compressor is perpendicular to the longitudinal extension direction L5 of the bottle 56.

[0127] The longitudinal extension directions L4 and L5, respectively of the compressor 20 and the bottle 56, extend parallel to the first, second and third planes P1, P2 and P3.

[0128] These arrangements of the compressor 20 and the bottle 56 make it possible to improve the compactness of the fluid management module of the thermal conditioning system 1.

[0129] The thermal conditioning system 1 within the refrigerant circuit 2 will now be described in relation to figures 5 and 6. Furthermore, the refrigerant circuit 2 will be described starting with the compressor 20, but it is understood that this only represents a fictitious starting point of the refrigerant circuit 2 and that said refrigerant circuit 2 forms a closed loop.

[0130] A first mode of operation of the refrigerant circuit 2, comprising the thermal conditioning system 1, and making it possible to heat and / or cool electrical and / or electronic elements of an electric or hybrid motor vehicle, and, preferably, the passenger compartment of said vehicle, will now be described in relation to FIG. 5.

[0131] In order to facilitate understanding, it should be considered that only the pipes symbolized by solid lines in Figure 5 will be described, since they are implemented in the first operating mode. Furthermore, thicker lines of the pipes or components of the refrigerant circuit 2 make it possible to symbolize the portions of the refrigerant circuit 2 where the refrigerant is at high pressure.

[0132] In this first mode of operation, the compressor 20, described above, makes it possible to compress the refrigerant fluid in order to increase its pressure, and, consequently, its temperature. Thus, it is understood that at the outlet of the compressor 20, the high-pressure refrigerant fluid is in the gaseous state and has a high temperature, that is to say higher than its inlet temperature in said compressor 20. The refrigerant fluid at the outlet of the compressor 20 circulates in a first pipe 110a, external to the support 10, then, via the first flange 101, in the main branch 60-1 of the first channel 60 and is directed by means of a first open stop valve 72-2 towards the first branch 60-2 then towards the condenser pass 17 of the condenser 52. Said condenser 52 then gives up its calories to a first heat transfer fluid 30a of the closed cooling circuit 44.Thus, at the outlet of the condenser 52, the refrigerant is colder than at the inlet and is at least partly in the liquid state. At the outlet of the condenser 52, the refrigerant is directed, via one of the second channels 62-1, towards the first heat exchanger 54. According to the embodiment illustrated in FIGS. 5 and 6, the first heat exchanger 54 is an internal heat exchanger. The high-pressure refrigerant circulating in the second pass 11b of said first heat exchanger 54 exchanges calories with the low-pressure refrigerant of another portion of the refrigerant circuit 2, circulating in the first pass 11a. This transfer makes it possible to improve the thermodynamic performances implemented in the refrigerant circuit 2.

[0133] At the end of its passage through the first heat exchanger 54 via the second pass 11b, the refrigerant circulates in one of the second channels 62-2 to a branch. The refrigerant then circulates in one of the second channels 62-3 and / or in one of the second channels 62-4 and passes respectively through a second expansion valve 28 and / or a first expansion valve 26 in order to lower its pressure and its evaporation point. It is understood that at this stage, we pass from the high pressure portion of the refrigerant circuit 2 to the low pressure portion of the latter.

[0134] At the outlet of the second expansion valve 28, the low-pressure refrigerant fluid is directed via one of the third channels 64-1 and circulates within the second evaporator 50 via the evaporator pass 13, in order to exchange calories with a second heat transfer liquid 30b intended to cool the electrical and / or electronic elements and passing through said second evaporator 50. More particularly, the second heat transfer liquid 30b passing through the second evaporator 50 is hot at the inlet of the second evaporator 50 and gives up its calories to the refrigerant fluid circulating in the evaporator pass 13, which thus evaporates, the change of state producing the energy necessary for cooling the electrical and / or electronic elements. Thus, it is understood that within the second evaporator 50, the refrigerant fluid evaporates under the effect of the capture of calories, the second expansion valve 28 having lowered its evaporation point.It is then understood that at the outlet of the second evaporator 50, the refrigerant fluid circulating in one of the third channels 64-2 is mainly in the gaseous state.

[0135] At the outlet of the first expansion valve 26, the cold, low-pressure refrigerant fluid is directed, via a third flange 103 then a second pipe 110b, external to the support 10, towards the first evaporator 48 of a thermal regulation device 38 of the passenger compartment of the vehicle, arranged for example in the passenger compartment of said vehicle. More particularly, the thermal regulation device 38 is arranged in the passenger compartment in such a way as to be crossed by an air flow F which is sent into the passenger compartment. Thus, it is understood that the air flow F passing through the first evaporator 48 is cooled by the cold refrigerant fluid circulating within the latter, thus making it possible to cool the passenger compartment.The refrigerant fluid passing through the first evaporator 48 is then evaporated by the effect of the captured calories, such that it exits at least partially in the gaseous state in a third pipe 110c, external to the support 10, up to a seventh flange 107 of the support 10.

[0136] Once passed through the second evaporator 50, the refrigerant coming from one of the third channels 64-2 passes through a fifth flange 105, circulates in a fourth pipe 110d, external to the support 10, and passes through the bottle 56, here the accumulator. The refrigerant coming from the first evaporator 48 passes through a seventh flange 107, then circulates in a fifth pipe 110 e, external to the support 10, to the bottle 56. The bottle 56, or accumulator, collects a liquid fraction of the refrigerant fluid at the outlet of the second evaporator 50 and / or the first evaporator 48. Such a passage in the bottle 56 is necessary prior to the passage of the refrigerant fluid into the compressor 20 which can only accept the refrigerant fluid in the gaseous state.

[0137] At the outlet of the bottle 56, the refrigerant, in the gaseous state and still at low pressure, is directed, via a sixth pipe 110f, external to the support 10, and a sixth flange 106 towards the first heat exchanger 54 by means of one of the third channels 64-3, in order to carry out the exchange of calories with the refrigerant of the high pressure portion of the refrigerant circuit 2 via the first pass 11a, as described previously. Subsequently, the refrigerant is directed towards the compressor 20 via a fifteenth flange 115 and a seventh pipe 110g, external to the support 10, so that the latter increases its pressure and its temperature as described previously. According to the embodiment illustrated in figures 5 and 6, the fifteenth flange 115 is directly integrated into the first exchanger 54. According to another embodiment, not illustrated, this fifteenth flange 115 could belong to the support 10.We understand that thus, at the outlet of compressor 20, we switch back to the high pressure portion of the refrigerant circuit 2 and that a new thermodynamic cycle can take place.

[0138] A second mode of operation of the refrigerant circuit 2 comprising the thermal conditioning system 1, and making it possible to heat and / or cool electrical and / or electronic elements of an electric or hybrid motor vehicle, and, preferably, the passenger compartment of said vehicle, will now be described in relation to FIG. 6.

[0139] To facilitate understanding, it should be considered that only the pipes symbolized by solid lines in Figure 6 will be described, since they are implemented in the second operating mode. Furthermore, thicker lines on the pipes are used to symbolize the portions of the refrigerant circuit 2 where the refrigerant is at high pressure.

[0140] In the same way as for the first operating mode, at the outlet of the compressor 20 in the first pipe 110a, external to the support 10, the refrigerant fluid has a high pressure, a high temperature and is in the gaseous state. The refrigerant fluid is then directed, by closing the first valve 72-2 and opening the second valve 72-3, via a first flange 101, a main branch 60-1, a second branch 60-3, a second flange 102 and an eighth pipe 110h, towards an internal condenser 46 of the thermal regulation device 38 of the passenger compartment, in order to heat the air flow F, here cold, passing through at least said internal condenser 46. Thus, it is understood that at the outlet of the internal condenser 46 of the thermal regulation device 38 of the passenger compartment, the refrigerant fluid is at least partially condensed, the latter having given up at least part of its calories to the cold air flow F in order to heat it and therefore to heat the passenger compartment.Subsequently, the refrigerant fluid exits the internal condenser 46 via a ninth line 110i.

[0141] The refrigerant fluid leaving the internal condenser 46 of the thermal regulation device 38 of the passenger compartment then joins one of the second channels 62-5 via the fourth flange 104. The refrigerant fluid circulates in one of the second channels 62-5 then in the second channel 62-2 and passes through the second expansion valve 28 in order to lower its pressure and its evaporation point. It is understood that at this stage, we move from the high pressure portion of the refrigerant fluid circuit 2 to the low pressure portion of the latter.

[0142] The refrigerant fluid then passes through one of the third channels 64-1 and then the second evaporator 50 via the evaporator pass 13 in order to capture the calories of the second heat transfer liquid 30b intended to cool electrical and / or electronic elements. By capturing the calories of the second heat transfer liquid 30b, the refrigerant fluid evaporates at least partially and continues its path in the refrigerant fluid circuit 2 in a manner identical to that described previously for the first operating mode.

[0143] According to a third mode of operation, not shown here, the condenser 52 has the function of exchanging calories with the first heat transfer fluid 30a intended, this time, to heat electrical and / or electronic elements of an electric or hybrid motor vehicle. In this mode of operation, the high-pressure refrigerant circulates within the condenser 52 via the condenser pass 17, in order to exchange calories with the first heat transfer fluid 30a intended here to heat the electrical and / or electronic elements and passing through said condenser 52. More particularly, the first heat transfer fluid 30a passing through the condenser 52 is cold at the inlet of the condenser 52 and captures calories from the refrigerant circulating in the condenser pass 17, which thus condenses, the change of state producing the energy necessary for heating the electrical and / or electronic elements.

[0144] According to an example of this mode of operation, on the side of the second evaporator 50, the refrigerant fluid would pass through the evaporator pass 13 in order to capture the calories from the second heat transfer liquid 30b, said second heat transfer liquid 30b circulating in a radiator, not shown, placed for example on the front of the vehicle. The heat transfer liquid 30b would then release the captured calories to the ambient air through said radiator.

[0145] We now refer to Figure 11 which represents another embodiment of a support 200 of a unit 217 for circulating a refrigerant fluid. According to this embodiment, the support 200 is in the general form of a substantially flat plate comprising a first face 200a and a second face 200b opposite one another and formed on either side of an extension plane P of the plate, this plane separating the two faces 200a, 200b. Figure 11A illustrates the support 200 seen from the first face 200a and Figure 11B illustrates the support seen from the second face 200b.

[0146] As shown, the first face 200a of the support 200 comprises a flat receiving zone 202 intended to receive channels 204 for circulating refrigerant fluid such as those described previously with reference to FIG. 3 or those described with reference to FIG. 7. The refrigerant circulation unit 217 thus comprises channels 204 carried by the first face 200a of the support 200 and conduits which are carried by the support 200 but not entirely as is the case with the channels 204. A conduit or pipe is illustrated at 110g in FIG. 8 and also with reference to FIG. 12A at 206. The support 200 described with reference to FIG. 8 can be used instead of the support described previously with reference to FIG. 3, the equipment described previously then being carried by this support 10 to perform the same functions.

[0147] As can be seen, the first face 200a and the second face 200b of the support each comprise a lattice structure formed by a plurality of first ribs 208 oriented in a first orientation and second ribs 210 oriented in a second orientation in the extension plane, the second orientation not being parallel to the first orientation. The ribs 208, 210 may be separated from each other by cells. In another embodiment, the first face 200a and the second face could comprise a lattice structure with ribs together delimiting cells having a honeycomb shape, that is to say with a hexagonal section. The ribs make it possible to stiffen the support. In Figure 11A, it can be seen that the flat receiving zone 202 is partly surrounded by a lattice structure formed by the ribs 208, 210.More practically, the upper surfaces of the ribs are flush with the flat receiving area 202.

[0148] The support 200 thus formed with a flat receiving zone 202 surrounded by a lattice structure proves to be rigid and lightweight. The support can be made of a composite material and / or a plastic material. Advantageously, it is therefore not made of a metallic material which makes it lighter. It can be, for example, a polypropylene or a polyamide loaded with fibers. Note that the support is preferably made of a less dense material than the material constituting the channels of the refrigerant circulation unit.

[0149] The second surface 200b of the support 200 comprises a member for receiving the compressor 20. To improve the rigidity of the assembly, the member 212 for receiving the compressor is formed opposite the flat part 202 of the support 200. It can be formed of several ribs with a concave curved upper edge making it possible to support in a complementary manner a convex rounded outer face of the compressor 20.

[0150] The support 200 comprises arms 214a, 214b substantially perpendicular to the extension plane of the support. These arms are intended to allow attachment to a casing or chassis of a motor vehicle for example. A first arm 214a extends from the first face and in a direction opposite to the second face. A second arm 214b extends from the second face and in a direction opposite to the first face. The first arm also has a portion 214a1 extending in the same manner as the second arm. The arms may comprise threaded metal tubular inserts for the passage of metal screws. The screws may also be fixed directly through the arms without an insert.

[0151] The support 200 may comprise windows 216 or passages allowing the first face 200a and the second face 200b to be joined. These windows are intended to allow the fluid connection between the components of the refrigerant circuit.

[0152] Figure 12 illustrates the support carrying the circulation unit 217 on the first face 200a, the circulation unit being carried by the flat receiving zone 202. The compressor 20 is carried on the opposite face 200b.

[0153] We now refer to Figure 13 which illustrates a support 200 identical to that described with reference to Figure 11 and on which is arranged a plurality of connecting channels 218 connecting components of the refrigerant circuit, that is to say at least two of a first heat exchanger 54, a second exchanger 50 and a compressor. According to the present document, at least one channel of the circulation unit 217 is carried by the flat receiving zone 202. Ideally, they are all carried by said flat receiving zone 202. The channels are thus carried by the flat receiving zone 202 of the support, which makes it possible to further stiffen the support 200. Thus positioned, the channels 218 are arranged opposite the compressor supported by the second face 200b of the support 200.

[0154] The channels illustrated with reference to Figure 13 but also with reference to Figure 14 each comprise a first planar wall element 218a and a second wall element 218b, each second wall element 218b comprising a cavity formed by a boss. The boss has a first face defining a groove extending between a first end 220 and a second end 222.

[0155] According to one aspect of the invention, each second wall element 218b comprises a peripheral edge 219b surrounding the boss or groove. This peripheral edge 219b is applied to a peripheral edge 219a of a first wall element 218a. Said peripheral edges are welded or brazed together. They could also be assembled by another connecting means such as gluing. The connecting means must be able to withstand the pressure and temperature of the fluid circulating in the channels.

[0156] As illustrated in Figure 14A and Figure 15, the first wall elements 218a are formed in a single piece. Preferably, they are all formed in the same piece 221 which is applied to the support 200 (Figure 16). Screws may be provided to make the connection between the circulation unit 217 and the support 200. The piece 221 advantageously has two substantially planar faces, a first 221a applied to the face 200a of the support 200 and a second face 221b receiving the second wall elements 218b.

[0157] Thus, in one embodiment, the part 221 has the shape of a plate having two faces 221a, 221b which are parallel and flat.

[0158] It is also observed that the second wall elements 218a are formed distinctly from each other and are each coupled to a first wall element 218b. Each second wall element 218b includes an orifice 223 formed at at least one of its first and second ends.

[0159] In a variant, the part 221 having the shape of a plate could comprise a second non-planar face 221b. In other words, it could be formed from a plurality of surfaces for receiving a second wall element 218b, each surface of a first wall element 218a being able to be inclined relative to another surface of another first wall element 218a. The face 221a can be planar in order to be applied to a corresponding planar face of the planar receiving zone 202. As illustrated in FIGS. 14, 15 and 16, spaces 224 can be provided between all or part of said first wall elements and / or the second wall elements. In this way, it is possible to reduce the heat transmission between two first wall elements 218a and / or between two second wall elements 218b.

[0160] We now refer to figure 17 which illustrates the first heat exchanger (or IHX) 54 which is carried by the first face of the support 200 and the compressor which is carried by the second face of the support 200. The illustrated assembly is also applicable to the support described with reference to figures 1 to 10.

[0161] Figure 17C illustrates the fluid connection 110g between the first heat exchanger and the compressor, more precisely between an outlet 228 and the inlet 230 of the compressor. In Figure 17c, the fluid conduit 110g is illustrated, which is rectilinear. More particularly, the inlet orifice 230 of the compressor is partially aligned with the outlet orifice 228 of the first heat exchanger. In this case, said orifices are coaxial. In this first configuration, the refrigerant circulating at low pressure at the outlet of the first heat exchanger undergoes only a few pressure losses before entering the compressor compared to the prior art where the conduit was bent.

[0162] In a second configuration illustrated in figure 18, the outlet of a second heat exchanger, such as the second evaporator 50 is aligned at least partially with an inlet of the first heat exchanger 54. In this case, the evaporator can be directly connected to the inlet of the first heat exchanger 54. In this second configuration, the second heat exchanger is then arranged in place of the compressor which can be offset outside the support 200.

[0163] By aligned orifice, it is meant that at least part of the section of an outlet orifice is aligned with part of the section of an inlet orifice. And more specifically the sections can be coaxial without being completely identical and can also be identical.

[0164] The length of the conduit which connects the two components concerned by the first configuration (figure 17) or the second configuration (figure 18) can be of the order of 20 to 50 mm, in particular 30 and 40 mm.

[0165] As mentioned above, the support may be formed by the circulation unit. In other words, the circulation unit may carry the first exchanger on a first face and the compressor or the second exchanger on a second, opposite face.

Claims

Claims 1. Thermal conditioning system comprising: a refrigerant circuit comprising at least one of a first configuration comprising a first heat exchanger (54) and a compressor and a second configuration comprising a first heat exchanger (54) and a second heat exchanger (50), wherein: for the first configuration, a conduit (110g) connects an outlet of the first heat exchanger (54) with an inlet of the compressor, the outlet of the first heat exchanger (54) being aligned with the inlet of the compressor (20), for the second configuration, a conduit connects the outlet of the second heat exchanger (50) with an inlet of the first heat exchanger (54), the inlet of the first heat exchanger (54) being aligned with the outlet of the second heat exchanger (50).

2. Packaging system according to the preceding claim, in which the conduit has a length of less than 60 mm.

3. System according to one of the preceding claims, comprising a support carrying on a first face the first exchanger (54) and on a second opposite face the compressor or the second exchanger (50).

4. System according to the preceding claim, in which the support comprises a window (216) and the conduit passes through said support from the first face to the second face through this window (216).

5. System according to one of the preceding claims, comprising a refrigerant circulation unit (217) comprising at least one channel (218).

6. System according to the preceding claim, in which the support (200) is formed in a part separate from said at least one channel and comprising a flat receiving zone on which is applied a face of said at least one first wall element of said at least one channel (218).

7. System according to claim 5, wherein the support is formed by the circulation unit, the circulation unit carrying on a first face the first heat exchanger (54) and on a second opposite face the compressor (20) or the second heat exchanger (50).

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