Assembly for a thermal conditioning system for a vehicle, particularly an automobile

Abstract

The invention relates to a fluid circulation unit (217) for a vehicle thermal conditioning system comprising a plurality of channels (218) each connecting two components of a refrigerant circuit, each channel being formed of a first planar wall element (218a) and a second wall element, each second wall element (218b) being shaped so as to delimit a cavity which is closed by the first wall element, in which at least two channels of the plurality of channels are such that the first wall elements (218a) are formed by the same part (221) and the second wall elements (218b) are formed in separate parts.

Description

Title of the invention: Assembly for a thermal conditioning system for a vehicle, particularly an automobile

[0001] 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.

[0002] Thermal conditioning systems commonly use a refrigerant loop and a heat transfer fluid loop exchanging heat with the refrigerant. Such systems are thus called indirect. The refrigerant loop is formed 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 air flow intended for the passenger compartment in order to heat it. The heat transfer fluid circuit also makes it possible to cool elements of the vehicle's powertrain that dissipate heat, such as the vehicle's electric traction motor or the power electronics controlling the electric motor. For this, another heat exchanger makes it possible to carry out a heat exchange between the heat transfer fluid and the refrigerant in order to cool the heat transfer fluid.

[0003] There is thus a need to be able to have thermal conditioning systems which can offer different modes of cooling and / or heating the battery or different elements of the vehicle's powertrain, in particular without requiring circulation of pressurized refrigerant fluid.

[0004] Thermal conditioning systems consist in particular of thermal management components, such as pumps, valves, heat exchangers, as well as components for temperature regulation. Components, such as conduits, are also provided for guiding a fluid and fluidically connecting the thermal management components to each other.

[0005] 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, space-saving systems reduced, lightweight, simple to manufacture and integrate into the environment of a motor vehicle.

[0006] The invention aims to propose a solution to improve the situation.

[0007] To this end, the present invention provides a fluid circulation unit for a vehicle thermal conditioning system comprising a plurality of channels each connecting two components of a refrigerant circuit, each channel being formed of a first planar wall element and a second wall element, each second wall element being shaped to delimit a cavity which is closed by the first wall element, wherein at least two channels of the plurality of channels are such that the first wall elements are formed by the same part and the second wall elements are formed in separate parts.

[0008] In this configuration, at least some of the second elements can be made in two separate parts, which facilitates their manufacture. The production of the part comprising the first wall elements is simple. The assembly of the refrigerant circulation unit is also simplified. Furthermore, the positioning of each second wall element on a first wall element can be improved due to the independence of the second wall elements.

[0009] All the channels may have their first wall elements formed in a single part. Thus, a part comprises all the first wall elements which are all formed on a single part. This part thus comprises a plurality of different zones each delimiting said first wall elements.

[0010] Said first wall elements of the first channels may be formed in the same substantially flat part, such as a flat plate.

[0011] Spaces may be provided between all or part of said first wall elements. In this way, it is possible to reduce the heat transmission between two first wall elements.

[0012] The second wall elements of said at least two channels may have different thicknesses.

[0013] The second wall elements of said at least two channels may be formed from different materials.

[0014] At least two channels may have their second wall element formed by the same part. When the channels are close, it is indeed preferable to form some of the second wall elements in the same part, others of the second wall elements being different.

[0015] Each second wall element may comprise a boss defining a groove and surrounded by a peripheral rim applied to a corresponding peripheral edge of a first wall element.

[0016] The peripheral edge of a first wall element may be welded or brazed to a peripheral edge of a second wall element.

[0017] At least two channels may have different sections.

[0018] Spaces are provided between all or part of said second wall elements. In this way, it is possible to reduce the heat transmission between two second wall elements.

[0019] Each channel may extend between a first end and a second end, each second wall member including an orifice formed at at least one of its first and second ends.

[0020] The present document also relates to an assembly for a vehicle thermal conditioning system comprising a refrigerant circulation unit as described above, and a support formed in a separate part of the plurality of channels.

[0021] The support may comprise a flat receiving area on which one face of said first wall elements of said plurality of channels is applied. The support may carry a compressor on the face opposite that comprising the flat receiving area.

[0022] The support can be made of a composite material and / or a plastic material.

[0023] The second wall elements can be manufactured from stamped metal plates.

[0024] 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:

[0025] [Fig-1] is a simplified perspective view of a circulation unit for a fluid management module for a vehicle, particularly an automobile.

[0026] [Fig.2] is a side view of the circulation unit of [Fig.l].

[0027] [Fig.3] is a simplified bottom view of one face of the circulation unit of [Fig.l]; this face presenting the circulation channels and part of the elements arranged on this face.

[0028] [Fig.4] is a simplified top view of the opposite face of the circulation unit.

[0029] [Fig.5] is a schematic view of the refrigerant circuit associated with the unit of circulation of [Fig.l], operating according to a first mode of operation.

[0030] [Fig.6] is a schematic view of the refrigerant circuit associated with the circulation unit of [Fig.l], operating according to a second mode of operation.

[0031] [Fig.7] is a simplified perspective view of the opposite face of [Fig.4], this opposite face showing part of the elements arranged on this second face.

[0032] [Fig.8] is a simplified perspective view of the fluid management module comprising the unit of [Fig.l].

[0033] [Fig.9] is a bottom view of the module of [Fig.8].

[0034] [Fig. 10] is a top view of the fluid management module.

[0035] [Fig. 11] is a schematic view of a first embodiment of the invention wherein 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.

[0036] [Fig. 12] is a schematic view of the refrigerant circulation unit support of [Fig. 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).

[0037] [Fig. 13] is a schematic perspective view of a support with 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.

[0038] [Fig. 14] is a schematic perspective view of the conduits of a refrigerant circulation unit in part A and of only the first wall elements of said conduits in part B.

[0039] [Fig. 15] is a schematic perspective view illustrating the cooperation between first wall elements formed from a single piece and second wall elements.

[0040] [Fig. 16] represents a schematic diagram of an example assembly of a support with first and second wall elements.

[0041] [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 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.

[0042] [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.

[0043] [Fig. 19] [Fig.20] [Fig.21] [Fig.22] represent in perspective an isolated circulation unit support according to a second embodiment.

[0044] [Fig.23] [Fig.24] [Fig.25] represent in perspective the support of figures 19 to 22 with a part of the fluid circulation unit.

[0045] [Fig.26] is a schematic diagram illustrating the positioning of the fixing arms and the installation portion of the compressor on the support.

[0046] The invention relates to the field of thermal conditioning systems 1 for heating and / or cooling electrical and / or electronic elements of an electric or hybrid motor vehicle, as well as the passenger compartment of said vehicle.

[0047] This type of system may comprise a heat transfer fluid circuit for heating and / or cooling the electrical and / or electronic elements, and, preferably, the passenger compartment of the vehicle, as well as a refrigerant fluid 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.

[0048] This type of system may comprise a fluid management module in which the fluid management module comprises a circulation unit 10 (also subsequently referred to as "the unit 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 circulation unit 10 supporting at least the second evaporator and the second face 42 of the circulation unit 10 supporting at least one valve 72-2 or 72-3. This type of module and circuit is for example described in French patent application FR2204401.

[0049] The refrigerant fluid used by the refrigerant circuit 2 is here a chemical fluid such as R1234yf. Other refrigerants could be used, such as for example R 134a, or even R290.

[0050] “High pressure refrigerant” means a refrigerant at a pressure of around 20 bars, “low pressure refrigerant” means a pressure of 3 bars.

[0051] Firstly, the fluid management module of the thermal management system will be described based on Figures 1 to 4. The thermal conditioning system as a whole will then be detailed based on Figures 5 and 6.

[0052] In Figures 1 to 4, the circulation unit 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.

[0053] The unit 10 is also called a central platform (or "hub" in its English name). The circulation unit 10 is intended to be part of a thermal conditioning system 1 of a motor vehicle in which the refrigerant circulates, in particular in an air conditioning and / or heat pump circuit.

[0054] The refrigerant fluid circulation unit 10 here has a function of supporting components such as valves and exchangers, and a function of circulating the fluid with channels. The unit 10 is here 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. In other words, in the case of figures 1 and 4 and subsequently 7 to 10, the unit 10 integrating the channels for the circulation of the refrigerant fluid 2 also has a function of supporting components such as exchangers, valves, etc. To do this, the plates forming the unit 10 each comprise one or more flat regions 15 between the channels 60, 64. 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.

[0055] The unit shown in Figures 1 to 4 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. The unit 10 comprises at least a second plate called support plate 82. The support plate 82 is configured to provide the interface between the circulation unit 10 and elements secured to this unit 10. The support plate 82 may be flat to be in contact with a portion of the elements secured to the unit 10. The support plate 82 partly defines the conduits for the refrigerant fluid.

[0056] In [Fig.3], it can be seen that the unit 10 comprises at least one first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0057] The first channel 60, intended for the circulation of the high-pressure refrigerant fluid, here has a substantially Y-shape, with a main branch 60-1 and two branches called first (60-2) and second (60-3) branches. 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.

[0058] Figures 3 and 4 also show two valve support blocks 70-2 and 70-3, each of which is inserted into a branch 60-2 or 60-3 of the first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0059] 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 [Fig.7].

[0060] Alternative embodiments not shown propose that the circulation unit 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 circulation unit 10 via a valve support block common to several valves and / or an individual support block specific for each valve.

[0061] Thus, the circulation unit 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 circulation unit 10.

[0062] 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 the valve support block 70-2 or 70-3.

[0063] 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.

[0064] A temperature sensor 74 (visible for example in [Fig.7]) is provided at the level of the first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0065] 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).

[0066] More particularly, the temperature sensor 74 is arranged near the junction between the main branch 60-1 and the two ramifications 60-2 and 60-3 of the first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0067] As indicated above, the first channel 60 is intended for the circulation of the high-pressure refrigerant fluid.

[0068] 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.

[0069] The first branch 60-2 is intended to ensure communication between the main branch 60-1 and a condenser 52.

[0070] The condenser 52 is configured to carry out an exchange of calories between the high-pressure refrigerant fluid and a heat transfer liquid.

[0071] 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.

[0072] 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.

[0073] The circulation unit 10 also comprises at least one second channel 62 intended for the circulation of the high-pressure refrigerant fluid.

[0074] The circulation unit 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.

[0075] 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.

[0076] In [Fig.9], the first heat exchanger 54 is an internal heat exchanger, said internal heat exchanger making it possible to transfer 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.

[0077] 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.

[0078] 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.

[0079] 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 referred to as the first expansion valve 26.

[0080] 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 fluid to pass through can be adjusted continuously 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 fluid.

[0081] The first expansion valve 26 is here directly connected to a third flange 103, itself fluidically connected to a first evaporator 48, not shown.

[0082] 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.

[0083] 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.

[0084] The circulation unit 10 also comprises at least one third channel 64, intended for the circulation of the refrigerant fluid at low pressure.

[0085] It can be seen in [Fig. 3] that the circulation unit 10 comprises three third channels 64-1, 64-2 and 64-3 intended for the circulation of the refrigerant fluid at low pressure. 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.

[0086] Here, 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.

[0087] 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.

[0088] The bottle 56 is advantageously an accumulator, configured to contain the refrigerant at low pressure. The bottle 56 may be provided with a refrigerant charging valve 156. According to a variant not shown, the bottle 56 may be a desiccant bottle configured to contain the refrigerant at high pressure and capture the moisture from the refrigerant passing through it. According to this variant, the bottle 56, or desiccant bottle, would be placed on a high pressure portion of the circuit.

[0089] 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.

[0090] Furthermore, the circulation unit 10 comprises a seventh flange 107, fluidically connected to the first evaporator 48.

[0091] The two expansion valves 26, 28 make it possible to control the supply of refrigerant fluid to the first evaporator 48 and to 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 fluid.

[0092] 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.

[0093] It can be seen in [Fig. 3] that 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 pressure is arranged on a second circulation zone 14 of the refrigerant fluid intended for the circulation of the refrigerant fluid at low pressure.

[0094] The first circulation zone 12 of the refrigerant fluid extends substantially along a first plane PI and the second circulation zone 14 of the refrigerant fluid extends substantially along a second plane P2 and in which the first plane PI 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.

[0095] 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.

[0096] The circulation unit 10 comprises a third zone 18 capable of receiving at least in part 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.

[0097] The third zone 18 extends substantially along a third plane P3, the third plane P3 being different from the first plane PI 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. The first plane PI 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.

[0098] The third zone 18 and the second circulation zone 14 of the refrigerant fluid are connected by a second common edge 22.

[0099] The circulation unit 10 comprises a first opening 32 extending at least over the third zone 18 capable of receiving at least in part the compressor 20.

[0100] This first opening 22 can be seen as a cutout making it possible to lighten the circulation unit and making it possible to define two fixing lugs for the compressor 20.

[0101] 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.

[0102] It can be seen in [Fig.8] that the circulation unit 10 comprises a second opening 24, the second opening 24 receiving at least in part a fifteenth flange 115.

[0103] This fifteenth flange 115 ensures fluid communication between the first heat exchanger 54 and the compressor 20.

[0104] According to another aspect of the invention, not shown here, the fifteenth flange 115 could belong to the circulation unit 10.

[0105] It can be seen in Figures 8 to 10 that the second face 42 of the circulation unit also accommodates a compressor 20. The compressor 20 is secured to the second face 42 of the circulation unit by any means such as, for example, screws.

[0106] It can be seen in Figures 8 and 10 that the second face 42 of the circulation unit also accommodates a bottle 56. In other words, the bottle 56 is secured to the second face 42 of the circulation unit 10.

[0107] The condenser 52 is arranged on a first circulation zone 12 of the refrigerant fluid of the unit 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 unit 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.

[0108] It can be seen in [Fig. 10] that the compressor 20 and the bottle 56 each have 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. This arrangement is also repeated in the first embodiment, as can be seen in Figure 12b.

[0109] The longitudinal extension directions L4 and L5, respectively of the compressor 20 and of the bottle 56, extend parallel to the first, second and third planes PI, P2 and P3.

[0110] 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.

[0111] The thermal conditioning system 1 within the refrigerant circuit 2 will now be described in relation to FIGS. 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.

[0112] 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].

[0113] In order to facilitate understanding, it should be considered that only the pipes symbolized by solid lines in [Fig.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.

[0114] In this first mode of operation, the compressor 20, described previously, makes it possible to compress the refrigerant fluid in order to increase its pressure, and, by consequently, its temperature. Thus, it is understood that at the outlet of the compressor 20, the high-pressure refrigerant 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 at the outlet of the compressor 20 circulates in a first pipe 110a, external to the circulation unit 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.

[0115] 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 operating mode 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.

[0116] 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, the passage is made from the high-pressure portion of the refrigerant circuit 2 to the low-pressure portion of the latter.

[0117] 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 circulating in one of the third channels 64-2 is mainly in the gaseous state.

[0118] 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 unit 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, so that it exits at least partially in the gaseous state in a third pipe 110c, external to the unit 10, up to a seventh flange 107 of the unit 10.

[0119] 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 unit 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 110e, external to the unit 10, to the bottle 56. The bottle 56, or accumulator, collects a liquid fraction of the refrigerant at the outlet of the second evaporator 50 and / or the first evaporator 48. Such a passage through the bottle 56 is necessary prior to the passage of the refrigerant into the compressor 20 which can only accept the refrigerant in the gaseous state.

[0120] At the outlet of the bottle 56, the refrigerant, in the gaseous state and still at low pressure, is directed, via a sixth pipe IlOf, external to the circulation unit 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 circulation unit 10, so that the latter increases its pressure and its temperature as described previously. According to the operating mode illustrated in figures 5 and 6, the fifteenth flange 115 is directly integrated into the first exchanger 54. According to a variant, not illustrated, this fifteenth flange 115 could belong to the circulation unit 10.We understand that thus, at the output of compressor 20, we . switches back into the high pressure portion of the refrigerant circuit 2 and a new thermodynamic cycle can take place.

[0121] 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].

[0122] In order to facilitate understanding, it should be considered that only the pipes symbolized by solid lines in [Fig.6] will be described, since they are implemented in the second operating mode. Furthermore, thicker lines of the pipes make it possible to symbolize the portions of the refrigerant circuit 2 where the refrigerant is at high pressure.

[0123] In the same way as for the first operating mode, at the outlet of compressor 20 in the first pipe 110a, external to the unit 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 100, 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 leaves the internal condenser 46 via a ninth pipe 110i.

[0124] 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 pass from the high pressure portion of the refrigerant fluid circuit 2 to the low pressure portion of the latter.

[0125] 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 circuit of refrigerant fluid 2 in an identical manner to that described previously for the first operating mode.

[0126] 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.

[0127] 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.

[0128] We now refer to [Fig. 1 1] which represents a circulation unit support according to a first embodiment of the invention. In [Fig. 11] is represented a support 200 of a unit 217 for circulating a refrigerant fluid. According to this embodiment, the support 200 has a general shape of a substantially flat plate and comprising a first face 200a and a second face 200b opposite one another and formed on either side of a median extension plane PM 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. The support-circulation unit assembly according to the first embodiment can be applied to a circuit and for a thermal conditioning system as described above but is in no way limited to this circuit and this system.

[0129] As shown, the first face 200a of the support 200 comprises a flat receiving zone 202 intended to receive refrigerant circulation channels 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 218 applied against the first face 200a of the support 200 and tubular conduits 206 which are spaced from the support 200. This type of conduit is illustrated at 110g in [Fig. 8] and also with reference to FIG. 12A at 206.

[0130] 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, i.e. with a hexagonal section. The ribs make it possible to stiffen the support.

[0131] In Figure 1 1A, it can be seen that the flat receiving area 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.

[0132] The support 200 thus formed with a flat receiving zone 202 surrounded by a lattice structure proves to be rigid and light. 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 and does not transmit heat. 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.

[0133] The second surface 200b of the support 200 comprises a portion for installing the compressor 20. The compressor also provides additional rigidity to the assembly and prevents twisting of the support.

[0134] The receiving member 212 of the compressor is advantageously formed opposite the flat receiving zone 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.

[0135] The support 200 comprises arms 214a, 214b, 214c substantially perpendicular to the plane of extension 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. A third arm 214c extends in the same manner as the second arm 214b. The arms may comprise threaded metal tubular inserts for the passage of attachment members to the chassis. The attachment members may also be attached directly through the arms without an insert.

[0136] 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.

[0137] [Fig. 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.

[0138] We now refer to [Fig. 13] which illustrates a support 200 identical to that described with reference to [Fig.l 1] 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.

[0139] The channels illustrated with reference to [Fig. 13] but also with reference to [Fig. 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.

[0140] According to one aspect of the invention, each second wall element 218b comprises a peripheral edge 219b surrounding the boss or the 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.

[0141] As illustrated in Figure 14A and [Fig.15], the first wall elements 218a are formed in a single piece. In this embodiment, they are all formed in the same piece 221 which is applied to the support 200 ([Fig. 16]).

[0142] Screw-nut connections may be provided to provide the connection between the circulation unit 217 and the support 200. Metal inserts may be present in the support to cooperate with the screws. Screwing the screw into a thread in the support, possibly the threading of a recessed insert, may also be proposed.

[0143] The part 221 advantageously has two substantially flat faces, a first 221a applied to the face 200a of the support 200 and a second face 221b receiving the second wall elements 218b. The second wall elements can in particular be manufactured from stamped metal plates.

[0144] Thus, in one embodiment, the part 221 has the shape of a plate having two faces 221a, 221b which are parallel and flat.

[0145] It is also observed that the second wall elements 218b may be formed separately from each other (in separate pieces) and are each coupled to a first wall element 218a. Each second wall element 218b comprises an orifice 223 formed at at least one of its first and second ends.

[0146] 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.

[0147] As illustrated in Figures 14, 15 and 16, spaces 224 may be provided between all or part of said first wall elements and / or 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.

[0148] We now refer to [Fig. 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.

[0149] 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 fluid which circulates 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.

[0150] In a second configuration illustrated in [Fig. 18], the outlet of a second heat exchanger, such as the second evaporator 50 could be aligned at least partially with an inlet of the first heat exchanger 54. In this case, the evaporator could be directly connected to the inlet of the first heat exchanger 54. In this second configuration, the second heat exchanger 50 is then arranged in place of the compressor which can be offset outside the support 200.

[0151] By aligned orifice, it is understood that at least a portion of the section of an outlet orifice is aligned with a portion of the section of an inlet orifice. And more specifically the sections of the orifices can be coaxial without being totally identical and can also be identical.

[0152] The length of the conduit which connects the two components concerned by the first configuration ([Fig.17]) or the second configuration ([Fig.18]) may be less than 60 mm, for example between 20 and 50 mm, in particular between 30 and 40 mm.

[0153] A second embodiment of the invention is shown in Figures 19 to 25. This embodiment is distinguished by the implementation of a support of a different shape and by a different channel configuration for the circulation unit.

[0154] Figures 19 and 20 show the support isolated on the side of the first face 200a while Figures 21 and 22 show the support isolated on the side of the second face 200b.

[0155] In this second embodiment, the support comprises at least one recess 241 inside which the receiving zone 202 is located. The support 200 comprises cavities 251, 252.

[0156] The cavities 251, 252 are arranged in the first face 200a of the support as well as in the second face 200b of the support. The cavities 251, 252 of the support are blind. In other words, the cavities have a bottom and form pockets, hollow relative to the first face 200a and the second face 200b. Preferably, the cavities 251, 252 have a polyhedron or prism shape extending orthogonally to the receiving zone 202, for example a right prism shape with a hexagonal base or a diamond base. Some cavities are located within the receiving zone.

[0157] It can be seen that the cavities 251, 252 of one and / or the other of the first face 200a and the second face 200b are arranged in a staggered pattern.

[0158] The support comprises a first group of cavities 251 arranged in the first face 200a and a second group of cavities 252 arranged in the second face 200b, the cavities 252 of the second group each being arranged between several cavities 251 of the first group of cavities 251, the cavities 251 of the first group and the cavities 252 of the second group being offset from each other.

[0159] As can be seen in [Fig.21], the cavities 251, 252 are distributed so that the support has a substantially constant thickness within the receiving zone 202.

[0160] In this [Fig.21], we see that in a section perpendicular to the longitudinal direction of the support passing through the receiving zone, the support 202 has a section winding on either side of a median plane PM of the plate.

[0161] In Figures 21 and 22, it can be seen that the support comprises a third group of cavities 253 arranged in the second face (200b), the third group of cavities (253) being in the shape of a right prism with a diamond base. The cavities 253 of the third group of cavities each extend between two cavities 252 of the second group of cavities. The cavities of the first group of cavities 251 comprise a bottom 251a and the cavities 253 of the third group of cavities each extend between two bottoms 251a of cavities 251 of the first group of cavities.

[0162] As previously, the circulation unit 217 comprises a plurality of channels 218 connecting a plurality of components of a fluid circuit. At least two channels of the plurality of channels being such that the first wall elements are formed by a same part 221 and that the second wall elements 218b are formed in separate parts. A plurality of first wall elements is disposed in the recess 241.

[0163] Several first wall elements 218a of the channels are formed in the same flat plate.

[0164] In this embodiment, the assembly comprises a plurality of circulation units 2171, 2172, 2173 each comprising at least one first wall element and at least one second wall element, the first wall elements of the different units being formed by separate plates spaced apart from each other, each circulation unit comprising a single flat plate for forming its or its first wall elements. Advantageously, these flat plates are arranged in the same plane.

[0165] In [Fig.23], it can be seen that the recess is delimited by a rim 242 and one of the flat plates comprises a border 1181 of which at least a part is placed against the rim 242 of the recess 241.

[0166] The support 200 comprises at least one through window 216 and the fluid circulation unit 217 comprises at least one through conduit which passes through this window to circulate the fluid from one side to the other of the support 200; the through conduit also passing through a passage orifice formed in a flat plate forming several first wall elements, the passage orifice opening inside the window 216 of the support.

[0167] As previously, the support 200 comprises fixing arms 214a, 214b, 214c to a chassis of a vehicle.

[0168] The receiving area 202 and the fixing arms 214a, 214b, 214c are formed on the same part. In other words, the support is monolithic from the receiving area to the fixing arms. These fixing arms 214a, 214b, 214c extend substantially orthogonally to the receiving area of ​​the support to one end.

[0169] The fixing arms 214a, 214b, 214c each comprise a housing, each housing being capable of receiving a damping decoupling element intended to cooperate with a fixing element of the vehicle chassis. Each housing extends along an axis perpendicular to the direction of extension of the corresponding arm.

[0170] The support preferably comprises at least three arms 214a, 214b, 214c.

[0171] In this embodiment, the two arms 214a and 214c are arranged so that one of these two arms 214a extends from the first face 200a and extends the other of these two arms 214c which extends from the second face 200b.

[0172] It can be seen in [Fig.22] that a set of cavities extend along the fixing arm 214b. This set of cavities extends perpendicular to the receiving zone 202. This arm 214b comprises a plurality of cavities closed at the end of the arm and open on the first face 200a and at least one cavity open at the end of the arm and closed in the plane of the first face 200a. The cavities of the arm have hexagonal and / or diamond sections.

[0173] The support 200 comprises an installation portion 212 capable of receiving a compressor 20. As in the first embodiment, the installation portion 212 is formed to project relative to the second face 200b of the support 200, and in one piece with the receiving zone 202 of the support. The installation portion has a curved concavity capable of retaining two opposite sides of the compressor.

[0174] While the receiving concavity was formed by the ribs in the first embodiment, the curved concavity is formed here by a portion of cylinder extending between two ridges.

[0175] The concavity is supported by ribs 212a connecting the two ridges 212c to the first face. The ribs are parallel. A portion of the receiving area 202 is formed by the end of the ribs of the installation portion of the compressor. The plate extends around the installation portion 212 in this second embodiment. Only the ends of the ribs form a portion of the receiving area 202 opposite the installation portion 212.

[0176] The installation portion also comprises three threads 213 arranged orthogonally to the receiving zone 202. The threads 213 can be formed directly in the support 200 or in added inserts. Thus the compressor 29 can be screwed onto the support.

[0177] The threads 213 are provided inside tubes, each tube extending from the first face 200a to one of the ridges 212c. For example, the tubes 212f are arranged in support cones 212d of the installation portion 212.

[0178] It is also noted in [Fig.22] that the support also advantageously comprises a concave receiving portion 279 arranged to fit the shape of an accumulator or a bottle.

[0179] [Fig.26] shows schematically the positioning of the arms and the installation portion of the compressor within the support according to the first and second embodiments. Considering a median straight line LM perpendicular to the length L1 of the support 200 and separating the support into two substantially equal half-surfaces DSI and DS2 of support, the compressor 20 is arranged so that it spans the median line LM. The compressor thus provides additional rigidity to the assembly and prevents twisting of the support.

[0180] The fixing arms 214a, 214b; 214c are arranged so that each thread 213 is arranged longitudinally between the center line LM and one of the arms 214A, 214b, 214c.

[0181] The compressor 20 extends longitudinally over at least a quarter of the length L1 of the support 200.

[0182] Considering two straight lines LP1 and LP2 perpendicular to the length L1 of the support and separating the support into three portions of support surfaces PSI, PS2, and PS3 substantially equal, the arms are arranged on each portion of end surface PSI and PS3.

[0183] Generally speaking, the plurality of channels of the circulation unit extends substantially parallel to the axis of the compressor 20, in other words perpendicular to the ribs 212a of the installation portion 212 of the compressor 20. The installation portion being configured so that the compressor extends longitudinally parallel to the length L1 of the support and substantially in the same direction as the plurality of channels of the circulation unit, the compressor makes it possible to effectively stiffen the support-circulation unit assembly.

Claims

Claims

1. Assembly for a vehicle thermal conditioning system, said assembly comprising: - a refrigerant circulation unit (217) comprising a plurality of channels (218) each connecting two components of a refrigerant circuit and - a support formed in a part separate from the plurality of channels, in which each channel is formed of a first planar wall element (218a) and a second wall element, each second wall element (218b) being shaped so as to delimit a cavity which is closed by the first wall element,the support comprising a flat receiving zone on which is applied one face of said first wall elements of said plurality of channels (218) characterized in that: - at least two channels of the plurality of channels are such that the first wall elements (218a) are formed by the same part (221) and that the second wall elements (218b) are formed in separate parts.,

2. An assembly according to claim 1, wherein all of the channels have their first wall elements (218a) which are formed in a single piece.

3. An assembly according to claim 1 or 2, wherein said first wall elements (218a) of the channels are formed in a single substantially planar part, such as a flat plate.

4. Assembly according to one of the preceding claims, in which spaces (224) are provided between all or part of said first wall elements.

5. Assembly according to one of the preceding claims, in which the second wall elements of said at least two channels have different thicknesses.

6. An assembly according to one of the preceding claims, wherein the second wall elements (218b) of said at least two channels are formed from different materials.

7. Assembly according to one of the preceding claims, in which at least two channels have their second wall element (218b) formed by the same part.

8. An assembly according to any preceding claim, wherein each second wall element comprises a boss defining a groove and surrounded by a peripheral edge (219b) applied to a corresponding peripheral edge (219a) of a first wall element (218a).

9. An assembly according to the preceding claim, wherein the peripheral edge of a first wall element (218a) is welded or brazed with a peripheral edge of a second wall element (218b).

10. Assembly according to one of the preceding claims, in which spaces (224) are provided between all or part of said second wall elements.

11. An assembly according to one of the preceding claims, wherein the second wall elements are made from stamped metal plates.

12. Assembly according to one of the preceding claims, in which the support (200) is made of a composite material and / or a plastic material.

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