Thermal conditioning system for vehicles, in particular motor vehicles

Abstract

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

Description

Technical Field

[0001] This invention relates to the field of thermal regulation systems. These systems are particularly suitable for equipping motor vehicles. Such systems allow for the thermal regulation of various components of the vehicle, such as the interior or energy storage batteries in the case of electric vehicles. Heat exchange is primarily managed through the compression and expansion of refrigerant within various heat exchangers, thereby allowing for the heating or cooling of various components. Background Technology

[0002] Thermal control systems typically utilize a refrigerant circuit and a circuit for a heat transfer fluid that exchanges heat with the refrigerant. Such systems are therefore referred to as indirect. The refrigerant circuit is configured such that the refrigerant releases heat to the heat transfer fluid in a first heat exchanger. The heat released to the heat transfer fluid can then be dissipated into the airflow used for the interior, thus heating it. The heat transfer fluid circuit also allows for the cooling of heat-dissipating components of the vehicle's drivetrain, such as the vehicle's electric drive motor or the power electronics controlling the electric motor. For this purpose, another heat exchanger allows for heat exchange between the heat transfer fluid and the refrigerant, thereby cooling the heat transfer fluid.

[0003] Therefore, there is a need for thermal regulation systems that can provide different modes for cooling and / or heating various components in the battery or vehicle drivetrain, especially without relying on pressurized refrigerant circulation.

[0004] Thermal control systems typically consist of thermal management components such as pumps, valves, heat exchangers, and components for temperature regulation. Components such as pipes are also provided that guide fluid and fluidly connect the thermal management components to each other.

[0005] The development of electric vehicles has increased the demand for optimized thermal control systems with simplified and economical manufacturing methods, while also creating a need for systems that are efficient, compact, lightweight, easy to manufacture, and easy to integrate into the environment of motor vehicles.

[0006] Documents US2019 / 047373, US2004 / 112073 and EP1354735 disclose various types of connections between a compressor and a heat exchanger or between two heat exchangers. Summary of the Invention

[0007] The present invention aims to propose a solution to improve this situation.

[0008] Therefore, the present invention relates to a thermal control system comprising:

[0009] - A refrigerant circuit having at least one of a first configuration including a first heat exchanger and a compressor and a second configuration including a first heat exchanger and a second heat exchanger.

[0010] in:

[0011] In the first configuration, a conduit connects the outlet of the first heat exchanger to the inlet of the compressor, and the outlet orifice of the first heat exchanger is aligned with the inlet orifice of the compressor.

[0012] - In the second configuration, the pipe connects the outlet of the second heat exchanger to the inlet of the first heat exchanger, and the inlet orifice of the first heat exchanger is aligned with the outlet orifice of the second heat exchanger.

[0013] Therefore, compared to existing technologies with bends in the piping, the refrigerant circulating at low pressure from the outlet of the first heat exchanger experiences only a small pressure drop before entering the compressor. The same applies when the outlet of the second heat exchanger is aligned with the inlet of the first heat exchanger. Thus, the refrigerant can circulate more easily.

[0014] Advantageously, the pipe is straight.

[0015] Pipes can have lengths of less than 60 mm, for example, between 20 mm and 50 mm, and especially between 30 mm and 40 mm.

[0016] The support member can support the first exchanger on the first surface and the compressor or the second exchanger on the opposite second surface.

[0017] The support can have a generally flat overall shape.

[0018] The support may include an orifice, through which a pipe can pass from the first side through the support to the second side.

[0019] The system may include a refrigerant circulation unit, which includes at least one channel.

[0020] The fluid circulation unit may include, for example, a block made of aluminum, wherein channels are obtained by drilling or during the casting of the block.

[0021] The channel can be formed by a flat first wall element and a second wall element, the second wall element being shaped in such a way as to define a cavity closed by the first wall element.

[0022] Advantageously, the support is formed in a component different from the at least one channel and includes a flat receiving area on which one face of at least one first wall element of the at least one channel rests.

[0023] Advantageously, the support member carrying the channel includes a flat area of ​​a flat first wall element for receiving the channel. Therefore, the receiving surface is directly disposed on the support member or frame, which can have a flat, integral shape to support the channel of the circulation unit.

[0024] Each first wall element may have a substantially flat overall shape. It may include a substantially flat first surface and a substantially flat opposing second surface. The first and second surfaces may be parallel to each other. In practice, the first surface presses against the flat receiving area, and the second surface receives the second wall element.

[0025] The support member may be formed of a material that is not as dense as the material of the at least one channel.

[0026] The support may include a portion for receiving the compressor, which is formed on the surface of the support opposite to the surface where the flat receiving area is formed. This positioning provides the compressor with additional rigidity and prevents the support from twisting.

[0027] According to another alternative, the cyclic unit forms the support.

[0028] In other words, the circulation unit can carry a first heat exchanger on a first surface and a compressor or a second heat exchanger on the opposite second surface.

[0029] The circulation unit may include multiple channels, each channel connecting two components of the refrigerant circuit, wherein at least two of the multiple channels are such that the first wall element is formed of the same component and the second wall element is formed of different components.

[0030] All channels may have a first wall element formed in the same component.

[0031] The first wall element of the first channel can be formed in the same substantially flat component (such as a plate).

[0032] A space may be formed between all or part of the first wall element and / or the second wall element to reduce heat transfer between the wall elements.

[0033] The second wall elements of the at least two channels can have different thicknesses. This is made more likely by the fact that the second wall elements are formed in different components, unlike the prior art, in which all second wall elements are formed in the same component and all have walls of the same thickness.

[0034] The second wall element of the at least two channels can be made of different materials.

[0035] At least two channels can make their second wall element formed from the same component.

[0036] Each second wall element may include a boss defining a recess, the recess being surrounded by a peripheral edge that can press against a corresponding peripheral edge belonging to the first wall element.

[0037] The peripheral edge of the first wall element is welded or brazed to the peripheral edge of the second wall element.

[0038] In other words, the present invention relates to a thermal control system comprising a refrigerant circuit including a first heat exchanger (e.g., an internal heat exchanger) and at least one of a compressor and a second heat exchanger, wherein conduits connect the outlet of the first heat exchanger to the inlet of the compressor, or connect the inlet of the first heat exchanger to the outlet of the second heat exchanger, and the control system is arranged such that the outlet orifice of the first heat exchanger is aligned with the inlet orifice of the compressor, or the inlet orifice of the first heat exchanger is aligned with the outlet orifice of the second heat exchanger. Therefore, the conduits are preferably straight.

[0039] In other words, the present invention relates to a thermal control system comprising a refrigerant circuit including a first heat exchanger (e.g., an internal heat exchanger) and a conduit connecting the first heat exchanger to an upstream component (e.g., a second heat exchanger) or a downstream component (e.g., a compressor). The conduit is straight and aligned with the outlet port of the upstream component and the inlet port of the first heat exchanger, or with the inlet port of the downstream component and the outlet port of the first heat exchanger. The length of the conduit is preferably less than 60 mm.

[0040] One of a compressor or a second heat exchanger, wherein a conduit connects the outlet of the first heat exchanger to the inlet of the compressor or the first heat exchanger, and the outlet orifice of the first heat exchanger is aligned with the inlet orifice of the compressor or the first heat exchanger.

[0041] The present invention also relates to a thermal regulation system for heating and / or cooling electrical and / or electronic components of an electric or hybrid motor vehicle, and preferably for heating and / or cooling the interior of the vehicle, the thermal regulation system comprising components according to any one of the preceding claims.

[0042] According to one aspect of the invention, the second exchanger is a water-cooled evaporator. This type of water-cooled evaporator allows heat exchange between the refrigerant and the heat transfer liquid (e.g., water-glycol).

[0043] According to one aspect of the invention, the refrigerant circuit may include a condenser of the water-cooled condenser (WCDS) type. A water-cooled condenser of this type is also capable of heat exchange between the refrigerant and the heat transfer liquid (e.g., water glycol).

[0044] In the embodiment shown in the figure, the first heat exchanger is an exchanger referred to as an IHX (internal heat exchanger). An internal heat exchanger type of first heat exchanger allows heat exchange between refrigerant circulating at high pressure and refrigerant circulating at low pressure.

[0045] According to another embodiment, the support can carry a bottle, such as a desiccant bottle, which has the function of separating liquid and gaseous refrigerant under high pressure and capturing and storing moisture from the refrigerant passing through it. The bottle or desiccant bottle can be placed on a second surface of the support. Attached Figure Description

[0046] Other advantages and features of the invention will become clearer from the following description and accompanying drawings, which are given in a non-limiting manner, in which:

[0047] Figure 1 This is a simplified perspective view of the circulation unit of a fluid management module for vehicles (especially motor vehicles).

[0048] Figure 2 yes Figure 1 A side view of the loop unit.

[0049] Figure 3 yes Figure 1 A simplified top view of one face of the circulation unit; the face shows the circulation channel and a portion of the elements arranged on that face.

[0050] Figure 4 This is a simplified view of the opposite sides of the loop unit from above.

[0051] Figure 5 It is operated in the first operating mode and Figure 1 A schematic diagram of the refrigerant circuit associated with the cycle unit.

[0052] Figure 6 It is operated in the second operating mode. Figure 1 A schematic diagram of the refrigerant circuit associated with the cycle unit.

[0053] Figure 7 yes Figure 4 A simplified perspective view of the opposite face, which shows some elements arranged on the second face.

[0054] Figure 8 It includes Figure 1 A simplified perspective view of the fluid management module of the unit.

[0055] Figure 9 yes Figure 8 The bottom view of the module.

[0056] Figure 10 This is a top view of the fluid management module.

[0057] Figure 11This is a schematic diagram of a first embodiment of the present invention, wherein a refrigerant circulation unit support is depicted from a first side in part A and from an opposite second side in part B, the support being shown separately.

[0058] Figure 12 yes Figure 11 A schematic diagram of a refrigerant circulation unit support from a first side in part A and a second side opposite to each other in part B. The support carries the refrigerant circulation unit and components such as a heat exchanger (part A) and a compressor (part B).

[0059] Figure 13 These are schematic perspective views of a support member having a portion of a refrigerant circulation unit in section A, and schematic perspective views of a support member not having a fluid circulation unit in section B.

[0060] Figure 14 This is a schematic perspective view of the piping of the refrigerant circulation unit in part A and the piping in part B, showing only the first wall element.

[0061] Figure 15 It is a schematic perspective view showing the cooperation between the first wall element and the second wall element formed by individual pieces.

[0062] Figure 16 This is a schematic diagram of an example of a support assembly having a first wall element and a second wall element.

[0063] Figure 17 This is a schematic perspective view of a portion of the module associated with the first embodiment, wherein portions A and B are viewed from the same angle, the first heat exchanger (internal heat exchanger) in portion B has been removed, and portion C shows a cross-sectional view of the pipes through which the compressor fluid is connected to the first heat exchanger.

[0064] Figure 18 This is a schematic diagram showing the alignment of the outlet of the second heat exchanger associated with the module according to a variant embodiment with that of the first heat exchanger. Detailed Implementation

[0065] This invention relates to a thermal regulation system 1 for heating and / or cooling electrical and / or electronic components of an electric or hybrid motor vehicle, and preferably for heating and / or cooling the interior of the vehicle. The thermal regulation system comprises: a heat transfer liquid circuit for heating and / or cooling electrical and / or electronic components, and preferably for heating and / or cooling the interior of the vehicle; a refrigerant circuit 2 including a condenser 52, a compressor 20, a first evaporator 48 for cooling the interior of the vehicle, and a second evaporator 50 for cooling electrical and / or electronic components, such that the second evaporator 50 is thermally connected to the heat transfer liquid circuit; and a fluid management module, characterized in that the fluid management module comprises: a support member 10 having a first surface 40 and a second surface 42, the first surface 40 being on the opposite side of the second surface 42; and at least one channel 60, 62, 64 for the refrigerant circuit 2, the first surface 40 of the support member 10 supporting at least the second evaporator, and the second surface 42 of the support member 10 supporting at least one valve 72-2 or 72-3.

[0066] The refrigerant used in refrigerant circuit 2 in this case is a chemical fluid such as R1234yf. Other refrigerants, such as R134a or R290, can also be used.

[0067] "High-pressure refrigerant" refers to refrigerant with a pressure of around 20 bar, while "low-pressure refrigerant" refers to refrigerant with a pressure of 3 bar.

[0068] First, will Figures 1 to 4 The fluid management module of the thermal management system is described with the support of [the relevant authority]. Then [then...] Figure 5 and Figure 6 The entire thermal control system will be described in detail with the support of [the relevant authority / resources].

[0069] exist Figures 1 to 4 In a particular embodiment of the fluid management module of the thermal regulation system 1 shown in the figure, the support 10 is composed of at least a first refrigerant circulation region 12 and a second refrigerant circulation region 14. The first refrigerant circulation region 12 is used for the circulation of refrigerant under high pressure, and the second refrigerant circulation region 14 is used for the circulation of refrigerant under high pressure and / or low pressure.

[0070] The support 10 is also referred to as the center platform (or hub). The support 10 is intended to form part of the thermal regulation system 1 of the motor vehicle, in which refrigerant circulates, particularly in the air conditioning and / or heat pump circuit.

[0071] In other words, the support 10 includes a refrigerant circulation unit.

[0072] According to the embodiment shown here, the support 10 consists of two plates fixed to each other. In this case, the passage for the refrigerant circuit 2 is formed by deformation of at least one of the two plates.

[0073] In other words, and in this particular embodiment, the support 10 includes a channel for the refrigerant circuit 2.

[0074] According to this embodiment, each plate forming the support 10 includes one or more flat regions 15 between channels 60, 64.

[0075] Again, according to this embodiment, the thickness of the plate forming the support is substantially uniform in both the flat area and the channels 60 and 64.

[0076] One particular embodiment shown here proposes that the support 10 includes at least one first plate, referred to as a transfer plate 80, which is shaped to form at least one channel or fold for fluid circulation. In other words, the curvature of the transfer plate 80 constitutes a pathway for forming the channel.

[0077] Still in this particular embodiment, the support 10 includes at least a second plate, referred to as support plate 82. Support plate 82 is configured to provide an interface between the support 10 and the elements fixed to the support 10.

[0078] The support plate 82 may be flat so as to contact a portion of the element fixed to the support member 10.

[0079] In other words, in this embodiment, the support plate 82 partially defines the conduit for the refrigerant.

[0080] exist Figure 3 In the illustrated embodiment, the support 10 includes at least one first channel 60, which is designed for the circulation of refrigerant under high pressure.

[0081] In the embodiment shown here, the first channel 60 for circulating the refrigerant under high pressure has a substantially Y-shaped shape, having a main branch 60-1 and two branches referred to as the first branch (60-2) and the second branch (60-3).

[0082] In a particular embodiment, at least one valve support block is inserted into a branch of a first channel 60, which is intended for the circulation of refrigerant under high pressure.

[0083] exist Figure 3 and Figure 4 In the specific embodiment shown, two valve support blocks 70-2 and 70-3 are each inserted into a branch 60-2 or 60-3 of a first channel 60, which is intended for refrigerant circulation under high pressure.

[0084] In this configuration, valve support blocks 70-2 and 70-3 can each receive a valve, particularly a shut-off valve 72-2 or 72-3, such as... Figure 7 As shown.

[0085] According to an alternative embodiment not shown, the support 10 includes valves, such as progressive valves, EXVs (electronic expansion valves), or TXVs (thermostatic expansion valves). These valves are preferably secured to the support 10 via a valve support block shared by several valves and / or a separate support block dedicated to each valve.

[0086] Therefore, the support 10 includes at least one valve support block 70-2 or 70-3, which can be considered as a block for distributing refrigerant in the support 10.

[0087] In other words, shut-off valve 72-2 or 72-3 is positioned in fluid communication with first channel 60, which is intended for circulating refrigerant via valve support block 70-2 or 70-3 under high pressure (in this particular embodiment).

[0088] More specifically, in this case, fluid communication is achieved at each corresponding branch 60-2 or 60-3 of the first channel 60, which is designed for the circulation of refrigerant under high pressure.

[0089] Temperature sensor 74 (e.g. in Figure 7 (As shown in the image) is located at the first channel 60, which is intended for the circulation of refrigerant under high pressure.

[0090] In the embodiment shown here, the temperature sensor 74 is arranged on one of the two branches of the first channel 60 intended for circulating the refrigerant under high pressure (in this case, the second branch 60-2).

[0091] More specifically, the temperature sensor 74 is located near the junction between the main branch 60-1 of the first channel 60 for refrigerant circulation under high pressure and the two branches 60-2 and 60-3.

[0092] As described above, the first channel 60 is used for refrigerant circulation under high pressure.

[0093] In this embodiment, the main branch 60-1 of the first channel 60 is designed to ensure communication between the first flange 101 of the compressor 20 and the first (60-2) and second (60-3) branches.

[0094] The first branch 60-2 is designed to ensure the connection between the main branch 60-1 and the condenser 52.

[0095] The condenser 52 is configured to exchange heat between the refrigerant and the heat transfer liquid under high pressure.

[0096] The second branch 60-3 is designed to ensure communication between the main branch 60-1 and the second flange 102, which is fluidly connected to the internal condenser 46 (not shown here).

[0097] The internal condenser 46 is a heat exchanger for use inside a vehicle, for example, located inside the vehicle. The internal condenser 46 is used to heat the airflow passing through it.

[0098] The support 10 also includes at least one second channel 62, which is designed for the circulation of refrigerant under high pressure.

[0099] exist Figure 3 In the specific embodiment shown, the support 10 includes five second channels 62-1, 62-2, 62-3, 62-4 and 62-5 designed for refrigerant circulation under high pressure.

[0100] In the same embodiment, one of the second channels (hereinafter referred to as 62-1) is designed to ensure communication between the condenser 52 and another heat exchanger (hereinafter referred to as the first heat exchanger 54).

[0101] according to Figure 9 In the illustrated embodiment, the first heat exchanger 54 is an internal heat exchanger that allows heat to be transferred between the low-pressure portion and the high-pressure portion of the refrigerant circuit 2. This heat exchange allows for optimization of the thermodynamic properties of the refrigerant circuit 2.

[0102] In the same embodiment still shown here, one of the second channels (hereinafter referred to as 62-2) is designed to ensure communication between the first heat exchanger 54 and the joint, which is split to form one of the second channels (hereinafter referred to as 62-3) and the other of the second channels (hereinafter referred to as 62-4).

[0103] The second channel 62-3 is designed to ensure communication between the second channel 62-2 and the valve (preferably an expansion valve). In the remainder of the specification, this expansion valve will be referred to as the second expansion valve 28.

[0104] In the same embodiment still shown 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 specification, this expansion valve will be referred to as the first expansion valve 26.

[0105] Each of the expansion valves 26 and 28 can be an electronic expansion valve or EXV, a thermostatic expansion valve or TXV, or a calibration orifice. In the case of an electronic expansion valve, the flow area allowing refrigerant to pass through can be continuously adjusted between a closed position and a fully open position. For this purpose, an electronic controller controls an electric motor that moves a movable closing device, thereby controlling the available flow area of ​​refrigerant.

[0106] The first expansion valve 26 is directly connected here to the third flange 103, which itself is fluidly connected to the first evaporator 48 (not shown).

[0107] The first evaporator 48 is an exchanger for heat regulation inside the vehicle, for example, located inside the vehicle. The first evaporator 48 is used to cool the airflow passing through it.

[0108] In the same embodiment, a second channel in the second channel (hereinafter referred to as 62-5) is designed to ensure communication between the second channel 62-2 and the fourth flange 104, which is fluidly connected to the internal condenser 46.

[0109] The support 10 also includes at least one third channel 64 for refrigerant circulation at low pressure.

[0110] exist Figure 3 In the specific embodiment shown, the support 10 includes three third channels 64-1, 64-2 and 64-3 for refrigerant circulation at low pressure.

[0111] According to the same embodiment, one of the third channels (hereinafter referred to as 64-1) is designed to ensure communication between the second expansion valve 28 and the second evaporator 50.

[0112] According to this embodiment, the second evaporator 50 is a stacked plate water-cooled cooler (or refrigeration unit) type. The second evaporator is configured to exchange heat energy between the refrigerant and the heat transfer liquid at low pressure.

[0113] In the same embodiment still shown here, one of the third channels (hereinafter labeled 64-2) is designed to ensure communication between the second evaporator 50 and the fifth flange 105 that is fluidly connected to the bottle 56.

[0114] According to this embodiment, bottle 56 is a collector configured to contain refrigerant at low pressure.

[0115] According to this embodiment, bottle 56 may be equipped with a refrigerant loading valve 156.

[0116] According to another embodiment (not shown), bottle 56 may be a desiccant bottle configured to contain refrigerant under high pressure and capture moisture from the refrigerant passing through it. According to this other embodiment, bottle 56 or the desiccant bottle will be placed on the high-pressure section of the circuit.

[0117] In the same embodiment shown here, one of the third channels (hereinafter labeled 64-3) is designed to ensure fluid connection between the sixth flange 106 of bottle 56 and the first heat exchanger 54.

[0118] In addition, the support member 10 includes a seventh flange 107 that is fluidly connected to the first evaporator 48.

[0119] The two expansion valves 26 and 28 allow for control of the refrigerant supply to the first evaporator 48 and the second evaporator 50. Therefore, depending on the position of the expansion valves 26 and 28, refrigerant can be supplied to the first evaporator 48 and / or the second evaporator 50.

[0120] According to one embodiment, a first heat exchanger (54), a second evaporator (50), and a condenser (52) are fluidly connected via flanges to a first channel 60, a second channel 62, and a third channel 64. More specifically, the first heat exchanger 54 is connected to the second channel 62-1, the second channel 62-2, and the third channel 64-3 via eighth, ninth, and tenth flanges, respectively; the second evaporator 50 is connected to the third channel 64-1 and the third channel 64-2 via eleventh and twelfth flanges, respectively; and the condenser 52 is connected to the first branch 60-2 and the second channel 62-1 of the first channel 60 via thirteenth and fourteenth flanges, respectively.

[0121] exist Figure 3 In the embodiments particularly shown in the following figures, at least a first channel 60 for refrigerant circulation under high pressure is arranged in a first refrigerant circulation region 12 for refrigerant circulation under high pressure, while at least a third channel 64 for refrigerant circulation under low pressure is arranged in a second refrigerant circulation region 14 for refrigerant circulation under low pressure.

[0122] In this embodiment, the first refrigerant circulation region 12 extends substantially in the first plane P1, and the second refrigerant circulation region 14 extends substantially in the second plane P2, wherein the first plane P1 of the first refrigerant circulation region 12 and the second plane P2 of the second refrigerant circulation region 14 are different.

[0123] In this embodiment, the first refrigerant circulation region 12 and the second refrigerant circulation region 14 are connected by a first common edge 16.

[0124] In this embodiment, the support 10 includes a third region 18 capable of receiving at least a portion of the compressor 20, the third region 18 being different from the first refrigerant circulation region 12 and the second refrigerant circulation region 14.

[0125] In this embodiment, the third region 18 extends substantially within a third plane P3, which is different from the first plane P1 of the first refrigerant circulation region 12 and different from the second plane P2 of the second refrigerant circulation region 14. In this embodiment, the first plane P1 of the first refrigerant circulation region 12, the second plane P2 of the second refrigerant circulation region 14, and the third plane P3 of the third region 18 are parallel planes.

[0126] In this embodiment, the third region 18 and the second refrigerant circulation region 14 are connected by a second common edge 22.

[0127] In this embodiment, the support 10 includes a first opening 32 extending at least over the third region 18, which is capable of receiving at least a portion of the compressor 20.

[0128] The first opening 22 can be considered a cut, which allows the support 10 to be lighter and allows the two attachment lugs for the compressor 20 to be defined.

[0129] In this embodiment, the first opening 32 also extends on the second edge 22 shared by the third region 18 and the second refrigerant circulation region 14.

[0130] exist Figure 8 In the embodiment specifically depicted, the support 10 includes a second opening 24 that at least partially receives the fifteenth flange 115.

[0131] The fifteenth flange 115 provides fluid communication between the first heat exchanger 54 and the compressor 20.

[0132] According to another aspect of the invention (not shown here), the fifteenth flange 115 may belong to the support member 10.

[0133] exist Figure 8 and Figure 10 In the embodiment specifically depicted, the second surface 42 of the support 10 also includes a compressor 20.

[0134] In this embodiment, the compressor 20 is fixed to the second surface 42 of the support 10 by any means (e.g., screws).

[0135] exist Figure 8 and Figure 10 In the embodiment specifically depicted, the second side 42 of the support 10 also includes a bottle 56.

[0136] In other words, in this embodiment, the bottle 56 is fixed to the second side 42 of the support 10.

[0137] according to Figure 9 In the embodiment depicted, 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, the second evaporator 50, and the condenser 52 defines longitudinal extension directions L1, L2, and L3, respectively. The longitudinal extension directions L2 and L3 of the second evaporator 50 and the condenser 52 are parallel. 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.

[0138] This distribution also helps to improve the efficiency of heat exchange through the modules by helping to generate thermal gradients.

[0139] Still according to this embodiment, the condenser 52 is arranged in the first refrigerant circulation region 12 of the support 10, which is used for refrigerant circulation under high pressure, and the second evaporator 50 and the first heat exchanger 54 are arranged in the second refrigerant circulation region 14 of the support 10, which is used for refrigerant circulation under high pressure and / or refrigerant circulation under low pressure.

[0140] according to Figure 10 In the embodiment depicted, the compressor 20 and the bottle 56 each include longitudinal extending directions L4 and L5, respectively, and wherein the longitudinal extending direction L4 of the compressor is perpendicular to the longitudinal extending direction L5 of the bottle 56.

[0141] The longitudinal extension directions L4 and L5 of the compressor 20 and bottle 56 extend parallel to the first plane P1, the second plane P2 and the third plane P3, respectively.

[0142] The arrangement of the compressor 20 and the bottle 56 allows for a more compact fluid management module in the thermal regulation system 1.

[0143] Now we will combine Figure 5 and Figure 6 The thermal regulation system 1 within the refrigerant circuit 2 is described. Furthermore, the refrigerant circuit 2 will be described starting with the compressor 20; however, it should be understood that the compressor only represents a hypothetical starting point for the refrigerant circuit 2, and that the refrigerant circuit 2 forms a closed loop.

[0144] Now we will combine Figure 5 A first operating mode of the refrigerant circuit 2 is described, the refrigerant circuit 2 including a thermal regulation system 1 and capable of heating and / or cooling electrical and / or electronic components of an electric or hybrid motor vehicle, and preferably capable of heating and / or cooling the interior of the vehicle.

[0145] For ease of understanding, it should be noted that only descriptions will be provided. Figure 5 The conduits are indicated by solid lines because these are the conduits used in the first operating mode. Additionally, the conduits or components of refrigerant circuit 2, indicated by thicker lines, represent the portion of refrigerant circuit 2 where the refrigerant is at high pressure.

[0146] In this first operating mode, the previously described compressor 20 compresses the refrigerant to increase its pressure and thus its temperature. Therefore, it should be understood that at the outlet of the compressor 20, the high-pressure refrigerant is in a gaseous state and has a high temperature, i.e., higher than its temperature at the inlet of the compressor 20. The refrigerant leaving the compressor 20 circulates in the first conduit 110a outside the support 10, then enters the main branch 60-1 of the first channel 60 via the first flange 101, and is guided towards the first branch 60-2 by means of the open first shut-off valve 72-2, and then to the condenser passage 17 of the condenser 52. The condenser 52 then releases its heat energy to the first heat transfer fluid 30a of the closed cooling circuit 44. Therefore, upon leaving the condenser 52, the refrigerant is colder than it was at the inlet and is at least partially liquid.

[0147] Upon exiting the condenser 52, the refrigerant is directed toward the first heat exchanger 54 via one of the second channels 62-1. According to... Figure 5 and Figure 6 In the illustrated embodiment, the first heat exchanger 54 is an internal heat exchanger. High-pressure refrigerant circulating in the second passage 11b of the first heat exchanger 54 exchanges heat with low-pressure refrigerant circulating through another portion of the refrigerant circuit 2 via the first passage 11a. This transfer allows for improvement in the thermodynamic performance of the refrigerant circuit 2.

[0148] Once the refrigerant has passed through the first heat exchanger 54 via the second passage 11b, it circulates in one of the second passages 62-2 until the junction. Then, the refrigerant circulates in one of the second passages 62-3 and / or one of the second passages 62-4, passing through the second expansion valve 28 and / or the first expansion valve 26 respectively, to reduce its pressure and its evaporation point. It should be understood that this stage marks the transition from the high-pressure portion of the refrigerant circuit 2 to its low-pressure portion.

[0149] Upon exiting the second expansion valve 28, the refrigerant, under low pressure, is guided through one of the third channels 64-1 and circulates within the second evaporator 50 via the evaporator passage 13 to exchange heat with the second heat transfer liquid 30b, which is intended for cooling electrical and / or electronic components, and passes through the second evaporator 50. More specifically, the second heat transfer liquid 30b, upon entering the second evaporator 50, is hot and releases its heat energy to the refrigerant circulating in the evaporator passage 13, causing the refrigerant to evaporate. This change in state generates the energy required to cool the electrical and / or electronic components. Therefore, it should be understood that within the second evaporator 50, the refrigerant evaporates under the influence of absorbed heat energy, and the second expansion valve 28 has lowered its evaporation point. It should be understood that when the refrigerant exits the second evaporator 50, the refrigerant circulating in one of the third channels 64-2 is primarily in a gaseous state.

[0150] As the cold, low-pressure refrigerant exits the first expansion valve 26, it is directed via the third flange 103 and then via the second conduit 110b outside the support member 10 to the first evaporator 48 of the vehicle interior thermal conditioning device 38, which is arranged, for example, inside the vehicle. More specifically, the thermal conditioning device 38 is arranged inside so that it is passed through by the airflow F introduced into the interior. Thus, it should be understood that the airflow F through the first evaporator 48 is cooled by the cold refrigerant circulating through the evaporator, thereby cooling the interior. The refrigerant through the first evaporator 48 then evaporates due to the absorption of heat energy, causing it to exit at least partially in a gaseous state into the third conduit 110c outside the support member 10, as far as the seventh flange 107 of the support member 10.

[0151] Once the refrigerant has passed through the second evaporator 50, refrigerant from one of the three channels 64-2 circulates through the fifth flange 105, in the fourth conduit 110d outside the support 10, and through the bottle 56 (in this case, the collector). Refrigerant from the first evaporator 48 circulates through the seventh flange 107, then in the fifth conduit 110e outside the support 10, all the way to the bottle 56. The bottle 56, or collector, collects the liquid portion of the refrigerant leaving the second evaporator 50 and / or the first evaporator 48. The refrigerant must pass through the bottle 56 in this manner before entering the compressor 20, which can only accept gaseous refrigerant.

[0152] Upon exiting bottle 56, the gaseous refrigerant, still under low pressure, is guided towards the first heat exchanger 54 via the sixth conduit 110f and sixth flange 106 outside the support 10 through one of the third channels 64-3, to exchange heat with the refrigerant from the high-pressure section of the refrigerant circuit 2 via the first passage 11a, as previously described. Thereafter, the refrigerant is directed to the compressor 20 via the fifteenth flange 115 and seventh conduit 110g outside the support 10, causing the fluid to undergo an increase in pressure and temperature as previously described. Figure 5 and Figure 6 In the illustrated embodiment, the fifteenth flange 115 is directly coupled to the first exchanger 54. According to another embodiment (not shown), the fifteenth flange 115 may be part of the support 10. Therefore, it should be understood that the departure of the compressor 20 again constitutes a transition to the high-pressure section of the refrigerant circuit 2, and can initiate further thermodynamic cycles.

[0153] Now we will combine Figure 6 A second operating mode of the refrigerant circuit 2 is described, the refrigerant circuit 2 including a thermal regulation system 1 and capable of heating and / or cooling electrical and / or electronic components of an electric or hybrid motor vehicle, and preferably capable of heating and / or cooling the interior of the vehicle.

[0154] For ease of understanding, it should be noted that only descriptions will be provided. Figure 6 The conduits indicated by solid lines are those used in the second operating mode. Additionally, the conduits indicated by thick lines represent the portion of refrigerant circuit 2 where the refrigerant is at high pressure.

[0155] As in the first operating mode, when the refrigerant exits the compressor 20 through the first conduit 110a outside the support 10, it is under high pressure, high temperature, and in a gaseous state. Then, by closing the first valve 72-2 and opening the second valve 72-3, the refrigerant is guided towards the internal condenser 46 of the internal thermal conditioning unit 38 via the first flange 101, main branch 60-1, second branch 60-3, second flange 102, and eighth conduit 110h, to heat at least the airflow F (in this case, cold air) passing through the internal condenser 46. Therefore, it can be understood that upon exiting the internal condenser 46 of the internal thermal conditioning unit 38, the refrigerant at least partially condenses, releasing at least part of its heat energy to the cold airflow F to heat the cold airflow F, thereby heating the interior. Thereafter, the refrigerant exits the internal condenser 46 via the ninth conduit 1101.

[0156] Then, the refrigerant leaving the internal condenser 46 of the internal thermal conditioning unit 38 reaches one of the second channels 62-5 via the fourth flange 104. The refrigerant circulates in one of the second channels 62-5, then in the second channel 62-2, and passes through the second expansion valve 28 to reduce its pressure and evaporation point. It should be understood that this stage marks the transition from the high-pressure section of the refrigerant circuit 2 to its low-pressure section.

[0157] The refrigerant then passes through one of the third channels 64-1, and then through the second evaporator 50 via evaporator passage 13, to absorb heat energy from the second heat transfer liquid 30b used for cooling electrical and / or electronic components. By absorbing heat energy from the second heat transfer liquid 30b, the refrigerant at least partially evaporates and continues along its path through the refrigerant loop 2 in the same manner as described above with respect to the first operating mode.

[0158] According to a third operating mode (not shown here), the condenser 52 has the function of exchanging heat energy with a first heat transfer liquid 30a, in which case the first heat transfer liquid 30a is used to heat the electrical and / or electronic components of an electric or hybrid motor vehicle. In this operating mode, high-pressure refrigerant circulates in the condenser 52 via the condenser passage 17 to exchange heat energy with the first heat transfer liquid 30a, in which case the first heat transfer liquid 30a is used to heat the electrical and / or electronic components and passes through the condenser 52. More specifically, the first heat transfer liquid 30a passing through the condenser 52 is cold when it enters the condenser 52 and absorbs heat energy from the refrigerant circulating in the condenser passage 17, thereby condensing. This change in state generates the energy required to heat the electrical and / or electronic components.

[0159] In one example of this operating mode, at the second evaporator 50, refrigerant passes through evaporator passage 13 to absorb heat energy from a second heat transfer liquid 30b, which circulates in a radiator (not shown), for example, located at the front of the vehicle. The heat transfer liquid 30b then releases the absorbed heat energy to the ambient air through the radiator.

[0160] Now for reference Figure 11 This describes another embodiment of the support member 200 of the refrigerant circulation unit 217. According to this embodiment, the support member 200 has an overall shape of a generally flat plate, including a first surface 200a and a second surface 200b, which are opposite to each other and are formed on both sides of an extension plane P of the plate, which separates the two surfaces 200a and 200b. Figure 11 A shows the support member 200 as viewed from the first surface 200a. Figure 11 B shows the support member as viewed from the second side 200b.

[0161] As depicted, the first surface 200a of the support 200 includes a flat receiving area 202, which is intended to receive a refrigerant circulation channel 204, as described in the reference above. Figure 3 Those described or referenced Figure 7 Those described. Therefore, the refrigerant circulation unit 217 includes a channel 204 supported by a first surface 200a of a support 200 and a conduit supported by the support 200 but not integrally supported like the channel 204. The conduit or pipe is in Figure 8 The weight is listed as 110g, and references... Figure 12 A is also shown as 206. (Reference) Figure 8 The described support member 200 can be used in place of the previous reference. Figure 3 The device described above is then supported by the support 10 to perform the same function.

[0162] As can be seen, the first surface 200a and the second surface 200b of the support each include a grid structure, which consists of a plurality of first ribs 208 oriented along a first orientation in the extending plane and second ribs 210 oriented along a second orientation, the second orientation being not parallel to the first orientation. The ribs 208 and 210 can be separated from each other by unit cavities. In another embodiment, the first surface 200a and the second surface may include a lattice structure with ribs, which together define unit cavities with a honeycomb shape (i.e., a hexagonal cross-section). The ribs make the support rigid.

[0163] exist Figure 11 As can be seen in A, the flat receiving area 202 is partially surrounded by a grid structure formed by ribs 208 and 210. More practically, the upper surface of the ribs is flush with the flat receiving area 202.

[0164] The support 200, thus forming a flat receiving area 202 surrounded by a grid structure, proves to be rigid and lightweight. The support can be made of composite and / or plastic materials. Advantageously, it is therefore not made of metal, meaning it can be lighter. This could be, for example, fiber-reinforced polyamide or propylene. Note that the support is preferably made of a material less dense than the material used to form the channels of the refrigerant circulation unit.

[0165] The second surface 200b of the support member 200 includes a receiving member for receiving the compressor 20. To improve the rigidity of the body, the receiving member 212 for receiving the compressor is formed as a flat portion 202 facing the support member 200. It can be formed by a plurality of ribs having a concave curved upper edge, which is also capable of supporting the convex circular outer surface of the compressor 20.

[0166] The support member 200 includes arms 214a and 214b that are substantially perpendicular to the extending plane of the support member. These arms are designed to allow attachment to, for example, a frame or chassis of a motor vehicle. A first arm 214a extends from a first face and in a direction away from a second face. A second arm 214b extends from a second face and in a direction away from the first face. The first arm also has a portion 214a1 that extends in the same manner as the second arm. The arm may include a threaded tubular insert made of metal to receive metal screws. Alternatively, the screw may be attached directly through the arm without the insert.

[0167] The support member 200 may include orifices 216 or passages connecting the first surface 200a and the second surface 200b. These orifices are designed to allow fluid connection between components of the refrigerant circuit.

[0168] Figure 12 A support member carrying the circulation unit 217 is shown on the first surface 200a, the circulation unit being supported by a flat receiving area 202. The compressor 20 is supported by the opposite surface 200b.

[0169] Now for reference Figure 13 It shows a reference Figure 11 The support member 200 described is identical to the support member 200, and a plurality of connecting channels 218 are arranged on the support member 200. The connecting channels 218 connect to components of the refrigerant circuit, namely at least two of the following: a first heat exchanger 54, a second heat exchanger 50, and a compressor. According to this document, at least one channel of the circulation unit 217 is carried by a flat receiving area 202. Ideally, they are all carried by said flat receiving area 202. Therefore, the channels are carried by the flat receiving area 202 of the support member, so that the support member 200 can be further reinforced. Positioned in this way, the channels 218 are arranged to face the compressor supported by the second surface 200b of the support member 200.

[0170] refer to Figure 13 And reference Figure 14 The channels shown each include a flat first wall element 218a and a second wall element 218b, each second wall element 218b including a cavity formed by a boss. The boss has a first surface that defines a groove extending between a first end 220 and a second end 222.

[0171] According to one aspect of the invention, each second wall element 218b includes a peripheral edge 219b surrounding a boss or recess. This peripheral edge 219b presses against the peripheral edge 219a of the first wall element 218a. The peripheral edges are welded or brazed together. Alternatively, they can be assembled by some other connection method (e.g., adhesive bonding). The connection method needs to be able to withstand the pressure and temperature of the fluid circulating in the channel.

[0172] like Figure 14 A and Figure 15 As shown, the first wall elements 218a are formed as a single piece. Preferably, they are all formed from the same component 221 that presses against the support member 200. Figure 16 Screws may be provided for connection between the circulation unit 217 and the support member 200. Component 221 advantageously has two substantially flat surfaces, namely a first surface 221a that presses against the surface 200a of the support member 200 and a second surface 221b that receives the second wall element 218b.

[0173] Therefore, in one embodiment, component 221 takes the form of a plate having two parallel and flat surfaces 221a, 221b.

[0174] It can also be seen that the second wall elements 218a are formed differently from each other and are each connected to the first wall element 218b. Each second wall element 218b includes an aperture 223 formed at at least one of its first and second ends.

[0175] As a variation, the plate-like member 221 may have a non-flat second surface 221b. In other words, it may be formed of multiple receiving surfaces for receiving the second wall element 218b, each surface of the first wall element 218a being inclined relative to another surface of the other first wall element 218a. Surface 221a may be flat so as to press against a corresponding flat surface of the flat receiving region 202.

[0176] like Figure 14 , Figure 15 and Figure 16 As shown, space 224 may be formed between all or some of the first wall elements and / or the second wall elements. In this way, heat transfer between the two first wall elements 218a and / or the two second wall elements 218b can be reduced.

[0177] Now for reference Figure 17 It shows a first heat exchanger (or IHX) 54 supported by a first side of support 200 and a compressor supported by a second side of support 200. The setup shown also applies to the reference. Figures 1 to 10 The described support component.

[0178] Figure 17 C shows the fluid connection 110g between the first heat exchanger and the compressor, and more specifically the fluid connection 110g between the compressor outlet 228 and inlet 230. Figure 17Figure c shows a straight fluid conduit 110g. More specifically, the compressor inlet orifice 230 is partially aligned with the outlet orifice 228 of the first heat exchanger. In this particular case, the orifices are coaxial. In this first configuration, compared to prior art where the conduit has bends, the refrigerant circulating at low pressure from the outlet of the first heat exchanger experiences only a small pressure drop before entering the compressor.

[0179] exist Figure 18 In the second configuration shown, the outlet of the second heat exchanger (e.g., the second evaporator 50) is at least partially aligned with the 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 positioned in the location of the compressor, which can be repositioned outside the support 200.

[0180] When orifices are referred to as aligned, it must be understood that at least a portion of the cross-section of the outlet orifice is aligned with a portion of the cross-section of the inlet orifice. More specifically, the cross-sections may be coaxial rather than identical, and may also be the same.

[0181] Connect the first construction ( Figure 17 ) or second construction ( Figure 18 The length of the pipes for the two components involved in the process can be on the order of 20 to 50 mm, especially 30 and 40 mm.

[0182] As previously mentioned, the support member can be formed from a circulation unit. In other words, the circulation unit can support the first exchanger on a first surface and the compressor or second exchanger on the opposite second surface.

Claims

1. A thermal control system, comprising: - A refrigerant circuit having at least one of a first configuration including a first heat exchanger (54) and a compressor, and a second configuration including a first heat exchanger (54) and a second heat exchanger (50). in: In the first configuration, a conduit (110g) connects the outlet of the first heat exchanger (54) to the inlet of the compressor, and the outlet orifice of the first heat exchanger (54) is aligned with the inlet orifice of the compressor (20). - In the second configuration, the pipe connects the outlet of the second heat exchanger (50) to the inlet of the first heat exchanger (54), and the inlet orifice of the first heat exchanger (54) is aligned with the outlet orifice of the second heat exchanger (50).

2. The regulating system according to the preceding claim, wherein the pipe has a length of less than 60 mm.

3. The system according to any one of the preceding claims includes a support member that supports the first exchanger (54) on a first surface and the compressor or the second exchanger (50) on an opposite second surface.

4. The system according to the preceding claim, wherein, The support includes an opening (216), and the pipe passes through the support from the first surface to the second surface via the opening (216).

5. The system according to any one of the preceding claims includes a refrigerant circulation unit (217), the refrigerant circulation unit including at least one channel (218).

6. The system according to the preceding claim, wherein, The support (200) is formed in a component different from the at least one channel and includes a flat receiving area, on which one face of at least one first wall element of the at least one channel (218) presses against the flat receiving area.

7. The system according to claim 5, wherein, The support is formed by the circulation unit, which carries the first heat exchanger (54) on a first surface and the compressor (20) or the second heat exchanger (50) on an opposite second surface.

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