Vehicle heat treatment module and system

Abstract

The invention relates to a vehicle heat treatment module comprising: - a stack of plates (P) defining: -- a heat exchanger (6), -- a condenser (2), -- an internal heat exchanger (4) defining a common base for the heat exchanger and the condenser, - first connections (2'e, 2's, 6'e, 6's) for the inlet and outlet of the heat transfer fluid and second connections for the inlet and outlet of the refrigerant, characterized in that the first connections are installed on a closing plate (41) of the internal heat exchanger, which closing plate defines a first end face of said module. Figure 2A

Description

Title of the invention: Vehicle heat treatment module and system technical field

[0001] The invention relates to a heat treatment module for vehicles and a heat treatment system comprising such a module.

[0002] The invention relates to the technical field of heat treatment of fluids within a vehicle using plate heat exchangers. The vehicle is preferably a motor vehicle (car, truck, etc.), but more generally, can be of a land, sea or air type. State of the art

[0003] Motor vehicles are commonly equipped with a refrigerant circuit and at least one heat transfer fluid circuit, both used to contribute to the thermal treatment of different areas or components of the vehicle. It is particularly known to use the refrigerant circuit and / or the heat transfer fluid circuit to thermally treat an airflow sent into the passenger compartment of a vehicle equipped with such a circuit and / or to cool components of the vehicle's powertrain (battery, engine, etc.).

[0004] The refrigerant and the heat transfer fluid usually circulate within their respective circuits and interact with each other via a plurality of heat exchangers, ensuring heat exchange between the two fluids. To improve the compactness of the heat treatment system, several of these heat exchangers can be grouped into a heat treatment module. Since automotive manufacturers are constantly striving to improve their vehicles, one improvement objective is to group more elements of the heat treatment system into heat treatment modules to reduce the space occupied by these elements.

[0005] A particularly compact vehicle heat treatment module incorporating several functions is known from patent document FR3124248. This module consists of a stack of plates arranged and configured to house several heat exchangers, including: a condenser for heat exchange between the refrigerant and a heat transfer fluid, a heat exchanger (or chiller) for heat exchange between the refrigerant and a heat transfer fluid, and an internal heat exchanger (IHX) for heat exchange between the refrigerant at two different temperature levels. The IHX defines a common base for the chiller and the condenser.

[0006] This prior art module includes connections for the inlet and outlet of the heat transfer fluid and connections for the inlet and outlet of the refrigerant. The heat transfer fluid connections are distributed on a closing plate of the IHX, on a closing plate of the condenser and on a closing plate of the chiller.

[0007] In practice, due to this dispersed arrangement of the heat transfer fluid connections, access to them can prove to be relatively complicated, making assembly, maintenance and repair operations difficult, particularly in an environment where access to these connections is often hampered by complex configurations and small spaces.

[0008] Furthermore, connecting these connectors to other heat exchangers in the system, such as a radiator or an air conditioning element in the passenger compartment of the vehicle, requires additional and / or relatively long external fittings, conduits or tubing, reducing the available space around the module.

[0009] In addition, in some use cases, it may be observed that the condenser and / or chiller plates could be subjected to significant thermal stress, in particular due to a high thermal gradient between the heat transfer fluid and the refrigerant circulating in these exchangers, and which could lead to premature wear of the plates.

[0010] The invention aims to remedy all or part of the aforementioned drawbacks. In particular, it aims to achieve all or part of the following objectives: reduce the costs and operational time associated with the assembly, maintenance and repair phases of the heat treatment module; extend the service life of the condenser and / or chiller plates. Presentation of the invention

[0011] The solution proposed by the invention is a vehicle heat treatment module comprising: - a stack of plates defining: — a heat exchanger for heat exchange between a refrigerant and a heat transfer fluid, — a condenser for heat exchange between the refrigerant and a heat transfer fluid, — an internal heat exchanger for heat exchange between the refrigerant subjected to two different temperature levels, which internal heat exchanger defines a common base for the heat exchanger and the condenser, - initial connections for the inlet and outlet of heat transfer fluid and second connectors for the inlet and outlet of refrigerant fluid, and in which the first connectors are installed on a closing plate of the internal heat exchanger, which closing plate defines a first end face of said module.

[0012] Instead of having to work on several scattered connections, operators can now focus on a single location. This grouping and centralization of the first heat transfer fluid connections at the IHX level therefore simplifies the assembly, maintenance, and repair operations of the module.

[0013] Furthermore, it turns out that connecting these initial connections to the other heat exchangers in the system can be achieved by reducing the number and / or length of external fittings, conduits, or pipes, thereby freeing up available space around the module. This is a particularly desirable advantage in environments where space is limited, such as in vehicle engine compartments. Another significant consequence is that pressure losses are reduced in this external connection network.

[0014] Furthermore, the heat transfer fluid now passes through the IHX, which acts as a thermal mediator, regulating the temperature of said fluid before its circulation in the condenser and chiller. The portion of circulation within the IHX thus allows control of the thermal gradient between the heat transfer fluid and the refrigerant circulating in these exchangers, with the aim of reducing the risk of thermal stress that could affect their physical integrity. Positioning the first heat transfer fluid connections at the IHX ensures the best compromise between, on the one hand, the overall thermal efficiency of the module, and on the other hand, the preservation of the physical integrity of the condenser and chiller.

[0015] Other advantageous features of the invention are listed below. Each of these features may be considered alone or in combination with the notable features defined above. Each of these features contributes, where appropriate, to the resolution of specific technical problems defined further in the description and in which the other features defined above do not necessarily participate. The following features may thus be the subject, where appropriate, of one or more divisional patent applications:

[0016] According to one embodiment, the first connectors are aligned along an edge of the closing plate, preferably above the condenser.

[0017] According to one embodiment, conduits fixed to the closing plate of the internal heat exchanger connect the first connections for the inlet and outlet of the heat transfer fluid in the heat exchanger with circulation orifices formed in said closing plate, which conduits preferably have a concave cross-section, preferably U-shaped, which is closed by said closure plate.

[0018] According to one embodiment, second connections for the inlet and outlet of the refrigerant fluid subjected to a first temperature level in the internal heat exchanger are installed on a closing plate of said exchanger.

[0019] According to one embodiment, second connectors for the inlet and outlet of the refrigerant subjected to a second temperature level in the internal heat exchanger and a second connector for the inlet of the refrigerant into the heat exchanger are installed on a closing plate of said heat exchanger, which closing plate defines a second end face of said module which is opposite to the first end face.

[0020] According to one embodiment, the second connections for the inlet and outlet of the refrigerant fluid subjected to the second temperature level in the internal heat exchanger and the second connection for the inlet of the refrigerant fluid in the heat exchanger, are installed on an adapter flange (8) attached to the closing plate of said heat exchanger.

[0021] According to one embodiment, a pressure relief valve is associated with the second inlet connection of the refrigerant in the heat exchanger, which valve is fixed on the adapter flange.

[0022] According to one embodiment: - a heat exchanger closure plate has a first opening leading into a collector defined in the stack of plates for the evacuation of the refrigerant fluid from said heat exchanger, and a second opening leading into a collector defined in the stack of plates for the arrival of the refrigerant fluid into the internal heat exchanger; - an adapter flange supporting refrigerant inlet and outlet connections is attached to said closure plate, which flange is configured to connect the first opening and the second opening in fluid communication.

[0023] According to one embodiment, the module further comprises a desiccant bottle installed against a side wall of the condenser, said bottle having a longitudinal axis, which bottle is installed so that said longitudinal axis is parallel to said side wall and perpendicular to a stacking direction of the plates.

[0024] Another aspect of the invention relates to a heat treatment system for a vehicle, which system includes a heat treatment module conforming to one of the preceding characteristics. Brief description of the figures

[0025] Other advantages and features of the invention will become clearer upon reading the description of the embodiments that follow, with reference to the accompanying drawings, which are provided by way of illustrative and non-limiting examples and on which: [Fig.1] schematically illustrates an example of a heat treatment system for a motor vehicle, comprising a heat treatment module according to the invention. [Fig.2A] is a perspective representation of a heat treatment module according to the invention, seen from a first face (called top view). [Fig.2B] illustrates the heat treatment module of [Fig.2A], seen from a second face (called bottom view) opposite to the first face. [Fig.3A], [Fig.3B], [Fig.3C], [Fig.3D] and [Fig.3E] are different cross-sectional views of a heat treatment module according to the invention. [Fig.4A] is a perspective representation of the IHX, chiller and condenser, seen from above. [Fig.4B] is a perspective representation of the IHX, chiller and condenser, seen from below. [Fig.5A] is a perspective representation of the flange, showing the external face of said flange. [Fig.5B] is a perspective representation of the flange, showing the inner face of said flange. [Fig.6] is a perspective representation of a connecting piece suitable for attachment to the flange. Description of the implementation methods

[0026] To possibly supplement their current definition, the following clarifications are provided for certain terms used in the claims and the description: - As used here, unless otherwise indicated, the possible use of the ordinal adjectives "first", "second", etc., to describe an object simply indicates that different occurrences of similar objects are being mentioned and does not imply that the objects so described must be in any given sequence, whether in time, space, ranking, or any other way. - "X and / or Y" means: X alone or Y alone or X+Y. - In general, it will be appreciated that on the various attached drawings, the objects are drawn arbitrarily to facilitate their reading.

[0027] Figure 1 represents a heat pump-type thermal treatment system 100 for a motor vehicle. This system comprises a first refrigerant loop 101, shown in solid lines, in which a refrigerant circulates (e.g., R134a, R1234yf, R290, R744), and one or more heat transfer fluid loops 102i, 1022, shown in dashed lines, in which a heat transfer fluid circulates. (e.g., glycol water, dielectric fluid).

[0028] The first refrigerant loop 101 comprises, in the direction of refrigerant flow: a compressor 1, a condenser 2, a desiccant bottle 3, an internal heat exchanger 4 or IHX (for the English acronym for Internal Heat EXchanger), an expansion device 5, and a thermal heat exchanger 6 of the water evaporator type, or chiller in English.

[0029] The condenser 2 is preferably a water-cooled condenser or WCDS (Water Cooled Condenser). It is a two-fluid heat exchanger, located downstream of the compressor 1, and configured to extract heat from the condensing refrigerant and transfer it to the heat transfer fluid circulating in the heat transfer fluid loop 102i. The condenser 2 has a refrigerant inlet 2e and an outlet 2s, and a heat transfer fluid inlet 2'e and an outlet 2's. The inlet 2e is fluidly connected to the outlet 1s of the compressor 1. The refrigerant and heat transfer fluids circulate preferably in counter-current flow to optimize heat exchange.

[0030] The desiccant bottle 3 is configured to remove a gaseous fraction of the refrigerant that has not been condensed in the condenser 2. The desiccant bottle 3 is disposed between the condenser 2 and the IHX 4. More particularly, the desiccant bottle 3 comprises an inlet 3e fluidically connected to the outlet 2s of the condenser 2 and an outlet 3s fluidly connected to an inlet 4e of the IHX 4.

[0031] The IHX 4 is configured for heat exchange between the refrigerant at two different temperature levels. To this end, the IHX comprises two heat exchange stages. Specifically, the IHX 4 cools the refrigerant by heat exchange between the high-temperature, high-pressure refrigerant from the condenser 2 and the low-temperature, low-pressure refrigerant from the chiller 6. On the high-temperature side, the IHX 4 has an inlet 4e fluidically connected to the outlet 3s of the desiccant receiver 3, and an outlet 4s fluidly connected to the expansion valve 5. On the low-temperature side, it has an inlet 40e fluidly connected to the outlet 6s of the chiller 6, and an outlet 40s fluidly connected to the inlet 1 of the compressor 1.

[0032] The expansion valve 5 is, for example, of the EXV type (for the English acronym for Electronic Expansion Valve). It is configured to expand the high-pressure refrigerant to a first pressure level (low pressure), this pressure reduction being accompanied by a temperature decrease. This expansion valve provides a fluidic connection between the IHX 4 and the chiller 6. In particular, it has an inlet 5e fluidically connected to the outlet 4s of the IHX 4 and an outlet 5s fluidly connected to the inlet 6e of the chiller 6.

[0033] The chiller 6 is configured to extract heat from the circulating heat transfer fluid in the heat transfer fluid loop 1022 and transfer it to the refrigerant. On the refrigerant side, it has an inlet 6e associated with the expansion valve 5 and an outlet 6s fluidically connected to the inlet 40e of the IHX 4. The chiller 6 also has an inlet 6'e and an outlet 6's for the heat transfer fluid. The circulation of the refrigerant and heat transfer fluids is preferably counter-current to optimize heat exchange.

[0034] In one embodiment, the heat transfer fluid loop 102i is used for heat exchange with an airflow directed into the vehicle's passenger compartment, for example, by being connected to the passenger compartment's radiator 110 for heating. The heat transfer fluid loop 1022 allows heat exchange with one or more components 111 of the vehicle's powertrain for cooling or heat recovery, for example, with the electronic part of said powertrain (or PEEM, for Power Electronics and Electric Machinery), with the motor, and / or with the batteries. In a preferred embodiment, the heat transfer fluid circulating in loop 102i and that circulating in 1022 are not the same.

[0035] In the system of [Fig. 1], a portion of the refrigerant exiting the high-temperature stage of the IHX 4 via outlet 4s also passes through another heat exchanger 112, enabling heat exchange between the refrigerant and an airflow, for example, an interior airflow for heating the vehicle's passenger compartment. The refrigerant is expanded upstream of this exchanger to lower its temperature. This expansion is achieved by means of an expansion device 7 of the type described previously. The refrigerant exiting this exchanger 112 then returns to the low-temperature stage of the IHX 4 and / or circulates to an additional heat exchanger 113. This latter exchanger can, for example, be located within the vehicle so as to be subjected to an external airflow, for example, at the front of the vehicle.This additional heat exchanger 113 can act as a condenser or as an evaporator depending on the operating mode of the heat treatment system. The refrigerant exiting this additional heat exchanger 113 then returns to the low-temperature stage of the IHX 4.

[0036] It is therefore observed that the low temperature stage of the IHX 4 is supplied by the refrigerant from the chiller 6, by the refrigerant from the exchanger 112, and by the refrigerant from the additional exchanger 113. According to one embodiment, the heat treatment module 10 aims to integrate this multi-way connection at the inlet 40e of the IHX 4.

[0037] Referring to Figures 2A and 2B, module 10 is formed by a stack of plates P (partially shown in [Fig. 2A] for clarity) defining the condenser 2, the IHX 4, and the chiller 6. These plates define manifolds and fluid circulation passes for each of these heat exchangers. Module 10 is thus of multifunctional type, that is to say that it performs three distinct heat exchange functions and is suitable for integration into a system of the type illustrated in [Fig.1].

[0038] The plates P can be common to the different heat exchangers or dedicated to a single heat exchanger. The different heat exchangers 2, 4, 6 are in this case added together and assembled together.

[0039] The plates P are stacked along a stacking axis A which is perpendicular or substantially perpendicular to the planes of the plates P. These plates P are, for example, rectangular in shape and made by stamping sheet metal. They are specifically configured and arranged to form channels for fluid circulation and advantageously include corrugations or elements that disrupt the fluid flow to improve heat transfer. Since these plates P are known to those skilled in the art, they will not be described in further detail.

[0040] The IHX 4 defines a common base for the condenser 2 and the chiller 6. Thanks to this arrangement, the module 10 is particularly compact, and the fluid manifolds defined within said module can be shaped to minimize bends, changes of direction, or intersections that could increase pressure losses. As explained further in the description, this arrangement also allows the various fluid inlet and outlet connections to be arranged to limit the number and / or length of external fittings or tubing and to optimize the space in and around the module 10.

[0041] The condenser 2 and the chiller 6 each comprise a first end plate 21, 61 corresponding to closure plates for said heat exchangers. In other words, these plates 21 and 61 respectively close off the condenser 2 and the chiller 6 at their ends opposite the IHX 4. The IHX 4 also comprises closure plates 41, 42 closing off the ends of said IHX.

[0042] According to one embodiment, the closing plate 42 of the IHX 4, which is adjacent to the condenser 2 and the chiller 6, also serves as a common closing plate for these heat exchangers. In other words, the closing plate 42 closes the condenser 2 and the chiller 6 at their end adjacent to the IHX 4. This solution has the advantage of simplifying the design of the module 10 and reducing the number of plates.

[0043] According to an alternative embodiment, the condenser 2 and the chiller 6 each comprise a second closing plate 22, 62 closing said exchangers at their end adjacent to the IHX 4. The closing plates 22, 62 are then adjacent to the closing plate 42. This solution has the advantage of allowing the IHX 4, the condenser 2 and the chiller 6 to be formed separately and assembled subsequently.

[0044] In any event, the closure plate 41 of the IHX 4 defines a first end face of the module 10 and the closure plates 21 of the condenser 2 and 61 of the chiller 6 define second end faces opposite to said first face.

[0045] Connections for the fluid inlet / outlet are arranged on the various closing plates. For the sake of simplicity and clarity, the connections installed on module 10 bear the same reference numbers as the inlets / outlets of the various heat exchangers 2, 4, 6 and other components 3, 5 illustrated in [Fig. 1], insofar as these connections are associated with said inlets / outlets. However, reference 40e in [Fig. 1] becomes 40ie and 402e in the other figures. These connections may be in the form of fittings, conduits, pipes, valves, and more generally, any means, elements, or components enabling a fluid connection between said inlets / outlets and the fluid manifolds formed in module 10.

[0046] In the following description, the heat transfer fluid inlet / outlet connections are designated as "first connections" and the refrigerant fluid inlet / outlet connections are designated as "second connections". The first connections include: the 2'e inlet and 2's outlet connections for heat transfer fluid in condenser 2 and the 6'e inlet and 6's outlet connections for heat transfer fluid in chiller 6. The second connections include: the 2'e inlet and 2's outlet connections for refrigerant fluid in condenser 2, the 4'e inlet and 4's outlet connections for refrigerant fluid in the high-temperature stage of IHX 4, the 40ie, 402e inlet and 40s outlet connections for refrigerant fluid in the low-temperature stage of said IHX, and the 6'e inlet and 6's outlet connections for refrigerant fluid in chiller 6.

[0047] In accordance with the invention, and with particular reference to [Fig. 2A], all the first heat transfer fluid connections 2'e, 2's, 6'e, 6's are grouped and centralized on the closing plate 41 of the IHX 4, which facilitates their assembly and maintenance operations. They are preferably aligned along one edge of the closing plate 41, which tends to facilitate their access and also allows a portion of said plate and the surrounding space to be left free, to permit the installation of other system components in this space and / or improve their accessibility. According to one embodiment, the first connections 2'e, 2's, 6'e, 6's are arranged above the condenser 2. This arrangement minimizes the length of the heat transfer fluid manifolds between the IHX 4 and the condenser 2, thereby helping to reduce heat losses.

[0048] In the accompanying figures, the closing plate 41 also includes the inlet 4e and outlet 4s connections for the refrigerant in the high-temperature stage of the IHX. More specifically, one and / or the other of these connections 4e, 4s are aligned with the first 2'e, 2's, 6'e, 6's connectors, to facilitate their access and to avoid further cluttering the closing plate 41, thus optimizing the extent of the free part of it.

[0049] The closing plate 21 of the condenser 2 includes the inlet 2e and outlet 2s connections of the refrigerant fluid in said condenser.

[0050] The chiller 6's closing plate 61 includes an adapter flange 8 supporting refrigerant inlet 40ie, 402e and outlet 40s connections. In a preferred embodiment, the expansion valve 5 is also supported by the flange 8. This flange 8 is described in more detail later in the description.

[0051] With reference to Figures 3A, 3B and 3C, collectors are defined in the stack of plates P for the circulation of fluid inside the module 10.

[0052] In particular, the IHX 4 has a manifold Cl for the refrigerant supply to the high-temperature stage and a manifold C2 for the discharge of said refrigerant from said stage. These two manifolds Cl and C2 extend straight down the height of the IHX 4 and open respectively at an opening 01 and an opening 02 made in the closing plate 41 of the IHX 4. The openings 01 and 02 are configured to receive the aforementioned connectors 4e and 4s, respectively. This particular arrangement of the connectors 4e and 4s makes it possible to reduce the length of the manifolds Cl and C2 inside the module 10 and the associated pressure losses.Indeed, by arranging these 4e, 4s connections as close as possible to the IHX 4, the Cl and C2 manifolds are more direct and shorter, eliminating, or at least reducing, the need to route said manifolds through additional sections or stages and / or more convoluted fluid paths.

[0053] The IHX 4 also has a manifold C3 for the refrigerant supply to the low-temperature stage and a manifold C4 for the discharge of said refrigerant from said stage. These two manifolds extend in a straight line through the height of the IHX 4 and the chiller 6 to open respectively at an opening 03 and an opening 04 made in the closing plate 61 of the chiller 6.

[0054] The condenser 2 has a collector C5 for draining the refrigerant from said condenser. This collector extends straight down the height of the condenser 2 to open at an opening 05 in the cover plate 21 of said condenser. This opening 05 is configured to receive the connector 2s. The cover plate 21 also includes an opening 012 for the refrigerant to enter the condenser 2. This opening 012 can lead into the stack of plates of the condenser 2 or into a collector defined in this stack. This positioning allows several connectors dedicated to the refrigerant to be grouped on the same side of the module 10, which facilitates assembly and maintenance operations.

[0055] The chiller 6 has a manifold C6 and a manifold C7 for the inlet and outlet of the refrigerant fluid in said chiller, respectively. These two manifolds extend straight up the height of the chiller 6 and open respectively at an opening 06 and an opening 07 made in the closing plate 61 of said chiller.

[0056] Regarding the heat transfer fluid, the condenser 2 has a manifold C8 and a manifold C9 for the inlet and outlet of the heat transfer fluid in said condenser, respectively. They extend straight up the height of the IHX 4 and the condenser 2 to open respectively at an opening 08 and an opening 09 made in the closing plate 41 of the IHX 4. The openings 08 and 09 are configured to receive the aforementioned 2'e and 2's connectors, respectively.

[0057] The chiller 6 has a manifold CIO and a manifold Cl 1 for the inlet and outlet of the heat transfer fluid in said chiller, respectively. These manifolds extend in a straight line through the height of the IHX 4 and the chiller 6 to open respectively at an opening 010 and an opening 011 made in the closing plate 41 of said IHX.

[0058] The heat transfer fluid inlet 6'e and outlet 6's connections are in fluidic communication with the manifolds CIO and Cl 1, respectively, through openings O10 and O11. Referring particularly to [Fig. 3A], the connections 6'e and 6's are offset from openings O10 and O11. Openings O10 and O11 are located above the chiller 6, while the connections 6'e and 6's are located above the condenser 2. The fluidic connection between the connections 6'e and 6's and openings O10 and O11 is advantageously made by means of conduits 600 fixed to the closing plate 41, thus avoiding the need to create fluid circulation paths inside the IHX 4. These conduits 600 have a concave cross-section, preferably in U, which is closed by plate 41, so that the bulk of said conduits is minimized in terms of height and it is not necessary to use additional closing pieces.

[0059] Due to the positioning of the first connections on the closing plate 41 of the IHX 4, the heat transfer fluid manifolds C8, C9, C10, and Cl1 each have a portion extending the height of the IHX 4. As a result, before entering the condenser 2 and the chiller 6, respectively, the heat transfer fluid passes through the IHX 4, which acts as a thermal mediator regulating the temperature of said fluid. The portion circulating within the IHX 4 thus preheats the heat transfer fluid to lower the temperature gradient between said heat transfer fluid and the refrigerant circulating in the condenser 2 and the chiller 6, respectively. The risks of thermal stress that could affect the physical integrity of the heat exchangers 2 and 6 are then reduced. reduced. This control of the thermal gradient tends to very slightly degrade the efficiency of heat exchange in condenser 2 and chiller 4. However, upon exiting condenser 2 and chiller 6 respectively, the heat transfer fluid passes again through IHX 4 where it is superheated, so the overall thermal efficiency of module 10 remains excellent. Ultimately, the positioning of the first connections on IHX 4 ensures the best compromise between, on the one hand, the overall thermal efficiency of module 10, and on the other hand, the preservation of the physical integrity of condenser 2 and chiller 6.

[0060] Figures 4A and 4B illustrate the arrangement of the various Ol-Oll openings on the different closing plates. The other openings 030, 040, 090, 0100, 0110 are additional openings made in the different closing plates 22, 42, 62 for the fluidic communication of the manifolds C3, C4, C9, C10, and Cl1 between the IHX4 and the condenser 2 or the chiller 6. The opening 012 made in the closing plate 61 of the condenser is configured to receive the aforementioned 2e connection. These various openings are preferably circular, but can be of another shape (e.g., polygonal, oval, triangular, etc.).

[0061] As stated above, the closing plate 61 of the chiller 6 has: a first opening 07 leading into the refrigerant discharge manifold C7 of said chiller, and a second opening 03 leading into the refrigerant inlet manifold C3 in the low-temperature stage of the IHX 4. Due to the proximity of the two openings 07 and 03 on the closing plate 61, the refrigerant circulation path between manifolds C7 and C3 is particularly short, thus minimizing the pressure losses associated with this circulation. Furthermore, manifolds C7 and C3 can be placed closer together in module 10 and optimized in terms of length and linearity, thereby freeing up space within module 10 and / or improving its compactness.

[0062] The two openings 07, 03 are connected via the flange 8, without the need for additional internal circulation paths within the module 10, or external fittings, conduits or tubing, to connect the manifolds C7 and C3 via the fluid. As a result, the internal space within the module 10 and the external space around said module are optimized, which facilitates access for the installation and maintenance of said module.

[0063] In Figures 5A and 5B, the flange 8 is substantially parallelepiped in shape and is advantageously in the form of a single piece. It is preferably rigid, for example made of steel, aluminum-type metal, or any other material suitable to those skilled in the art.

[0064] The flange 8 is configured to be fixed against the outer face of the closure plate 61, by screwing, welding, bonding, or by any other means or technique ensuring a stable mechanical fixing, eliminating any risk of loosening or displacement due in particular to vehicle vibrations and / or thermal cycles.

[0065] The face 81 of the flange 8 intended to be pressed against the external face of the closing plate 61 is called the "internal face" and the face 82 opposite this face is called the "external face".

[0066] According to one embodiment, a channel 83 is formed within the thickness of the flange 8. This channel 83 has a U-shaped cross-section, meaning that it is open at its outer face 81. The channel 83 can thus be closed by the plate 61 without the need for an additional closing piece. To simplify the design, the channel 83 can, for example, be machined from the outer face 81. One or more seals can be arranged to provide a fluid seal between the flange 8 and the closing plate 81 at the channel 83.

[0067] The flange 8 is positioned on the closing plate 61 so that the openings 07 and 03 lead into the channel 83. The channel 83 is thus common to these two openings and allows their fluidic communication. A keying device may be provided on the flange 8 and / or on the closing plate 61 to ensure the precise positioning of said flange.

[0068] To limit pressure losses in the channel 83, it is preferably straight between the openings 07 and 03 so that the fluid path is as direct as possible. Furthermore, its width and depth advantageously correspond to the diameter of said openings.

[0069] As previously indicated with reference to [Fig. 1], the low-temperature stage of the IHX 4 can also be supplied with refrigerant from the heat exchanger 112 and / or from the additional heat exchanger 113. Also, according to one embodiment, the flange 8 supports a first inlet connection 40ie and optionally a second connection 402e of refrigerant in the low-temperature stage of the IHX 4. These connections 40ie, 402e are configured to be fluidly connected respectively to the outlet of the heat exchanger 112 and to the outlet of the additional heat exchanger 113, for example by means of fittings or tubing. They are advantageously installed on the external face 82 of the flange 8. This is then configured to put the first connector 40ie and, if necessary, the second connector 402e into fluidic communication with the openings 07 and 03.To simplify the design and improve the compactness of flange 8, connectors 40ie, 402e open into the common channel 83.

[0070] According to one embodiment, the flange 8 also supports the 40s connection for draining the refrigerant fluid from the low-temperature stage of the IHX 4, which is advantageously installed on the external face 82 of said flange. The flange 8 is configured to provide fluid communication between the 40s connection and the aforementioned opening 04. To simplify the design and improve the compactness of flange 8, the 40s connector is coaxial to opening 04 and opens directly into it.

[0071] According to one embodiment, the flange 8 also supports the refrigerant inlet connection 6e for the chiller 6, which is advantageously installed on the external face 82 of said flange. The flange 8 is configured to provide fluid communication between the connection 6e and the aforementioned opening 06. To simplify the design and improve the compactness of the flange 8, the connection 6e is coaxial with the opening 06 and opens directly into it.

[0072] The flange 8 is thus multifunctional in that it serves not only as a means of fluid communication between the chiller 6 and the IHX 4, but also as a multi-way connector for the low-temperature inlet of the IHX and as a grouped support for the 40ie, 402e, 40s, and 6e connectors. This multifunctional flange thus reduces the number of components required for the operation of the module 10 and simplifies its design, as it reduces the need for additional external conduits or dispersed components. The assembly of the module 10 is therefore faster and less prone to assembly errors. Furthermore, by grouping the 40ie, 402e, 40s, and 6e connectors on the flange 8, centralized access is provided, so that in the event of a failure, it is simply a matter of removing the flange to work on these connectors, without having to disassemble the entire module 10.

[0073] According to one embodiment, the refrigerant inlet connection 6e in the chiller 6 and the refrigerant inlet connection 402e in the IHX 4 are grouped on a part 9 fixed to the flange 8. In [Fig. 6], this part 9 is parallelepiped-shaped and one-piece. It is rigid, for example made of steel, aluminum, or any other material suitable to those skilled in the art. Part 9 helps to reinforce the robustness of the flange 8. Its one-piece design also simplifies the assembly and maintenance steps of the module 10. In particular, in the event of failure of the connector 6e and / or the connector 402e, only part 9 needs to be removed, without having to dismantle the flange 8. It is configured to be fixed against the external face 82 of the flange 8, by screwing, welding, gluing, or by any other means or technique ensuring a stable mechanical fixing.

[0074] Part 9 has on its face intended to be fixed to flange 8 female and male fittings, respectively, 60e and 4002e, configured to connect to male and female fittings, respectively, provided on said flange (corresponding to connections 6e and 402e in [Fig. 5A]). Sealing gaskets are advantageously provided at these fittings. Fittings 60e and 4002e open onto two distinct faces of part 9, respectively, at connections 6e and 402e. The arrangement on Two distinct faces for the 6e and 402e connectors facilitate access and allow them to be distinguished more clearly.

[0075] To simplify assembly and improve the compactness of module 10, the detent member 5 associated with the connector 6e is advantageously fixed to part 9, upstream of said connector. By being thus offset from the flange 8, the detent member 5 does not obstruct access to the other connectors supported by said flange. In particular, it can be easily installed on a large face of part 9 onto which the connector 6e opens. If flange 8 does not support part 9, the detent member 5 can, however, be fixed directly to said flange.

[0076] According to one embodiment, the refrigerant inlet connection 6e in the chiller 6 and the refrigerant inlet connection 402e in the IHX 4 are two separate elements installed on the flange 8.

[0077] According to an embodiment illustrated in particular by [Fig. 2B], the height of the condenser 2 is greater than that of the chiller 6, so that the module 10 has a recess at the level of said chiller. This recess allows all or part of the space occupied by the flange 8, and where applicable, by the part 9, installed on the closing plate 61, so that the module 10 remains particularly compact. In addition, the total surface area available for heat transfer in the condenser 2 is maximized.

[0078] In Figures 2A, 2B, 3A, 3B and 3C, the desiccant bottle 3 is installed against a side wall of the condenser 2. To optimize the compactness of the module 10, the bottle 3 is installed so that its longitudinal axis is parallel to the side wall - or to the plane of said wall - of the condenser 2 and perpendicular to the stacking direction A of the plates P. This compactness is further improved when the length of the bottle 3 is less than or equal to the length of the side wall of the condenser 2.

[0079] In this arrangement, the inlet connection 3e of the bottle 3 is as close as possible to the outlet connection 2s of the condenser 2 and the outlet connection 3s of said bottle is as close as possible to the inlet connection 4e of the IHX 4. This proximity of the bottle 3 with the condenser 2 and the IHX 4 makes it possible to reduce the length of the conduits or tubing 30 connecting the connections 2s-3e and 3s-4e, and therefore the associated pressure losses, as well as the lost volumes and the quantity of fluid carried in the system 100.

[0080] The simplified arrangement of the various elements described above, particularly the connectors, simplifies not only the connection of these connectors to each other, but also the connections between these connectors and the various elements of system 100, in particular the compressor 1, and the heat exchangers 110, 111, 112. In particular, the pipes, conduits or fittings located outside the module 10 and which The connections between the fittings, or between them and the various elements of the system, can be shorter and more direct, thus reducing the number of bends or changes of direction that could complicate the assembly and increase pressure losses. This reduction also helps to reduce the volume lost and the amount of fluid carried in the system.

[0081] This simplified arrangement also allows for a more compact assembly of module 10, which is a major advantage in space-constrained environments such as vehicles. Furthermore, this simplicity speeds up assembly, maintenance, and repair operations and reduces the risk of errors—significant benefits in large-scale production environments.

[0082] The arrangement of the various elements and / or means and / or steps of the invention, in the embodiments described above, should not be understood as requiring such an arrangement in all implementations. In any event, it will be understood that various modifications may be made to these elements and / or means and / or steps without departing from the scope of the invention.

[0083] Furthermore, one or more features described only in one embodiment can be combined with one or more other features described only in another embodiment. Similarly, one or more features described only in one embodiment can be generalized to other embodiments, even if this or these features are described only in combination with other features.

Claims

Demands

1. Vehicle heat treatment module comprising: - a stack of plates (P) defining: — a heat exchanger (6) for heat exchange between a refrigerant and a heat transfer fluid, — a condenser (2) for heat exchange between the refrigerant and a heat transfer fluid, — an internal heat exchanger (4) for heat exchange between the refrigerant subjected to two different temperature levels, which internal heat exchanger defines a common base for the heat exchanger (6) and the condenser (2), - first connections (2'e, 2's, 6'e, 6's) for the inlet and outlet of the heat transfer fluid and second connections (2e, 2s, 4e, 4s, 40ie, 402e, 40s, 6e, 6s) for the inlet and outlet of the refrigerant, characterized in that the first connections are installed on a closing plate (41) of the internal heat exchanger (4),which closing plate defines a first end face of said module.

2. Module according to claim 1, wherein the first connectors (2'e, 2's, 6'e, 6's) are aligned along an edge of the closing plate (41), preferably above the condenser (2).

3. Module according to any one of the preceding claims, wherein conduits (600) fixed on the closing plate (41) of the internal heat exchanger (4) connect the first connections (6'e, 6's) for the inlet and outlet of heat transfer fluid in the heat exchanger (6) with circulation orifices (O10, O11) formed in said closing plate, which conduits preferably have a concave cross-section, preferably U-shaped, which is closed by said closing plate.

4. Module according to any one of the preceding claims, wherein second connectors (4e, 4s) for the inlet and outlet of the refrigerant fluid subjected to a first temperature level in the internal heat exchanger (4) are installed on a closing plate (41) of said exchanger.

5. Module according to any one of the preceding claims, wherein second connectors (40ie, 402e, 40s) for the inlet and outlet of the refrigerant fluid subjected to a second temperature level in the internal heat exchanger (4) and a second connector (6e) for the inlet of the refrigerant fluid into the heat exchanger (6) are installed on a closing plate (61) of said heat exchanger, which closing plate defines a second end face of said module which is opposite to the first end face.

6. Module according to claim 5, wherein the second connectors (40ie, 402e, 40s) for the inlet and outlet of the refrigerant fluid subjected to the second temperature level in the internal heat exchanger (4) and the second connector (6e) for the inlet of the refrigerant fluid into the heat exchanger (6), are installed on an adapter flange (8) attached to the closing plate (61) of said heat exchanger.

7. Module according to claim 6, wherein a pressure relief member (5) is associated with the second connection (6e) for the inlet of the refrigerant fluid into the heat exchanger (6), which member is fixed on the adapter flange (8).

8. Module according to any one of claims 1 to 5, wherein: - a closing plate (61) of the heat exchanger (6) has: — a first opening (07) leading into a collector (C7) defined in the stack of plates for the evacuation of the refrigerant fluid from said heat exchanger, — a second opening (03) leading into a collector (C3) defined in the stack of plates for the arrival of the refrigerant fluid into the internal heat exchanger (4), - an adapter flange (8) supporting refrigerant inlet and outlet connections is attached to said closing plate (61), which flange is configured to connect the first opening (07) and the second opening (03) fluidically.

9. Module according to any one of the preceding claims, further comprising a desiccant bottle (3) installed against a side wall of the condenser (2), said bottle having a longitudinal axis, which bottle is installed so that said longitudinal axis is parallel to said side wall and perpendicular to a stacking direction (A) of the plates (P).

10. A vehicle heat treatment system, characterized in that it comprises a heat treatment module according to one of the preceding claims.

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