Fluid management module for a vehicle, in particular a car

Abstract

The invention relates to a fluid management module for a vehicle, in particular a motor vehicle, comprising: - a support (10) having a first face (40) and a second face (42), the first face (40) being opposite the second face (42), and - at least one channel (60, 62; 64) for a coolant circuit, characterized in that the first face (40) of the support (10) supports at least one first heat exchanger (54), and the second face of the support (10) supports at least one valve.

Description

[0001] The invention relates to a fluid management module for a vehicle, in particular an automobile.

[0002] Motor vehicles, particularly electric vehicles, are equipped with thermal management systems such as cooling and / or heating circuits to ensure user comfort and control the temperature of vehicle components, such as batteries. These circuits commonly employ a refrigerant loop and a heat transfer fluid loop that exchanges heat with the refrigerant.

[0003] Cooling and / or heating circuits consist, in particular, of thermal management components, such as pumps, valves, heat exchangers, and components used for temperature regulation. Components such as conduits, guiding a fluid and fluidically connecting the thermal management components, are also included. Document DE 10 2015 014830 A1 describes a fluid management module for a vehicle according to the preamble of claim 1.

[0004] The development of electric vehicles has increased the need for optimized air conditioning and / or heat pump systems with simplified and economical manufacturing processes, while also creating demand for compact systems. The invention aims to provide a solution to improve this situation.

[0005] In this capacity, it offers a fluid management module for vehicles, particularly automobiles, comprising: a support having a first face and a second face, the first face being opposite the second face, and at least one channel for the circuit of a refrigerant fluid, in which the first face of the support supports at least one first heat exchanger and the second face of the support supports at least one valve, characterized in that the first face of the support supports a second heat exchanger.

[0006] Thus, such a support for a fluid management module offers an optimized layout of the components equipping this module. This results in a reduced footprint for the fluid management module.

[0007] The fluid management module according to the invention may further include at least one of the following features, taken alone or in combination: The support consists of at least one first refrigerant circulation zone intended for high-pressure refrigerant circulation and a second refrigerant circulation zone intended for at least high-pressure and / or low-pressure refrigerant circulation. The support is a refrigerant circulation unit. The support consists of two plates attached to each other. The channels for the refrigerant circuit are formed by at least one deformation of one of the two plates. The support incorporates the channels for the refrigerant circuit. The support includes at least one first plate, called the transfer plate, shaped to form at least one channel or corrugation for fluid circulation. The support includes at least one second plate, called the support plate, configured to provide the interface between the support and elements attached to the support.The support plate is flat to be in contact with part of the components attached to the support. The flat support plate partially defines the refrigerant conduits. The support consists of a flat plate onto which refrigerant conduits are attached and secured. The support includes at least one first channel for the circulation of the high-pressure refrigerant. This first channel for the circulation of the high-pressure refrigerant has a substantially Y-shaped form, with a main branch and two branches, referred to as the first and second branches. At least one valve support block is inserted on a branch of the first channel for the circulation of the high-pressure refrigerant. Two valve support blocks are each inserted on a branch of the first channel for the circulation of the high-pressure refrigerant.The valve support blocks are each suitable for receiving a valve, in particular a shut-off valve; the main branch of the first channel is intended to ensure communication between a first flange, fluidly connected to a compressor, and the first and second branches; the second branch is intended to ensure communication between the main branch and a second flange, fluidly connected to an internal condenser; the support also includes at least one second channel intended for the circulation of the high-pressure refrigerant; the support includes four second channels intended for the circulation of the high-pressure refrigerant; one of the second channels is intended to ensure communication between a third flange, fluidly connected to a receiver, and another heat exchanger; one of the second channels is intended to ensure communication between a heat exchanger and a fourth flange, fluidly connected to the receiver.One of the second channels is intended to ensure communication between a heat exchanger and a valve, preferably an expansion valve; the support also includes at least one third channel intended for the circulation of the low-pressure refrigerant; the support includes five third channels intended for the circulation of the low-pressure refrigerant; one of the third channels is intended to ensure communication between a fifth flange fluidly connected to an evaporator and a heat exchanger; one of the third channels is intended to ensure communication between a heat exchanger and a sixth flange fluidly connected to the compressor; one of the third channels is intended to ensure communication between yet another heat exchanger and a heat exchanger.One of the third channels is intended to ensure communication between an expansion valve and a heat exchanger; one of the third channels is intended to ensure communication between an expansion valve and a seventh flange fluidically connected to the evaporator; the at least first channel intended for the circulation of the high-pressure refrigerant is disposed on the first refrigerant circulation zone and intended for the circulation of the high-pressure refrigerant, while the at least third channel intended for the circulation of the low-pressure refrigerant is disposed on a second refrigerant circulation zone intended for the circulation of the low-pressure refrigerant; the first circulation zone is separate from the second refrigerant circulation zone; the first circulation zone may be thermally insulated from the second circulation zone.The first refrigerant circulation zone extends substantially along a first plane, and the second refrigerant circulation zone extends substantially along a second plane. The first plane of the first refrigerant circulation zone and the second plane of the second refrigerant circulation zone are different. The first plane of the first refrigerant circulation zone and the second plane of the second refrigerant circulation zone are parallel planes. The first refrigerant circulation zone and the second refrigerant circulation zone are connected by a first common edge. The first common edge has openings. The support has a third zone suitable for receiving at least part of a compressor. The third zone is distinct from the first and second refrigerant circulation zones.The third zone extends substantially along a third plane, this third plane being different from the first plane of the first refrigerant circulation zone and the second plane of the second refrigerant circulation zone. The first plane of the first refrigerant circulation zone, the second plane of the second refrigerant circulation zone, and the third plane of the third zone are parallel planes. The third zone and the second refrigerant circulation zone are connected by a second common edge. The support further includes a first opening suitable for receiving, at least partially, an expansion valve. This first opening receives, at least partially, two bodies of two expansion valves, each distinct from the other. The support includes a second opening extending at least into the third zone, suitable for receiving, at least partially, a compressor.The second opening also extends along the common edge of the third zone and the second refrigerant circulation zone; the first opening has a step defining a first and a second landing; the first opening is suitable for receiving, at least in part, a first and a second expansion valve; each of the first and second landings is suitable for receiving a first or a second expansion valve; the first common edge extends along the first opening.The first insertion block allows the integration of fluid distribution and temperature sensor functions into the fluid management module. The first insertion block allows the first expansion valve to be inserted parallel to the plane of the first refrigerant circulation zone. The shut-off valve is secured to the support via a valve support block common to several valves and / or a specific individual support block for each valve. The shut-off valve is connected via fluid to the first channel for high-pressure refrigerant circulation, preferably through the valve support block. A temperature sensor is provided on one of the two branches of the first high-pressure refrigerant circulation channel. A water-cooled condenser heat exchanger is also included.The bottle is a desiccant bottle, configured to contain the high-pressure refrigerant and capture the moisture from the refrigerant flowing through it; an internal heat exchanger, said internal heat exchanger enabling heat transfer between a low-pressure portion of the refrigerant circuit and a high-pressure portion of said refrigerant circuit; expansion valves, also called expansion valves, which may be an electronic expansion valve (EXV), a thermostatic expansion valve (TXV), or a calibrated orifice; a water-cooled heat exchanger; three heat exchangers are fluidly connected to the first, second, and third channels via flanges; the module also includes a first expansion valve; the first bearing includes a first insertion block for the first expansion valve.The first insertion block is machined to allow the insertion of the first expansion valve in a direction parallel to an extension plane of the support. The first insertion block is also machined to accommodate a second temperature sensor. A longitudinal extension axis of an expansion valve is parallel to the plane of the first refrigerant circulation zone. The module further includes a second expansion valve, and the second bearing includes a second insertion block for the second expansion valve. The second expansion valve is connected to a heat exchanger, preferably a water chiller, and is positioned on the support and opposite the second expansion valve. The second insertion block allows the insertion of the second expansion valve in a direction parallel to an extension plane of the support. The second insertion block is machined to allow the insertion of the second expansion valve in a direction parallel to the plane of the first refrigerant circulation zone. The longitudinal extension axis of the second expansion valve is parallel to the plane of the first refrigerant circulation zone. The first face of the support supports a third heat exchanger. The second heat exchanger is located between the first and third heat exchangers. The first heat exchanger is an internal exchanger and is located at a distance from the third heat exchanger, which is a water condenser type. The first, second, and third heat exchangers each have a length and a width.The length of each of the first, second, and third heat exchangers defines a longitudinal extension direction, and the longitudinal extension directions of the second and third heat exchangers are parallel, and the longitudinal extension direction of the first heat exchanger is perpendicular to the longitudinal extension directions of the second and third heat exchangers. The first expansion valve is located near the second water-cooled heat exchanger. The first heat exchanger is located on a first refrigerant circulation zone of the support, intended for high-pressure refrigerant circulation.The second and third heat exchangers are arranged on a second refrigerant circulation zone of the support, intended for high-pressure and / or low-pressure refrigerant circulation. The second face of the support further includes a compressor. The compressor is secured to the second face of the support by any means, such as screws. Vibration-absorbing devices are arranged between the support and the compressor. The second face of the support further includes a receiver. The compressor and the receiver each have a longitudinal extension direction, and the longitudinal extension direction of the compressor is perpendicular to the longitudinal extension direction of the receiver. The module includes two shut-off valves, preferably arranged on valve support blocks.The second face of the support includes at least one temperature sensor; a first temperature sensor is located near at least one shut-off valve; a second temperature sensor is located near the first expansion valve; the second temperature sensor is inserted into the first insertion block for the first expansion valve; the first insertion block for the first expansion valve also integrates the temperature sensor function; the shut-off valve(s) and the temperature sensor(s) have parallel longitudinal extension directions; and the longitudinal extension directions of the first and second shut-off valves, as well as the first and second temperature sensors, are perpendicular to the longitudinal extension axes of the first and second expansion valves.at least one shut-off valve is provided on a first refrigerant circulation zone of the support and intended for the circulation of high-pressure refrigerant; at least one temperature sensor is provided on a second refrigerant circulation zone of the support and intended for the circulation of high-pressure refrigerant and / or low-pressure refrigerant.

[0008] Other advantages and features of the present invention will become more apparent upon reading the following description, given by way of illustration and not limitation, and the accompanying drawings in which: There figure 1 [Fig.1 [ ] is a simplified perspective view of a support for the fluid management module for a vehicle according to the invention, on which the circulation channels have not been shown. figure 2 [Fig.2 ] is a side view of the support for the fluid management module of the figure 1 [Fig. 1 ]. There figure 3 [Fig.3 [ ] is a simplified top view of a second face of the support for the fluid management module according to the invention; the second face showing the circulation channels and some of the elements arranged on this second face. figure 4 [Fig.4 [ ] is a simplified perspective view of the second face of the support for the fluid management module according to the invention; the second face showing the circulation channels and some of the elements arranged on this second face. figure 5 [Fig.5 [ ] is a simplified top view of a portion of the second face of the support for the fluid management module according to the invention; in particular, a first refrigerant circulation zone intended for the circulation of the refrigerant at high pressure, this first zone having the circulation channels and some of the elements arranged on this first zone. figure 6 [Fig. 6 [ ] is a bottom view of a first face of the support for the fluid management module according to the invention. The figure 7 [Fig. 7 [ ] is a top view of the second face of the support for the fluid management module according to the invention. The figure 8 [Fig. 8 ] is a simplified side view of the second face of the support for the fluid management module according to the invention, the second face showing the circulation channels and part of the elements arranged on this second face.

[0009] A fluid management module for a vehicle, in particular a motor vehicle, includes a support 10 having at least two channels 60 and 64 for the circuit of a refrigerant fluid.

[0010] Here, the support 10 is formed of at least a first circulation zone 12 of the refrigerant fluid intended for the circulation of the refrigerant fluid at high pressure and a second circulation zone 14 of the refrigerant fluid intended at least for the circulation of the refrigerant fluid at low pressure.

[0011] The refrigerant used in the refrigerant circuit is a chemical fluid such as R1234yf. Other refrigerants could be used, such as R134a or R290.

[0012] The term "high pressure refrigerant" refers to a refrigerant at a pressure of around 20 bar, and "low pressure refrigerant" to a pressure of 3 bar.

[0013] In the particular embodiment illustrated in particular in figures 3 And 4, the support 10 is formed of at least a first circulation zone 12 of the refrigerant fluid intended for the circulation of the refrigerant fluid at high pressure and a second circulation zone 14 of the refrigerant fluid intended at least for the circulation of the refrigerant fluid at high pressure and / or at low pressure.

[0014] This support 10 is also called the central platform (or "hub" in its English name). The support 10 is intended to be part of a thermal management system of a motor vehicle in which the refrigerant circulates, in particular in an air conditioning and / or heat pump circuit.

[0015] In other words, support 10 is a refrigerant fluid circulation unit.

[0016] According to one embodiment, the support 10 is formed of two plates fixed to each other. In such a case, the channels for the refrigerant circuit are formed by at least one deformation of one of the two plates.

[0017] Put another way, and in this particular embodiment, the support 10 integrates the channels for the circuit of a refrigerant fluid.

[0018] According to this embodiment, the plates forming the support 10 each have one or more flat regions between the channels 60, 64.

[0019] According to this embodiment again, the thickness of the plates forming the support is substantially uniform both at the level of the flat regions and at the level of the channels 60, 64.

[0020] One particular, unillustrated embodiment proposes that the support 10 includes at least one first plate, called a transfer plate, shaped to form at least one channel or corrugation for the flow of the fluid. In other words, the curvatures of the transfer plate constitute passages that form the channels.

[0021] In this particular, unillustrated embodiment, the support 10 includes at least one second plate called a support plate. The support plate is configured to provide the interface between the support 10 and elements attached to the support 10.

[0022] The support plate may be flat in order to be in contact with part of the elements fixed to the support 10.

[0023] Put another way, in this embodiment, the flat support plate partly defines the conduits for the refrigerant.

[0024] According to another embodiment, the support 10 is formed of a flat plate on which conduits for the refrigerant fluid are attached and secured.

[0025] In the embodiment illustrated in the figure 3 , the support 10 includes at least one first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0026] The first channel 60, intended for the circulation of the high-pressure refrigerant fluid, has in the embodiment illustrated here a substantially Y-shaped form, with a main branch 60-1 and two branches called first (60-2) and second (60-3) branches.

[0027] In a particular embodiment, at least one valve support block is inserted on a branch of the first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0028] In the particular embodiment illustrated in figures 3 And 4, two valve support blocks 70-2 and 70-3 are each inserted on a branch 60-2 or 60-3 of the first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0029] Here, the valve support blocks 70-2 and 70-3 are each suitable for receiving a valve, in particular a shut-off valve 72-2 or 72-3 visible at the figure 5 .

[0030] Alternative embodiments not shown propose that the support 10 incorporate valves such as progressive, EXV (for "electronic expansion valve") or TXV (for "thermostatic expansion valve") valves. These valves will preferably be attached to the support 10 via a valve support block common to several valves and / or an individual support block specific to each valve.

[0031] Thus, the support 10 includes at least one valve support block 70-2 or 70-3 which can be seen as a refrigerant distribution block in the support 10.

[0032] Put another way, a shut-off valve 72-2 or 72-3 is made in fluidic communication with the first channel 60 intended for the circulation of the high-pressure refrigerant fluid via, in this particular embodiment, the valve support block 70-2 or 70-3.

[0033] More specifically, here, the fluid communication takes place at the level of each respective branch 60-2 or 60-3 of the first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0034] A temperature sensor 74 (visible for example at the figure 5 ) is planned at the level of the first channel 60 intended for the circulation of the high-pressure refrigerant fluid.

[0035] In the embodiment illustrated here, the temperature sensor 74 is arranged on one of the two branches of the first channel 60 intended for the circulation of the high-pressure refrigerant fluid (here the second branch 60-2).

[0036] In particular, the temperature sensor 74 is located near the junction between the main branch 60-1 and the two branches 60-2 and 60-3 of the first channel 60 intended for the circulation of the high-pressure refrigerant.

[0037] As mentioned above, the first channel 60 is intended for the circulation of the high-pressure refrigerant fluid.

[0038] In this embodiment, the main branch 60-1 of the first channel 60 is intended to ensure communication between a first flange 101, fluidly connected to a compressor 20, and the first (60-2) and second (60-3) branches.

[0039] The first branch 60-2 is intended to provide communication between the main branch 60-1 and a heat exchanger, hereinafter referred to as the third heat exchanger.

[0040] According to this embodiment, the third heat exchanger 52 is a water-cooled condenser type. This exchanger is configured to perform heat exchange between the high-pressure refrigerant and a heat transfer fluid.

[0041] The second branch 60-3 is designed to provide communication between the main branch 60-1 and a second flange 102, which is fluidically connected to an internal condenser, not shown here. This internal condenser is a thermal regulation device for the vehicle's passenger compartment, located, for example, within the vehicle's passenger compartment. The internal condenser is designed to heat an airflow passing through it.

[0042] The support 10 also includes at least one second channel 62 for the circulation of the high-pressure refrigerant fluid.

[0043] In the particular embodiment illustrated in the figure 3 , the support 10 has four second channels 62-1, 62-2, 62-3, 62-4 intended for the circulation of the high-pressure refrigerant fluid.

[0044] In this same embodiment, one of the second channels, hereinafter referred to as 62-1, is intended to ensure communication between a third flange 103, fluidly connected to a bottle 56 and another heat exchanger, hereinafter referred to as the first heat exchanger 54.

[0045] According to this embodiment, bottle 56 is a desiccant bottle, configured to contain the refrigerant fluid at high pressure and capture the moisture from the refrigerant fluid passing through it.

[0046] According to another embodiment, not shown, bottle 56 can be an accumulator. In this alternative embodiment, bottle 56, or the accumulator, would be placed on a low-pressure section of the circuit.

[0047] According to the embodiment illustrated in the figure 3 The first heat exchanger 54 is an internal heat exchanger, which transfers heat between a low-pressure section of the refrigerant circuit and a high-pressure section of the same circuit. This heat exchange optimizes the thermodynamic properties of the refrigerant circuit.

[0048] In this same embodiment, one of the second channels, hereinafter referred to as 62-2, is intended to ensure communication between the third heat exchanger 52 and a fourth flange 104, fluidly connected to the bottle 56.

[0049] In the same embodiment illustrated here, one of the second channels, hereinafter referred to as 62-3, is intended to provide communication between the first heat exchanger 54 and a valve, preferably an expansion valve. In the remainder of this description, this expansion valve will be referred to as the second expansion valve 28.

[0050] In the same embodiment illustrated here, one of the second channels, referenced below as 62-4, is intended to provide communication between the first heat exchanger 54 and another valve, preferably an expansion valve. In the remainder of this description, this expansion valve will be referred to as the first expansion valve 26.

[0051] Each of the expansion valves 26, 28, also called expansion valves, can be an electronic expansion valve (EXV), a thermostatic expansion valve (TXV), or a calibrated orifice. In the case of an electronic expansion valve, the passage area allowing the refrigerant to pass through can be continuously adjusted between a closed position and a maximum open position. For this purpose, an electronic controller drives an electric motor that moves a movable shutter, thus controlling the passage area available to the refrigerant.

[0052] The support 10 also includes at least a third channel 64, intended for the circulation of the low-pressure refrigerant fluid.

[0053] In the particular embodiment illustrated in the figure 3 , the support 10 has five third channels 64-1, 64-2, 64-3, 64-4 and 64-5 intended for the circulation of the low pressure refrigerant fluid.

[0054] In this same embodiment, one of the third channels, hereinafter referred to as 64-1, is intended to provide communication between a fifth flange 105, fluidly connected to an evaporator (not shown), and the first heat exchanger 54. This evaporator is a thermal regulation device for the vehicle's passenger compartment, located, for example, within the passenger compartment of said vehicle. The evaporator is intended to cool an airflow passing through it.

[0055] Still in this same embodiment illustrated here, one of the third channels, hereinafter referred to as 64-2, is intended to ensure communication between the first heat exchanger 54 and a sixth flange 106, fluidly connected to the compressor 20.

[0056] In this same embodiment, one of the third channels, hereinafter referred to as 64-3, is intended to ensure communication between yet another heat exchanger (hereinafter referred to as the second heat exchanger 50) and the first heat exchanger 54.

[0057] According to this embodiment, the second heat exchanger 50 is a water chiller (or "chiller" in its English name). This exchanger is configured to perform a heat exchange between the low-pressure refrigerant and a heat transfer fluid.

[0058] Still in this same embodiment, one of the third channels, hereinafter referred to as 64-4, is intended to ensure communication between the second expansion valve 28 and the second heat exchanger 50.

[0059] In this same embodiment, one of the third channels, hereinafter referred to as 64-5, is intended to ensure communication between the first expansion valve 26 and the seventh flange 107, fluidly connected to the evaporator.

[0060] The two expansion valves 26, 28 allow control of the refrigerant supply to the evaporator and the second heat exchanger 50. Thus, depending on the position of the expansion valves, 26, 28 the evaporator and / or the second heat exchanger 50 can be supplied with refrigerant.

[0061] According to one embodiment, the first (54), second (50) and third (52) heat exchangers are fluidically connected to the first, second and third channels 60, 62, 64, via flanges. More specifically, the first heat exchanger 54 is connected by means of an eighth, ninth, tenth and eleventh flange, respectively to the second channel 62-1, the second channels 62-3 and 62-4, the third channel 64-2 and the third channels 64-1 and 64-3; the second heat exchanger 50 is connected by means of a twelfth and thirteenth flange, respectively to the third channel 64-3 and the third channel 64-4; the third heat exchanger 52 is connected by means of a fourteenth flange and a fifteenth flange, respectively to the first branch 60-2 of the first channel 60 and to the second channel 62-2.

[0062] In the embodiment illustrated in particular in figures 3 and following, the at least first channel 60 intended for the circulation of the high-pressure refrigerant is disposed on the first circulation zone 12 of the refrigerant and intended for the circulation of the high-pressure refrigerant, while the at least third channel 64 intended for the circulation of the low-pressure refrigerant is disposed on a second circulation zone 14 of the refrigerant intended for the circulation of the low-pressure refrigerant.

[0063] In the particular example illustrated here, the first circulation zone 12 is distinct from the second circulation zone 14 of the refrigerant fluid.

[0064] The first traffic zone 12 can be thermally insulated from the second traffic zone 14.

[0065] The first circulation zone 12 of the refrigerant extends substantially along a first plane P1 and the second circulation zone 14 of the refrigerant extends substantially along a second plane P2.

[0066] The first plan P1 of the first circulation zone 12 of the refrigerant fluid and the second plan P2 of the second circulation zone 14 of the refrigerant fluid are different.

[0067] In this embodiment, the first plane P1 of the first circulation zone 12 of the refrigerant fluid and the second plane P2 of the second circulation zone 14 of the refrigerant fluid are parallel planes.

[0068] The first refrigerant circulation zone 12 and the second refrigerant circulation zone 14 are connected by a first common edge 16.

[0069] In an embodiment not shown, the first common edge 16 has openings.

[0070] According to the invention, the support 10 further comprises a first opening 24 suitable for receiving at least in part an expansion valve 26.

[0071] In the embodiment shown here, the first opening 24 receives at least in part two bodies of two expansion valves 26 and 28 distinct from each other.

[0072] The first expansion valve 26 is connected to the evaporator (not shown) and located in another part of the motor vehicle, specifically in an air conditioning unit.

[0073] The second expansion valve 28 is connected to a second exchanger 50, preferably of the water cooler type, and arranged on one face of the support 10 and opposite the second expansion valve 28.

[0074] In the embodiment shown here, the first common edge 16 extends along the first opening 24. This extension provides, in particular, a mechanical reinforcement function for the support 10.

[0075] The support 10 has a second opening 33 extending at least over the third zone 18 suitable for receiving at least part of the compressor 20.

[0076] This second opening 22 can be seen as a cutout allowing lightening of the support 10 and allowing definition of two fixing tabs for the compressor 20.

[0077] The second opening 33 also extends over the common edge 22 to the third zone 18 and the second circulation zone 14 of the refrigerant fluid.

[0078] In other words, this first opening 24 allows the body of the expansion valve 26 to be housed at least in part.

[0079] In a particular embodiment, the expansion valve 26 is an electronically controlled expansion valve.

[0080] The first expansion valve 26 is connected to an evaporator (not shown) and located elsewhere in the motor vehicle, specifically in an air conditioning unit.

[0081] The first opening 24 includes a step 32 defining a first landing 32-1 and a second landing 32-2.

[0082] The first opening 24 is suitable to receive at least in part a first 26 and a second 28 expansion valve.

[0083] Each of the first and second bearings 32-1 and 32-2 is suitable for receiving a first or second expansion valve 26 and 28.

[0084] The first bearing 32-1 comprising a first insertion block 34 for the first expansion valve 26.

[0085] Here, the first insertion block 34 is machined to allow the insertion of the first expansion valve 26 in a direction parallel to an extension plane of the support 10. This saves space, making the module more compact.

[0086] An illustrated method of implementation figure 7 proposes that the first insertion block 34 be also machined to accommodate a second temperature sensor 76.

[0087] In other words, the first insertion block 34 allows the integration of fluid distribution functions (via the valve, here expansion) and temperature sensor into the fluid management module.

[0088] In the embodiment illustrated here, the first insertion block 34 allows insertion of the first expansion valve 26 in a direction parallel to the plane P1 of the first circulation zone 12 of the refrigerant fluid.

[0089] In this particular embodiment, the first expansion valve 26 has a longitudinal extension axis. The longitudinal extension axis of the first expansion valve 26 is parallel to plane P1 of the first circulation zone 12 of the refrigerant.

[0090] The second bearing 32-2 includes a second insertion block 36 for the second expansion valve 28.

[0091] The second expansion valve 28 is connected to a second heat exchanger 50, preferably a water cooler type heat exchanger, and is positioned on the support 10 and opposite the second expansion valve 28.

[0092] In other words, this first opening 24 allows at least part of the body of the second expansion valve 28 to be housed.

[0093] In the embodiment illustrated here, the first opening 24 accommodates two expansion valves 26 and 28.

[0094] In a particular embodiment, the second expansion valve 28 is an electronically controlled expansion valve.

[0095] Here, the second insertion block 36 allows the insertion of the second expansion valve 28 in a direction parallel to an extension plane of the support 10. This saves space, making the module more compact.

[0096] In the embodiment illustrated here, the second insertion block 36 is machined so as to allow the insertion of the second expansion valve 28 in a direction parallel to the plane P1 of the first circulation zone 12 of the refrigerant fluid.

[0097] In this particular embodiment, the second expansion valve 28 has a longitudinal extension axis. The longitudinal extension axis of the second expansion valve 28 is parallel to the plane P1 of the first circulation zone 12 of the refrigerant.

[0098] The support 10 includes a third zone 18 suitable for receiving at least part of a compressor 20, the third zone 18 being separate from the first refrigerant circulation zone 12 and the second refrigerant circulation zone 14.

[0099] The third zone 18 extends substantially along a third plane P3, the third plane P3 being different from the first plane P1 of the first circulation zone 12 of the refrigerant fluid and from the second plane P2 of the second circulation zone 14 of the refrigerant fluid.

[0100] In this embodiment, the first plane P1 of the first circulation zone 12 of the refrigerant fluid, the second plane P2 of the second circulation zone 14 of the refrigerant fluid and the third plane P3 of the third zone 18 are parallel planes.

[0101] The third zone 18 and the second circulation zone 14 of the refrigerant fluid are connected by a second common edge 22.

[0102] According to the invention, the fluid management module for a vehicle, particularly a motor vehicle, comprises: the support 10 having a first face 40 and a second face 42, the first face 40 being opposite the second face 42, and, at least one channel 60, 62 and 64 for the circuit of a refrigerant fluid the first face 40 of the support 10 supports at least one first heat exchanger 54 and the second face 42 of the support 10 supports at least one valve 72-2 or 72-3.

[0103] Such a configuration allows for space saving by placing different elements of the fluid management module on both sides of support 10 in an optimized manner.

[0104] In the embodiment illustrated here, the first heat exchanger 54 is an exchanger called an internal heat exchanger (or "IHX" for "Internal Heat Exchanger" in its English name). The first internal heat exchanger 54 allows heat exchange between the refrigerant circulating at high pressure and the refrigerant circulating at low pressure.

[0105] The first face 40 of the support 10 supports a second heat exchanger 50.

[0106] In the embodiment illustrated here, the second heat exchanger 50 is a water-cooled type heat exchanger. This second water-cooled heat exchanger 50 enables heat exchange between the refrigerant and a heat transfer fluid, in this case, glycol water.

[0107] The first face 40 of the support 10 supports a third heat exchanger 52.

[0108] In the embodiment illustrated here, the third heat exchanger 52 is a water-cooled condenser (or "WCDS" for "Water Condenser" in its English name). This third water-cooled condenser also allows for heat exchange between the refrigerant and a heat transfer fluid, in this case, glycol water.

[0109] The second heat exchanger 50 is arranged between the first heat exchanger 54 and the third heat exchanger 52.

[0110] This has the technical effect of improving the efficiency of heat exchange through the module by contributing to the creation of a thermal gradient. Indeed, the third heat exchanger 52, a water-cooled condenser, has a refrigerant circulating that is warmer than the one circulating in the second heat exchanger 50, a water-cooled chiller.

[0111] The first internal heat exchanger 54 is positioned at a distance from the third water condenser heat exchanger 52 so that the latter does not transmit heat to the first internal heat exchanger 54.

[0112] More specifically, an air gap separates the first heat exchanger 54 from the third heat exchanger 52, this air gap having the effect of thermally insulating them from each other.

[0113] The first heat exchanger 54, the second heat exchanger 50, and the third heat exchanger 52 each have a length and a width. The length of each of the first heat exchanger 54, second heat exchanger 50, and third heat exchanger 52 defines a longitudinal extension direction L1, L2, and L3, respectively. The longitudinal extension directions L2 and L3 of the second heat exchanger 50 and the third heat exchanger 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 heat exchanger 50 and the third heat exchanger 52.

[0114] Such a distribution also contributes to improving the efficiency of heat exchange through the module by participating in the creation of a thermal gradient.

[0115] In the embodiment illustrated here, the first heat exchanger 54 includes a notch, or cutout, extending from the side of the support 10, perpendicular to the longitudinal extension direction L1 of said first heat exchanger 54. This cutout has the effect of creating a space allowing the passage of at least one of the channels 60, 62, 64 of the fluid management module.

[0116] In the embodiment illustrated here, it should be noted that the first expansion valve 26 is located near the second heat exchanger 50 of the water cooler type.

[0117] As mentioned above, the first expansion valve 26 has a longitudinal extension axis. The longitudinal extension axis of the first expansion valve 26 is parallel to the plane P1 of the first refrigerant circulation zone 12.

[0118] Moreover, here, the longitudinal extension axis of the first expansion valve 26 is parallel to the longitudinal extension directions L2 and L3 of the second heat exchanger 50 and the third heat exchanger 52.

[0119] This arrangement also leads to improved compactness of the fluid management module.

[0120] The first heat exchanger 54 is arranged on a first circulation zone 12 of the refrigerant fluid of the support 10 and intended for the circulation of the refrigerant fluid at high pressure.

[0121] The second heat exchanger 50 and the third heat exchanger 52 are arranged on a second circulation zone 14 of the refrigerant fluid of the support 10 and intended for the circulation of the refrigerant fluid at high pressure and / or for the circulation of the refrigerant fluid at low pressure.

[0122] The second side 42 of the support 10 also includes a compressor 20.

[0123] In this embodiment, the compressor 20 is attached to the second face 42 of the support 10 by any means such as, for example, screws.

[0124] It is also possible to provide vibration absorption devices placed between the support 10 and the compressor 20.

[0125] Such absorption devices, or other mechanical decoupling elements, could also be interposed between the support 10 and the vehicle structure.

[0126] The second side 42 of the support 10 also includes a bottle 56.

[0127] In other words, in this embodiment, the bottle 56 is attached to the second face 42 of the support 10.

[0128] Bottle 56 is a desiccant bottle, with the function of separating the liquid refrigerant and the gaseous refrigerant, at high pressure, to allow storage and to capture the moisture of the refrigerant that passes through it.

[0129] In another embodiment, bottle 56 could be an accumulator. According to this alternative embodiment, bottle 56, or the accumulator, would be placed on a low-pressure section of the circuit.

[0130] Bottle 56 could be fitted with a refrigerant charging valve.

[0131] Compressor 20 and bottle 56 each have a longitudinal extension direction L4 and L5 respectively. The longitudinal extension direction L4 of the compressor is perpendicular to the longitudinal extension direction L5 of bottle 56.

[0132] The longitudinal extension directions L4 and L5, respectively of compressor 20 and bottle 56, extend parallel to the first, second and third planes P1, P2 and P3.

[0133] These arrangements of compressor 20 and bottle 56 improve the compactness of the fluid management module.

[0134] The second face 42 of the support 10 has at least one valve 73-2 or 72-3.

[0135] In the embodiment illustrated in the figure 7 Two valves are planned, here stop valves 72-1 and 72-2. In particular, these stop valves 72-2 and 72-3 are planned to be arranged on valve support blocks 70-2 and 70-3 (not visible at the figure 7 ).

[0136] The second face 42 of the support 10 has at least one temperature sensor 74 or 76.

[0137] In the embodiment illustrated in the figure 7 , a first temperature sensor 74 is disposed near at least one shut-off valve 72-2 or 72-4.

[0138] As an example of implementation, it is possible to provide a second temperature sensor 76 placed here near the first expansion valve 26.

[0139] More specifically, the second temperature sensor 76 is inserted into the first insertion block 34 for the first expansion valve 26.

[0140] In other words, the first insertion block 34 for the first expansion valve 26 also incorporates the temperature sensor function. To achieve this, a particular embodiment provides that the first insertion block 34 for the first expansion valve 26 is machined to receive the second temperature sensor 76.

[0141] The first and second shut-off valves 72-2 and 72-3 and the first and second temperature sensors 74 and 76 all have a longitudinal extension direction.

[0142] The shut-off valve 72-2 or 72-3 and the temperature sensor 74 or 76 have parallel longitudinal extension directions.

[0143] In this embodiment, notably illustrated in the figure 8, the longitudinal extension directions of the first and second stop valves 72-2 and 72-3 as well as the first and second temperature sensors 74 and 76 are all parallel to each other and parallel to the X direction.

[0144] It should be noted that in this particular embodiment, the longitudinal extension directions of the first and second stop valves 72-2 and 72-3 and of the first and second temperature sensors 74 and 76 are perpendicular to the longitudinal extension axes of the first expansion valve 26 and the second expansion valve 28.

[0145] At least one shut-off valve 72-2 or 72-3 is disposed on a first circulation zone 12 of the refrigerant fluid of the support 10 and intended for the circulation of the refrigerant fluid at high pressure. At least one temperature sensor 76 is disposed on a second circulation zone 14 of the refrigerant fluid of the support 10 and intended for the circulation of the refrigerant fluid at high pressure and / or for the circulation of the refrigerant fluid at low pressure.

[0146] The invention is not limited to the embodiments shown, and other embodiments will be obvious to those skilled in the art. In particular, any other fastening means may be used, provided they are reversible.

Claims

1. A fluid management module for a vehicle, in particular a motor vehicle, comprising: • a support (10) having a first face (40) and a second face (42), the first face (40) being opposite the second face (42), and, • at least one channel (60, 62; 64) for the circuit of a refrigerant fluid, • wherein the first face (40) of the support (10) supports at least one first heat exchanger (54) and the second face (42) of the support (10) supports at least one valve (72-2; 72-3), characterized in that the first face (40) of the support (10) supports a second heat exchanger (50).

2. The fluid management module according to the preceding claim, wherein the first face (40) of the support (10) supports a third heat exchanger (52).

3. The fluid management module (10) according to the preceding claim, wherein the second heat exchanger (50) is disposed between the first heat exchanger (54) and the third heat exchanger (52).

4. The fluid management module according to the preceding claim, wherein the first heat exchanger (54), the second heat exchanger (50), and the third heat exchanger (52) each have a length and a width, the length of each of the first heat exchanger (54), second heat exchanger (50), and third heat exchanger (52) respectively defining a longitudinal extension direction (L1, L2; L3), and wherein the longitudinal extension directions (L2; L3) of the second heat exchanger (50) and the third heat exchanger (52) are parallel, and wherein the longitudinal extension direction (L1) of the first heat exchanger (54) is perpendicular to the longitudinal extension directions (L2; L3) of the second heat exchanger (50) and the third heat exchanger (52).

5. The fluid management module according to claims 2 to 4, wherein: • the first heat exchanger (54) is disposed on a first circulation zone (12) of the refrigerant fluid of the support (10) and intended for the circulation of the high-pressure refrigerant fluid, and, • the second heat exchanger (50) and the third heat exchanger (52) are disposed on a second circulation zone (14) of the refrigerant fluid of the support (10) and intended for the circulation of the high-pressure refrigerant fluid and / or for the circulation of the low-pressure refrigerant fluid.

6. The fluid management module according to the preceding claim, wherein the first circulation zone (12) of the refrigerant fluid extends substantially along a first plane (P1) and the second circulation zone (14) of the refrigerant fluid extends substantially along a second plane (P2), and wherein the first plane (P1) of the first circulation zone (12) of the refrigerant fluid and the second plane (P2) of the second circulation zone (14) of the refrigerant fluid are different.

7. The fluid management module according to the preceding claim, wherein the first circulation zone (12) of the refrigerant fluid and the second circulation zone (14) of the refrigerant fluid are connected by a first common edge (16).

8. The fluid management module for a vehicle, in particular a motor vehicle, according to one of the preceding claims, wherein the second face (42) of the support (10) further comprises a compressor (20).

9. The fluid management module for a vehicle, in particular a motor vehicle, according to one of the preceding claims, wherein the second face (42) of the support (10) further comprises a bottle (56).

10. The fluid management module for a vehicle, in particular a motor vehicle, according to one of the preceding claims, wherein the second face (42) of the support (10) comprises at least one temperature sensor (74; 76).

11. The fluid management module for a vehicle, in particular a motor vehicle, according to the preceding claim, wherein the valve (72-2; 72-3) and the temperature sensor (74; 76) have parallel longitudinal extension directions.

12. The fluid management module according to claims 10 to 11, wherein: • At least one valve (72-2; 72-3) is disposed on a first circulation zone (12) of the refrigerant fluid of the support (10) and intended for the circulation of the high-pressure refrigerant fluid. • At least one temperature sensor (76) is disposed on a second circulation zone (14) of the refrigerant fluid of the support (10) and intended for the circulation of the high-pressure refrigerant fluid and / or for the circulation of the low-pressure refrigerant fluid.

13. The fluid management module according to the preceding claim, wherein the first circulation zone (12) of the refrigerant fluid extends substantially along a first plane (P1) and the second circulation zone (14) of the refrigerant fluid extends substantially along a second plane (P2), and wherein the first plane (P1) of the first circulation zone (12) of the refrigerant fluid and the second plane (P2) of the second circulation zone (14) of the refrigerant fluid are different.

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