FR3134883A1 - Support for a fluid management module for a vehicle, in particular an automobile, and a fluid management module comprising such a support - Google Patents

Abstract

The invention relates to a support (10) for a fluid management module for a vehicle, in particular a motor vehicle, said support (10) comprising at least two channels (60; 64) for the circuit of a refrigerant fluid characterized in that the support (10) is formed of at least a first circulation zone (12) of the refrigerant fluid and intended for the circulation of the refrigerant fluid at high pressure and of a second circulation zone (14) of the refrigerant fluid and intended at least for the circulation of the refrigerant fluid at low pressure. [Fig. 1]

Description

Support for a fluid management module for a vehicle, in particular an automobile, and a fluid management module comprising such a support

The invention relates to a support for a fluid management module for a vehicle, in particular an automobile, and a fluid management module comprising such a support.

Motor vehicles, in particular electric vehicles, are equipped with thermal management systems such as cooling and/or heating circuits in order to ensure comfort functions for the users of this vehicle and necessary control of the temperature of the vehicle. components of the motor vehicle, such as, for example, batteries. Such circuits commonly use a refrigerant loop and a heat transfer liquid loop exchanging heat with the refrigerant.

The cooling and/or heating circuits consist in particular of thermal management components, such as pumps, valves, heat exchangers, as well as components used for temperature regulation. Components, such as conduits, guiding a fluid and fluidly connecting the thermal management components together are also provided.

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 creating demand for space-saving systems.

The invention aims to propose a solution to improve the situation.

As such, it proposes a support for a fluid management module for a vehicle, in particular a motor vehicle, said support comprising at least two channels for the circuit of a refrigerant fluid characterized in that the support is formed of at least at least a first circulation zone of the refrigerant fluid and intended for the circulation of the refrigerant fluid at high pressure and a second circulation zone of the refrigerant fluid and intended at least for the circulation of the refrigerant fluid at low pressure.

Thus, such a support for a fluid management module offers an optimized arrangement of the refrigerant fluid circulation channels which results in a reduced footprint of the fluid management module equipped with such a support.

The support for a fluid management module according to the invention may further comprise at least one of the following characteristics, taken alone or in combination:

• the support is formed of at least a first circulation zone of the refrigerant fluid and intended for the circulation of the refrigerant fluid at high pressure and of a second circulation zone of the refrigerant fluid and intended at least for the circulation of the refrigerant fluid at high pressure pressure and/or low pressure,
• the support is a refrigerant circulation unit,
• the support is formed of two plates secured to each other,
• the channels for the circuit of a refrigerating fluid are formed by at least one deformation of one of the two plates,
• The support integrates the channels for the circuit of a refrigerant fluid,
• the support comprises at least a first plate, called a transfer plate, shaped to form at least one channel or an undulation for the circulation of the fluid,
• the support comprises at least a second plate called a support plate configured to provide the interface between the support and elements secured to the support,
• the support plate is flat to be in contact with part of the elements secured to the support,
• the flat support plate partly defines the conduits for the refrigerant fluid,
• the support is formed of a flat plate on which conduits for the refrigerant fluid are attached and secured,
• the support comprises at least a first channel intended for the circulation of the refrigerant fluid at high pressure.
• a first channel intended for the circulation of the refrigerant fluid at high pressure, has a substantially Y shape, with a main branch and two branches called first and second branches,
• at least one valve support block is inserted on a branch of the first channel intended for the circulation of the refrigerant fluid at high pressure,
• two valve support blocks are each inserted on a branch of the first channel intended for the circulation of the refrigerant fluid at high pressure,
• the valve support blocks are capable of each receiving a valve, in particular a stop 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 comprises at least a second channel intended for the circulation of the refrigerant fluid at high pressure,
• the support comprises four second channels intended for the circulation of the refrigerant fluid at high pressure,
• one of the second channels is intended to ensure communication between a third flange, fluidly connected to a bottle 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 bottle,
• one of the second channels is intended to ensure communication between a heat exchanger and a valve, preferably an expansion valve,
• one of the second channels is intended to ensure communication between a heat exchanger and a valve, preferably an expansion valve,
• the support also comprises at least a third channel intended for the circulation of the refrigerant fluid at low pressure,
• the support has five third channels intended for the circulation of the refrigerant fluid at low pressure,
• 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 fluidly connected to the evaporator,
• the at least first channel intended for the circulation of the refrigerant fluid at high pressure is arranged on the first zone of circulation of the refrigerant fluid and intended for the circulation of the refrigerant fluid at high pressure, while the at least third channel intended for the circulation of the low-pressure refrigerant fluid is arranged in a second refrigerant circulation zone intended for the circulation of the low-pressure refrigerant fluid,
• the first circulation zone is distinct from the second circulation zone of the refrigerant fluid,
• the first circulation zone can be thermally isolated from the second circulation zone,
• the first circulation zone of the refrigerant fluid extends substantially along a first plane and the second circulation zone of the refrigerant fluid extends substantially along a second plane and the first plane of the first circulation zone of the refrigerant fluid and the second plane of the second refrigerant circulation zone are different,
• the first plane of the first circulation zone of the refrigerant fluid and the second plane of the second circulation zone of the refrigerant fluid 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 comprises a third zone capable of receiving at least in part a compressor, the third zone being distinct from the first zone of circulation of the refrigerant fluid and the second zone of circulation of the refrigerant fluid,
• the third zone extends substantially along a third plane, the third plane being different from the first plane of the first zone of circulation of the refrigerant fluid and the second plane of the second zone of circulation of the refrigerant fluid,
• the first plane of the first zone of circulation of the refrigerant fluid, the second plane of the second zone of circulation of the refrigerant fluid and the third plane of the third zone are parallel planes,
• the third zone and the second zone of circulation of the refrigerant fluid and are connected by a second common edge
• the support further comprises a first opening capable of receiving at least in part an expansion valve,
• the first opening receives at least in part two bodies of two expansion valves distinct from each other.
• the support comprises a second opening extending at least over the third zone capable of receiving at least in part a compressor,
• the second opening also extends on the edge common to the third zone and the second zone of circulation of the refrigerant fluid,
• the first opening comprises a step defining a first landing and a second landing,
• the first opening is capable of receiving at least in part a first and a second expansion valve,
• each of the first and second bearings is capable of receiving a first or a second expansion valve,
• the first common edge extends along the first opening,
• The first insert block allows the integration of fluid distribution and temperature sensor functions into the fluid management module.
• the first insertion block allows insertion of the first expansion valve in a direction parallel to the plane of the first circulation zone of the refrigerant fluid.

The invention also relates to a fluid management module comprising a support as described above.

The fluid management module may also include at least one of the following characteristics, taken alone or in combination:

• the stop valve is secured to the support via a valve support block common to several valves and/or an individual support block specific for each valve.
• the stop valve is placed in fluid communication with the first channel intended for the circulation of the refrigerant fluid at high pressure via, preferably, the valve support block.
• a temperature sensor is provided at the level of the first channel intended for the circulation of the refrigerant fluid at high pressure,
• the temperature sensor is arranged on one of the two branches of the first channel intended for the circulation of the refrigerant fluid at high pressure
• a water condenser type heat exchanger,
• the bottle is a desiccant bottle, configured to contain the refrigerant at high pressure and capture the humidity of the refrigerant passing through it,
• an internal heat exchanger, said internal heat exchanger making it possible to carry out a transfer of calories between a low pressure portion of the refrigerant circuit and a high pressure portion of said refrigerant circuit,
• expansion valves, also called expansion valves, can be an electronic expansion valve, or EXV, a thermostatic expansion valve, or TXV, or a calibrated orifice,
• a water cooler type heat exchanger,
• three heat exchangers are fluidly connected to the first, second and third channels via flanges,
• the module further comprises a first expansion valve, the first bearing comprising a first insertion block for the first expansion valve,
• the first insertion block is machined so as 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 so as to accommodate a second temperature sensor,
• a longitudinal extension axis of an expansion valve is parallel to the plane of the first circulation zone of the refrigerant fluid,
• the module further comprises a second expansion valve and the second bearing comprises a second insertion block for the second expansion valve,
• the second expansion valve is connected to a heat exchanger, preferably a water cooler, and arranged 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 so as to allow the insertion of the second expansion valve in a direction parallel to the plane of the first circulation zone of the refrigerant fluid,
• the axis of longitudinal extension of the second expansion valve is parallel to the plane of the first circulation zone of the refrigerant fluid,
• the fluid management module for a vehicle, in particular an automobile, comprises 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, 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,
• the first face of the support supports a second heat exchanger,
• the first face of the support supports a third heat exchanger,
• the second heat exchanger is arranged between the first heat exchanger and the third heat exchanger,
• the first heat exchanger is an internal exchanger and is arranged at a distance from the third water condenser type heat exchanger
• the first heat exchanger, the second heat exchanger and the third heat exchanger each have a length and a width, the length of each of the first heat exchanger, second heat exchanger and third heat exchanger defining a direction of extension longitudinal and the longitudinal extension directions of the second heat exchanger and the third heat exchanger are parallel and the longitudinal extension direction of the first heat exchanger is perpendicular to the longitudinal extension directions of the second heat exchanger and the third exchanger heat,
• the first expansion valve is arranged near the second water cooler type heat exchanger,
• the first heat exchanger is arranged on a first circulation zone of the refrigerant fluid of the support and intended for the circulation of the refrigerant fluid at high pressure, and, the second heat exchanger and the third heat exchanger are arranged on a second zone of circulation of the refrigerant fluid of the support and intended for the circulation of the refrigerant fluid at high pressure and/or for the circulation of the refrigerant fluid at low pressure,
• the second face of the support further comprises a compressor,
• the compressor is secured to the second face of the support by any means such as for example screws.
• vibration absorption devices placed between the support and the compressor,
• the second face of the support further comprises a bottle,
• the compressor and the bottle each have a direction of longitudinal extension respectively and the directions of longitudinal extension of the compressor is perpendicular to the direction of longitudinal extension of the bottle,
• the module has two stops, preferably arranged on valve support blocks,
• the second face of the support comprises at least one temperature sensor,
• a first temperature sensor is placed near at least one stop valve,
• a second temperature sensor is arranged 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 stop valve(s) and the temperature sensor(s) have parallel longitudinal extension directions and the longitudinal extension directions of the first and second stop valves as well as the first and second temperature sensors are perpendicular to the axes longitudinal extensions of the first expansion valve and the second expansion valve,
• at least one stop valve is arranged on a first refrigerant circulation zone of the support and intended for the circulation of the refrigerant fluid at high pressure
• at least one temperature sensor is arranged on a second refrigerant circulation zone of the support and intended for the circulation of the refrigerant fluid at high pressure and/or for the circulation of the refrigerant fluid at low pressure.

Other advantages and characteristics of the present invention will appear more clearly on reading the following description, given by way of illustration and not limitation, and the appended drawings in which:

There is a simplified perspective view of a support for a fluid management module for a vehicle, in particular an automobile according to the invention, support on which the circulation channels have not been represented.

There is a side view of the fluid management module support of the .

There is a simplified top view of a second face of the support for a fluid management module according to the invention; the second face presenting the circulation channels and part of the elements arranged on this second face.

There is a simplified perspective view of the second face of the support for a fluid management module according to the invention; the second face presenting the circulation channels and part of the elements arranged on this second face.

There is a simplified top view of a part of the second face of the support for a fluid management module according to the invention; in particular a first zone for circulation of the refrigerant fluid and intended for the circulation of the refrigerant fluid at high pressure, this first zone presenting the circulation channels and part of the elements arranged in this first zone.

There is a bottom view of a first face of the support for a fluid management module according to the invention.

There is a top view of the second face of the support for a fluid management module according to the invention.

There is a simplified side view of the second face of the support for a fluid management module according to the invention, the second face presenting the circulation channels and part of the elements arranged on this second face.

The invention relates to a support 10 for a fluid management module for a vehicle, in particular a motor vehicle, said support 10 comprising at least two channels 60 and 64 for the circuit of a refrigerant fluid characterized in that the support 10 is formed of at least a first circulation zone 12 of the refrigerant fluid and intended for the circulation of the refrigerant fluid at high pressure and of a second circulation zone 14 of the refrigerant fluid and intended at least for the circulation of the refrigerant fluid at low pressure .

The refrigerant fluid used by the refrigerant circuit is here a chemical fluid such as R1234yf. Other refrigerant fluids could be used, such as R134a or R290.

By “high pressure refrigerant fluid” is meant a refrigerant fluid at a pressure of around 20 bars, by “low pressure refrigerant fluid” at a pressure of 3 bars.

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 and intended for the circulation of the refrigerant fluid at high pressure and of a second zone of circulation 14 of the refrigerant fluid and intended at least for the circulation of the refrigerant fluid at high pressure and/or low pressure.

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

In other words, the support 10 is a refrigerant circulation unit.

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

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

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

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.

A particular and not illustrated embodiment proposes that the support 10 comprises at least a first plate, called a transfer plate, shaped to form at least one channel or an undulation for the circulation of the fluid. In other words, the curvatures of the transfer plate constitute passages which form the channels.

Still in this particular and not illustrated embodiment, the support 10 comprises at least a second plate called support plate. The support plate is configured to provide the interface between the support 10 and elements secured on the support 10.

The support plate may be flat to be in contact with part of the elements secured on the support 10.

In other words, in this embodiment, the flat support plate partly defines the conduits for the refrigerant fluid.

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

In the embodiment illustrated in , the support 10 comprises at least a first channel 60 intended for the circulation of the refrigerant fluid at high pressure.

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

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 refrigerant fluid at high pressure.

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 refrigerant fluid to high pressure.

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

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

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

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

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

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

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 refrigerant fluid at high pressure (here the second branch 60-2).

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

As indicated above, the first channel 60 is intended for the circulation of the refrigerant fluid at high pressure.

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) ramifications.

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

According to this embodiment, the third heat exchanger 52 is of the water condenser type. This exchanger is configured to carry out a heat exchange between the high pressure refrigerant fluid and a heat transfer liquid.

The second branch 60-3 is intended to ensure communication between the main branch 60-1 and a second flange 102, fluidly connected to an internal condenser, not shown here. This internal condenser is a thermal regulation device for the passenger compartment of the vehicle, placed for example in the passenger compartment of said vehicle. Said internal condenser is intended to heat a flow of air passing through it.

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

In the particular embodiment illustrated in , the support 10 comprises four second channels 62-1, 62-2, 62-3, 62-4 intended for the circulation of the refrigerant fluid at high pressure.

In this same embodiment, one of the second channels, hereinafter referenced 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.

According to this embodiment, the bottle 56 is a desiccant bottle, configured to contain the refrigerant fluid at high pressure and capture the humidity of the refrigerant fluid passing through it.

According to another embodiment, not shown, the bottle 56 can be an accumulator. According to this other embodiment, the bottle 56, or accumulator, would be placed on a low pressure portion of the circuit.

According to the embodiment illustrated in , the first heat exchanger 54 is an internal heat exchanger, said internal heat exchanger making it possible to carry out a transfer of calories between a low pressure portion of the refrigerant circuit and a high pressure portion of said refrigerant circuit. Such an exchange of calories makes it possible to optimize the thermodynamic properties of the refrigerant circuit.

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

Still in this same embodiment illustrated here, one of the second channels, hereinafter referenced 62-3, is intended to ensure communication between the first heat exchanger 54 and a valve, preferably an expansion valve. In the remainder of the description, this expansion valve will be called second expansion valve 28.

Still in this same embodiment illustrated here, one of the second channels hereinafter referenced 62-4 is intended to ensure communication between the first heat exchanger 54 and another valve, preferably an expansion valve. In the remainder of the description, this expansion valve will be called first expansion valve 26.

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

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

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

In this same embodiment, one of the third channels, hereinafter referenced 64-1, is intended to ensure communication between a fifth flange 105, fluidly connected to an evaporator, not shown, and to the first heat exchanger 54. This evaporator is a thermal regulation device for the passenger compartment of the vehicle, placed for example in the passenger compartment of said vehicle. Said evaporator is intended to cool a flow of air passing through it.

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

In this same embodiment, one of the third channels, hereinafter referenced 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.

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

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

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

The two expansion valves 26, 28 make it possible to control the supply of refrigerant fluid 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 fluid.

According to one embodiment, the first (54), second (50) and third (52) heat exchangers are fluidly connected to the first, second and third channels 60, 62, 64, via flanges. More precisely, the first heat exchanger 54 is connected by means of an eighth, ninth, tenth and eleventh flanges, respectively to the second channel 62-1, to the second channels 62-3 and 62-4, to the third channel 64-2 and to the third channels 64-1 and 64-3, the second heat exchanger 50 is connected by means of a twelfth and thirteenth flanges, respectively to the third channel 64-3 and to 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.

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

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

The first circulation zone 12 can be thermally isolated from the second circulation zone 14.

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.

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.

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.

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.

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

The support 10 further comprises a first opening 24 capable of receiving at least in part an expansion valve 26.

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.

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

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.

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

The support 10 comprises a second opening 33 extending at least over the third zone 18 capable of receiving at least partly the compressor 20.

This second opening 22 can be seen as a cutout making it possible to lighten the support 10 and making it possible to define two fixing lugs for the compressor 20.

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

In other words, this first opening 24 makes it possible to accommodate at least part of the body of the expansion valve 26.

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

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

The first opening 24 includes a step 32 defining a first bearing 32-1 and a second bearing 32-2.

The first opening 24 is capable of receiving at least in part a first 26 and a second 28 expansion valve.

Each of the first and second bearings 32-1 and 32-2 is capable of receiving a first or a second expansion valve 26 and 28.

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

Here, the first insertion block 34 is machined so as 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, thus making the more compact module.

An embodiment illustrated in proposes that the first insertion block 34 is also machined so as to accommodate a second temperature sensor 76.

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

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.

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

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

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

In other words, this first opening 24 makes it possible to accommodate at least partly the body of the second expansion valve 28.

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

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

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, thus making the module more compact.

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.

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

The support 10 comprises a third zone 18 capable of receiving at least in part a compressor 20, the third zone 18 being distinct from the first circulation zone 12 of the refrigerant fluid and from the second circulation zone 14 of the refrigerant fluid.

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

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

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

The fluid management module for a vehicle, particularly an automobile, includes:

• 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 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.

Such a configuration saves space by arranging different elements of the fluid management module on both sides of the support 10 in an optimized manner.

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 heat exchanger 54 of the internal exchanger type allows a heat exchange between the refrigerant fluid circulating at high pressure and the refrigerant fluid circulating at low pressure.

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

In the embodiment illustrated here, the second heat exchanger 50 is a water cooler type exchanger. The second heat exchanger 50 of the water cooler type allows a heat exchange between the refrigerant fluid and a heat transfer liquid, in particular, here, brine.

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

In the embodiment illustrated here, the third heat exchanger 52 is a water condenser type exchanger (or “WCDS” for “Water Condenser” in its English name). The third heat exchanger 52 of the water condenser type also allows a heat exchange between the refrigerant fluid and a heat transfer liquid, in particular, here, glycol water.

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

This has the technical effect of improving the efficiency of heat exchange through the module by participating in the creation of a thermal gradient. Indeed, the third heat exchanger 52 of the water condenser type circulates a refrigerant fluid hotter than that circulating in the second heat exchanger 50 of the water cooler type.

The first heat exchanger 54 of the internal exchanger type is arranged at a distance from the third heat exchanger 52 of the water condenser type so that the latter does not transmit heat to the first heat exchanger 54 of the internal exchanger type.

More precisely, 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.

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 defining a direction of longitudinal extension respectively L1, L2 and L3. The longitudinal extension directions L2 and L3 of the second heat exchanger 50 and the third heat exchanger 52 are parallel. The direction of longitudinal extension L1 of the first heat exchanger 54 is perpendicular to the directions of longitudinal extension L2 and L3 of the second heat exchanger 50 and the third heat exchanger 52.

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

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

In the embodiment illustrated here, it will be noted that the first expansion valve 26 is arranged near the second heat exchanger 50 of the water cooler type.

As indicated above, the first expansion valve 26 comprises a longitudinal extension axis. The axis of longitudinal extension of the first expansion valve 26 is parallel to the plane P1 of the first circulation zone 12 of the refrigerant fluid.

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

This arrangement also leads to improving the compactness of the fluid management module.

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.

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. pressure.

The second face 42 of the support 10 further comprises a compressor 20.

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

It is also possible to provide vibration absorption devices arranged between the support 10 and the compressor 20.

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

The second face 42 of the support 10 further comprises a bottle 56.

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

The bottle 56 is a desiccant bottle, with the function of separating the liquid refrigerant fluid and the gaseous refrigerant fluid, at high pressure, to allow storage and to capture the humidity of the refrigerant fluid passing through it.

According to another embodiment, the bottle 56 could be an accumulator. According to this other embodiment, the bottle 56, or accumulator, would be placed on a low pressure portion of the circuit.

Bottle 56 could be fitted with a refrigerant charging valve.

The compressor 20 and the bottle 56 each have a direction of longitudinal extension L4 and L5 respectively. The directions of longitudinal extension L4 of the compressor are perpendicular to the direction of longitudinal extension L5 of the bottle 56.

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

These arrangements of the compressor 20 and the bottle 56 make it possible to improve the compactness of the fluid management module.

The second face 42 of the support 10 comprises at least one valve 73-2 or 72-3.

In the embodiment illustrated in , two valves are provided, here stop valves 72-1 and 72-2. In particular, these stop valves 72-2 and 72-3 are provided arranged on valve support blocks 70-2 and 70-3 (not visible at the ).

The second face 42 of the support 10 comprises at least one temperature sensor 74 or 76.

In the embodiment illustrated in , a first temperature sensor 74 is arranged near at least one stop valve 72-2 or 72-4.

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

More particularly, the second temperature sensor 76 is inserted into the first insertion block 34 for the first expansion valve 26.

In other words, the first insertion block 34 for the first expansion valve 26 also integrates the temperature sensor function. To do this, a particular embodiment proposes that the first insertion block 34 for the first expansion valve 26 be machined so as to receive the second temperature sensor 76.

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

The stop valve 72-2 or 72-3 and the temperature sensor 74 or 76 have parallel longitudinal extension directions.

In this embodiment illustrated in particular in , the directions of longitudinal extensions 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 direction X.

It will be noted that in this particular embodiment, the directions of longitudinal extensions 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 perpendicular to the axes of extension. longitudinal sections of the first expansion valve 26 and the second expansion valve 28.

At least one stop valve 72-2 or 72-3 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

At least one temperature sensor 76 is 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.

The invention is not limited to the embodiments presented and other embodiments will be clearly apparent to those skilled in the art. In particular, it is possible to use any other fixing means as long as they are reversible fixing means.

Claims (12)

Support (10) for a fluid management module for a vehicle, in particular a motor vehicle, said support (10) comprising at least two channels (60) and (64) for the circuit of a refrigerant fluid characterized in that the support (10) is formed of at least a first circulation zone (12) of the refrigerant fluid and intended for the circulation of the refrigerant fluid at high pressure and of a second circulation zone (14) of the refrigerant fluid and intended at least to the circulation of the refrigerant fluid at low pressure. Support (10) according to claim 1 in which the first circulation zone (12) is distinct from the second circulation zone (14) of the refrigerant fluid. Support (10) according to claim 1 or 2:

• in which the first circulation zone (12) of the refrigerant fluid extends substantially along a first plane (P1) and the second circulation zone (14) of the refrigerant fluid extends substantially along a second plane (P2) and
• in which the first plane (P1) of the first circulation zone (12) of the refrigerant fluid and the second plane (P2) of the second circulation zone (14) of the refrigerant fluid are different.

Support (10) according to the preceding claim in which 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). Support (10) according to one of the preceding claims comprising a third zone (18) capable of receiving at least in part a compressor (20), the third zone (18) being distinct from the first circulation zone (12) of the fluid refrigerant and the second circulation zone (14) of the refrigerant fluid. Support (10) according to the preceding claim in which 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 of the second plane (P2) of the second circulation zone (14) of the refrigerant fluid. Support (10) according to the preceding claim in which the third zone (18) and the second circulation zone (14) of the refrigerant fluid are connected by a second common edge (22). Support (10) according to the preceding claim further comprising a first opening (24) capable of receiving at least in part an expansion valve (26). Support (10) according to one of the preceding claims in which the first edge (16) extends along the first opening (24). Support (10) according to one of the preceding claims comprising a second opening (32) extending at least over the third zone (18) capable of receiving at least partly the compressor (20). Support (10 according to the preceding claim in which the second opening (32) also extends on the common edge (22) of the third zone (18) and the second circulation zone (14) of the refrigerant fluid. Fluid management module comprising a support according to one of the preceding claims.