FR3135422A1 - Thermal conditioning system comprising a fluid management module for a vehicle, particularly an automobile - Google Patents

Abstract

The invention relates to a thermal conditioning system (1) for heating and/or cooling electrical and/or electronic elements of an electric or hybrid motor vehicle, and comprising: a heat transfer liquid circuit, a refrigerant fluid circuit ( 2) comprising: a condenser (52), a compressor (20), a first evaporator (48) for cooling the passenger compartment of the vehicle, a second evaporator (50) for cooling the electrical and/or electronic elements, a management module fluids characterized in that the fluid management module comprises: a support (10) having a first face (40) and a second face (42), at least one channel (60, 62, 64) for the fluid circuit refrigerant (2), the first face (40) of the support (10) supporting at least the second evaporator (50) and the second face (42) of the support (10) supporting at least one valve (72-2, 72-3 ). Abstract Figure: Figure 8

Description

Thermal conditioning system comprising a fluid management module for a vehicle, particularly an automobile

The present invention relates to the field of thermal conditioning systems. These systems can in particular equip a motor vehicle. Such systems make it possible to achieve thermal regulation of different components of the vehicle, such as for example the passenger compartment or an electrical energy storage battery, in the case of an electrically powered vehicle. Heat exchanges are managed mainly by the compression and expansion of a refrigerant fluid within different heat exchangers making it possible to ensure heating or cooling of different organs.

Thermal conditioning systems commonly use a refrigerant loop and a heat transfer liquid loop exchanging heat with the refrigerant. Such systems are thus called indirect. The refrigerant loop is formed such that the refrigerant transfers heat to a heat transfer liquid in a first heat exchanger. The heat given up to the heat transfer liquid can then be dissipated in a flow of air intended for the passenger compartment in order to heat it. The heat transfer liquid circuit also makes it possible to cool heat-dissipating elements of the vehicle's traction chain, such as the vehicle's electric traction motor or the power electronics controlling the electric motor. For this, another heat exchanger makes it possible to carry out a heat exchange between the heat transfer liquid and the refrigerant fluid in order to cool the heat transfer liquid.

There is thus a need to be able to have thermal conditioning systems that can offer different modes of cooling and/or heating the battery or different elements of the vehicle's traction chain, in particular without using a circulation of refrigerant fluid. under pressure.

Thermal conditioning systems include thermal management components, such as pumps, valves, heat exchangers, and temperature control components. 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 thermal conditioning 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.

To this end, the present invention proposes a thermal conditioning system for heating and/or cooling electrical and/or electronic elements of an electric or hybrid motor vehicle, and, preferably, the passenger compartment of said vehicle, comprising:

• a heat transfer liquid circuit to heat and/or cool the electrical and/or electronic elements, and, preferably, the passenger compartment of the vehicle,
• a refrigerant fluid circuit comprising:
  • a condenser,
  • a compressor,
  • a first evaporator to cool the passenger compartment of the vehicle,
  • a second evaporator for cooling the electrical and/or electronic elements, such that the second evaporator is thermally coupled to the heat transfer liquid circuit,
  • a fluid management module

characterized in that the fluid management module 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 refrigerant circuit
• the first face of the support supporting at least the second evaporator and the second face of the support supporting at least one valve.

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

The thermal conditioning system according to the invention may also comprise at least one of the following characteristics, taken alone or in combination:

According to one aspect of the invention, the first face of the support supports the second evaporator.

According to one aspect of the invention, the second evaporator is a water cooler type exchanger. The second water cooler type evaporator allows a heat exchange between the refrigerant fluid and a heat transfer liquid, in particular, here, brine.

According to one aspect of the invention, the first face of the support supports the condenser.

According to one aspect of the invention, the condenser is a water condenser type exchanger (or “WCDS” for “Water Condenser” in its English name). The water condenser type condenser also allows a heat exchange between the refrigerant fluid and a heat transfer liquid, in particular, here, brine.

According to one aspect of the invention, the first face of the support supports a first heat exchanger.

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

According to one aspect of the invention, the condenser 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, while the second evaporator and the first heat exchanger are 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.

According to one aspect of the invention, the first zone of circulation of the refrigerant fluid extends substantially along a first plane and the second zone of circulation of the refrigerant fluid extends substantially along a second plane and in which the first plane of the first refrigerant circulation zone and the second plane of the second refrigerant circulation zone are different.

According to one aspect of the invention, 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.

According to one aspect of the invention, 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 . In this embodiment, 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.

According to one aspect of the invention, the first refrigerant circulation zone and the second refrigerant circulation zone are connected by a first common edge.

According to one aspect of the invention, the support comprises a first opening extending at least over the third zone capable of receiving at least partly the compressor.

This first opening can be seen as a cutout to lighten the support and to define two fixing brackets for the compressor.

According to one aspect of the invention, the first refrigerant circulation zone and the second refrigerant circulation zone are connected by a common edge.

According to one aspect of the invention, the third zone and the second zone of circulation of the refrigerant fluid are connected by a second common edge.

According to one aspect of the invention, the first opening also extends over the second edge common to the third zone and the second zone of circulation of the refrigerant fluid.

According to one aspect of the invention, the second face of the support further comprises the compressor.

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

According to one aspect of the invention, the second face of the support further comprises a bottle.

In other words, according to this aspect of the invention, the bottle is secured to the second face of the support.

According to one aspect of the invention, the bottle is an accumulator, with the function of separating the liquid refrigerant fluid and the gaseous refrigerant fluid, at low pressure, and of allowing storage.

According to another embodiment, the bottle could be 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 which passes through it . According to this other embodiment, the bottle, or desiccant bottle, would be placed on a high pressure portion of the circuit.

The bottle could be fitted with a refrigerant charging valve.

According to one aspect of the invention, the compressor and the bottle each comprise a direction of longitudinal extension respectively and in which the direction of longitudinal extension of the compressor is perpendicular to the direction of longitudinal extension of the bottle.

The longitudinal extension directions of the compressor and the bottle extend parallel to the first, second and third planes.

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

According to one aspect of the invention, the second face of the support comprises at least one valve.

According to one aspect of the invention, two stop valves are provided. In particular, these stop valves are provided arranged on valve support blocks.

According to one aspect of the invention, the second face of the support comprises at least one temperature sensor.

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

According to one aspect of the invention, 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.

According to one aspect of the invention, the support comprises a second opening, the second opening receiving at least in part a fifteenth flange.

This fifteenth flange ensures fluid communication between the first heat exchanger and the compressor.

According to another aspect of the invention, the fifteenth flange could belong to the support.

The subject of the invention is a thermal conditioning system comprising a fluid management module support as described above.

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.

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

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

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

There is a schematic view of the refrigerant circuit of the operating according to a first mode of operation.

There is a schematic view of the refrigerant circuit of the operating according to a second mode of operation.

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 part of the elements arranged on this second face.

There is a simplified perspective view of the fluid management module support of the .

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.

The invention relates to a thermal conditioning system 1 for heating and/or cooling electrical and/or electronic elements of an electric or hybrid motor vehicle, and, preferably, the passenger compartment of said vehicle, comprising: a heat transfer liquid circuit for heating and/or cooling the electrical and/or electronic elements, and, preferably, the passenger compartment of the vehicle, a refrigerant fluid circuit 2 comprising a condenser 52, a compressor 20, a first evaporator 48 for cooling the passenger compartment of the vehicle, a second evaporator 50 for cooling the electrical and/or electronic elements, such that the second evaporator 50 is thermally coupled to the heat transfer liquid circuit, a fluid management module, characterized in that the fluid management module comprises: 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 refrigerant circuit 2, the first face 40 of the support 10 supporting at least the second evaporator and the second face 42 of the support 10 supporting at least one valve 72-2 or 72-3.

The refrigerant fluid used by the refrigerant circuit 2 is here a chemical fluid such as R1234yf. Other refrigerant fluids could be used, such as R134a or R290.

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

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

In the particular embodiment of the fluid management module of the thermal conditioning system 1 illustrated in particular in Figures 1 to 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 high pressure refrigerant fluid and a second circulation zone 14 of the refrigerant fluid and intended at least for the circulation of the refrigerant fluid at high pressure and/or 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 conditioning system 1 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 the embodiment illustrated here, the support 10 is formed of two plates secured to each other. In such a case, the channels for the circuit of a refrigerating fluid 2 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 2.

According to this embodiment, the plates forming the support 10 each include one or more flat regions 15 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 embodiment illustrated here proposes that the support 10 comprises at least a first plate, called transfer plate 80, 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 80 constitute passages which form the channels.

Still in this particular embodiment, the support 10 comprises at least a second plate called support plate 82. The support plate 82 is configured to provide the interface between the support 10 and elements secured to the support 10.

The support plate 82 may be flat to be in contact with part of the elements secured on the support 10.

In other words, in this embodiment, the support plate 82 partly defines the conduits for the refrigerant fluid.

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 block for distributing the refrigerant fluid 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 condenser 52.

The condenser 52 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 46, not shown here.

This internal condenser 46 is a thermal regulation exchanger for the passenger compartment of the vehicle, placed for example in the passenger compartment of said vehicle. Said internal condenser 46 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 five second channels 62-1, 62-2, 62-3, 62-4 and 62-5 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 the condenser 52 and another heat exchanger, hereinafter referred to as the first heat exchanger 54.

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 2 and a high pressure portion of said refrigerant circuit 2. such heat exchange makes it possible to optimize the thermodynamic properties of the refrigerant circuit 2.

Still in this same embodiment illustrated here, one of the second channels, hereinafter referenced 62-2, is intended to ensure communication between the first heat exchanger 54 and a branch, said branch being divided into one of the second channels, hereinafter referenced 62-3 and another of the second channels, hereinafter referenced 62-4.

The second channel 62-3 is intended to ensure communication between the second channel 62-2 and a valve, preferably an expansion valve. In the remainder of the description, this expansion valve will be called second expansion valve 28.

Still in this same embodiment illustrated here, the second channel 62-4 is intended to ensure communication between the second channel 62-2 and another valve, preferably an expansion valve. In the remainder of the 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 first expansion valve 26 is here directly connected to a third flange 103, itself fluidly connected to a first evaporator 48, not shown.

This first evaporator 48 is a thermal regulation exchanger for the passenger compartment of the vehicle, placed for example in the passenger compartment of said vehicle. Said first evaporator 48 is intended to cool an air flow passing through it.

According to this same embodiment, one of the second channels, hereinafter referenced 62-5, is intended to ensure communication between the second channel 62-2 and a fourth flange 104, fluidly connected to the internal condenser 46.

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 three third channels 64-1, 64-2 and 64-3 intended for the circulation of the refrigerant fluid at low pressure.

According to this same embodiment, one of the third channels, hereinafter referenced 64-1, is intended to ensure communication between the second expansion valve 28 and the second evaporator 50.

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

Still in this same embodiment illustrated here, one of the third channels, hereinafter referenced 64-2, is intended to ensure communication between the second evaporator 50 and a fifth flange 105, fluidly connected to a bottle 56.

According to this embodiment, the bottle 56 is an accumulator, configured to contain the refrigerant fluid at low pressure.

According to this embodiment, the bottle 56 could be provided with a refrigerant charging valve 156.

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

In this same embodiment illustrated here, one of the third channels, hereinafter referenced 64-3, is intended to ensure communication between a sixth flange 106, fluidly connected to the bottle 56, and the first heat exchanger 54.

Furthermore, the support 10 comprises a seventh flange 107, fluidly connected to the first evaporator 48.

The two expansion valves 26, 28 make it possible to control the supply of refrigerant fluid to the first evaporator 48 and the second evaporator 50. Thus, depending on the position of the expansion valves, 26, 28 the first evaporator 48 and/or or the second evaporator 50 can be supplied with refrigerant fluid.

According to one embodiment, the first heat exchanger (54), the second evaporator (50) and the condenser (52) 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 and tenth flanges, respectively to the second channel 62-1, to the second channels 62-2, to the third channel 64-3, the second evaporator 50 is connected by means of an eleventh and twelfth flanges, respectively to the third channel 64-1 and to the third channel 64-2, the condenser 52 is connected by means of a thirteenth flange and a fourteenth flange respectively to the first branch 60 -2 of the first channel 60 and the second channel 62-1.

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 the 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 this embodiment, 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.

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

In this embodiment, 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 zone of circulation 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.

In this embodiment, the third zone 18 and the second circulation zone 14 of the refrigerant fluid are connected by a second common edge 22.

In this embodiment, the support 10 comprises a first opening 32 extending at least over the third zone 18 capable of receiving at least partly the compressor 20.

This first 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.

In this embodiment, the first opening 32 also extends over the second common edge 22 to the third zone 18 and the second circulation zone 14 of the refrigerant fluid.

In the embodiment shown in particular , the support 10 comprises a second opening 24, the second opening 24 receiving at least in part a fifteenth flange 115.

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

According to another aspect of the invention, not shown here, the fifteenth flange 115 could belong to the support 10.

In the embodiment shown in particular and 10, 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.

In the embodiment shown in particular and 10, 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.

According to one embodiment shown , the first heat exchanger 54, the second evaporator 50 and the condenser 52 each have a length and a width, the length of each of the first heat exchanger 54, second evaporator 50 and condenser 52 defining a direction of longitudinal extension respectively L1 , L2 and L3 and in which the directions of longitudinal extension L2 and L3 of the second evaporator 50 and the condenser 52 are parallel and in which 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 evaporator 50 and the condenser 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.

Still according to this embodiment, the condenser 52 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 evaporator 50 and the first heat exchanger 54 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.

According to one embodiment shown , the compressor 20 and the bottle 56 each have a direction of longitudinal extension L4 and L5 respectively and in which the direction of longitudinal extension L4 of the compressor is 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 of the thermal conditioning system 1.

The thermal conditioning system 1 within the refrigerant fluid circuit 2 will now be described in relation to Figures 5 and 6. Furthermore, the refrigerant fluid circuit 2 will be described starting with the compressor 20, but it is understood that this only represents a fictitious starting point of the refrigerant fluid circuit 2 and that said refrigerant fluid circuit 2 forms a closed loop.

A first mode of operation of the refrigerant fluid circuit 2, comprising the thermal conditioning system 1, and making it possible to heat and/or cool electrical and/or electronic elements of an electric or hybrid motor vehicle, and, preferably, the passenger compartment of said vehicle, will now be described in relation to the .

In order to facilitate understanding, it should be considered that only the pipes symbolized in solid lines on the will be described, because they are implemented in the first mode of operation. Furthermore, thicker lines of the pipes or components of the refrigerant circuit 2 make it possible to symbolize the portions of the refrigerant circuit 2 where the refrigerant fluid is at high pressure.

In this first mode of operation, the compressor 20, described previously, makes it possible to compress the refrigerant fluid in order to increase its pressure, and, consequently, its temperature. Thus, we understand that at the outlet of compressor 20, the high pressure refrigerant fluid is in the gaseous state and has a high temperature, that is to say higher than its entry temperature into said compressor 20. The refrigerant fluid leaving the compressor 20 circulates in a first pipe 110a, external to the support 10, then, via the first flange 101, in the main branch 60-1 of the first channel 60 and is directed by means of a first valve. stop 72-2 open towards the first branch 60-2 then towards the condenser pass 17 of the condenser 52. Said condenser 52 then transfers its calories to a first heat transfer fluid 30a of the closed cooling circuit 44. Thus, at the outlet of condenser 52 , the refrigerant fluid is colder than at the inlet and is at least partly in the liquid state.

At the outlet of the condenser 52, the refrigerant fluid is directed, via one of the second channels 62-1, towards the first heat exchanger 54. According to the embodiment illustrated in Figures 5 and 6, the first heat exchanger 54 is a internal heat exchanger. The high pressure refrigerant fluid circulating in the second pass 11b of said first heat exchanger 54 exchanges calories with the low pressure refrigerant fluid from another portion of the refrigerant fluid circuit 2, circulating in the first pass 11a. This transfer makes it possible to improve the thermodynamic performances implemented in the refrigerant circuit 2.

After passing through the first heat exchanger 54 via the second pass 11b, the refrigerant circulates in one of the second channels 62-2 to a branch. The refrigerant fluid then circulates in one of the second channels 62-3 and/or in one of the second channels 62-4 and respectively passes through a second expansion valve 28 and/or a first expansion valve 26 in order to lower its pressure and its evaporation point. We understand that at this stage, we move from the high pressure portion of the refrigerant circuit 2 to the low pressure portion of the latter.

At the outlet of the second expansion valve 28, the refrigerant and low pressure fluid is directed via one of the third channels 64-1 and circulates within the second evaporator 50 via the evaporator pass 13, in order to exchange calories with a second heat transfer liquid 30b intended to cool the electrical and/or electronic elements and passing through said second evaporator 50. More particularly, the second heat transfer liquid 30b passing through the second evaporator 50 is hot at the inlet of the second evaporator 50 and gives up its calories to the refrigerant fluid circulating in the evaporator pass 13, which thus evaporates, the change of state producing the energy necessary for cooling the electrical and/or electronic elements. Thus, we understand that within the second evaporator 50, the refrigerant fluid evaporates under the effect of the capture of calories, the second expansion valve 28 having lowered its evaporation point. We then understand that at the outlet of the second evaporator 50, the refrigerant fluid circulating in one of the third channels 64-2 is mainly in the gaseous state.

At the outlet of the first expansion valve 26, the cold and low-pressure refrigerant fluid is directed, via a third flange 103 then a second pipe 110b, external to the support 10, towards the first evaporator 48 of a thermal regulation device 38 of the passenger compartment of the vehicle, arranged for example in the passenger compartment of said vehicle. More particularly, the thermal regulation device 38 is arranged in the passenger compartment such that it is crossed by an air flow F which is sent into the passenger compartment. Thus, we understand that the air flow F passing through the first evaporator 48 is cooled by the cold refrigerant fluid circulating within the latter, thus making it possible to cool the passenger compartment. The refrigerant fluid passing through the first evaporator 48 is then evaporated by the effect of the captured calories, so that it exits at least partially in the gaseous state in a third pipe 110c, external to the support 10, up to a seventh flange 107 of support 10.

Once passing through the second evaporator 50, the refrigerant fluid coming from one of the third channels 64-2 passes through a fifth flange 105, circulates in a fourth pipe 110d, external to the support 10, and passes through the bottle 56, here the accumulator. The refrigerant fluid coming from the first evaporator 48 passes through a seventh flange 107, then circulates in a fifth pipe 110e, external to the support 10, up to the bottle 56. The bottle 56, or accumulator, collects a liquid fraction of the refrigerant fluid in outlet of the second evaporator 50 and/or the first evaporator 48. Such a passage in the bottle 56 is necessary prior to the passage of the refrigerant fluid into the compressor 20 which can only accept the refrigerant fluid in the gaseous state.

At the bottle outlet 56, the refrigerant fluid, in the gaseous state and always at low pressure, is directed, via a sixth pipe 110f, external to the support 10, and a sixth flange 106 towards the first heat exchanger 54 by means of one of the third channels 64-3, in order to carry out the exchange of calories with the refrigerant fluid of the high pressure portion of the refrigerant fluid circuit 2 via the first pass 11a, as described previously. Subsequently, the refrigerant fluid is directed towards the compressor 20 via a fifteenth flange 115 and a seventh pipe 110g, external to the support 10, so that the latter increases its pressure and its temperature as described previously. According to the embodiment illustrated in Figures 5 and 6, the fifteenth flange 115 is directly integrated into the first exchanger 54. According to another embodiment, not illustrated, this fifteenth flange 115 could belong to the support 10. It is understood that thus, in compressor outlet 20, we switch again to the high pressure portion of the refrigerant fluid circuit 2 and a new thermodynamic cycle can take place.

A second mode of operation of the refrigerant circuit 2 comprising the thermal conditioning system 1, and making it possible to heat and/or cool electrical and/or electronic elements of an electric or hybrid motor vehicle, and, preferably, the passenger compartment of said vehicle, will now be described in relation to the .

In order to facilitate understanding, it should be considered that only the pipes symbolized in solid lines on the will be described, because they are implemented in the second mode of operation. Furthermore, thicker lines of the pipes make it possible to symbolize the portions of the refrigerant circuit 2 where the refrigerant is at high pressure.

In the same way as for the first mode of operation, at the outlet of compressor 20 in the first pipe 110a, external to the support 10, the refrigerant fluid has a high pressure, a high temperature and is in the gaseous state. The refrigerant fluid is then directed, by closing the first valve 72-2 and opening the second valve 72-3, via a first flange 101, a main branch 60-1, a second branch 60-3, a second flange 102 and an eighth pipe 110h, to an internal condenser 46 of the thermal regulation device 38 of the passenger compartment, in order to heat the air flow F, here cold, passing through at least said internal condenser 46. Thus, we understand that at the outlet of the internal condenser 46 of the thermal regulation device 38 of the passenger compartment, the refrigerant fluid is at least partially condensed, the latter having given up at least partly its calories to the flow of cold air F in order to heat it and therefore heat the passenger compartment. Subsequently, the refrigerant fluid leaves the internal condenser 46 via a ninth line 110i.

The refrigerant fluid leaving the internal condenser 46 of the thermal regulation device 38 of the passenger compartment then joins one of the second channels 62-5 via the fourth flange 104. The refrigerant fluid circulates in one of the second channels 62-5 then in the second channel 62-2 and passes through the second expansion valve 28 in order to lower its pressure and its evaporation point. We understand that at this stage, we move from the high pressure portion of the refrigerant circuit 2 to the low pressure portion of the latter.

The refrigerant fluid then passes through one of the third channels 64-1 then the second evaporator 50 via the evaporator pass 13 in order to capture the calories of the second heat transfer liquid 30b intended to cool electrical and/or electronic elements. By capturing the calories of the second heat transfer liquid 30b, the refrigerant fluid evaporates at least partially and continues its path in the refrigerant fluid circuit 2 in a manner identical to what was described previously for the first mode of operation.

According to a third mode of operation, not shown here, the condenser 52 has the function of exchanging calories with the first heat transfer liquid 30a intended, this time, to heat electrical and/or electronic elements of an electric motor vehicle or hybrid. In this mode of operation, the high pressure refrigerant fluid circulates within the condenser 52 via the condenser pass 17, in order to exchange calories with the first heat transfer liquid 30a intended here to heat the electrical and/or electronic elements and passing through said condenser 52. More particularly, the first heat transfer liquid 30a passing through the condenser 52 is cold at the inlet of the condenser 52 and captures calories from the refrigerant fluid circulating in the condenser pass 17, which thus condenses, the change of state producing the energy necessary for heating electrical and/or electronic elements.

According to an example of this mode of operation, on the side of the second evaporator 50, the refrigerant fluid would pass through the evaporator pass 13 in order to capture the calories of the second heat transfer liquid 30b, said second heat transfer liquid 30b circulating in a radiator, not shown, placed for example on the front of the vehicle. The heat transfer liquid 30b would then release the captured calories to the ambient air through said radiator.

Claims (11)

Thermal conditioning system (1) for heating and/or cooling electrical and/or electronic elements of an electric or hybrid motor vehicle, and, preferably, the passenger compartment of said vehicle, comprising:

• a heat transfer liquid circuit for heating and/or cooling the electrical and/or electronic elements, and, preferably, the passenger compartment of the vehicle,
• a refrigerant circuit (2) comprising:
  • a condenser (52),
  • a compressor (20),
  • a first evaporator (48) to cool the passenger compartment of the vehicle,
  • a second evaporator (50) for cooling the electrical and/or electronic elements, such that the second evaporator (50) is thermally coupled to the heat transfer liquid circuit,
  • a fluid management module

characterized in that the fluid management module comprises:

• 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 refrigerant fluid circuit (2),
• the first face (40) of the support (10) supporting at least the second evaporator (50) and the second face (42) of the support (10) supporting at least one valve (72-2, 72-3).

Thermal conditioning system (1) according to the preceding claim in which the first face (40) of the support (10) supports the second evaporator (50). Thermal conditioning system (1) according to the preceding claim in which the first face (40) of the support (10) supports the condenser (52). Thermal conditioning system (1) according to the preceding claim in which the first face (40) of the support (10) supports a first heat exchanger (54). Thermal conditioning system (1) according to the preceding claim in which:

• the condenser (52) 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 evaporator (50) and the first heat exchanger (54) 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 the circulation of the refrigerant fluid at low pressure.

Thermal conditioning system (1) according to the preceding claim 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 . Thermal conditioning system (1) according to any one of claims 5 to 6 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). Thermal conditioning system (1) according to any one of the preceding claims in which the second face (42) of the support (10) further comprises a compressor (20). Thermal conditioning system (1) according to any one of the preceding claims in which the second face (42) of the support (10) further comprises a bottle (56). Thermal conditioning system (1) according to any one of the preceding claims in which the second face (42) of the support (10) comprises at least one temperature sensor (74, 76). Thermal conditioning system (1) according to the preceding claim in which:

• At least one stop valve (72-2, 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 (74, 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.