WO2021204915A1

WO2021204915A1 - Thermal conditioning system for a motor vehicle

Info

Publication number: WO2021204915A1
Application number: PCT/EP2021/059122
Authority: WO
Inventors: Regis Beauvis; Rody El Chammas; Jinming Liu; Muriel Porto; Mohamed Yahia
Original assignee: Valeo Systemes Thermiques
Priority date: 2020-04-08
Filing date: 2021-04-08
Publication date: 2021-10-14

Abstract

The invention relates to a thermal conditioning system (100) for a motor vehicle, comprising: - a coolant circuit (1) comprising: - a main loop (A) successively comprising, in the direction of flow of the coolant: - a compression device (2); - a dual-fluid heat exchanger (3); - a first expansion device (4); - a first heat exchanger (5); - a first bypass branch (B) having a second heat exchanger (7) configured to exchange heat with an external air flow (Fe) outside the passenger compartment of the vehicle; - a second bypass branch (C) connecting a third connection point (13), which is located between an outlet of the compression device (2) and the first expansion device (4) along the main loop (A), to a fourth connection point (14), which is located between the first heat exchanger (5) and the second connection point (12) along the main loop (A), the second bypass branch (C) having a third expansion device (8) and a third heat exchanger (9); - a heat transfer fluid circuit (20), the dual-fluid heat exchanger (3) being arranged both along the coolant circuit (1) and along the heat transfer fluid circuit (20) so as to allow for heat exchange between the coolant and the heat transfer fluid, the main loop (A) comprising a first internal heat exchanger (21) configured to allow for heat exchange between the high-pressure coolant flowing downstream of the dual-fluid heat exchanger (3) and the coolant downstream of the second connection point (12).

Description

MOTOR VEHICLE HEAT CONDITIONING SYSTEM

[1] The present invention relates to the field of thermal conditioning systems for motor vehicles. Such systems allow, for example, thermal regulation of various components of the vehicle, such as the passenger compartment or an electric energy storage battery, in the case of an electrically propelled vehicle. Heat exchanges are managed mainly by the compression and expansion of a refrigerant fluid within several heat exchangers arranged along a closed circuit.

[2] Some thermal conditioning systems use a refrigerant fluid loop and a heat transfer fluid loop exchanging heat with the refrigerant fluid. Such systems are thus called indirect. Application FR3064946 is an example of this. Multiple bypass branches allow many operating modes to be carried out, such as, for example, cooling the air in the passenger compartment, heating the air in the passenger compartment, dehumidifying the air in the passenger compartment, or the cooling of the vehicle batteries.

[3] However, it may be desirable to have other modes of operation as well, such as a mode for recovering thermal energy dissipated by the electric powertrain, also called an electric drive train. It is also advantageous to be able to have a mode of dehumidifying the air in the passenger compartment by using a reduced number of heat exchangers and a reduced number of shut-off valves.

[4] The present invention thus aims to add modes of operation to the systems of the prior art and to reduce the number of components required.

[5] Thus, the invention provides a thermal conditioning system for a motor vehicle, comprising:

- A refrigerant fluid circuit configured to circulate a refrigerant fluid, the refrigerant circuit comprising:

- A main loop comprising successively depending on the direction of travel refrigerant: a compression device, a bifluid heat exchanger, a first expansion device, a first heat exchanger,

- A first branching branch connecting a first connection point disposed on the main loop upstream of the first heat exchanger to a second connection point disposed on the main loop downstream of the first heat exchanger, the first branching branch comprising a second heat exchanger configured to exchange heat with a flow of air outside the vehicle interior,

- A second branch branch connecting a third connection point arranged on the main loop and between an outlet of the compression device and the first expansion device to a fourth connection point arranged on the main loop and between the first heat exchanger heat and the second connection point, the second branch branch comprising a third expansion device and a third heat exchanger,

- A heat transfer fluid circuit configured to circulate a heat transfer fluid, the bifluid heat exchanger being arranged jointly on the refrigerant circuit and on the heat transfer fluid circuit so as to allow heat exchange between the refrigerant fluid and the coolant, the main loop comprising a first internal heat exchanger configured to allow heat exchange between the high pressure refrigerant circulating downstream of the bifluid heat exchanger and the low pressure refrigerant circulating downstream of the second point connection.

[6] According to the invention, the first bypass branch allows the refrigerant circulating in the main loop upstream of the first heat exchanger to join the second heat exchanger without passing through the first heat exchanger. [7] Thanks to this refrigerant circuit architecture, it is thus possible to circulate refrigerant fluid at low pressure in the second heat exchanger, without the refrigerant fluid passing through the first heat exchanger. The thermal conditioning system thus has a new heating method.

[8] According to one embodiment, the main loop also includes a second internal heat exchanger configured to allow heat exchange between the high pressure refrigerant fluid circulating downstream of the first internal exchanger and upstream of the third connection point, and the low pressure refrigerant fluid circulating between the fourth connection point and the second connection point.

[9] The second internal heat exchanger improves the efficiency of the thermal conditioning system, especially during cooling operation phases.

[10] According to one embodiment, the first connection point is between the first expansion device and the first heat exchanger.

[11] According to one embodiment, the first heat exchanger is configured to exchange heat with a flow of air inside a vehicle cabin.

[12] According to this same embodiment, the third heat exchanger is configured to exchange heat with an electric energy storage battery of the vehicle.

[13] A cooling of the battery supplying the electrical energy of an electric traction chain vehicle can thus be ensured. More generally, regulation of the temperature of the battery can thus be achieved.

[14] According to this same embodiment, the third heat exchanger is a bifluid heat exchanger configured to exchange heat with a coolant.

[15] In other words, according to one embodiment of the thermal conditioning system, the first heat exchanger is configured to exchange heat with a flow of air inside a passenger compartment of the vehicle and the third Heat exchanger is a bifluid heat exchanger configured to exchange heat with a coolant and configured to exchange heat with an electrical energy storage battery of the vehicle.

[16] According to another embodiment of the thermal conditioning system, the third heat exchanger is configured to exchange heat with a flow of air inside a vehicle cabin and the first heat exchanger is a heat exchanger. bifluid configured to exchange heat with a heat transfer fluid and configured to exchange heat with an electrical energy storage battery of the vehicle.

[17] According to one embodiment, the first expansion device is a thermostatically controlled expansion valve and the third expansion device is an electronically controlled expansion valve.

[18] According to the invention, the main loop includes a first shut-off valve disposed between the first connection point and the first heat exchanger.

[19] This shut-off valve prevents the passage of refrigerant fluid in the main loop when the valve is closed. The passage of refrigerant is possible when the valve is open.

[20] According to one embodiment of the thermal conditioning system, the first branch branch comprises a second expansion device.

[21] The second expansion device is arranged on the first branch branch between the first connection point and the second heat exchanger.

[22] According to another embodiment, the first bypass branch includes a second shut-off valve.

[23] In this embodiment, the second shut-off valve is disposed on the first bypass branch between the first connection point and the second heat exchanger.

[24] According to one embodiment of the thermal conditioning system, it comprises a third branch branch connecting a fifth connection point arranged on the main loop and between the first expansion device and the first heat exchanger to a sixth connection point disposed on the main loop between the fourth connection point and an inlet of the compression device, the third bypass branch comprising a fourth heat exchanger.

[25] The third bypass branch has a shut-off valve, known as the fourth shut-off valve. The fourth shut-off valve is disposed on the third bypass branch upstream of the fourth heat exchanger.

[26] According to a variant, the sixth connection point is upstream of the second internal heat exchanger.

[27] According to another variant, the sixth connection point is downstream of the second internal heat exchanger and upstream of the first internal heat exchanger.

[28] In an exemplary implementation of this variant, the sixth connection point is between the second internal heat exchanger and the second connection point.

[29] In another example of implementation of this variant, the sixth connection point is between the second connection point and the first internal heat exchanger.

[30] According to yet another variant, the sixth connection point is between the first internal heat exchanger and an inlet of the compression device.

[31] According to another embodiment, the first bypass branch comprises a fourth heat exchanger included between the first connection point and the second heat exchanger.

[32] Preferably, the fourth heat exchanger is disposed between the first connection point and the second shut-off valve.

[33] According to yet another embodiment, the thermal conditioning system comprises a fourth branch branch connecting a seventh connection point arranged on the main loop and included between the fourth heat exchanger and the second shut-off valve at a eighth point connection arranged on the main loop between the fourth connection point and an inlet of the compression device.

[34] The fourth branch branch has a third shut-off valve disposed between the seventh connection point and the eighth connection point.

[35] Preferably, the eighth connection point is between the fourth connection point and the second connection point.

[36] Advantageously, the eighth connection point is between the second internal heat exchanger and the second connection point.

[37] Preferably, the fourth heat exchanger is configured to exchange heat with an element of an electric drivetrain of the vehicle.

[38] By circulating refrigerant fluid at low pressure in the fourth heat exchanger, it is thus possible to recover the thermal energy dissipated by the operation of the element of the electric power train. When the thermal conditioning system operates in this powertrain energy recovery mode, the interior air can be heated while minimizing energy consumption. The driving range of the electric vehicle is thus improved.

[39] According to an exemplary implementation, part of an electric drive train of the vehicle is an electric traction motor.

[40] According to another example of implementation, the element of an electric traction chain of the vehicle is an electronic module for controlling an electric traction motor.

[41] Preferably, the fourth heat exchanger is a bifluid exchanger configured to exchange heat with a coolant.

[42] The heat exchange between the coolant and the element of the electric power train is thus ensured through the coolant.

[43] According to one aspect of the invention, the heat transfer fluid circuit comprises a fifth heat exchanger configured to exchange heat with a flow of air inside a passenger compartment of the vehicle. [44] The fifth heat exchanger can thus heat the passenger compartment of the vehicle, by dissipating heat in the air flow intended to supply the interior of the passenger compartment.

[45] According to one aspect of the invention, the coolant circuit includes a sixth heat exchanger configured to exchange heat with a flow of air outside the vehicle cabin.

[46] The sixth heat exchanger makes it possible to cool the heat transfer fluid in certain operating modes of the thermal conditioning system.

[47] According to one aspect of the invention, the refrigerant circuit comprises a refrigerant accumulator device arranged on the main loop at the outlet of the bifluid exchanger.

[48] This accumulation device allows the amount of fluid circulating in the refrigerant circuit to adjust to the conditions of use.

[49] The invention also relates to a method of operating a thermal conditioning system as described above, in a heating mode in which:

- the refrigerant fluid circulates in the compression device where it passes at high pressure, and circulates successively in the bifluid heat exchanger where it gives up heat to the coolant, in the first internal heat exchanger, in the second heat exchanger internal heat, in the first expansion device where it passes at low pressure, in the first bypass branch, in the second expansion device, in the second heat exchanger where it absorbs heat from the external air flow, in the first internal heat exchanger, then the low pressure refrigerant fluid returns to the compression device.

[50] This mode of circulation of the refrigerant fluid corresponds to the operation in heating mode for a thermal conditioning system according to a first embodiment.

[51] The invention also relates to a method of operating a thermal conditioning system according to another embodiment, in one embodiment. heating in which:

- the refrigerant fluid circulates in the compression device where it passes at high pressure, and circulates successively in the bifluid heat exchanger where it gives up heat to the coolant, in the first internal heat exchanger, in the second heat exchanger internal heat, in the first expansion device where it passes at low pressure, in the first bypass branch, in the second shut-off valve, in the second heat exchanger where it absorbs heat from the external air flow, in the first internal heat exchanger, then the low pressure refrigerant fluid returns to the compression device.

[52] This method of circulating the refrigerant fluid corresponds to the operation in heating mode for a thermal conditioning system according to a second embodiment.

[53] According to one aspect of the operating process, the heat transfer fluid circulates in the bifluid exchanger and then part of the heat transfer fluid circulates in the fifth heat exchanger where it transfers heat to the internal air flow.

[54] In the operating modes in which heating of the air in the passenger compartment is carried out, the heating is provided at least in part by heat exchange between the fifth heat exchanger and the air intended for the passenger compartment . The coolant transfers heat to the coolant, which in turn transfers heat to the air in the passenger compartment.

[55] The invention also relates to a method of operating a thermal conditioning system as described above, in a so-called parallel dehumidification mode, in which the refrigerant fluid circulates in the compression device where it goes to high. pressure, and circulates successively in the bifluid heat exchanger where it transfers heat to the coolant, in the first internal heat exchanger, in the second internal heat exchanger, in the first expansion device where it passes at low pressure , is divided between a first flow circulating in the first bypass branch and a second flow circulating in the main loop, the first flow circulating successively in the second expansion device and in the second heat exchanger where it absorbs heat from the outdoor air flow, the second flow circulates successively in the first heat exchanger where it absorbs heat from the indoor air flow, in the second internal heat exchanger , the first flow of low pressure refrigerant fluid and the second flow of low pressure refrigerant meet at the second connection point, the low pressure refrigerant then circulates in the first internal heat exchanger and returns to the compression device.

[56] This mode of circulation of the refrigerant fluid corresponds to the operation in parallel dehumidification mode for a thermal conditioning system according to the first embodiment, in which the first heat exchanger performs in exchange with the flow of air inside the passenger compartment. . In this operating mode, the low-pressure refrigerant fluid passes in parallel through the first heat exchanger and into the second heat exchanger. The air intended for the passenger compartment is thus cooled by passing through the first heat exchanger, then heated by passing through the fifth heat exchanger which receives the heat taken from the flow of outside air. The air is thus dehumidified.

[57] The invention also relates to a method of operating a thermal conditioning system according to another embodiment, in a so-called parallel dehumidification mode, in which the refrigerant fluid circulates in the compression device where it passes. at high pressure, and circulates successively in the bifluid heat exchanger where it transfers heat to the coolant, in the first internal heat exchanger, in the second internal heat exchanger, in the first expansion device where it passes to low pressure, is divided between a first flow circulating in the first bypass branch and a second flow circulating in the main loop, the first flow circulating successively in the second shut-off valve and in the second heat exchanger where it absorbs heat from the external air flow, the second flow circulates successively in the first heat exchanger where it absorbs heat from the internal air flow laughing, in the second interchange of internal heat, the first flow of low pressure refrigerant fluid and the second flow of low pressure refrigerant meet at the second connection point, the low pressure refrigerant then circulates through the first internal heat exchanger and returns to the control device. compression.

[58] This mode of circulation of the refrigerant fluid corresponds to the operation in parallel dehumidification mode for a thermal conditioning system according to the second embodiment.

[59] The invention also relates to a method of operating a thermal conditioning system as described above, in a so-called energy recovery mode, in which the refrigerant fluid circulates in the compression device where it passes. at high pressure, and circulates successively in the bifluid heat exchanger where it transfers heat to the coolant, in the first internal heat exchanger, the second internal heat exchanger, the first expansion device where it passes at low pressure , in the third branch branch, the fourth heat exchanger where the low pressure refrigerant absorbs heat, joins the main loop at the sixth connection point, the low pressure refrigerant then circulates in the first internal heat exchanger and returns to the compression device.

[60] This refrigerant circulation mode corresponds to the operation in energy recovery mode for a thermal conditioning system according to a third embodiment.

[61] The invention also relates to a method of operating a thermal conditioning system as described above, in a so-called energy recovery and heat pump mode, in which the refrigerant fluid circulates in the control device. compression where it passes to high pressure, and circulates successively in the bifluid heat exchanger where it transfers heat to the coolant, in the first internal heat exchanger, the second internal heat exchanger, the first expansion device where it passes at low pressure, is divided between a first flow circulating in the third bypass branch and a second flow circulating in the first bypass branch, - the first flow circulates in the fourth heat exchanger where the low-pressure refrigerant fluid absorbs heat then joins the main loop at the sixth connection point,

- the second flow circulates successively in the first shut-off valve and in the second heat exchanger where it absorbs heat from the flow of outside air, the first flow of refrigerant fluid at low pressure and the second flow of refrigerant fluid at low pressure meet at the second connection point, the low pressure refrigerant then circulates through the first internal heat exchanger and returns to the compression device.

[62] This refrigerant circulation mode corresponds to the operation in energy recovery and heat pump mode for a thermal conditioning system according to the third embodiment. In this operating mode, the low-pressure refrigerant fluid recovers the heat dissipated by the electric traction chain in the fourth heat exchanger. Energy consumption for heating the passenger compartment is thus minimized, since the heat lost for the operation of the powertrain is recovered.

[63] The invention also relates to a method of operating a thermal conditioning system as described above, in a so-called energy recovery and heat pump mode, in which the refrigerant fluid circulates in the control device. compression where it passes to high pressure, and circulates successively in the bifluid heat exchanger where it transfers heat to the coolant, in the first internal heat exchanger, the second internal heat exchanger, the first expansion device where it passes at low pressure, in the first bypass branch, the fourth heat exchanger where the low pressure refrigerant absorbs heat, the second heat exchanger where the low pressure refrigerant absorbs heat from the air flow outside, joins the main loop at the second connection point, the low pressure refrigerant then circulates in the first internal heat exchanger and returns to the compression device. [64] This mode of circulation of the refrigerant fluid corresponds to the operation in energy recovery and heat pump mode for a thermal conditioning system according to a fourth embodiment.

[65] The invention also relates to a method of operating a thermal conditioning system as described above, in a mode called energy recovery and parallel dehumidification, in which the refrigerant fluid circulates in the compression device. where it passes at high pressure, and circulates successively in the bifluid heat exchanger where it transfers heat to the coolant, in the first internal heat exchanger, the second internal heat exchanger, the first expansion device where it passes at low pressure, is divided between a first flow circulating in the first bypass branch and a second flow circulating in the main loop, the first flow circulating successively in the fourth heat exchanger where the refrigerant at low pressure absorbs heat, the second heat exchanger where the low pressure refrigerant fluid absorbs heat from the outside air flow, the second die bit circulates successively in the first heat exchanger where it absorbs heat from the internal air flow, in the second internal heat exchanger, the first flow and the second low pressure refrigerant flow meet at the second connection point , the refrigerant then circulates in the first internal heat exchanger and returns to the compression device.

[66] In this operating mode, the low-pressure refrigerant fluid passes in parallel in the first heat exchanger and in the fourth heat exchanger. The air intended for the passenger compartment is cooled by the first heat exchanger and heated by the fifth heat exchanger, which corresponds to dehumidification. At the same time, thermal energy is recovered from the traction chain and also from the flow of outside air. This mode makes it possible to avoid misting the passenger compartment by optimizing the energy expenditure of the system and without risking icing the second heat exchanger. [67] This mode of circulation of the refrigerant fluid corresponds to the operation in energy recovery and parallel dehumidification mode for a thermal conditioning system according to the fourth embodiment.

[68] The invention finally relates to a method of operating a thermal conditioning system as described above, in a so-called energy recovery and heat pump mode, in which the refrigerant fluid circulates in the control device. compression where it passes to high pressure, and circulates successively in the bifluid heat exchanger where it transfers heat to the coolant, in the first internal heat exchanger, the second internal heat exchanger, the first expansion device where it passes at low pressure, in the first bypass branch, the fourth heat exchanger where the refrigerant at low pressure absorbs heat, is divided between a first flow circulating in the first bypass branch and a second flow circulating in the fourth bypass branch, the first flow circulates in the second heat exchanger where the low pressure refrigerant fluid absorbs heat from the air flow r outside, the second flow circulates in the fourth bypass branch, the first flow and the second flow meet at the second connection point, the low pressure refrigerant then circulates in the first internal heat exchanger and returns to the compression device .

[69] This refrigerant circulation mode corresponds to the operation in energy recovery and heat pump mode for a thermal conditioning system according to a fifth embodiment. The heat transfer fluid can be heated by recovering heat from the drivetrain and simultaneously from the outside air flow.

[70] Other characteristics and advantages of the invention will become apparent on reading the detailed description of the embodiments given by way of non-limiting examples, accompanied by the figures below:

[71] - Figure 1 shows a schematic view of a thermal conditioning system according to a first embodiment of the invention, [72] - Figure 2 shows a schematic view of a thermal conditioning system according to a second embodiment of the invention,

[73] - Figure 3 shows a schematic view of a thermal conditioning system according to a third embodiment of the invention,

[74] - Figure 4 shows a schematic view of a thermal conditioning system according to a fourth embodiment of the invention,

[75] - Figure 5 shows a schematic view of a thermal conditioning system according to a fifth embodiment of the invention,

[76] - Figure 6 shows a schematic view of the thermal conditioning system of Figure 1 according to a first mode of operation, called heating, [77] - Figure 7 shows a schematic view of the thermal conditioning system of Figure 1 according to a second operating mode called parallel dehumidification,

[78] - Figure 8 shows a schematic view of the thermal conditioning system of Figure 2 according to the first operating mode called heating,

[79] - Figure 9 shows a schematic view of the thermal conditioning system of Figure 2 according to the second operating mode called parallel dehumidification,

[80] - Figure 10 shows a schematic view of the thermal conditioning system of Figure 3 according to a third operating mode called energy recovery,

[81] - Figure 11 shows a schematic view of the thermal conditioning system of Figure 3 according to a fourth operating mode, called energy recovery and heat pump, [82] - Figure 12 shows a schematic view of the thermal conditioning system of Figure 4 according to the fourth operating mode, called energy recovery and heat pump,

[83] - Figure 13 shows a schematic view of the thermal conditioning system of Figure 4 according to a fifth operating mode, called energy recovery and parallel dehumidification,

[84] - Figure 14 shows a schematic view of the thermal conditioning system of Figure 5 according to the fourth mode of operation, called energy recovery and heat pump.

[85] - Figure 15 shows a schematic view of the thermal conditioning system of Figure 5 according to the third mode of operation, called energy recovery.

[86] In order to make the figures easier to read, the different elements are not necessarily shown to scale. In these figures, identical elements bear the same references. Certain elements or parameters can be indexed, that is to say designated for example by first element or second element, or even first parameter and second parameter, etc. The purpose of this indexing is to differentiate elements or parameters that are similar, but not identical. This indexing does not imply a priority of one element, or parameter over another, and the names can be interchanged.

In the following description, the term "a first element upstream of a second element" means that the first element is placed before the second element with respect to the direction of flow of a fluid. Similarly, the term "a first element downstream of a second element" means that the first element is placed after the second element with respect to the direction of flow of the fluid considered.

[87] In particular, FIG. 1 shows a thermal conditioning system 100 for a motor vehicle, comprising a refrigerant fluid circuit 1 configured to circulate a refrigerant fluid.

[88] In other words, in normal operation of the thermal conditioning system 100, a refrigerant fluid circulates at least in a part of the circuit 1 of the refrigerant fluid. The thermal conditioning system 100 makes it possible to regulate the temperature as well as the humidity level of the air present in the vehicle interior, in order to ensure passenger comfort. It also makes it possible to cool one or more components of an electric traction chain of the vehicle, such as for example a battery comprising a set of cells for storing electrical energy. The refrigerant fluid used by the refrigerant fluid circuit 1 is here a chemical fluid such as R1234yf. Other refrigerant fluids could be used, such as for example R134a.

[89] The refrigerant fluid circuit 100 comprises a main loop A comprising successively according to the direction of travel of the refrigerant fluid: a compression device 2, a bifluid heat exchanger 3, a first expansion device 4, a first heat exchanger 5.

The refrigerant fluid circuit 100 comprises a first bypass branch B connecting a first connection point 11 arranged on the main loop A upstream of the first heat exchanger 5 to a second connection point 12 arranged on the main loop A downstream of the first heat exchanger 5, the first bypass branch B comprising a second heat exchanger 7 configured to exchange heat with a flow of air Fe outside the vehicle interior.

The refrigerant fluid circuit 100 comprises a second bypass branch C connecting a third connection point 13 arranged on the main loop A and included between an outlet of the compression device 2 and the first expansion device 4 to a fourth connection point 14 arranged on the main loop A and included between the first heat exchanger 5 and the second connection point 12, the second bypass branch C comprising a third expansion device 8 and a third heat exchanger 9.

The thermal conditioning system 100 includes a heat transfer fluid circuit 20 configured to circulate a heat transfer fluid.

The bifluid heat exchanger 3 is arranged jointly on the refrigerant circuit 1 and on the heat transfer fluid circuit 20 so as to allow a heat exchange between the refrigerant fluid and the heat transfer fluid.

The main loop A comprises a first internal heat exchanger 21 configured to allow heat exchange between the high pressure refrigerant circulating downstream of the bifluid heat exchanger 3 and the low pressure refrigerant circulating downstream of the second point connection 12.

[90] In other words, the first bypass branch B allows the refrigerant circulating in the main loop A upstream of the first heat exchanger 5 to join the second heat exchanger 7 without passing through the first heat exchanger 5.

[91] Thanks to this refrigerant circuit architecture, it is thus possible to circulate refrigerant fluid at low pressure in the second heat exchanger, without the refrigerant fluid passing through the first heat exchanger. The thermal conditioning system thus has a new heating mode compared to the systems of the prior art.

[92] According to one embodiment, the main loop A also comprises a second internal heat exchanger 22 configured to allow heat exchange between the high pressure refrigerant fluid circulating downstream of the first internal exchanger 21 and upstream of the third point connection 13, and the low-pressure refrigerant circulating between the fourth connection point 14 and the second connection point 12.

[93] The second internal heat exchanger improves the efficiency of the thermal conditioning system, especially during the operating phases of the system in cooling mode.

[94] In the example illustrated, the first connection point 11 is between the first expansion device 4 and the first heat exchanger 5.

[95] According to one embodiment, and as shown in the examples of the figures, the first heat exchanger 5 is configured to exchange heat with an internal air flow Fi to a vehicle cabin.

[96] The term internal air flow Fi is understood to mean an air flow intended for the passenger compartment of the motor vehicle. This indoor air flow can circulate in an installation of heating, ventilation and air conditioning, often referred to by the English term "HVAC" meaning "Heating, Ventilating and Air Conditioning". This installation has not been shown in the figures. The term “external air flow Fe” is understood to mean an air flow which is not intended for the passenger compartment. In other words, this air flow Fe remains outside the vehicle. The second heat exchanger 7 can be placed on the front face of the vehicle, and receives the air flow generated by the advancement of the vehicle. A motor-fan unit, not shown, can be activated in order to increase, if necessary, the flow rate of the external air flow Fe. Likewise, another motor-fan group, not shown in the figures, is placed in the installation. of heating, ventilation and air conditioning in order to increase, if necessary, the flow rate of the internal air flow Fi.

[97] The first heat exchanger 5 is also called a passenger compartment evaporator, and the second heat exchanger 7 is also called an evapo-condenser.

The first expansion device 4 is arranged upstream of the first heat exchanger 5. The second expansion device 6, when present, is arranged upstream of the second heat exchanger 7. Each of the expansion devices thus makes it possible to control the pressure of the refrigerant fluid passing through the corresponding heat exchanger, and therefore to manage the associated heat exchange.

[98] An electronic control unit, not shown in the figures, receives information from various sensors measuring in particular the characteristics of the refrigerant fluid at various points in the circuit. The electronic unit also receives the instructions requested by the occupants of the vehicle, such as the desired temperature inside the passenger compartment. The electronic unit implements control laws allowing the control of the various actuators, in order to control the thermal conditioning system 1.

[99] The compression device can be an electric compressor, that is to say a compressor whose moving parts are driven by an electric motor. The compression device comprises a suction side of the low-pressure refrigerant fluid, also called the inlet of the compression device, and a delivery side of the high-pressure refrigerant fluid, also called the outlet of the compression device. The internal moving parts of the compressor change the refrigerant from a low pressure on the inlet side to a high pressure. pressure on the outlet side. After expansion in one or more expansion members of the circuit, the refrigerant returns to the compressor inlet and begins a new cycle.

[100] Each internal heat exchanger 21, 22 has a high pressure refrigerant fluid inlet, a high pressure coolant outlet, a low pressure coolant inlet, a low pressure coolant outlet. Within each internal heat exchanger 21, 22, the high pressure and high temperature refrigerant fluid transfers heat to the low pressure refrigerant fluid.

[101] According to this same embodiment, the third heat exchanger 9 is configured to exchange heat with an electric energy storage battery 25 of the vehicle.

[102] A cooling of the battery supplying the electrical energy of an electric traction chain vehicle can thus be ensured. More generally, regulation of the temperature of the battery can thus be achieved.

[103] According to this same embodiment, the third heat exchanger 9 is a bifluid heat exchanger configured to exchange heat with a coolant. In other words, the third heat exchanger 9 is arranged jointly on the refrigerant fluid circuit 1 and on a heat transfer fluid circuit, so as to allow heat exchange between the refrigerant fluid and the heat transfer fluid. Advantageously, the third heat exchanger 9 is arranged on the heat transfer fluid circuit 20.

[104] In the examples illustrated here, the first heat exchanger 5 is configured to exchange heat with an interior air flow Fi at a vehicle cabin and the third heat exchanger 9 is a bifluid heat exchanger configured for exchanging heat with a coolant and configured to exchange heat with an electric energy storage battery of the vehicle.

[105] According to one embodiment, the first expansion device 4 is a thermostatically controlled expansion valve and the third expansion device 8 is an electronically controlled expansion valve. In other words, in this case the first expansion device 4 is a mechanical actuator without control. electric. The third expansion device 8 is an actuator comprising an electric motor and at least one shutter position sensor. The third expansion device 8 is controlled by the electronic control unit of the system, which controls the movement of the movable shutter managing the passage section of the expansion device.

[106] The main loop A comprises a first shut-off valve 31 arranged between the first connection point 11 and the first heat exchanger 5. This shut-off valve makes it possible to prevent the passage of refrigerant fluid in the main loop when the valve is closed. The passage of refrigerant is possible when the valve is open.

[107] According to a first embodiment of the thermal conditioning system, illustrated in particular in Figure 1, the first branch B branch comprises a second expansion device 6. The first branch B branch is then devoid of shut-off valve . The second expansion device 6 is placed on the first bypass branch B between the first connection point 11 and the second heat exchanger 7. According to the direction of travel of the refrigerant fluid in the first bypass branch B in normal operation of the system. , the second expansion device 6 is placed upstream of the second heat exchanger 7.

[108] Each of the first, second, and third expansion devices may be an electronic expansion valve, a thermostatic expansion valve, or a calibrated orifice. In the case of an electronic expansion valve and a thermostatic expansion valve, the passage section allowing the refrigerant to pass can be continuously adjusted between a closed position and a maximum open position. In the case of a calibrated orifice, the passage section allowing the refrigerant to pass through is constant.

[109] According to a second embodiment, illustrated in particular in FIG. 2, the first bypass branch B comprises a second shut-off valve 32. The first bypass branch B is then devoid of an expansion device. In this second embodiment, the second shut-off valve 32 is arranged on the first bypass branch B between the first connection point 11 and the second heat exchanger 7. In other words, according to the direction of flow of the refrigerant fluid in the first bypass branch B in normal operation of the system, the second shut-off valve 32 is arranged upstream of the second heat exchanger 7.

[110] According to a third embodiment, illustrated in particular in Figure 3, the thermal conditioning system comprises a third branch branch D connecting a fifth connection point 15 arranged on the main loop A and between the first expansion device 4 and the first heat exchanger 5 at a sixth connection point 16-1, 16-2 arranged on the main loop A between the fourth connection point 14 and an inlet of the compression device 2, the third bypass branch D comprising a fourth heat exchanger 23. In other words, the fourth heat exchanger 23 is arranged in parallel with the second heat exchanger 7. The third bypass branch D comprises a shut-off valve, called the fourth shut-off valve 34 arranged in upstream of the fourth heat exchanger 23.

[111] According to a variant, the sixth connection point 16-2 is upstream of the second internal heat exchanger 22.

[112] According to another variant, the sixth connection point 16-1 is downstream of the second internal heat exchanger 22 and upstream of the first internal heat exchanger 21. The two configurations are illustrated in the same FIG. 3, the configuration where the sixth connection point 16-2 is upstream of the second internal heat exchanger 22 being shown in dotted lines, and the configuration where the sixth connection point 16-1 is downstream of the second internal heat exchanger 22 being shown in line continued.

[113] In the example of Figure 3, the sixth connection point 16-1 is between the second internal heat exchanger 22 and the second connection point 12. In other words, the sixth connection point 16-1 is located between the outlet of the low pressure branch of the second internal heat exchanger 22 and the second connection point 12.

[114] According to a fourth embodiment, illustrated in particular in Figure 4, the first bypass branch B comprises a fourth heat exchanger 23 between the first connection point 11 and the second exchanger heat 7. In other words, the fourth heat exchanger 23 is arranged in series with the second heat exchanger 7 on the first bypass branch B. The fourth heat exchanger 23 is arranged upstream of the second heat exchanger 7 according to the direction of flow of the refrigerant in normal operation of the system.

[115] In the example of Figure 4, the fourth heat exchanger 23 is disposed between the first connection point 11 and the second shut-off valve 32.

[116] According to a fifth embodiment, illustrated in particular in FIG. 5, the thermal conditioning system 100 comprises a fourth branch branch E connecting a seventh connection point 17 disposed on the main loop A and included between the fourth heat exchanger. heat 23 and the second shut-off valve 32 at an eighth connection point 18 arranged on the main loop A between the fourth connection point 14 and an inlet of the compression device 2.

[117] The fourth branch E branch comprises a third shut-off valve 33 disposed between the seventh connection point 17 and the eighth connection point 18.

[118] The eighth connection point 18 is between the fourth connection point 14 and the second connection point 12.

[119] In the example of Figure 5, the eighth connection point 18 is between the second internal heat exchanger 22 and the second connection point 12. The eighth connection point 18 is thus located between the outlet of the low-pressure branch of the second internal heat exchanger 22 and the second connection point 12. In the example shown, the second connection point 12, the sixth connection point 16-1 and the eighth connection point 18 are distinct. They could quite be confused two by two, or all three confused.

[120] Each connection point 11-18 allows the refrigerant fluid to pass through one or the other of the circuit portions which meet at this connection point. The distribution of the refrigerant between the two circuit portions meeting at a connection point is effected by adjusting the opening or the closing of the shut-off valves or expansion devices included on each of the two branches. In other words, each connection point is a means of redirecting the fluid arriving at this connection point. The first connection point 11 is arranged on the first bypass branch B upstream of the connection point 12, according to the direction of travel of the refrigerant fluid in normal operation of the system. The third connection point 13 is arranged on the second branch branch C upstream of the fourth connection point 14. The fifth connection point 15 is disposed on the third branch branch D upstream from the sixth connection point 16-1, 16-2. The seventh connection point 17 is arranged on the fourth branch branch E upstream of the sixth connection point 18. By way of example, at the first connection point 11, the refrigerant coming from the first expansion device 4 on the main loop A can be redirected to the first bypass branch B or to the first heat exchanger 5 on the main loop A. At the third connection point 13, the refrigerant coming from the compression device 2 on the main loop A can be redirected to the second bypass branch C or to the first expansion device 4 on the main loop A. At the second connection point 12, the refrigerant coming from the second heat exchanger 7 on the first bypass branch B and the refrigerant from the main loop A can collect and be redirected to the inlet of the compression device 2. The m The same principle applies to the other connection points.

[121] The shut-off valves 31, 32, 33 thus make it possible to selectively direct the refrigerant fluid in the different branches of the refrigerant circuit, in order to ensure different operating modes, as will be described later.

[122] The fourth heat exchanger 23 is configured to exchange heat with a member 24 of an electric power train of the vehicle.

[123] By circulating refrigerant fluid at low pressure in the fourth heat exchanger, it is thus possible to recover the thermal energy dissipated by the operation of the element of the electric traction chain. When the thermal conditioning system is operating in this mode of energy recovery from the powertrain, heating of the air in the passenger compartment can be ensured while minimizing energy consumption. The driving range of the electric vehicle is thus improved.

[124] According to an exemplary implementation, the element 24 of an electric traction chain of the vehicle is an electric traction motor.

[125] According to another exemplary implementation, the element 24 of an electric traction chain of the vehicle is an electronic module for controlling an electric traction motor.

[126] Preferably, the fourth heat exchanger 23 is a bifluid exchanger configured to exchange heat with a coolant. The heat exchange between the coolant and the element 24 of the electric traction chain is thus ensured through the coolant. For this, the heat transfer fluid circulates around the element or elements of the traction chain which dissipate heat, for example the stator of the electric motor, or the power components of the control electronics of the electric motor.

[127] In other words, the fourth heat exchanger 23 is arranged jointly on the refrigerant circuit 1 and on a coolant circuit, so as to allow heat exchange between the coolant and the coolant. Advantageously, the fourth heat exchanger 23 is arranged on the heat transfer fluid circuit 20. In the example illustrated here, the bifluid exchanger 3, the third heat exchanger 9 and the fourth heat exchanger 23 are all three arranged on the same heat transfer fluid circuit 20.

[128] The coolant circuit 20 includes a fifth heat exchanger 30 configured to exchange heat with an internal air flow Fi to a vehicle cabin. The fifth heat exchanger can thus heat the interior of the vehicle, by dissipating heat in the air flow intended to supply the interior of the passenger compartment. The fifth heat exchanger 30, also called a heating radiator, is placed in the heating, ventilation and air conditioning installation downstream of the first heat exchanger 5.

[129] The heat transfer fluid circuit 20 comprises a sixth heat exchanger 35 configured to exchange heat with an external air flow Fe at the vehicle interior. The sixth heat exchanger is used to cool the heat transfer fluid in certain operating modes of the thermal conditioning system.

[130] In the example described, the same heat transfer fluid circuit 20 makes it possible to thermally couple the fifth heat exchanger 30 contributing to heating the air flow Fi inside the passenger compartment, the sixth heat exchanger 35, the third heat exchanger 9 ensuring the cooling of the battery, the fourth heat exchanger 23 ensuring the recovery of thermal energy dissipated by the electric traction chain.

[131] In order to simplify the figures, the heat transfer fluid circuit 20 comprising in particular the fifth heat exchanger 30 and the sixth heat exchanger 35 have been shown only in FIG. 1. The heat transfer fluid circuit is identical in the different embodiments.

[132] The heat transfer fluid circuit 20 also comprises several pumps making it possible to circulate the heat transfer fluid in the different branches of the heat transfer circuit. The heat transfer fluid circuit also includes several shut-off valves allowing the heat transfer fluid to be selectively sent to the different branches. Pumps and valves have not been shown in the figures, in order to simplify the figures.

[133] The refrigerant fluid circuit 1 comprises a refrigerant fluid accumulation device 29 arranged on the main loop A at the outlet of the bifluid exchanger 3. This accumulation device allows the quantity of fluid circulating in the circuit to refrigerant fluid adjusts to the conditions of use.

[134] We will now describe, as illustrated in Figures 6 to 14, some of the different possible operating modes of the thermal conditioning system 100. In these figures, the portions of the circuit in which the refrigerant circulates are shown. in thick solid line. The portions of the circuit in which the refrigerant does not circulate are shown in dotted lines.

[135] First operating mode:

FIGS. 6 and 8 illustrate the operation of the thermal conditioning system 100 according to a first operating mode, called the “heating” mode of the air in the passenger compartment. Figure 6 illustrates the operation of the first mode of embodiment, the one shown schematically in Figure 1. FIG. 8 illustrates the operation of the second embodiment, shown schematically in FIG. 2. The term “heating mode” and the term “heat pump mode” are equivalent.

[136] In this first mode of operation of the first embodiment of the thermal conditioning system 100, and as shown in FIG. 6, the refrigerant fluid circulates in the compression device 2 where it passes at high pressure, and circulates successively in the bifluid heat exchanger 3 where it transfers heat to the coolant, in the first internal heat exchanger 21, in the second internal heat exchanger 22, in the first expansion device 4 where it passes at low pressure, in the first bypass branch B, in the second expansion device 6, in the second heat exchanger 7 where it absorbs heat from the external air flow Fe, in the first internal heat exchanger 21, then the refrigerant fluid at low pressure returns to the compression device 2.]

[137] The high pressure refrigerant fluid coming from the outlet of the compression device 2 successively passes through the bifluid heat exchanger 3, the storage device 29, the high pressure branch of the first internal heat exchanger 21, the high branch pressure of the second internal heat exchanger 22. At the third connection point 13, the refrigerant does not circulate in the second bypass branch C, because the third expansion device 8 is in a closed position which prevents the passage of the refrigerant. Except for the leakage rate, all the refrigerant fluid continues to circulate in the portion of the main loop located downstream of the third connection point 13. The refrigerant fluid is expanded by passing through the expansion device 4. At the first connection point 11, the refrigerant fluid passes through the first bypass branch B and does not travel through the portion of the main loop located downstream of the first connection point 11 because the first stop valve 31 is in the closed position. The refrigerant fluid passes through the second expansion device, then the second heat exchanger 7. The refrigerant fluid joins the main loop at the second connection point 12, passes through the low pressure branch of the first internal heat exchanger 21 and joins the inlet of the compression device 2 where the refrigerant is again compressed and begins a new cycle. As the portion of the main loop between the first connection point 11 and the second connection point 12 is not traversed by the refrigerant fluid, the second heat exchanger 22 is inactive and does not allow heat exchange, since the low side pressure of this internal exchanger does not receive a flow of refrigerant fluid.

[138] In this first mode of operation of the second embodiment of the thermal conditioning system 100, and as shown in FIG. 8, the refrigerant fluid circulates in the compression device 2 where it passes at high pressure, and circulates successively in the bifluid heat exchanger 3 where it transfers heat to the coolant, in the first internal heat exchanger 21, in the second internal heat exchanger 22, in the first expansion device 4 where it passes at low pressure, in the first bypass branch B, in the second shut-off valve 32, in the second heat exchanger 7 where it absorbs heat from the external air flow Fe, in the first internal heat exchanger 21, then the fluid low pressure refrigerant returns to the compressor 2.

[139] In this first mode of operation of the second embodiment of the thermal conditioning system 100, the path of the refrigerant fluid is the same as for the first embodiment, except that the refrigerant fluid circulating in the first bypass branch B passes through the second shut-off valve 32 before joining the second heat exchanger 7.

[140] In the first embodiment as in the second, the flow of refrigerant fluid circulating in the refrigerant fluid loop is controlled by the passage section of the second expansion device 6 as well as by the speed of rotation of the compression device. 2. The refrigerant fluid is expanded to a pressure making it possible to have an evaporation temperature lower than the ambient temperature. The heat of vaporization of the refrigerant fluid is thus supplied by the flow of outside air Fe. The heat supplied to the air in the passenger compartment Fi being taken from the flow of outside air Fe, this mode is also called pump mode. heat. [141] In this first mode of operation, the heating of the air in the passenger compartment is carried out without the refrigerant passing through the first heat exchanger 5.

[142] The heat transfer fluid circulates in the bifluid heat exchanger 3 then part of the heat transfer fluid circulates in the fifth heat exchanger 30 where it transfers heat to the internal air flow Fi. Heating of the interior air flow Fi is provided by heat exchange between the fifth heat exchanger 30 and the air flow Fi intended for the passenger compartment. The coolant transfers heat to the coolant, which in turn transfers heat to the air in the passenger compartment. This operation is identical for all the illustrated embodiments.

[143] Second operating mode:

FIGS. 7 and 9 illustrate the operation of the thermal conditioning system 100 according to a second operating mode, called “parallel dehumidification” mode. FIG. 7 illustrates the operation of the first embodiment, that shown diagrammatically in FIG. 1. Figure 9 illustrates the operation of the second embodiment, shown schematically in Figure 2.

[144] In this second mode of operation called parallel dehumidification of the first embodiment of the thermal conditioning system 100, and as shown in FIG. 7, the refrigerant fluid circulates in the compression device 2 where it passes at high pressure , and circulates successively in the bifluid heat exchanger 3 where it transfers heat to the coolant, in the first internal heat exchanger 21, in the second internal heat exchanger 22, in the first expansion device 4 where it passes at low pressure, is divided between a first flow circulating in the first bypass branch B and a second flow circulating in the main loop A, the first flow circulating successively in the second expansion device 6 and in the second heat exchanger 7 where it absorbs heat from the external air flow Fe, the second flow circulates successively in the first heat exchanger 5 where it absorbs heat hauler of the internal air flow Fi, in the second internal heat exchanger 22, the first flow of low-pressure refrigerant fluid and the second flow of low-pressure refrigerant fluid meet at the second point of connection 12, the low-pressure refrigerant then circulates in the first internal heat exchanger 21 and returns to the compression device 2.

[145] In this operating mode, the low-pressure refrigerant fluid passes in parallel in the first heat exchanger and in the second heat exchanger. The air intended for the passenger compartment is thus cooled by passing through the first heat exchanger, then heated by passing through the fifth heat exchanger which receives the heat taken from the flow of outside air.

The air is thus dehumidified.

[146] In this second mode of operation of the first embodiment of the thermal conditioning system 100, the path of the refrigerant fluid between the outlet of the compression device 2 and the first expansion device 4 is identical to that of the operation according to the first operating mode, called heating mode. The refrigerant fluid is expanded in the first expansion device 4 where it passes at low pressure. At the first connection point 11, the flow of refrigerant fluid is divided into two. Part of the refrigerant fluid circulates in the first bypass branch B and the part complementary to the total flow circulates in the portion of the main loop A located downstream from point 11. Indeed, the first stop valve 31 is in an open position allowing the passage of the refrigerant fluid. This additional part of the low-pressure refrigerant fluid passes through the first heat exchanger 5 where it evaporates, which makes it possible to cool the internal air flow Fi. The low pressure refrigerant fluid coming from the first heat exchanger 5 then takes the main loop A, passes through the low pressure branch of the first internal heat exchanger 21 and reaches the second connection point 12. At the second connection point 12, the flow of refrigerant fluid from the second heat exchanger 7 and the flow of refrigerant fluid from the first heat exchanger 5 come together and the total flow passes through the first internal exchanger 21 and joins the inlet of the compressor 2. The first internal exchanger 21 and the second internal exchanger 22 are both active, that is to say that each of the exchangers allows a heat exchange between the refrigerant at low pressure and high pressure refrigerant flowing through each of its branches.

[147] In this second mode of operation called parallel dehumidification of the second embodiment of the thermal conditioning system 100, and as shown in FIG. 9, the refrigerant fluid circulates in the compression device 2 where it passes at high pressure , and circulates successively in the bifluid heat exchanger 3 where it transfers heat to the coolant, in the first internal heat exchanger 21, in the second internal heat exchanger 22, in the first expansion device 4 where it passes at low pressure, is divided between a first flow circulating in the first bypass branch B and a second flow circulating in the main loop A, the first flow circulating successively in the second shut-off valve 32 and in the second heat exchanger 7 where it absorbs heat from the external air flow Fe, the second flow circulates successively in the first heat exchanger 5 where it absorbs heat of the internal air flow Fi, in the second internal heat exchanger 22, the first flow of low-pressure refrigerant fluid and the second flow of low-pressure refrigerant fluid meet at the second connection point 12, the low-pressure refrigerant fluid pressure then flows through the first internal heat exchanger 21 and returns to the compression device 2

[148] In this second mode of operation of the second embodiment of the thermal conditioning system 100, the path of the refrigerant fluid is the same as for the first embodiment, except that the refrigerant fluid circulating in the first bypass branch B passes through the second shut-off valve 32 before joining the second heat exchanger 7. The path of the refrigerant fluid on the main loop A is itself identical.

[149] Third operating mode:

FIGS. 10 and 15 illustrate the operation of the thermal conditioning system 100 according to a third operating mode, called “energy recovery” mode. FIG. 10 illustrates the operation of the third embodiment, the architecture of which is shown diagrammatically in FIG. 3. FIG. 15 illustrates the operation of the fifth embodiment, the architecture of which is shown diagrammatically in FIG. 5.

[150] In this third mode of operation called energy recovery of the third embodiment of the thermal conditioning system 100, and as shown in FIG. 10, the refrigerant fluid circulates in the compression device 2 where it passes to high pressure, and circulates successively in the bifluid heat exchanger 3 where it transfers heat to the coolant, in the first internal heat exchanger 21, the second internal heat exchanger 22, the first expansion device 4 where it passes at low pressure, in the third branch branch D, the fourth heat exchanger 23 where the low-pressure refrigerant fluid absorbs heat, joins the main loop A at the sixth connection point 16-1, 16-2, the fluid Low pressure refrigerant then circulates in the first internal heat exchanger 21 and returns to the compression device 2.

[151] In this third mode of operation of the third embodiment of the thermal conditioning system 100, the path of the refrigerant fluid between the outlet of the compression device 2 and the first expansion device 4 is identical to that of the operation according to the first operating mode, called heating mode. Thus, the high pressure refrigerant fluid coming from the outlet of the compression device 2 successively passes through the bifluid heat exchanger 3, the accumulation device 29, the high pressure branch of the first internal heat exchanger 21, the high pressure branch of the second internal heat exchanger 22. At the third connection point 13, the refrigerant does not circulate in the second bypass branch C and all the flow of refrigerant continues to circulate in the portion of the main loop A located downstream of the third connection point 13. The refrigerant is expanded by passing through the expansion device 4 and passes at low pressure. At the fifth connection point 15, the refrigerant flows through the third auxiliary branch D. The first stop valve 31 and the second stop valve 32 are in the closed position. Consequently, the refrigerant does not circulate in the first bypass branch B nor in the portion of the main loop between the first stop valve 31 and the sixth connection point 16-1. The fourth stop valve 34 is in open position. The refrigerant fluid passes through the fourth heat exchanger 23 where the low pressure refrigerant fluid absorbs heat taken from the element 24 of the traction chain of the vehicle. At the sixth connection point 16-1, the refrigerant fluid joins the main loop A, then passes through the low pressure branch of the first internal heat exchanger 21 and joins the inlet of the compressor 2. The first internal exchanger 21 is active, the second internal exchanger 22 is inactive.

[152] The thermal energy recovered on the element 24 of the traction chain can be returned to the heat transfer fluid at the level of the bifluid heat exchanger 3 and thus participate in the heating of the passenger compartment via the heat transfer fluid circuit and the fifth heat exchanger 30. The energy consumption for heating the passenger compartment is thus minimized, since the heat lost for the operation of the traction chain is recovered.

[153] In the variant embodiment in which the third auxiliary branch D joins the main loop A at the connection point 16-2, that is to say upstream of the second internal heat exchanger 22, the second heat exchanger internal 22 and the first internal heat exchanger 22 are both active and allow heat exchange between the low pressure refrigerant fluid and the high pressure refrigerant.

[154] In this third mode of operation called energy recovery of the fifth embodiment of the thermal conditioning system 100, and as shown in FIG. 15, the refrigerant fluid circulates in the compression device 2 where it passes to high pressure, and circulates successively in the bifluid heat exchanger 3 where it transfers heat to the coolant, in the first internal heat exchanger 21, the second internal heat exchanger 22, the first expansion device 4 where it passes at low pressure, in the first bypass branch B, the fourth heat exchanger 23 where the low pressure refrigerant absorbs heat, joins the fourth bypass branch E at the seventh connection point 17, the low pressure refrigerant fluid then circulates in the first internal heat exchanger 21 and returns to the compression device 2. [155] Fourth operating mode:

Figures 11, 12 and 14 illustrate the operation of the thermal conditioning system 100 according to a fourth mode of operation, called the "energy recovery and heat pump" mode. Figure 11 illustrates the operation of the third embodiment, that shown schematically in Figure 3. Figure 12 illustrates the operation of the fourth embodiment, shown schematically in Figure 4. Figure 14 illustrates the operation of the fifth embodiment, schematically in figure 5.

[156] In this fourth mode of operation called "energy recovery and heat pump" of the third embodiment of the thermal conditioning system 100, and as shown in Figure 11, the refrigerant circulates in the device. compression 2 where it passes at high pressure, and circulates successively in the bifluid heat exchanger 3 where it transfers heat to the coolant, in the first internal heat exchanger 21, the second internal heat exchanger 22, the first device expansion valve 4 where it passes at low pressure, is divided between a first flow circulating in the third bypass branch D and a second flow circulating in the first bypass branch B,

- the first flow circulates successively in the fourth shut-off valve 34 then in the fourth heat exchanger 23 where the low pressure refrigerant absorbs heat then joins the main loop A at the sixth connection point 16-1, 16- 2,

- the second flow circulates successively in the first shut-off valve 32 and in the second heat exchanger 7 where it absorbs heat from the outside air flow Fe, the first flow of refrigerant at low pressure and the second flow of low pressure refrigerant meet at the second connection point 12, the low pressure refrigerant then circulates in the first internal heat exchanger 21 and returns to the compression device 2.

[157] In this operating mode, the refrigerant at low pressure recovers the heat dissipated by the electric traction chain in the fourth heat exchanger, and also recovers heat from the outside air flow Fe.

[158] In this fourth mode of operation of the third embodiment of the thermal conditioning system 100, the path of the refrigerant fluid between the outlet of the compression device 2 and the first expansion device 4 is identical to that of the operation according to the third operating mode, called “energy recovery” mode. The refrigerant fluid is expanded by passing through the first expansion device 4 and passes at low pressure. The total flow of refrigerant fluid is divided between a part which circulates in the third bypass branch D and a part which circulates in the first bypass branch B. The first stop valve 31 is in the closed position and there is no no circulation of refrigerant fluid in the first heat exchanger 5 and the portion of the main loop A between the first connection point 11 and the sixth connection point 16-1, 16-2. The second shut-off valve 32 is in the open position and the refrigerant can circulate in the first bypass branch B from the first connection point 11. This flow of refrigerant fluid at low pressure passes through the second heat exchanger 7, where it absorbs heat from the external air flow Fe. This flow of refrigerant fluid joins at the second connection point 12 the flow of refrigerant fluid coming from the sixth connection point 16-1, 16-2. The total flow of refrigerant fluid passes through the low pressure branch of the first internal heat exchanger 21 and reaches the inlet of compressor 2.

[159] In this embodiment and this mode of operation, heat is taken from both the external air flow Fe and from the element 24 of the traction chain, the refrigerant at low pressure circulating in parallel. in the second heat exchanger 7 and in the fourth heat exchanger 23.

[160] In this fourth mode of operation called "energy recovery and heat pump" of the fourth embodiment of the thermal conditioning system 100, and as shown in Figure 12, the refrigerant circulates in the device. compression 2 where it passes to high pressure, and circulates successively in the bifluid heat exchanger 3 where it transfers heat to the coolant, in the first heat exchanger internal 21, the second internal heat exchanger 22, the first expansion device 4 where it passes at low pressure, in the first bypass branch B, the fourth heat exchanger 23 where the refrigerant at low pressure absorbs heat, the second heat exchanger 7 where the low-pressure refrigerant fluid absorbs heat from the external air flow Fe, joins the main loop A at the second connection point 12, the low-pressure refrigerant then circulates in the first heat exchanger internal heat 21 and returns to the compression device 2.

[161] In this fourth mode of operation of the fourth embodiment of the thermal conditioning system 100, the path of the refrigerant fluid between the outlet of the compression device 2 and the first expansion device 4 is identical to that of the operation according to the fourth mode of operation of the third embodiment. The third expansion device 8 and the first shut-off valve 31 are in the closed position, and at the leakage rate nearly all the refrigerant fluid flow circulates in the first bypass branch B. In this embodiment, the low pressure branch of the second internal heat exchanger 22 is not traversed by the refrigerant fluid.

[162] In this embodiment and this mode of operation, heat is taken from both the external air flow Fe and from the element 24 of the traction chain, the low pressure refrigerant circulating in series. , and successively, in the second heat exchanger 7 and in the fourth heat exchanger 23. The same quantity of refrigerant fluid passes successively through the fourth heat exchanger 23 and the second heat exchanger 7.

[163] In this fourth mode of operation called "energy recovery and heat pump" of the fifth embodiment of the thermal conditioning system 100, and as shown in Figure 14, the refrigerant circulates in the device. compression 2 where it passes at high pressure, and circulates successively in the bifluid heat exchanger 3 where it transfers heat to the coolant, in the first internal heat exchanger 21, the second internal heat exchanger 22, the first device trigger 4 where it passes at low pressure, in the first branch branch B, the fourth heat exchanger 23 where the low-pressure refrigerant fluid absorbs heat, is divided between a first flow circulating in the first bypass branch B and a second flow circulating in the fourth bypass branch E, the first flow circulates in the second heat exchanger 7 where the low-pressure refrigerant fluid absorbs heat from the outside air flow Fe, the second flow circulates in the fourth bypass branch E, the first flow and the second flow meet at the second connection point 12, the low-pressure refrigerant then circulates in the first internal heat exchanger 21 and returns to the compression device 2.

[164] In this fifth embodiment and this mode of operation in energy recovery and heat pump, the circulation of refrigerant fluid between the outlet of the compression device 2 and the fourth heat exchanger 23 is identical to that of the fourth. embodiment. The low pressure refrigerant flow from the fourth heat exchanger 23 is divided at the seventh connection point 17 into a flow which circulates in the first bypass branch B and a complementary flow which circulates in the fourth bypass branch D. third stop valve 33 is in the open position. The flow circulating in the fourth bypass branch D joins the main loop A at the eighth connection point 18, then circulates to the second connection point 12, where it joins the flow of refrigerant circulating in the first bypass branch B and coming from the second heat exchanger 7. The total flow of refrigerant fluid passes through the low pressure branch of the first internal heat exchanger 21 and reaches the inlet of the compressor 2. The second heat exchanger 22 is not active.

[165] In this embodiment and this mode of operation, heat is taken from both the external air flow Fe and from the element 24 of the traction chain, the low pressure refrigerant circulating in series. , and successively, in the second heat exchanger 7 and in the fourth heat exchanger 23. The amount of refrigerant passing through the fourth heat exchanger 23 is greater than the amount of refrigerant passing through the second heat exchanger 7, since a part of the refrigerant flow borrows the fourth branch E branch and does not cross the second heat exchanger 7.

[166] Fifth operating mode:

FIG. 13 illustrates the operation of the thermal conditioning system 100 according to a fifth mode of operation, called the "energy recovery and parallel dehumidification" mode. The fourth embodiment is illustrated, the one whose architecture is shown schematically in Figure 4.

[167] In this fifth mode of operation called "energy recovery and parallel dehumidification" of the fourth embodiment of the thermal conditioning system 100, and as shown in Figure 13, the refrigerant circulates in the compression device 2 where it passes at high pressure, and circulates successively in the bifluid heat exchanger 3 where it transfers heat to the coolant, in the first internal heat exchanger 21, the second internal heat exchanger 22, the first device for expansion 4 where it passes at low pressure, is divided between a first flow circulating in the first bypass branch B and a second flow circulating in the main loop A, the first flow circulating successively in the fourth heat exchanger 23 where the refrigerant fluid at low pressure absorbs heat, the second heat exchanger 7 where the refrigerant at low pressure absorbs heat from the flow of a ir outside Fe, the second flow circulates successively in the first heat exchanger 5 where it absorbs heat from the internal air flow Fi, in the second internal heat exchanger 22, the first flow and the second flow of refrigerant fluid to low pressure meet at the second connection point 12, the refrigerant then circulates in the first internal heat exchanger 21 and returns to the compression device 2.

[168] In this fifth mode of operation called "energy recovery and parallel dehumidification" of the fourth embodiment, the circulation of refrigerant fluid differs from that of the fourth mode of operation in that a part of the refrigerant also circulates in the first heat exchanger 5 in order to cool the internal air flow Fi. At the first point of connection 11, the flow of refrigerant fluid is divided into a flow which circulates in the first bypass branch B and an additional flow which circulates in the main loop A. The first stop valve 31 is in the open position. The flow of low pressure refrigerant fluid circulating in the main loop A passes through the low pressure branch of the second heat exchanger 22. The flow circulating in the first bypass branch B and the flow circulating in the main loop A meet at the second point connection 12. The total flow of refrigerant fluid passes through the low pressure branch of the first internal heat exchanger 21 and reaches the inlet of the compressor 2. The two internal heat exchangers 21 and 22 are both active.

[169] In this operating mode, the low-pressure refrigerant fluid passes in parallel through the first heat exchanger and into the fourth heat exchanger. The air for the passenger compartment is cooled by the first heat exchanger and reheated by the fifth heat exchanger, which corresponds to dehumidification. At the same time, thermal energy is recovered from the drivetrain and also from the outside air flow. This mode makes it possible to avoid misting the passenger compartment by optimizing the energy expenditure of the system and without risking icing the second heat exchanger.

[170] Many other operating modes are also possible, by adjusting the flow of refrigerant fluid passing through the main loop A and each of the bypass branches B, C, D, E as well as on the level of expansion provided by each of the expansion devices 4, 6, 8.

[171] By way of example, we can cite a so-called “energy recovery and dehumidification” mode derived from the “energy recovery and heat pump” mode as illustrated in FIG. 14. In this mode, the refrigerant fluid at low pressure circulates in the first exchanger 5 and in the fourth exchanger 23. The refrigerant thus circulates in the main loop A and in the fourth bypass branch E. The refrigerant does not circulate in the portion of the first branch of bypass B located downstream of the seventh connection point 17 because the second shut-off valve 32 is in the closed position. The refrigerant does not pass through the second heat exchanger 7. The internal air flow Fi is therefore cooled by passing through the first heat exchanger 5, and reheated by passing through the fifth heat exchanger 30 which dissipates the heat from the fluid. coolant. The internal air flow Fi is thus dehumidified. Simultaneously, the fourth heat exchanger 23 recovers heat dissipated by the electric traction chain.

[172] According to embodiments not shown, the thermal management circuit according to the invention can also include one or more of the characteristics below, considered individually or combined with one another:

[173] The third heat exchanger 9 can be configured to exchange heat with an interior air flow Fi to a vehicle cabin and the first heat exchanger 5 is a bifluid heat exchanger configured to exchange heat with it. a heat transfer fluid and configured to exchange heat with an electric energy storage battery of the vehicle. In other words, the roles of the first heat exchanger 5 and of the third heat exchanger 9 are in this case reversed with respect to the examples shown in the figures.

[174] The sixth connection point 16-1 can be included between the second connection point 12 and the first internal heat exchanger 21. In other words, the sixth connection point 16-1 can be arranged between the second connection point 12 and the low pressure inlet of the first internal heat exchanger 21.

[175] The sixth connection point 16-1 can also be included between the first internal heat exchanger 21 and an inlet of the compression device 2. In other words, in this variant, the sixth connection point 16-1 is arranged between the low pressure outlet of the first internal heat exchanger 21 and the inlet of the compression device.

[176] The heat transfer fluid circuit may include an electric heating device. This heating device makes it possible to supplement, or replace, the heating provided by the bifluid exchanger 3.]

Claims

1. Thermal conditioning system (100) for a motor vehicle, comprising:

- A refrigerant fluid circuit (1) configured to circulate a refrigerant fluid, the refrigerant fluid circuit comprising: a main loop (A) comprising successively according to the direction of travel of the refrigerant fluid: a compression device (2), a bifluid heat exchanger (3), a first expansion device (4), a first heat exchanger (5), a first bypass branch (B) connecting a first connection point (11) arranged on the main loop (A ) upstream of the first heat exchanger (5) to a second connection point (12) arranged on the main loop (A) downstream of the first heat exchanger (5), the first bypass branch (B) comprising a second heat exchanger (7) configured to exchange heat with a flow of air (Fe) outside the vehicle interior, a second bypass branch (C) connecting a third connection point (13) arranged on the loop main (A) and included e between an outlet of the compression device (2) and the first expansion device (4) at a fourth connection point (14) arranged on the main loop (A) and between the first heat exchanger (5) and the second connection point (12), the second bypass branch (C) comprising a third expansion device (8) and a third heat exchanger (9),

- A heat transfer fluid circuit (20) configured to circulate a heat transfer fluid, the bifluid heat exchanger (3) being arranged jointly on the refrigerant circuit (1) and on the heat transfer fluid circuit (20) so to allow heat exchange between the refrigerant fluid and the heat transfer fluid, the main loop (A) comprising a first internal heat exchanger (21) configured to allow heat exchange between the fluid high pressure refrigerant circulating downstream of the bifluid heat exchanger (3) and low pressure refrigerant circulating downstream of the second connection point (12).

2. A thermal conditioning system (100) according to claim 1, wherein the main loop (A) also comprises a second internal heat exchanger (22) configured to allow heat exchange between the high pressure refrigerant flowing downstream. of the first internal exchanger (21) and upstream of the third connection point (13), and the low-pressure refrigerant circulating between the fourth connection point (14) and the second connection point (12).

3. Thermal conditioning system (100) according to one of the preceding claims, wherein the first bypass branch (B) allows the refrigerant circulating in the main loop (A) upstream of the first heat exchanger (5) of join the second heat exchanger (7) without passing through the first heat exchanger (5).

4. Thermal conditioning system (100) according to one of the preceding claims, wherein the first connection point (11) is between the first expansion device (4) and the first heat exchanger (5).

5. Thermal conditioning system (100) according to one of claims 1 to 4, wherein the first heat exchanger (5) is configured to exchange heat with an interior air flow (Fi) to a passenger compartment of the. vehicle and the third heat exchanger (9) is a bifluid heat exchanger configured to exchange heat with a coolant and configured to exchange heat with an electric energy storage battery (25) of the vehicle.

6. Thermal conditioning system (100) according to one of claims 1 to 4, wherein the third heat exchanger (9) is configured to exchange heat with an interior air flow (Fi) to a passenger compartment of the. vehicle and the first heat exchanger (5) is a bifluid heat exchanger configured to exchange heat with a coolant and configured to exchange heat with an electric energy storage battery (25) of the vehicle.

7. Thermal conditioning system (100) according to one of claims 1 to 6, wherein the first branch branch (B) comprises a second expansion device (6), the second expansion device (6) being disposed on the first branch branch (B) between the first connection point (11) and the second heat exchanger (7).

8. Thermal conditioning system (100) according to one of claims 1 to 6, wherein the first bypass branch (B) comprises a second shut-off valve (32), the second shut-off valve (32) being arranged on the first bypass branch (B) between the first connection point (11) and the second heat exchanger (7).

9. Thermal conditioning system (100) according to one of claims 1 to 8, comprising a third branch branch (D) connecting a fifth connection point (15) disposed on the main loop (A) and between the first expansion device (4) and the first heat exchanger (5) at a sixth connection point (16-1, 16-2) arranged on the main loop (A) between the fourth connection point (14) and an inlet of the compression device (2), the third bypass branch (D) comprising a fourth heat exchanger (23), the fourth heat exchanger (23) being configured to exchange heat with an element (24) of a electric drive chain of the vehicle.

10. Thermal conditioning system (100) according to the preceding claim, wherein the sixth connection point (16-1) is downstream of the second internal heat exchanger (22) and upstream of the first internal heat exchanger (21). .

11. Thermal conditioning system (100) according to one of claims 1 to 8, wherein the first branch branch (B) comprises a fourth heat exchanger (23) between the first connection point (11) and the second heat exchanger (7), the fourth heat exchanger (23) being configured to exchange heat with an element (24) of an electric traction chain of the vehicle.

12. Thermal conditioning system (100) according to claim 11, comprising a fourth branch branch (E) connecting a seventh connection point (17) arranged on the main loop (A) and included between the fourth heat exchanger (23) and the second shut-off valve (32) at an eighth connection point (18) arranged on the main loop (A) between the fourth connection point (14) and an inlet of the device compression (2).

13. A thermal conditioning system (100) according to one of claims 9 to 12, wherein the fourth heat exchanger (23) is a bifluid exchanger configured to exchange heat with a coolant.

14. Thermal conditioning system (100) according to one of the preceding claims, wherein the heat transfer fluid circuit (20) comprises a fifth heat exchanger (30) configured to exchange heat with an internal air flow ( Fi) to a vehicle interior.

15. A method of operating a thermal conditioning system (100) according to claim 7, in a heating mode in which the refrigerant fluid circulates in the compression device (2) where it passes at high pressure, and successively circulates in the bifluid heat exchanger (3) where it transfers heat to the coolant, in the first internal heat exchanger (21), in the second internal heat exchanger (22), in the first expansion device (4) where it passes at low pressure, in the first bypass branch (B), in the second expansion device (6), in the second heat exchanger (7) where it absorbs heat from the external air flow (Fe ), in the first internal heat exchanger (21), then the low pressure refrigerant fluid returns to the compression device (2).

16. A method of operating a thermal conditioning system (100) according to claim 8, in a heating mode in which the refrigerant fluid circulates in the compression device (2) where it passes at high pressure, and circulates successively in the bifluid heat exchanger (3) where it transfers heat to the coolant, in the first internal heat exchanger (21), in the second internal heat exchanger (22), in the first expansion device (4) where it passes at low pressure, in the first bypass branch (B), in the second shut-off valve (32), in the second heat exchanger (7) where it absorbs heat from the external air flow ( Fe), in the first heat exchanger internal heat (21), then the low-pressure refrigerant fluid returns to the compression device (2).

17. A method of operating a thermal conditioning system (100) according to claim 7 in combination with claim 5, in a so-called parallel dehumidification mode, in which the refrigerant fluid circulates in the compression device (2) where it. passes at high pressure, and circulates successively in the bifluid heat exchanger (3) where it transfers heat to the coolant, in the first internal heat exchanger (21), in the second internal heat exchanger (22), in the first expansion device (4) where it passes at low pressure, is divided between a first flow circulating in the first bypass branch (B) and a second flow circulating in the main loop (A), the first flow circulating successively in the second expansion device (6) and in the second heat exchanger (7) where it absorbs heat from the external air flow (Fe), the second flow circulates successively in the first heat exchanger eur (5) where it absorbs heat from the internal air flow (Fi), in the second internal heat exchanger (22), the first low pressure refrigerant flow rate and the second low pressure refrigerant flow rate meet at the second connection point (12), the low pressure refrigerant then circulates in the first internal heat exchanger (21) and returns to the compression device (2).

18. A method of operating a thermal conditioning system (100) according to claim 8 in combination with claim 5, in a so-called parallel dehumidification mode, in which the refrigerant fluid circulates in the compression device (2) where it. passes at high pressure, and circulates successively in the bifluid heat exchanger (3) where it transfers heat to the coolant, in the first internal heat exchanger (21), in the second internal heat exchanger (22), in the first expansion device (4) where it passes at low pressure, is divided between a first flow circulating in the first bypass branch (B) and a second flow circulating in the main loop (A), the first flow circulates successively in the second shut-off valve (32) and in the second heat exchanger (7) where it absorbs heat from the external air flow (Fe), the second flow circulates successively in the first exchanger heat exchanger (5) where it absorbs heat from the indoor air flow (Fi), in the second internal heat exchanger (22), the first low pressure refrigerant flow rate and the second low pressure refrigerant flow rate pressure meet at the second connection point (12), the low pressure refrigerant then circulates in the first internal heat exchanger (21) and returns to the compression device (2).

19. A method of operating a thermal conditioning system (100) according to claim 11 or 12, in a so-called energy recovery and heat pump mode, in which the refrigerant fluid circulates in the compression device (2). where it passes at high pressure, and circulates successively in the bifluid heat exchanger (3) where it transfers heat to the coolant, in the first internal heat exchanger (21), the second internal heat exchanger (22) , the first expansion device (4) where it passes at low pressure, in the first bypass branch (B), the fourth heat exchanger (23) where the refrigerant at low pressure absorbs heat, the second heat exchanger heat (7) where the low pressure refrigerant absorbs heat from the outside air flow (Fe), joins the main loop (A) at the second connection point (12), the low pressure refrigerant then circulates in the first interchange of internal heat (21) and returns to the compression device (2).

20. Operating method according to one of claims 15 to 19, in combination with claim 14, wherein the coolant circulates in the bifluid exchanger (3) then a portion of the coolant circulates in the fifth heat exchanger ( 30) where it gives up heat to the interior air flow (Fi).