Automotive Vehicle Thermal Conditioning System

Abstract

The invention relates to a thermal conditioning system (100) for a motor vehicle, comprising a refrigerant circuit (10) including: - a main loop (A) comprising successively: - a compressor (7), - a first heat exchanger (1) thermally coupled to an interior airflow (Fi) to the vehicle's passenger compartment, - a first expansion valve (21), - a second heat exchanger (2) thermally coupled to an exterior airflow (Fe) to the passenger compartment and comprising successively: - a first heat exchange section (2A), - a refrigerant accumulator (5), - a second heat exchange section (2B), - a second expansion valve (22), - a third heat exchanger (3),- a first branch (B) connecting a first connection point (11) located downstream of the first heat exchange section (2A) and upstream of the accumulator (5) to a second connection point (12) located downstream of the second heat exchange section (2B) and upstream of the third exchanger (3). Figure 1,

Description

Title of the invention: Thermal conditioning system for motor vehicles technical field

[0001] The present invention relates to the field of thermal conditioning systems. Such systems can, for example, be fitted to motor vehicles. These systems ensure thermal regulation of various vehicle components, such as the passenger compartment or an electrical energy storage battery, when the vehicle is electrically powered. Heat exchange is managed primarily by the compression and expansion of a refrigerant circulating in a circuit containing several heat exchangers. A compressor forces the refrigerant into a high-pressure state, allowing its circulation within the circuit. Previous technique

[0002] The mass of refrigerant circulating in the circuit may vary depending on the operating mode used and the operating conditions. To compensate for these variations, the refrigerant circuit includes a refrigerant accumulation device serving as a refrigerant storage reservoir.

[0003] It is known to integrate this refrigerant accumulation device with a heat exchanger that allows the high-pressure refrigerant to condense, dissipating the heat of condensation into the ambient air. This integration into the exchanger enables forced subcooling of the refrigerant, which improves the performance of the thermal conditioning system.

[0004] However, this integration of the refrigerant accumulation device into the heat exchanger creates a pressure drop that can degrade system performance in certain operating modes. Therefore, it is desirable to have thermal conditioning systems with improved energy efficiency. Summary

[0005] To this end, a thermal conditioning system for motor vehicles is proposed, comprising a refrigerant circuit configured to circulate a refrigerant, the refrigerant circuit comprising: - a main loop comprising successively, according to the direction of refrigerant flow: — a compressor, — a first heat exchanger thermally coupled to an airflow inside the passenger compartment of a motor vehicle, — a first expansion valve, — a second heat exchanger thermally coupled to an external airflow to the passenger compartment of the motor vehicle, the second exchanger comprising successively: — a first heat exchange section, — a first refrigerant accumulation device, — a second heat exchange section, — a second expansion valve, — a third heat exchanger, - a first branch connecting a first connection point located on the main loop downstream of the first heat exchange section of the second heat exchanger and upstream of the first refrigerant fluid accumulation device to a second connection point located on the main loop downstream of the second heat exchange section of the second heat exchanger and upstream of the third heat exchanger.

[0006] The bypass branch connected to the main loop upstream of the first storage device allows, in certain operating modes, for the first refrigerant storage device to be bypassed in order to reduce the pressure drop in the circuit. For example, the refrigerant does not circulate in the first storage device when the second heat exchanger is operating as an evaporator. The efficiency of the heat conditioning system is thus improved under these operating conditions.

[0007] The features listed in the following paragraphs can be implemented independently of each other or in any technically possible combination:

[0008] According to one embodiment, the thermal conditioning system comprises: - a second branch connecting a third connection point located on the main loop downstream of the first heat exchanger and upstream of the first heat exchange section of the second heat exchanger to a fourth connection point located on the main loop downstream of the third heat exchanger and upstream of the compressor, the second branch comprising a third expansion valve and a fourth heat exchanger configured to exchange heat with the indoor airflow, - a third branch connecting a fifth connection point located on the second branch between the third connection point and the third expansion valve to a sixth connection point located on the loop main downstream of the second heat exchange section of the second exchanger and upstream of the second connection point.

[0009] The second branch of the bypass and the third branch of the bypass allow for cooling of the vehicle's passenger compartment, as well as additional operating modes to optimize the operation of the thermal conditioning system.

[0010] According to one embodiment of the thermal conditioning system, the main loop includes a second accumulation device disposed downstream of the third exchanger and upstream of a compressor inlet.

[0011] The second accumulation device is arranged between the fourth connection point and the compressor inlet.

[0012] According to one embodiment of the thermal conditioning system, the first expansion valve is arranged jointly on the main loop and on the second bypass branch, and is configured to: - expanding the refrigerant fluid coming from the first heat exchanger, - selectively direct the expanded refrigerant either to the first heat exchange section of the second exchanger, or to the fifth connection point.

[0013] The use of a three-way regulator makes it possible to limit the number of components necessary, and therefore to simplify the thermal conditioning system.

[0014] The third connection point is part of the first regulator.

[0015] A section of passage of the refrigerant fluid through the first expansion valve can vary between a maximum opening position in which the refrigerant fluid passes through the first expansion valve without undergoing expansion, and a minimum opening position.

[0016] A section of the refrigerant fluid passing through the first expansion valve can vary continuously between the maximum opening position and the minimum opening position.

[0017] According to one embodiment of the thermal conditioning system, the second expansion valve is arranged jointly on the main loop and on the first bypass branch, and is configured to: - either expand the refrigerant from the sixth connection point and direct the expanded refrigerant to the third exchanger, while simultaneously blocking the refrigerant flow in the first branch of the bypass, - or allow refrigerant flow in the first branch of the bypass to the third exchanger, and simultaneously blocking the refrigerant flow between the sixth connection point and the third exchanger.

[0018] As before, the use of a second three-way regulator makes it possible to limit the number of components required, and therefore to simplify the thermal conditioning system.

[0019] The second connection point is part of the second regulator.

[0020] A section of the refrigerant fluid passing through the second expansion valve can vary between a maximum opening position in which the refrigerant fluid passes through the second expansion valve without undergoing expansion, and a minimum opening position.

[0021] A section of the refrigerant fluid passing through the second expansion valve can vary continuously between the maximum opening position and the minimum opening position.

[0022] The first exchanger is configured to operate as a high-pressure refrigerant fluid condenser.

[0023] The second exchanger is configured to operate selectively as a refrigerant fluid evaporator or as a refrigerant fluid condenser.

[0024] The third exchanger being configured to operate as a refrigerant fluid evaporator.

[0025] According to one example of implementation of the thermal conditioning system, the third exchanger is thermally coupled with an element of an electric powertrain of the vehicle.

[0026] The third exchanger is thermally coupled with an element of an electric traction chain of the vehicle via a heat transfer fluid circulating in a heat transfer fluid circuit.

[0027] The heat transfer fluid circuit may include an electric heating device configured to heat the heat transfer fluid circulating in the circuit.

[0028] According to one embodiment, the element of the vehicle's electric powertrain includes an electrical energy storage battery.

[0029] According to one variant, or in a complementary manner, the element of the vehicle's electric drive chain includes an electric vehicle traction motor.

[0030] Alternatively, or in addition, the element of the vehicle's electric traction chain may include an electronic control unit for the vehicle's electric traction motor.

[0031] According to one embodiment of the thermal conditioning system, the main loop includes an internal heat exchanger configured to allow heat exchange between: - the refrigerant circulating between the second heat exchange section of the second exchanger and the second expansion valve, and - the refrigerant fluid downstream of the second accumulation device and upstream of a compressor inlet.

[0032] The internal exchanger makes it possible to increase the enthalpy variation of the refrigerant fluid during the thermodynamic cycle, and therefore to increase the thermal power of the thermal conditioning system.

[0033] The internal exchanger includes a first heat exchange section arranged on the main loop between the second heat exchange section of the second exchanger and the second expansion valve, as well as a second heat exchange section arranged on the main loop downstream of the second accumulation device and upstream of the compressor inlet.

[0034] The first heat exchange section is arranged on the main loop downstream of the second heat exchange section of the second exchanger and upstream of the sixth connection point.

[0035] The internal heat exchanger is configured to allow heat exchange between the refrigerant in the first heat exchange section and the refrigerant in the second heat exchange section.

[0036] According to an unshown variant, the internal heat exchanger is configured to allow heat exchange between: - the refrigerant circulating in the main loop downstream of the fourth connection point and upstream of the second expansion valve, and - the refrigerant circulating in the main loop downstream of the second connection point and upstream of the second accumulation device.

[0037] According to another variant not shown, the internal exchanger is configured to allow heat exchange between: - the refrigerant circulating in the second branch of the bypass between the fourth connection point and the third connection point, and - the refrigerant circulating in the first branch of the bypass downstream of the fourth exchanger and upstream of the second connection point.

[0038] According to yet another variant not shown, the internal exchanger is configured to allow heat exchange between: - the refrigerant circulating in the first branch of the bypass downstream of the third connection point and upstream of the third expansion valve, and - the refrigerant circulating in the first branch of the bypass downstream of the fourth exchanger and upstream of the fourth connection point.

[0039] The second exchanger comprises a front face configured to receive the outside airflow and two lateral faces extending transversely to the front face.

[0040] According to one embodiment of the thermal conditioning system, the first heat exchange section of the second exchanger and the second heat exchange section of the second exchanger are arranged one above the other.

[0041] The second heat exchange section of the second exchanger is below the first heat exchange section of the second exchanger when the second exchanger is in its nominal installation position.

[0042] According to an example embodiment of the thermal conditioning system, the first heat exchange section of the second exchanger includes a refrigerant inlet and a refrigerant outlet, and wherein the refrigerant inlet of the first heat exchange section of the second exchanger and the refrigerant outlet of the first heat exchange section of the second exchanger are arranged on the same face of the second exchanger.

[0043] The first heat exchange section of the second exchanger comprises, for example, two passes.

[0044] According to an example embodiment of the thermal conditioning system, the second heat exchange section of the second exchanger comprises a refrigerant inlet and a refrigerant outlet, and wherein the refrigerant inlet of the second heat exchange section of the second exchanger and the refrigerant outlet of the second heat exchange section of the second exchanger are arranged on opposite faces of the second exchanger.

[0045] The refrigerant outlet of the first heat exchange section of the second exchanger and the refrigerant inlet of the second heat exchange section of the second exchanger are thus arranged on the same face of the second exchanger.

[0046] The second exchanger can thus have a particularly compact shape, facilitating its integration into the vehicle.

[0047] According to one embodiment, the first refrigerant fluid accumulation device is arranged opposite a lateral face of the second exchanger.

[0048] The invention also relates to a method of operating a thermal conditioning system as described above, in a first operating mode called "passenger compartment and battery cooling" in which: - a first flow of refrigerant circulates in the compression device where it passes through a high pressure, and circulates successively in the first heat exchanger without releasing heat, in the first expansion valve without undergoing expansion, in the first heat exchange section of the second heat exchanger, in the first accumulation device, in the second heat exchange section of the second heat exchanger, and is divided into: — a second flow of refrigerant circulating in the main loop, in the second expansion valve where it undergoes expansion and passes to a low pressure lower than the high pressure, then in the third heat exchanger where it evaporates, — a third flow of refrigerant circulating in the third branch of the bypass, then in the third expansion valve where it undergoes expansion and passes to low pressure, then in the fourth exchanger where it evaporates, and joins the refrigerant from the third exchanger, the total flow formed circulates in the second accumulation device and returns to the compressor.

[0049] In this first mode of operation: - The refrigerant flow rate in the first branch of the bypass is zero. - The refrigerant flow rate in the portion of the second branch of the bypass between the third connection point and the fifth connection point is zero. - The total flow of refrigerant, referred to as the first flow, circulates in the first accumulation device. The second heat exchange section of the second exchanger subcools the refrigerant condensed in the first heat exchange section of the second exchanger.

[0050] The invention also relates to a method of operating a thermal conditioning system as described above, in a second mode of operation called "heat pump and energy recovery" in which: - a flow of refrigerant circulates in the compression device where it passes to high pressure, and circulates successively in the first exchanger where it gives up heat, in the first expansion valve where it undergoes expansion and passes to a low pressure lower than the high pressure, in the first heat exchange section of the second exchanger where it evaporates at least in part, in the first bypass branch, in the second expansion valve without undergoing expansion, in the third exchanger where it evaporates at least in part, then in the second refrigerant accumulation device and returns to the compressor.

[0051] In this second mode of operation: - The refrigerant flow rate in the first refrigerant accumulation device is zero. - The flow rate of refrigerant fluid in the second heat exchange section of the second exchanger is zero. - The refrigerant flow rate in the second bypass branch is zero.

[0052] The invention also relates to a method of operating a thermal conditioning system as described above, in a third operating mode called the "first dehumidification mode" in which: - a flow of refrigerant circulates in the compression device where it passes to high pressure, and circulates successively in the first exchanger where it gives up heat, in the first expansion valve where it undergoes expansion and passes to an intermediate pressure lower than the high pressure, in the first heat exchange section of the second exchanger, in the first accumulation device, in the second heat exchange section of the second exchanger, in the third bypass branch, in the third expansion valve where it undergoes expansion and passes to a low pressure lower than the intermediate pressure, in the fourth exchanger where it evaporates, then in the second refrigerant accumulation device and returns to the compressor.

[0053] In this third mode of operation: - The refrigerant flow rate in the first branch of the bypass is zero. - The flow rate of refrigerant in the third exchanger is zero. - The refrigerant flow rate in the portion of the main loop between the sixth connection point and the fourth connection point is zero. - The refrigerant flow rate in the portion of the second branch of the bypass between the third connection point and the fifth connection point is zero. - The total flow of refrigerant circulates in the first accumulation device. The second heat exchange section of the second exchanger performs subcooling of the refrigerant condensed in the first heat exchange section of the second exchanger.

[0054] The invention also relates to a method of operating a thermal conditioning system as described above, in a fourth operating mode called the "second dehumidification mode" in which: - a first flow of refrigerant circulates in the compression device where it passes through high pressure, and circulates successively in the first heat exchanger where it releases heat, in the first expansion valve where it undergoes expansion and passes through an intermediate pressure lower than the high pressure, in the second bypass branch, and divides into: — a second flow of refrigerant circulating in the second bypass branch, successively in the third expansion valve where it undergoes expansion and passes to a low pressure lower than the intermediate pressure, then in the fourth exchanger where it evaporates, — a third flow of refrigerant circulating in the third bypass branch, then in the second expansion valve where it undergoes expansion and passes to low pressure, then in the third heat exchanger where it evaporates, and rejoins the refrigerant coming from the fourth heat exchanger, The total flow formed circulates through the second accumulation device and returns to the compressor.

[0055] In this fourth mode of operation: - The flow rate of refrigerant in the second exchanger is zero. - The refrigerant flow rate in the first branch of the bypass is zero. - The refrigerant flow rate in the portion of the main loop between the third connection point and the sixth connection point is zero.

[0056] The invention also relates to a method of operating a thermal conditioning system as described above, in a fifth operating mode called the "third dehumidification mode" in which: - a flow of refrigerant fluid circulates in the compression device where it passes to high pressure, and circulates successively in the first exchanger where it gives up heat, in the first expansion valve where it undergoes expansion and passes to an intermediate pressure lower than the high pressure, then in the second bypass branch, successively in the third expansion valve where it undergoes expansion and passes to a low pressure lower than the intermediate pressure, in the fourth exchanger where it evaporates, then in the second accumulation device, and returns to the compressor.

[0057] In this fifth mode of operation: - The flow rate of refrigerant in the second exchanger is zero. - The refrigerant flow rate in the first branch of the bypass is zero. - The flow rate of refrigerant in the third exchanger is zero. - The refrigerant flow rate in the third branch of the bypass is zero.

[0058] The invention also relates to a method of operating a thermal conditioning system as described above, in a sixth operating mode called "energy recovery" in which: - a flow of refrigerant fluid circulates in the compression device where it passes to high pressure, and circulates successively in the first exchanger where it gives up heat, in the first expansion valve without undergoing expansion, in the second bypass branch, in the third bypass branch, in the second expansion valve where it undergoes expansion and passes to a low pressure lower than the high pressure, in the third exchanger where it evaporates, then in the second accumulation device and returns to the compressor.

[0059] In this sixth mode of operation: - The flow rate of refrigerant in the second exchanger is zero. - The refrigerant flow rate in the first branch of the bypass is zero. - The flow rate of refrigerant in the fourth exchanger is zero. Brief description of the drawings

[0060] Other features, details and advantages will become apparent upon reading the detailed description below, and upon analysis of the accompanying drawings, on which:

[0061] [Fig-1] is a schematic view of a first embodiment of the system of Thermal conditioning offered,

[0062] [Fig.2] is a schematic view of a second embodiment of the proposed thermal conditioning system,

[0063] [Fig.3] is a schematic view of the thermal conditioning system of the [Fig.1], operating according to a first mode of operation, called passenger compartment and battery cooling mode,

[0064] [Fig.4] is a schematic view of the thermal conditioning system of [Fig.1], operating according to a second mode of operation, called heat pump and energy recovery mode,

[0065] [Fig.5] is a schematic view of the thermal conditioning system of [Fig.1], operating according to a third mode of operation, called the first dehumidification mode,

[0066] [Fig.6] is a schematic view of the thermal conditioning system of [Fig.1], operating according to a fourth operating mode, called the second dehumidification mode,

[0067] [Fig.7] is a schematic view of the thermal conditioning system of [Fig.1], operating according to a fifth operating mode, called the third dehumidification mode,

[0068] [Fig.8] is a schematic view of the thermal conditioning system of [Fig.1], operating according to a sixth operating mode, called energy recovery mode,

[0069] [Fig.9] is a schematic view detailing part of the proposed thermal conditioning system,

[0070] [Fig. 10] is another schematic view detailing part of the proposed thermal conditioning system. Description of the implementation methods

[0071] To facilitate reading the figures, the various elements are not necessarily drawn to scale. In these figures, identical elements bear the same reference numerals. Certain elements or parameters may be indexed, that is, designated, for example, as first element or second element, or first parameter and second parameter, etc. This indexing aims to differentiate between similar, but not identical, elements or parameters. This Indexing does not imply a priority of one element or parameter over another, and the names can be interchanged.

[0072] In the following description, the expression "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, or path, 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, or path, of the fluid in question. In the case of the refrigerant circuit, the term "a first element is upstream of a second element" means that the refrigerant flows successively through the first element, then the second element, without passing through the compression device. In other words, the refrigerant exits the compression device, possibly passes through one or more elements, then passes through the first element, then the second element, and then returns to the compression device, possibly after passing through other elements..

[0073] The expression "a second element is placed between a first element and a third element" means that the shortest path to go from the first element to the third element passes through the second element.

[0074] When it is specified that a subsystem includes a given element, this does not exclude the presence of other elements in that subsystem.

[0075] The thermal conditioning system 100, which will be described below, comprises an electronic control unit that receives information from various sensors, notably those measuring the characteristics of the refrigerant at various points in the circuit. The electronic control unit also receives commands from the vehicle occupants, such as the desired temperature inside the passenger compartment. The electronic control unit can also receive commands from other electronic subsystems, such as the battery management system for electrical energy storage. The electronic control unit implements control laws to operate the various actuators, thereby ensuring that the thermal conditioning system 100 is controlled in such a way as to maintain the received commands.

[0076] A compression device 7 allows a refrigerant to circulate in a refrigerant circulation circuit 10. The refrigerant circuit 10 forms a closed circuit in which the refrigerant can circulate. The refrigerant circuit 10 is leak-proof when it is in a nominal operating state, that is, without any faults or leaks. Each connection point of the circuit 10 allows the refrigerant to pass into one or the other of the circuit portions that meet at that connection point. The distribution of the refrigerant between the portions of The circuit joining at a connection point is controlled by opening or closing shut-off valves, check valves, or expansion devices located on each section. In other words, each connection point redirects the refrigerant arriving at that point. Various shut-off valves and check valves allow the refrigerant to be selectively directed to the different branches of the refrigerant circuit, thus ensuring different operating modes, as will be described later.

[0077] The refrigerant used by the refrigerant circuit 10 is here a chemical fluid such as R1234yf, or 134a. A natural refrigerant, such as R290 or R744, can also be used.

[0078] Each refrigerant expansion device, also called an expansion valve, can be an electronic expansion valve. In an electronic expansion valve, the passage area through which the refrigerant passes can be continuously adjusted between a closed position and a maximum open position. To achieve this, an electronic control module for the expansion valve drives an electric motor that moves a movable shutter, thus controlling the passage area available to the refrigerant.

[0079] The heat transfer fluid circuit(s) also form one or more closed and sealed circuits in which a heat transfer fluid can circulate. The heat transfer fluid can exchange heat during its circulation.

[0080] The term "interior airflow Fi" refers to an airflow directed towards the passenger compartment of the motor vehicle. This interior airflow Fi may circulate within a heating, ventilation, and / or air conditioning (HVAC) system. This system is not shown in the various figures. A first motor-fan unit, not shown, is located within the HVAC system to increase the flow rate of the interior airflow Fi if necessary.

[0081] The term "external airflow Fe" refers to an airflow that is not directed towards the vehicle's passenger compartment. In other words, this airflow Fe remains outside the vehicle's passenger compartment. A second motor-fan unit, also not shown, can be activated to increase the flow rate of the external airflow Fe if necessary. The airflow provided by both the first and second motor-fan units can be adjusted in real time according to heat exchange requirements, for example, by the electronic control unit of the climate control system 100.

[0082] The term "first exchanger" is equivalent to the term "first heat exchanger". Similarly, the term "internal exchanger" is equivalent to the term "internal heat exchanger". The term "storage device" is equivalent to the term "refrigerant storage device".

[0083] A thermal conditioning system 100 for a motor vehicle is schematically represented in [Fig. 1]. The thermal conditioning system 100 comprises a refrigerant circuit 10 configured to circulate a refrigerant. The refrigerant circuit 10 comprises a main loop A including successively, according to the direction of refrigerant flow: - a compressor 7, - a first heat exchanger 1 thermally coupled to an internal airflow Fi in the passenger compartment of a motor vehicle, - a first expansion valve 21, - a second heat exchanger 2 thermally coupled to an outside airflow Fe to the passenger compartment of the motor vehicle, the second heat exchanger 2 comprising successively: — a first heat exchange section 2A, — a first refrigerant fluid accumulation device 5, — a second heat exchange section 2B, — a second expansion valve 22, - a third heat exchanger 3. The refrigerant circuit 10 includes a first branch B connecting a first connection point 11 located on the main loop A downstream of the first heat exchange section 2A of the second heat exchanger 2 and upstream of the first refrigerant storage device 5 to a second connection point 12 located on the main loop A downstream of the second heat exchange section 2B of the second heat exchanger 2 and upstream of the third heat exchanger 3.

[0084] The first branch B, connected to the main loop A upstream of the first storage unit 5, allows, in certain operating modes, the first refrigerant storage unit 5 to be bypassed in order to reduce the pressure drop in the circuit 10. In other words, the refrigerant does not circulate through the first storage unit 5 in certain operating modes. Thus, the refrigerant does not circulate through the first storage unit 5 when the second heat exchanger 2 is operating as an evaporator. Thanks to the associated reduction in pressure drop, the efficiency of the thermal conditioning system 100 is improved. Fig. 9 is a detailed, enlarged view of the portion of circuit 10 in the vicinity of the second exchanger 2. The first accumulation device 5 is a desiccant bottle.

[0085] According to the illustrated embodiment, the thermal conditioning system 100 also comprises: - a second branch C connecting a third connection point 13 located on the main loop A downstream of the first heat exchanger 1 and upstream of the first heat exchange section 2A of the second heat exchanger 2 to a fourth connection point 14 located on the main loop A downstream of the third heat exchanger 3 and upstream of the compressor 7, the second branch C comprising a third expansion valve 23 and a fourth heat exchanger 4 configured to exchange heat with the indoor air flow Fi, - a third branch D connecting a fifth connection point 15 located on the second branch C between the third connection point 13 and the third expansion valve 23 to a sixth connection point 16 located on the main loop A downstream of the second heat exchange section 2B of the second heat exchanger 2 and upstream of the second connection point 12.

[0086] The third expansion valve 23 is arranged between the fifth connection point 15 and the fourth heat exchanger 4, and allows the fourth heat exchanger 4 to be supplied with low-pressure refrigerant. The second branch of the C bypass and the third branch of the D bypass allow for cooling of the vehicle's passenger compartment, as well as additional operating modes to optimize the operation of the thermal conditioning system.

[0087] According to the illustrated example, the main loop A includes a second accumulation device 6 located downstream of the third exchanger 3 and upstream of an inlet 7a of the compressor 7. The second accumulation device 6 is arranged between the fourth connection point 14 and the inlet 7a of the compressor 7. The second accumulation device 6 ensures that the refrigerant arriving at the inlet 7a of the compressor 7 is in a completely gaseous state.

[0088] According to the illustrated example, the first regulator 21 is arranged jointly on the main loop A and on the second branch C. The first regulator 21 is configured to: - to expand the refrigerant fluid coming from the first heat exchanger 1, - selectively direct the expanded refrigerant either to the first heat exchange section 2A of the second exchanger 2, or to the fifth connection point 15.

[0089] The use of a three-way regulator makes it possible to limit the number of components required, and therefore to simplify the thermal conditioning system.

[0090] The third connection point 13 is part of the first regulator 21.

[0091] A section of the refrigerant fluid passing through the first expansion valve 21 can vary between a maximum opening position in which the refrigerant fluid passes through the first expansion valve 21 without undergoing expansion, and a minimum opening position.

[0092] A section of the refrigerant fluid passing through the first expansion valve 21 can vary continuously between the maximum opening position and the minimum opening position.

[0093] The first regulator 21 is a three-way valve capable of jointly providing controlled expansion. The first expansion valve 21 includes a refrigerant inlet and two refrigerant outlets. The first expansion valve 21 can supply expanded refrigerant at the first outlet or at the second outlet, simultaneously closing the other outlet. Communication between the inlet and one of the outlets of the first regulator 21 is always maintained. The two outlets of the first regulator 21 cannot be simultaneously closed. The expansion rate achieved at the outlet supplying the refrigerant can vary continuously, from zero expansion to maximum expansion.

[0094] The first regulator 21 includes, for example, a rotating movable obturator having the shape of a sphere having an internal recess forming an internal fluid circulation conduit. The hollow comprises a first portion extending radially from the periphery of the sphere to the center of the sphere. The hollow comprises a second portion extending perpendicularly from the first portion. This second portion extends radially from the center of the sphere to the periphery of the sphere. The second and first sections are, for example, perpendicular. The movable shutter is housed within a casing that forms three refrigerant circulation channels. The movable shutter separates the different fluid circulation channels and can be moved by a control mechanism. The movable shutter forms a fluid passage opening whose effective section is controlled by the angular position of the movable shutter.

[0095] According to the illustrated example, the second regulator 22 is arranged jointly on the main loop A and on the first branch B. The second regulator 22 is configured to: - either expand the refrigerant from the sixth connection point 16 and direct the expanded refrigerant to the third exchanger 3, blocking jointly the circulation of refrigerant fluid in the first branch of bypass B, - either allow refrigerant flow in the first branch of bypass B towards the third exchanger 3, and jointly block refrigerant flow between the sixth connection point 16 and the third exchanger 3.

[0096] As before, the use of a second three-way regulator makes it possible to limit the number of components required, and therefore to simplify the thermal conditioning system.

[0097] Like the first regulator 21, the second regulator 22 is a three-way valve capable of jointly providing controlled expansion.

[0098] The second connection point 12 is part of the second regulator 22.

[0099] A section of the refrigerant fluid passing through the second expansion valve 22 can vary between a maximum opening position in which the refrigerant fluid passes through the second expansion valve 22 without undergoing expansion, and a minimum opening position.

[0100] A section of the refrigerant fluid passing through the second expansion valve 22 can vary continuously between the maximum opening position and the minimum opening position.

[0101] The second regulator 22 can be identical to the first regulator 21. The first expansion valve 21 and the second expansion valve 22 are electronic expansion valves. An electronic control module drives an electric motor that moves the movable damper, controlling the cross-sectional area of ​​the refrigerant flow. This allows for real-time, closed-loop control of the damper's position.

[0102] The first exchanger 1 is configured to operate as a high-pressure refrigerant fluid condenser. Indeed, the first exchanger 1 receives the high-pressure refrigerant fluid from the outlet 7b of the compressor 7.

[0103] According to the illustrated example, the first exchanger 1 is configured to exchange heat with an interior airflow Fi to the passenger compartment of a motor vehicle. The thermal coupling between the first exchanger 1 and the internal airflow Fi is then said to be direct. The first heat exchanger 1 is located in the vehicle's heating, ventilation and / or air conditioning system.

[0104] According to another embodiment, not illustrated, the first heat exchanger 1 is configured to exchange heat with a heat transfer fluid circulating in a closed heat transfer fluid circuit, and the heat transfer fluid circuit comprises a heat exchanger configured to exchange heat with an interior airflow Fi to the vehicle's passenger compartment. In this case, the thermal coupling between the first exchanger 1 and the indoor airflow Fi is said to be indirect, since the thermal coupling takes place via a heat transfer fluid. The heat exchanger located on the heat transfer fluid circuit and capable of exchanging heat with the interior airflow Fi is designated by the term heater radiator, and is located in the heating, ventilation and / or air conditioning system of the vehicle.

[0105] The second exchanger 2 is configured to operate selectively as a refrigerant fluid evaporator or as a refrigerant fluid condenser. Indeed, the second exchanger 2 can, depending on the operating modes, receive either high-pressure gaseous refrigerant or low-pressure liquid refrigerant. The second exchanger 2 is for example located in the front of the vehicle, in order to receive the outside airflow Fe. The second interchange 2 thus receives the airflow resulting from the forward movement of the vehicle. A motor-fan unit, not shown, can increase the outside air flow Fe on the second exchanger 2.

[0106] The third exchanger 3 being configured to operate as a refrigerant fluid evaporator.

[0107] According to the illustrated example, the third heat exchanger 3 is thermally coupled with an element 25 of an electric drive chain of the vehicle. The third exchanger 3 allows the element 25 of the vehicle's electric traction chain to be cooled, or heat dissipated by the operation of the element 25 to be recovered.

[0108] The third heat exchanger 3 is thermally coupled with the element 25 of the vehicle's electric drive chain via a heat transfer fluid circulating in a heat transfer fluid circuit 40. The heat transfer fluid is, for example, a mixture of water and glycol. A circulation pump, not shown, allows the heat transfer fluid to circulate in circuit 40. The circulation pump is, for example, an electric pump that can be selectively activated or deactivated.

[0109] The heat transfer fluid circuit 40 may include an electric heating device 26 configured to heat the heat transfer fluid circulating in the circuit. The electric heating device 26 includes an electric resistance element for dissipating heat into the heat transfer fluid. The electric heating device 26 can be selectively switched on or off.

[0110] In the illustrated example, element 25 of the vehicle's electric drive chain includes an electrical energy storage battery.

[0111] According to one variant, or in a complementary manner, element 25 of the vehicle's electric drive chain may include an electric vehicle traction motor.

[0112] According to another embodiment, or complementaryly, element 25 of the vehicle's electric drive chain may include an electronic control unit for the vehicle's electric traction motor.

[0113] The fourth heat exchanger 4 is configured to operate as a refrigerant evaporator and cools the interior airflow Fi to the vehicle's passenger compartment. The fourth heat exchanger 4 is located in the vehicle's heating, ventilation, and / or air conditioning system. The fourth exchanger 4 is positioned upstream of the first exchanger 1 according to the direction of flow of the internal air flow Fi.

[0114] Fig. 2 schematically represents a second embodiment of the thermal conditioning system 100. According to this second embodiment, the main loop A includes an internal heat exchanger 9 configured to allow heat exchange between: - the refrigerant circulating between the second heat exchange section 2B of the second exchanger 2 and the second expansion valve 22, and - the refrigerant fluid downstream of the second accumulation device 6 and upstream of an inlet 7a of the compressor 7.

[0115] The internal exchanger 9 makes it possible to increase the enthalpy variation of the refrigerant during the thermodynamic cycle, and therefore to increase the thermal power of the thermal conditioning system.

[0116] The internal exchanger 9 includes a first heat exchange section 9a arranged on the main loop A between the second heat exchange section 2B of the second exchanger 2 and the second expansion valve 22, and a second heat exchange section 9b arranged on the main loop A downstream of the second storage device 6 and upstream of the inlet 7a of the compressor 7.

[0117] The internal heat exchanger 9 is configured to allow heat exchange between the refrigerant in the first heat exchange section 9a and the refrigerant in the second heat exchange section 9b.

[0118] More specifically, the first heat exchange section 9a is arranged on the main loop A downstream of the second heat exchange section 2B of the second exchanger 2 and upstream of the sixth connection point 16.

[0119] The internal exchanger 9 can be arranged in different ways on the refrigerant circuit 10.

[0120] According to an alternative embodiment not shown, the internal heat exchanger 9 is configured to allow heat exchange between: - the refrigerant circulating in the main loop A downstream of the sixth connection point 16 and upstream of the second expansion valve 22, and - the refrigerant circulating in the main loop A downstream of the fourth connection point 14 and upstream of the second accumulation device 6.

[0121] In this case, the first heat exchange section 9a of the internal exchanger 9 is arranged between the sixth connection point 16 and the second expansion valve 22, and the second heat exchange section 9b of the internal exchanger 9 is arranged between the fourth connection point 14 and the second storage device 6.

[0122] According to another variant not shown, the internal heat exchanger 9 is configured to allow heat exchange between: - the refrigerant circulating in the third branch of bypass D between the fifth connection point 15 and the sixth connection point 16, and - the refrigerant circulating in the second branch of bypass C downstream of the fourth exchanger 4 and upstream of the fourth connection point 14.

[0123] In this variant, the first heat exchange section 9a of the internal exchanger 9 is arranged on the third branch branch D, and the second heat exchange section 9b of the internal exchanger 9 is arranged on the second branch branch C between the fourth exchanger 4 and the fourth connection point 14.

[0124] According to yet another variant not shown, the internal exchanger 9 is configured to allow heat exchange between: - the refrigerant circulating in the second branch of bypass C downstream of the fifth connection point 15 and upstream of the third expansion valve 23, and - the refrigerant circulating in the second branch of bypass C downstream of the fourth exchanger 4 and upstream of the fourth connection point 14.

[0125] In this variant, the first heat exchange section 9a of the internal exchanger 9 is arranged on the second branch branch C between the fifth connection point 15 and the third expansion valve 23, and the second heat exchange section 9b of the internal exchanger 9 is arranged on the second branch branch C between the fourth exchanger 4 and the fourth connection point 14.

[0126] The second exchanger 2 comprises a front face Fl configured to receive the outside air flow Fe and two lateral faces F2, F3 extending transversely to the front face Fl.

[0127] Fig. 10 illustrates construction details of the second interchange 2. According to this embodiment example, the first heat exchange section 2A of the second exchanger 2 and the second heat exchange section 2B of the second exchanger 2 are arranged one above the other.

[0128] The second heat exchange section 2B of the second exchanger 2 is below the first heat exchange section 2A of the second exchanger 2 when the second exchanger 2 is in its nominal installation position.

[0129] In [Fig. 10], the Z-axis corresponds to the vertical axis, oriented from bottom to top. The X-axis corresponds to the longitudinal axis of the vehicle, oriented from front to back. The Y-axis corresponds to the transverse axis of the vehicle.

[0130] According to the example illustrated in [Fig. 10], the first heat exchange section 2A of the second heat exchanger 2 comprises a refrigerant inlet 2A_I and a refrigerant outlet 2A_O. The refrigerant inlet 2A_I of the first heat exchange section 2A of the second heat exchanger 2 and the refrigerant outlet 2A_O of the first heat exchange section 2A of the second heat exchanger 2 are located on the same face F2 of the second heat exchanger 2.

[0131] The first heat exchange section 2A of the second heat exchanger 2 comprises, for example, two passes, as illustrated in [Fig. 10]. The two passes are arranged one above the other along the vertical axis Z. The refrigerant flows in the same direction in the first and second passes, and in opposite directions in the second pass.

[0132] According to the example illustrated in [Fig. 10], the second heat exchange section 2B of the second heat exchanger 2 comprises a refrigerant inlet 2B_I and a refrigerant outlet 2B_O. The refrigerant inlet 2B_I of the second heat exchange section 2B of the second heat exchanger 2 and the refrigerant outlet 2B_O of the second heat exchange section 2B of the second heat exchanger 2 are arranged on opposite faces F2, F3 of the second heat exchanger 2.

[0133] The refrigerant outlet 2A_O of the first heat exchange section 2A of the second exchanger 2 and the refrigerant inlet 2B_I of the second heat exchange section 2B of the second exchanger 2 are thus arranged on the same face F2 of the second exchanger 2.

[0134] The inlet 2A_I of the first heat exchange section 2A is arranged, along the vertical axis Z, between the outlet 2A_O of the first heat exchange section 2A and the inlet 2B_I of the second heat exchange section 2B. As before, the exchanger 2 is assumed to be oriented according to its nominal installation position in the vehicle.

[0135] The second interchange 2 can thus have a particularly compact shape, facilitating its integration into the vehicle.

[0136] According to one embodiment, the first refrigerant storage device 5 is arranged opposite a lateral face F2 of the second heat exchanger 2. The first storage device 5 is a receiver drier. The first storage device has a cylindrical shape, and its axis is oriented parallel to the plane of extension of the lateral face F2.

[0137] Figures 3 to 8 illustrate the operation of the thermal conditioning system 100 of [Fig.1] according to different operating modes. In these figures, the portions of circuit 10 in which refrigerant flows are shown as thick solid lines, while the portions in which refrigerant does not flow are shown as thin dashed lines. The different arrows indicate the direction of refrigerant flow in the various portions of the refrigerant circuit 10.

[0138] In steady state, the time variation of the mass of refrigerant in a heat exchanger is zero, and the flow rate of refrigerant downstream of a heat exchanger is equal to the flow rate of refrigerant upstream of this heat exchanger. Similarly, there is no accumulation of refrigerant in an expansion valve, and the flow rate of refrigerant downstream of an expansion valve is equal to the flow rate upstream of that expansion valve.

[0139] Fig. 3 schematically illustrates a method of operation of the thermal conditioning system 100, in a first mode of operation called "cabin and battery cooling". In this first operating mode, an initial flow Qrl of refrigerant circulates through the compression device 7 where it is subjected to high pressure, and then flows successively through the first heat exchanger 1 without releasing heat, through the first expansion valve 21 without undergoing expansion, through the first heat exchange section 2A of the second heat exchanger 2, through the first storage device 5, through the second heat exchange section 2B of the second heat exchanger 2, and is divided into: - a second flow Qr2 of refrigerant circulating in the main loop A, through the second expansion valve 22 where it undergoes expansion and passes to a lower pressure than the high pressure, then through the third heat exchanger 3 where it evaporates, - a third flow Qr3 of refrigerant circulating in the third branch of the bypass D, then through the third expansion valve 23 where it undergoes expansion and passes to low pressure, then in the fourth exchanger 4 where it evaporates, and joins the refrigerant fluid from the third exchanger 3. The total flow formed circulates in the second accumulation device 6 and returns to the compressor 7.

[0140] In this first mode of operation: - The flow rate of refrigerant fluid in the first branch of bypass B is zero. - The refrigerant flow rate in the portion of the second branch of the bypass C between the third connection point 13 and the fifth connection point 15 is zero. - The total flow of refrigerant, called first flow Qrl, circulates in the first accumulation device 5. The second heat exchange section 2B of the second exchanger 2 performs a subcooling of the refrigerant condensed in the first heat exchange section 2A of the second exchanger 2.

[0141] In this mode of operation, the second exchanger 2 operates as a refrigerant fluid condenser, and allows subcooling of the refrigerant fluid. The circulation of the refrigerant fluid in the second exchanger 2 is schematically represented by the symbol C2, on part B of [Fig. 10]. The refrigerant from outlet 2A_O of the first heat exchange section 2A flows into the first storage device 5, then joins the inlet 2B_I of the second heat exchange section 2B. The subcooled liquid exits at outlet 2B_O.

[0142] The third heat exchanger 3 functions as an evaporator and cools the traction chain element 25. The fourth heat exchanger 4 functions as an evaporator and cools the interior airflow Fi. The vehicle passenger compartment is thus cooled.

[0143] The sixth connection point 16 is a point of separation of the first flow Qrl of refrigerant into two distinct flows Qr2, Qr3. The fourth connection point 14 is a point of regrouping of the flow Qr2 of refrigerant from the third heat exchanger 3 and the flow Qr3 of refrigerant from the fourth heat exchanger 4. The first expansion valve 21 directs the refrigerant from the first exchanger 1 to the second exchanger 2 and blocks the circulation of refrigerant to the fifth connection point 15. The second expansion valve 22 directs the refrigerant from the sixth connection point 16 to the third exchanger 3 and blocks the circulation of refrigerant between the first connection point 11 and the second connection point 12. The high-pressure refrigerant from the first heat exchanger 1 reaches the sixth connection point 16 without undergoing expansion. The high-pressure refrigerant is expanded in parallel by the second expansion valve 22 and by the third expansion valve 23.

[0144] Fig. 4 schematically illustrates a method of operation of the thermal conditioning system 100, in a second operating mode called "heat pump and energy recovery". In this second mode of operation, a flow Qr of refrigerant circulates in the compression device 7 where it passes to high pressure, and circulates successively in the first exchanger 1 where it gives up heat, in the first expansion valve 21 where it undergoes expansion and passes to a low pressure lower than the high pressure, in the first heat exchange section 2A of the second exchanger 2 where it evaporates at least in part, in the first bypass branch B, in the second expansion valve 22 without undergoing expansion, in the third exchanger 3 where it evaporates at least in part, then in the second refrigerant storage device 6 and returns to the compressor 7.

[0145] The evaporation of the refrigerant is distributed between the first heat exchange section 2A of the second heat exchanger 2 and the third heat exchanger 3. Part of the low-pressure refrigerant evaporates in the first heat exchange section 2A of the second heat exchanger 2. The part not evaporated in the second heat exchanger 2, still in liquid form, evaporates in the third heat exchanger 3.

[0146] In this second mode of operation: - The refrigerant flow rate in the first refrigerant accumulation device 5 is zero. - The flow rate of refrigerant fluid in the second heat exchange section 2B of the second exchanger 2 is zero. - The refrigerant flow rate in the second bypass branch C is zero.

[0147] In this operating mode, the second heat exchanger 2 functions as a refrigerant evaporator. Only the first heat exchange section 2A carries the refrigerant, and the second heat exchange section 2B of the second heat exchanger 2 does not perform any heat exchange. The evaporated refrigerant does not circulate in the first storage device 5, which limits the pressure drop in the low-pressure part of the refrigerant circuit. The second heat exchanger 2 can thus operate with a lower evaporation pressure, allowing an increase in the heat recovered from the outside airflow Fe. The circulation of the refrigerant fluid in the second exchanger 2 is schematically represented by the symbol Cl, on part A of [Fig. 10]. The refrigerant fluid from outlet 2A_O of the first heat exchange section 2A does not circulate in the first storage device 5, and is directed to the first branch of bypass B.

[0148] The first heat exchanger 1 heats the vehicle's passenger compartment by recovering thermal energy from the outside airflow at the second heat exchanger 2 and by recovering thermal energy from the traction chain element 25 at the third heat exchanger 3. When an electric heating device 26 is available on the heat transfer fluid circuit 40, the third heat exchanger 3 can also recover the heat dissipated by the electric heater 26. The fourth exchanger 4 does not perform heat exchange.

[0149] The first expansion valve 21 directs the refrigerant from the first heat exchanger 1 to the second heat exchanger 2 and blocks the circulation of refrigerant to the fifth connection point 15. The second expansion valve 22 allows the refrigerant from the first connection point 11 to flow in the first branch branch B to the second connection point 12, and directs it to the third exchanger 3. The circulation of refrigerant between the sixth connection point 16 and the second connection point 12 is blocked. In steady state, the refrigerant flow rate is the same in the first exchanger 1, in the first heat exchange section 2A of the second exchanger 2 and in the third exchanger 3. The refrigerant fluid from the first exchanger 1 is expanded by the first expansion valve 21.

[0150] Fig. 5 schematically illustrates a method of operation of the thermal conditioning system 100, in a third operating mode called "first dehumidification mode". In this third mode of operation, a flow Qr of refrigerant circulates in the compression device 7 where it passes to high pressure, and circulates successively in the first exchanger 1 where it gives up heat, in the first expansion valve 21 where it undergoes expansion and passes to an intermediate pressure lower than the high pressure, in the first heat exchange section 2A of the second exchanger 2, in the first storage device 5, in the second heat exchange section 2B of the second exchanger 2, in the third bypass branch D, in the third expansion valve 23 where it undergoes expansion and passes to a low pressure lower than the intermediate pressure, in the fourth exchanger 4 where it evaporates, then in the second refrigerant storage device 6 and returns to the compressor 7.

[0151] In this third mode of operation: - The flow rate of refrigerant fluid in the first branch of bypass B is zero. - The flow rate of refrigerant fluid in the third exchanger 3 is zero. - The refrigerant flow rate in the portion of the main loop A between the sixth connection point 16 and the fourth connection point 14 is zero. - The refrigerant flow rate in the portion of the second branch C between the third connection point 13 and the fifth connection point 15 is zero. - The total refrigerant flow circulates in the first accumulation device 5. The second heat exchange section 2B of the second exchanger 2 performs a subcooling of the refrigerant condensed in the first heat exchange section 2A of the second exchanger 2.

[0152] In this operating mode, the fourth exchanger 4 cools the interior airflow Fi. The first exchanger 1 heats the interior airflow Fi, which allows the interior airflow Fi to be dehumidified. The second heat exchanger 2 operates as an intermediate-pressure refrigerant condenser, and allows for subcooling of the refrigerant. The refrigerant circulation in the second heat exchanger 2 corresponds to part A of [Fig. 10]. The level of expansion achieved by the first expansion valve 21 allows the amount of heat dissipated in the outside air flow Fe to be adjusted at the level of the second exchanger 2. The third exchanger 3 is inactive.

[0153] The first expansion valve 21 directs the refrigerant from the first heat exchanger 1 to the second heat exchanger 2 and blocks the circulation of refrigerant to the fifth connection point 15. The second expansion valve 22 blocks the circulation of refrigerant between the sixth connection point 16 and the third exchanger 3, and jointly blocks the circulation of refrigerant in the first branch of bypass B, between the first connection point 11 and the second connection point 12. In steady state, the refrigerant flow rate is the same in the first heat exchanger 1, in the first heat exchange section 2A of the second heat exchanger 2, in the second heat exchange section 2B of the second heat exchanger 2 and in the third heat exchanger 3. The high-pressure refrigerant fluid from the first exchanger 1 is expanded a first time by the first expansion valve 21, then a second time by the third expansion valve 23.

[0154] Fig. 6 schematically illustrates a method of operation of the thermal conditioning system 100, in a fourth operating mode called "second dehumidification mode". In this fourth operating mode, a first flow Qrl of refrigerant circulates in the compression device 7 where it is at high pressure, and circulates successively in the first heat exchanger 1 where it releases heat, in the first expansion valve 21 where it undergoes expansion and passes to an intermediate pressure lower than the high pressure, in the second bypass branch C, and divides into: - a second flow Qr2 of refrigerant circulating in the second bypass branch C, successively in the third expansion valve 23 where it undergoes expansion and passes to a low pressure lower than the intermediate pressure, then in the fourth heat exchanger 4 where it evaporates, and - a third flow Qr3 of refrigerant circulating in the third branch of bypass D, then in the second expansion valve 22 where it undergoes expansion and passes to low pressure, then in the third exchanger 3 where it evaporates, and joins the refrigerant from the fourth exchanger 4. The total flow formed circulates in the second accumulation device 6 and returns to the compressor 7.

[0155] In this fourth mode of operation: - The flow rate of refrigerant fluid in the second exchanger 2 is zero. - The flow rate of refrigerant fluid in the first branch of bypass B is zero. - The refrigerant flow rate in the portion of the main loop A between the third connection point 13 and the sixth connection point 16 is zero.

[0156] In this operating mode, the fourth heat exchanger 4 functions as an evaporator and cools the interior airflow Fi. The first heat exchanger 1 functions as a high-pressure refrigerant condenser and heats the interior airflow Fi. The interior airflow Fi is thus dehumidified. The second exchanger 2 is not traversed by the refrigerant fluid, and is thermally inactive. The third exchanger 3 operates as a low-pressure refrigerant fluid evaporator, and allows heat to be recovered from the heat transfer fluid.

[0157] The fifth connection point 15 is a point of separation of the first flow Qrl of refrigerant into two distinct flows Qr2, Qr3. The flow Qr2 circulates in the second branch of bypass C towards the third expansion valve 23. The flow Qr3 circulates in the third branch of bypass D towards the sixth connection point 16. The fourth connection point 14 is a regrouping point of the flow Qr2 of refrigerant from the third heat exchanger 3 and the flow Qr3 of refrigerant from the fourth heat exchanger 4. The first expansion valve 21 directs the refrigerant from the first exchanger 1 to the fifth connection point 15 and blocks the circulation of refrigerant in the main loop A towards the second exchanger 2. The second expansion valve 22 directs the refrigerant from the sixth connection point 16 to the third exchanger 3 and blocks the circulation of refrigerant between the first connection point 11 and the second connection point 12. The flow rate of refrigerant circulating in the fourth exchanger 4 is lower than the flow rate circulating in the first exchanger 1, due to the separation carried out at the fifth connection point 15. The high-pressure refrigerant from the first heat exchanger 1 is expanded to an intermediate pressure by the first expansion valve 21. The intermediate-pressure refrigerant is expanded in parallel by the third expansion valve 23 and the second expansion valve 22.

[0158] The direction of circulation of the refrigerant fluid in the third branch of the bypass D is reversed compared to the direction of circulation of the previous third operating mode.

[0159] Figure 7 schematically illustrates a method of operation of the conditioning system thermal 100, in a fifth operating mode called "third dehumidification mode". In this fifth mode of operation, a flow Qr of refrigerant circulates in the compression device 7 where it passes to high pressure, and circulates successively in the first exchanger 1 where it gives up heat, in the first expansion valve 21 where it undergoes expansion and passes to an intermediate pressure lower than the high pressure, then in the second bypass branch C, successively in the third expansion valve 23 where it undergoes expansion and passes to a low pressure lower than the intermediate pressure, in the fourth exchanger 4 where it evaporates, then in the second storage device 6, and returns to the compressor 7.

[0160] In this fifth mode of operation: - The flow rate of refrigerant fluid in the second exchanger 2 is zero. - The flow rate of refrigerant fluid in the first branch of bypass B is zero. - The flow rate of refrigerant fluid in the third exchanger 3 is zero. - The refrigerant flow rate in the third branch of the bypass D is zero.

[0161] In this operating mode, the first heat exchanger 1 heats the interior airflow Fi, and the fourth heat exchanger 4 cools the interior airflow Fi, thereby dehumidifying the interior airflow Fi. The second exchanger 2 and the third exchanger 3 are not traversed by the refrigerant fluid, and are both thermally inactive.

[0162] The first expansion valve 21 directs the refrigerant from the first heat exchanger 1 to the fifth connection point 15 and blocks the circulation of refrigerant in the main loop A towards the second heat exchanger 2. The second expansion valve 22 blocks the circulation of refrigerant between the sixth connection point 16 and the third exchanger 3, and jointly blocks the circulation of refrigerant in the first branch of bypass B, between the first connection point 11 and the second connection point 12. In steady state, the refrigerant flow rate is the same in the first exchanger 1 and in the fourth exchanger 4. The high-pressure refrigerant fluid from the first exchanger 1 is expanded a first time by the first expansion valve 21, then a second time by the third expansion valve 23.

[0163] Fig. 8 schematically illustrates a method of operation of the thermal conditioning system 100, in a sixth operating mode called "energy recovery". In this sixth mode of operation, a flow Qr of refrigerant fluid circulates in the compression device 7 where it passes to high pressure, and circulates successively in the first exchanger 1 where it gives up heat, in the first expansion valve 21 without undergoing expansion, in the second bypass branch C, in the third bypass branch D, in the second expansion valve 22 where it undergoes expansion and passes to a low pressure lower than the high pressure, in the third exchanger 3 where it evaporates, then in the second storage device 6 and returns to the compressor 7.

[0164] In this sixth mode of operation: - The flow rate of refrigerant fluid in the second exchanger 2 is zero. - The flow rate of refrigerant fluid in the first branch of bypass B is zero. - The flow rate of refrigerant fluid in the fourth exchanger 4 is zero.

[0165] In this operating mode, the first heat exchanger 1 heats the interior airflow Fi, and thus the vehicle's passenger compartment. The thermal energy dissipated by the traction chain element 25 is recovered at the third heat exchanger 3. The second heat exchanger 2 and the fourth heat exchanger 4 do not carry the refrigerant and are thermally inactive. In steady state, the refrigerant flow rate is the same in the first exchanger 1 and in the third exchanger 3.

[0166] The first expansion valve 21 directs the refrigerant from the first heat exchanger 1 to the fifth connection point 15 and blocks the circulation of refrigerant in the main loop A to the second heat exchanger 2. The second expansion valve 22 directs the refrigerant from the sixth connection point 16 to the third exchanger 3 and blocks the circulation of refrigerant between the first connection point 11 and the second connection point 12. The refrigerant fluid from the first exchanger 1 is expanded by the second expansion valve 22. Many other operating modes of the thermal conditioning system, not described, are of course possible.

Claims

Demands

1. A thermal conditioning system (100) for a motor vehicle, comprising a refrigerant circuit (10) configured for circulating a refrigerant, the refrigerant circuit (10) comprising: - a main loop (A) comprising successively, according to the direction of refrigerant flow: — a compressor (7), — a first heat exchanger (1) thermally coupled to an interior airflow (Fi) to a passenger compartment of a motor vehicle, — a first expansion valve (21), — a second heat exchanger (2) thermally coupled to an exterior airflow (Fe) to the passenger compartment of the motor vehicle, the second heat exchanger (2) comprising successively: — a first heat exchange section (2A), — a first refrigerant accumulation device (5), — a second heat exchange section (2B), — a second expansion valve (22), — a third heat exchanger (3),- a first branch branch (B) connecting a first connection point (11) located on the main loop (A) downstream of the first heat exchange section (2A) of the second heat exchanger (2) and upstream of the first refrigerant fluid accumulation device (5) to a second connection point (12) located on the main loop (A) downstream of the second heat exchange section (2B) of the second heat exchanger (2) and upstream of the third heat exchanger (3).

2. Thermal conditioning system (100) according to claim 1, comprising: - a second branch (C) connecting a third connection point (13) located on the main loop (A) downstream of the first heat exchanger (1) and upstream of the first heat exchange section (2A) of the second heat exchanger (2) to a fourth connection point (14) located on the main loop (A) downstream of the third heat exchanger (3) and upstream of the compressor (7), the second branch (C) comprising a third expansion valve (23) and a fourth heat exchanger (4) configured to exchange heat with the indoor airflow (Fi), - a third branch branch (D) connecting a fifth connection point (15) disposed on the second branch branch (C) between the third connection point (13) and the third expansion valve (23) to a sixth connection point (16) disposed on the main loop (A) downstream of the second heat exchange section (2B) of the second exchanger (2) and upstream of the second connection point (12).

3. Thermal conditioning system (100) according to claim 1 or 2, wherein the main loop (A) includes a second accumulation device (6) disposed downstream of the third exchanger (3) and upstream of an inlet (7a) of the compressor (7).

4. Thermal conditioning system (100) according to any one of the preceding claims in combination with claim 2, wherein the first expansion valve (21) is jointly arranged on the main loop (A) and on the second branch (C), and is configured to: - expand the refrigerant from the first heat exchanger (1), - selectively direct the expanded refrigerant either to the first heat exchange section (2A) of the second heat exchanger (2), or to the fifth connection point (15).

5. Thermal conditioning system (100) according to any one of the preceding claims in combination with claim 2, wherein the second expansion valve (22) is jointly disposed on the main loop (A) and on the first branch (B), and is configured to: - either expand the refrigerant from the sixth connection point (16) and direct the expanded refrigerant to the third heat exchanger (3), jointly blocking the refrigerant flow in the first branch (B), - or permit refrigerant flow in the first branch (B) to the third heat exchanger (3), and jointly blocking the refrigerant flow between the sixth connection point (16) and the third heat exchanger (3).

6. Thermal conditioning system (100) according to any one of the preceding claims, wherein the third heat exchanger (3) is thermally coupled with an element (25) of an electric drive chain of the vehicle.

7. Thermal conditioning system (100) according to any one of the preceding claims in combination with claim 3, wherein the main loop (A) includes an internal exchanger (9) configured to permit heat exchange between: - the refrigerant circulating between the second heat exchange section (2B) of the second exchanger (2) and the second expansion valve (22), and - the refrigerant downstream of the second storage device (6) and upstream of an inlet (7a) of the compressor (7).

8. Thermal conditioning system (100) according to any one of the preceding claims, wherein the first heat exchange section (2A) of the second exchanger (2) and the second heat exchange section (2B) of the second exchanger (2) are arranged one above the other.

9. Thermal conditioning system (100) according to any one of the preceding claims, wherein the first heat exchange section (2A) of the second exchanger (2) comprises a refrigerant inlet (2A-I) and a refrigerant outlet (2A_O), and wherein the refrigerant inlet (2A_I) of the first heat exchange section (2A) of the second exchanger (2) and the refrigerant outlet (2A_O) of the first heat exchange section (2A) of the second exchanger (2) are arranged on the same face (F2) of the second exchanger (2).

10. Thermal conditioning system (100) according to the preceding claim, wherein the second heat exchange section (2B) of the second heat exchanger (2) comprises a refrigerant inlet (2B-I) and a refrigerant outlet (2B_O), and wherein: - the refrigerant inlet (2B-I) of the second heat exchange section (2B) of the second heat exchanger (2) and the refrigerant outlet (2B_O) of the second heat exchange section (2B) of the second heat exchanger (2) are disposed on opposite faces (F2, F3) of the second heat exchanger (2), and - the refrigerant outlet (2A_O) of the first heat exchange section (2A) of the second heat exchanger (2) and the refrigerant inlet (2B-I) of the second heat exchange section thermal (2B) of the second exchanger (2) are arranged on the same face of the second exchanger (2).

11. A method of operating a thermal conditioning system according to any one of claims 1 to 10 in combination with claim 3, in a first operating mode called "passenger compartment and battery cooling" in which: - a first flow (Qrl) of refrigerant circulates in the compression device (7) where it passes through a high pressure, and circulates successively in the first heat exchanger (1) without releasing heat, in the first expansion valve (21) without undergoing expansion, in the first heat exchange section (2A) of the second heat exchanger (2), in the first accumulation device (5), in the second heat exchange section (2B) of the second heat exchanger (2), and divides into: — a second flow (Qr2) of refrigerant circulating in the main loop (A), in the second expansion valve (22) where it undergoes expansion and passes through a low pressure lower than the high pressure, then in the third heat exchanger (3) where it evaporates,— a third flow (Qr3) of refrigerant circulating in the third bypass branch (D), then in the third expansion valve (23) where it undergoes expansion and passes to low pressure, then in the fourth heat exchanger (4) where it evaporates, and rejoins the refrigerant from the third heat exchanger (3), the total flow formed circulates in the second accumulation device (6) and returns to the compressor (7).

12. A method of operating a thermal conditioning system according to any one of claims 1 to 10 in combination with claim 3, in a second operating mode called "heat pump and energy recovery" in which: - a flow (Qr) of refrigerant circulates in the compression device (7) where it passes through a high pressure, and circulates successively in the first heat exchanger (1) where it releases heat, in the first expansion valve (21) where it undergoes expansion and passes through a low pressure lower than the high pressure, in the first heat exchange section (2A) of the second heat exchanger (2) where it evaporates at least partially, in the first bypass branch (B), in the second expansion valve (22) without undergoing expansion, in the third heat exchanger (3) where it evaporates at least partially

13.

14. part, then in the second refrigerant accumulation device (6) and returns to the compressor (7). A method for operating a thermal conditioning system according to any one of claims 1 to 10 in combination with claim 3, in a third operating mode referred to as the "first dehumidification mode" in which: - a flow (Qr) of refrigerant fluid circulates in the compression device (7) where it passes to high pressure, and circulates successively in the first exchanger (1) where it gives up heat, in the first expansion valve (21) where it undergoes expansion and passes to an intermediate pressure lower than the high pressure, in the first heat exchange section (2A) of the second exchanger (2), in the first accumulation device (5), in the second heat exchange section (2B) of the second exchanger (2), in the third bypass branch (D), in the third expansion valve (23) where it undergoes expansion and passes to a low pressure lower than the intermediate pressure, in the fourth exchanger (4) where it evaporates, then in the second accumulation device (6) of refrigerant fluid and returns to the compressor (7). Method of operating a thermal conditioning system according to any one of claims 1 to 10 in combination with claim 3, in a fourth operating mode referred to as the "second dehumidification mode" in which: - a first flow (Qrl) of refrigerant circulates in the compression device (7) where it passes through high pressure, and circulates successively in the first exchanger (1) where it releases heat, in the first expansion valve (21) where it undergoes expansion and passes through an intermediate pressure lower than the high pressure, in the second bypass branch (C), and divides into: — a second flow (Qr2) of refrigerant circulating in the second bypass branch (C), successively in the third expansion valve (23) where it undergoes expansion and passes to a low pressure lower than the intermediate pressure, then in the fourth exchanger (4) where it evaporates, — a third flow (Qr3) of refrigerant circulating in the third bypass branch (D), then in the second expansion valve (22) where it undergoes expansion and passes to low pressure, then in the third exchanger (3) where it evaporates, and joins the refrigerant from the fourth exchanger (4), the total flow formed circulates in the second accumulation device (6) and returns to the compressor (7).

15. A method of operating a thermal conditioning system according to any one of claims 1 to 10 in combination with claim 3, in a fifth operating mode called the "third dehumidification mode" in which: - a flow (Qr) of refrigerant fluid circulates in the compression device (7) where it passes to high pressure, and circulates successively in the first exchanger (1) where it gives up heat, in the first expansion valve (21) where it undergoes expansion and passes to an intermediate pressure lower than the high pressure, then in the second bypass branch (C), successively in the third expansion valve (23) where it undergoes expansion and passes to a low pressure lower than the intermediate pressure, in the fourth exchanger (4) where it evaporates, then in the second accumulation device (6), and returns to the compressor (7).

16. A method of operating a thermal conditioning system according to any one of claims 1 to 10 in combination with claim 3, in a sixth operating mode called "energy recovery" in which: - a flow (Qr) of refrigerant fluid circulates in the compression device (7) where it passes to high pressure, and circulates successively in the first exchanger (1) where it gives up heat, in the first expansion valve (21) without undergoing expansion, in the second bypass branch (C), in the third bypass branch (D), in the second expansion valve (22) where it undergoes expansion and passes to a low pressure lower than the high pressure, in the third exchanger (3) where it evaporates, then in the second accumulation device (6) and returns to the compressor (7).

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