WO2024160823A1 - Thermal conditioning system - Google Patents

Abstract

The invention relates to a thermal conditioning system (100) for a motor vehicle, comprising a refrigerant circuit (10) comprising: - a main loop (A) comprising, successively: -- a compressor (7), -- a first exchanger (1) thermally coupled with an internal air flow (Fi) to a passenger compartment of the vehicle, -- a first expansion valve (31), -- a second expansion valve (32), -- a second exchanger (2) thermally coupled with an external air flow (Fe) to the passenger compartment of the vehicle, -- a refrigerant accumulation device (8), -- a first bypass branch (B) of the main loop (A), which branch comprises a third expansion valve (33), -- a second bypass branch (C) of the main loop (A), which branch comprises successively a fourth expansion valve (34) and a third exchanger (3), wherein the main loop (A) comprises an internal exchanger (6) configured to allow heat to be exchanged between the refrigerant circulating between the first expansion valve (31) and the second expansion valve (32) and the refrigerant downstream of the accumulation device (8) and upstream of an inlet (7a) of the compressor (7).

Description

Description

Title: THERMAL CONDITIONING SYSTEM

Technical area

[1] 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 parts of the vehicle, such as the passenger compartment or an electrical energy storage battery, when the vehicle is electrically powered. Heat exchanges are managed mainly by the compression and expansion of a refrigerant fluid circulating in a circuit in which several heat exchangers are arranged. A compressor discharges the refrigerant fluid in a high pressure state and allows circulation of the refrigerant fluid in the circuit.

Prior art

[2] So-called chemical refrigerants generally have a high global warming potential (GWP coefficient), which is a disadvantage. It is possible to use carbon dioxide as a refrigerant, which by definition has a global warming coefficient equal to one. The thermodynamic properties of this gas mean that the compressor discharge pressure is generally in the range 80 to 130 bar, so that the system provides sufficient thermal power. The discharge temperature of the refrigerant for this pressure range can in certain cases of use be problematic for the compressor, because it is too high. In addition, this high discharge temperature can also be annoying for certain organs in which the refrigerant fluid at high pressure and high temperature circulates.

[3] In addition, in the case of an electric vehicle, it may be necessary to be able to heat the battery, in particular in order to be able to charge it quickly in cold ambient temperatures, particularly negative ones. Dedicated heaters can be used. Such dedicated devices increase the price and weight of the thermal conditioning system. [4] There is therefore a need to have a thermal conditioning system making it possible to control the discharge temperature of the refrigerant fluid and making it possible to heat the battery.

Summary

[5] For this purpose, a thermal conditioning system for a motor vehicle is proposed, comprising a refrigerant fluid circuit configured to circulate a refrigerant fluid, the refrigerant fluid circuit comprising:

A main loop comprising successively according to the direction of circulation of the refrigerant fluid: -- a compressor,

-- a first heat exchanger thermally coupled with an interior air flow to a passenger compartment of the vehicle,

-- a first regulator,

-- a second regulator,

-- a second heat exchanger configured to exchange heat with an air flow outside the vehicle passenger compartment,

-- a refrigerant accumulation device,

A first branch branch connecting a first connection point arranged on the main loop downstream of an outlet of the compressor and upstream of the first exchanger to a second connection point arranged on the main loop downstream of the second heat exchanger and upstream upstream of the accumulation device, the first branch comprising a third regulator,

- A second bypass branch connecting a third connection point arranged on the main loop between the first exchanger and the second expansion valve to a fourth connection point arranged on the main loop downstream of the second exchanger and upstream of the accumulation device, the second bypass branch successively comprising a fourth expansion valve and a third heat exchanger, in which the main loop comprises an internal exchanger configured to allow heat exchange between the refrigerant fluid circulating between the first expansion valve and the second expansion valve and the refrigerant fluid downstream of the accumulation device and upstream of a compressor inlet.

[6] In some operating modes of the thermal conditioning system, the refrigerant circulating between the first expansion valve and the second expansion valve circulates from the first expansion valve to the second expansion valve.

[7] According to other modes of operation, the refrigerant fluid circulating between the first expander and the second expander circulates from the second expander to the first expander.

[8] This refrigerant circuit architecture allows heat to be transferred to the indoor air flow at the first heat exchanger and selectively absorb heat or transfer heat to the outdoor air flow at the second exchanger, by controlling the pressure at the inlet of the second exchanger. The second exchanger can selectively absorb a controlled amount of heat from the ambient air, or transfer a controlled amount of heat to the ambient air. In both cases, the efficiency of the internal heat exchanger can also be controlled, which allows the compressor discharge temperature to be controlled.

[9] The characteristics listed in the following paragraphs can be implemented independently of each other or in all technically possible combinations:

[10] According to one embodiment, the first heat exchanger is configured to exchange heat with an air flow inside a passenger compartment of the vehicle.

[11] According to a variant embodiment, the first heat exchanger is configured to exchange heat with a heat transfer liquid circulating in a closed heat transfer liquid circuit, the heat transfer liquid circuit comprising a heat exchanger configured to exchange heat with a flow of air inside the passenger compartment of the vehicle.

[12] The internal heat exchanger comprises a first heat exchange section arranged on the main loop between the first expander and the second expander, as well as a second heat exchange section arranged on the main loop downstream of the accumulator and upstream of the compressor inlet.

The internal heat exchanger is configured to enable heat exchange between the refrigerant in the first heat exchange section and the refrigerant in the second heat exchange section.

[13] According to one embodiment, the third heat exchanger is thermally coupled with an element of an electric drive chain of a motor vehicle.

[14] The third heat exchanger makes it possible to selectively cool or heat the element of the vehicle's electric powertrain.

[15] According to an exemplary embodiment, the element of the electric traction chain of the vehicle comprises an electrical energy storage battery.

[16] Alternatively or additionally, the element of the electric drive chain of the vehicle comprises an electric traction motor of the vehicle.

[17] Alternatively or additionally, the element of the electric traction chain of the vehicle comprises an electronic unit for controlling the electric traction motor of the vehicle.

[18] According to an exemplary embodiment, the third heat exchanger is thermally coupled with the element of the electric traction chain via a heat transfer liquid circulating in a heat transfer liquid circuit.

[19] The first regulator is for example an electronic regulator. Likewise, the second regulator, the third regulator, the fourth regulator can be electronic expansion valves.

[20] According to one embodiment, the thermal conditioning system comprises:

- A third branch branch connecting a fifth connection point arranged on the main loop between the second regulator and the first regulator to a sixth connection point arranged on the main loop between the second connection point and the fourth connection point, the third branch of diversion successively comprising a fifth expansion valve and a fourth heat exchanger configured to exchange heat with the interior air flow.

[21] The fourth heat exchanger can cool the air flow inside the passenger compartment, so as to cool the passenger compartment.

[22] In this embodiment, the refrigerant circuit may comprise a first one-way valve arranged on the main loop between the sixth connection point and the fourth connection point.

The first one-way valve is configured to allow circulation of refrigerant fluid from the sixth connection point to the fourth connection point and configured to prohibit circulation of refrigerant fluid from the fourth connection point to the sixth connection point.

[23] The first one-way valve is for example a non-return valve.

[24] According to another embodiment, the thermal conditioning system comprises:

- A third branch branch connecting a fifth connection point arranged on the second branch branch between the third connection point and the fourth regulator to a sixth connection point arranged on the second branch branch between the third exchanger and the fourth point connection, the third branch branch successively comprising a fifth regulator and a fourth heat exchanger configured to exchange heat with the interior air flow.

[25] With this arrangement of the third branch of diversion, the fourth heat exchanger can selectively cool the flow of air inside the passenger compartment or heat this flow of interior air.

[26] The fourth exchanger is arranged upstream of the first exchanger in a direction of flow of the interior air flow.

[27] In this embodiment, the refrigerant fluid circuit comprises a first one-way valve arranged on the third branch branch between the fourth exchanger and the sixth connection point. The first one-way valve is configured to allow circulation of refrigerant from the fifth connection point to the sixth connection point and configured to prohibit circulation of refrigerant from the sixth connection point to the fifth connection point.

[28] According to one embodiment, the thermal conditioning system comprises:

- A fourth branch branch connecting a seventh connection point located on the main loop downstream of the first connection point and upstream of the first exchanger to an eighth connection point located on the second branch branch downstream of the fourth regulator and further upstream of the fourth connection point, the fourth branch branch comprising a sixth regulator.

[29] The fourth branch of diversion allows the high pressure and high temperature refrigerant fluid leaving the compressor to return to the compressor inlet without passing through the first exchanger or the second exchanger. The fourth branch of diversion brings the refrigerant fluid at high pressure to the inlet of the accumulator. The flow circulating in the fourth branch of diversion makes it possible to increase the total flow of refrigerant fluid supplied by the compressor and thus increase the thermal heating power supplied by the refrigerant fluid.

[30] According to an alternative embodiment of the thermal conditioning system, the eighth connection point is arranged downstream of the third exchanger.

[31] According to another alternative embodiment, the eighth connection point is arranged upstream of the third exchanger.

[32] According to yet another alternative embodiment, the thermal conditioning system comprises a fourth branch branch connecting a seventh connection point arranged on the main loop downstream of the first connection point and upstream of the first exchanger to an eighth point connection arranged on the main loop downstream of the fourth connection point and upstream of the accumulation device, the fourth branch branch comprising a sixth regulator. [33] According to one embodiment, the thermal conditioning system comprises:

- A fifth branch branch connecting a ninth connection point arranged on the second branch branch downstream of the third exchanger and upstream of the fourth connection point to a tenth connection point located on the main loop between the third connection point and the second regulator.

[34] According to an alternative embodiment of the thermal conditioning system, the tenth connection point is arranged between the first regulator and the internal exchanger.

[35] According to an alternative embodiment of the thermal conditioning system, the tenth connection point is arranged between the internal exchanger and the second regulator.

[36] The refrigerant circuit comprises a second one-way valve disposed on the fifth branch. The second one-way valve is configured to allow refrigerant flow from the ninth connection point to the tenth connection point and configured to prohibit refrigerant flow from the tenth connection point to the ninth connection point.

[37] The fifth branch of diversion allows the refrigerant fluid at high pressure or intermediate pressure leaving the third exchanger to join the main loop and from there reach the inlet of the compressor. The fifth branch of diversion thus allows the refrigerant fluid to provide heat to the element of the electric traction chain at the level of the third exchanger, that is to say allows heating of the element of the chain electric traction.

[38] The second one-way valve is for example a check valve.

[39] The ninth connection point can be confused with the sixth connection point. [40] According to one embodiment of the thermal conditioning system, the second branch branch comprises a seventh regulator disposed between the ninth connection point and the fourth connection point.

[41] The seventh expansion valve allows the refrigerant fluid coming from the third exchanger to be expanded before it mixes with the refrigerant fluid leaving the fourth exchanger. The fourth exchanger can therefore operate at a higher pressure than that of the third exchanger, therefore at a higher temperature.

[42] When the fourth branch is present, the seventh regulator is arranged between the ninth connection point and the eighth connection point.

[43] According to an exemplary embodiment of the thermal conditioning system, the fifth branch of diversion comprises an eighth regulator.

[44] The eighth expander makes it possible to expand the refrigerant fluid coming from the third exchanger before entering the first heat exchange section of the internal exchanger, and therefore to control the heat exchange in the internal exchanger.

[45] The eighth regulator is for example a calibrated orifice.

[46] According to one embodiment, the first regulator is arranged between the first exchanger and the third connection point.

[47] According to another embodiment, the first regulator is arranged between the tenth connection point and the third connection point.

[48] The refrigerant circuit may include a third one-way valve arranged on the main loop between the first exchanger and the third connection point.

The third one-way valve is configured to allow circulation of refrigerant fluid from the first exchanger to the third connection point and configured to prohibit circulation of refrigerant fluid from the third connection point to the first exchanger. [49] The third one-way valve is for example a non-return valve.

[50] The main loop comprises a first shut-off valve disposed between the first connection point and the first heat exchanger.

[51] The first shut-off valve is arranged between the first connection point and the seventh connection point.

[52] The main loop includes a second shut-off valve disposed between the second connection point and the fourth connection point.

[53] The second stop valve is arranged between the second connection point and the sixth connection point.

[54] The first shut-off valve is an electrically operated valve.

The second shut-off valve is an electrically operated valve.

[55] The first shut-off valve is a two-way valve. Likewise, the second shut-off valve is a two-way valve.

[56] According to one embodiment, the thermal conditioning system comprises a refrigerant distribution module comprising:

- a first refrigerant fluid inlet,

- a second refrigerant fluid inlet,

- a first refrigerant outlet,

- a second refrigerant fluid outlet,

- a first channel connecting the first input to the first output,

- a second channel connecting the second input to a connection point arranged on the first channel between the first input and the first output,

- a third channel connecting the second output to the connection point,

- a seventh regulator placed on the first channel between the connection point and the first outlet,

- a one-way valve arranged on the second channel between the connection point and the second outlet, in which: the first channel partly forms the second branch of diversion, the second channel partly forms the third branch of diversion, the third channel partly forms the fifth branch of diversion.

[57] The integration of certain components and part of the refrigerant circulation circuit in the form of a distribution module makes it possible to facilitate the mechanical integration of the components and to reduce the overall size.

[58] The channels of the refrigerant distribution module module are formed by internal recesses of a metal block.

[59] The refrigerant distribution module may include an eighth regulator placed on the third channel.

[60] According to another embodiment, the thermal conditioning system comprises a refrigerant distribution module comprising:

- a first refrigerant fluid inlet,

- a second refrigerant fluid inlet/outlet,

- a third refrigerant inlet/outlet,

- a first channel connecting the second input/output to the third input/output,

- a second channel connecting the first input to a connection point arranged on the first channel between the second input/output and the third input/output,

- the first regulator,

- a one-way valve arranged on the second channel between the first inlet and the connection point, in which: the first regulator is arranged on the first channel between the third inlet/outlet and the connection point, the first channel partly forms the main loop, the second channel partly forms the fifth branch.

[61] The channels of the refrigerant distribution module module are formed by internal recesses of a metal block.

[62] The refrigerant distribution module may include an eighth regulator placed on the second channel. [63] The invention also relates to a method of operating a thermal conditioning system as described above, in a mode known as passenger compartment dehumidification and battery cooling in which:

— a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and is divided between:

-- a second flow circulating in the main loop, successively in the first exchanger where it transfers heat to the interior air flow, in the first regulator where it passes at intermediate pressure,

-- a third flow circulating in the first branch of diversion, successively in the third regulator where it passes at intermediate pressure, in the second exchanger where it transfers heat to the outside air flow, in the second regulator, in the internal exchanger, and is divided between:

— a fourth flow circulating in the third branch, successively in the fifth regulator where it passes at low pressure, in the fourth exchanger where it receives heat from the interior air flow, in the main loop,

— a fifth flow circulating in the main loop and joining the second flow, the second flow and the fifth flow forming a sixth flow circulating in the second branch of diversion, successively in the fourth regulator where it passes at low pressure, in the third exchanger where it receives heat, and joins the fourth flow, the sixth flow and the fourth flow forming the total flow, the total flow formed circulates in the main loop, successively in the accumulation device, in the internal exchanger, and returns to the compressor.

[64] The intermediate pressure value is lower than the high pressure value.

[65] The low pressure value is lower than the intermediate pressure value.

[66] The invention also relates to a method of operating a thermal conditioning system as described previously, in a so-called mode of battery heating with energy recovery from outside air in which:

- a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates in the main loop, in the first exchanger, in the second branch of diversion, successively in the fourth expander where it passes at intermediate pressure, in the third heat exchanger where it transfers heat, in the fifth branch of diversion, in the main loop successively in the internal exchanger, in the second expander where it passes at low pressure, in the second exchanger where it receives heat heat from the outside air flow, in the accumulation device, in the internal exchanger, and returns to the compressor.

[67] In this operating mode, the total flow of refrigerant can transfer heat to the interior air flow at the level of the first exchanger.

[68] In this mode of operation, the total flow of refrigerant fluid can also circulate in the first exchanger without giving up heat to the interior air flow.

[69] The invention also relates to a method of operating a thermal conditioning system as already described, in a mode known as battery heating and passenger compartment heating with energy recovery from the outside air in which:

- a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates in the main loop, in the first exchanger where it transfers heat to the interior air flow, and is divided between:

-- a second flow circulating in the second branch of diversion, successively in the fourth regulator where it passes at intermediate pressure, in the third heat exchanger where it releases heat,

-- a third flow circulating in the third branch of diversion, successively in the fifth regulator where it passes at intermediate pressure, in the fourth heat exchanger where it transfers heat to the internal air flow, and joins the second flow, the second flow and the third flow forming the total flow, the total flow formed circulating in the fifth branch of diversion, in the main loop successively in the internal exchanger, in the second regulator where it passes at low pressure, into the second exchanger where it receives heat from the external air flow, into the accumulation device, into the internal exchanger, and returns to the compressor.

[70] The invention also relates to a method of operating a thermal conditioning system as described, in a so-called passenger compartment dehumidification mode with energy recovery from the outside air in which:

- a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates in the main loop, in the first exchanger where it transfers heat to the interior air flow, and is divided between:

-- a second flow circulating in the third branch, successively in the fifth expander where it passes at intermediate pressure, in the fourth heat exchanger where it receives heat from the interior air flow, in the main loop, in the seventh expander where it passes at low pressure,

-- a third flow circulating in the main loop, successively in the first expander, in the internal exchanger, in the second expander where it passes at low pressure, in the second heat exchanger where it receives heat from the outside air flow, and joins the second flow, the second flow and the third flow forming the total flow, the total flow formed circulating in the main loop A successively in the accumulation device, in the internal exchanger, and returns to the compressor.

[71] The fourth exchanger and the second exchanger both operate as an evaporator. At the level of the fourth exchanger, the refrigerant fluid receives heat from the interior air flow, with the aim of cooling and dehumidifying it. At the level of the second exchanger, the refrigerant fluid receives heat from the exterior air flow, this heat contributing to heating the interior air flow at the level of the first exchanger. The pressure in the fourth exchanger can be higher than the pressure in the second exchanger, since the refrigerant fluid coming from the fourth exchanger undergoes expansion while passing through the seventh expander before joining the refrigerant fluid coming from the second exchanger. The evaporation temperature in the fourth exchanger can therefore be higher than that in the second interchange. It is therefore possible to recover heat at the level of the second exchanger even in a negative ambient temperature, without risking icing up the fourth exchanger.

[72] The invention also relates to a method of operating a thermal conditioning system as previously described, in a mode known as accelerated heating of the passenger compartment and the battery in which:

- a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, circulates in the main loop and is divided between:

-- a second flow circulating in the main loop, in the first exchanger where it transfers heat to the interior air flow, in the second branch of diversion, successively in the fourth regulator where it passes at intermediate pressure, in the third heat exchanger where it gives up heat, in the seventh expansion valve where it passes at low pressure,

-- a third flow circulating in the fourth branch of diversion, in the sixth regulator where it undergoes an expansion, and joins the second flow, the second flow and the third flow thus forming the total flow, the total flow formed circulates in the loop main, successively in the accumulation device, in the internal exchanger and returns to the compressor.

[73] The invention also relates to a method of operating a thermal conditioning system as described above, in a so-called passenger compartment heating and energy recovery mode in which:

- a total flow of refrigerant fluid circulates in the compressor where it passes at high pressure, and circulates in the main loop, in the first exchanger where it transfers heat to the interior air flow, and is divided between:

-- a second flow circulating in the second branch of diversion, successively in the fourth regulator where it passes at a first intermediate pressure, in the third heat exchanger where it receives heat, in the seventh regulator where it passes at low pressure ,

-- a third flow circulating in the main loop, successively in the first regulator where it passes to a second intermediate pressure greater than or equal to the first intermediate pressure, in the internal exchanger, in the second regulator where it passes at low pressure, into the second exchanger where it receives heat from the outside air flow, and joins the second flow, the second flow and the third flow thus forming the total flow, the total flow formed circulates in the main loop, successively in the accumulation device, in the internal exchanger and returns to the compressor.

Brief description of the drawings

[74] Other characteristics, details and advantages will appear on reading the detailed description below, and on analyzing the appended drawings, in which:

[75] [Fig. 1] is a schematic view of a thermal conditioning system according to a first embodiment of the invention,

[76] [Fig. 2] is a schematic view of a thermal conditioning system according to a first variant of the first embodiment of the invention,

[77] [Fig. 3] is a schematic view of a thermal conditioning system according to a second variant of the first embodiment of the invention,

[78] [Fig. 4] is a schematic view of a thermal conditioning system according to a second embodiment of the invention,

[79] [Fig. 5] is a schematic view of a thermal conditioning system according to a first variant of the second embodiment of the invention,

[80] [Fig. 6] is a schematic view of a thermal conditioning system according to a second variant of the second embodiment of the invention,

[81] [Fig. 7] is a schematic view of a thermal conditioning system according to a third variant of the second embodiment of the invention,

[82] [Fig. 8] is a schematic view of a thermal conditioning system according to a fourth variant of the second embodiment of the invention,

[83] [Fig. 9] is a schematic view of the thermal conditioning system of Figure 1, operating in a first mode of operation, called passenger compartment dehumidification and battery cooling mode, [84] [Fig. 10] is a schematic view of the thermal conditioning system of Figure 4, operating in a second operating mode, called battery heating mode with energy recovery from the outside air,

[85] [Fig. 1 1 ] is a schematic view of the thermal conditioning system of Figure 5, operating in a third operating mode, called battery heating and passenger compartment heating mode with energy recovery from the outside air,

[86] [Fig. 12] is a schematic view of the thermal conditioning system of Figure 5, operating according to a fourth mode of operation, called passenger compartment dehumidification mode with energy recovery from the outside air,

[87] [Fig. 13] is a schematic view of the thermal conditioning system of Figure 4, operating in a fourth mode of operation, called accelerated heating mode of the passenger compartment and the battery,

[88] [Fig. 14] is a schematic view of the thermal conditioning system of Figure 4, operating in one mode, called passenger compartment heating and energy recovery mode.

Description of embodiments

[89] To make the figures easier to read, the different elements are not necessarily represented 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. This indexing aims to differentiate similar, but not identical, elements or parameters. This indexing does not imply a priority of one element, or parameter in relation to another and the names can be interchanged.

[90] In the description which follows, 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 circulation, or travel, of a fluid . Analogously, 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 circulation, or path, of the fluid considered. In the case of the refrigerant fluid circuit, the term "a first element is upstream of a second element" means that the refrigerant fluid successively travels through the first element, then the second element, without passing through the compression device. In other words, the refrigerant fluid leaves the compression device, possibly passes through one or more elements, then passes through the first element, then the second element, then returns to the compression device, possibly after passing through other elements.

[91] 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 or from the third element to the first element passes through the second element.

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

[93] The thermal conditioning system 100 which will be described comprises an electronic control unit 60 receiving information from different sensors measuring in particular the characteristics of the refrigerant fluid at various points of the circuit. The electronic control unit 60 also receives instructions issued by the occupants of the vehicle, such as for example the desired temperature inside the passenger compartment. The electronic control unit 60 can also receive instructions from other electronic subsystems, such as for example the electrical energy storage battery management system. The electronic control unit 60 implements control laws allowing the control of the different actuators, in order to ensure the control of the thermal conditioning system 100 so as to ensure the instructions received.

[94] A compression device 7, also called a compressor, allows a refrigerant fluid to circulate in a refrigerant circulation circuit 10. The compression device 7 can be an electric compressor, that is to say a compressor whose moving parts are driven by an electric motor. The compression device 7 comprises a suction side of the low-pressure refrigerant fluid, also called inlet 7a of the compression device, and a side delivery of the refrigerant fluid at high pressure, also called outlet 7b of the compression device 7. The internal moving parts of the compressor 7 pass the refrigerant fluid from a low pressure on the inlet side 7a to a high pressure on the outlet side 7b. After expansion in one or more expansion members and circulation in at least part of the circuit, the refrigerant fluid returns to inlet 7a of compressor 7 and begins a new thermodynamic cycle.

[95] The refrigerant fluid circuit 10 forms a closed circuit in which the refrigerant fluid can circulate. The refrigerant fluid circuit 10 is sealed when it is in a nominal operating state, that is to say without defects or leaks. Each connection point of circuit 10 allows the refrigerant fluid to pass into one or other of the circuit portions joining at this connection point. The distribution of the refrigerant fluid between the circuit portions joining at a connection point is done by adjusting the opening or closing of the stop valves, non-return valves or expansion devices included on each of these portions. In other words, each connection point is a means of redirecting the refrigerant fluid arriving at this connection point. Various shut-off valves and non-return valves thus make it possible to selectively direct the refrigerant fluid into the different branches of the refrigerant circuit, in order to ensure different operating modes, as will be described later.

[96] The refrigerant fluid used by the refrigerant fluid circuit 10 is here a natural fluid, such as R744. It is also possible to use a chemical refrigerant, such as R1234yf, or R134a.

[97] Each refrigerant expansion device, also called an expansion valve, can be an electronic expansion valve. In an electronic expansion valve, the passage section for passing the refrigerant fluid can be adjusted continuously between a closed position and a maximum open position. To do this, an electronic regulator control module controls an electric motor which moves a movable shutter controlling the passage section offered to the refrigerant fluid. In the closed position, also called the closed position, the circulation of refrigerant is interrupted, that is to say that the flow of refrigerant passing through the electronic expansion valve is zero. In the maximum open position, the refrigerant fluid passes through the regulator without undergoing expansion.

[98] The term interior air flow Fi means a flow of air intended for the passenger compartment of the motor vehicle. This interior air flow Fi can circulate in a heating, ventilation and/or air conditioning installation, frequently referred to by the English term “HVAC”, for “Heating, Ventilating and Air Conditioning”. This installation has not been shown in the various figures. A first motor-fan group, not shown, is placed in the heating, ventilation and/or air conditioning installation in order to increase, if necessary, the flow rate of the interior air flow Fi.

[99] By external air flow Fe we mean an air flow which is not intended for the passenger compartment of the vehicle. In other words, this air flow Fe remains outside the vehicle cabin. A second motor-fan group, also not shown, can be activated in order to increase if necessary the flow rate of the exterior air flow Fe. The air flow provided by the first as well as by the second motor-fan group can be adjusted in real time according to heat exchange needs, for example by the electronic unit 60 for controlling the thermal conditioning system 100.

[100] The term “first exchanger” is equivalent to the term “first heat exchanger”. Likewise, the term “internal exchanger” is equivalent to the term “internal heat exchanger”. The term “accumulation device” is equivalent to the term “refrigerant accumulation device”.

[101] The heat transfer liquid circuit(s) also form one or more closed and sealed circuits in which a heat transfer liquid can circulate.

[102] Figure 1 shows a thermal conditioning system 100 for a motor vehicle, comprising a refrigerant circuit 10 configured to circulate a refrigerant fluid.

The refrigerant circuit 10 includes:

A main loop A comprising successively according to the direction of circulation of the refrigerant fluid:

- a compressor 7, -- a first heat exchanger 1 thermally coupled with an interior air flow Fi to a passenger compartment of the vehicle,

-- a first regulator 31,

-- a second regulator 32,

-- a second heat exchanger 2 configured to exchange heat with an external air flow Fe to the passenger compartment of the vehicle,

-- a refrigerant fluid accumulation device 8,

A first branch B connecting a first connection point 11 arranged on the main loop A downstream of an outlet 7b of the compressor 7 and upstream of the first exchanger 1 to a second connection point 12 arranged on the main loop A downstream of the second heat exchanger 2 and upstream of the accumulation device 8, the first branch B comprising a third expansion valve 33,

- A second branch C connecting a third connection point 13 located on the main loop A between the first exchanger 1 and the second regulator 32 to a fourth connection point 14 located on the main loop A downstream of the second exchanger 2 and upstream of the accumulation device 8, the second branch C successively comprising a fourth regulator 34 and a third heat exchanger 3.

The main loop A comprises an internal exchanger 6 configured to allow heat exchange between the refrigerant fluid circulating between the first expander 31 and the second expander 32 and the refrigerant fluid downstream of the accumulation device 8 and upstream of an inlet 7a of compressor 7.

[103] The accumulation device 8, also called an accumulator, forms a liquid refrigerant storage volume. The accumulation device 8 makes it possible to compensate for the variations depending on the operating conditions of the quantity of refrigerant circulating in the circuit 10. The accumulation device 8 also makes it possible to separate the liquid phase and the gas phase of the refrigerant fluid from so as to supply the compressor 7 with refrigerant in gaseous form. [104] According to certain operating modes of the thermal conditioning system 100, the refrigerant fluid circulating between the first expander 31 and the second expander 32 circulates from the first expander 31 to the second expander 32.

According to other modes of operation of the thermal conditioning system 100, the refrigerant fluid circulating between the first expander 31 and the second expander 32 circulates from the second expander 32 to the first expander 31.

[105] This refrigerant circuit architecture makes it possible to transfer heat to the interior air flow Fi at the level of the first heat exchanger 1 and to selectively absorb heat or transfer heat to the exterior air flow Fe at the level of the second exchanger 2, while controlling the pressure at the inlet of the second exchanger 2. The second exchanger 2 can selectively absorb a controlled quantity of heat from the outside air Fe, or release a controlled quantity of heat to the outside air Fe. In both cases, the efficiency of the internal heat exchanger 6 can be controlled by controlling the pressure at the inlet of the internal exchanger 6, which makes it possible to control the discharge temperature of the compressor 7. By discharge temperature we mean the temperature of the refrigerant fluid leaving compressor 7.

[106] According to one embodiment, the first heat exchanger 1 is configured to exchange heat with an interior air flow Fi in a passenger compartment of the vehicle. The thermal coupling between the first heat exchanger 1 and the interior air flow Fi is said to be direct. In fact, the air flow Fi is in contact with the walls of the heat exchanger in which the refrigerant fluid circulates.

In this embodiment, the first exchanger 1 is arranged in the heating, ventilation and/or air conditioning installation of the vehicle.

[107] According to an alternative embodiment, shown in Figure 2, the first heat exchanger 1 is configured to exchange heat with a heat transfer liquid circulating in a closed circuit 30 of heat transfer liquid. The heat transfer liquid circuit 30 comprises a heat exchanger 1 B configured to exchange heat with an interior air flow Fi in the passenger compartment of the vehicle. The thermal coupling between the first heat exchanger 1 and the interior air flow Fi is in this case called indirect, since it is carried out via a heat transfer liquid which transfers the heat supplied by the refrigerant fluid to the flow of air Fi supplying the passenger compartment of the vehicle.

The heat transfer liquid circulating in circuit 30 is for example a mixture of water and glycol.

According to this variant, the heat exchanger 1 B, also called heating radiator, is arranged in the heating, ventilation and/or air conditioning installation of the vehicle.

[108] The second exchanger 2 is for example arranged in the front of the vehicle, in order to directly receive the flow of outside air. The second exchanger 2 can be placed just behind the grille of the vehicle. The grille may include a movable shutter making it possible to control, that is to say vary on demand, the section of passage of the exterior air flow in the grille.

[109] The internal heat exchanger 6 comprises a first heat exchange section 6a arranged on the main loop A between the first expander 31 and the second expander 32. The internal heat exchanger 6 also includes a second heat exchanger section 6a. heat exchange 6b arranged on the main loop A downstream of the accumulator 8 and upstream of the inlet 7a of the compressor 7.

The internal heat exchanger 6 is configured to allow heat exchange between the refrigerant in the first heat exchange section 6a and the refrigerant in the second heat exchange section 6b.

[110] The refrigerant fluid circulating at high pressure in the main loop A can thus transfer heat to the refrigerant fluid circulating at a lower pressure in the main loop A.

[111] The third heat exchanger 3 is thermally coupled with an element 25 of an electric traction chain of a motor vehicle.

[112] The third heat exchanger 3 makes it possible to selectively cool or heat the element 25 of the vehicle's electric traction chain. Element 25 of the vehicle's electric traction chain can thus be maintained, or placed, in a preferential temperature range corresponding to the optimal operation of the element.

[113] Element 25 of the vehicle's electric traction chain here includes an electrical energy storage battery.

[114] Alternatively or in a complementary manner, element 25 of the vehicle's electric traction chain comprises an electric vehicle traction motor.

[115] Alternatively or in a complementary manner, element 25 of the electric traction chain of the vehicle comprises an electronic unit for controlling the electric traction motor of the vehicle.

[116] According to the example illustrated, the third heat exchanger 3 is thermally coupled with element 25 of the electric traction chain via a heat transfer liquid circulating in a heat transfer liquid circuit 40.

[117] The heat transfer liquid circulating in the heat transfer liquid circuit 40 can exchange heat on the one hand with the refrigerant fluid circulating in the third heat exchanger 3 and on the other hand with the element 25 of the traction chain electric vehicle. The heat transfer liquid thus allows a heat transfer between the refrigerant fluid and element 25 of the electric traction chain.

For example, the heat transfer liquid circulates between the elements of the battery, or inside the wall of the electric motor, or the electric motor.

The heat transfer liquid circuit 40 and the heat transfer liquid circuit 30 are not connected. In other words, the heat transfer liquid from circuit 40 does not mix with the heat transfer liquid from circuit 30.

The heat transfer liquid of circuit 40 may be a dielectric fluid. When the heat transfer liquid of circuit 40 is a dielectric liquid, it can be in direct contact with electrically live components. [118] The first expansion valve 31 is for example an electronic expansion valve. Likewise, the second expander 32, the third expander 33, the fourth expander 34 can be electronic expanders.

[119] According to the embodiment of Figure 1, the thermal conditioning system 100 comprises a third branch branch D1 connecting a fifth connection point 15-1 arranged on the main loop A between the second regulator 32 and the first regulator 31 to a sixth connection point 16-1 arranged on the main loop A between the second connection point 12 and the fourth connection point 14.

The third branch D1 successively comprises a fifth expander 35 and a fourth heat exchanger 4 configured to exchange heat with the interior air flow Fi.

[120] The fourth heat exchanger 4 makes it possible to cool the interior air flow Fi in the passenger compartment, so as to cool the passenger compartment and ensure the thermal comfort of the passengers.

[121] In this embodiment, the refrigerant fluid circuit 10 comprises a first one-way valve 43-1 arranged on the main loop A between the sixth connection point 16-1 and the fourth connection point 14.

The first unidirectional valve 43-1 is configured to authorize a circulation of refrigerant fluid from the sixth connection point 16-1 to the fourth connection point 14. The first unidirectional valve 43-1 is also configured to prohibit a circulation of refrigerant fluid from the fourth connection point 14 towards the sixth connection point 16-1.

The first one-way valve 43-1 is in the example illustrated a non-return valve. A check valve is a passive member reacting to the pressure difference existing between its inlet and its outlet. No electrical control is necessary.

[122] According to an alternative embodiment, illustrated in Figure 3, the thermal conditioning system 100 comprises a third branch of branch D2 connecting a fifth connection point 15-2 arranged on the second branch of branch C between the third point of connection 13 and the fourth regulator 34 at a sixth connection point 16-2 arranged on the second branch of diversion C between the third exchanger 3 and the fourth connection point 14.

The third branch D2 successively comprising a fifth expansion valve 35 and a fourth heat exchanger 4 configured to exchange heat with the interior air flow Fi.

In other words, the third branch of derivation can be chosen according to two distinct variants D1 and D2.

These two variants are mutually exclusive, that is to say that if the refrigerant circuit 10 includes a third branch of type D1, no branch of type D2 is present, and vice versa.

[123] Tank] The fourth exchanger 4 is arranged in the heating, ventilation and/or air conditioning system of the vehicle. The fourth exchanger 4 is arranged upstream of the exchanger ensuring the heating of the interior air flow Fi, which is, depending on the embodiments, the first exchanger 1 or the exchanger 1 B.

[124] According to this alternative embodiment, the refrigerant fluid circuit 10 comprises a first one-way valve 43-2 arranged on the third branch branch D2 between the fourth exchanger 4 and the sixth connection point 16-2.

The first one-way valve 43-2 is configured to allow circulation of refrigerant fluid from the fifth connection point 15-2 to the sixth connection point 16-2 and configured to prohibit circulation of refrigerant fluid from the sixth connection point 16-2 towards the fifth connection point 15-2.

[125] When the first exchanger 1 is filled with refrigerant fluid, the same direction of circulation is identical in all operating modes. Likewise, the third exchanger 3 and the fourth exchanger 4 always pass in the same direction of circulation of the refrigerant fluid, when they are traversed by refrigerant fluid.

According to certain operating modes, the circulation of refrigerant in each exchanger may be blocked. [126] The direction of circulation of the refrigerant fluid in the second exchanger 2 can be reversed depending on the operating modes of the thermal conditioning system. In particular, the direction of operation may be different depending on whether the second exchanger 2 transfers heat to the exterior air flow Fe or receives heat from the exterior air flow Fe.

[127] In the same way, the direction of circulation in the first heat exchange section 6a of the internal exchanger 6 can be reversed depending on the operating modes of the thermal conditioning system.

In other words, according to certain operating modes the first heat exchange section 6a of the internal exchanger 6 receives the refrigerant fluid coming from the second expander 32, and according to other operating modes the first heat exchange section 6a of the The internal exchanger 6 supplies refrigerant fluid to the second expander 32. The second expander 32 is a bidirectional expander.

[128] The direction of circulation in the second heat exchange section 6b of the internal exchanger 6 is constant. By this we mean that the direction of circulation of the refrigerant fluid in the second heat exchange section 6b is identical for all operating modes of the thermal conditioning system 100.

[129] According to one embodiment, illustrated in Figures 4 to 8, the thermal conditioning system 100 comprises a fourth branch E connecting a seventh connection point 17 arranged on the main loop A downstream of the first connection point 11 and upstream of the first exchanger 1 to an eighth connection point 18 arranged on the second branch of diversion C downstream of the fourth regulator 34 and upstream of the fourth connection point 14. The fourth branch of diversion E comprises a sixth regulator 36 .

[130] The fourth branch of diversion E allows the refrigerant fluid at high pressure and high temperature at the outlet of the compressor 7 to return to the inlet 7a of the compressor without passing through the first exchanger 1 nor through the second exchanger 2. The fourth branch of bypass E returns the refrigerant to high pressure towards the inlet of the accumulator 8. The flow circulating in the fourth branch E makes it possible to increase the total flow of refrigerant fluid supplied by the compressor 7 and thus increase the thermal heating power supplied by the refrigerant fluid .

[131] According to the variants of Figures 4 to 7, the eighth connection point 18 is arranged downstream of the third exchanger 3.

The refrigerant fluid traveling through the fourth branch E does not pass through the third exchanger 3.

[132] According to the variant of Figure 8, the eighth connection point 18 is arranged upstream of the third exchanger 3.

The eighth connection point 18 is thus arranged between the outlet 34b of the fourth expander 34 and the inlet 3a of the third exchanger 3. The refrigerant fluid passing through the fourth branch E can pass through the third exchanger 3 then join the main loop A at the level of the fourth connection point 14.

[133] According to another alternative embodiment, not shown, the thermal conditioning system 100 comprises a fourth branch E connecting a seventh connection point 17 disposed on the main loop A downstream of the first connection point 1 1 and downstream upstream of the first exchanger 1 to an eighth connection point 18 arranged on the main loop A downstream of the fourth connection point 14 and upstream of the accumulation device 8. As previously, the fourth branch E comprises a sixth regulator 36 .

In other words, in this variant not shown, the eighth connection point 18 is arranged between the fourth connection point 14 and the input of the accumulator 8.

[134] According to one embodiment, illustrated in particular in Figures 4 to 8, the thermal conditioning system 100 comprises a fifth branch F connecting a ninth connection point 19 arranged on the second branch C downstream of the third exchanger 3 and upstream of the fourth connection point 14 to a tenth connection point 20 arranged on the main loop A between the third connection point 13 and the second regulator 32.

[135] According to the variants of Figures 4 to 7, the tenth connection point 20 is arranged between the first regulator 31 and the internal exchanger 6.

[136] According to the variant of Figure 8, the tenth connection point 20 is arranged between the internal exchanger 6 and the second regulator 32.

[137] The refrigerant fluid circuit 10 comprises a second one-way valve 44 arranged on the fifth branch F. The second one-way valve 44 is configured to allow circulation of refrigerant fluid from the ninth connection point 19 to the tenth connection point 20 and configured to prohibit a circulation of refrigerant fluid from the tenth connection point 20 to the ninth connection point 19.

[138] The second one-way valve 44 is for example a non-return valve.

[139] The fifth branch of diversion F allows the refrigerant fluid at high pressure or at intermediate pressure at the outlet of the third exchanger 3 to join the main loop A, pass through the second expander 32 and the second exchanger 2, then join the inlet 7a of the compressor 7. The seventh expansion valve 37 makes it possible to block the circulation of refrigerant fluid from the ninth connection point 19 to the fourth connection point 14, so that the refrigerant fluid coming from the third exchanger 3 passes through the fifth branch F The fifth branch F thus allows the refrigerant fluid to supply heat to the element 25 of the electric traction chain at the level of the third exchanger 3, that is to say that this branch allows heating to be carried out. of element 25 of the electric traction chain.

[140] In the same way, when the third branch branch is of type D2, as illustrated in Figure 5, the refrigerant fluid at high pressure or at intermediate pressure at the outlet of the fourth exchanger 4 can join the main loop A by circulating in the fifth branch of diversion F. The fourth exchanger 4 can thus heat the interior air flow Fi. [141] The ninth connection point 19 can be confused with the sixth connection point 16-2.

[142] According to the second embodiment of the thermal conditioning system 100, illustrated in particular in FIGS. 4 to 8, the second branch C comprises a seventh pressure reducer 37 arranged between the ninth connection point 19 and the fourth connection point 14.

[143] When the third branch of diversion is of type D1, as illustrated in Figure 4, the seventh regulator 37 makes it possible to expand the refrigerant fluid coming from the third exchanger 3 before it mixes with the refrigerant fluid in outlet of the fourth exchanger 4. The fourth exchanger 4 can therefore operate at a lower pressure than that of the third exchanger 3, therefore at a lower evaporation temperature. The fourth exchanger 4 and the third exchanger 3 can thus each provide cooling, with two different temperature levels.

[144] In addition, when the third branch of diversion is of type D2, as illustrated in Figure 5, the seventh regulator 37 makes it possible to expand the refrigerant fluid coming from the fourth exchanger 4 before it mixes with the refrigerant fluid leaving the second exchanger 2. As before, the fourth exchanger 4 can therefore operate at a higher pressure than that of the second exchanger 2, therefore at a higher evaporation temperature. This case is used for example during an operating mode aimed at dehumidifying the air in the passenger compartment, which will be described later.

[145] When the fourth branch of diversion E is present and connected to the second branch of branch C downstream of the third exchanger 3, the seventh regulator 37 is arranged between the ninth connection point 19 and the eighth connection point 18. This configuration is illustrated in Figures 4 to 7.

[146] The fifth branch F can include an eighth regulator 38.

The eighth regulator 38 is for example a calibrated orifice.

The eighth regulator 38 is optional, that is to say it may not be present. [147] The eighth expander makes it possible to expand the refrigerant fluid coming from the third exchanger 3 before entering the first heat exchange section 6a of the internal exchanger 6, and thus to control the heat exchange in the internal exchanger 6.

[148] According to the first embodiment and its variants, illustrated in Figures 1 to 3, the first regulator 31 is arranged between the first exchanger 1 and the third connection point 13.

[149] According to the second embodiment, illustrated in Figures 4 to 8, the first regulator 31 is arranged between the tenth connection point 20 and the third connection point 13.

[150] The refrigerant fluid circuit 10 comprises a third one-way valve 45 arranged on the main loop A between the first exchanger

I and the third connection point 13.

The third one-way valve 45 is configured to allow circulation of refrigerant fluid from the first exchanger 1 to the third connection point

13. The third one-way valve 45 is also configured to prevent circulation of refrigerant fluid from the third connection point 13 to the first exchanger 1.

The third one-way valve 45 is for example a non-return valve.

[151] Each non-return valve 43, 44, 45 can be replaced by an electrically operated valve controlled so as to ensure the same conditions of circulation of the refrigerant fluid.

[152] The main loop A comprises a first stop valve 41 arranged between the first connection point 11 and the first heat exchanger 1.

The first stop valve 41 is arranged between the first connection point

I I and the seventh connection point 17.

[153] The main loop A comprises a second shut-off valve 42 arranged between the second connection point 12 and the fourth connection point.

14. The second stop valve 42 is arranged between the second connection point 12 and the sixth connection point 16-1.

[154] The first stop valve 41 is an electrically controlled valve. Similarly, the second stop valve 42 is an electrically controlled valve.

The first stop valve 41 is a two-way valve. Likewise, the second stop valve 42 is a two-way valve.

[155] Figures 6 and 7 schematically show two variants of the second embodiment in which part of the circuit 10 is formed by a refrigerant distribution module.

[156] According to the variant of Figure 6, the thermal conditioning system 100 comprises a refrigerant distribution module 50 comprising:

- a first refrigerant fluid inlet 11,

- a second refrigerant fluid inlet I2,

- a first S1 outlet of refrigerant fluid,

- a second refrigerant fluid outlet S2,

- a first channel C1 connecting the first input 11 to the first output S1,

- a second channel C2 connecting the second input I2 to a connection point P arranged on the first channel C1 between the first input 11 and the first output S1,

- a third channel C3 connecting the second output S2 to the connection point P,

- a seventh regulator 37 arranged on the first channel C1 between the connection point P and the first output S1,

- a one-way valve 44 placed on the second channel C2 between the connection point P and the second outlet S.

The first channel C1 partly forms the second branch of diversion C.

The second channel C2 partly forms the third branch of diversion D2.

The third channel C3 partly forms the fifth branch of diversion F.

[157] The distribution module 50 integrates certain components and forms part of the refrigerant circulation circuit, which facilitates the mechanical integration of the components. The distribution module 50 can be delivered pre-assembled, which reduces the number of components to be assembled on the vehicle. In addition, the overall size is reduced. [158] The connection point P is here confused with the sixth connection point 16-2 and with the ninth connection point 19.

[159] The channels C1, C2, C3 of the refrigerant distribution module module 50 are formed by internal recesses of a metal block. The distribution module 50 can for example be obtained by aluminum casting and machining.

[160] The refrigerant distribution module 50 may include an eighth regulator 38 disposed on the third channel C3.

The eighth regulator 38 is for example arranged on the third channel C3 between the connection point P and the one-way valve 44.

[161] Figure 7 schematizes a 50’ distribution module according to another definition.

[162] In this variant, the refrigerant distribution module 50' comprises:

- a first refrigerant fluid inlet 11’,

- a second inlet/outlet ES2’ of refrigerant fluid,

- a third inlet/outlet ES3’ of refrigerant fluid,

- a first channel C1’ connecting the second input/output ES2’ to the third input/output ES3’,

- a second channel C2' connecting the first input 11' to a connection point P' arranged on the first channel C1' between the second input/output ES2' and the third input/output ES3',

- the first regulator 31,

- a one-way valve 44 placed on the second channel C2’ between the first inlet 11’ and the connection point P’.

The first regulator 31 is arranged on the first channel C1’ between the third input/output ES3’ and the connection point P’.

The first channel C1 'partly forms the main loop A.

The second channel C2’ partly forms the fifth branch of diversion F.

[163] The connection point P' is here confused with the tenth connection point 20. [164] As previously, the channels C1', C2' of the refrigerant distribution module module 50' are for example formed by internal recesses of a metal block.

[165] The refrigerant distribution module 50' may include an eighth regulator 38 placed on the second channel C2'. The eighth regulator 38 is for example arranged on the second channel C2' between the first inlet 11' and the one-way valve 44.

[166] Figures 9 to 14 illustrate several operating modes of the thermal conditioning system 100. These different modes can be selectively activated, for example by the control unit 60, depending on the instructions of the occupants of the vehicle and depending on the Terms of use.

[167] Figure 9 illustrates an operating method of a thermal conditioning system 100 according to the first embodiment, in a so-called passenger compartment dehumidification and battery cooling mode.

In this operating mode:

— a total flow rate Q1 of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and is divided between:

-- a second flow Q2 circulating in the main loop A, successively in the first exchanger 1 where it transfers heat to the interior air flow Fi, in the first regulator 31 where it passes at intermediate pressure,

-- a third flow Q3 circulating in the first branch B, successively in the third regulator 33 where it passes at intermediate pressure, in the second exchanger 2 where it transfers heat to the external air flow Fe, in the second regulator 32, in the internal exchanger 6, and is divided between:

— a fourth flow Q4 circulating in the third branch D1, successively in the fifth expander 35 where it passes at low pressure, in the fourth exchanger 4 where it receives heat from the interior air flow Fi, in the main loop A,

— a fifth flow Q5 circulating in the main loop A and joining the second flow Q2, the second flow Q2 and the fifth flow Q5 forming a sixth circulating flow Q6 in the second branch of diversion C, successively in the fourth regulator 34 where it passes at low pressure, in the third exchanger 3 where it receives heat, and joins the fourth flow Q4, the sixth flow Q6 and the fourth flow Q4 forming the total flow Q1, the total flow Q1 circulates successively in the accumulation device 8, in the internal exchanger 6, and returns to the compressor 7.

[168] The value of the “high pressure” type pressure is for example between 80 bars and 120 bars.

The value of the so-called “intermediate” pressure is lower than the value of the high pressure. The intermediate pressure is for example between 40 bars and 70 bars.

The value of the so-called “low pressure” pressure is lower than the value of the intermediate pressure.

Low pressure is for example between 1 bar and 50 bars.

[169] In this mode of operation, the interior air flow Fi is cooled at the fourth exchanger 4, and heated at the first exchanger 1, which makes it possible to dehumidify the interior air flow Fi.

The refrigerant fluid absorbs heat from element 25 of the traction chain at the level of the third exchanger 3, which allows element 25 of the traction chain to be cooled.

The third regulator 33 makes it possible to control the value of the intermediate pressure in the second exchanger 2, and thus the quantity of heat dissipated in the external air flow Fe. In addition, controlling the intermediate pressure makes it possible to control the quantity of heat exchanged at the internal exchanger 6.

The internal exchanger 6 participates in the heat exchanges, since the first heat exchange section 6a and the second heat exchange section 6b are both filled with refrigerant fluid.

The second shut-off valve 42 is in the closed position, which prevents the circulation of refrigerant fluid in the portion of the main loop A between the second connection point 12 and the sixth connection point 16-1. All the other portions of the refrigerant circuit 10 are traversed by fluid refrigerant.

The fifth flow Q5 can take negative values, that is to say flow from the third connection point 13 to the fifth connection point 15-1. In this case, the fourth flow rate Q4 is greater than the third flow rate Q3.

When the fifth flow rate is positive, as is the case in Figure 9, the circulation of refrigerant fluid takes place from the fifth connection point 15-1 to the third connection point 13. The third flow rate Q3 is then greater than the fifth flow rate Q5. The direction of flow Q5 depends on the respective value of flow rates Q2, Q3 and Q6, which vary depending on the conditions of use.

[170] Figure 10 illustrates a method of operating a thermal conditioning system 100 according to the second embodiment, in a so-called battery heating mode with energy recovery from the outside air.

In this operating mode:

- a total flow rate Q of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates in the main loop A, in the first exchanger 1, in the second branch of diversion C, successively in the fourth regulator 34 where it passes at intermediate pressure, in the third heat exchanger 3 where it transfers heat, in the fifth branch of diversion F, in the main loop A successively in the internal exchanger 6, in the second regulator 32 where it passes at low pressure, in the second exchanger 2 where it receives heat from the external air flow Fe, in the accumulation device 8, in the internal exchanger 6, and returns to the compressor 7.

[171] In this operating mode, the total flow rate Q of refrigerant fluid can transfer heat to the indoor air flow Fi at the first exchanger 1. For this, the flow rate of the indoor air flow Fi can be controlled to a non-zero value.

[172] In this mode of operation, the total flow rate Q of refrigerant fluid can also circulate in the first exchanger 1 without transferring heat to the interior air flow Fi. For this, the flow rate of the interior air flow Fi is for example maintained at a zero value.

[173] In this mode of operation, the refrigerant fluid transfers heat to element 25 of the traction chain at the level of the third exchanger 3, which allows element 25 of the traction chain to be heated. The fourth regulator 34 makes it possible to control the value of the intermediate pressure.

The low pressure refrigerant fluid receives heat from the external air flow Fe at the level of the second exchanger 2.

The direction of circulation of the refrigerant fluid in the second exchanger 2 is reversed compared to the previous operating mode.

The internal exchanger 6 participates in heat exchange.

The fourth exchanger 4 is not traversed by the refrigerant fluid. The fifth expansion valve 35 is in the closed position, which blocks the circulation of refrigerant fluid in the third bypass branch D1.

The portion of second branch C between the ninth connection point 19 and the fourth connection point 14 does not pass through the refrigerant fluid.

The portion of main loop A between the third connection point 13 and the tenth connection point 20 is not traversed by the refrigerant fluid, the first expansion valve 31 being in the closed position.

Likewise, the first branch of diversion B and the fourth branch of diversion E do not pass through the refrigerant fluid.

[174] Figure 11 illustrates a method of operating a thermal conditioning system 100 according to the first variant of the second embodiment, in a so-called battery heating and passenger compartment heating mode with energy recovery from the outside air.

In this operating mode:

- a total flow rate Q1 of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates in the main loop A, in the first exchanger 1 where it transfers heat to the interior air flow Fi, and divides between :

-- a second flow Q2 circulating in the second branch of diversion C, successively in the fourth regulator 34 where it passes at intermediate pressure, in the third heat exchanger 3 where it releases heat, -- a third flow Q3 circulating in the third branch of diversion D2, successively in the fifth regulator 35 where it passes pressure intermediate, in the fourth heat exchanger 4 where it transfers heat to the interior air flow Fi, and joins the second flow Q2, the second flow Q2 and the third flow Q3 forming the total flow Q1, the total flow Q1 formed circulating in the fifth branch of diversion F, in the main loop A successively in the internal exchanger 6, in the second regulator 32 where it passes at low pressure, in the second exchanger 2 where it receives heat from the air flow exterior Fe, in the accumulation device 8, in the internal exchanger 6, and returns to the compressor 7.

[175] This mode of operation differs from the previous mode in that the flow of refrigerant fluid leaving the first exchanger 1 can be divided at the fifth connection point 15-2 and circulate in parallel in the third exchanger 3 and in the fourth exchanger 4. This division is made possible by the particular arrangement of the third branch of diversion D2. The third exchanger 3 and the fourth exchanger 4 can thus ensure heating, respectively of the element 25 of the traction chain, and of the interior air flow Fi. The interior air flow Fi is thus heated both at the level of the first exchanger 1 and at the level of the fourth exchanger 4, which makes it possible to increase the heating power and the speed of rise in temperature of the passenger compartment.

[176] The low-pressure refrigerant fluid receives heat from the external air flow Fe at the level of the second exchanger 2.

The first branch of diversion B and the fourth branch of branch E do not pass through the refrigerant fluid.

The portion of second branch C between the ninth connection point 19 and the fourth connection point 14 does not pass through the refrigerant fluid.

The portion of main loop A between the third connection point 13 and the tenth connection point 20 does not pass through the refrigerant fluid, the first regulator 31 being in the closed position.

The internal exchanger 6 participates in heat exchange.

[177] Figure 12 illustrates a method of operating a thermal conditioning system 100 according to the first variant of the second mode of production, in a so-called cabin dehumidification mode with energy recovery from the outside air.

In this operating mode:

- a total flow rate Q1 of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates in the main loop A, in the first exchanger 1 where it transfers heat to the interior air flow Fi, and divides between :

-- a second flow Q2 circulating in the third branch of diversion D2, successively in the fifth regulator 35 where it passes at intermediate pressure, in the fourth heat exchanger 4 where it receives heat from the interior air flow Fi, in the main loop A, in the seventh regulator 37 where it passes at low pressure,

-- a third flow Q3 circulating in the main loop A, successively in the first expander 31, in the internal exchanger 6, in the second expander 32 where it passes at low pressure, in the second heat exchanger 2 where it receives the heat of the exterior air flow Fe, and joins the second flow Q2, the second flow Q2 and the third flow Q3 forming the total flow Q1, the total flow Q1 formed circulating in the main loop A successively in the accumulation device 8, in the internal exchanger 6, and returns to the compressor 7.

[178] The fourth exchanger 4 and the second exchanger 2 both operate as an evaporator. At the level of the fourth exchanger 4, the refrigerant fluid receives heat from the interior air flow Fi, with the aim of cooling it. At the level of the second exchanger 2, the refrigerant fluid receives heat from the exterior air flow Fe. This heat contributes to heating the interior air flow Fi at the level of the first exchanger 1. The pressure in the fourth exchanger 4 can be higher than the pressure in the second exchanger 2, since the refrigerant fluid coming from the fourth exchanger 4 undergoes expansion while passing through the seventh expander 37 before joining at the fourth connection point 14 the refrigerant fluid coming from the second exchanger 2. The evaporation temperature in the fourth exchanger 4 can therefore be higher than that in the second exchanger 2. It is therefore possible to recover heat at the level of the second exchanger 2 even at a temperature negative ambient, that is to say a negative temperature of the external air flow Fe, without risking simultaneously icing the fourth exchanger 4.

[179] Figure 13 illustrates a method of operating a thermal conditioning system 100 according to the second embodiment, in a mode called accelerated heating of the passenger compartment and the battery.

In this operating mode:

- a total flow Q1 of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, circulates in the main loop A and is divided between:

-- a second flow Q2 circulating in the main loop A, in the first exchanger 1 where it transfers heat to the interior air flow Fi, in the second branch of diversion C, successively in the fourth expander 34 where it passes to intermediate pressure, in the third heat exchanger 3 where it transfers heat, in the seventh expander 37 where it passes at low pressure,

-- a third flow Q3 circulating in the fourth branch E, in the sixth regulator 36 where it undergoes an expansion, and joins the second flow Q2, the second flow Q2 and the third flow Q3 thus forming the total flow Q1, the total flow rate Q1 formed circulates in the main loop A, successively in the accumulation device 8, in the internal exchanger 6 and returns to the compressor 7.

[180] In this operating mode, the interior air flow Fi is heated by the high pressure refrigerant fluid at the first exchanger 1, which allows the passenger compartment to be heated.

The refrigerant fluid at intermediate pressure transfers heat to element 25 of the traction chain at the level of the third exchanger 3, which makes it possible to heat element 25 of the traction chain.

The flow rate Q2 of refrigerant fluid, mainly in liquid form at the outlet of the third exchanger 3 and the seventh expander 37, is mixed with the flow rate Q3 of gaseous refrigerant fluid at high temperature which leaves the sixth expander 36.

The third flow Q3 joins the second flow Q2 between the seventh regulator 37 and the fourth connection point 14.

The mixture formed, essentially or totally in gaseous form, is re-aspirated by the compressor 7 after passing through the accumulation device 8.

The additional flow circulating in the fourth branch E makes it possible to increase the heating power supplied and accelerate the rise in temperature of the passenger compartment. It is therefore not necessary to equip the vehicle's heating system with additional electric heating.

[181] The second exchanger 2 and the fourth exchanger 4 do not participate in the heat exchanges.

The internal exchanger 6 does not participate in the heat exchanges, because the flow of refrigerant fluid in the first heat exchange section 6a is zero.

The first regulator 31, the second regulator 32, the third regulator 33 and the fifth regulator 35 are in the closed position.

The first branch of bypass B and the fifth branch of bypass F are not crossed by the refrigerant fluid.

The portion of main loop A between the third connection point 13 and the fourth connection point 14 does not pass through the refrigerant fluid.

[182] Figure 14 illustrates a method of operating a thermal conditioning system 100 according to the second embodiment, in a so-called passenger compartment heating and energy recovery mode.

According to this mode of operation:

- a total flow rate Q1 of refrigerant fluid circulates in the compressor 7 where it passes at high pressure, and circulates in the main loop A, in the first exchanger 1 where it transfers heat to the interior air flow Fi, and divides between :

-- a second flow Q2 circulating in the second branch of diversion C, successively in the fourth expander 34 where it passes to a first intermediate pressure, in the third heat exchanger 3 where it receives heat, in the seventh expander 37 where it goes to low pressure,

-- a third flow Q3 circulating in the main loop A, successively in the first regulator 31 where it passes to a second intermediate pressure greater than or equal to the first intermediate pressure, in the internal exchanger 6, in the second regulator 32 where it passes at low pressure, in the second exchanger 2 where it receives heat from the exterior air flow Fe, and joins the second flow Q2, the second flow Q2 and the third flow Q3 thus forming the total flow Q1, the total flow Q1 formed circulates in the main loop A , successively in the accumulation device 8, in the internal exchanger 6 and returns to the compressor 7.

[183] In this operating mode, the interior air flow Fi is heated at the level of the first exchanger 1, which allows the passenger compartment to be heated.

The refrigerant fluid can receive heat from element 25 of the traction chain at the level of the third exchanger 3, which makes it possible to achieve energy recovery. The fourth regulator 34 makes it possible to control the value of the intermediate pressure.

The low pressure refrigerant fluid receives heat from the external air flow Fe at the level of the second exchanger 2.

The heat taken from the exterior air flow Fe and the heat recovered from thermal losses from the electric traction chain both contribute to heating the vehicle's passenger compartment.

The fourth exchanger 4 does not participate in heat exchanges.

The internal exchanger 6 participates in heat exchange.

The first branch of diversion B and the third branch of branch D1 do not pass through the refrigerant fluid.

Likewise, the fifth branch of branch F is not traversed by the refrigerant fluid. In fact, the second one-way valve 44 prevents the circulation of the refrigerant fluid from the tenth connection point 20 to the ninth connection point 19.

[184] Many other modes of operation, not shown, are also possible.

[185] For example, according to a mode called passenger compartment cooling and traction chain cooling, the first stop valve 41 is closed so as to prevent the circulation of refrigerant fluid in the first exchanger 1. The high pressure refrigerant fluid thus circulates in the second exchanger 2 where the heat of the refrigerant fluid is dissipated in the outside air flow, then circulates in parallel in the fourth exchanger 4 and in the third exchanger 3. The fifth expander 35 and the fourth expander 34 expand the refrigerant fluid to a state of low pressure.

The sixth expansion valve 36 is in the partially open position. Thus, the circuit portion 10 between the first stop valve 41 and the third one-way valve 45, including the first exchanger 1, is maintained in a low pressure state, which is the state of the refrigerant fluid downstream of the seventh expansion valve 37.

Thus, the mass of refrigerant fluid included in this portion of the circuit can be minimized, which makes it possible to reduce the quantity of refrigerant fluid necessary.

[186] Other refrigerant circuit architectures are possible.

[187] In particular, according to variants not shown, the fourth branch E may be present without the fifth branch F being present. Similarly, the fifth branch F may be present while the fourth branch E is not present.

The fifth branch of branch F can have the definition shown in Figure 8 with a fourth branch of branch E defined as in Figures 4 to 7. Likewise, the fourth branch of branch E can have the definition shown in Figure 8 with a fifth branch of derivation F defined as in Figures 4 to 7.

Claims

Claims [Claim 1] Thermal conditioning system (100) for a motor vehicle, comprising a refrigerant fluid circuit (10) configured to circulate a refrigerant fluid, the refrigerant fluid circuit (10) comprising: A main loop (A) comprising successively according to the direction of circulation of the refrigerant fluid: -- a compressor (7), -- a first heat exchanger (1) thermally coupled with an interior air flow (Fi) to a passenger compartment of the vehicle, -- a first regulator (31), -- a second regulator (32), -- a second heat exchanger (2) configured to exchange heat with an exterior air flow (Fe) to the passenger compartment of the vehicle, -- a refrigerant accumulation device (8), A first branch branch (B) connecting a first connection point (11) arranged on the main loop (A) downstream of an outlet (7b) of the compressor (7) and upstream of the first exchanger (1) to a second connection point (12) arranged on the main loop (A) downstream of the second heat exchanger (2) and upstream of the accumulation device (8), the first branch branch (B) comprising a third regulator ( 33), - A second branch branch (C) connecting a third connection point (13) arranged on the main loop (A) between the first exchanger (1) and the second regulator (32) to a fourth connection point (14) arranged on the main loop (A) downstream of the second exchanger (2) and upstream of the accumulation device (8), the second branch of diversion (C) successively comprising a fourth expander (34) and a third heat exchanger ( 3), in which the main loop (A) comprises an internal exchanger (6) configured to allow heat exchange between the refrigerant fluid circulating between the first expander (31) and the second expander (32) and the refrigerant fluid downstream of the accumulation device (8) and upstream of an inlet (7a) of the compressor (7). [Claim 2] Thermal conditioning system (100) according to claim 1, in which the third heat exchanger (3) is thermally coupled with an element (25) of an electric traction chain of a motor vehicle. [Claim 3] A thermal conditioning system (100) according to claim 1 or 2, comprising: - A third branch branch (D1) connecting a fifth connection point (15-1) arranged on the main loop (A) between the second regulator (32) and the first regulator (31) to a sixth connection point (16 -1) arranged on the main loop (A) between the second connection point (12) and the fourth connection point (14), the third branch branch (D1) successively comprising a fifth regulator (35) and a fourth exchanger heat exchanger (4) configured to exchange heat with the interior air flow (Fi). [Claim 4] Thermal conditioning system (100) according to claim 1 or 2, comprising: - A third branch branch (D2) connecting a fifth connection point (15-2) arranged on the second branch branch (C) between the third connection point (13) and the fourth regulator (34) to a sixth point connection (16-2) arranged on the second branch branch (C) between the third exchanger (3) and the fourth connection point (14), the third branch branch (D2) successively comprising a fifth regulator (35) and a fourth heat exchanger (4) configured to exchange heat with the indoor air flow (Fi). [Claim 5] Thermal conditioning system (100) according to one of the preceding claims, comprising: - A fourth branch branch (E) connecting a seventh connection point (17) located on the main loop (A) downstream of the first connection point (1 1) and upstream of the first exchanger (1) to an eighth point connection (18) arranged on the second branch branch (C) downstream of the fourth regulator (34) and upstream of the fourth connection point (14), the fourth branch of diversion (E) comprising a sixth regulator (36). [Claim 6] Thermal conditioning system (100) according to one of the preceding claims, comprising: - A fifth branch of diversion (F) connecting a ninth connection point (19) arranged on the second branch of branch (C) downstream of the third exchanger (3) and upstream of the fourth connection point (14) to a tenth connection point (20) arranged on the main loop (A) between the third connection point (13) and the second regulator (32), in which the refrigerant fluid circuit (10) comprises a second one-way valve (44) arranged on the fifth branch branch (F), the second one-way valve (44) being configured to authorize a circulation of refrigerant from the ninth connection point (19) to the tenth connection point (20) and configured to prohibit a circulation of refrigerant fluid from the tenth connection point (20) to the ninth connection point (19). [Claim 7] Thermal conditioning system (100) according to the preceding claim, in which the second branch branch (C) comprises a seventh regulator (37) disposed between the ninth connection point (19) and the fourth connection point ( 14). [Claim 8] Thermal conditioning system (100) according to claim 6 or 7, in which the fifth branch of diversion (F) comprises an eighth regulator (38). [Claim 9] Thermal conditioning system (100) according to one of claims 6 to 8 in combination with claim 7, comprising a refrigerant distribution module (50) comprising: - a first inlet (11) of refrigerant fluid, - a second refrigerant fluid inlet (I2), - a first outlet (S1) of refrigerant fluid, - a second outlet (S2) of refrigerant fluid, - a first channel (C1) connecting the first input (11) to the first output (S1), - a second channel (C2) connecting the second input (12) to a connection point (P) arranged on the first channel (C1) between the first input (11) and the first output (S1), - a third channel (C3) connecting the second output (S2) to the connection point (P), - a seventh regulator (37) arranged on the first channel (C1) between the connection point (P) and the first outlet (S1), - a one-way valve (44) arranged on the second channel (C2) between the connection point (P) and the second outlet (S2), in which: the first channel (C1) partly forms the second branch of diversion (C ), the second channel (C2) partly forms the third branch (D2), the third channel (C3) partly forms the fifth branch (F). [Claim 10] Thermal conditioning system (100) according to one of claims 6 to 8, comprising a refrigerant fluid distribution module (50') comprising: - a first inlet (11’) of refrigerant fluid, - a second inlet/outlet (ES2’) of refrigerant fluid, - a third inlet/outlet (ES3’) of refrigerant fluid, - a first channel (C1’) connecting the second input/output (ES2’) to the third input/output (ES3’), - a second channel (C2') connecting the first input (11') to a connection point (P') arranged on the first channel (C1') between the second input/output (ES2') and the third input/output (ES3'), - the first regulator (31), - a one-way valve (44) arranged on the second channel (C2') between the first inlet (11') and the connection point (P'), in which: the first regulator (31) is arranged on the first channel ( C1') between the third input/output (ES3') and the connection point (P'), the first channel (C1') partly forms the main loop (A), the second channel (C2') partly forms the fifth branch of diversion (F). [Claim 11] Method of operating a thermal conditioning system (100) according to one of the preceding claims in combination with claim 3, in a so-called passenger compartment dehumidification and battery cooling mode in which: — a total flow rate (Q1) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and is divided between: -- a second flow (Q2) circulating in the main loop (A), successively in the first exchanger (1) where it transfers heat to the interior air flow (Fi), in the first regulator (31) where it passes to intermediate pressure, -- a third flow (Q3) circulating in the first branch of diversion (B), successively in the third regulator (33) where it passes at intermediate pressure, in the second exchanger (2) where it transfers heat to the flow The outside air (Fe), in the second regulator (32), in the internal exchanger (6), and is divided between: — a fourth flow (Q4) circulating in the third branch of diversion (D1), successively in the fifth regulator (35) where it passes at low pressure, in the fourth exchanger (4) where it receives heat from the flow of indoor air (Fi), in the main loop (A), — a fifth flow (Q5) circulating in the main loop (A) and joining the second flow (Q2), the second flow (Q2) and the fifth flow (Q5) forming a sixth flow (Q6) circulating in the second branch of bypass (C), successively in the fourth expander (34) where it passes at low pressure, in the third exchanger (3) where it receives heat, and joins the fourth flow (Q4), the sixth flow (Q6) and the fourth flow (Q4) forming the total flow (Q1), the total flow (Q1) formed circulates in the main loop (A), successively in the accumulation device (8), in the internal exchanger (6), and returns to the compressor (7). [Claim 12] Method of operating a thermal conditioning system (100) according to one of the preceding claims in combination with claims 3 and 6, in a so-called battery heating mode with energy recovery from the outside air in which : - a total flow rate (Q) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates in the main loop (A), in the first exchanger (1), in the second branch of diversion (C ), successively in the fourth expander (34) where it passes at intermediate pressure, in the third heat exchanger (3) where it releases heat, in the fifth branch of diversion (F), in the main loop (A) successively in the internal exchanger (6), in the second regulator (32) where it passes at low pressure, in the second exchanger (2) where it receives heat from the external air flow (Fe), in the device accumulation (8), in the internal exchanger (6), and returns to the compressor (7). [Claim 13] Method of operating a thermal conditioning system (100) according to one of the preceding claims in combination with claims 4 and 6, in a so-called battery heating and passenger compartment heating mode with energy recovery from the outside air in which: - a total flow (Q1) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates in the main loop (A), in the first exchanger (1) where it gives off heat to the interior air flow (Fi), and is divided between: -- a second flow (Q2) circulating in the second branch of diversion (C), successively in the fourth regulator (34) where it passes at intermediate pressure, in the third heat exchanger (3) where it releases heat, -- a third flow (Q3) circulating in the third branch of diversion (D2), successively in the fifth regulator (35) where it passes at intermediate pressure, in the fourth heat exchanger (4) where it transfers heat to the interior air flow (Fi), and joins the second flow (Q2), the second flow (Q2) and the third flow (Q3) forming the total flow (Q1), the total flow (Q1) formed circulating in the fifth branch branch (F), in the main loop (A) successively in the internal exchanger (6), in the second regulator (32) where it passes at low pressure, in the second exchanger (2) where it receives heat from the exterior air flow (Fe), in the accumulation device (8), in the internal exchanger (6), and returns to the compressor (7). [Claim 14] Method of operating a thermal conditioning system (100) according to one of the preceding claims in combination with claims 4,6,7, in a so-called passenger compartment dehumidification mode with energy recovery from outside air in which: - a total flow rate (Q1) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates in the main loop (A), in the first exchanger (1) where it transfers heat to the flow indoor air (Fi), and is divided between: -- a second flow (Q2) circulating in the third branch of diversion (D2), successively in the fifth regulator (35) where it passes at intermediate pressure, in the fourth heat exchanger (4) where it receives heat from the interior air flow (Fi), in the main loop A, in the seventh regulator (37) where it passes at low pressure, -- a third flow (Q3) circulating in the main loop (A), successively in the first regulator (31), in the internal exchanger (6), in the second regulator (32) where it passes at low pressure, in the second heat exchanger (2) where it receives heat from the outside air flow (Fe), and joins the second flow (Q2), the second flow (Q2) and the third flow (Q3) forming the total flow (Q1), the total flow (Q1) formed circulating in the main loop A successively in the accumulation device (8), in the internal exchanger (6), and returns to the compressor (7). [Claim 15] Method of operating a thermal conditioning system (100) according to one of the preceding claims in combination with claims 5 and 7, in a so-called accelerated heating mode of the passenger compartment and the battery in which : - a total flow rate (Q1) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, circulates in the main loop (A) and is divided between: -- a second flow (Q2) circulating in the main loop (A), in the first exchanger (1) where it transfers heat to the interior air flow (Fi), in the second branch of diversion (C), successively in the fourth expander (34) where it passes at intermediate pressure, in the third heat exchanger (3) where it releases heat, in the seventh expander (37) where it passes at low pressure, -- a third flow (Q3) circulating in the fourth branch of diversion (E), in the sixth regulator (36) where it undergoes an expansion, and joins the second flow (Q2), the second flow (Q2) and the third flow (Q3) thus forming the total flow (Q1), the total flow (Q1) formed circulates in the main loop A, successively in the accumulation device (8), in the internal exchanger (6) and returns to the compressor (7). [Claim 16] Method of operating a thermal conditioning system (100) according to one of the preceding claims in combination with claims 4 and 7, in a so-called passenger compartment heating and energy recovery mode in which: - a total flow rate (Q1) of refrigerant fluid circulates in the compressor (7) where it passes at high pressure, and circulates in the main loop (A), in the first exchanger (1) where it transfers heat to the flow indoor air (Fi), and is divided between: -- a second flow (Q2) circulating in the second branch of diversion (C), successively in the fourth regulator (34) where it passes to a first intermediate pressure, in the third heat exchanger (3) where it receives heat heat, in the seventh regulator (37) where it passes at low pressure, -- a third flow (Q3) circulating in the main loop (A), successively in the first regulator (31) where it passes to a second intermediate pressure greater than or equal to the first intermediate pressure, in the internal exchanger (6) , in the second expander (32) where it passes at low pressure, in the second exchanger (2) where it receives heat from the outside air flow (Fe), and joins the second flow (Q2), the second flow (Q2) and the third flow (Q3) thus forming the total flow (Q1), the total flow (Q1) formed circulates in the main loop A, successively in the accumulation device (8), in the internal exchanger ( 6) and returns to the compressor (7).