WO2017162941A1

WO2017162941A1 - Refrigerant circulation device for thermal conditioning of a motor vehicle

Info

Publication number: WO2017162941A1
Application number: PCT/FR2017/050341
Authority: WO
Inventors: Samy Hammi; Régine Haller; Mohamed Yahia; Bertrand Nicolas; Jin-ming LIU; Abdelmajid Taklanti
Original assignee: Valeo Systemes Thermiques
Priority date: 2016-03-24
Filing date: 2017-02-15
Publication date: 2017-09-28
Also published as: FR3049339B1; FR3049339A1

Abstract

The invention relates to a refrigerant circulation device (1) for thermal conditioning of a motor vehicle, including a so-called main air-conditioning loop, comprising a machine (M), capable of operating as a compressor, and a so-called secondary air-conditioning loop, comprising a pump (P), the main and secondary loops being interconnected, characterised in that the machine (M) is configured to allow torque recovery due to an expansion of said refrigerant, and the device (1) is configured to connect the loops so that said refrigerant undergoes a Rankine thermodynamic cycle, circulating the refrigerant through the pump (P) and the machine (M).

Description

Refrigerant circulation device for the thermal conditioning of a motor vehicle

TECHNICAL AREA

The present invention relates to a refrigerant circulation device for the thermal conditioning of a motor vehicle.

STATE OF THE ART

It is known to use one or more circulation devices for thermal conditioning capable of performing the following functions:

î o - heating the passenger compartment of a vehicle,

- cooling of the passenger compartment, this function being also called air conditioning of the passenger compartment, and

- Dehumidification of the passenger compartment.

The thermal conditioning of the passenger compartment (heating, air conditioning and / or dehumidification) makes it possible to improve the comfort for the driver or passengers of the vehicle.

It is known from document FR-A1 -3017450 (in the name of the applicant), a refrigerant circulation device providing the air conditioning function, this device comprising a boiler, a condenser, a

Evaporator, pump, expander, ejector and compressor.

More specifically, in this circulating device of the prior art, the device is configured to operate according to three modes of operation, depending on the thermal load required.

A first mode of operation is used when there is not enough heat power available at the boiler. According to this first mode of operation corresponding to an air conditioning loop of traditional configuration, the refrigerant crosses in particular the condenser, the expander, the evaporator and the compressor. In this first mode of operation, the compressor alone makes it possible to obtain the capacity of

Desired cooling.

A second mode of operation is used when thermal power is available at the boiler and the need for cooling is relatively low. According to this second mode of operation corresponding to a second air conditioning loop, the refrigerant crosses in particular, the condenser, the pump, the boiler, the ejector, the expander, and the evaporator. In this second mode of operation, the ejector alone allows to obtain the desired cooling capacity.

A third mode of operation is used when thermal power is available at the boiler and the cooling requirements are relatively high. According to this third mode of operation, the refrigerant crosses in particular the condenser, the pump, the boiler, the ejector, the expander, the evaporator and the compressor. In this third mode of operation, the compressor and the ejector make it possible to obtain the desired cooling capacity.

It can be seen that over the course of a year, on a number of occasions, air conditioning requirements are low or even non-existent, and in other words that the circulation device operates below its maximum capacity or

15 is stopped.

We also note that when the need for air conditioning is low or nonexistent, the thermal energy available at the boiler is, respectively, exploited in part or not at all.

The object of the present invention is to provide a refrigerant circulation device for optimizing the use of thermal energy available at the boiler when the need for air conditioning is low or non-existent.

SUMMARY OF THE INVENTION

The subject of the invention is thus a refrigerant circulation device 25 for the thermal conditioning of a motor vehicle, comprising a so-called principal air-conditioning loop comprising a machine capable of operating as a compressor and an air-conditioning loop. said secondary, comprising a pump, the main and secondary loops being interconnected, characterized in that the machine is configured to allow a recovery of torque, in particular of mechanical torque, under the effect of an expansion of said refrigerant and the device is configured to connect the loops so that said refrigerant undergoes a cycle Rankine thermodynamics by circulating fluid in the pump and machine.

In particular, the term "interconnected" means that the main and secondary air conditioning loops are connected via a plurality of fluidic connections allowing the refrigerant to pass from one loop to the other.

The term "Rankine thermodynamic cycle" is intended to mean a thermodynamic cycle in which the refrigerant will successively undergo compression, in particular adiabatic compression, vaporization in particular isobaric, expansion in particular adiabatic and liquefaction in particular isobaric,

The device allows, throughout the year, to exploit the thermal energy available at the level of the boiler when the need for air conditioning is low or non-existent by generating a torque via the machine operating in torque recovery. The torque obtained may for example be transmitted, by a mechanical connection, to at least one mechanical receiver requiring the addition of a torque 15 to operate and / or be converted into electrical energy.

The device according to the invention can comprise one or more of the following characteristics, taken separately or in combination with each other:

the machine is able to function as a compressor in a first direction of circulation of the fluid and adapted to allow a recovery of torque in a second direction of circulation of the fluid, opposite to the first direction of circulation;

the main and secondary loops are configured to limit the energy consumption of the machine at least in certain modes of

Operation of the device;

the secondary loop comprises an ejector comprising a driving input, a suction inlet and an output;

the device comprises at least one boiler, a condenser, a first evaporator and a first expander;

The device is configured to circulate the fluid according to at least one of the following closed circuits:

A first closed circuit in which the fluid, driven by the pump, passes successively through at least the condenser, the boiler and then the machine operating in torque recovery before crossing the condenser again;

A second closed circuit in which the fluid, driven by the pump, passes successively through at least the condenser, a first portion of the fluid passing through the first expander and then the first evaporator before entering the ejector through the inlet of suction, a second part of the fluid passing through the boiler before separating into a third and a fourth part, the third part of the fluid passing through the machine operating in torque recovery before crossing the condenser again, the fourth part entering the ejector via the drive input, the first and fourth parts exiting the ejector through the outlet before traversing the condenser again;

the device is configured to circulate the fluid in a third closed circuit in which the fluid passes successively through at least the condenser,

A first part of the fluid passing through the pump and then the boiler before entering the ejector via the drive inlet, a second part of the fluid passing through the first expander and then the first evaporator before separating into a third and fourth part, the third part entering the ejector through the suction inlet, the fourth part passing through the machine

Operating as a compressor before traversing the condenser again, the first and third portions emerging from the ejector through the outlet before passing through the condenser again;

the device is configured to circulate the fluid in a fourth closed circuit in which the fluid passes successively through at least the condenser,

The first expander, the first evaporator and then the machine operating as a compressor before traversing the condenser again;

the device is configured to circulate the fluid in a fifth closed circuit in which the fluid passes successively through at least the condenser, a first portion of the fluid passing through the pump and then the front boiler

30 to enter the ejector through the drive inlet, a second portion of the fluid passing through the first expander and then the first evaporator before entering the ejector through the suction inlet, the first and second parts emerging from the ejector through the outlet before crossing the condenser again; the device comprises a second expander and a second evaporator;

the device is configured to circulate the fluid in a sixth closed circuit in which the fluid passes successively through at least the condenser, a first portion of the fluid passing through the pump and then the front boiler

5 to enter the ejector by the drive inlet, a second part of the fluid passing through the second expander and then the second evaporator before entering the ejector through the suction inlet, the first and second parts of the fluid exiting the ejector through the exit before crossing the condenser again;

- The device is configured to circulate the fluid in a seventh closed circuit in which the fluid passes through at least the condenser successively, a first portion of the fluid passing through the pump and the boiler before entering the ejector by the driving input, a second part of the fluid passing through the second regulator and then the second evaporator before entering

In the ejector via the suction inlet, a third portion of the fluid passing through the first expander, the first evaporator and the machine operating as a compressor before passing through the condenser again, the first and second parts emerging from the ejector through the outlet before traversing the condenser again;

The device is configured to circulate the fluid according to an eighth closed circuit in which the fluid passes successively through at least the condenser, a first portion of the fluid passing through the second expander and then the second evaporator before entering the ejector through the suction inlet, a second part of the fluid passing through the pump, the boiler before

Separating into a third and a fourth part, the third part of the fluid passing through the machine operating in torque recovery before passing through the condenser again, the fourth part entering the ejector via the drive inlet, the first and fourth parts fluid exiting the ejector through the outlet before passing through the condenser again;

The device comprises a heat exchanger able to exchange heat between the part of the refrigerant coming from the condenser and the part of the fluid intended to pass through the machine;

- the machine is connected to the pump by a clutch and / or a freewheel, the clutch and / or the freewheel being configured to allow the total or partial torque transmission, available at the machine operating in torque recovery, to the pump;

the device comprises components common to the main loop and the secondary loop;

the common components comprise at least the condenser, the first expander and the first evaporator.

The second subject of the invention is an assembly of a cooling circuit of a heat engine, the cooling circuit using a heat transfer fluid, and an exhaust line of the combustion gases coming from the heat engine, and of a device as described above, the boiler being able to exchange heat with the heat transfer fluid of the cooling circuit and / or with the combustion gases of the exhaust line.

DESCRIPTION OF THE FIGURES

Other features, details and advantages of the invention will emerge more clearly on reading the description given below as an indication in relation to drawings in which:

FIG. 1 is a schematic view of a first embodiment of the device,

FIG. 2 is a view of the device of FIG. 1, according to a first mode of operation,

FIG. 3 is a view of the device of FIG. 1, according to a second mode of operation,

FIG. 4 is a view of the device of FIG. 1, according to a third mode of operation,

FIG. 5 is a view of the device of FIG. 1, according to a fourth mode of operation,

FIG. 6 is a view of the device of FIG. 1, according to a fifth mode of operation,

FIG. 7 is a view of the device of FIG. 1, according to a first variant embodiment,

FIG. 8 is a schematic view of a second embodiment of the device, FIG. 9 is a view of the device of FIG. 8, according to a first variant embodiment,

FIG. 10 is a view of the device of FIG. 8, according to a second and third variant embodiment,

5 DETAILED DESCRIPTION

Figures 1 to 7 illustrate a refrigerant circulation device 1 for the thermal conditioning of a motor vehicle, according to a first embodiment.

The device 1 comprises a boiler 2, a condenser 3, a first evaporator 4, a reversible machine M, an ejector E, a bottle B for storing the refrigerant, a first expander D1, a pump P, a first valve V1 stop, a second valve V2 stop, a third valve V3 with three channels, a fourth valve V4 with three channels and a check valve C anti-return.

The boiler 2 may be able to exchange heat with a heat transfer fluid of a cooling circuit of a vehicle engine and / or with exhaust gases of such a heat engine.

The condenser 3 can be placed in front of the vehicle, so as to exchange heat with the outside air of the vehicle.

The first evaporator 4 can exchange heat with a flow of air F for entering the passenger compartment of the vehicle.

The reversible machine M comprises at least a first orifice 5 and at least a second orifice 6.

The reversible machine M is, on the one hand, able to function as a compressor, and in other words to compress the fluid entering through the first orifice 5, the fluid passing through the machine M from the first orifice 5 to the second orifice 6, this direction of circulation of the fluid being hereinafter called the first direction of circulation S1.

The reversible machine M is, on the other hand, configured to allow a

30 recovery torque under the effect of a relaxation of the fluid, and in other words to relax the fluid entering through the second orifice 6, the fluid passing through the machine M from the second orifice 6 to the first orifice 5, this direction of circulation of the fluid being hereinafter called second direction of circulation S2. Reversible means that a single machine M can operate as a compressor in the first flow direction S1 of the fluid, but also in torque recovery in the second direction of flow S2 of the fluid, opposite the first direction S1 circulation.

The ejector E comprises a driving input 7, a suction inlet 8 and an outlet 9. The ejector E is configured in that the refrigerant entering through the drive inlet 7 causes the suction of the refrigerant at the suction inlet 8, the entire refrigerant, mixed, finally being ejected through the outlet 9 of the ejector E.

According to an alternative embodiment not shown, the bottle B is integrated in the condenser 3.

The first expander D1 may for example be a thermostatic expansion valve or an electronic expansion valve known by the acronym EXV for

"Electronic Expansion Valve".

The device 1 comprises in particular a so-called main air-conditioning loop and a so-called secondary air-conditioning loop.

For the purposes of the invention, the term "main air conditioning loop" means an air conditioning loop in which the fluid passes through at least one evaporator and is circulated by the machine M operating as a compressor. By secondary air conditioning loop is meant an air conditioning loop in which the fluid passes through at least one evaporator and is circulated by the pump P.

As illustrated in Figure 1, the device 1 further comprises:

a first portion P1 connecting a first branch E1 to the first valve V1,

a second portion P2 connecting the first valve V1 to the inlet of the pump P,

a third portion P3 connecting the output of the pump P to the inlet of the boiler 2,

A fourth portion P4 connecting the outlet of the boiler 2 to a first channel of the third valve V3,

a fifth portion P5 connecting a second channel of the third valve V3 to a first channel of the fourth valve V4, a sixth portion P6 connecting a second channel of the fourth valve V4 to the second port 6 of the machine M, the second port 6 being an input when the machine M operates in torque recovery and an output when the machine M functions as a compressor a seventh portion P7 connecting the first port 5 of the machine M to a third branch E3, the first port 5 being an input when the machine M operates as a compressor and an output when the machine operates in torque recovery,

an eighth portion P8 connecting the first branch E1 to the first expander D1,

a ninth portion P9 connecting the first expander D1 to the inlet of the first evaporator 4,

a tenth portion P10 connecting the output of the first evaporator 4 to a second branch E2,

an eleventh portion P1 1 connecting the second branch E2 to the non-return valve C,

a twelfth portion P12 connecting the non-return valve C to the third branch E3,

a thirteenth portion P13 connecting the first branch E1 to the bottle B,

a fourteenth portion P14 connecting the bottle B to the outlet of the condenser 3,

a fifteenth portion P15 connecting the inlet of the condenser 3 to a fourth branch E4,

a sixteenth portion P16 connecting a third channel of the third valve V3 to the drive input 7 of the ejector E,

a seventeenth portion P17 connecting the second branch E2 to the suction inlet 8 of the ejector E,

an eighteenth portion P18 connecting the output 9 of the ejector E to the fourth branch E4,

a nineteenth portion P19 connecting the fourth branch E4 to a fifth branch E5,

a twentieth portion P20 connecting the fifth branch E5 to a third way of the fourth valve V4,

a twenty-first portion P21 connecting the fifth branch E5 to the second valve V2,

a twenty-second portion P22 connecting the second valve V2 to the third branch E3.

It is noted that the term "portion" means any device for establishing a fluid connection such as for example a pipe, a pipe, a pipe, etc.

It should be noted that the non-return valve C is configured to allow the passage of the fluid coming from the eleventh portion P1 1 towards the twelfth portion P12, and to prohibit the passage of the fluid coming from the twelfth portion P12 in the direction of the eleventh portion. P1 1.

Note that in Figures 2 to 6, the bodies which are not traversed by the refrigerant in the operating mode considered have been shown in dashed lines, the others being shown in solid lines.

FIG. 2 illustrates a first mode of operation of the device 1 in which the refrigerant flows in a fifth closed circuit. The first function mode corresponds to a secondary air conditioning loop. In this operating mode, the pump P is started, the machine M is stopped, the first valve V1 is open, the second valve V2 is closed, the first and

Third channels of the third valve V3 are open, the second channel of the third valve V3 is closed and all the channels of the fourth valve V4 are closed.

In this first mode of operation, the fluid passes successively through the condenser 3, the bottle B, a first part of the fluid passing through the

25 first valve V1, the pump P, the boiler 2 and the third valve V3 before entering the ejector E by the drive input 7, a second portion of the fluid passing through the first expander D1 and the first evaporator 4 before enter the ejector E through the suction inlet 8, the first and second parts of the fluid leaving the ejector E through the outlet 9 before crossing again the

Condenser 3.

In this first operating mode, calories are taken using the boiler 2, on the heat transfer fluid of the engine cooling circuit and / or on the exhaust gas of the engine. The condenser 3 evacuates the heat to the outside and the first evaporator 4 has the function of cooling the air flow F intended to enter the passenger compartment of the vehicle.

The first mode of operation can for example be used when the heat transfer fluid of the engine cooling circuit is hot (or the exhaust gases are sufficiently hot), that is to say when there is sufficient thermal power available at the level of the boiler 2, and that the needs for air conditioning are relatively low. This mode of operation is for example used when the ambient air temperature, and in other words outside the vehicle, is between 10 ° C and 25 ° C.

FIG. 3 illustrates a second mode of operation of the device 1 in which the refrigerant flows in a third closed circuit. The second mode of operation corresponds to the accumulation of a main air conditioning loop and a secondary air conditioning loop. In this operating mode, pump P is started, machine M operates as

15 compressor, the first valve V1 is open, the second valve V2 is closed, the first and third channels of the third valve V3 are open, the second channel of the third valve V3 is closed, the first channel of the fourth valve V4 is closed, the second and third channels of the fourth valve V4 are open.

In this second mode of operation, the fluid passes successively through the condenser 3, the bottle B, a first portion of the fluid passing through the first valve V1, the pump P, the boiler 2 and then the third valve V3 before entering the ejector E by the drive input 7, a second part of the fluid passing through the first expander D1 and then the first evaporator 4 before separating into a third and a fourth part, the third part entering the ejector E through the inlet 8, the fourth portion passing through the check valve C, the machine M operating as a compressor, the fourth valve V4 before crossing again the condenser 3, the first and third parts of the fluid leaving the ejector E by exit 9 before crossing to

30 again the condenser 3.

In the second mode of operation, calories are taken using the boiler 2, on the heat transfer fluid of the engine cooling circuit and / or on the engine exhaust gas. The condenser 3 evacuates the heat outside. Moreover, the first evaporator 4 has the function of cooling the air flow F intended to enter the passenger compartment of the vehicle.

The second mode of operation can for example be used when the heat transfer fluid of the engine cooling circuit is hot (or the exhaust gases are sufficiently hot), that is to say when there is sufficient power thermal available at the level of the boiler 2, and that the needs for air conditioning are relatively high. This mode of operation is for example used when the ambient air temperature, and in other words outside the vehicle, is between 10 ° C and 25 ° C or greater than 25 ° C.

FIG. 4 illustrates a third mode of operation of the device 1 in which the refrigerant flows in a fourth closed circuit. The third mode of operation corresponds to a main air conditioning loop. In this operating mode, the pump P is stopped, the machine M operates as a compressor, the first valve V1 is closed, the second valve V2 is closed, all the channels of the third valve V3 are closed, the first fourth valve V4 channel is closed, the second and third channels of the fourth valve V4 are open.

In this third mode of operation, the fluid passes successively through the condenser 3, the bottle B, the first expander D1, the first evaporator 4, the non-return valve C, the machine M functioning as a compressor and the fourth valve V4 before crossing. again the condenser 3.

In the third mode of operation, the first evaporator 4 is used to cool the air flow F intended to open into the passenger compartment of the vehicle and the condenser 3 discharges heat to the outside. The operation of the circuit is provided by the reversible machine M operating as a compressor.

This third mode of operation can for example be used when the engine is cold, and therefore when the heat transfer fluid of the cooling circuit is also cold, that is to say when there is not enough thermal power available. This mode of operation is for example used when the ambient air temperature, and in other words outside the vehicle, is between 10 ° C. and 25 ° C. greater than 25 ° C.

FIG. 5 illustrates a fourth mode of operation of the device 1 in which the refrigerant flows in a first closed circuit. In this operating mode, the pump P is started, the machine M operates in 5 torque recovery, the first valve V1 is open, the second valve V2 is open, the first and second channels of the third valve V3 are open, the third channel of the third valve V3 is closed, the first and second channels of the fourth valve V4 are open, the third channel of the fourth valve V4 is closed.

In this fourth mode of operation, the fluid passes successively through the condenser 3, the bottle B, the first valve V1, the pump P, the boiler 2, the third valve V3, the fourth valve V4, the machine M operating in recovery mode. torque then the second valve V2 before crossing again the condenser 3.

In the fourth mode of operation, the device 1 operates according to a Rankine thermodynamic cycle. Calories are taken using the boiler 2 on the heat transfer fluid of the engine cooling circuit and / or on the engine exhaust gas. The condenser 3 discharges heat outside. The relaxation of the refrigerant by the reversible machine M

20 operating in torque recovery can generate a torque.

By Rankine thermodynamic cycle is meant a thermodynamic cycle in which the refrigerant will successively undergo compression (pump P), vaporization (boiler 2), expansion (machine M) and liquefaction (condenser 3).

The fourth mode of operation can for example be used when the heat transfer fluid of the engine cooling circuit is hot (or the exhaust gases are hot enough), that is to say when there is sufficient thermal power available at the level of the boiler 2, and that the needs for air conditioning are zero. This mode of operation is

The example used when the ambient temperature of the air, and in other words outside the vehicle, is below 10 ° C.

FIG. 6 illustrates a fifth mode of operation of the device 1 in which the refrigerant flows in a second closed circuit. In this mode operating mode, the pump P is started, the machine M operates in torque recovery, the first valve V1 is open, the second valve V2 is open, all the channels of the third valve V3 are open, the first and second channels of the fourth valve V4 are open, the third channel of the fourth valve V4 is closed.

In this fifth mode of operation, the fluid passes successively through the condenser 3, the bottle B, a first portion of the fluid passing through the first expander D1 and then the first evaporator 4 before entering the ejector E via the suction inlet 8, a second part of the fluid passing through the first valve V1, the pump P, the boiler 2 before separating into a third and a fourth part in the third valve V3, the third part of the fluid passing through the fourth valve V4, the machine M operating in torque recovery then the second valve V2 before crossing again the condenser 3, the fourth part of the fluid entering the ejector E through the inlet

15, the first and fourth parts emerging from the ejector E through the outlet 9 before passing through the condenser 3 again.

In the fifth mode of operation, the device 1 operates on the one hand according to a Rankine thermodynamic cycle and on the other hand allows the cooling of the air flow F intended to lead into the passenger compartment of the vehicle via

The first evaporator 4, according to a secondary air conditioning loop. Calories are taken using the boiler 2, on the heat transfer fluid of the engine cooling circuit and / or on the engine exhaust gas. The condenser 3 discharges heat outside. The expansion of a portion of the refrigerant leaving the boiler 2 by the reversible machine M operating in 25 torque recovery can generate a torque.

The fifth mode of operation can for example be used when the heat transfer fluid of the engine cooling circuit is hot (or the exhaust gases are sufficiently hot), that is to say when there is sufficient power available at boiler level 2, and that

Air conditioning needs are low. This mode of operation is for example used when the ambient air temperature, and in other words outside the vehicle, is between 10 ° C and 25 ° C.

The obtained torque, when the device 1 operates according to the fourth and / or fifth mode of operation, can be transmitted, by a mechanical connection, to at least one mechanical receiver requiring the addition of a torque to operate and / or be converted into electrical energy by for example an electric generator.

The mechanical receiver may be for example an accessory of the engine and / or the engine and / or the pump P.

The reversible machine M could for example be linked to the pump P by a clutch and / or a freewheel. The clutch and / or the freewheel could thus be configured to allow the total or partial transmission of the torque, available at the level of the reversible machine M operating in torque recovery, to the pump P.

As a variant, the pump P may be driven for example by the heat engine and / or an electric motor.

The reversible machine M operating as a compressor may for example be driven by the heat engine and / or an electric motor.

The machine M could also for example be coupled to an electric motor generator capable of forming an electric motor driving the reversible machine M when the latter operates as a compressor, and able to form an electric generator driven by the reversible machine M when this Last 20 works in torque recovery.

According to a first variant of the first embodiment, represented in FIG. 7, the third and fourth valves V3, V4 comprising three channels are replaced by fifth, sixth and seventh stop valves V5, V6, V7.

According to this first embodiment shown in FIG. 7, the device 1 comprises:

a twenty-third portion P23 connecting the outlet of the boiler 2 to a sixth branch E6,

a twenty-fourth portion P24 connecting the sixth branch E6 to the fifth valve V5,

A twenty-fifth portion P25 connecting the sixth branch E6 to the sixth valve V6,

a twenty-sixth portion P26 connecting the fifth valve V5 to the driving input 7 of the ejector E, a twenty-seventh portion P27 connecting the sixth valve V6 to a seventh branch E7,

a twenty-eighth portion P28 connecting the seventh branch E7 to the seventh valve V7,

A twenty-ninth portion P29 connecting the seventh branch E7 to the second port 6 of the reversible machine M,

a thirtieth portion P30 connecting the seventh valve V7 to the fifth branch E5.

In this first embodiment, according to the modes of operation, the fifth, sixth and seventh valves V5, V6, V7 are configured as follows:

in the first mode of operation, the fifth valve V5 is open, the sixth and seventh valves V6, V7 are closed,

in the second mode of operation, the fifth and seventh valves V5, V7 are open, the sixth valve V6 is closed,

in the third mode of operation, the seventh valve V7 is open, the fifth and sixth valves V5, V6 are closed,

in the fourth mode of operation, the sixth valve V6 is open, the fifth and seventh valves V5, V7 are closed,

In the fifth mode of operation, the fifth and sixth valves V5, V6 are open and the seventh valve V7 is closed.

According to a second variant of the first embodiment, not shown, the device 1 could comprise at least one heat exchanger comprising a first part and a second part so as to form an IHX type exchanger (for Heat Internanl eXchanger, in English), this type of exchanger being designed to exchange heat between the refrigerant flowing through the first part and the refrigerant flowing through the second part.

The heat exchanger could for example be used to exchange heat between the refrigerant from the condenser 3 or the bottle B, and the part of the fluid intended to pass through the machine M when it operates as a compressor .

The first part could for example be reported on the eighth portion P8 and the second part on the eleventh portion P1 1.

The integration of such an exchanger would improve the performance of the device 1.

Figures 8 to 10 illustrate the refrigerant circulation device 1 for the thermal conditioning of the motor vehicle, according to a second embodiment.

Note that the common organs with the first embodiment retain the same numbering.

As shown in FIG. 8, in this second embodiment, the device 1 further comprises a second expander D2 and a second evaporator 10.

The second expander D2 may for example be a thermostatic expansion valve or an electrically controlled expander.

Advantageously, the first expander D1 is a thermostatic expansion valve 15 and the second expander D2 is an electrically controlled expander.

As shown in FIG. 8, according to the second embodiment, the device 1 further comprises:

a thirty-first portion P31 connecting the first branch E1 to an eighth branch E8,

A thirty-second portion P32 connecting the eighth branch E8 to the first expander D1,

a thirty-third portion P33 connecting the eighth branch E8 to the second expander D2,

a thirty-fourth portion P34 connecting the second expander D2 to the inlet of the second evaporator 10,

a thirty-fifth portion P35 connecting the output of the second evaporator 10 to the suction inlet 8 of the ejector E,

a thirty-sixth portion P36 connecting the outlet of the first evaporator 4 to the non-return valve C.

According to the first mode of operation, the refrigerant circulates in a sixth closed circuit, the fluid successively passing through the condenser 3, the bottle B, a first portion of the fluid passing through the first valve V1, the pump P, the boiler 2 and then the third valve V3 before entering the ejector E by the driving input 7, a second part of the fluid passing through the second expander D2 and then the second evaporator 10 before entering the ejector E by the suction inlet 8, the first and second parts of the fluid leaving the ejector E through the outlet 9 before crossing the condenser 3 again.

According to the second mode of operation, the refrigerant circulates in a seventh closed circuit, the fluid successively passing through the condenser 3, the bottle B, a first portion of the fluid passing through the first valve V1, the pump P, the boiler 2 and then the third valve V3 before entering the ejector E by the drive input 7, a second portion of the fluid passing through the second expander D D2 and the second evaporator 10 before entering the ejector E through the inlet d 8, a third part of the fluid passing through the first expander D1, the first evaporator 4, the non-return valve C, the machine M functioning as a compressor and then the fourth valve V4 before crossing again the condenser 3, the first and second parts of the fluid

15 exiting the ejector E through the exit 9 before crossing again the condenser 3.

In comparison with the first embodiment, the fact of having two evaporators 4, 10 makes it possible to distribute the needs for air conditioning, the flow of air F intended to open into the passenger compartment being cooled a first time during its

20 passes through the second evaporator 10 and then cooled a second time during its passage through the first evaporator 4. This architecture allows to have the refrigerant at a higher pressure at the suction inlet 8 of the ejector E and thus limit the amount of work to provide the reversible machine M operating as a compressor.

The third and fourth modes of operation, according to the second embodiment, are similar to the third and fourth modes of operation of the first embodiment.

According to the fifth mode of operation, the refrigerant circulates in an eighth closed circuit, the fluid successively passing through the condenser

3, the bottle B, a first portion of the fluid passing through the second expander

D2 then the second evaporator 10 before entering the ejector E by the suction inlet 8, a second portion of the fluid passing through the first valve V1, the pump P, the boiler 2 before separating into a third and a fourth part in the third valve V3, the third part of the fluid passing through the fourth valve V4, the machine M operating in torque recovery then the second valve V2 before crossing again the condenser 3, the fourth part entering the ejector E by the driving input 7, the first and fourth parts of the fluid leaving the ejector E through the outlet 9 before passing through the condenser 3 again.

According to a first variant of the second embodiment shown in FIG. 9, the device 1 comprises an eighth valve V8 comprising three channels.

According to this first variant represented in FIG. 9, the device 1 comprises:

a thirty-seventh portion P37 connecting the output of the second evaporator 10 to the first channel of the eighth valve V8,

a thirty-eighth portion P38 connecting the second channel of the eighth valve V8 to the suction inlet 8 of the ejector E,

a thirty-ninth portion P39 connecting the third channel of the eighth valve V8 to a ninth branch E9,

a 40th portion P40 connecting the outlet of the first evaporator 4 to the ninth branch E9,

a forty-first portion P41 connecting the ninth branch E9 to the non-return valve C.

This first variant makes it possible, when the device 1 operates according to the first and / or fifth modes of operation, to circulate the refrigerant fluid either:

only in the second evaporator 10 having the first and second channels of the eighth valve V8 open and the third channel of the eighth valve V8 closed,

- only in the first evaporator 4 having the second and third channels of the eighth valve V8 open and the first channel of the eighth valve V8 closed,

- Simultaneously in the first and second evaporators 4, 10 having all the channels of the eighth valve V8 open.

This first variant also allows, when the device 1 operates according to the third mode of operation, to simultaneously circulate the fluid in the first and second evaporators 4, 10 having the first and third channels of the eighth valve V8 open, and the second channel of the eighth valve V8 closed.

According to a second variant of the second embodiment shown in FIG. 10, the device 1 comprises ninth, tenth and eleventh stop valves V9, V10, V1.

According to this second variant represented in FIG. 10, the device 1 comprises:

a forty-second portion P42 connecting the outlet of the second evaporator changer 10 to the ninth valve V9,

a forty-third portion P43 connecting the ninth valve V9 to a tenth branch E10,

a forty-fourth portion P44 connecting the tenth branch E10 to the tenth valve V10,

a forty-fifth portion P45 connecting the tenth valve V10 to the suction inlet 8 of the ejector E,

a forty-sixth portion P46 connecting the tenth branch E10 to the eleventh valve V1 1,

A forty-seventh portion P47 connecting the eleventh valve V1 1 to an eleventh branch E1 1,

a forty-eighth portion P48 connecting the output of the first evaporator 4 to the eleventh branch E1 1,

a forty-ninth portion P49 connecting the eleventh branch 25 E1 1 to the non-return valve C.

This second variant makes it possible, when the device 1 operates according to the first and / or fifth modes of operation, to circulate the refrigerant either:

- only in the second evaporator 10 having the ninth

30 and tenth valves V9, V10 open and the eleventh valve V1 1 closed,

- only in the first evaporator 4 having the tenth and eleventh valves V10, V1 1 open and the ninth valve V9 closed,

- simultaneously in the first and second evaporators 4, 10 in having the ninth, tenth and eleventh valves V9, V10, V1 1 open.

This second variant further allows, when the device 1 operates in the third mode of operation, to simultaneously circulate the fluid in the first and second evaporators 4, 10 having the ninth and eleventh valves V9, V1 1 open, and the tenth closed V10 valve.

When the device 1 operates according to the first and / or fifth modes of operation, the first and second variants according to the arrangement of the evaporators 4, 10 and when the fluid flows only in o one of them, of circulating the fluid in the evaporator 4, 10 which will be crossed second by the air flow F to enter the passenger compartment to prevent any heating thereof.

According to this second variant, in the case where the first expander D1 is able to prevent the passage of the fluid in a sealed manner, the eleventh valve V1 1 15 may be omitted. In the same way, in the case where the second expander D2 is able to prevent the passage of the fluid tightly, the ninth valve V9 can be omitted.

According to a third variant of the second embodiment shown in FIG. 10, described in the first variant of the first embodiment, the

Third and fourth valves V3, V4 having three channels are replaced by the fifth, sixth and seventh valves V5, V6, V7 stop.

According to a fourth variant of the second embodiment, presented in the second variant of the first embodiment, the device 1 could comprise an IHX type heat exchanger (for Heat Internanl 25 eXchanger, in English) comprising a first part and a second part. part.

The heat exchanger could for example be used to exchange heat between the refrigerant from the condenser 3 or the bottle B, and the part of the fluid for passing through the machine M when it operates as a compressor.

The first part could for example be reported on the thirty-first portion P31 and the second portion on the thirty-sixth portion P36 or the forty-first portion P41 or the forty-ninth portion P49.

The invention also relates to a thermal conditioning method using the device 1 described above, according to the different operating modes mentioned.

Claims

1. Device (1) for circulating refrigerant for the thermal conditioning of a motor vehicle, comprising a loop of

5 air conditioning, said main, comprising a machine (M), able to operate in compressor, and a so-called secondary air conditioning loop, comprising a pump (P), the main and secondary loops being interconnected, characterized in that the machine ( M) is configured to allow torque recovery upon expansion of said refrigerant and the device (1) is configured to connect the loops such that said refrigerant undergoes a thermodynamic Rankine cycle in which circulating the fluid in the pump (P) and the machine (M).

2. Device (1) according to claim 1, characterized in that the machine (M) is able to function as a compressor in a first direction of circulation (S1) of the fluid and adapted to allow a recovery of torque according to a second flow direction (S2) of the fluid, opposite the first direction of circulation (S1).

3. Device (1) according to claim 1 or 2, characterized in that the main and secondary loops are configured to limit the power consumption of the machine (M) at least in certain operating modes of the device (1) .

4. Device (1) according to one of the preceding claims, characterized in that the secondary loop comprises an ejector (E) having a drive input (7), a suction inlet (8) and an outlet (9) .

5. Device (1) according to one of the preceding claims, characterized in that it comprises at least one boiler (2), a condenser (3), a first evaporator (4) and a first expander (D1).

6. Device (1) according to claim 5, characterized in that the device (1) is configured to circulate the fluid in at least one of the following closed circuits:

• a first closed circuit in which the fluid, driven by the pump (P) passes successively at least the condenser (3), the boiler (2) and the machine (M) operating in torque recovery before crossing again the condenser (3);

A second closed circuit in which the fluid, driven by the pump (P), passes successively through at least the condenser (3), a first portion of the fluid passing through the first expander (D1) and then the first evaporator (4) before enter the ejector (E) through the suction inlet (8), a second part of the fluid passing through the boiler (2) before separating into a third and a fourth part, the third part of the fluid passing through the machine (M) operating in torque recovery before crossing again the condenser (3), the fourth part entering the ejector (E) via the driving input (7), the first and fourth parts coming out of the ejector ( E) through the outlet (9) before crossing the condenser (3) again.

7. Device (1) according to claim 6, characterized in that the device (1) is configured to circulate the fluid in a third closed circuit in which the fluid passes successively through at least the condenser (3), a first part of the fluid passing through the pump (P) and then the boiler (2) before entering the ejector (E) via the drive inlet (7), a second portion of the fluid passing through the first expander (D1) and then the first evaporator ( 4) before separating into a third and fourth part, the third part entering the ejector (E) through the suction inlet (8), the fourth part passing through the machine (M) operating as a front compressor to cross again the condenser (3), the first and third parts leaving the ejector (E) through the outlet (9) before crossing again the condenser (3).

8. Device (1) according to claim 6 or 7, characterized in that the device (1) is configured to circulate the fluid in a fourth circuit in which the fluid passes successively through at least the condenser (3), the first expander (D1), the first evaporator (4) and the machine (M) operating as a compressor before passing through the condenser (3) again.

5

9. Device (1) according to one of claims 6 to 8, characterized in that the device (1) is configured to circulate the fluid in a fifth closed circuit in which the fluid passes through at least the condenser (3) , a first part of the fluid passing through the pump (P) then the boiler (2) before entering the ejector (E) via the drive inlet (7), a second part of the fluid passing through the first expander ( D1) then the first evaporator (4) before entering the ejector (E) via the suction inlet (8), the first and second parts emerging from the ejector (E) through the outlet (9) before crossing the condenser again (3).

15

10. Device (1) according to one of the preceding claims, characterized in that it comprises a second expander (D2) and a second evaporator (10).

20 1 1. Device (1) according to claim 10, characterized in that the device (1) is configured to circulate the fluid in a sixth closed circuit in which the fluid passes successively through at least the condenser (3), a first portion of the fluid passing through the pump (P) then the boiler (2) before entering the ejector (E) via the drive inlet (7), a second portion of the fluid 25 passing through the second expander (D2) and then the second evaporator (10). ) before entering the ejector (E) through the suction inlet (8), the first and second parts of the fluid leaving the ejector (E) through the outlet (9) before crossing again the condenser (3).

12. Device (1) according to claim 10 or 1 1, characterized in that the device (1) is configured to circulate the fluid in a seventh closed circuit in which the fluid passes successively through at least the condenser (3), a first portion of the fluid passing through the pump (P) and then the boiler (2) before entering the ejector (E) via the drive inlet (7), a second part of the fluid passing through the second expander (D2) and then the second evaporator (10) before entering the ejector (E) via the suction inlet (8), a third part of the fluid passing through the first expander ( D1), the first evaporator (4) and the machine (M) operating as a compressor before passing through the condenser (3) again, the first and second parts emerging from the ejector (E) through the outlet (9). ) before crossing the condenser again (3).

13. Device (1) according to one of claims 10 to 12, î o characterized in that the device (1) is configured to circulate the fluid in an eighth closed circuit in which the fluid passes through at least the condenser ( 3), a first portion of the fluid passing through the second expander (D2) and then the second evaporator (10) before entering the ejector (E) via the suction inlet (8), a second portion of the fluid passing through the pump 15 (P), the boiler (2) before separating into a third and a fourth part, the third part of the fluid passing through the machine (M) operating in torque recovery before crossing again the condenser (3) , the fourth part entering the ejector (E) via the drive inlet (7), the first and fourth parts of the fluid leaving the ejector (E) through the outlet (9) before passing through

20 again the condenser (3).

14. Device (1) according to one of claims 5 to 13, characterized in that it comprises a heat exchanger capable of exchanging heat between

The part of the refrigerant coming from the condenser (3) and the part of the fluid intended to pass through the machine (M).

15. Device (1) according to one of the preceding claims, characterized in that the machine (M) is connected to the pump (P) by a clutch and / or

A free wheel, the clutch and / or the freewheel being configured to allow the total or partial torque transmission, available at the machine (M) operating in torque recovery, to the pump (P) .

16. Assembly of a cooling circuit of a heat engine, the cooling circuit using a coolant, and an exhaust line of the combustion gases from the engine, and a device (1) according to one of claims 5 to 1 5, the boiler (2) being able to exchange heat with the heat transfer fluid of the cooling circuit and / or with the combustion gases of the exhaust line.