FR3051891B1 - AIR CONDITIONING SYSTEM, IN PARTICULAR FOR A MOTOR VEHICLE - Google Patents

Abstract

The invention relates to an air conditioning system for a compartment, comprising an external heat exchanger (OGC) for exchanging heat between a refrigerant (FF) and the air outside the compartment, a first indoor heat exchanger (E1) for exchanging heat between the refrigerant and the air to be blown inside the compartment, a second indoor heat exchanger (E2) for exchanging heat with the refrigerant (FF), an ejector (40), said ejector including a high pressure inlet (41) connected to a high pressure primary refrigerant circuit, and a low pressure inlet (42) connected to a low pressure secondary circuit of the refrigerant. According to the invention, the system is configured to operate in a heat recovery mode, in which the first indoor heat exchanger (E1) is in the secondary circuit and the second indoor heat exchanger (E2) is in the primary circuit, the external heat exchanger (OGC) is not traversed by the refrigerant.

Description

The invention relates to a system for conditioning a flow of air entering a compartment, for example a vehicle interior, especially a system for ventilation, heating and / or air conditioning of the compartment.

Motor vehicles are commonly equipped with a ventilation system, heating and / or air conditioning to change the air-temperature parameters of the air contained inside the cabin of the vehicle. Such modification is obtained from the delivery of a pulsed air flow inside the passenger compartment. In the case of an electric or hybrid vehicle, whose propulsion is provided at least partially by an electric motor, such a system is necessarily adapted to the permanent absence (electric vehicle) or temporary (hybrid vehicle) of hot source such as a thermal engine on this type of vehicles.

Such a system is expected to fulfill at least the following functions or modes: - Cooling, also known as air-conditioning, - Heating, - Dehumidification, ie the cooling of the pulsed air in the interior, which either in the cooling function or the heating function, so as to cause the condensation of part of the water vaporizer it contains.

Such a system comprises in known manner an air conditioning unit usually housed under a dashboard of the vehicle.

The housing includes a ventilation unit, it receives a flux of outside area and the draw for its delivery inside the cockpit. Inside this housing are usually housed a first heat exchanger for cooling the pulsed air to the passenger compartment of the vehicle and a second heat exchanger for heating the cabin. These different organs are connected to each other and to another heat exchanger, saidexterior, located in front of the vehicle to exchange heat with aflux of outside air, a circuit of pipes in which circulates a refrigerant fluid. This circuit further comprises a compressor, at least one expander suitable for decompressing the fluid and means such as valves for orienting the fluid differently in the different pipes according to the operating mode sought by the user.

This system can be used in cooling mode or heating mode. In cooling mode, the refrigerant is sent from the compressor to the external heat exchanger acting as a condenser where it is cooled by the outside air flow. Then, the refrigerant flows to a pressure reducer where it undergoes a lowering of its pressure before entering the first heat exchanger operating as an evaporator. The refrigerant fluid passing through the evaporator is then heated by the flow of air entering the ventilation system, which is correlatively reflected by a cooling of this air flow in order to air-condition the passenger compartment of the vehicle. The circuit being a closed loop, the refrigerant then returns to the compressor.

In heating mode, the refrigerant is sent from the compressor to the first and / or the second heat exchanger. The latter behave like condensers, in which the refrigerant is cooled by the air circulating in the ventilation system. This air therefore heats contact with the first and / or the second heat exchanger and thus provides calories to the passenger compartment of the vehicle. After passing through this or these exchangers, the refrigerant fluid is expanded by a pressure regulator before arriving in the external heat exchanger acting as an evaporator. It is then warmed by the outside air. The refrigerant then returns to the compressor.

Also known are systems comprising an ejector, that is to say a device comprising a high pressure inlet, a low pressure inlet and an outlet. The high pressure inlet has a nozzle, followed by a converging-diverging communicating with the low pressure inlet. The high-pressure primary fluid is accelerated and expanded within the converging-diverging, which creates a pressure drop that sucks the low-pressure secondary fluid. The ejector thus makes it possible to convert the work of relaxation into a work of compression of the refrigerant. The advantage of an ejector is then to increase the pressure of the fluid entering the compressor, and thus reduce the work required for compression by the compressor, which improves the efficiency of the cycle and therefore its coefficient of performance.

These systems usually comprise two circuits of refrigerant fluid. By convention, the fluid circuit connected to the high pressure input and the secondary circuit are called the primary circuit and the fluid circuit is connected to the low pressure inlet of the ejector. These systems also usually comprise, downstream of the ejector, a gas-liquid phase separator, the gas phase being sucked by the compressor and circulating in the primary circuit, the liquid phase being sucked by the ejector into the secondary circuit. Thus, it is known from EP 1 327 838 an air conditioning systemcomprising an ejector, a gas-liquid separator, a primary circuit and a secondary circuit, capable of performing the functions of cooling and heating as well as the dehumidification function, in cooling mode and heating mode.

The systems with known ejector are however not entirely satisfactory because their configuration does not give access to some useful modes of operation. The invention aims to overcome the disadvantages mentioned above andonconcerne for this purpose, an air conditioning system for acompartiment, comprising: - an external heat exchanger to achieve a heat exchange between the refrigerant and air to the outside the compartment; a first internal heat exchanger for exchanging heat between the refrigerant and the air to be blown inside the compartment; a second indoor heat exchanger for performing a heat exchange involving the refrigerant; an ejector comprising: a high-pressure inlet connected to a high-pressure refrigerant primary circuit, and a low-pressure inlet connected to a low-pressure secondary circuit of the refrigerant; characterized in that the system is configured to operate in a heat recovery mode in which the first indoor heat exchanger is in the secondary circuit and the second indoor heat exchanger is in the primary circuit, the outdoor heat exchanger is not being crossed by the coolant cooler. The invention thus makes it possible to carry out heat recovery, that is to say to ensure heating of the passenger compartment only by means of the first and second heat exchangers of the housing, without having to resort to the external heat exchanger. . This mode is used when the outdoor temperature is low and the outdoor heat exchanger, which in heating mode operates as an evaporator, frost or is about to frost. We then use the own heat of the cabin which, at this stage, is normally already at a certain temperature.

In other embodiments that can be taken together or separately: the system is configured to further operate in a cool mode to cool the compartment and / or a warm up mode to warm the compartment, the second interior heat exchanger is configured to perform a heat exchange between the refrigerant and the air to be blown inside the compartment and said second indoor heat exchanger is disposed on a downstream air side of the first indoor heat exchanger, - the air conditioning system comprises in addition a compressor in the primary circuit for sucking and compressing the refrigerant, - said system comprises a branch connecting a compressor outlet to the second exchanger and said system is configured to be able to supply the second exchanger refrigerant fluid leaving the compressor without supplying the first exchanger fluid refrigerant leaving the compressor, - the air conditioning system further comprises a gas-liquid separator for separating the refrigerant refrigerant and refrigerant liquid, located downstream of the ejector and upstream compressor, coupled to the compressor so that the refrigerant gas was sucked by the compressor, the air conditioning system furthermore comprises a first expansion element disposed in a refrigerant passage connecting a outlet of the gas-liquid separator and the first indoor heat exchanger, which can take an open position in which the refrigerant fluid which the cross is relaxed and a closed position; said outlet is advantageously the gas outlet; the air conditioning system furthermore comprises a second expansion member disposed in a refrigerant passage connecting a outlet of the gas-liquid separator and the external heat exchanger, which can take an open position in the refrigerant flowing through it is expanded and a closed position; said outlet is advantageously the gas outlet, - said system is configured so that, in the heat recovery mode, the refrigerant circulates in: • the primary circuit, provided comprising in this order the gas-liquid separator, the compressor, the second exchanger of the internal heat, and the high-pressure inlet of the ejector, the secondary circuit, comprising in this order the gas-liquid separator, the first expansion member in an open position, the first indoor heat exchanger and the low-pressure inlet of the ejector, the second expansion member being in a closed position, - said system is configured so that, in the cooling mode, the refrigerant circulates in: • the primary circuit, provided in this order comprising the gas separator - liquid, the compressor, the external heat exchanger and the high pressure inlet of the ejector, the secondary circuit, provided in this order the gas-liquid separator, the first expansion member in an open position, the first indoor heat exchanger and the low-pressure inlet of the ejector, the second expansion member being in a closed position, - said system is configured so that, in a dehumidification - cooling mode, the refrigerant circulating in the primary circuit is furthermore circulated in the second internal heat exchanger, in parallel with the external heat exchanger, - said system is configured so that, in the heating mode, the refrigerant circulates in: • the primary circuit, comprising in this order the gas-liquid separator, the compressor, the second internal heat exchanger, and the high pressure inlet of the ejector, • the secondary circuit, provided in this order the gas separator - liquid, the second detent in a positi the external heat exchanger and the low-pressure inlet of the ejector are opened, the first expansion element being in a closed position, said system being configured so that, in a dehumidification-heating mode, the refrigerant circulates in: • the primary circuit, comprising in this order the gas-liquid separator, the compressor, the second internal heat exchanger, and the high-pressure inlet of the ejector, • a secondary circuit comprising in this order the gas-liquid separator and in parallel:> the first expansion member in an open position, the first indoor heat exchanger and the low pressure inlet of the ejector,> the second expansion member in an open position, the external heat exchanger and the the low pressure inlet of the ejector, the first and / or the second expansion element is a sealed pressure regulator, the first and / or second organ detent comprises an expander and a valve mounted in series after or before said expander with respect to the fluid flow direction, - said system comprises: • a first valve located on a branch of the secondary circuit connecting the external heat exchanger and the ejector, • A second valve located on a branch of the primary circuit linking the compressor and the external heat exchanger, • A third valve located on the branch of the primary circuit linking the compressor and the second indoor heat exchanger, - the air conditioning system comprises in addition: • A first non-return valve mounted in series with the first valve and passing in the direction of the external heat exchanger towards the ejector, • A second non-return valve connected in series with the second expansion member and passing through the direction of the compressor to the external heat exchanger, • A third non-return valve mounted on a primary circuit branch connecting the external heat exchanger and the ejector and passing in the direction of the external heat exchanger to the ejector, - the air conditioning system further comprises an internal heat exchange unit, said unit comprising a first and a second refrigerant passage of the primary circuit, the first passage being located between an outlet of the gas-liquid separator and the compressor, the second passage being located between the outlet of at least one exchanger of said primary circuit and the ejector; said outlet is advantageously the exitgaz of the separator, the air conditioning system furthermore comprises a set comprising a third expander and a third exchanger, mounted together, the assembly being mounted in parallel with the first internal heat exchanger, the third exchanger is integrated in a third circuit furthermore comprising a remote heat exchanger and in which a first coolant circulates, - the air conditioning system further comprises another exchanger, mounted between an outlet of the ejector and the gas-liquid separator, - said second inner heat exchanger is configured to perform heat exchange between the refrigerant and a second heat transfer fluid; - the second indoor heat exchanger is integrated in a fourth circuit in which the second heat transfer fluid flows andcomprising in addition a fourth inner heat exchanger, said fourth heat exchanger being for heat exchange between the air to be blown inside the compartment and said second coolant, said fourth exchanger being disposed on a downstream air side of the first indoor heat exchanger.

Embodiments and variants will be described hereinafter, as non-limiting examples, with reference to the accompanying drawings in which:

FIGS. 1A and 1B are respectively a schematic representation and a more complete representation of an air conditioning system according to the invention, in air conditioning mode,

FIGS. 2A and 2B are respectively a schematic representation and a more complete representation of the system of FIG. 1, in air-conditioning dehumidification mode,

FIG. 2C is a schematic representation of a variant, according to the invention, of the system of FIG.

FIGS. 3A and 3B are respectively a schematic representation and a more complete representation of the system of FIG. 1, in heating mode,

FIGS. 4A and 4B are respectively a schematic representation and a more complete representation of the system of FIG. 1, in heating dehumidification mode,

FIGS. 5A and 5B are respectively a schematic representation and a more complete representation of the system of FIG. 1, in heat recovery mode,

FIG. 6 is a diagrammatic representation of a variant according to the invention of the system of FIG. 1,

FIGS. 7A and 7B are diagrammatic representations of two embodiments of a variant of the system of FIG.

FIG. 8 is a schematic representation of a variant according to the invention of the system of FIG. 1,

Figure 9 is a recovery of the system of Figure 1.

The inlets and outlets of the exchangers correspond to the directions of flow of the coolant indicated by the arrows in the figure.

Figures ΙΑ, 2A, 3A, 4A and 5A are schematic and simplified representations of the air conditioning system according to the invention, in its different operating modes.

The system includes a refrigerant circulation loop.The fluid is selected from, for example, carbon dioxide, fluorocarbon and a hydrocarbon.

In these figures, the configuration of said loop is shown in simplified form by only showing the parts traversed by circulating refrigerant fluid. Only the main organs are represented. Not shown, including the valves that can route the circuit with its pipes in this or that mode.

Said loop comprises a primary circuit C1 having one or more OGC or E2 exchangers, operating in condenser mode, that is to say heating the air passing through it, and a secondary circuit C2 comprising one or more OGC or El exchangers, operating in evaporator mode, that is to say heating the air that passes through them.

Said system comprises an ejector 40 such as, for example, that described above. Said ejector 40 is common to both circuits C1, C2. It comprisesa high pressure input 41, connected to the primary circuit C1, and a low pressure input 42, connected to the secondary circuit C2. By high pressure, it is understood that the refrigerant is received in the liquid or gaseous phase at high pressure. At low pressure, it is meant to accept the refrigerant in gaseous phase, or diphasic in general, at low pressure.

The system further comprises a separator 50 for separating the liquid and gaseous phases of the refrigerant FF. This separator can also have a refrigerant storage or buffer functionFF. An outlet 43 of the ejector 40 is connected to an inlet of a liquid-gas separator 50. The primary circuit C1 is connected to a gas outlet 51 of the liquid-gas separator 50 and the secondary circuit C2 is connected to a liquid outlet 52 of the separator. 50. In other words, the gas-liquid separator 50 is located at the interface of the two circuits C1, C2.

A compressor 10 is also provided in the primary circuit C1, below the gas outlet of the separator 50.

FIGS. 1B, 2B, 3B, 4B and 5B are schematic and complete diagrams of the system in its various modes of operation, ie comprising all its organs and the way in which they are positioned.

In these figures, the following convention is used for cabling: - the pipes traversed by refrigerant FF under high pressure are represented in long thick dashes, - the pipes traversed by refrigerant under low pressure are represented by dashes during thick, - the pipes not traversed by fluid in the mode considered are represented in fine continuous lines.

Refrigerant control members FF (valves, expansion valves) are operable by a control unit (not shown) and can be put in the open or closed position; they comprise a barrier bar when they are in the closed position in the mode considered.

As illustrated in these various figures and as shown in Figure 9, the system comprises: - the compressor 10, - the ejector 40, - the gas-liquid separator 50, - an external heat exchanger OGC to achieve an exchange of heat between the refrigerant and the air outside the compartment, - a first internal heat exchanger El to achieve a heat exchange between the refrigerant and the air to be blown inside the compartment, - a second internal heat exchanger E2 for performing a heat exchange involving the refrigerant, - a first 33 and a second 34 expansion members, preferably sealed, and a first 61, a second 62 and a third 63vannes, allowing or not the circulation refrigerant in such branch out of the circuit to switch the system from one mode to another, in their open or closed state, - a pr 64, a second 65 and a third 66 check valves to ensure proper flow of refrigerant in the chosen mode.

In said system, there is observed: - a first refrigerant passage or pipe 101 connecting the outlet 43 of the ejector and the inlet of the gas-liquid separator 50, - a second pipe 102 connecting the liquid outlet 52 of the gas-liquid separator 50 and a input 01 of the OGC external exchanger, andcomprising in this order, according to the direction of flow of the refrigerant, the second expander 34 and the second nonreturn valve 65, mounted in the separator direction towards the external exchanger, - a third pipe 103 connecting an outlet 02 of the OGC external heat exchanger and the low pressure inlet 42 of the ejector, and comprising in this order, according to the direction of flow of the refrigerant, the first valve61 and the first non-return valve 64 , mounted in the external exchanger-to-ejector direction, - a fourth pipe 104 connecting the gas outlet 51 of the gas-liquid separator 50 and the inlet 01 of the echo external OGC, and comprising a low pressure portion of an internal heat exchanger 70, the compressor 10and the second valve 62; As shown, this pipe 104 comprises a common part with the second pipe 102, serving for the connection to the inlet 01 of the OGC external heat exchanger, - a fifth pipe 105 connecting the outlet 02 of the OGC outer heat exchanger and the upper inlet pressure 41 of the ejector, and comprisingthree-second check valve 66 mounted passing in the direction external exchangeror ejector and a high pressure part of the internal heat exchanger 70, as shown, this pipe 105 has a common part with the third pipe 103, serving for the connection to the OGC external exchanger outlet 02, - a sixth pipe 106 connecting the liquid outlet 52 of the gas-liquid separator 50 and an inlet of the first exchanger E1, and comprising the first expander 33; As shown, this pipe 106 has a common portion with the second pipe 102 serving for connection with the liquid outlet 52 of the separator 50, - a seventh pipe 107 connecting an outlet of the first heat exchanger EL and the low pressure inlet 42 of the ejector 40 ; As shown, this channelization 108 has a common portion with the third pipe 103, serving to connect with the low pressure inlet 42 of the ejector, - an eighth pipe 108 connecting the gas outlet 51 of the gas-liquid separator 50 and a input of the second indoor heat exchanger E2 and comprising the compressor 10 and the third valve 63; as shown, this pipe108 has a common part with the fourth pipe 104 serving to connect with an outlet of the compressor, - a ninth pipe 109 connecting an outlet of the second inner heat exchanger E2 and the high pressure inlet 41 of the ejector 40; as shown, this pipe 109 has a common part with the fifth pipe 105, serving for connection to the high pressure inlet 41 of the ejector.

The sealed expansion valves 32, 33, the valves 61, 62, 63 and the non-return valves 64, 65, 66 are located on portions of the pipes of the system which do not form a part common with other pipes.

The regulators 33, 34 are called sealed expansion valves in that they can take in particular an open position and a closed position, the opening of the sealed expansion valves can be reduced or increased depending on the desired temperature. In other embodiments, a sealed expander can be replaced by a single expansion valve and a valve, connected in series.

The valves 61, 62, 63 are here two-way valves. Alternatively, the seconds and third valves 62, 63 are replaced by a three-way valve at the bifurcation of the fourth and eighth conduits 104, 108.

In the practical embodiment of the housing, the first and second internal exchangers E1, E2 are traversed by the same pulsed air flow. The second exchanger E2 is placed downstream of the first exchanger E1, an arrangement that is shown in FIGS. 1B, 2B, 3B, 4B and 5B by placing the exchangers facing each other. In these figures, the flow of air passing through the two inner heat exchangers E1, E2 is illustrated, as the case may be, by the arrow curve F.

Figures IA and IB illustrate the system according to the invention in the air conditioning mode.

As illustrated in FIG. 1A: the primary circuit C1 comprises, downstream of the gas-liquid separator 50, the compressor 10 mounted for sucking and compressing the gas phase of the refrigerant, the OGC external exchanger and a return to the high-pressure inlet 41 the ejector 40; the refrigerant gas is heated by the compression it undergoes in the compressor; the external OGC exchanger operates as a condenser: it is traversed by the outside air to which it gives up calories, the refrigerant fluid is cooled and returns at least partially in liquid phase; The secondary circuit C2 comprises, downstream of the liquid-gas separator 50, the first expander 33 for expanding the refrigerant fluid FF, the first internal exchanger E1 and a return to the low-pressure inlet 42 of the ejector 40; the first expander 33vaporizes at least partially and thus cools the refrigerant fluid; the internal heat exchanger El operates as an evaporator: it is crossed by air coming from outside or, in moderecyclage, air from the passenger compartment and intended for the passenger compartment, from which it takes calories; the pulsed air intended for the passenger compartment is therefore cooled; the refrigerant is then sucked by the low pressure inlet 42 of the ejector 40. In FIG. 1B, it can be seen that the primary circuit C1 comprises in this order: the fourth pipe 104 connecting the gas outlet 51 of the gas-liquid separator 50 and the input 01 of the external exchanger OGC operating as a condenser, the second valve 62 then being in open position; the refrigerant can not go to the second exchanger E2 because the third valve 63 is in closed position; the fluid can not either go to the first internal exchanger El because the second non-return valve 65 opposes; - The pipe 105 connecting the outlet 02 of the OGC outer heat exchanger and the high pressure inlet 41 of the ejector 40, having the third non-return valve 66 in the forward direction; the fluid can not go to the low pressure inlet 42 of the ejector because the first valve 61is in the closed position. The internal exchanger 70 of the primary circuit C1 (not shown in FIG. 1A) is designed to allow exchanges of heat between two branches of the primary circuit C1, a first branch situated between the gas-liquid separator 50 and the compressor 10, belonging to the pipe 104, and a second branch belonging to the pipe 105. This internal exchanger 70 is mainly in air conditioning mode by improving the COP (Coefficient of Performance) of the system.

The secondary circuit C2 comprises in this order: the pipe 106 connecting the liquid outlet of the liquid-gas separator 50 and the inlet of the first exchanger E1 operating in a vaporizer, preceded by the first expander 33; the refrigerant fluid EL can not go to the external exchanger OGC because the second expander 34 is closed; - The pipe 107 connecting the outlet of the first exchanger El and the low pressure inlet 42 of the ejector 40; the fluid can not go to the OGC external exchanger because the first non-return valve 64 opposes it; in any event, the first valve 61 is closed.

Note that in this mode of operation, the pulsed air flow Is not influenced by the second internal exchanger E2 which is notcouru by the refrigerant.

FIGS. 2A and 2B illustrate the system according to the invention in the modu dehumidification in air conditioning. In FIG. 2A, it can be seen that it differs from the diagram of the circuit in the modeclimatization of FIG. 1A only by putting the second internal exchanger E2, operating as a condenser, in parallel with the external exchanger OGC. The second internal heat exchanger E2 is also placed in the situation of being able to give up heat. In FIG. 2B, with respect to FIG. 1B, it can be seen that the primary circuit C1 further comprises: the eighth duct 108 connecting the gas outlet 51 of the separator 50 and the inlet of the second internal exchanger E2, simply by virtue of the opening of the third valve 63 downstream of the compressor 10, the ninth pipe 109 connecting the outlet of the second internal exchanger E2 and the high pressure inlet 41 of the ejector 40; the refrigerant FF can not go to the external exchanger OGC because the third non-return valve 66 of the pipe 105 is opposed.

The secondary circuit is unchanged from Fig. 1B.

To obtain the dehumidification mode, the first heat exchanger El is set at a very low temperature by restricting the opening of the first expander33; the pulsed air F is therefore very cooled and dehumidified but, in order not to overcool the passenger compartment, it is heated by the second exchanger E2.

In the embodiments illustrated in FIG. 2B, a mixing point 80 of the pipes 105 and 109 is located downstream of the internal exchanger 70. In other embodiments, it could be located upstream as shown in FIG. 2C.

FIGS. 3A and 3B illustrate the system according to the invention in the heating mode. In FIG. 3A, it can be seen that: the external exchanger OGC is now in the secondary circuit C2, it is preceded by the second expander 34 and thus used as an evaporator, the second internal exchanger E2 is in the primary circuit C1, is used in condenser. In FIG. 3B, it can be seen that the primary circuit C1 comprises in this order: the pipes 108 and 109 already described, the second internal exchanger E2 operating as a condenser, the third valve 63 being in the open position; the fluid passing through the eighth duct 108 can go towards the OGC external exchanger since the second valve 62 of the fourth duct 104 is in the closed position; the fluid passing through the ninth pipe 109 can not go to the external exchanger OGC because the third non-return valve 66 of the fifth line 105 is opposed.

The secondary circuit C2 comprises in this order: the second duct 102 connecting the gas outlet 51 of the gas-liquid separator 50 and the inlet 01 of the external exchanger OGC operating as an evaporator, the second expander 34 being in the open position and the second flapper anti-return 65 being in the past passing; the refrigerant can not go to the first internal exchanger E1 since the first expander 33 upstream of the first internal exchanger E1 is in the closed position, the duct 103 connecting the outlet 02 of the external exchanger OGCand the low pressure inlet 42 of the ejector 40, the first valve 61 being in the open position and the first valve 64 in the passing direction, the refrigerant can not be directed to the high pressure inlet 41 of the ejector 40 although the third non-return valve 66 of the fifth line 105 is in the passing direction because it is blocked by the high pressure that exists downstream of this valve.

Note that in this mode of operation, the pulsed air flow F is not influenced by the first inner heat exchanger El which is notcouru refrigerant.

Figures 4A and 4B illustrate the system according to the invention in the modedhumidification in heating. In FIG. 4A, it can be seen that it differs from the diagram of the circuit in heating mode of FIG. 3A only by putting in parallel the first internal exchanger E1, preceded by the first expander 33, with the external exchanger OOGC. The first internal heat exchanger El is therefore also put in a position to also be able to absorb heat. In FIG. 4B, with respect to FIG. 3B, it can be seen that the secondary circuit C2 further comprises the pipes 106 and 107 previously described and the first internal heat exchanger E 1 functioning as an evaporator, simply by virtue of the opening of the expansion valve 33 upstream of said first exchanger inside. The pipes 102 and 107 have a common point 90.

The primary circuit C1 is unchanged with respect to FIG. 3B.

Figures 5A and 5B illustrate the system according to the invention in the heat recovery moderation. In FIG. 5A, it can be observed that in this mode, the first internal heat exchanger E1 and the second internal heat exchanger E2 are alone in function and in each of the different circuits: primary circuit C1 for the second internal heat exchanger E2 and secondary circuit C2 for the first internal heat exchanger E In FIG. 5B, it can be seen that the primary circuit C1 comprises the ducts 108 and 109 already described and the second internal exchanger E2 operating as a condenser, the third valve 63 being in the open position; the refrigerant FF can not go to the external exchanger OGC because: the second valve 62 of the fourth pipe 104 is in closed position, the third non-return valve 66 of the fifth pipe 105 opposes it.

The secondary circuit C2 comprises the pipes 106 and 107 already described; the first internal heat exchanger El, comprising upstream the first expander 33, in the open position, operates as an evaporator; the fluid can not be directed to the external exchanger OGC because - the second expander 34 of the second duct 102 is in closed position, - the first non-return valve 64 of the third duct 103 is opposed thereto; it is noted that the position of the first valve 61 of the third pipe 103 is indifferent because the refrigerant netraverse OGC outdoor exchanger.

In this mode of operation, the OGC external exchanger is not circulated by the refrigerant. In the heating mode described above in relation to FIGS. 3A and 3B, the air conditioning-heating circuit operates as a heat pump, that is to say that it takes heat from the outside area through the heat exchanger. OGC exterior. When the outdoor temperature becomes close to 0 °, the operation of the outdoor exchangerOGC is no longer optimum and it can frost. The heat recovery mode allows, at least temporarily, to continue to provide heat to the habitat, through the second indoor heat exchanger E2 because the latter produces more heat than the first heat exchanger El produces cold.

As can be seen from the foregoing and according to the invention, it is noted that in the proposed system: the first exchanger E1, when it is in operation, is always in the secondary circuit C2, and the second exchanger E2, when it is in operation, is always in the primary circuit Cl, - only the external heat exchanger OGC, when it is in operation, changes of assignment between the primary circuit Cl and the secondary circuit C2.

The system according to the invention thus makes it possible to obtain the five functions or desired operating modes, this with only three mono-directional valves 61, 62, 63 and two sealed expansion valves 33, 34, an equivalent of five valves. It is a kind of number substantially inferior to the systems of the state of the art; in addition, state-of-the-art systems often use four-way valves which are complex objects.

The table below gives the position of these bodies.

These different positions are obtained, for example, using the control unit, according to user requests.

In all the modes described above, the refrigerant FF circulates in the exchangers E1, E2, OGC always in the same direction, namely from the bottom upwards in the figures for the first and the second exchanger E1, E2, and from top to bottom for the OGC external exchanger. There may be an interest in recirculating the refrigerant in the opposite direction in some modes, in particular the heating mode for the OGC external exchanger. As a consequence, the notions of "input" 01 and "output" 02 of the external exchanger OGCare arbitrary because they can be inverted.

Figure 6 illustrates such a variant in heating mode. It can be seen, in comparison with FIG. 3B, that the primary circuit C1 is unchanged but that the secondary circuit C2 comprises: a third duct 103 'connecting the liquid outlet of the gas-liquid separator of the separator 50 and the "outlet" 02 of the exchanger

external OGC acting as an inlet, this pipecomportant a second expander 34 'and a second non-return valve 65' mounted in the direction from the separator to the outer exchanger; a second pipe 102 'connecting the' inlet 'of the external exchanger OGC acting as an outlet and the low pressure inlet 42 of the ejector 40, this pipe 102' comprising the first valve 61 'in the open position and a first valve -return 64 'in the direction passing from the exchanger to the separator and taking again part of the seventh pipe 107 already described.

Another alternative embodiment is illustrated in FIG. 7A. In this variant the system comprises a third circuit C3 in which circulates a first heat transfer fluid FC1, for example glycol water, comprising: a third internal exchanger E3, acting as an evaporator, placed below a third expander 35, said third exchanger interior and said expander being connected in parallel with the first heat exchanger Elet of the first expander 33; the third exchanger E3, unlike the first exchanger E1, is not traversed by the incoming air flow F, - a remote exchanger E'3, associated with a member 100 such asbattery, - pipes connecting the third internal exchanger E3 and the remote exchanger E'3 and transporting the first coolant CF1, for example by a pump, not shown.

The third circuit C3 is thus dedicated to the cooling of the member 100.

The third expander 35 can be controlled independently of the first expander 33 associated with the first exchanger E1. Because, like the first exchanger E1, this third internal exchanger E3 is always in the secondary circuit C2, it is easy to see that it can be put in five operating modes described above.

Another embodiment of this variant is illustrated in FIG. 7B. The third internal exchanger E3, acting as an evaporator, is this timeplaced on the first pipe, between the outlet 43 of the ejector 40 and the gas-liquid separator 50. figure, the third circuit C3 associated third exchanger E3 is not shown.

Another variant embodiment is illustrated in FIG. 8. In this variant, the system comprises a fourth circuit C4 in which circulates a second heat transfer fluid FC2, for example brine, comprising: the second internal exchanger E2, but which does not is not crossed by the flow of pulsed air F; consequently, this exchanger has a different structure, enabling it to exchange heat between the refrigerant fluid FF and the second heat transfer fluid FC2, - a fourth internal exchanger E4 acting as a heating radiator, designed to exchange heat between the flow of heat. pulsed airF and the second heat transfer fluid FC2, - pipes connecting the second inner heat exchanger E2 and the fourth inner heat exchanger E4 and in which circulates the second heat transfer fluid FC2 for example by means of a pump, not shown.

In this configuration, the heat exchange functions with the pulsed air flow F and the heat exchange with the refrigerant FF are decoupled.

Claims (9)

1. Air conditioning system for a compartment, comprising: - an external heat exchanger (OGC) for exchanging heat between a refrigerant (FF) and the air outside the compartment; a first indoor heat exchanger (El) for exchanging heat between the refrigerant and the air to be blown inside the compartment; - a second indoor heat exchanger (E2) for performing a heat exchange involving the refrigerant (FF); - an ejector (40) comprising: • a high-pressure inlet (41) connected to a high-pressure refrigerant primary circuit, and • a low-pressure inlet (42) connected to a low-pressure secondary circuit of the refrigerant; characterized in that the system is configured, by control of a control unit, to operate in a heat recovery mode, in which the first indoor heat exchanger (El) is in the secondary circuit and the second indoor heat exchanger ( E2) is located in the primary circuit, the external heat exchanger (OGC) not being traversed by the refrigerant. 2. An air conditioning system according to the preceding claim, characterized in that the system is configured to operate further in a cooling mode for cooling the compartment and / or a heating mode for heating the compartment. 3. Air conditioning system according to one of claims 1 or 2, characterized in that the second inner heat exchanger (E2) is configured to perform a heat exchange between the refrigerant (FF) and the air (F) in front of blowing inside the compartment and in that said second indoor heat exchanger (E2) is disposed on a downstream air side of the first indoor heat exchanger (E1). 4. An air conditioning system according to one of the preceding claims, characterized in that it further comprises a compressor (10) in the primary circuit (Cl) for sucking and compressing the refrigerant fluid (FF). 5. Air conditioning system according to claim 4, characterized in that it further comprises a gas-liquid separator (50) for separating the refrigerant refrigerant gas and refrigerant, located downstream of the ejector ( 40) and upstream of the compressor (10), coupled to the compressor so that the refrigerant gas is sucked by the compressor. 6. Air conditioning system according to claim 5, characterized in that it further comprises a first expansion member (33) disposed in a refrigerant passage connecting an outlet of the gas-liquid separator (50) and the first exchanger heat sink (El), which can assume an open position in which the refrigerant (FF) passing therethrough is expanded and a closed position. 7. Air conditioning system according to claim 6, characterized in that it further comprises a second expansion member (34) disposed in a refrigerant passage connecting an outlet of the gas-liquid separator (50) and the exchanger of external heat (OGC), which can assume an open position in which the refrigerant (FF) flowing through it is expanded and a closed position. 8. An air conditioning system according to claim 7, in which said system is configured so that, in the heat recovery mode, the refrigerant (FF) flows in: - the primary circuit (C1), provided with in this gas-liquid separator (50), compressor (10), second indoor heat exchanger (E2), and high-pressure inlet (41) of ejector (40), - secondary circuit (C2), comprising in this order the gas-liquid separator (50), the first expansion member (33) in an open position, the first indoor heat exchanger (El) and the low-pressure inlet (42) of the ejector ( 40), the second detent member (34) being in a closed position. 9. The air conditioning system according to one of claims 7 or 8, wherein, said system is configured so that, in the cooling mode, the refrigerant (FF) circulates in: - the primary circuit (Cl), provided comprising in this order the gas-liquid separator (50), the compressor (10), the external heat exchanger (OGC) and the high-pressure inlet (41) of the ejector (40), - the secondary circuit (C2 ), having in this order the gas-liquid separator (50), the first expansion member (33) in an open position, the first indoor heat exchanger (El) and the low-pressure inlet (42) of the ejector (40), the second detent member (34) being in a closed position. An air conditioning system according to claim 9, wherein said system is configured so that in a dehumidification-cooling mode, the refrigerant (FF) flowing in the primary circuit further flows into the second indoor heat exchanger ( E2), in parallel with the external heat exchanger (OGC). 11. An air conditioning system according to one of claims 7 to 10, wherein, said system is configured so that in the heating mode, the refrigerant (FF) flows in: the primary circuit, provided in this order the gas-liquid separator (50), the compressor (10), the second internal heat exchanger (E2), and the high-pressure inlet (41) of the ejector (40), the secondary circuit, provided with in this order the gas-liquid separator (50), the second expansion member (34) in an open position, the external heat exchanger (OGC) and the pressure inlet (42,43) of the ejector (40), the first detent member (33) being in a closed position. 12. The air conditioning system according to one of claims 7 to 10, wherein, said system is configured so that in a dehumidification mode - heating, the refrigerant (FF) circulates in: - the primary circuit, provided with in in this order the gas-liquid separator (50), the compressor (10), the second internal heat exchanger (E2), and the high-pressure inlet (41) of the ejector (40), the secondary circuit, provided with in this order the gas-liquid separator (50) and, in parallel: • the first expansion element (33) in an open position, the first indoor heat exchanger (El) and the low-pressure inlet (42) of the ejector (40), • the second expansion member (34) in an open position, the external heat exchanger (OGC) and the low pressure inlet (42, 43) of the ejector (40). 13. An air conditioning system according to one of claims 7 to 12, wherein the first and / or second expansion member (33, 34) is a sealed pressure reducer. The air conditioning system according to one of claims 7 to 12, wherein the first and / or second expansion member (33, 34) comprises an expander and a valve mounted in series after or before said expander with respect to flow direction of the fluid. 15. An air conditioning system according to any one of claims 4 to 14, wherein said system comprises a connectingelelienant an output of the compressor (10) to the second exchanger (E2) anditsitsystem is configured so as to power the second exchanger (E2) refrigerant leaving the compressor (10) without supplying the first exchanger (El) refrigerant leaving the compressor (10). 16. An air conditioning system according to the preceding claim, comprising: - a first valve (61) located on a branch of the secondary circuiterelienieur the external heat exchanger (OGC) and the ejector (40), - a second valve (61) 62) located on a branch of the primary circuit linking the compressor (10) and the external heat exchanger (OGC), - a third valve (63) located on the branch of the primary circuiteleliant the compressor (10) and the second inner heat exchanger (E2). 17. An air conditioning system according to claim 16, characterized in that it further comprises: a first non-return valve (64) connected in series with the first valve (61) and passing in the direction of the external heat exchanger (OGC) to the ejector (40), - a second non-return valve (65) connected in series with the second expansion member (34) and passing in the direction of the compressor (10) towards the heat exchanger external heat (OGC), - a third non-return valve (66) mounted on a branch of the primary circuit (C1) connecting the external heat exchanger (OGC) and the ejector (40) and passing in the direction of the exchanger from outside heat to the ejector. 18. An air conditioning system according to one of claims 4 to 17, characterized in that it further comprises an internal heat exchange unit (70), said unit comprising a first and a second refrigerantpass of the primary circuit, the first passage being located between the outlet of the gas-liquid separator (50) and the compressor (10), the second passage being located between the outlet of at least one exchanger of said primary circuit (OGC, E2) and the ejector (40) . 19. An air conditioning system according to one of the preceding claims, characterized in that it further comprises a setcomportant a third expander (35) and a third exchanger (E3), connected in series, the assembly being mounted in parallel of the first indoor heat exchanger (El). 20. An air conditioning system according to claim 19, characterized in that the third heat exchanger (E3) is integrated in a third circuit (C3) further comprising a remote heat exchanger (E '3) and in which circulates a first coolant ( FC1). 21. An air conditioning system according to one of claims 1 to 19, characterized in that it further comprises another exchanger (E3), mounted between an outlet (43) of the ejector (40) and the separator gas - liquid (50). 22. Air conditioning system according to one of claims 1,2 and 4 to 20, characterized in that said second inner heat exchanger (E2) is configured to perform a heat exchange between the refrigerant (FF) and a second coolant (FC2). 23. An air conditioning system according to claim 22, characterized in that the second indoor heat exchanger (E2) is integrated in a fourth circuit (C4) in which circulates the second heat transfer fluid (FC2) and further comprising a fourth heat exchanger interior (E4), said fourth exchanger being provided for effecting a heat exchange between the air (F) to be blown inside the compartment and said second heat transfer fluid (FC2), said fourth exchanger (E4) beingposed on one side downstream of the first indoor heat exchanger (El).