Air conditioning unit for a vehicle
The air conditioning system addresses fog and CO2 issues in recirculated air by using a heat pump circuit with a single heat exchanger and air dehumidification, achieving reduced humidity and CO2 levels for improved vehicle comfort and efficiency.
Patent Information
- Authority / Receiving Office
- FR · FR
- Patent Type
- Patents
- Current Assignee / Owner
- VALEO SYST THERMIQUES SAS
- Filing Date
- 2024-06-06
- Publication Date
- 2026-06-19
Smart Images
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Abstract
Description
Title of the invention: Air conditioning unit for a vehicle
[0001] The invention relates to an air conditioning unit for a vehicle, in particular for a motor vehicle.
[0002] Nowadays, the search for energy savings in vehicle thermal comfort systems tends to favor air recirculation modes (thus avoiding the use of fresh air from outside the vehicle). However, this can lead to certain safety problems due to increased humidity inside the vehicle (especially in cold weather) with the formation of fog on the windshield, causing visibility problems. Furthermore, a high rate of air recirculation can cause an increase in CO2 concentration in the passenger compartment that can exceed 2000 ppm, a level that induces drowsiness.
[0003] In particular, there is a need to remedy the above problems.
[0004] The invention thus relates to an air conditioning system, in particular configured to equip a vehicle, especially a motor vehicle, comprising: - a heat pump circuit in which a refrigerant is used, in particular a refrigerant of type R744 or R1234yf or R290, and configured to operate selectively in cooling mode and in heating mode; - an air conditioning system equipped with a heat exchanger configured to cool or heat air circulating in the air conditioning system, this heat exchanger being the only heat exchanger in the air conditioning system heated or cooled directly or indirectly by the refrigerant from the heat pump circuit; - an air treatment module including an air dehumidification device, preferably located upstream of the air conditioning system configured to dehumidify air passing through the air conditioning system.
[0005] In the case where the single heat exchanger is heated or cooled "directly" by the refrigerant of the heat pump circuit, this single heat exchanger is configured to be traversed by the refrigerant of the heat pump circuit.
[0006] In the case where the single heat exchanger is heated or cooled "indirectly" by the refrigerant of the heat pump circuit, the single heat exchanger is configured to be traversed by an intermediate heat transfer fluid which is cooled or heated by a bi-fluid intermediate heat exchanger suitable for traversing the intermediate heat transfer fluid and the refrigerant of the heat pump circuit.
[0007] The term "single heat exchanger of the air conditioning system heated or cooled directly or indirectly by the refrigerant of the heat pump circuit" or "single heat exchanger capable of being heated or cooled directly or indirectly by a refrigerant of a heat pump circuit" means that the air conditioning system contains only one heat exchanger thermally connected to the heat pump. The implementation of an additional heat exchanger in the air conditioning system, such as an additional electric heater to heat the airflow circulating in the air conditioning system, remains possible.
[0008] According to one embodiment, "the single heat exchanger of the air conditioning system heated or cooled directly or indirectly by the refrigerant of the heat pump circuit" is the single heat exchanger of the air conditioning system.
[0009] According to one aspect of the invention, the heat pump circuit includes an external heat exchanger which is outside the air conditioning system.
[0010] According to one aspect of the invention, the external heat exchanger is configured to be placed on a front face of a vehicle.
[0011] According to one aspect of the invention, the external heat exchanger is a gas cooler in the case where the refrigerant is R744.
[0012] According to one aspect of the invention, the gas cooler is configured to cool the R744 refrigerant without phase change.
[0013] According to one aspect of the invention, the external heat exchanger is an evaporator-condenser, particularly in the case where the refrigerant is R1234yf.
[0014] According to one aspect of the invention, the external heat exchanger is a gas evaporator-cooler.
[0015] According to one aspect of the invention, the heat pump circuit includes an internal heat exchanger (designated by the acronym IHX) configured to transfer heat between a low pressure part and a high pressure part of the heat pump circuit.
[0016] According to one aspect of the invention, the heat pump circuit includes an accumulator placed in the low pressure part, in particular upstream of a compressor, configured to ensure the absence of liquid refrigerant entering the compressor, in particular this accumulator being further placed upstream of the internal heat exchanger (designated by the acronym IHX).
[0017] According to one aspect of the invention, when the heat pump circuit includes an accumulator, the heat exchanger in the air conditioning system is configured to operate, in air conditioning mode, in co-current with respect to the airflow passing through it in the case of a direct type heat pump.
[0018] Co-current operation makes it possible in particular to obtain a two-phase fluid at the evaporator outlet at a temperature lower than the inlet temperature. The efficiency is better.
[0019] In the case of an indirect type heat pump, it is in particular the intermediate two-fluid heat exchanger which is configured to operate, in air conditioning mode, in co-current for the two fluids (intermediate heat transfer fluid and refrigerant fluid).
[0020] According to one aspect of the invention, the heat pump circuit includes a receiver dryer filter placed in the high pressure part of the heat pump circuit.
[0021] In this case, the heat pump circuit may be without an internal heat exchanger.
[0022] When the heat pump circuit includes a receiver dryer, the heat exchanger in the air conditioning system can be configured to operate in counter-current to the airflow passing through it in the case of a direct type heat pump.
[0023] In the case of an indirect type heat pump, it is in particular the intermediate two-fluid heat exchanger which is configured to operate in counter-current for the two fluids (intermediate heat transfer fluid and refrigerant fluid).
[0024] According to one aspect of the invention, the filter dryer operates with a refrigerant of the type R1234yf.
[0025] According to one aspect of the invention, the heat pump circuit includes an expansion valve configured to produce, in heating mode, an expansion of the refrigerant before the refrigerant is evaporated in the external heat exchanger.
[0026] According to one aspect of the invention, the external heat exchanger is configured to condense the refrigerant fluid, in air conditioning mode.
[0027] According to one aspect of the invention, the only heat exchanger in the air conditioning system is an evaporator-condenser configured to operate as an evaporator in air conditioning mode (to produce cold) and as a condenser in heating mode (to generate heat).
[0028] According to one aspect of the invention, the heat pump circuit is configured so that the direction of refrigerant flow is reversed in air conditioning mode and in heating mode in the outdoor heat exchanger.
[0029] According to another aspect of the invention, the heat pump circuit is configured so that the direction of refrigerant flow is reversed in air conditioning mode and in heating mode in the heat exchanger of the air conditioning system.
[0030] According to another aspect of the invention, the heat pump circuit is configured so that the direction of refrigerant flow is reversed in air conditioning mode and in heating mode, both in the outdoor heat exchanger and in the heat exchanger of the air conditioning system.
[0031] According to another aspect of the invention, the heat pump circuit is configured so that the direction of refrigerant flow is the same in air conditioning mode and in heating mode in the heat exchanger of the air conditioning system, and the direction of refrigerant flow is reversed in air conditioning mode and in heating mode in the outdoor heat exchanger.
[0032] According to another aspect of the invention, in air conditioning mode, the refrigerant, after the heat exchanger of the air conditioning system, passes through the accumulator and the internal heat exchanger, then (as a gaseous refrigerant) through the compressor. In heating mode, the refrigerant, after the external heat exchanger, passes through the accumulator and the internal heat exchanger, then (as a gaseous refrigerant) through the compressor. By changing modes, the direction of flow in the external heat exchanger is reversed.
[0033] According to one aspect of the invention, the heat pump circuit comprises: - two regulators, - a shut-off valve, also known as a "shut-off valve," placed between the outdoor heat exchanger and the storage tank, - multi-way valves, including two three-way valves.
[0034] This configuration requires fewer valves overall and offers better efficiency on the heat exchangers because it allows for co-current flow in cooling mode (so the pressure drop helps lower the fluid temperature, which boosts heat exchange) and counter-current flow in heating mode (the hottest refrigerant is in contact with the already preheated air). Generally, co-current flow is preferred in cooling mode.
[0035] According to another aspect of the invention, the heat pump circuit comprises: - two expansion valves, - a shut-off valve, also known as a "shut-off valve," placed between the outdoor heat exchanger and the storage tank, - multi-way valves, including two three-way valves, - a one-way valve.
[0036] According to another aspect of the invention, the heat pump circuit comprises: - two expansion valves, - a shut-off valve, also known as a "shut-off valve" placed between the external heat exchanger and the accumulator, - multi-way valves, including three three-way valves, - a one-way valve.
[0037] According to one aspect of the invention, the heat pump circuit is configured so that the direction of refrigerant flow is reversed in air conditioning mode and in heating mode in the heat exchanger of the air conditioning system, and the direction of refrigerant flow is the same in air conditioning mode and in heating mode in the outdoor heat exchanger.
[0038] According to another aspect of the invention, the heat pump circuit is configured so that the direction of refrigerant flow is the same in air conditioning mode and in heating mode, both in the outdoor heat exchanger and in the heat exchanger of the air conditioning system.
[0039] The heat pump circuit can be of the direct type, or alternatively of the indirect type, for example when the refrigerant includes propane (or R290).
[0040] In the case of an indirect heat pump, at least one water exchanger is added in a known manner, which then supplies the heat exchanger of the air conditioning system.
[0041] As a reminder, in co-current flow, the two fluids flow in the same direction.
[0042] Against the current, the two fluids flow in opposite directions.
[0043] Upstream of the HVAC, the air dehumidification device is notably under the hood.
[0044] According to one variant, the air dehumidification device is downstream, for example in the vehicle's passenger compartment, and therefore the air first passes through the air conditioning system and then through the dehumidification device.
[0045] The invention also relates to a method for managing an air conditioning system as described above, comprising the following steps: - operate the entire air conditioning system in air conditioning mode, or - operate the entire air conditioning system in heating mode.
[0046] The invention also relates to an air conditioning system, in particular for equipping an air conditioning unit as mentioned above, this system comprising a single heat exchanger capable of being heated or cooled directly or indirectly by a refrigerant fluid from a heat pump circuit.
[0047] Because there is a single heat exchanger, the air conditioning system can be devoid of a mixing chamber and / or mixing damper.
[0048] According to a preferred embodiment, this single heat exchanger is configured so that it can be bypassed by a bypass duct, placed in particular above the heat exchanger, i.e. in the opposite direction to the direction taken by the condensate when it falls by gravity.
[0049] According to a preferred embodiment, a flap is placed in the bypass duct to prohibit or allow the airflow, at least partially, to bypassing this single heat exchanger. This allows for better management of temperature stratification at the high and low outlet(s) of the air conditioning system.
[0050] The invention thus relates to an air conditioning system for a vehicle, in particular for a motor vehicle, comprising, on the one hand, an air conditioning system for a predetermined enclosure such as a vehicle passenger compartment and, on the other hand, an air handling module, the air handling module comprising: - an air inlet configured to be supplied, in operation, at least in part by indoor air taken from the predetermined enclosure; - a capture device configured to capture CO2 contained in the air passing through the air treatment module; - an air dehumidification device that passes through the air treatment module; - a treated air outlet configured to deliver air treated by the air handling module to the air conditioning system.
[0051] According to one aspect of the invention, the dehumidification device is devoid of an evaporator-type heat exchanger. The dehumidification device includes, in particular, a desiccant, for example a desiccant wheel, or any other type of means known for dehumidifying air.
[0052] According to one aspect of the invention, the maximum air treatment flow rate by the air conditioning system is for example between 400 and 600 m3 / h, in particular between 450 m3 / h and 550 m3 / h, for example 500 m3 / h.
[0053] According to one aspect of the invention, the air handling module is sized so that the maximum air flow treated in the air handling module is less than the maximum air flow treated in the air conditioning system.
[0054] According to one aspect of the invention, the air conditioning system is devoid of a fresh air inlet.
[0055] According to one aspect of the invention, the air conditioning unit is devoid of a fresh air inlet.
[0056] Air coming from outside the vehicle is called "fresh air".
[0057] The present invention allows operation without using fresh air, by using air recirculation from only the passenger compartment (also called 100% air recirculation mode).
[0058] The invention is advantageous in that the sizing of the air handling module provides a treatment capacity that corresponds to only a portion, namely strictly less than 100%, of the maximum airflow treated by the air conditioning system, in particular less than 70%, especially less than 50%, for example less than 40%. The air handling module can thus have a reduced footprint. The lower the proportion of airflow treated, the smaller the treatment module can be. The inventors observed satisfactory results in terms of the size / air quality trade-off with a treated airflow proportion (relative to the maximum airflow of the air conditioning system) between 25% and 60%, particularly between 30% and 50%. This differs from the case where an air treatment module would be designed to deliver 100% of the air volume used by the air conditioning system. In that case, the air treatment module would require greater capacity and therefore a larger footprint, resulting in a higher cost.
[0059] In the invention, it has been found that dehumidifying only a part of the air that passes through the air conditioning system is sufficient to perform the windshield defogging function usually performed by the air conditioning system.
[0060] The invention thus makes it possible to eliminate the need for the fresh air intake demisting function of the air conditioning system. This notably reduces the electrical consumption of the air conditioning system.
[0061] In summary, the 100% air recirculation provided by the air conditioning unit according to the invention makes it possible to eliminate CO2 and humidity from the air. If necessary, only a portion of the airflow required for thermal comfort needs to be treated (for example: 180 m³ / h), thus ensuring the removal of water and the treatment of CO2.
[0062] According to one aspect of the invention, the air handling module is sized to deliver treated air in a proportion at least twice as small as the treatment capacity of the air conditioning system; in other words, in a proportion less than half the treatment capacity of the air conditioning system.
[0063] Advantageously the air handling module is configured to deliver treated air with a flow rate of 180 m3 / hour (generally a flow rate which can be chosen between 125 and 300 m3 / h, in particular between 150m3 / h and 250m3 / h), for a treatment capacity by the air conditioning system which is 500 m3 / hour.
[0064] According to one aspect of the invention, the air treatment module is configured to be able to treat air coming only from the predetermined enclosure (for example the passenger compartment).
[0065] According to one aspect of the invention, the air conditioning unit is configured to be able to process air coming only from the predetermined enclosure (for example, the passenger compartment).
[0066] According to one aspect of the invention, the air conditioning unit is configured so that the air conditioning system receives a mixture of air coming solely from: - from the enclosure, directly, in other words without treatment; - of the processing module.
[0067] The invention makes it possible, in particular, thanks to this air treatment module, to dehumidify the air without using an evaporator in the air conditioning system. For example, the air conditioning system can operate without an evaporator when it delivers hot air (heating mode), thus reducing the cost of such a system, which can be of a simpler design. In other words, the air conditioning system can be exempt from the air dehumidification function when it is in heating mode. That is to say, the dehumidification of the air passing through the air conditioning system can be carried out entirely by the treatment module in heating mode.If the air conditioning system includes a refrigerant exchanger of the evaporator type, it can be used as an evaporator, but only in air conditioning mode, to cool the passenger compartment (i.e., not in dehumidification or heating mode).
[0068] If desired, the conventional air conditioning system includes an evaporator.
[0069] According to one aspect of the invention, the treated air outlet of the treatment module The air is configured to be placed opposite an air intake of the air conditioning system.
[0070] According to one aspect of the invention, the treated air outlet of the air treatment module has a smaller cross-section than the cross-section of the air inlet of the air conditioning system.
[0071] This allows the air conditioning system to draw not only air from the air treatment module but also air taken directly from the passenger compartment (and therefore not treated by the air treatment module).
[0072] According to one aspect of the invention, the air outlet of the air handling module is configured to be located at a non-zero distance from the air inlet of the air conditioning system.
[0073] Thus, it is not necessary to physically connect the air outlet of the air treatment module to the air conditioning system.
[0074] Alternatively, the air outlet of the air handling module is connected to the air conditioning system.
[0075] According to one aspect of the invention, the air handling module includes a motor-fan unit (or “Blower” in English), in particular of axial or radial type, to force air circulation within the air handling module.
[0076] According to one aspect of the invention, the motor-fan group is provided in addition to a main motor-fan group, in particular of axial or centrifugal-axial type, which equips the ventilation system.
[0077] Alternatively, the air handling module is without a motor-fan unit.
[0078] According to one aspect of the invention, the air outlet of the air treatment module is placed opposite the inlet of a motor-fan unit belonging to the air conditioning system.
[0079] According to one aspect of the invention, the motor-fan group of the air conditioning system can be of axial or centrifugal-axial type.
[0080] In the invention, the airflow coming out of the air treatment module is calibrated using, for example, one or more flaps which regulate the passage of air coming out of the air treatment module.
[0081] Thus the air treatment module can be equipped with one or more flaps which regulate the passage of air at the outlet of the air treatment module.
[0082] According to one aspect of the invention, the capture device configured to capture CO2 contained in the air passing through the treatment module is configured to adsorb the CO2.
[0083] According to one aspect of the invention, the CO2 capture device comprises an activated carbon or other adsorbent filter and / or a metallo-organic structure filter.
[0084] Other means of capturing gases, in particular polluting gases, may be provided in the air treatment module.
[0085] According to one aspect of the invention, the air treatment module comprises one or more particle filters.
[0086] For example, the air treatment module includes a high-efficiency air filter, specifically called a HEPA filter in English (for High Efficiency Particulate Air).
[0087] According to one aspect of the invention, the air treatment module may include a vacuum pump or an air pump or a motor-fan unit (or any other suitable means) for forcing dry air used for dehumidification to pass through the dehumidification device.
[0088] If dehumidification is required, the flow rate through the air treatment module is chosen to be between 180 and 250 m3 / hour.
[0089] According to one aspect of the invention, the air treatment module forms an autonomous module independent of the air conditioning system.
[0090] The air treatment module allows, for example, the adsorption and / or absorption of substances such as CO2 and H2O (in vapor form in particular), and also nitrogen oxides (NOx) and / or volatile organic compounds.
[0091] According to one aspect of the invention, the air conditioning system comprises a single heat exchanger, for example, an evaporator-condenser. The evaporator-condenser is configured to operate as an evaporator in "summer" mode (in warm weather, i.e., air conditioning mode) and as a condenser in "winter" mode (in cold weather, i.e., heating mode). For example, in warm weather (or air conditioning mode), dehumidification is performed by the evaporator-condenser (in evaporator mode) of the In an air conditioning system, during cold weather (or heating mode), dehumidification is handled by the air handling unit and not by the evaporator-condenser, which then functions as a condenser. In other words, the invention allows for a single heat exchanger in the air conditioning (or HVAC) system: in "summer" mode, this heat exchanger performs an evaporation function (air conditioning mode), and in "winter" mode, this heat exchanger performs a heating function (heating mode). The invention thus eliminates the need for two successive heat exchangers used between the air conditioning and heating modes (namely, an evaporator for dehumidification followed by a heater to warm the air to the desired temperature).
[0092] According to one aspect of the invention, the air conditioning unit is configured to be able to dehumidify the air in the passenger compartment by means of an evaporator of the air conditioning system, in "summer" mode (i.e., in air conditioning mode).
[0093] Thus, in this case, the air treatment module is not used at all or not used alone to dehumidify the passenger compartment air. If desired, the treatment module can be used in "summer" mode in conjunction with the air conditioning system's evaporator.
[0094] In other words, the air conditioning system is configured to be able to deactivate or bypass the air handling module when the air handling module is not used to dehumidify the passenger compartment air. If the air handling module is not used to dehumidify the air, it is configured to allow air to pass through. To this end, the air handling module is configured to be able to be deactivated to allow air to pass through, thus enabling the flow rate necessary for comfort, and simultaneously allowing CO2 treatment.
[0095] According to one aspect of the invention, the air conditioning assembly includes a control unit configured to control the type of air to be sent into the air conditioning system, the type of air being chosen in particular from air treated by the air treatment module, air coming directly from the predetermined enclosure such as a passenger compartment, or a mixture of the two.
[0096] According to one aspect of the invention, the control unit is configured to control a flap which, depending on its angular position, modifies the treated / untreated air ratio to be sent into the air conditioning system.
[0097] The invention further relates to an air treatment method using an air conditioning unit comprising an air conditioning system and an air treatment module as described above, the method comprising the following step: - deliver air treated by the air treatment module, which represents only a part of the maximum treatment flow rate by the air conditioning system.
[0098] The invention also relates to an air treatment module comprising: - an air inlet configured to be supplied, in operation, at least in part by indoor air taken from a predetermined enclosure such as a vehicle passenger compartment; - a capture device configured to capture CO2 contained in the air passing through the air treatment module; - a device for dehumidifying the air that passes through the treatment module; - a treated air outlet configured to deliver air treated by the capture device and the dehumidification device to an air conditioning system of the predetermined enclosure, the air handling module being sized so that the maximum air flow treated in the air handling module is less than the maximum air flow treated by the air conditioning system.
[0099] The air handling module can be stand-alone, or be a module combined with the air conditioning (HVAC) system.
[0100] In the case of a self-contained air handling module, a motor-fan unit may be provided.
[0101] In the case of a module combined with the air conditioning (HVAC) system, an actuator and a flap / flaps are provided to manage the airflow required for the air intake of the air conditioning (HVAC) system in order to ensure that a sufficient portion of the recycled air passes through the air handling module.
[0102] Other features, details and advantages of the invention will become clearer upon reading the following description on the one hand, and several illustrative and non-limiting examples of embodiments given with reference to the accompanying schematic drawings on the other hand, in which:
[0103] [Fig-1] Fig. 1 is a schematic, perspective view of a set of air conditioning for a vehicle according to an example of an embodiment of the invention;
[0104] [Fig.2] Fig.2 is a perspective diagram of the air conditioning system of the [Fig.l], according to a different view;
[0105] [Fig.3] [Fig.3] is a schematic representation of the air conditioning assembly of the [Fig.1], illustrating the air paths;
[0106] [Fig.4] Fig.4 is a schematic representation of an alternative embodiment of the [Fig.3];
[0107] [Fig.5] The [Fig.5] is a schematic representation of another variant embodiment of the [Fig.3];
[0108] [Fig.6] The [Fig.6] is a schematic representation of another variant embodiment of the [Fig.3],
[0109] [Fig.7] Fig.7 is a schematic representation of the air conditioning system according to the invention, which comprises a single heat exchanger,
[0110] [Fig.8A] Fig.8A is a schematic representation of a heat pump circuit according to an example of the invention, operating in air conditioning mode.
[0111] [Fig.8B] [Fig.8B] is a schematic representation of the heat pump circuit of [Fig.8A], operating in heating mode,
[0112] [Fig.9A] Fig.9A is a schematic representation of a heat pump circuit according to another embodiment of the invention, operating in air conditioning mode,
[0113] [Fig.9B] [Fig.9B] is a schematic representation of the heat pump circuit of [Fig.9A], operating in heating mode,
[0114] [Fig. 10A] [Fig. 10A] is a schematic representation of a heat pump circuit according to another embodiment of the invention, operating in air conditioning mode,
[0115] [Fig. 10B] [Fig. 10B] is a schematic representation of the heat pump circuit of [Fig. 10A], operating in heating mode,
[0116] [Fig. 11 A] The [Fig. 11 A] is a schematic representation of a pump circuit heat according to another example of the invention, operating in air conditioning mode,
[0117] [Fig. 1 IB] The [Fig. 1 IB] is a schematic representation of the heat pump circuit of the [Fig. 11 A], operating in heating mode,
[0118] [Fig. 12] The [Fig. 12] is a schematic representation of an embodiment of the invention with an indirect type heat pump circuit,
[0119] [Fig. 13] The [Fig. 13] is a schematic, cross-sectional representation of the air conditioning system of the [Fig.7].
[0120] The features, variants, and different embodiments of the invention can be combined in various ways, provided they are not incompatible or mutually exclusive. In particular, variants of the invention may be conceived comprising only a selection of features, described hereafter in isolation from the other described features, if this selection of features is sufficient to confer a technical advantage and / or to differentiate the invention from the prior art.
[0121] Figures 1 and 2 show an air conditioning unit 100 for a motor vehicle, comprising, on the one hand, an air conditioning system 200 also called HVAC and, on the other hand, an air handling module 1.
[0122] The air handling module 1 comprises: - a body 10 substantially tubular, here made in two parts 11 and 12 which are assembled one after the other in the direction of the airflow; - an air inlet 2 configured to be supplied, in operation, at least in part by interior air taken from a predetermined enclosure 50, here a passenger compartment of the vehicle; - a capture device 4 (shown in [Fig.3]) configured to capture CO2 contained in the air passing through the air treatment module; - an air dehumidification device 5 (shown in [Fig.3]) which passes through the air treatment module; - a treated air outlet 3 configured to deliver air treated by the air handling module to the air conditioning system.
[0123] The CO2 capture device 4 and the air dehumidification device 5 are placed inside the body 10, one after the other, so that the air flowing into the body 10 passes successively through the CO2 capture device 4 and then the air dehumidification device 5. In another embodiment of the invention, it is possible to have first the air dehumidification device 5 and then the CO2 capture device 4.
[0124] The dehumidification device 5 is devoid of an evaporator-type heat exchanger. The dehumidification device 5 here includes a desiccant, for example a desiccant wheel, or any other known means of air dehumidification.
[0125] The maximum air treatment flow rate by the air conditioning system 200 is for example between 400 and 600 m3 / h, in particular between 450 m3 / h and 550 m3 / h, for example 500 m3 / h.
[0126] The air handling module 1 is sized so that the maximum air flow treated in the air handling module 1 is less than the maximum air flow treated in the air conditioning system 200.
[0127] The air conditioning unit 100 and the air conditioning system 200 are, where applicable, without fresh air inlets.
[0128] Air coming from outside the vehicle is called "fresh air".
[0129] The invention is advantageous in that the sizing of the air handling module 1 provides a treatment capacity that corresponds to only a portion, namely strictly less than 100%, of the maximum airflow treated by the air conditioning system 200, in particular less than 70%, especially less than 50%, for example less than 40%. The air handling module 1 can thus have a reduced footprint. The lower the proportion of the airflow treated, the smaller the footprint of the treatment module 1 can be. The inventors observed satisfactory results in terms of the size / air quality trade-off with a proportion of the airflow treated (relative to the maximum flow of the system) air conditioning) between 25% and 60%, specifically between 30% and 50%. This differs from the case where an air handling unit 1 would be considered, which delivers 100% of the air volume used by the air conditioning system 200. In this case, the air handling unit 1 would require greater capacity and therefore a larger footprint, with a higher cost as well.
[0130] The air handling module 1 is configured for example to deliver treated air with a flow rate of 180 m3 / hour (generally a flow rate which can be chosen between 125 and 300 m3 / h, in particular between 150m3 / h and 250m3 / h), for a treatment capacity by the air conditioning system which is 500 m3 / hour.
[0131] The air handling module 1 is configured to be able to handle air coming only from the predetermined enclosure, here the passenger compartment 50.
[0132] The air conditioning unit 100 is configured so that the air conditioning system 200 receives a mixture of air coming solely from: - from enclosure 50, directly, in other words without processing; - of processing module 1.
[0133] The invention makes it possible, in particular, thanks to this air treatment module 1, to dehumidify the air without using an evaporator. For example, the air conditioning system 200 can be operated without an evaporator when it delivers hot air, thus reducing the cost of such an air conditioning system, which can be of a simpler design.
[0134] The treated air outlet 3 of the air handling module 1 is configured to be placed opposite an air inlet 201 of the air conditioning system 200.
[0135] The treated air outlet 3 of the air treatment module 1 has a smaller passage cross-section than the cross-section of the air inlet 201 of the air conditioning system 200.
[0136] This allows the air conditioning system 200 to take not only air Fl from the air handling module 1 but also air F2 taken directly from the passenger compartment 50 (and therefore not treated by the air handling module), as illustrated in [Fig.3].
[0137] For example, the air outlet 3 of the air handling module 1 is configured to be located at a non-zero distance Dist from the air inlet 201 of the air conditioning system 200 (see [Fig.2]).
[0138] Thus it is not necessary to physically connect the air outlet 3 of the air treatment module 1 to the air conditioning system 200.
[0139] Alternatively, the air outlet 3 of the air treatment module 1 is connected to the air conditioning system 200 for example by a dedicated pipe 63 (see [Fig.6]).
[0140] The air handling module 1 includes a motor-fan unit 15 (or “Blower” in English), in particular of axial or radial type, to force air circulation within the body 10 of the air handling module 1.
[0141] The motor-fan group 15 is provided in addition to a main motor-fan group 215, in particular of axial or centrifugal-axial or centrifugal type, which equips the ventilation system 200.
[0142] The air inlet 2 of the air treatment module 1 is formed on a convergent 27 connecting to the inlet of the motor-fan group 15.
[0143] In figures 1 and 2, the housing of the motor-fan assembly 215 is partially cut out visually in order to show the blades.
[0144] Alternatively, the air handling module 1 is without a motor-fan assembly.
[0145] The air outlet 3 of the air handling module 1 is then positioned opposite the inlet 201 of the main motor-fan assembly 215 belonging to the air conditioning system 200.
[0146] Preferably, the CO2 capture device 4 from the air includes an activated carbon or other adsorbent filter and / or a metallo-organic structure filter.
[0147] If desired, the air treatment module 1 includes a particle filter 19, placed between the capture device 4 and the dehumidification device 5, here a high efficiency air filter, in particular called a HEPA filter in English (for High Efficiency Particulate Air).
[0148] Advantageously, it is possible to use a combined filter which performs several functions, for example of capturing CO2 and / or capturing certain gases and / or capturing certain particles.
[0149] The air handling module 1 may include a vacuum pump 18 (or an air pump or other pump / motor-fan unit system) to force dry air used for dehumidification to pass through the dehumidification device 5. The air to be dehumidified is set in motion, for example, by a motor-fan unit.
[0150] If dehumidification is required, the flow rate through the air treatment module 1 is chosen to be between 180 and 250 m3 / hour.
[0151] The air treatment module 1 allows, for example, the adsorption and / or absorption of substances such as CO2 and H2O (in vapor form in particular), and also nitrogen oxides (NOx) and / or volatile organic compounds.
[0152] The air handling module 1 forms a self-contained module independent of the air conditioning system 200.
[0153] In the example described, the air conditioning system 200 has a single heat exchanger, here an evaporator-condenser 220. The evaporator-condenser 220 is configured to operate as an evaporator in "summer" mode (in hot weather, to generate coolness, i.e., an air conditioning mode) and as a condenser in "winter" mode (in cold weather, to generate heat, i.e., a heating mode).
[0154] The single heat exchanger 220 is configured so that it can be bypassed by a bypass conduit 225, placed in particular above the heat exchanger 220, i.e. in the opposite direction to the direction taken by the condensate when it falls by gravity, as illustrated in [Fig. 13].
[0155] A hinged flap 226 is placed in the bypass duct 225 to prohibit or allow the airflow, at least in part, to bypass this single heat exchanger 220. This allows for better management of temperature stratification at the high and low outlet(s) of the air conditioning system.
[0156] The air conditioning assembly 100 is configured to be able to disable the air handling module 1 or to bypass the air handling module 1, when the air handling module 1 is not required to dehumidify the passenger compartment air in addition to the air conditioning system evaporator, particularly in "summer" conditions, in air conditioning mode.
[0157] Thus, in an example of an embodiment of the invention illustrated in [Fig.6], the air conditioning assembly 100 includes a control unit 60 configured to control the type of air to be sent into the air conditioning system 200, the type of air being chosen from air treated by the air treatment module 1, air coming directly from the predetermined enclosure such as a passenger compartment 50, or a mixture of the two according to an adjustable treated / untreated air ratio.
[0158] The control unit 60 is configured to control a flap 65 which, depending on its angular position, allows the treated / untreated air ratio to be changed to be sent into the air conditioning system 200.
[0159] The air flow rate exiting the air treatment module 1 can thus be calibrated using the flap 65 which regulates the passage of air exiting the air treatment module 1.
[0160] Module 1 can thus be a combined module with the air conditioning (HVAC) system, an actuator and a flap / flaps are provided to manage the airflow required for the air intake of the air conditioning (HVAC) system in order to ensure that a sufficient portion of the recycled air passes through the air handling module.
[0161] The invention thus enables the following step: - deliver air treated by the air treatment module 1, which represents only a part of the maximum treatment flow rate by the air conditioning system 200.
[0162] In the example of [Fig.3], the air handling module 1 is placed globally in space 70 under the hood of the vehicle, and the air conditioning system 200 (HVAC) is placed on the passenger compartment side 50.
[0163] Alternatively, as in the example of [Fig.4], the air handling module 1 and the air conditioning system 200 (HVAC) are placed on the passenger compartment side 50.
[0164] Alternatively, as in the example of [Fig.5], the air handling module 1 and the main motor-fan group 215 of the air conditioning system 200 (HVAC) are placed globally in the space 70 under the hood of the vehicle, while the heat exchanger 220, in particular of the evaporator-condenser type, of the air conditioning system 200 is located on the passenger compartment side 50.
[0165] With reference to [Fig. 7], the air conditioning system 200 is illustrated, comprising a single refrigerant heat exchanger (here an evaporator-condenser 220) housed in a casing 202, for example made of plastic. The treated air outlet 3 of the air handling unit 1 is configured to be positioned opposite the air inlet 201 of the air conditioning system 200. Arrow Fi shows the airflow entering the air conditioning system 200.
[0166] The housing 202 includes various air distribution vents 204 configured to distribute treated air from the air conditioning system 200 to various areas of the vehicle's interior (for example, including upper areas, footwell areas, front areas, rear areas of the passenger compartment, and windshield defogging areas). Movable flaps are provided in the air distribution vents 204 to control the airflow.
[0167] The heat exchanger 220 accommodates a circulation of refrigerant fluid which arrives through a fluid inlet pipe 208 and exits through a fluid outlet pipe 209.
[0168] In the example of [Fig.7], the incoming airflow Fi first sees the incoming refrigerant (because the inlet pipe 208 is placed closer to the inlet face of the heat exchanger 220 than the fluid outlet pipe 209). As a result, the airflow Fi and the flow of refrigerant in the heat exchanger 220 are in a "co-current" configuration.
[0169] In another configuration called "counter-current" (not illustrated), the incoming airflow Fi first sees the outgoing refrigerant (because the fluid outlet pipe 209 is placed closer to the inlet face of the heat exchanger 220 than the fluid inlet pipe 208). The inlet pipes 208 and outlet pipes 209 would be reversed in [Fig.7].
[0170] We will now describe different examples of a heat pump circuit that can be used in connection with the air conditioning unit 100.
[0171] This air conditioning unit 100 comprises the air conditioning system 200 and the air handling module 1 described above, the air dehumidification device 5 being preferably located upstream of the air conditioning system 200 (or HVAC).
[0172] The air conditioning unit 100 includes a heat pump circuit 150 in which a refrigerant is used, in particular a refrigerant, for example of type R744 or 1234yf, and configured to operate selectively in cooling mode and heating mode.
[0173] In the embodiment of the invention illustrated in Figures 8A and 8B, the heat pump circuit 150 includes an external heat exchanger 151 (noted "OHX" in Figures 8A and 8B) which is outside the air conditioning system 200.
[0174] The external heat exchanger 151 is, for example, configured to be placed on the front of a vehicle.
[0175] The external heat exchanger 151 is in particular a gas cooler in the case where the refrigerant is R744.
[0176] The gas cooler is configured to cool the R744 refrigerant without phase change.
[0177] The external heat exchanger 151 can also be an evaporator-condenser, particularly in the case where the refrigerant is 1234yf.
[0178] The external heat exchanger 151 can still be a gas evaporator-cooler.
[0179] The heat pump circuit 150 includes an internal heat exchanger 152 (designated by the acronym IHX) configured to transfer heat between a low pressure part 153 and a high pressure part 154 of the heat pump circuit 150.
[0180] The heat pump circuit 150 includes an accumulator 155 placed in the low pressure part 153, in particular upstream of a compressor 156, configured to ensure the absence of liquid refrigerant entering the compressor 156.
[0181] This accumulator 155 is further placed upstream of the internal heat exchanger 152.
[0182] When the heat pump circuit 150 includes an accumulator 155, the heat exchanger 220 (designated as "HVAC HEX" in Figures 8A and 8B) in the air conditioning system 200 is configured to operate, in air conditioning mode (illustrated in [Fig.8A]), in co-current with respect to the airflow Fi passing through it.
[0183] This, in combination with the accumulator 155, prevents overheating at the outlet of the exchanger 220 and thus preserves the benefit of using a heat exchanger in co-current mode (illustrated in [Fig.8A]).
[0184] The mode described with reference to Figures 8A and 8B can operate with R774 and 1234yf refrigerants.
[0185] The heat pump circuit 150 includes an expansion valve 157 (sometimes referred to by the acronym "EXV") configured to produce, in heating mode (Figures 8B), an expansion of the refrigerant before the refrigerant is evaporated in the outdoor heat exchanger 151.
[0186] The outdoor heat exchanger 151 is configured to condense the refrigerant, in air conditioning mode (figures 8A).
[0187] The only heat exchanger 220 with refrigerant in the air conditioning system 200 is an evaporator-condenser configured to operate as an evaporator in air conditioning mode (to produce cold, mode of [Fig.8A]) and as a condenser in heating mode (to generate heat, mode of [Fig.8B]).
[0188] In the example of Figures 8A and 8B, the heat pump circuit 150 comprises: - two expansion valves 157 and 158, expansion valve 157 being associated with the external heat exchanger 151 and expansion valve 158 being associated with the heat exchanger 220, - a shut-off valve type 159 or in English "Shut Off Valve" (SOV) placed between the external heat exchanger 151 and the accumulator 155, - two multi-way valves, here two three-way valves 160 and 161.
[0189] The circuit includes a main air conditioning loop arranged to circulate the refrigerant successively through the compressor 156, the outdoor heat exchanger 151, the expansion valve 157, the high-pressure part 154 of the internal heat exchanger 152, the expansion valve 158 in which the refrigerant undergoes a pressure drop, the heat exchanger 220 of the air conditioning system 200, the accumulator 155, then the low-pressure part 153 of the internal heat exchanger 152, etc.
[0190] According to one embodiment, the refrigerant fluid passes through the expansion valve 157 without pressure drop in cooling mode, the expansion valve 157 having a maximum opening level allowing passage without significant pressure loss.
[0191] According to another embodiment, the refrigerant passes through the expansion valve 157 with a pressure drop in the cooling mode, bringing the refrigerant at the outlet of the expansion valve 157 to an intermediate pressure higher than the pressure at the outlet of the expansion valve 158. Such use of the expansion valve 157 makes it possible to lower the pressure level in the high pressure part 154 of the internal heat exchanger 152, and thus adjust the efficiency of the internal heat exchanger 152 to a desired level.
[0192] The circuit further includes a first branch in parallel with the main loop, this first branch in parallel extending between a first branch located at the outlet of the compressor 156 and a second branch located between the heat exchanger 220 of the air conditioning system 200 and the accumulator 155.
[0193] The circuit further comprises a second branch branching off from the main loop, this second branch branch extending between, on the one hand, a third branch located between the first branch and the exchanger of external heat 151 and on the other hand a fourth branch located between the second branch and the accumulator 155.
[0194] Thus, in heating mode, the circuit is configured to circulate the refrigerant successively through the compressor 156, the first bypass branch, the heat exchanger 220 of the air conditioning system 200, the expansion valve 158, the high-pressure part 154 of the internal heat exchanger 152, the expansion valve 157 in which the refrigerant undergoes a pressure drop, the external heat exchanger 151, the second bypass branch, the accumulator 155, then the low-pressure part 153 of the internal heat exchanger 152, etc.
[0195] According to one embodiment, the refrigerant fluid passes through the expansion valve 158 without pressure drop in heating mode, the expansion valve 158 having a maximum opening level allowing passage without significant pressure loss.
[0196] According to another embodiment, the refrigerant passes through the expansion valve 158 with a pressure drop in the heating mode, bringing the refrigerant at the outlet of the expansion valve 158 to an intermediate pressure higher than the pressure at the outlet of the expansion valve 157. Such use of the expansion valve 158 makes it possible to lower the pressure level in the high pressure part 154 of the internal heat exchanger 152, and thus adjust the efficiency of the internal heat exchanger 152 to a desired level.
[0197] The first branch can be formed by a three-way valve.
[0198] The second branch can also be formed by a three-way valve.
[0199] The 159 type stop valve or in English “Shut Off Valve” (SOV) is placed in the second branch in bypass.
[0200] The three-way valves 160 and 161 are configured, in air conditioning mode ([Fig.8A]), to direct the refrigerant from the heat exchanger 220 to the accumulator 155 and then from the compressor 156 to the heat exchanger 151. The three-way valves 160 and 161 are configured, in heating mode ([Fig.8B]), to direct the refrigerant from the compressor 156 to the heat exchanger 220.
[0201] This configuration (Figures 8A and 8B) requires fewer valves overall and offers better efficiency on the heat exchangers because co-current flow is possible in cooling mode (so the pressure drop helps lower the fluid temperature, which boosts heat exchange) and counter-current flow is possible in heating mode (the hottest refrigerant is in contact with the already preheated air). Generally, co-current flow is preferred in cooling mode (especially if there is no superheat at the evaporator outlet).
[0202] In the example of Figures 8A and 8B, the heat pump circuit 150 is configured so that the direction of refrigerant flow is reversed in cooling mode ([Fig.8A]) and in heating mode ([Fig.8B]), both in the outdoor heat exchanger 151 and in the heat exchanger 220 of the air conditioning system 200.
[0203] In air conditioning mode ([Fig.8A]), the refrigerant, after the heat exchanger 220 of the air conditioning system 200, passes through the accumulator 155 and the internal heat exchanger 152 and then (as a gaseous refrigerant) through the compressor 156. In heating mode ([Fig.8B]), the refrigerant, after the external heat exchanger 151, passes through the accumulator 155 and the internal heat exchanger 152 and then (as a gaseous refrigerant) through the compressor 156. When changing modes, the direction of circulation in the external heat exchanger 151 is reversed.
[0204] The heat pump circuit 150 can be of the direct type, or alternatively of the indirect type.
[0205] In the case of an indirect heat pump, at least one water exchanger is added in a known manner, which then supplies the heat exchanger 220 of the air conditioning system 200.
[0206] In the case of an indirect system, the heat exchanger of the air conditioning system 200 is a water exchanger and the refrigerant exchanger of the evaporator-condenser type is not in the air conditioning system.
[0207] We will now describe, with reference to Figures 9A and 9B, another example of a heat pump circuit 170, which comprises: - two expansion valves 157 and 158, expansion valve 157 being associated with the external heat exchanger 151 and expansion valve 158 being associated with the heat exchanger 220 of the air conditioning system 200, - a shut-off valve type 159 or in English "Shut Off Valve" (SOV) placed between the external heat exchanger 151 and the accumulator 155, - two multi-way valves, here two three-way valves 160 and 161, - a one-way valve 171 (or "check valve" in English) between the internal heat exchanger 152 and the expansion valve 158, configured to ensure that the refrigerant flows through the heat exchanger 220 of the air conditioning system 200 always in the same direction, here in the opposite direction.
[0208] By adding this one-way valve 171 (compared to the previous heat pump circuit 150), the heat pump circuit 170 is configured so that the direction of refrigerant flow is the same in cooling mode ([Fig.9A]) and in heating mode ([Fig.9B]) in the heat exchanger 220 of the air conditioning system 200, and the direction of refrigerant flow is reversed in cooling mode ([Fig.9A]) and in heating mode ([Fig.9B]) in the outdoor heat exchanger 151.
[0209] In air conditioning mode ([Fig.9A]), the refrigerant, after the heat exchanger 220 of the air conditioning system 200, passes through the accumulator 155 and the internal heat exchanger 152 and then (as a gaseous refrigerant) through the compressor 156. In heating mode ([Fig.9B]), the refrigerant, after the external heat exchanger 151, passes through the accumulator 155 and the internal heat exchanger 152 and then (as a gaseous refrigerant) through the compressor 156. When changing modes, the direction of circulation in the external heat exchanger 151 is reversed.
[0210] We will now describe, with reference to Figures 10A and 10B, another example of a heat pump circuit 180, which comprises: - two expansion valves 157 and 158, expansion valve 157 being associated with the external heat exchanger 151 and expansion valve 158 being associated with the heat exchanger 220 of the air conditioning system 200, - a shut-off valve 159, or in English "Shut Off Valve" (SOV), placed between the external heat exchanger 151 and the accumulator 155, - three three-way valves 160, 161 and 162, - a one-way valve 171 (or "check valve" in English) between the internal heat exchanger 152 and the expansion valve 158, configured to ensure that the refrigerant flows through the heat exchanger 220 of the air conditioning system 200 always in the same direction.
[0211] In air conditioning mode ([Fig. 10A]), the refrigerant, after the heat exchanger 220 of the air conditioning system 200, passes through the accumulator 155 and the internal heat exchanger 152 and then (as a gaseous refrigerant) through the compressor 156. In heating mode ([Fig. 1OB]), the refrigerant, after the external heat exchanger 151, passes through the accumulator 155 (via the valve 159) and the internal heat exchanger 152 and then (as a gaseous refrigerant) through the compressor 156. When changing modes, the same direction of circulation is maintained in the external heat exchanger 151 thanks in particular to the addition of the appropriately placed three-way valve 162.
[0212] The heat pump circuit 180 is configured so that the direction of refrigerant flow is the same in air conditioning mode ([Fig.1OA]) and in heating mode ([Fig.1OB]), both in the outdoor heat exchanger 151 and in the heat exchanger 220 of the air conditioning system 200.
[0213] Figures 1 IA and 1 IB show an example of an embodiment of the invention in which the heat pump circuit 190 includes a receiver dryer 191 placed in the high pressure part.
[0214] In this case, the heat pump circuit 190 is devoid of an internal heat exchanger.
[0215] The heat pump circuit 190 thus comprises: - two expansion valves 157 and 158, expansion valve 157 being associated with heat exchanger 151 and expansion valve 158 being associated with heat exchanger 220, - a shut-off valve 159, or in English "Shut Off Valve" (SOV), placed between the external heat exchanger 151 and the compressor 156, - two three-way valves, 160 and 161, - two one-way valves 172 and 173 (or "check valve" in English) between the heat exchanger 151 and the filter drier 191, arranged so that, when changing modes (between the air conditioning mode in [Fig. 1 IA] and the heating mode in [Fig. 1 IB]), the direction of circulation in the outdoor heat exchanger 151 is reversed
[0216] When the heat pump circuit includes a filter drier 191, the heat exchanger 220 in the air conditioning system 200 can be configured to operate in counter-current to the airflow passing through it.
[0217] The heat pump circuit 190 is configured so that the direction of refrigerant flow is the same in air conditioning mode ([Fig.11A]) and in heating mode ([Fig.11B]) in the heat exchanger 220 of the air conditioning system 220, and the direction of refrigerant flow is reversed in air conditioning mode ([Fig.11A]) and in heating mode ([Fig.11B]) in the outdoor heat exchanger 151.
[0218] In air conditioning mode ([Fig. 1 IA]), the refrigerant, after the heat exchanger 220 of the air conditioning system 200, passes through the compressor 156 and then through (gaseous refrigerant) the outdoor heat exchanger 151 and then the filter drier 191 to return to the expansion valve 158 associated with the heat exchanger 220.
[0219] In heating mode ([Fig. 1 IB]), the refrigerant, after the external heat exchanger 151, passes (gaseous refrigerant) through the compressor 156 and then through the expansion valve 158 (fully open in this case) and the heat exchanger 220. Then the refrigerant passes through the filter-drier 191 to return to the expansion valve 157 before reaching the external heat exchanger 151.
[0220] Here the filter dryer 191 operates with refrigerant which is of type R1234yf.
[0221] It can also be provided that the heat pump circuit is configured so that the direction of refrigerant flow is reversed in air conditioning mode and in heating mode in the heat exchanger 220 of the air conditioning system, and the direction of refrigerant flow is the same in air conditioning mode and in heating mode in the outdoor heat exchanger 151 (case not shown).
[0222] The air conditioning system 200 may include a bypass along an upper edge of the heat exchanger 220 allowing air to bypass this heat exchanger 220. The lower edge of the heat exchanger 220 does not have such a bypass, so as not to impede the evacuation of condensate at the bottom of the air conditioning system 200. In the preceding examples, the heat pump circuit 150 is of the direct type.
[0223] Figure 12 shows another embodiment of the invention similar to that of Figures 8A and 8B, but with an indirect-type heat pump circuit 228. The single heat exchanger 220 is configured to carry an intermediate heat transfer fluid which is cooled or heated by a two-fluid intermediate heat exchanger 227 adapted to carry the intermediate heat transfer fluid and the refrigerant of the heat pump circuit 228.
[0224] Similarly, there is another intermediate two-fluid heat exchanger 227 between the heat pump circuit 228 and the external heat exchanger 151.
Claims
Demands
1. Air conditioning assembly (100), in particular configured to equip a vehicle, in particular a motor vehicle, comprising: - a heat pump circuit (150) in which a refrigerant is used, in particular a refrigerant of type R744 or R1234yf or R290, and configured to operate selectively in air conditioning mode and in heating mode; - an air conditioning system (200) provided with a heat exchanger (220) configured to cool or heat air circulating in the air conditioning system (200), this heat exchanger being the only heat exchanger of the air conditioning system heated or cooled directly or indirectly by the refrigerant of the heat pump circuit;- an air treatment module (1) comprising an air dehumidification device, configured to dehumidify air passing through the air conditioning system (200) characterized in that the heat pump circuit includes an internal heat exchanger configured to transfer heat between a low pressure part and a high pressure part of the heat pump circuit (150).
2. Air conditioning assembly (100) according to any one of the preceding claims, wherein the heat pump circuit (150) includes an accumulator (155) located in the low-pressure part, in particular upstream of a compressor, configured to ensure that no liquid refrigerant enters the compressor, in particular this accumulator being further located upstream of the internal heat exchanger.
3. Air conditioning assembly (100) according to the preceding claim, wherein, when the heat pump circuit (150) includes an accumulator, the heat exchanger of the air conditioning system (200) is configured to operate, in air conditioning mode, in co-current with respect to the airflow passing through it.
4. Air conditioning unit (100) according to any one of the preceding claims, wherein the heat pump circuit (150) includes a receiver dryer filter located in the high-pressure part of the heat pump circuit.
5. Air conditioning assembly (100) according to any one of the preceding claims, wherein the only heat exchanger in the air conditioning system (200) is an evaporator-condenser configured to operate as an evaporator in air conditioning mode (to produce cold) and as a condenser in heating mode (to generate heat).
6. Air conditioning assembly (100) according to any one of the preceding claims, wherein the heat pump circuit (150) is configured so that the direction of refrigerant flow is reversed in air conditioning mode and in heating mode in the heat exchanger of the air conditioning system (200).
7. Air conditioning assembly (100) according to any one of the preceding claims, wherein the heat pump circuit (150) includes an external heat exchanger (151) which is outside the air conditioning system (200), and the external heat exchanger is in particular configured to be placed on a front face of a vehicle, being for example a gas cooler in the case where the refrigerant is R744 or an evaporator-condenser, in particular in the case where the refrigerant is 1234yf.
8. Air conditioning assembly (100) according to the preceding claim, wherein the heat pump circuit (150) is configured so that the direction of refrigerant flow is reversed in air conditioning mode and in heating mode in the outdoor heat exchanger.
9. Air conditioning assembly (100) according to any one of claims 7 to 8, wherein the heat pump circuit (150) is configured so that the direction of refrigerant flow is reversed in air conditioning mode and in heating mode, both in the outdoor heat exchanger (151) and in the air conditioning system heat exchanger (200).
10. Air conditioning unit (100) according to any one of claims 7 to 8, wherein the heat pump circuit (150) is configured such that the direction of refrigerant flow is the same in air conditioning mode and in heating mode in the heat exchanger heat from the air conditioning system (200), and the direction of refrigerant flow is reversed in air conditioning mode and in heating mode in the outdoor heat exchanger.
11. Air conditioning unit (100) according to any one of the preceding claims, wherein the heat pump circuit (150) comprises: - two expansion valves (157, 158), - a shut-off valve (159) located between the outdoor heat exchanger (151) and the accumulator, - multi-way valves (160, 161), including two three-way valves.
12. A method for managing an air conditioning unit (100) according to any one of the preceding claims, comprising the following steps: - operating the air conditioning unit (100) in air conditioning mode, or - operating the air conditioning unit (100) in heating mode.
13. Air conditioning system (200), in particular for equipping an air conditioning unit according to any one of claims 1 to 11, this system comprising a single heat exchanger (220) capable of being heated or cooled directly or indirectly by a refrigerant from a heat pump circuit.
14. Air conditioning system (200) according to the preceding claim, wherein this single heat exchanger (220) is configured to be able to be bypassed by a bypass duct (225), placed in particular above the heat exchanger, i.e. in the opposite direction to the direction taken by the condensate when it falls by gravity.