• 专利附录
  • 专利说明
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    • 专利摘要:
    The present invention relates to an indirect reversible air conditioning circuit (1) comprising: a first refrigerant fluid loop (A) comprising: a compressor (3), a bifluid heat exchanger (5), a first expansion device (7), a first heat exchanger (9), a second expansion device (11), a second heat exchanger (13), and a bypass line (30) of the second heat exchanger (13). ), A second heat transfer fluid loop (B) having a fourth heat exchanger (64), and the two-fluid heat exchanger (5) being arranged jointly on the first refrigerant loop (A) and on the second coolant loop (B), • a pressure sensor (44) of the low-pressure coolant disposed downstream of the bypass line (30), • a central control unit (40) connected to said pressure sensor (44); ), the compressor (3) and to the first (7) and second (11) expansion devices so that they can be traversed without loss of pressure or bypassed.
    公开号:FR3064945A1
    申请号:FR1752949
    申请日:2017-04-05
    公开日:2018-10-12
    发明作者:Jugurtha BENOUALI；Regis Beauvis；Laurent Delaforge
    申请人:Valeo Systemes Thermiques SAS；
    IPC主号:
    专利说明:

    © Publication number: 3,064,945 (to be used only for reproduction orders) © National registration number: 17,52949 ® FRENCH REPUBLIC
    NATIONAL INSTITUTE OF INDUSTRIAL PROPERTY
    COURBEVOIE © Int Cl 8 : B 60 H 1/00 (2017.01), F25 B 49/02, 25/00
    A1 PATENT APPLICATION
    ©) Date of filing: 05.04.17. ® Applicant (s): VALEO THERMAL SYSTEMS (® Priority: Simplified joint stock company - FR. @ Inventor (s): BENOUALI JUGURTHA, BEAUVIS REGIS and DELAFORGE LAURENT. (43) Date of public availability of the request: 12.10.18 Bulletin 18/41. ©) List of documents cited in the report preliminary research: Refer to end of present booklet (© References to other national documents ® Holder (s): VALEO THERMAL SYSTEMS related: Joint stock company. ©) Extension request (s): © Agent (s): VALEO THERMAL SYSTEMS.
    INDIRECT INVERSIBLE AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE AND MANAGEMENT METHOD IN DEFROST MODE.
    FR 3,064,945 - A1 (5 /) The present invention relates to an indirect reversible air conditioning circuit (1) comprising:
    a first coolant loop (A) comprising:
    0 a compressor (3), 0 a dual fluid heat exchanger (5), 0 a first expansion device (7), 0 a first heat exchanger (9), 0 a second expansion device (11), 0 a second heat exchanger (13), and 0 a bypass line (30) of the second heat exchanger (13), a second heat transfer fluid loop (B) comprising a fourth heat exchanger (64), and the heat exchanger bifluid (5) being arranged jointly on the first coolant loop (A) and on the second coolant loop (B), a pressure sensor (44) of the low pressure coolant disposed downstream of the bypass line (30), a central control unit (40) connected to said pressure sensor (44), to the compressor (3) and to the first (7) and to the second (11) expansion device so that they can be passed through without pressure loss or bypassed.

    The invention relates to the field of motor vehicles and more particularly to a motor vehicle air conditioning circuit and its management method in heat pump mode.
    Today's motor vehicles increasingly include an air conditioning circuit. Generally, in a “conventional” air conditioning circuit, a refrigerant passes successively through a compressor, a first heat exchanger, called a condenser, placed in contact with an air flow outside the motor vehicle to release heat, a device expansion valve and a second heat exchanger, called an evaporator, placed in contact with an air flow inside the motor vehicle to cool it.
    There are also more complex air conditioning circuit architectures which make it possible to obtain an invertible air conditioning circuit, that is to say that it can use a heat pump operating mode in which it is able to absorb heat. heat energy in the outside air at the level of the first heat exchanger, then called evapo-condenser, and restore it in the passenger compartment in particular by means of a third dedicated heat exchanger.
    This is possible in particular by using an indirect air conditioning circuit. Indirect here means that the air conditioning circuit has two circulation loops of two separate fluids (such as a refrigerant and glycol water) in order to carry out the various heat exchanges.
    The air conditioning circuit thus comprises a first coolant loop in which a coolant circulates, a second coolant loop in which a coolant circulates, and a two-fluid heat exchanger arranged jointly on the first coolant loop and on the second loop of heat transfer fluid, so as to allow heat exchanges between said loops.
    When using such reversible air conditioning circuits in a heat pump mode, frost may form at the evaporator located on the front of the motor vehicle. This frost reduces the heat exchange between the flow of outside air passing through said evaporator and the refrigerant, which greatly reduces the performance of the reversible air conditioning circuit in heat pump mode.
    A known solution for removing the frost that has formed at the front face evaporator is to return the invertible air conditioning circuit to air conditioning mode so that hot refrigerant passes through said front face evaporator or in order to heat the flow of outside air in the case of an indirect air conditioning circuit. However, this solution is not satisfactory, since switching to air conditioning mode results in cold air being sent into the passenger compartment and therefore reducing the comfort of the occupants.
    One of the aims of the present invention is therefore to at least partially remedy the drawbacks of the prior art and to propose an improved air conditioning circuit as well as its management method in defrosting mode.
    The present invention therefore relates to an indirect reversible air conditioning circuit for a motor vehicle, said indirect reversible air conditioning circuit comprising:
    A first coolant loop in which a coolant circulates, said first coolant loop comprising in the direction of circulation of the coolant:
    ° a compressor, ° a two-fluid heat exchanger ° a first expansion device, ° a first heat exchanger being intended to be traversed by a flow of air inside the motor vehicle, ° a second expansion device, ° a second exchanger of heat being intended to be traversed by an air flow outside the motor vehicle, and ° a bypass pipe of the second heat exchanger, • a second loop of heat transfer fluid in which a heat transfer fluid circulates, said second circulation pipe of heat transfer fluid comprising a fourth heat exchanger intended to be traversed by the outside air flow, said fourth heat exchanger being arranged upstream of the second heat exchanger in the direction of circulation of the outside air flow, • the exchanger dual fluid heat being arranged jointly on the first coolant loop downstream of the compressor, between said compressor and the first device f expansion valve, and on the second heat transfer fluid loop, so as to allow heat exchange between the first coolant loop and the second heat transfer fluid loop, the indirect reversible air conditioning circuit further comprising:
    • a low pressure refrigerant pressure sensor, said pressure sensor being arranged downstream of the bypass line, between said bypass line and the compressor, • a central control unit connected to said coolant pressure sensor at low pressure and said compressor, said central control unit also being connected to the first and second expansion device so that they can be traversed by the refrigerant without loss of pressure or bypassed.
    According to one aspect of the invention, the indirect reversible circuit includes a high pressure refrigerant pressure sensor, said sensor being arranged downstream of the dual fluid heat exchanger, between said dual fluid heat exchanger and the electronic valve of expansion, the central control unit being connected to said high pressure refrigerant temperature sensor.
    According to another aspect of the invention, the indirect reversible circuit comprises a pressure sensor of the coolant at intermediate pressure, said pressure sensor being arranged downstream of the electronic expansion valve, between said electronic expansion valve and the second expansion device, centrale central control unit being connected to said intermediate pressure refrigerant pressure sensor.
    According to another aspect of the invention, the indirect reversible air conditioning circuit comprises, at the level of the front face of the motor vehicle, a shutter device for moving front face between a shutter position and an open position, centrale central unit of control being connected to said front panel closure device.
    According to another aspect of the invention, the indirect reversible air conditioning circuit comprises a front face fan arranged on the front face of the motor vehicle in order to produce the outside air flow Γ central control unit being connected to said front face fan.
    The present invention also relates to a method of operating an indirect reversible air conditioning circuit according to a defrosting mode in which, when frost is detected at the second heat exchanger:
    the second heat transfer fluid loop is stopped, the internal air flow and the external air flow are stopped, the refrigerant fluid from the first refrigerant loop passes successively through the compressor where said refrigerant fluid is compressed , the two-fluid heat exchanger, the first expansion device that said refrigerant passes through without loss of pressure, the first heat exchanger, the second expansion device that said refrigerant passes through without pressure loss and the second heat exchanger before to return to the compressor, when the pressure of the coolant measured by the low pressure coolant pressure sensor is such that said coolant is in the two-phase state with a saturation temperature above 0 ° C:
    the second heat transfer fluid loop is restarted so that the heat transfer fluid circulates in the two-fluid exchanger and the fourth heat exchanger, the compressor is stopped, an external air flow is generated.
    According to one aspect of the method according to the invention, the indirect reversible air conditioning circuit includes a high pressure refrigerant pressure sensor and that the restarting of the second heat transfer fluid loop, the stopping of the compressor and the generation of the external air flows are also carried out if the coolant pressure measured at the high pressure coolant pressure sensor is greater than or equal to 20 bars.
    According to another aspect of the method according to the invention, the indirect reversible air conditioning circuit comprises a pressure sensor of the coolant at intermediate pressure and that the restarting of the second loop of heat transfer fluid, the stopping of the compressor and the generation external air flow are also carried out if the refrigerant pressure measured at the intermediate pressure refrigerant pressure sensor is greater than or equal to 10 bars.
    According to another aspect of the method according to the invention, the indirect invertible air conditioning circuit comprises a shutter device on the front face and that in order to generate external air flow, said shutter device on the front face is in the open position .
    According to another aspect of the method according to the invention, the indirect reversible air conditioning circuit includes a front fan and that during the generation of the external air flow, said front fan is started at maximum speed for a duration between 10 and 60s.
    Other characteristics and advantages of the invention will appear more clearly on reading the following description, given by way of illustrative and nonlimiting example, and of the appended drawings among which:
    Figure 1 shows a schematic representation of an indirect reversible air conditioning circuit according to a first embodiment, Figure 2 shows a schematic representation of an indirect reversible air conditioning circuit according to a second embodiment, Figure 3 shows a representation schematic of an indirect reversible air conditioning circuit according to a third embodiment, FIGS. 4a and 4b show schematic representations of expansion devices according to different embodiments, FIG. 5 shows a schematic representation of the second loop of heat transfer fluid of the indirect reversible air conditioning circuit of Figures 1 to 3, according to an alternative embodiment, Figure 6a shows the indirect invertible air conditioning circuit of Figure 1 according to a cooling mode, Figure 6b shows a pressure / enthalpy diagram of the mode of cooling illustrated in Figure 6a, l Figure 7a shows the indirect reversible air conditioning circuit of Figure 1 in a heat pump mode, Figure 7b shows a pressure / enthalpy diagram of the heat pump mode illustrated in Figure 9a, Figures 8a and 8b show the circuit of indirect reversible air conditioning in FIG. 1 according to the two stages of a defrosting mode, FIG. 9 shows a flow diagram of an example of the operating method of the indirect reversible air conditioning circuit according to a defrosting mode.
    In the various figures, identical elements have the same reference numbers.
    The following embodiments are examples. Although the description refers to one or more embodiments, this does not necessarily mean that each reference relates to the same embodiment, or that the characteristics apply only to a single embodiment. Simple features of different embodiments can also be combined and / or interchanged to provide other embodiments.
    In the present description, it is possible to index certain elements or parameters, such as for example first element or second element as well as first parameter and second parameter or again first criterion and second criterion, etc. In this case, it is a simple indexing to differentiate and name elements or parameters or criteria close, but not identical. This indexing does not imply a priority of an element, parameter or criterion over another and one can easily interchange such names without departing from the scope of this description. This indexing does not imply an order in time for example to assess this or that criterion.
    In the present description, the term "placed upstream" means that one element is placed before another with respect to the direction of circulation of a fluid. Conversely, by "placed downstream" is meant that one element is placed after another with respect to the direction of circulation of the fluid.
    Figure 1 shows an indirect air conditioning circuit 1 for a motor vehicle. This indirect air conditioning circuit 1 includes in particular:
    • a first coolant loop A in which a coolant circulates, • a second coolant loop B in which a coolant circulates, and • a two-fluid heat exchanger 5 arranged jointly on the first coolant loop A and on the second heat transfer fluid loop B, so as to allow heat exchanges between said first coolant fluid loop A and said second heat transfer fluid loop B.
    The first coolant loop A, shown in solid lines in the various figures, more particularly comprises in the direction of circulation of the coolant:
    ° a compressor 3, ° the two-fluid heat exchanger 5, arranged downstream of said compressor 3, ° a first expansion device 7, for example an electronic expansion valve, ° a first heat exchanger 9 being intended to be traversed by an internal air flow 100 to the motor vehicle, ° a second expansion device 11, for example a tube orifice, ° a second heat exchanger 13 being intended to be traversed by an external air flow 200 to the motor vehicle, and ° a bypass pipe 30 of the second heat exchanger 13.
    The bypass pipe 30 can more specifically connect a first connection point 31 and a second connection point 32.
    The first connection point 31 is preferably arranged, in the direction of circulation of the coolant, downstream of the first heat exchanger 9, between said first heat exchanger 9 and the second heat exchanger 13. More particularly, and as illustrated in FIG. 1, the first connection point 31 is disposed between the first heat exchanger 9 and the second expansion device 11. It is however quite possible to imagine that the first connection point 31 is disposed between the second expansion device 11 and the second heat exchanger 13 as long as the refrigerant has the possibility of bypassing said second expansion device 11 or passing through it without undergoing pressure loss.
    The second connection point 32 is preferably arranged downstream of the second heat exchanger 13, between said heat exchanger 13 and the compressor 3.
    As illustrated in FIG. 2, the first refrigerant loop A can also include a first internal heat exchanger 19 (IHX for "internai heat exchanger") allowing heat exchange between the refrigerant leaving the heat exchanger dual fluid 5 and the refrigerant leaving the second heat exchanger 13 or the bypass pipe 30. This first internal heat exchanger 19 comprises in particular an inlet and an outlet for refrigerant coming from the second connection point 32, as well as '' an inlet and an outlet for refrigerant coming from the two-fluid heat exchanger 5.
    As illustrated in FIG. 3, the first refrigerant loop A can comprise, in addition to the first internal heat exchanger 19, a second internal heat exchanger 19 ′ allowing heat exchange between the high pressure refrigerant leaving the first internal heat exchanger 19 and the low pressure refrigerant flowing in the bypass pipe 30, that is to say coming from the first connection point 31. By high pressure refrigerant, this is understood to mean a refrigerant having undergone an increase in pressure at the compressor 3 and that it has not yet suffered a pressure loss due to the first expansion device 7 or the second expansion device 11. This second internal heat exchanger 19 ′ notably comprises a coolant inlet and outlet from the first connection point 31, as well as a high pressure coolant inlet and outlet from prov the first internal heat exchanger 19.
    At least one of the first 19 or second 19 ′ internal heat exchangers can be a coaxial heat exchanger, that is to say comprising two coaxial tubes and between which the heat exchanges take place.
    Preferably, the first internal heat exchanger 19 can be a coaxial internal heat exchanger with a length between 50 and 120 mm while the second internal heat exchanger 19 'can be a coaxial internal heat exchanger with a length between 200 and 700mm.
    As shown in Figures 1 and 2, the first coolant loop may also include an accumulator 15 disposed upstream of the compressor 3, more precisely between the second connection point 32 and said compressor 3. In the case where a first heat exchanger internal heat 19 is present, said accumulator 15 is disposed upstream of said first internal heat exchanger 19, between the second connection point 32 and said first internal heat exchanger 19. This accumulator 15 makes it possible in particular to achieve phase separation of the fluid refrigerant so that the refrigerant arriving at the compressor 3 or in the first internal heat exchanger 19 is in the gas phase.
    According to a variant illustrated in Figure 3, the first loop of refrigerant
    A may include, instead of an accumulator 15, a desiccant bottle 15 'disposed downstream of the dual-fluid heat exchanger 5, more precisely between said dual-fluid heat exchanger 5 and the first internal heat exchanger 19. Such a bottle desiccant 15 'arranged on the high pressure side of the air conditioning circuit, that is to say downstream of the dual-fluid heat exchanger 5 and upstream of an expansion device, has a smaller footprint as well as a cost reduced compared to other phase separation solutions such as an accumulator which would be disposed on the low pressure side of the air conditioning circuit, that is to say upstream of the compressor 3, in particular upstream of the first internal heat exchanger 19 .
    The indirect reversible air conditioning circuit 1 also includes a device for redirecting the refrigerant coming from the first heat exchanger 9 to the second heat exchanger 13 or to the bypass pipe 30.
    This device for redirecting the refrigerant coming from the first heat exchanger 9 can in particular comprise:
    • a first stop valve 22 disposed downstream of the first connection point 31, between said first connection point 31 and the second expansion device 11. An alternative to this first stop valve 22 may be that the second expansion valve 11 has a stop function so as to be able to block the coolant and prevent it from circulating, • a second stop valve 33 disposed on the bypass pipe 30, and • a non-return valve 23 disposed downstream of the second heat exchanger 13, between said second heat exchanger 13 and the second connection point 32.
    Another alternative (not shown) may also be to have a three-way valve at the first connection point 31.
    By stop valve, non-return valve, three-way valve or expansion device with stop function, we mean here mechanical or electromechanical elements which can be controlled by an electronic control unit on board the motor vehicle.
    As shown in more detail in FIGS. 4a and 4b, the first expansion device 7 and the second expansion device 11 can be bypassed by a bypass line A ', notably comprising a stop valve 25, 25 ’. This bypass line A 'allows the refrigerant to bypass the first expansion device 7 and / or the second expansion device 11 without undergoing a pressure loss. An alternative for the refrigerant to pass through the first expansion device 7 without loss of pressure is that the latter includes a maximum opening function in which the refrigerant passes through it without loss of pressure.
    The second heat transfer fluid loop B, shown in a line comprising three dashes and two points in the different figures, may in turn include:
    ° the two-fluid heat exchanger 5, ° a first circulation pipe 50 of heat transfer fluid comprising a third heat exchanger 54 intended to be traversed by an interior air flow 100 to the motor vehicle, and connecting a first junction point 61 disposed downstream of the dual-fluid heat exchanger 5 and a second junction point 62 disposed upstream of said dual-fluid heat exchanger 5, ° a second circulation pipe 60 of coolant comprising a fourth heat exchanger 64 intended to be traversed by an outside air flow 200 to the motor vehicle, and connecting the first junction point 61 disposed downstream of the dual-fluid heat exchanger 5 and the second junction point 62 disposed upstream of said dual-fluid heat exchanger 5, and ° a pump 17 arranged downstream or upstream of the two-fluid heat exchanger 5, between the first junction point 61 and the second junction point 62.
    The fourth heat exchanger 64 is more particularly arranged upstream of the second heat exchanger 13 in the direction of circulation of the outside air flow 200.
    The indirect reversible air conditioning circuit 1 includes, within the second heat transfer fluid loop B, a device for redirection of the heat transfer fluid from the two-fluid heat exchanger 5 to the first circulation line 50 and / or to the second heat line traffic 60.
    As illustrated in FIGS. 1 to 3, said device for redirection of the heat-transfer fluid coming from the dual-fluid heat exchanger 5 may in particular comprise a fourth stop valve 63 disposed on the second circulation pipe 60 in order to block or not block the heat transfer fluid and prevent it from circulating in said second circulation line 60.
    The indirect reversible air conditioning circuit 1 may also include a shutter 310 for blocking the interior air flow 100 passing through the third heat exchanger 54.
    This embodiment makes it possible in particular to limit the number of valves on the second heat transfer fluid loop B and thus makes it possible to limit the production costs.
    According to an alternative embodiment illustrated in FIG. 5, the device for redirection of the heat-transfer fluid coming from the dual-fluid heat exchanger 5 may in particular comprise • a fourth stop valve 63 disposed on the second circulation pipe in order to block or not the heat transfer fluid and prevent it from flowing in said second circulation pipe 60, and • a fifth stop valve 53 disposed on the first circulation pipe in order to block or not the heat transfer fluid and prevent it from circulate in said first circulation pipe 50.
    The second heat transfer fluid loop B can also include an electric heating element 55 of the heat transfer fluid. Said electric heating element 55 is in particular arranged, in the direction of circulation of the heat-transfer fluid, downstream of the two-fluid heat exchanger 5, between said two-fluid heat exchanger 5 and the first junction point 61.
    The indirect reversible air conditioning circuit 1 may also include a front face fan 91 disposed on the front face of the motor vehicle in order to produce the flow of outside air 200, in particular when the motor vehicle is stopped or when its speed n is not sufficient to create an outside air flow 200 with sufficient flow. The front face fan 91 can in particular be arranged downstream of the fourth heat exchanger 64 and of the second heat exchanger 13 in the direction of circulation of the external air flow 200.
    The indirect reversible air conditioning circuit 1 may also include an internal fan 92 disposed at the first heat exchanger 9 in order to produce the interior air flow 100. The internal fan 92 may in particular be arranged upstream of the first heat exchanger 9 and the third heat exchanger 54 in the direction of circulation of the interior air flow 100.
    The indirect reversible air conditioning circuit 1 may also include at the front face of the motor vehicle, a shutter device 93 on the front face which may in particular comprise a series of movable flaps between a shutter position where the flaps block the flow of outside air 200 so that it does not pass through the fourth heat exchanger 64 and the second heat exchanger 13 and an open position where the flow of outside air can pass through said heat exchangers 64, 13.
    As shown in Figures 1 to 3, the indirect reversible air conditioning circuit further comprises a central control unit 40 shown in dotted lines controlling and controlling various elements in order to allow the passage from one operating mode to another as well as for controlling the different modes of operation.
    In order to control in particular the change from one operating mode to another, centrale central control unit 40 can in particular be connected to the device for redirecting the refrigerant coming from the first heat exchanger 9 and more particularly to the first valve. stop 22 and the second stop valve 33 in order to control their opening or closing. The central control unit 40 can also be connected to the shut-off valves 25 and / or 25 'of the bypass lines A' allowing the first expansion device 7 and the second expansion device 11 to be bypassed. These different connections are not not shown in the figures. The central control unit 40 can also be connected to the heat transfer fluid redirection device in order to control the circulation of the heat transfer fluid in the second heat transfer fluid loop B.
    The central control unit 40 can be connected to the first expansion device 7 when the latter is in particular an electronic expansion valve, in order to control its opening and to define the pressure of the coolant leaving the said electronic valve. expansion. Similarly, if the second expansion device 11 is an electronic expansion valve, centrale central control unit 40 can be connected to the latter in order to control its opening and to define the pressure of the refrigerant fluid at the outlet of said electronic valve d 'expansion.
    The central control unit 40 can also be connected to the compressor 3 in order to control its stopping, its start-up. The central control unit 40 can also define the speed of the compressor 3 and thus define the pressure of the refrigerant fluid leaving said compressor 3.
    Similarly, centrale central control unit 40 can be connected to the pump 17 in order to control its stopping, its starting and thus controlling the starting or stopping of the second loop of heat transfer fluid B.
    The central control unit 40 can also be connected to the shutter device 93 on the front panel in order to control its opening and closing and thus influence the outside air flow 200.
    The indirect reversible air conditioning circuit 1 may include a pressure sensor 41 for the high pressure refrigerant. This sensor 41 is arranged downstream of the two-fluid heat exchanger 5, between said two-fluid heat exchanger 5 and the first expansion device 7. When the indirect reversible circuit 1 comprises a first internal heat exchanger 19, the pressure sensor 41 of the high pressure refrigerant is placed between the two-fluid heat exchanger 5 and the first internal heat exchanger 19 so that the pressure and temperature measurements are not affected by said first internal heat exchanger 19. This sensor pressure 41 of the high pressure refrigerant is connected to centrale central control unit 40 and allows the latter to know the pressure of the refrigerant leaving the dual-fluid heat exchanger 5.
    The indirect invertible air conditioning circuit 1 may include a temperature sensor 42 for the outside temperature as well as a pressure sensor 43 for the refrigerant at intermediate pressure. This pressure sensor 43 is disposed downstream of the first expansion device 7, between said first expansion device 7 and the second expansion device 11. More particularly, the pressure sensor 43 of the refrigerant at intermediate pressure is disposed downstream of the first heat exchanger 9, between said first heat exchanger 9 and the first connection point 31, as illustrated in FIGS. 1, 2 and 3. It is nevertheless quite possible to have this pressure sensor 43 upstream of the first heat exchanger 9, between the first expansion device 7 and said first heat exchanger 9.
    The temperature sensor 42 for the outside temperature as well as the pressure sensor 43 for the intermediate pressure refrigerant are both connected to the central control unit 40 and allow the latter to know the temperature of the air outside the motor vehicle. as well as the pressure of the refrigerant leaving the first expansion device 7.
    The indirect reversible air conditioning circuit 1 includes a pressure sensor 44 of the low pressure refrigerant. This pressure sensor 44 is arranged downstream of the bypass pipe 30, more precisely between the second connection point 32 and the compressor 3. When the indirect reversible circuit 1 comprises a first internal heat exchanger 19, the pressure sensor 41 low pressure refrigerant is placed between the second connection point 32 and the first internal heat exchanger 19 so that the pressure measurement is not affected by said first internal heat exchanger 19.
    In FIGS. 6a to 7b are illustrated methods of operation of the indirect invertible air conditioning circuit 1 according to different modes of operation. In FIGS. 6a and 7a, only the elements in which the coolant and / or the coolant circulate are shown. The direction of circulation of the coolant and / or the coolant is represented by arrows.
    FIG. 6a more particularly shows an operating method according to a cooling mode in which:
    • the refrigerant passes successively through the compressor 3, the two-fluid heat exchanger 5, the first expansion device 7 and the first heat exchanger 9 before returning to the compressor 3, • a portion of the heat transfer fluid leaving the dual fluid heat exchanger 5 circulates in the third heat exchanger 54 of the first circulation line 50 and another portion of the heat transfer fluid leaving the dual fluid heat exchanger 5 circulates in the fourth heat exchanger 64 of the second circulation 50, • the obstruction flap 310 is closed so as to prevent the interior air flow 100 from circulating in the third heat exchanger 54.
    The pressure and enthalpy variations undergone by the refrigerant during this cooling mode are illustrated in the pressure / enthalpy diagram in Figure 6b. Curve X represents the saturation curve of the refrigerant.
    The refrigerant at the inlet of compressor 3 is in the gas phase. The refrigerant undergoes compression, illustrated by the arrow 300, passing through the compressor 3. This is called high pressure refrigerant.
    The high-pressure refrigerant passes through the dual-fluid heat exchanger 5 and undergoes a loss of enthalpy, illustrated by arrow 500, due to the passage in the liquid phase of the refrigerant and the transfer of enthalpy to the heat transfer fluid of the second heat transfer fluid loop B. The refrigerant fluid then loses enthalpy while remaining at a constant pressure.
    The refrigerant then passes through the first expansion device 7. The refrigerant undergoes an isenthalpic pressure loss, illustrated by arrow 700 and crosses the saturation curve X, which makes it pass into a state of liquid mixture plus gas. This is called low pressure refrigerant.
    The low pressure refrigerant then passes into the first heat exchanger 9 where it gains enthalpy as illustrated by the arrow 900 by cooling the interior air flow 100. The low pressure refrigerant thus joins the saturation curve X and returns to the gaseous state.
    At the outlet of the first heat exchanger 9, the low-pressure refrigerant is redirected to the bypass pipe 30 before re-entering the compressor 3.
    This cooling mode is useful for cooling the indoor air flow 100.
    In this cooling mode, the coolant redirection device is configured so that the coolant does not circulate in the second heat exchanger 13.
    This is in particular possible by closing the first stop valve 22 and by opening the second stop valve 33 so that the low-pressure refrigerant leaving the first heat exchanger 9 does not circulate in the second heat exchanger 13 and passes through bypass 30.
    The non-return valve 23 makes it possible to prevent low-pressure refrigerant leaving the bypass pipe 30 from flowing back to the second heat exchanger 13.
    According to a first variant not shown, the cooling mode can operate when the indirect reversible air conditioning circuit 1 comprises a first internal heat exchanger 19. This first variant of the cooling mode comprises the same steps as the cooling mode illustrated in FIG. 6a, with the difference that:
    • before arriving in the first expansion device 7, the high pressure refrigerant passes through the first internal heat exchanger 19, and • before arriving in the compressor 3, the low pressure refrigerant coming from the bypass line 30 also passes through the first internal heat exchanger 19.
    The first internal heat exchanger 19 allows a reduction in the enthalpy of the high pressure refrigerant before entering the first heat exchanger 9 by transferring part of its enthalpy to the low pressure refrigerant upstream of the compressor 3. The first internal heat exchanger 19 allows an increase in cooling power and improves the coefficient of performance (or COP for “coefficient of performance”) by reducing the enthalpy of the high-pressure refrigerant leaving the dual-fluid heat exchanger 5 and by transferring it to the low-pressure refrigerant before it enters the compressor 3.
    According to a second variant, not shown, the cooling mode can operate when the indirect reversible air conditioning circuit 1 comprises first and second 19 ’internal heat exchangers. This second variant of the cooling mode comprises the same steps as the cooling mode illustrated in FIG. 6a, with the difference that:
    Before arriving in the first expansion device 7, the high pressure refrigerant passes successively through the first internal heat exchanger 19 and the second internal heat exchanger 19 ′, and • before arriving in the compressor 3, the low pressure refrigerant coming from the first heat exchanger 9 passes into the second internal heat exchanger 19 ′ by passing through the bypass pipe 30 and then passes through the first internal heat exchanger 19.
    In this second variant of the cooling mode, the two internal heat exchangers 19 and 19 'are active and their effects add up. The use of internal heat exchangers 19 and 19 ′ one after the other makes it possible to reduce the enthalpy of the high pressure refrigerant at the inlet of the first expansion device 7. The high pressure refrigerant at the the liquid state at the outlet of the dual-fluid heat exchanger 5 is cooled by the refrigerating fluid in the gaseous state and at low pressure leaving the first heat exchanger 9. The enthalpy difference across the terminals of the first heat exchanger 9 significantly increases which allows both an increase in the cooling capacity available at said first heat exchanger 9 which cools the air flow 100 and this therefore results in an improvement in the performance coefficient.
    In addition, the addition of enthalpy to the low-pressure refrigerant at the first 19 and second 19 'internal heat exchangers makes it possible to limit the proportion of refrigerant in the liquid phase before they have entered the compressor 3, in particular when the air conditioning circuit 1 comprises a desiccant bottle 15 disposed downstream of the dual-fluid heat exchanger 5.
    At the second heat transfer fluid loop B, the heat transfer fluid gains enthalpy from the coolant at the two-fluid heat exchanger 5.
    As illustrated in FIG. 6a, a portion of the heat transfer fluid circulates in the first circulation pipe 50 and passes through the third heat exchanger 54. The heat transfer fluid does not, however, lose any enthalpy, since the obstruction flap 310 is closed and blocks the interior air flow 100 so that it does not pass through the third heat exchanger 54.
    Another portion of the heat transfer fluid circulates in the second circulation line 60 and passes through the fourth heat exchanger 64. The heat transfer fluid loses hal enthalpy at the level of said heat exchanger 64 by releasing it into the external air flow 200. The fourth stop valve 63 is open to allow the passage of the heat transfer fluid.
    An alternative solution (not shown) so that the heat transfer fluid does not exchange with the interior air flow 100 at the third heat exchanger 54, is to provide, as in FIG. 4, the first circulation pipe 50 of the fifth shut-off valve 53 and to close it so as to prevent the coolant from flowing in said first circulation pipe 50.
    FIG. 7a more particularly shows an operating method according to a heat pump mode in which:
    • the refrigerant passes successively through the compressor 3, the two-fluid heat exchanger 5, the first expansion device 7, the first heat exchanger 9, the second expansion device 11 and the second heat exchanger 13 before returning to the compressor 3, • the heat transfer fluid at the outlet of the dual-fluid heat exchanger 5 circulates only in the third heat exchanger 54 of the first circulation pipe 50, • the obstruction flap 310, when it is present, is open so as to allow the interior air flow 100 to circulate in the third heat exchanger 54.
    The pressure and enthalpy variations undergone by the refrigerant in this heat pump mode are illustrated in the pressure / enthalpy diagram in Figure 7b. Curve X represents the saturation curve of the refrigerant.
    The refrigerant at the inlet of compressor 3 is in the gas phase. The refrigerant undergoes compression, illustrated by the arrow 300, passing through the compressor 3. Here we speak of high pressure refrigerant.
    The high-pressure refrigerant passes through the dual-fluid heat exchanger 5 and undergoes a loss of enthalpy, illustrated by arrow 500, due to the passage in the liquid phase of the refrigerant and the transfer of enthalpy to the heat transfer fluid of the second heat transfer fluid loop B. The high pressure refrigerant then loses enthalpy while remaining at a constant pressure.
    The high pressure refrigerant then passes through the first expansion device 7. The refrigerant undergoes a first isenthalpic pressure loss, illustrated by arrow 700 and crosses the saturation curve X, which puts it in a state of mixing liquid plus gas. We are talking here about medium pressure fluid.
    The refrigerant at intermediate pressure then passes through the first heat exchanger 9 where it continues to lose enthalpy as illustrated by the arrow 900 by heating the interior air flow 100.
    At the outlet of the first heat exchanger 9, the refrigerant at intermediate pressure is redirected to the second heat exchanger 13. Before arriving at the second heat exchanger 13, the refrigerant at intermediate pressure passes into the second expansion device 11 where it undergoes a second isenthalpic pressure loss illustrated by the arrow 110. We then speak of low pressure fluid.
    The low pressure refrigerant then passes through the second heat exchanger 13 where it gains enthalpy, as illustrated by arrow 130, by absorbing enthalpy from the outside air flow 200. The low pressure refrigerant joins thus the saturation curve X and returns to the gaseous state.
    The low pressure refrigerant then joins the compressor 3.
    In this heat pump mode, the coolant redirection device is configured so that the coolant at intermediate pressure does not circulate in the bypass line 30.
    This is in particular possible by opening the first stop valve 22 and closing the second stop valve 33 so that the refrigerant at intermediate pressure at the outlet of the first heat exchanger 9 does not circulate in the bypass pipe 30 and passes in the second expansion device 11 and the second heat exchanger 13.
    According to a first variant not shown, the heat pump mode can operate when the indirect reversible air conditioning circuit 1 comprises a first internal heat exchanger 19. This variant of the heat pump mode comprises the same steps as the dehumidification mode illustrated in FIG. Figure 7a, with the difference that:
    • before arriving in the first expansion device 7, the high pressure refrigerant passes through the first internal heat exchanger 19, and • before arriving in the compressor 3, the low pressure refrigerant coming from the second heat exchanger 13 also passes through the first internal heat exchanger 19.
    According to a second variant not shown, the heat pump mode can operate when the indirect reversible air conditioning circuit 1 comprises a first 19 and a second 19 ’internal heat exchanger. This second variant of the cooling mode comprises the same steps as the cooling mode illustrated in FIG. 6a, with the difference that before arriving in the first expansion device 7, the high pressure refrigerant passes successively through the first internal heat exchanger 19 and the second internal heat exchanger 19 '.
    However, the second internal heat exchanger 19 ’has no influence, since the refrigerant does not pass through the bypass loop 30.
    The first internal heat exchanger 19 allows a reduction in Γenthalpy of the high pressure refrigerant before entering the first heat exchanger 9 by transferring part of its enthalpy to the low pressure refrigerant upstream of the compressor 3. The addition enthalpy of the low pressure refrigerant at the first internal heat exchanger 19 makes it possible to limit the proportion of low pressure refrigerant in the liquid phase before it enters the compressor 3, in particular when the air conditioning circuit 1 comprises a bottle desiccant 15 disposed downstream of the two-fluid heat exchanger 5.
    The effect of the first internal heat exchanger 19 can be limited when the latter is short, for example with a length between 50 and 120mm. This size makes it possible to limit the heat exchanges between the high pressure refrigerant fluid and the low pressure refrigerant fluid so that the exchanged enthalpy makes it possible to limit the proportion of refrigerant fluid in the liquid phase before it enters compressor 3 without as much to penalize the efficiency of the heat pump mode. Indeed, the purpose of this heat pump mode is to release as much enthalpy as possible into the interior air flow 100 in order to heat it up at the level of the first heat exchanger 9.
    At the level of the second heat transfer fluid loop B, the heat transfer fluid gains enthalpy from the coolant at the level of the two-fluid heat exchanger 5.
    As illustrated in FIG. 7a, the heat transfer fluid circulates in the first circulation pipe 50 and passes through the third heat exchanger 54. The heat transfer fluid loses enthalpy by heating the internal air flow 100. For this, the shutter obstruction 310 is open or the fifth stop valve 53 is open. The fourth stop valve 63 is closed in order to prevent the passage of the heat transfer fluid in the second circulation pipe 60.
    This heat pump mode is useful for heating the indoor air flow 100 both at the first heat exchanger 9 and the third heat exchanger by absorbing enthalpy from the outdoor air flow 200 at the second heat exchanger 13.
    In addition, the electric heating element 55 can be in operation in order to provide an additional supply of heat energy to the heat transfer fluid to heat the interior air flow 100.
    Figures 8a and 8b show a management method according to a defrosting mode which is triggered when frost is detected at the second heat exchanger 13. The detection of frost at the second heat exchanger 13 can be carried out according to several methods known to those skilled in the art, such as by means of dedicated sensors or by measuring and calculating various parameters, in particular in heat pump mode, such as the pressure of the refrigerant fluid at the pressure sensor 44 of the refrigerant fluid low pressure, the coefficient of performance, the speed of the compressor 3. Frost may appear on the exterior surface of the second heat exchanger 13 when the indirect reversible air conditioning circuit 1 operates in heat pump mode.
    Firstly, illustrated in Figure 8a, following the detection of frost at the second heat exchanger 13, the second heat transfer fluid loop B is stopped. For this, the central control unit 40 stops the pump 17 and the heat transfer fluid no longer circulates in the second heat transfer fluid loop B. The stopping of said second heat transfer fluid loop B results in the fact that there is no more or very little heat exchange between the refrigerant and the heat transfer fluid at the dual fluid heat exchanger 5.
    Likewise, the indoor air flow 100 and the outdoor air flow 200 are stopped.
    In order to stop the indoor air flow 100, centrale central control unit 40 can notably stop the indoor fan 92. In order to stop the outdoor air flow 200,
    Centrale central control unit 40 can in particular stop the front face fan 91 as well as close the shutter device 93 if it is present.
    Still at this first stage, the central control unit 40 controls the circulation of the coolant from the first coolant loop A so that it passes through the compressor 3 where said coolant is compressed. The compressor can in particular be controlled by T central control unit so that it has a gradual rise in speed. Such a gradual rise in speed saves the compressor 3 as well as the first heat exchanger 9 so as not to damage them with a rise in speed and in too sudden coolant pressure. In addition, this makes it possible to reduce the noise pollution linked to the rise in speed of the compressor 3. This rise in speed can in particular take place between 2000 rpm and a maximum speed Nmax of between 4500 and 8500 rpm.
    The refrigerant then passes through the two-fluid heat exchanger 5 which it passes through without heat exchange with the heat transfer fluid because the second loop of heat transfer fluid B is stopped.
    The coolant then passes through the first expansion device 7 that said coolant passes through without loss of pressure. For this, the central control unit 40 controls either directly said first expansion device 7 so that it is fully open, for example if it is an electronic expansion valve or then by controlling its bypass at the level a bypass line A ', if such a bypass loop A' is present.
    The refrigerant then passes through the first heat exchanger 9 where it does not exchange heat with the internal air flow 100 because the latter is not present.
    The refrigerant then passes into the second expansion device 7 which it passes through without loss of pressure. For this, the central control unit 40 controls either directly said second expansion device 7 so that it is fully open, for example if it is an electronic expansion valve or then by controlling its bypass at the level of a bypass line A ', if such a bypass loop A' is present, for example if the second expansion device 11 is a tube orifice.
    The refrigerant then passes through the second heat exchanger 13 where it does not exchange heat with the external air flow 200 because the latter is not present. The refrigerant then joins the compressor 3.
    This first step allows an increase in the pressure and the temperature of the coolant within the first coolant loop. The refrigerant will therefore gain in temperature and when it will pass through the second heat exchanger 13, it will heat said second heat exchanger 13 resulting in the start of defrosting.
    Secondly, illustrated in FIG. 8b, when the pressure of the coolant measured by the pressure sensor 44 of the coolant at low pressure is such that said coolant is in the two-phase state with a saturation temperature greater than 0 ° C:
    the second heat transfer fluid loop B is restarted so that the heat transfer fluid circulates in the two-fluid exchanger 5 and the fourth heat exchanger 64, the compressor 3 is stopped, and an outside air flow 200 is generated.
    Each refrigerant has a specific pressure value for which its saturation temperature is greater than or equal to 0 ° C. For example, a refrigerant such as R134a has a saturation temperature above 0 ° C when it is at a pressure above 2.92 bar.
    A refrigerant such as R1234yf has a saturation temperature greater than or equal to 0 ° C when it is at a pressure greater than or equal to 3.16 bars.
    Thus, in the context of the invention, the second stage of this defrosting mode can start when the refrigerant at the pressure sensor 44 of the low-pressure refrigerant is at a pressure greater than 3 bars when it is R134a. Or more than 3.2 bars when it comes to R1234yf.
    The second stage of the defrosting mode can also be triggered when the pressure of the refrigerant fluid measured at the level of the pressure sensor 41 of the high pressure refrigerant fluid is greater than 18 bars, preferably greater than or equal to 20 bars.
    The second stage of the defrosting mode can also be triggered when the pressure of the refrigerant fluid measured at the pressure sensor 43 of the refrigerant at intermediate pressure is greater than or equal to 10 bars. This makes it possible in particular to prevent the second heat exchanger 13 from being damaged by a coolant passing through it at too high a pressure.
    Still during this second time of the defrosting mode, the second heat transfer fluid loop B is restarted by starting the pump 17. The central control unit 40 can in particular control the starting of this pump 17 and control the flow of the heat transfer fluid so that it is between 150 and 800 l / h.
    The central control unit 40 controls more particularly the second loop of heat transfer fluid B so that the heat transfer fluid circulates in the two-fluid exchanger 5 and the fourth heat exchanger 64. For this Γ central control unit 40 controls the device for redirection of the heat transfer fluid in particular by opening the fourth stop valve 63. Because the interior air flow 100 is stopped, the heat transfer fluid can circulate in the third heat exchanger 54 without exchanging heat. If the second heat transfer fluid loop B has a fifth stop valve 53, this can be closed to redirect all of the refrigerant to the fourth heat exchanger.
    The circulation of the heat-transfer fluid in the second heat-transfer fluid loop B makes it possible, at the level of the two-fluid heat exchanger 5, to recover the heat energy accumulated in the coolant during the first stage of the defrosting mode. This heat energy is then transported to the fourth heat exchanger 64 by the heat transfer fluid.
    In order to generate an outside air flow 200 again, the central control unit 40 can control the shutter device 93 so that it opens, if the latter is present. In addition, the central control unit 40 can start the front panel fan 91, in particular if the motor vehicle is stopped.
    The generation of the outside air flow 200 allows the fourth heat exchanger 64 to transfer heat energy from the heat transfer fluid to the outside air flow 200. As the fourth heat exchanger 64 is disposed upstream of the second heat exchanger 13 in the direction of flow of the outside air flow 200, the air heated at the fourth heat exchanger 64 will allow the second heat exchanger 13 to be defrosted.
    In order to more effectively evacuate the water resulting from the melting of the frost, the front panel fan 91 can more particularly be started at maximum speed for a period of between 10 and 60 s.
    A complete defrost mode cycle can for example extend over a maximum duration of between 5 and 10 min.
    This defrosting mode thus allows the frost to melt at the second heat exchanger 13 without having any repercussions for the user inside the passenger compartment. Unlike a solution where defrosting takes place in cooling mode, no cold air is returned to the passenger compartment.
    FIG. 9 shows a flow diagram 80 of an example of an operating method of the indirect invertible air conditioning circuit 1, the refrigerant of which is R1234yf, in a defrosting mode.
    Step 801 corresponds to a step of detecting the presence of frost at the second heat exchanger 13. If this detection is positive, it is possible to go to step 802.
    Step 802 corresponds to a detection step if the vehicle is stopped or if the shutter device 93 is closed. This makes it possible to check whether the outside air flow 200 is properly blocked. If the shutter device 93 is in the open position, the central control unit 40 controls its closing. When the outside air flow 200 is blocked, it is possible to go to step 803.
    Step 803 corresponds to a step of stopping the front face fan 91, the internal fan 92 and the pump 17, if one or other of these elements was in operation. When these three elements are stopped, it is possible to go to step 804.
    Step 804 corresponds to a step of opening the first stop valve 22 and closing the second stop valve 33. The first 7 and the second 11 expansion device are also opened completely or then bypassed so that the coolant flows through them without loss of pressure. When these elements are in this configuration, it is possible to go to step 805.
    Step 805 is a step of starting the compressor 3 and increasing its speed by 2000 rpm at maximum speed Nmax between 4500 and 8500 rpm.
    During this rise in speed, the pressure of the refrigerant fluid is measured at the level of the pressure sensors 41, 43 and 44 in a step 806.
    In a control step 807, if:
    • the coolant pressure measured at the pressure sensor 41 of the high pressure coolant is less than 20 bars, or if • the coolant pressure measured at the pressure sensor 43 of the intermediate pressure coolant is lower at 10 bars, or if • the pressure of the refrigerant fluid measured at the level of the pressure sensor 44 of the refrigerant fluid at low pressure is less than 3.2 bars, then compressor 3 continues its ramp-up in a step 808.
    If one of its conditions is no longer met, then the pump 17 is started with a flow rate between 150 and 800 l / h in a step 809. When the flow rate of the heat transfer fluid reached is within this range, step 810 can be skipped.
    Step 810 corresponds to a step of opening the shutter device 93.
    When the shutter device 93 is open, the compressor 3 is stopped during a step 811.
    After the compressor 3 has stopped, the front fan 91 is started at maximum speed for a time interval between 10 and 60 s.
    Other operating modes such as dehumidification, defrosting or heating modes can also be envisaged with such an architecture of the indirect reversible air conditioning circuit 1.
    Thus, it is clear that due to its architecture and its operating process, the indirect invertible air conditioning circuit 1, allows a mode of operation in heat pump with an optimal performance coefficient.
    权利要求:
    Claims (10)
    [1" id="c-fr-0001]
    1. Indirect reversible air conditioning circuit (1) for a motor vehicle, said indirect invertible air conditioning circuit (1) comprising:
    A first coolant loop (A) in which a coolant circulates, said first coolant loop (A) comprising in the direction of circulation of the coolant:
    ° a compressor (3), ° a two-fluid heat exchanger (5) ° a first expansion device (7), ° a first heat exchanger (9) being intended to be traversed by an internal air flow (100) to the motor vehicle, ° a second expansion device (11), ° a second heat exchanger (13) being intended to be traversed by a flow of air outside (200) to the motor vehicle, and ° a bypass line (30 ) of the second heat exchanger (13), • a second loop of heat transfer fluid (B) in which a heat transfer fluid circulates, said second circulation pipe (60) of heat transfer fluid comprising a fourth heat exchanger (64) intended to be through which the outside air flow (200) passes, said fourth heat exchanger (64) being arranged upstream of the second heat exchanger (13) in the direction of circulation of the outside air flow (200), dual fluid heat exchanger (5) being arranged jointly on the first coolant loop (A) downstream of the compressor (3), between said compressor (3) and the first expansion device (7), and on the second coolant loop (B), so as to allow heat exchanges between the first coolant loop (A) and the second heat transfer fluid loop (B), characterized in that the indirect reversible air conditioning circuit (1) further comprises:
    A pressure sensor (44) of the low-pressure refrigerant, said pressure sensor (44) being arranged downstream of the bypass line (30), between said bypass line (30) and the compressor (3), • a central control unit (40) connected to said pressure sensor (44) of the low pressure refrigerant and to said compressor (3), said central control unit (40) also being connected to the first (7) and to the second ( 11) expansion device so that they can be traversed by the refrigerant without loss of pressure or bypassed.
    [2" id="c-fr-0002]
    2. Indirect reversible air conditioning circuit (1) according to the preceding claim, characterized in that the indirect invertible circuit (1) comprises a pressure sensor (41) of the high pressure refrigerant, said sensor (41) being arranged downstream of the two-fluid heat exchanger (5), between said two-fluid heat exchanger (5) and the electronic expansion valve (7), centrale central control unit (40) being connected to said coolant temperature sensor (41 ) at high pressure.
    [3" id="c-fr-0003]
    3. Indirect reversible air conditioning circuit (1) according to one of the preceding claims, characterized in that the indirect invertible circuit (1) comprises a pressure sensor (43) of the refrigerant at intermediate pressure, said pressure sensor (43 ) being arranged downstream of the electronic expansion valve (7), between said electronic expansion valve (7) and the second expansion device (11), centrale central control unit (40) being connected to said pressure sensor (43) refrigerant at intermediate pressure.
    [4" id="c-fr-0004]
    4. Indirect reversible air conditioning circuit (1) according to one of the preceding claims, characterized in that the indirect invertible air conditioning circuit (1) comprises, at the front face of the motor vehicle, a shutter device (93) front panel movable between a shutter position and an open position, centrale central control unit (40) being connected to said front panel shutter device (93).
    [5" id="c-fr-0005]
    5. Indirect reversible air conditioning circuit (1) according to one of the preceding claims, characterized in that the indirect invertible air conditioning circuit (1) comprises a front face fan (91) arranged on the front face of the motor vehicle in order to produce the external air flow (200) centrale central control unit (40) being connected to said front face fan (91).
    [6" id="c-fr-0006]
    6. Method of operating an indirect reversible air conditioning circuit (1) according to one of the preceding claims, according to a defrosting mode in which, when frost is detected at the second heat exchanger (13):
    the second heat transfer fluid loop (B) is stopped, the indoor air flow (100) and the outdoor air flow (200) are stopped, the refrigerant of the first coolant loop (A ) passes successively through the compressor (3) where said refrigerant is compressed, the two-fluid heat exchanger (5), the first expansion device (7) through which said refrigerant passes without loss of pressure, the first heat exchanger ( 9), the second expansion device (7) through which said coolant passes without loss of pressure and the second heat exchanger (13) before returning to the compressor (3), when the pressure of the coolant measured by the pressure sensor (44) of the low pressure refrigerant is such that the said refrigerant is in the two-phase state with a saturation temperature above 0 ° C:
    the second heat transfer fluid loop (B) is restarted so that the heat transfer fluid circulates in the two-fluid exchanger (5) and the fourth heat exchanger (64), the compressor (3) is stopped, a flow of outside air (200) is generated.
    [7" id="c-fr-0007]
    7. Operating method according to the preceding claim, characterized in that the indirect reversible air conditioning circuit (1) comprises a pressure sensor (41) of the high pressure refrigerant and that the restarting of the second loop of heat transfer fluid. (B), stopping the compressor (3) and generating the external air flow (200) are also carried out if the pressure of the refrigerant measured at the pressure sensor (41) of the high-pressure refrigerant is greater than or equal to 20 bars.
    [8" id="c-fr-0008]
    8. Operating method according to one of claims 6 or 7, characterized in that the indirect reversible air conditioning circuit (1) comprises a pressure sensor (43) of the refrigerant at intermediate pressure and that the restarting of the second heat transfer fluid loop (B), the compressor stops (3) and the generation of the outside air flow (200) is also carried out if the pressure of the coolant measured at the pressure sensor (43) of the fluid refrigerant at intermediate pressure is greater than or equal to 10 bars.
    [9" id="c-fr-0009]
    9. Operating method according to one of claims 6 to 8, characterized in that the indirect reversible air conditioning circuit (1) comprises a closure device (93) on the front face and that in order to generate air flow exterior (200), said shutter device (93) on the front face is in the open position.
    [10" id="c-fr-0010]
    10. Operating method according to one of claims 6 to 9, characterized in that the indirect reversible air conditioning circuit (1) comprises a front fan (91) and that during the generation of the external air flow ( 200), said front face fan (91) is started at maximum speed for a period of between 10 and 60 s.
    1/9
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    同族专利:
    公开号 | 公开日
    CN110678342A|2020-01-10|
    EP3606776B1|2022-02-23|
    WO2018185415A1|2018-10-11|
    FR3064945B1|2019-04-19|
    EP3606776A1|2020-02-12|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US5605051A|1991-04-26|1997-02-25|Nippondenso Co., Ltd.|Automotive air conditioner having condenser and evaporator provided within air duct|
    DE112012005123T5|2011-12-09|2014-11-27|Sanden Corporation|Air conditioning of a vehicle|
    EP2933586A1|2014-04-16|2015-10-21|Valeo Systemes Thermiques|Refrigeration circuit|EP3736148A1|2019-05-08|2020-11-11|LG Electronics Inc.|Heat pump system for electric vehicle and control method thereof|
    FR3105381A1|2019-12-18|2021-06-25|Valeo Systemes Thermiques|Method of defrosting a thermal regulation circuit for a vehicle, in particular for a motor vehicle|
    DE102020114555A1|2020-05-29|2021-12-02|Konvekta Aktiengesellschaft|Improved cooling and heating device for a vehicle as well as system and vehicle with it and method for it|
    法律状态:
    2018-04-26| PLFP| Fee payment|Year of fee payment: 2 |
    2018-10-12| PLSC| Publication of the preliminary search report|Effective date: 20181012 |
    2019-04-29| PLFP| Fee payment|Year of fee payment: 3 |
    2020-04-30| PLFP| Fee payment|Year of fee payment: 4 |
    2021-04-29| PLFP| Fee payment|Year of fee payment: 5 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1752949A|FR3064945B1|2017-04-05|2017-04-05|MOTOR VEHICLE INVERTING INDIRECT AIR CONDITIONING CIRCUIT AND DEFROSTING MODE MANAGEMENT METHOD|
    FR1752949|2017-04-05|FR1752949A| FR3064945B1|2017-04-05|2017-04-05|MOTOR VEHICLE INVERTING INDIRECT AIR CONDITIONING CIRCUIT AND DEFROSTING MODE MANAGEMENT METHOD|
    PCT/FR2018/050811| WO2018185415A1|2017-04-05|2018-03-30|Indirect reversible air-conditioning circuit for a motor vehicle, and method for operation in defrosting mode|
    CN201880035551.8A| CN110678342A|2017-04-05|2018-03-30|Indirect reversible air conditioning circuit for a motor vehicle and method of operation in defrost mode|
    EP18722672.5A| EP3606776B1|2017-04-05|2018-03-30|Indirect reversible air-conditioning circuit for a motor vehicle, and method for operation in defrosting mode|
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