• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
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  • 优先权
    • 专利摘要:
    The present invention relates to an indirect air conditioning circuit (1) for a motor vehicle comprising: a first refrigerant fluid loop (A) comprising, a compressor (3), a first expansion device (7), a first heat exchanger ( 9), a second expansion device (11), a second heat exchanger (13) and a first bypass line (30) of the second heat exchanger (13) having a first shut-off valve (33), second coolant loop (B), • a first two-fluid heat exchanger (5), • a first internal heat exchanger (19), • a second internal heat exchanger (19 '), and • a second bypass line (40) of the first expansion device (7) and the first heat exchanger (9) comprising a third expansion device (17) arranged upstream of a second bifluid heat exchanger (15) also arranged together on a loop of secondary thermal management.
    公开号:FR3064946A1
    申请号:FR1752950
    申请日:2017-04-05
    公开日:2018-10-12
    发明作者:Jugurtha BENOUALI
    申请人:Valeo Systemes Thermiques SAS；
    IPC主号:
    专利说明:

    © Publication no .: 3,064,946 (to be used only for reproduction orders)
    ©) National registration number: 17 52950 ® 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. ©) 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 CORRESPONDING OPERATING METHOD.
    FR 3 064 946 - A1
    The present invention relates to an indirect air conditioning circuit (1) for a motor vehicle comprising:
    a first refrigerant loop (A) comprising, a compressor (3), a first expansion device (7), a first heat exchanger (9), a second expansion device (11), a second heat exchanger ( 13) and a first bypass line (30) of the second heat exchanger (13) comprising a first shut-off valve (33), a second loop of heat transfer fluid (B), a first dual-fluid heat exchanger (5), a first internal heat exchanger (19), a second internal heat exchanger (19 '), and a second bypass line (40) of the first expansion device (7) and the first heat exchanger (9) comprising a third expansion device (17) disposed upstream of a second dual-fluid heat exchanger (15) also arranged jointly on a secondary thermal management loop.

    The invention relates to the field of motor vehicles and more particularly to a motor vehicle air conditioning circuit and its operating method.
    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 absorb heat energy in the outside air at the level of the first heat exchanger. heat, 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.
    Such an air conditioning circuit allows use in different operating modes, however in the context of an electric or hybrid vehicle, the thermal management of elements such as batteries and electronic components is carried out by a secondary thermal management loop. This configuration increases production costs and the heat generated by these elements is lost when it could be reused to heat the passenger compartment and thus reduce the power consumption of the heat pump mode of the air conditioning circuit.
    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 also allowing thermal management of elements such as batteries, electronic components and the electric motor in particular. in an electric or hybrid vehicle.
    The present invention therefore relates to an indirect air conditioning circuit for a motor vehicle 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 first 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 heat exchanger being intended to be traversed by a flow of air outside the motor vehicle, and ° a first bypass pipe of the second heat exchanger comprising a first shut-off valve, • a second loop of heat transfer fluid in which circulates a coolant, • the first two-fluid heat exchanger being arranged jointly on the first coolant loop downstream of the compressor, between said compressor and the first expansion device, and on the second coolant loop, so as to allow heat exchange between the first refrigerant loop and the second fl loop heat transfer fluid, • a first internal heat exchanger, allowing heat exchange between the high pressure refrigerant leaving the first dual-fluid heat exchanger and the low pressure refrigerant leaving the second heat exchanger or the first pipe bypass, • a second internal heat exchanger allowing a heat exchange between the high pressure refrigerant leaving the first internal heat exchanger and the low pressure refrigerant circulating in the first bypass line, • a second bypassing the first expansion device and the first heat exchanger, said second bypass pipe comprising a third expansion device disposed upstream of a second dual-fluid heat exchanger also arranged jointly on a secondary thermal management loop.
    According to one aspect of the invention, the second bypass line is connected on the one hand upstream of the first expansion device and on the other hand on the bypass line, upstream of the first stop valve and the second exchanger internal heat.
    According to another aspect of the invention, the second bypass pipe is connected on the one hand upstream of the first expansion device and on the other hand on the bypass pipe, upstream of the second heat exchanger and downstream of the first stop valve.
    According to another aspect of the invention, the second bypass pipe is connected on the one hand upstream of the first expansion device and on the other hand downstream of the second expansion device, between said second expansion device and the first exchanger internal heat.
    According to another aspect of the invention, the first coolant loop includes a bypass line connected on the one hand to the first bypass line, upstream of the stop valve of the second heat exchanger and on the other hand upstream of the third expansion device between said third expansion device and a second stop valve, said bypass pipe comprising a third stop valve.
    According to another aspect of the invention, the second loop of heat transfer fluid comprises:
    ° the first two-fluid heat exchanger, ° a first heat transfer fluid circulation pipe comprising a third heat exchanger intended to be traversed by a flow of air inside the motor vehicle, and connecting a first junction point arranged downstream of the first two-fluid heat exchanger and a second junction point arranged upstream of said first two-fluid heat exchanger, ° a second heat-transfer fluid circulation pipe comprising a fourth heat exchanger intended to be traversed by an air flow outside the motor vehicle, and connecting the first junction point arranged downstream of the first two-fluid heat exchanger and the second junction point arranged upstream of said first two-fluid heat exchanger, and ° a pump arranged downstream or upstream of the first two-fluid heat exchanger, between the first junction point and the second junction point.
    The present invention also relates to a method of operating an indirect reversible air conditioning circuit according to a parallel secondary cooling mode in which:
    ° the refrigerant circulates in the compressor where said refrigerant passes at high pressure and successively circulates in the first two-fluid heat exchanger, the first internal heat exchanger, the second internal heat exchanger:
    a first part of the refrigerant passes through the second bypass line, passes through the third expansion device where said refrigerant passes at low pressure, said refrigerant at low pressure then circulates in the second dual-fluid heat exchanger before joining the fluid low pressure refrigerant from the first heat exchanger upstream from the first internal heat exchanger, a second part of the refrigerant passes through the first expansion device where said refrigerant passes at low pressure, said low pressure refrigerant then flows successively in the first heat exchanger, the first bypass line where it passes through the second internal heat exchanger, and then through the first internal heat exchanger before returning to the compressor, ° the heat transfer fluid at the outlet of the first two-fluid heat exchanger flows d in the fourth heat exchanger of the second circulation line.
    The present invention also relates to a method of operating an indirect reversible air conditioning circuit according to a strict secondary cooling mode in which:
    ° the refrigerant circulates in the compressor where said refrigerant passes at high pressure and successively circulates in the first dual-fluid heat exchanger, the first internal heat exchanger, the second internal heat exchanger, the refrigerant then passes in the second pipe bypass, passes into the third expansion device where said refrigerant passes at low pressure, said low pressure refrigerant then circulates in the second two-fluid heat exchanger, ° the heat transfer fluid at the outlet of the first two-fluid heat exchanger circulates in the fourth heat exchanger of the second circulation line.
    The present invention also relates to a method of operating an indirect reversible air conditioning circuit according to a parallel secondary heat pump mode in which:
    ° the refrigerant circulates in the compressor where said refrigerant passes at high pressure and successively circulates in the first two-fluid heat exchanger, the first internal heat exchanger, the second internal heat exchanger:
    a first part of the refrigerant passes through the second bypass line passing through the third expansion device where the refrigerant passes at low pressure, the second dual-fluid heat exchanger before joining the refrigerant from the second heat exchanger upstream of the first internal heat exchanger, a second part of the refrigerant passes through the first expansion device where said refrigerant passes to an intermediate pressure, said refrigerant then circulates successively in the first heat exchanger, the second expansion device where said fluid refrigerant passes at low pressure, the second heat exchanger, the refrigerant at low pressure then passes through the first internal heat exchanger before returning to the compressor, ° the heat transfer fluid leaving the first dual-fluid heat exchanger circulates only in the tr third heat exchanger of the first circulation pipe.
    The present invention also relates to a method of operating an indirect reversible air conditioning circuit according to a strict secondary heat pump mode in which:
    ° the refrigerant circulates in the compressor where said refrigerant passes at high pressure and successively circulates in the first two-fluid heat exchanger, the first internal heat exchanger, the second internal heat exchanger, the first expansion device where said refrigerant passes to an intermediate pressure, said refrigerant then circulates successively in the first heat exchanger, the first bypass pipe, the bypass pipe, the third expansion device where said refrigerant passes at low pressure, the second two-fluid heat exchanger , the refrigerant at low pressure then passes through the first internal heat exchanger before returning to the compressor, ° the heat transfer fluid leaving the first dual-fluid heat exchanger circulates only in the third heat exchanger of the first circulation line.
    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, Figure 4 shows a schematic representation of an indirect reversible air conditioning circuit according to a fourth embodiment, Figure 5 shows a pressure reduction device according to one embodiment alternative embodiment, FIG. 6 shows a schematic representation of the second heat transfer fluid loop of the indirect reversible air conditioning circuit of FIGS. 1 to 4, according to an alternative embodiment, FIG. 7a shows the indirect reversible air conditioning circuit of FIGS. 1 to 3 according to a cooling mode, FIG. 7b shows the indirect reversible air conditioning circuit of figure 4 according to a cooling mode, figure 8a shows the indirect reversible air conditioning circuit of figure 1 according to a parallel secondary cooling mode, figure 8b shows the indirect reversible air conditioning circuit of Figure 2 according to a parallel secondary cooling mode, Figure 8c shows the indirect reversible air conditioning circuit of Figure 3 according to a parallel secondary cooling mode, Figure 8d shows the indirect reversible air conditioning circuit of Figure 4 according to a mode of secondary parallel cooling, FIG. 9a shows the indirect reversible air conditioning circuit of FIG. 1 according to a strict secondary cooling mode, FIG. 9b shows the indirect reversible air conditioning circuit of FIG. 2 according to a strict secondary cooling mode, the figure 9c shows the indirect reversible air conditioning circuit of FIG. 3 according to a strict secondary cooling mode, FIG. 9d shows the indirect reversible air conditioning circuit of FIG. 4 according to a strict secondary cooling mode, FIG. 10a shows the indirect reversible air conditioning circuit of FIGS. 1 to 3 according to a heat pump mode, FIG. 10b shows the indirect reversible air conditioning circuit of FIG. 4 according to a heat pump mode, FIG. 11a shows the indirect invertible air conditioning circuit of FIG. 2 according to a secondary heat pump mode parallel, FIG. 11b shows the indirect reversible air conditioning circuit of FIG. 3 according to a parallel secondary heat pump mode, FIG. 11c shows the indirect reversible air conditioning circuit of FIG. 4 according to a parallel secondary heat pump mode, and FIG. 12 shows the indirect reversible air conditioning circuit of FIG. 4 according to a striated secondary heat pump mode ct,
    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 even 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 flows, and • a first two-fluid heat exchanger 5 arranged jointly on the first coolant loop A and on the second loop of heat transfer fluid B, so as to allow heat exchanges between said first loop of coolant A and said second loop of heat transfer fluid B.
    The first refrigerant loop A comprises more particularly in the direction of circulation of the refrigerant:
    ° a compressor 3, ° the first two-fluid heat exchanger 5, arranged downstream of said compressor 3, ° a first expansion device 7, ° a first heat exchanger 9 being intended to be traversed by an internal air flow 100 at 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 first bypass line 30 of the second heat exchanger 13.
    The first 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.
    In order to control the passage of the coolant within the first bypass line 30 or not, the latter comprises a first stop valve 33. In order that the coolant does not pass through the second heat exchanger 13, the second device detent 11 may in particular include a stop function, that is to say that it is capable of blocking the flow of coolant when it is closed. An alternative may be to have a stop valve between the second expansion device 11 and the first connection point 31.
    Another alternative (not shown) may also be to have a three-way valve at the first connection point 31.
    The first refrigerant loop A can also include 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 in order to prevent refrigerant from the first bypass line 30 does not flow back to the second heat exchanger 13.
    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.
    The first refrigerant loop A also includes a first internal heat exchanger 19 (IHX for "internai heat exchanger") allowing a heat exchange between the high pressure refrigerant leaving the first dual fluid heat exchanger 5 and the refrigerant at low pressure at the outlet of the second heat exchanger 13 or of the first bypass pipe 30. This first internal heat exchanger 19 comprises in particular an inlet and an outlet of refrigerant at low pressure coming from the second connection point 32, thus that an inlet and an outlet for high pressure refrigerant coming from the first two-fluid heat exchanger 5.
    By high pressure refrigerant is meant by this a refrigerant having undergone an increase in pressure at the compressor 3 and that it has not yet suffered a loss of pressure due to one of the expansion devices. By low-pressure refrigerant is meant by this a refrigerant having undergone a pressure loss and at a pressure close to that at the inlet of the compressor 3.
    The first refrigerant loop A also includes a second internal heat exchanger 19 ′ allowing a heat exchange between the high pressure refrigerant leaving the first internal heat exchanger 19 and the low pressure refrigerant circulating in the first pipe. bypass 30. This second internal heat exchanger 19 ′ includes in particular an inlet and an outlet for low pressure refrigerant coming from the first connection point 31, as well as an inlet and an outlet for high pressure refrigerant coming from of the first internal heat exchanger 19. As illustrated in FIG. 1, the second internal heat exchanger 19 ′ can be arranged downstream of the first stop valve 33.
    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.
    The first cooling fluid loop A can also include a desiccant bottle 14 disposed downstream of the first dual-fluid heat exchanger 5, more precisely between said first dual-fluid heat exchanger 5 and the first internal heat exchanger 19. Such a desiccant bottle disposed 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 reduced cost compared to d 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 3064946, upstream of the compressor 3, in particular upstream of the first internal heat exchanger 19.
    The first 7 and second 11 expansion devices can be electronic expansion valves, that is to say the pressure of the refrigerant outlet fluid is controlled by an actuator which fixes the opening section of the expansion device, thereby fixing the pressure of the fluid output. Such an electronic expansion valve is in particular capable of allowing the coolant to pass without loss of pressure when said expansion device is fully open.
    According to a preferred embodiment, the first expansion device 7 is an electronic expansion valve controllable by a control unit integrated into the vehicle and the second expansion device 11 is a thermostatic expansion valve.
    The second expansion device 11 may in particular be a thermostatic expansion valve incorporating a stop function. In this case, said first 7 and second 11 expansion devices can be bypassed by a bypass line A ', comprising in particular a stop valve 25, as illustrated in FIG. 5. This bypass line A' allows the refrigerant fluid to bypass said first 7 and second 11 expansion devices without it suffering a pressure loss. Preferably, at least the second expansion device 11 is a thermostatic expansion valve comprising a bypass line A '. The first expansion device 7 can also include a stop function or else include a downstream stop valve in order to block or not the passage of the refrigerant.
    The first coolant loop A also includes a second bypass pipe 40 of the first expansion device 7 and the first heat exchanger 9. This second bypass pipe 40 includes a third expansion device 17 disposed upstream of a second exchanger two-fluid heat exchanger 15. This second two-fluid heat exchanger 15 is also arranged jointly on a secondary thermal management loop. The secondary thermal management loop can more particularly be a loop in which a heat transfer fluid circulates and connected to heat exchangers or cold plates at the level of batteries and / or electronic elements.
    The third expansion device 17 can also include a stop function in order to allow or not the refrigerant to pass through the second bypass pipe 40. An alternative is to have a stop valve on the second bypass pipe, upstream of the third expansion device 17.
    The second bypass pipe 40 is connected on the one hand upstream of the first expansion device 7. This connection is made at a third connection point 41 disposed upstream of the first expansion device 7, between the second heat exchanger heat 19 'and said first expansion device 7.
    According to a first embodiment illustrated in FIG. 1, the second bypass line 40 is connected on the other hand to the first bypass line 30, upstream from the first stop valve 33 and from the second internal heat exchanger 19 '. This connection is made at a fourth connection point 42 disposed between the first connection point 31 and the first stop valve 33 when the latter is disposed upstream of the second internal heat exchanger 19 ′ as in the figure 1.
    According to a second embodiment illustrated in Figure 2, the second bypass line 40 is connected on the other hand to the first bypass line 30, upstream of the second heat exchanger 19 'and downstream of the first valve stop 33. The fourth connection point 42 is then disposed between the first stop valve 33 and the second heat exchanger 19 'when the first stop valve 33 is arranged upstream of the second internal heat exchanger 19' as on Figure 2.
    FIG. 3 shows a third embodiment where the second bypass pipe 40 is connected on the one hand upstream of the first expansion device 7 and on the other hand downstream of the second expansion device 19 ', between said second device expansion 19 'and the first internal heat exchanger 19. The third connection point 41 is thus also arranged upstream of the first expansion device 7, between the second heat exchanger 19' and said first expansion device 7.
    In the example of FIG. 3, the fourth connection point 42 is arranged downstream of the first bypass pipe 30, between the second connection point 32 and the first internal heat exchanger 19. However, it is also quite possible to imagine that the fourth connection point 42 is disposed on the first bypass pipe 30, downstream of the first stop valve 33 and the second internal heat exchanger 19 '.
    FIG. 4 shows a fourth embodiment identical to that of FIG. 3 with the difference that the first coolant loop A comprises a bypass line 70 connected on the one hand to the first bypass line 30, upstream of the first shut-off valve 33 and second heat exchanger 19 '. The connection is made by a fifth connection point 71 disposed between the first connection point 31 and the first stop valve 33 when the latter is disposed upstream of the second internal heat exchanger 19 ′, as illustrated in FIG. 4 .
    This bypass line 70 is connected on the other hand to the second bypass line 40, upstream of the third expansion device 17 between said third expansion device 17 and a second stop valve 73. This second stop valve 73 is disposed between the third connection point 41 and the third expansion device 17. The connection of the bypass pipe 70 is then carried out at a fifth connection point 72 disposed downstream of the second stop valve 73. This bypass pipe 70 includes a third stop valve 74 in order to allow the refrigerant fluid to pass therein or not.
    The second heat transfer fluid loop B can include:
    ° the first two-fluid heat exchanger 5, ° a first circulation pipe 50 for 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 first dual-fluid heat exchanger 5 and a second junction point 62 disposed upstream of said first dual-fluid heat exchanger 5, ° a second circulation pipe 60 of coolant comprising a fourth heat exchanger 64 intended to be traversed by an external air flow 200 to the motor vehicle, and connecting the first junction point 61 disposed downstream of the first dual-fluid heat exchanger 5 and the second junction point 62 disposed upstream of said first dual-fluid heat exchanger 5, and ° a pump 18 disposed downstream or upstream of the first two-fluid heat exchanger 5, between the first junction point 6 1 and the second junction point 62.
    The indirect reversible air conditioning circuit 1 includes, within the second heat transfer fluid loop B, a device for redirecting the heat transfer fluid from the first two-fluid heat exchanger 5 to the first circulation line 50 and / or to the second circulation line 60.
    As illustrated in FIGS. 1 to 4, said device for redirection of the heat-transfer fluid coming from the first two-fluid heat exchanger 5 can in particular comprise a fourth stop valve 63 disposed on the second circulation pipe 60 in order to block or not the fluid coolant and prevent it from circulating in said second circulation pipe 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. 6, the device for redirection of the heat-transfer fluid coming from the first two-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 flowing in said first circulation line 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 first two-fluid heat exchanger 5, between said first two-fluid heat exchanger 5 and the first junction point 61.
    The present invention also relates to a method of operating the indirect reversible air conditioning circuit 1 according to different operating modes illustrated in FIGS. 7a to 12. In these FIGS. 7a, to 12, only the elements in which the refrigerant and / or the heat-transfer fluid circulating are represented. The direction of circulation of the refrigerant and / or the coolant is represented by arrows.
    FIGS. 7a and 7b show a cooling mode in which:
    • the refrigerant circulates in the compressor 3 where said refrigerant passes at high pressure and successively circulates in the first dual-fluid heat exchanger 5, the first internal heat exchanger 19, the second internal heat exchanger 19 ', and the first device expansion valve 7 where said refrigerant passes at low pressure, said refrigerant at low pressure then circulates successively in the first heat exchanger 9, the first bypass line 30 where it passes in the second internal heat exchanger 19 ', and then in the first internal heat exchanger 19 before returning to the compressor 3, • the heat transfer fluid leaving the first dual-fluid heat exchanger 5 circulates in the fourth heat exchanger 64 of the second circulation line 60.
    FIG. 7a shows this cooling mode when the indirect reversible air conditioning circuit 1 is according to the first embodiment of FIG. 1. However, when the indirect reversible air conditioning circuit 1 is according to the second embodiment of FIG. 2 or the third embodiment of FIG. 3, the circulation of the coolant is the same unlike the location of the fourth connection point 42.
    FIG. 7b shows this cooling mode when the indirect reversible air conditioning circuit 1 is according to the fourth embodiment of FIG. 4.
    As illustrated in FIGS. 7a and 7b, a portion of the heat transfer fluid at the outlet of the first two-fluid heat exchanger 5 circulates in the third heat exchanger 54 of the first circulation pipe 50 and another portion of the heat transfer fluid at the outlet of the first exchanger dual-fluid heat 5 circulates in the fourth heat exchanger 64 of the second circulation line 60. The obstruction flap 310 is closed so as to prevent the interior air flow 100 from circulating in the third heat exchanger 54.
    The refrigerant at the inlet of compressor 3 is in the gas phase. The refrigerant undergoes compression while passing through the compressor 3. Said refrigerant is then said to be at high pressure.
    The high pressure refrigerant passes through the first two-fluid heat exchanger 5 and undergoes a loss of enthalpy due to its passage into the liquid phase and the transfer of enthalpy to the heat transfer fluid of the second heat transfer fluid loop B. The fluid high pressure refrigerant then loses enthalpy while remaining at a constant pressure.
    The high pressure refrigerant then passes through the first internal heat exchanger 19 where it loses enthalpy. This enthalpy is transferred to the low pressure refrigerant fluid from the first bypass pipe 30.
    The high pressure refrigerant then passes through the second internal heat exchanger 19 'where it loses enthalpy again. This enthalpy is transferred to the low pressure refrigerant fluid passing through the first bypass pipe 30.
    As illustrated in FIG. 7a, at the outlet of the second internal heat exchanger 19 ’, the refrigerant does not circulate in the second bypass pipe 40 because the third expansion device 17 is closed.
    If the indirect reversible air conditioning circuit 1 is according to the fourth embodiment as illustrated in FIG. 7b, the refrigerant does not circulate in the second bypass pipe 40 because the second stop valve 73 is closed.
    The high pressure refrigerant then passes through the first expansion device 7. The high pressure refrigerant undergoes an isenthalpic pressure loss and passes into a two-phase mixture state. The refrigerant is now said to be at low pressure.
    The low pressure refrigerant then passes into the first heat exchanger 9 where it gains enthalpy by cooling the interior air flow 100. The refrigerant returns to the gaseous state. At the outlet of the first heat exchanger 9, the refrigerant is redirected to the first bypass pipe 30. So that the refrigerant does not pass into the second heat exchanger 13, the second expansion device 11 is closed.
    As illustrated in FIG. 7b, if a bypass line 70 is present, the refrigerant does not pass through said bypass line 70 because the third stop valve 74 is closed.
    The low pressure refrigerant then passes into the second internal heat exchanger 19 'where it gains enthalpy from the high pressure refrigerant passing through the second internal heat exchanger 19'.
    The low pressure refrigerant then passes into the first internal heat exchanger 19 where it again gains enthalpy from the high pressure refrigerant passing through the first internal heat exchanger 19. The low pressure refrigerant then returns to compressor 3.
    This cooling mode is useful for cooling the indoor air flow 100.
    In this 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 coolant entering the first expansion device 7. The coolant in the liquid state at the exit of the first two-fluid heat exchanger 5 is cooled by the refrigerant in the gaseous state and at low pressure leaving the first heat exchanger 9. The difference in enthalpy at the terminals of the first heat exchanger 9 increases appreciably which allows, 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 coefficient of performance (or COP for “coefficient of performance”).
    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 it enters the compressor 3, in particular when the air conditioning circuit 1 comprises a desiccant bottle 14 disposed downstream of the first two-fluid heat exchanger 5.
    At the second heat transfer fluid loop B, the heat transfer fluid gains enthalpy from the coolant at the first dual fluid heat exchanger 5.
    As illustrated in FIGS. 7a and 7b, a portion of the heat transfer fluid circulates in the first circulation line 50 and passes through the third heat exchanger 54. The heat transfer fluid does not, however, lose any enthalpy because 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 enthalpy at 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. 6, the first circulation pipe 50 with the fifth stop valve 53 and to close it so as to prevent the coolant from flowing in said first circulation pipe 50.
    FIGS. 8a to 8b show a parallel secondary cooling mode in which:
    The refrigerant circulates in the compressor 3 where said refrigerant passes at high pressure and circulates successively in the first dual-fluid heat exchanger 5, the first internal heat exchanger 19, the second internal heat exchanger 19 ':
    a first part of the refrigerant passes through the second bypass line 40, passes through the third expansion device 17 where said refrigerant passes at low pressure, said refrigerant at low pressure then circulates in the second dual-fluid heat exchanger 15 before join the low pressure refrigerant from the first heat exchanger 9 upstream of the first internal heat exchanger 19, a second part of the refrigerant passes through the first expansion device 7 where said refrigerant passes at low pressure, said refrigerant at low pressure then successively circulates in the first heat exchanger 9, the first bypass line 30 where it passes through the second internal heat exchanger 19 ′, and then through the first internal heat exchanger 19 before returning to the compressor 3, ° the heat transfer fluid at the outlet of the first exchanger of two-fluid heat 5 circulates in the fourth heat exchanger 64 of the second circulation line 50.
    As illustrated in FIGS. 8a to 8c, a portion of the heat transfer fluid at the outlet of the first two-fluid heat exchanger 5 circulates in the third heat exchanger 54 of the first circulation pipe 50 and another portion of the heat transfer fluid at the outlet of the first exchanger of dual-fluid heat 5 circulates in the fourth heat exchanger 64 of the second circulation line 50. The obstruction flap 310 is closed so as to prevent the internal air flow 100 from circulating in the third heat exchanger 54.
    FIGS. 8a and 8b show the parallel secondary cooling mode when the indirect reversible air conditioning circuit 1 is respectively according to the first embodiment of FIG. 1 and the second embodiment of FIG. 2.
    In these two embodiments, the refrigerant at the inlet of the compressor 3 is in the gas phase. The refrigerant undergoes compression while passing through the compressor 3. Said refrigerant is then said to be at high pressure at the outlet of said compressor 3.
    The high pressure refrigerant passes through the first two-fluid heat exchanger 5 and undergoes a loss of enthalpy due to its passage into the liquid phase and the transfer of enthalpy to the heat transfer fluid of the second heat transfer fluid loop B. The fluid high pressure refrigerant then loses enthalpy while remaining at a constant pressure.
    The high pressure refrigerant then passes through the first internal heat exchanger 19 where it loses enthalpy. This enthalpy is transferred to the low pressure refrigerant fluid from the first bypass pipe 30.
    The high pressure refrigerant then passes through the second internal heat exchanger 19 'where it loses enthalpy again. This enthalpy is transferred to the low pressure refrigerant fluid passing through the first bypass pipe 30.
    As illustrated in FIGS. 8a and 8b, at the outlet of the second internal heat exchanger 19 ′, a first part of the refrigerant passes through the second bypass pipe 40 and a second part of the refrigerant goes towards the first expansion device 7 .
    The first part of the refrigerant passes through the third expansion device 17. The high pressure refrigerant undergoes isenthalpic pressure loss and passes into a two-phase mixture state. The refrigerant is now said to be at low pressure.
    The low pressure refrigerant then passes into the second two-fluid heat exchanger 15 where it gains enthalpy by cooling the heat transfer fluid circulating in the secondary thermal management loop. The refrigerant returns to the gaseous state. At the outlet of the second dual-fluid heat exchanger 15, the coolant joins the first bypass line 30. In the first embodiment illustrated in FIG. 8a, the coolant joins the first bypass line 30 upstream of the first valve 33 and the second internal heat exchanger 19 '. In the second embodiment illustrated in Figure 8b, the refrigerant joins the first bypass line 30 downstream of the first stop valve 33 and upstream of the second internal heat exchanger 19 ’.
    The second part of the high pressure refrigerant passes through the first expansion device 7. The high pressure refrigerant undergoes an isenthalpic pressure loss and passes into a two-phase mixture state. The refrigerant is now said to be at low pressure.
    The low pressure refrigerant then passes into the first heat exchanger 9 where it gains enthalpy by cooling the interior air flow 100. The refrigerant returns to the gaseous state. At the outlet of the first heat exchanger 9, the refrigerant is redirected to the first bypass pipe 30. So that the refrigerant does not pass into the second heat exchanger 13, the second expansion device 11 is closed.
    The low pressure refrigerant from both the first heat exchanger 9 and the second bypass line 40 then passes into the second internal heat exchanger 19 'where it gains enthalpy from the high pressure refrigerant through the second internal heat exchanger 19 '.
    The low pressure refrigerant then passes into the first internal heat exchanger 19 where it again gains enthalpy from the high pressure refrigerant passing through the first internal heat exchanger 19. The low pressure refrigerant then returns to compressor 3.
    This cooling mode is useful for cooling the internal air flow 100 as well as for cooling the heat transfer fluid of the secondary thermal management loop in order to cool elements such as batteries and / or electronic elements.
    In this parallel secondary cooling mode, for the first and second embodiments, the two internal heat exchangers 19 and 19 ′ are active both for the coolant coming from the first heat exchanger 9 and the coolant passing through the second bypass 40, 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 coolant entering the first expansion device 7. The coolant in the liquid state at the exit of the first two-fluid heat exchanger 5 is cooled by the refrigerant in the gaseous state and at low pressure leaving the first heat exchanger 9 and the second two-fluid heat exchanger 15. The difference in enthalpy at the terminals of these two heat exchangers increases substantially which allows both an increase in the cooling capacity available at said first heat exchanger 9 and the second two-fluid heat exchanger 15 and this therefore leads to an improvement in the coefficient of performance (or COP for "coefficient of performance" ).
    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 entering the compressor 3, in particular when the air conditioning circuit 1 comprises a desiccant bottle 14 disposed downstream of the first two-fluid heat exchanger 5.
    FIGS. 8c and 8d show the parallel secondary cooling mode when the indirect reversible air conditioning circuit 1 is respectively according to the third embodiment of FIG. 3 and the fourth embodiment of FIG. 4.
    In these two embodiments, the refrigerant at the inlet of the compressor 3 is in the gas phase. The refrigerant undergoes compression while passing through the compressor 3. Said refrigerant is then said to be at high pressure.
    The high pressure refrigerant passes through the first two-fluid heat exchanger 5 and undergoes a loss of enthalpy due to its passage into the liquid phase and the transfer of enthalpy to the heat transfer fluid of the second heat transfer fluid loop B. The fluid high pressure refrigerant then loses enthalpy while remaining at a constant pressure.
    The high pressure refrigerant then passes through the first internal heat exchanger 19 where it loses enthalpy. This enthalpy is transferred to the low pressure refrigerant fluid from the first bypass pipe 30.
    The high pressure refrigerant then passes into the second internal heat exchanger 19 'where it loses heat again. This enthalpy is transferred to the low pressure refrigerant fluid passing through the first bypass pipe 30.
    As illustrated in FIGS. 8c and 8d, at the outlet of the second internal heat exchanger 19 ′, a first part of the refrigerant passes through the second bypass pipe 40 and a second part of the refrigerant goes towards the first expansion device 7 According to the fourth embodiment illustrated in FIG. 8d, the first part of the coolant can pass through the second bypass pipe 40 because the second stop valve 73 is open.
    The first part of the refrigerant passes through the third expansion device 17. The high pressure refrigerant undergoes isenthalpic pressure loss and passes into a two-phase mixture state. The refrigerant is now said to be at low pressure. According to the fourth embodiment illustrated in Figure 8d, the first part of the refrigerant does not pass through the bypass line 70 because the third stop valve 74 is closed.
    The low pressure refrigerant then passes into the second two-fluid heat exchanger 15 where it gains enthalpy by cooling the heat transfer fluid circulating in the secondary thermal management loop. The refrigerant returns to the gaseous state. At the outlet of the second dual-fluid heat exchanger 15, the refrigerant joins the second part of the refrigerant which comes from the first heat exchanger 9 downstream from the second internal heat exchanger 19 ’.
    The second part of the high pressure refrigerant passes through the first expansion device 7. The high pressure refrigerant undergoes an isenthalpic pressure loss and passes into a two-phase mixture state. The refrigerant is now said to be at low pressure.
    The low pressure refrigerant then passes into the first heat exchanger 9 where it gains enthalpy by cooling the interior air flow 100. The refrigerant returns to the gaseous state. At the outlet of the first heat exchanger 9, the refrigerant is redirected to the first bypass pipe 30. So that the refrigerant does not pass into the second heat exchanger 13, the second expansion device 11 is closed.
    The low pressure refrigerant from the first heat exchanger 9 then passes into the second internal heat exchanger 19 'where it gains enthalpy from the high pressure refrigerant passing through the second internal heat exchanger 19'.
    The low pressure refrigerant from both the first heat exchanger 9 and the second bypass line 40 then passes into the first internal heat exchanger 19 where it again gains enthalpy from the high pressure refrigerant passing through the first internal heat exchanger 19. The low pressure refrigerant then returns to the compressor 3.
    This cooling mode is useful for cooling the internal air flow 100 as well as for cooling the heat transfer fluid of the secondary thermal management loop in order to cool elements such as batteries and / or electronic elements.
    In this parallel secondary cooling mode, the two internal heat exchangers 19 and 19 'are active only for the refrigerant coming from the first heat exchanger 9, 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 coolant entering the first expansion device 7. The coolant in the liquid state at the exit of the first two-fluid heat exchanger 5 is cooled by the refrigerant in the gaseous state and at low pressure leaving the first heat exchanger 9. The difference in enthalpy at the terminals of the first heat exchanger 9 increases appreciably which allows, an increase in the cooling capacity available at said first heat exchanger 9 and therefore results in an improvement in the coefficient of performance (or COP for “coefficient of performance”).
    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 it enters the compressor 3, in particular when the air conditioning circuit 1 comprises a desiccant bottle 14 disposed downstream of the first two-fluid heat exchanger 5.
    At the second heat transfer fluid loop B, the heat transfer fluid gains enthalpy from the coolant at the first dual fluid heat exchanger 5.
    As illustrated in FIGS. 8a to 8d, 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 because 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 enthalpy at 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. 6, the first circulation pipe 50 with the fifth stop valve 53 and to close it so as to prevent the coolant from flowing in said first circulation pipe 50.
    FIGS. 9a to 9c show a strict secondary cooling mode in which:
    ° the refrigerant circulates in the compressor 3 where said refrigerant passes at high pressure and successively circulates in the first dual-fluid heat exchanger 5, the first internal heat exchanger 19, the second internal heat exchanger 19 ', the refrigerant passes then in the second bypass pipe 40, passes into the third expansion device 17 where said refrigerant passes at low pressure, said refrigerant at low pressure then circulates in the second dual-fluid heat exchanger 15, ° the heat transfer fluid leaving the first dual-fluid heat exchanger 5 circulates in the fourth heat exchanger 64 of the second circulation pipe 50.
    Figure 9a shows this strict secondary cooling mode for the first embodiment of Figure 1. Figure 9b shows this strict secondary cooling mode for the second embodiment of Figure 2. Figure 9c shows this cooling mode strict secondary for the third embodiment of FIG. 3. FIG. 9d shows this strict secondary cooling mode for the fourth embodiment of FIG. 4.
    This strict secondary cooling mode is identical to the parallel secondary cooling mode described above with the difference that the high pressure refrigerant leaving the second heat exchanger 19 ′ circulates only in the second bypass line 40 and does not pass by the first heat exchanger 9. For this, the first expansion device 7 is closed.
    This strict secondary cooling mode is therefore useful when you only want to cool the heat transfer fluid circulating in the secondary thermal management loop.
    Figures 10a and 10b show a heat pump mode in which:
    • the refrigerant circulates in the compressor 3 where said refrigerant passes at high pressure and successively circulates in the first dual-fluid heat exchanger 5, the first internal heat exchanger 19, the second internal heat exchanger 19 ', and the first device expansion valve 7 where said refrigerant passes to an intermediate pressure, said refrigerant at intermediate pressure then circulates successively in the first heat exchanger 9, the second expansion device 11 where said refrigerant passes at low pressure, the second heat exchanger 13 and then in the first internal heat exchanger 19 before returning to the compressor 3, • the heat transfer fluid at the outlet of the first dual-fluid heat exchanger 5 circulates only in the third heat exchanger 54 of the first circulation line 50.
    By intermediate pressure here is meant a pressure situated between the low pressure of the refrigerant when it enters the compressor 3 and the high pressure of the refrigerant at the outlet of said compressor 3.
    The refrigerant at the inlet of compressor 3 is in the gas phase. The refrigerant undergoes compression while passing through the compressor 3. Said refrigerant is then said to be at high pressure.
    The high pressure refrigerant passes through the first two-fluid heat exchanger 5 and undergoes a loss of enthalpy due to its passage into the liquid phase and the transfer of enthalpy to the heat transfer fluid of the second heat transfer fluid loop B. The fluid high pressure refrigerant then loses enthalpy while remaining at a constant pressure.
    The high pressure refrigerant then passes through the first internal heat exchanger 19 where it loses enthalpy. This enthalpy is transferred to the low pressure refrigerant coming from the second heat exchanger 13.
    The high pressure refrigerant then passes into the second internal heat exchanger 19 'where it does not lose enthalpy because there is no circulation of refrigerant in said second internal heat exchanger 19'.
    As illustrated in FIG. 10a, at the outlet of the second internal heat exchanger 19 ’, the refrigerant does not circulate in the second bypass pipe 40 because the third expansion device 17 is closed.
    If the indirect reversible air conditioning circuit 1 is according to the fourth embodiment as illustrated in FIG. 10b, the refrigerant does not circulate in the second bypass pipe 40 because the second stop valve 73 is closed.
    The high pressure refrigerant then passes through the first expansion device 7. The refrigerant undergoes a first isenthalpic pressure loss which causes it to pass into a state of two-phase mixture. The refrigerant is now at an intermediate pressure.
    The refrigerant then passes through the first heat exchanger 9 where it loses enthalpy by heating the indoor air flow 100.
    At the outlet of the first heat exchanger 9, the refrigerant is redirected to the second heat exchanger 13. For this, the first stop valve 33 of the first bypass pipe is closed. Before arriving at the second heat exchanger 13, the refrigerant passes through the first expansion device 11 where it undergoes a second isenthalpic pressure loss. The refrigerant is now at low pressure.
    As illustrated in FIG. 10b, if a bypass line 70 is present, the intermediate pressure refrigerant does not pass through said bypass line 70 because the third stop valve 74 is closed.
    The low pressure refrigerant then passes through the second heat exchanger 13 where it gains enthalpy by absorbing enthalpy from the outside air flow 200. The refrigerant thus returns to the gaseous state.
    The low pressure refrigerant then passes into the first internal heat exchanger 19 where it again gains enthalpy from the high pressure refrigerant passing through the first internal heat exchanger 19. The low pressure refrigerant then returns to compressor 3.
    In this heat pump mode, only the first internal heat exchanger 19 is active. Because the enthalpy of the low pressure refrigerant entering the compressor 3 is greater, the enthalpy of the high pressure refrigerant leaving the compressor 3 will also be greater than the enthalpy of the refrigerant when it there is no internal heat exchanger.
    In addition, the addition of enthalpy to the low pressure refrigerant at the first internal heat exchanger 19 makes it possible to limit the proportion of refrigerant in the liquid phase before it enters the compressor 3, in particular when the air conditioning circuit 1 comprises a desiccant bottle 14 disposed downstream of the first two-fluid heat exchanger 5. The effect of the first internal heat exchanger 19 is limited because its length is between 50 and 120 mm. 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 the 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. This enthalpy comes, in this pump mode to heat, from the outside air flow 200 via the second heat exchanger 13.
    At the second heat transfer fluid loop B, the heat transfer fluid gains enthalpy from the coolant at the first dual fluid heat exchanger 5.
    As illustrated in FIGS. 10a and 10b, 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 obstruction flap 310 is open and / 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 interior air flow 100 both at the level of the first heat exchanger 9 and of the third heat exchanger 54 by absorbing enthalpy of the exterior air flow 200 at the level of 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 indoor air flow 100.
    FIGS. 11a to 11c show a parallel secondary heat pump mode in which:
    The refrigerant circulates in the compressor 3 where said refrigerant passes at high pressure and circulates successively in the first dual-fluid heat exchanger 5, the first internal heat exchanger 19 and the second internal heat exchanger 19 ':
    a first part of the refrigerant passes through the second bypass pipe 40 through the third expansion device 17 where the refrigerant passes at low pressure, the second dual-fluid heat exchanger 15 before joining the refrigerant from the second heat exchanger upstream of the first internal heat exchanger 19, a second part of the refrigerant passes through the first expansion device 7 where said refrigerant passes to an intermediate pressure, said refrigerant then circulates successively in the first heat exchanger 9, the second expansion device 11 where said refrigerant passes at low pressure and in the second heat exchanger 13, the low pressure refrigerant then passes through the first internal heat exchanger (19) before returning to the compressor (3), ° the fluid coolant at the outlet of the first heat exchanger dual fluid (5) circulates only in the third heat exchanger (54) of the first circulation line (50).
    This parallel secondary heat pump mode is only possible if the refrigerant at intermediate pressure at the outlet of the first heat exchanger 9 does not pass through the first bypass pipe 30 and passes through the second expansion device 11 and the second heat exchanger. heat 13. This is therefore only possible if the first stop valve 33 is closed. In addition it is also necessary that part of the high pressure refrigerant can pass through the second bypass pipe 40 and join the low pressure refrigerant from the second heat exchanger 13. However, this is impossible in the case of the first embodiment where the second connection point 42 of the second bypass pipe 40 is located upstream of the first stop valve 33. Therefore only the second, third and fourth embodiments can implement this mode of pump parallel secondary heat.
    FIG. 11 a shows this secondary heat pump mode when the indirect reversible air conditioning circuit 1 is according to the second embodiment of FIG. 2.
    FIG. 1 lb shows this secondary heat pump mode when the indirect reversible air conditioning circuit 1 is according to the third embodiment of FIG. 3.
    FIG. 11c shows this secondary heat pump mode when the indirect reversible air conditioning circuit 1 is according to the fourth embodiment of FIG. 4.
    The refrigerant at the inlet of compressor 3 is in the gas phase. The refrigerant undergoes compression while passing through the compressor 3. Said refrigerant is then said to be at high pressure.
    The high pressure refrigerant passes through the first two-fluid heat exchanger 5 and undergoes a loss of enthalpy due to its passage into the liquid phase and the transfer of enthalpy to the heat transfer fluid of the second heat transfer fluid loop B. The fluid high pressure refrigerant then loses enthalpy while remaining at a constant pressure.
    The high pressure refrigerant then passes through the first internal heat exchanger 19 where it loses enthalpy. This enthalpy is transferred to the low pressure refrigerant coming from the second heat exchanger 13 and from the second bypass pipe 40.
    The high pressure refrigerant then passes through the second internal heat exchanger 19 '.
    When the indirect reversible air conditioning circuit 1 is according to the second embodiment as illustrated in FIG. 11a, the high pressure refrigerant exchanges heat with the low pressure refrigerant coming from the second bypass pipe 40 because that its second connection point 42 is upstream of the second internal heat exchanger 19 ′ on the first bypass pipe 30.
    When the indirect reversible air conditioning circuit 1 is according to the third or fourth embodiment as illustrated in FIGS. 11b and 11c, the high-pressure refrigerant does not lose enthalpy because there is no circulation of refrigerant. in said second internal heat exchanger 19 'because the second connection point 42 of the second bypass pipe 40 is downstream of the second internal heat exchanger 19'.
    The first part of the refrigerant passes through the third expansion device 17. The high pressure refrigerant undergoes isenthalpic pressure loss and passes into a two-phase mixture state. The refrigerant is now said to be at low pressure. When the indirect reversible air conditioning circuit 1 is according to the fourth embodiment, the second stop valve 73 is open as illustrated in Figure 1 le.
    The low pressure refrigerant then passes into the second two-fluid heat exchanger 15 where it gains enthalpy by cooling the heat transfer fluid circulating in the secondary thermal management loop. The refrigerant returns to the gaseous state.
    According to the second embodiment illustrated in FIG. 11a, at the outlet of the second dual-fluid heat exchanger 15, the refrigerant joins the first bypass pipe 30 downstream of the first stop valve 33 and upstream of the second heat exchanger internal heat 19 '. According to the third and fourth embodiments, the refrigerant joins the first bypass pipe 30 downstream from the second internal heat exchanger 19 ’.
    The second part of the high pressure refrigerant passes through the first expansion device 7. The refrigerant undergoes a first isenthalpic pressure loss which causes it to pass into a state of two-phase mixing. The refrigerant is now at an intermediate pressure.
    The refrigerant then passes through the first heat exchanger 9 where it loses enthalpy by heating the indoor air flow 100.
    At the outlet of the first heat exchanger 9, the refrigerant is redirected to the second heat exchanger 13. For this, the first stop valve 33 of the first bypass pipe 30 is closed. Before arriving at the second heat exchanger 13, the refrigerant passes through the first expansion device 11 where it undergoes a second isenthalpic pressure loss. The refrigerant is now at low pressure.
    As illustrated in FIG. 1c, if a bypass line 70 is present, the refrigerant at intermediate pressure does not pass through said bypass line 70 because the third stop valve 74 is closed.
    The low pressure refrigerant then passes through the second heat exchanger 13 where it gains enthalpy by absorbing enthalpy from the outside air flow 200. The refrigerant thus returns to the gaseous state. At the outlet of the second heat exchanger 13, the refrigerant is joined by the refrigerant having passed through the second bypass pipe 40.
    The low pressure refrigerant then passes into the first internal heat exchanger 19 where it again gains enthalpy from the high pressure refrigerant passing through the first internal heat exchanger 19. The low pressure refrigerant then returns to compressor 3.
    In this parallel secondary heat pump mode, the first internal heat exchanger 19 as well as the second internal heat exchanger 19 ’are active in the second embodiment.
    For the third and fourth embodiments, only the first internal heat exchanger 19 is active. Because the enthalpy of the low pressure refrigerant entering the compressor 3 is greater, the enthalpy of the high pressure refrigerant leaving the compressor 3 will also be greater than the enthalpy of the refrigerant when it there is no internal heat exchanger.
    In addition, the addition of enthalpy to the low pressure refrigerant at the first internal heat exchanger 19 makes it possible to limit the proportion of refrigerant in the liquid phase before it enters the compressor 3, in particular when the air conditioning circuit 1 comprises a desiccant bottle 14 disposed downstream of the first two-fluid heat exchanger 5. The effect of the first internal heat exchanger 19 is limited because its length is between 50 and 120 mm. 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 the compressor 3 without as much to penalize the efficiency of the parallel secondary heat pump mode. Indeed, the purpose of this parallel secondary 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. This enthalpy comes, in this mode parallel secondary heat pump, of the external air flow 200 via the second heat exchanger 13, but also of the secondary thermal management loop via the second dual-fluid heat exchanger 15.
    At the second heat transfer fluid loop B, the heat transfer fluid gains enthalpy from the coolant at the first dual fluid heat exchanger 5.
    As illustrated in FIGS. 11a to 11c, 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 interior air flow 100. For this, the obstruction flap 310 is open and / 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 parallel secondary heat pump mode is useful for heating the indoor air flow 100 both at the first heat exchanger 9 and at the third heat exchanger 54 by absorbing enthalpy from the outdoor air flow 200 at level of the second heat exchanger 13, but also of the secondary thermal management loop at the level of the second dual-fluid heat exchanger 15.
    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 indoor air flow 100.
    Preferably, for this parallel secondary heat pump mode, the first part of the refrigerant passing through the second bypass pipe 40 has a greater mass flow than the second part of refrigerant passing through the first heat exchanger 9.
    Figure 12 shows a strict secondary heat pump mode in which:
    ° the refrigerant circulates in the compressor 3 where said refrigerant passes at high pressure and circulates successively in the first dual-fluid heat exchanger 5, the first internal heat exchanger 19, the second internal heat exchanger 19 ', the first expansion 7 where said refrigerant passes to an intermediate pressure, said refrigerant then circulates successively in the first heat exchanger 9, the first bypass pipe 30, the bypass pipe 70, the third expansion device 17 where said refrigerant passes at low pressure, the second dual-fluid heat exchanger 15, the refrigerant at low pressure then passes through the first internal heat exchanger 19 before returning to the compressor 3, ° the heat transfer fluid at the outlet of the first dual-fluid heat exchanger 5 circulates only in the third heat exchanger 54 from the first traffic line 50.
    The refrigerant at the inlet of compressor 3 is in the gas phase. The refrigerant undergoes compression while passing through the compressor 3. Said refrigerant is then said to be at high pressure.
    The high pressure refrigerant passes through the first two-fluid heat exchanger 5 and undergoes a loss of enthalpy due to its passage into the liquid phase and the transfer of enthalpy to the heat transfer fluid of the second heat transfer fluid loop B. The fluid high pressure refrigerant then loses enthalpy while remaining at a constant pressure.
    The high pressure refrigerant then passes through the first internal heat exchanger 19 where it loses enthalpy. This enthalpy is transferred to the low pressure refrigerant coming from the second bypass pipe 40.
    The high pressure refrigerant then passes into the second internal heat exchanger 19 'where it does not lose enthalpy because there is no circulation of refrigerant in said second internal heat exchanger 19' because the second connection point 42 of the second bypass pipe 40 is downstream of the second internal heat exchanger 19 '.
    The high pressure refrigerant passes through the first expansion device
    7. The refrigerant undergoes a first isenthalpic pressure loss which puts it in a state of two-phase mixing. The refrigerant is now at an intermediate pressure. The high-pressure refrigerant does not pass into the second bypass line 40 at the outlet of the second internal heat exchanger 19 ’because the second stop valve 73 is closed.
    The refrigerant then passes through the first heat exchanger 9 where it loses enthalpy by heating the indoor air flow 100.
    At the outlet of the first heat exchanger 9, the refrigerant at intermediate pressure is redirected to the bypass pipe 70. For this, the first stop valve 33 of the first bypass pipe 30 is closed, as well as the second device expansion valve 11. The third stop valve 74 is open.
    The refrigerant at intermediate pressure then passes into the third expansion device 17. The refrigerant then undergoes a second isenthalpic pressure loss. The refrigerant is now said to be at low pressure.
    The low pressure refrigerant then passes into the second two-fluid heat exchanger 15 where it gains enthalpy by cooling the heat transfer fluid circulating in the secondary thermal management loop. The refrigerant returns to the gaseous state.
    The low pressure refrigerant then passes into the first internal heat exchanger 19 where it again gains enthalpy from the high pressure refrigerant passing through the first internal heat exchanger 19. The low pressure refrigerant then returns to compressor 3.
    In this strict secondary heat pump mode, only the first internal heat exchanger 19 is active. Because the enthalpy of the low pressure refrigerant entering the compressor 3 is greater, the enthalpy of the high pressure refrigerant leaving the compressor 3 will also be greater than the enthalpy of the refrigerant when it there is no internal heat exchanger.
    In addition, the addition of enthalpy to the low pressure refrigerant at the first internal heat exchanger 19 makes it possible to limit the proportion of refrigerant in the liquid phase before it enters the compressor 3, in particular when the air conditioning circuit 1 comprises a desiccant bottle 14 disposed downstream of the first two-fluid heat exchanger 5. The effect of the first internal heat exchanger 19 is limited because its length is between 50 and 120 mm. 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 the compressor 3 without as much to penalize the efficiency of strict secondary heat pump mode. In fact, the purpose of this strict secondary 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. This enthalpy comes, in this mode strict secondary heat pump, from the secondary thermal management loop via the second two-fluid heat exchanger 15.
    At the second heat transfer fluid loop B, the heat transfer fluid gains enthalpy from the coolant at the first dual fluid heat exchanger 5.
    As illustrated in FIG. 12, the heat transfer fluid circulates in the first circulation line 50 and passes through the third heat exchanger 54. The heat transfer fluid loses enthalpy by heating the interior air flow 100. For this, the shutter obstruction 310 is open and / 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 strict secondary heat pump mode is useful for heating the indoor air flow 100 both at the first heat exchanger 9 and at the third heat exchanger 54 by absorbing enthalpy only from the secondary thermal management loop. at the second two-fluid heat exchanger 15.
    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 indoor air flow 100.
    Other operating modes such as defrosting, dehumidification or heating can also be envisaged with such an architecture of the indirect reversible air conditioning circuit 1.
    Thus, it is clear that by its architecture and the presence of two internal heat exchangers 19 and 19 ', the air conditioning circuit 1 allows operation in a cooling mode having improved refrigeration performance and COP and in a pump mode heat where its effectiveness is little reduced by the effect of an internal heat exchanger. In addition, the presence of the second bypass loop 40 makes it possible to cool elements such as batteries and / or electronic components present in the secondary thermal management loop both during different cooling modes, but also during pump mode. heat where the heat energy released by the secondary thermal management loop makes it possible to heat the interior air flow 100 and therefore participates in the heating of the passenger compartment.
    权利要求:
    Claims (12)
    [1" id="c-fr-0001]
    1. Indirect air conditioning circuit (1) for a motor vehicle 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 first dual-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 first bypass (30) of the second heat exchanger (13) comprising a first shut-off valve (33), • a second loop of heat transfer fluid (B) in which a heat transfer fluid circulates, and • the first two-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 exchanges of warmth r between the first refrigerant loop (A) and the second heat transfer fluid loop (B), • a first internal heat exchanger (19), allowing heat exchange between the high pressure refrigerant at the outlet of the first exchanger dual-fluid heat (5) and the low-pressure refrigerant leaving the second heat exchanger (13) or the first bypass line (30), • 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 circulating in the first bypass line (30), • a second bypass line (40) of the first expansion device (7) and the first heat exchanger (9), said second bypass pipe (40) comprising a third expansion device (17) disposed upstream of a second dual fluid heat exchanger (15) also arranged jointly on a secondary thermal management loop.
    [2" id="c-fr-0002]
    2. Indirect reversible air conditioning circuit (1) according to claim 1, characterized in that the second bypass pipe (40) is connected on the one hand upstream of the first expansion device (7) and on the other hand on the first bypass line (30), upstream of the first shut-off valve (33) and the second internal heat exchanger (19 ').
    [3" id="c-fr-0003]
    3. Indirect reversible air conditioning circuit (1) according to claim 1, characterized in that the second bypass pipe (40) is connected on the one hand upstream of the first expansion device (7) and on the other hand on the first bypass line (30), upstream of the second heat exchanger (19 ') and downstream of the first stop valve (33).
    [4" id="c-fr-0004]
    4. Indirect reversible air conditioning circuit (1) according to claim 1, characterized in that the second bypass pipe (40) is connected on the one hand upstream of the first expansion device (7) and on the other hand downstream the second expansion device (19 '), between said second expansion device (19') and the first internal heat exchanger (19).
    [5" id="c-fr-0005]
    5. Indirect reversible air conditioning circuit (1) according to the preceding claim, characterized in that the first coolant loop (A) comprises a bypass pipe (70) connected on the one hand to the first bypass pipe (30) , upstream of the stop valve (33) of the second heat exchanger (19 ') and on the other hand upstream of the third expansion device (17) between said third expansion device (17) and a second valve d stop (73), said bypass line (70) comprising a third stop valve (74).
    [6" id="c-fr-0006]
    6. Indirect reversible air conditioning circuit (1) according to one of the preceding claims, characterized in that the second heat transfer fluid loop (B) comprises:
    ° the first 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 internal air flow (100) in the motor vehicle, and connecting a first junction point (61) disposed downstream of the first two-fluid heat exchanger (5) and a second junction point (62) disposed upstream of said first two-fluid heat exchanger (5), ° a second circulation pipe (60) of heat transfer fluid comprising a fourth heat exchanger (64) intended to be traversed by an external air flow (200) to the motor vehicle, and connecting the first junction point (61) disposed downstream of the first heat exchanger dual fluid heat (5) and the second junction point (62) disposed upstream of said first dual fluid heat exchanger (5), and ° a pump (18) disposed downstream or upstream of the first dual fluid heat exchanger (5), in be the first junction point (61) and the second junction point (62).
    [7" id="c-fr-0007]
    7. A method of operating an indirect invertible air conditioning circuit (1) according to claim 6, according to a parallel secondary cooling mode in which:
    ° the refrigerant circulates in the compressor (3) where said refrigerant passes at high pressure and successively circulates in the first two-fluid heat exchanger (5), the first internal heat exchanger (19), the second internal heat exchanger ( 19 '):
    a first part of the refrigerant passes through the second bypass line (40), passes through the third expansion device (17) where said refrigerant passes at low pressure, said refrigerant at low pressure then circulates in the second heat exchanger dual fluid (15) before joining the low pressure refrigerant from the first heat exchanger (9) upstream of the first internal heat exchanger (19), a second part of the refrigerant passes through the first expansion device (7) where said refrigerant passes at low pressure, said refrigerant at low pressure then circulates successively in the first heat exchanger (9), the first bypass line (30) where it passes in the second internal heat exchanger (19 ') , and then in the first internal heat exchanger (19) before returning to the compressor (3), ° the heat transfer fluid leaving it e of the first two-fluid heat exchanger (5) circulates in the fourth heat exchanger (64) of the second circulation line (50).
    [8" id="c-fr-0008]
    8. A method of operating an indirect invertible air conditioning circuit (1) according to claim 6, according to a strict secondary cooling mode in which:
    ° the refrigerant circulates in the compressor (3) where said refrigerant passes at high pressure and successively circulates in the first two-fluid heat exchanger (5), the first internal heat exchanger (19), the second internal heat exchanger ( 19 '), the refrigerant then passes into the second bypass pipe (40), passes into the third expansion device (17) where said refrigerant passes at low pressure, said refrigerant at low pressure then circulates in the second exchanger of two-fluid heat (15), ° the heat transfer fluid at the outlet of the first two-fluid heat exchanger (5) circulates in the fourth heat exchanger (64) of the second circulation line (50).
    [9" id="c-fr-0009]
    9. A method of operating an indirect invertible air conditioning circuit (1) according to claim 6 in combination with one of claims 3 to 5, according to a parallel secondary heat pump mode in which:
    ° the refrigerant circulates in the compressor (3) where said refrigerant passes at high pressure and successively circulates in the first two-fluid heat exchanger (5), the first internal heat exchanger (19), the second internal heat exchanger ( 19 '):
    a first part of the refrigerant passes through the second bypass pipe (40) through the third expansion device (17) where the refrigerant passes at low pressure, the second dual-fluid heat exchanger (15) before joining the refrigerant from the second heat exchanger upstream of the first internal heat exchanger (19), a second part of the refrigerant passes through the first expansion device (7) where said refrigerant passes to an intermediate pressure, said refrigerant then circulates successively in the first heat exchanger (9), the second expansion device (ff) where said refrigerant passes at low pressure, the second heat exchanger (13), the refrigerant at low pressure then passes through the first internal heat exchanger (19) before returning to the compressor (3), ° the heat transfer fluid at the outlet of the first exchanger bifluid heat (5) circulates only in the third heat exchanger (54) of the first circulation line (50).
    5 10. Method for operating an indirect invertible air conditioning circuit (1) according to claim 6 in combination with claim 5, according to a strict secondary heat pump mode in which:
    ° the refrigerant circulates in the compressor (3) where said refrigerant passes at high pressure and circulates successively in the first exchanger
    [10" id="c-fr-0010]
    10 dual-fluid heat (5), the first internal heat exchanger (19), the second internal heat exchanger (19 '), the first expansion device (7) where said refrigerant passes to an intermediate pressure, said refrigerant then flows successively through the first heat exchanger (9), the first bypass pipe (30), the
    [11" id="c-fr-0011]
    15 bypass (70), the third expansion device (17) where said refrigerant passes at low pressure, the second dual-fluid heat exchanger (15), the refrigerant at low pressure then passes through the first internal heat exchanger (19) before returning to the compressor (3), ° the heat transfer fluid at the outlet of the first two-fluid heat exchanger (5)
    [12" id="c-fr-0012]
    20 circulates only in the third heat exchanger (54) of the first circulation line (50).
    1/21
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    同族专利:
    公开号 | 公开日
    EP3606774B1|2021-08-18|
    WO2018185412A1|2018-10-11|
    EP3606774A1|2020-02-12|
    CN110678340A|2020-01-10|
    FR3064946B1|2019-04-05|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US20040079102A1|2002-10-22|2004-04-29|Makoto Umebayashi|Vehicle air conditioner having compressi on gas heater|
    EP2517906A1|2011-04-27|2012-10-31|Valeo Systèmes Thermiques|Method for controlling the coolant temperature at the input of a compressor|
    DE112014003888T5|2013-08-23|2016-06-09|Sanden Holdings Corporation|Vehicle air conditioning|
    EP2933586A1|2014-04-16|2015-10-21|Valeo Systemes Thermiques|Refrigeration circuit|
    DE102016110957A1|2015-06-22|2016-12-22|Valeo Systemes Thermiques|Thermal management device|WO2021204914A1|2020-04-08|2021-10-14|Valeo Systemes Thermiques|Thermal conditioning system for a motor vehicle|
    WO2021204915A1|2020-04-08|2021-10-14|Valeo Systemes Thermiques|Thermal conditioning system for a motor vehicle|
    FR3092653B1|2019-02-13|2021-02-19|Valeo Systemes Thermiques|Thermal management device for an electric or hybrid motor vehicle|
    FR3092651B1|2019-02-13|2021-04-30|Valeo Systemes Thermiques|Thermal management device for an electric or hybrid motor vehicle|
    FR3092652B1|2019-02-13|2021-02-19|Valeo Systemes Thermiques|Thermal management device for an electric or hybrid motor vehicle|
    法律状态:
    2018-04-26| PLFP| Fee payment|Year of fee payment: 2 |
    2018-10-12| PLSC| Search report ready|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
    FR1752950A|FR3064946B1|2017-04-05|2017-04-05|INDIRECT INDIRECT AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE AND METHOD OF OPERATING THE SAME|
    FR1752950|2017-04-05|FR1752950A| FR3064946B1|2017-04-05|2017-04-05|INDIRECT INDIRECT AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE AND METHOD OF OPERATING THE SAME|
    CN201880035148.5A| CN110678340A|2017-04-05|2018-03-30|Indirect reversible air-conditioning circuit for a motor vehicle and corresponding operating method|
    PCT/FR2018/050806| WO2018185412A1|2017-04-05|2018-03-30|Indirect reversible air-conditioning circuit for a motor vehicle and corresponding operating method|
    EP18722667.5A| EP3606774B1|2017-04-05|2018-03-30|Indirect reversible air-conditioning circuit for a motor vehicle and corresponding operating method|
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