• 专利附录
  • 专利说明
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    • 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 exchanger 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 fluid loop coolant (B), and • a two-fluid heat exchanger (5) arranged jointly on the first refrigerant loop (A) downstream of the compressor (3), and on the second coolant loop (B), • a first internal heat exchanger (19), the first refrigerant loop (A) also having a second internal heat exchanger (19 ') allowing a heat exchange between the high pressure refrigerant at the outlet of the first heat exchanger; internal heat (19) and the low pressure coolant circulating in the bypass line (30).
    公开号:FR3055250A1
    申请号:FR1658035
    申请日:2016-08-30
    公开日:2018-03-02
    发明作者:Jugurtha BENOUALI
    申请人:Valeo Systemes Thermiques SAS；
    IPC主号:
    专利说明:

    055 250
    58035 ® FRENCH REPUBLIC
    NATIONAL INSTITUTE OF INDUSTRIAL PROPERTY © Publication number:
    (only to be used for reproduction orders) © National registration number
    COURBEVOIE © Int Cl 8 : B 60 H 1/00 (2017.01), B 60 H 1/32, F25 B 29/00, 47/02, 49/02
    A1 PATENT APPLICATION
    ©) Date of filing: 30.08.16. © Applicant (s): VALEO THERMAL SYSTEMS (© Priority: Simplified joint stock company - FR. @ Inventor (s): BENOUALI JUGURTHA. ®) Date of public availability of the request: 02.03.18 Bulletin 18/09. ©) 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 OF MOTOR VEHICLE AND CORRESPONDING OPERATING METHOD.
    FR 3,055,250 - A1 (tv) The present invention relates to an indirect air conditioning circuit (1) for a motor vehicle comprising:
    a first coolant loop (A) comprising:
    O a compressor (3),
    O a first expansion device (7),
    O a first heat exchanger (9),
    O a second expansion device (11),
    O a second heat exchanger (13), and O a bypass line (30) of the second heat exchanger (13), a second loop of heat transfer fluid (B), and a two-fluid heat exchanger (5) arranged jointly on the first coolant loop (A) downstream of the compressor (3), and on the second coolant loop (B), a first internal heat exchanger (19), the first coolant loop (A) also comprising 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 bypass line (30).

    Indirect reversible air conditioning circuit of a motor vehicle and corresponding operating method
    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, 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 different 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 according to different operating modes but struggles to provide an operating mode whose performance is satisfactory both in an operating mode for cooling the air flow inside the vehicle and in a heat pump mode. in order to heat said air flow inside the vehicle.
    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.
    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 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 crossed by a flow of air 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, • a two-fluid heat exchanger arranged jointly on the first loop of coolant downstream of the compressor, between said compressor and the first expansion device, and on the second loop of coolant, so as to allow heat exchanges between the first loop of coolant and the second loop of coolant, and • a first internal heat exchanger, allowing heat exchange between the high-pressure refrigerant at the outlet of the exchange bifluid heat ur and the low pressure refrigerant leaving the second heat exchanger or the bypass line, the first refrigerant loop also comprising a second internal heat exchanger allowing heat exchange between the high refrigerant pressure at the outlet of the first internal heat exchanger and the low pressure refrigerant circulating in the bypass line.
    According to one aspect of the invention, the indirect reversible air conditioning circuit comprises a device for redirecting the refrigerant coming from the first heat exchanger to the second heat exchanger or to the bypass pipe.
    According to another aspect of the invention, at least one of the first or second internal heat exchangers can be a coaxial heat exchanger.
    According to another aspect of the invention, the first coaxial internal heat exchanger has a length between 50 and 120mm and the second coaxial internal heat exchanger has a length between 200 and 700mm.
    According to another aspect of the invention, the first expansion device is an electronic expansion valve controllable by a control unit integrated into the vehicle and the second expansion device is a thermostatic expansion valve.
    According to another aspect of the invention, the second expansion device is a thermostatic expansion valve incorporating a stop function.
    According to another aspect of the invention, the second heat transfer fluid loop comprises:
    ° the 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 'two-fluid heat exchanger and a second junction point arranged upstream of said two-fluid heat exchanger, ° a second coolant circulation pipe comprising a fourth heat exchanger intended to be traversed by a flow of air outside the motor vehicle, and connecting the first junction point arranged downstream of the two-fluid heat exchanger and the second junction point arranged upstream of said two-fluid heat exchanger, and ° a pump arranged downstream or upstream of the two-fluid heat exchanger, between the first junction point and the second junction point.
    According to another aspect of the invention, the first heat transfer fluid loop comprises an electric element heating the heat transfer fluid disposed, in the direction of circulation of the heat transfer fluid, downstream of the two-fluid heat exchanger, between said two-fluid heat exchanger and the first junction point.
    According to another aspect of the invention, the indirect reversible air conditioning circuit comprises a device for redirecting the heat transfer fluid coming from the dual-fluid heat exchanger towards the first circulation line and / or towards the second circulation line.
    According to another aspect of the invention, the indirect reversible air conditioning circuit comprises a shutter for obstructing the interior air flow passing through the third heat exchanger.
    The present invention also relates to a method of operating an indirect reversible air conditioning circuit according to a cooling mode in which:
    ° the refrigerant circulates in the compressor where said refrigerant passes at high pressure and successively circulates in the dual fluid heat exchanger, the first internal heat exchanger, the second internal heat exchanger, and the first expansion device where said fluid refrigerant passes at low pressure, said low pressure refrigerant then circulates successively in the first heat exchanger, the bypass branch where it passes in the second internal heat exchanger, and then in the first internal heat exchanger before returning to the compressor, ° the heat transfer fluid leaving the dual-fluid heat exchanger circulates in the fourth heat exchanger of the second circulation pipe.
    The present invention also relates to a method of operating an indirect reversible air conditioning circuit according to a dehumidification mode in which:
    ° the refrigerant circulates in the compressor where said refrigerant passes at high pressure and successively circulates in the dual fluid heat exchanger, the first internal heat exchanger, the second internal heat exchanger, and the first expansion device where said fluid refrigerant passes at low pressure, said low pressure refrigerant then circulates successively in the first heat exchanger, the second expansion device, the second heat exchanger and then in the first internal heat exchanger before returning to the compressor, ° a portion of the heat transfer fluid at the outlet of the dual-fluid heat exchanger circulates in the third heat exchanger of the first circulation line and another portion of the heat transfer fluid at the outlet of the dual-fluid heat exchanger circulates in the fourth heat exchanger the second traffic line.
    The present invention also relates to a method of operating an indirect reversible air conditioning circuit according to a heat pump mode in which:
    ° the refrigerant circulates in the compressor where said refrigerant passes at high pressure and successively circulates in the dual fluid heat exchanger, the first internal heat exchanger, the second internal heat exchanger, and the first expansion device where said fluid refrigerant passes to an intermediate pressure, said refrigerant then circulates successively in the first heat exchanger, the second expansion device where said refrigerant passes at low pressure, the second heat exchanger and then in the first internal heat exchanger before return to the compressor, ° the heat transfer fluid leaving the dual-fluid heat exchanger circulates only in the 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 first defrosting mode in which only the first loop of refrigerant is in operation, the refrigerant circulating successively in the compressor, the heat exchanger dual fluid, the first internal heat exchanger, the second internal heat exchanger, the first expansion device without undergoing pressure loss, the first heat exchanger, the second expansion device without undergoing pressure loss, the second heat exchanger heat and then into the first internal heat exchanger before returning to the compressor.
    The present invention also relates to a method of operating an indirect reversible air conditioning circuit according to a second defrosting mode in which only the second loop of heat transfer fluid is in operation, and in which the heat transfer fluid passes successively through:
    ° the pump, ° the heat exchanger, without exchanging enthalpy with the refrigerant of the first loop of refrigerant because the latter does not work, ° the electric heating element which is in operation, and then where :
    ° a portion of the heat transfer fluid circulating in the first circulation pipe and passing through the third heat exchanger and where the obstruction flap is closed, ° another portion of the heat transfer fluid circulates in the second circulation pipe and passes through the fourth heat exchanger heat.
    The present invention also relates to a method of operating an indirect reversible air conditioning circuit according to a third defrosting mode in which only the second loop of heat transfer fluid is in operation, and in which the heat transfer fluid passes successively through:
    ° the pump, ° the heat exchanger, without exchanging enthalpy with the refrigerant of the first loop of refrigerant because the latter does not work, ° the electric heating element which is in operation, all the fluid refrigerant then passing through the second circulation line and passing through the fourth heat exchanger.
    The present invention also relates to a method of operating an indirect reversible air conditioning circuit according to an electric heating mode in which only the second loop of heat transfer fluid is in operation and in which the heat transfer fluid passes successively through:
    ° the pump, ° the heat exchanger, without exchanging enthalpy with the coolant of the first coolant loop because the latter does not work, ° the electric heating element which is in operation, the heat transfer fluid then circulating only in the first circulation pipe and passing through the third heat exchanger.
    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 the appended drawings among which:
    Figure 1 shows a schematic representation of an indirect reversible air conditioning circuit, Figure 2 shows a schematic representation of expansion devices according to an alternative embodiment, Figure 3 shows a schematic representation of the second heat transfer fluid loop of the circuit of reversible indirect air conditioning in Figure 1, according to an alternative embodiment, Figure 4a shows the indirect reversible air conditioning circuit of Figure 1 in a cooling mode, Figure 4b shows a pressure / enthalpy diagram of the cooling mode illustrated in FIG. 4a, FIG. 5a shows the indirect reversible air conditioning circuit of FIG. 1 according to a dehumidification mode, FIG. 5b shows a pressure / enthalpy diagram of the dehumidification mode illustrated in FIG. 5a, FIG. 6a shows the circuit of indirect reversible air conditioning in Figure 1 in a heat pump mode, Figure 6b shows e a pressure / enthalpy diagram of the heat pump mode illustrated in FIG. 6a, FIG. 7 shows the first loop of refrigerant in FIG. 1 according to a first defrosting mode, FIGS. 8 and 9 show the second loops of heat transfer fluid Figures 1 and 3 respectively according to a second defrosting mode, Figure 10 shows a schematic representation of the second heat transfer fluid loop of the indirect reversible air conditioning circuit of Figure 1, according to an electric heating mode.
    In the different 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 that are similar 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 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 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 bypass line 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 Figure 1, the first connection point 31 is disposed between the first heat exchanger 9 and the second expansion device
    11. It is however entirely 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 device. trigger 11 or to cross 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.
    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 dual-fluid heat exchanger 5 and the fluid low pressure refrigerant at the outlet of the second heat exchanger 13 or the bypass pipe 30. This first IHX 19 notably has an inlet and an outlet for low pressure refrigerant coming from the second connection point 32, as well as a high pressure refrigerant inlet and outlet from the dual 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 pressure loss due to one of the first 7 or second 11 devices of relaxation. By low pressure refrigerant means by that a refrigerant having suffered a pressure loss due to one of the first 7 or second 11 expansion devices.
    The first refrigerant loop A also includes a second IHX 19 'allowing a heat exchange between the high pressure refrigerant leaving the first IHX 19 and the low pressure refrigerant circulating in the bypass line 30. This second IHX 19 ′ comprises 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 the first IHX 19.
    At least one of the first 19 or second 19 ′ IHX 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 IHX 19 can be a coaxial IHX with a length between 50 and 120mm while the second IHX 19 'can be a coaxial IHX with a length between 200 and 700mm.
    The first refrigerant loop A can also include 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 IHX 19. Such a desiccant bottle disposed on the upper side pressure of the air conditioning circuit, i.e. downstream of the compressor 3 and upstream of an expansion device, has a smaller footprint as well as a reduced cost compared to other phase separation solutions such as an accumulator which would be arranged 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 IHX 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, is meant here mechanical or electromechanical elements which can be controlled by an electronic control unit on board the motor vehicle.
    The first 7 and second 11 expansion devices can be electronic expansion valves, that is to say the pressure of the refrigerant fluid at the outlet is controlled by a solenoid valve whose open position determines the pressure of the fluid at the outlet. Such an electronic expansion valve is in particular capable of allowing the coolant to pass without loss of pressure when said solenoid valve 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. 2. 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 second heat transfer fluid loop B can 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 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 and 2, said device for redirection of the heat-transfer fluid coming from the dual-fluid heat exchanger 5 can in particular comprise a third 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 loop of heat transfer fluid B and thus makes it possible to limit the production costs.
    According to an alternative embodiment illustrated in FIG. 3, the device for redirection of the heat-transfer fluid coming from the dual-fluid heat exchanger 5 can in particular comprise • a third 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 fourth 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 electrical heating element 55 is notably arranged, in the direction of circulation of the heat-transfer fluid, downstream of the dual-fluid heat exchanger 5, between said dual-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. 4a to 9. In FIGS. 4a, 5a, 6a, 7, 8 and 9, only the elements in which the fluid refrigerant and / or the coolant circulating are shown. The direction of circulation of the coolant and / or the coolant is represented by arrows.
    FIG. 4a shows a cooling mode in which:
    • the refrigerant circulates in the compressor 3 where said refrigerant passes at high pressure and circulates successively in the two-fluid heat exchanger 5, the first IHX 19, the second IHX 19 ', and the first expansion device 7 where said fluid refrigerant passes at low pressure, said low pressure refrigerant then flows successively through the first heat exchanger 9, the bypass branch 30 where it passes into the second IHX 19 ', and then into the first IHX 19 before returning to the compressor 3, • the heat transfer fluid at the outlet of the dual-fluid heat exchanger 5 circulates in the fourth heat exchanger 64 of the second circulation pipe 60.
    As illustrated by FIG. 4a, a portion of the heat transfer fluid at the outlet of the dual-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 exchanger 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 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 on the pressure / enthalpy diagram in FIG. 4b. 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 arrow 300, passing through the compressor 3. Said refrigerant is then said to be at high pressure.
    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 into the first IHX 19 where it loses enthalpy, as illustrated by arrow 190a. This enthalpy is transferred to the refrigerant at low pressure as illustrated by the arrow 190b.
    The high pressure refrigerant then passes into the second IHX 19 'where it again loses enthalpy, as illustrated by the arrow 190'a. This enthalpy is transferred to the refrigerant at low pressure as illustrated by the arrow 190'b.
    The high pressure refrigerant then passes through the first expansion device 7. The high pressure 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. 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 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 refrigerant is redirected to the bypass pipe 30.
    The low pressure refrigerant then passes into the second IHX 19 'where it gains enthalpy, as illustrated by the arrow 190'b from the high pressure refrigerant passing through the second IHX 19'.
    The low pressure refrigerant then passes into the first IHX 19 where it again gains enthalpy, as illustrated by the arrow 190b coming from the high pressure refrigerant passing through the first IHX 19. The low pressure refrigerant then returns to compressor 3.
    This cooling mode is useful for cooling the interior 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 refrigerant leaving the first heat exchanger 9 does not circulate in the second heat exchanger 13 and passes into the bypass line 30.
    The non-return valve 23 makes it possible to prevent the coolant leaving the bypass pipe 30 from flowing back to the second heat exchanger 13.
    In this cooling mode, the two IHX 19 and 19 'are active and their effects add up. The use of IHX 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 outlet of the heat exchanger dual fluid heat 5 is cooled by the refrigerant in 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 both an increase the cooling power 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 level of the first 19 and second 19 'IHX 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 two-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. 4a, 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 blocked 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 third 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. 3, the first circulation pipe 50 with the fourth stop valve 53 and to close it so as to prevent the coolant from flowing in said first circulation pipe 50.
    FIG. 5a shows a dehumidification mode in which:
    • the refrigerant circulates in the compressor 3 where said refrigerant passes at high pressure and circulates successively in the two-fluid heat exchanger 5, the first IHX 19, the second IHX 19 ', and the first expansion device 7 where said fluid refrigerant passes at low pressure, said low pressure refrigerant then flows successively in the first heat exchanger 9, the second expansion device 11, the second heat exchanger 13 and then in the first IHX 19 before returning to the compressor
    3, • a portion of the heat transfer fluid at the outlet of the 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 two-fluid heat exchanger 5 circulates in the fourth heat exchanger 64 of the second circulation pipe 50, the obstruction flap 310 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 during this dehumidification mode are illustrated on the pressure / enthalpy diagram in FIG. 5b. 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 arrow 300, passing through the compressor 3. Said refrigerant is then said to be at high pressure.
    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 into the first IHX 19 where it loses enthalpy, as illustrated by arrow 190a. This enthalpy is transferred to the refrigerant at low pressure as illustrated by the arrow 190b.
    The high pressure refrigerant then passes into the second IHX 19 'where it does not lose enthalpy because there is no circulation of low pressure refrigerant in said second IHX 19'.
    The high pressure 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 liquid mixture state more gas. The refrigerant is now said to be at low pressure.
    The low pressure refrigerant then passes through the first heat exchanger 9 where it gains enthalpy as illustrated by the arrow 900 by cooling the interior air flow 100.
    At the outlet of the first heat exchanger 9, the low pressure refrigerant is redirected to the second heat exchanger 13. Before arriving at the second heat exchanger 13, the low pressure refrigerant passes through the first expansion device 11 without suffering pressure loss or bypasses it.
    The low pressure refrigerant then passes through the second heat exchanger 13 where it continues to gain enthalpy, as illustrated by arrow 130, by absorbing enthalpy from the flow of outside air 200. The refrigerant thus joins the saturation curve X and returns to the gaseous state.
    The low pressure refrigerant then passes into the first IHX 19 where it again gains enthalpy, as illustrated by the arrow 190b, coming from the high pressure refrigerant passing through the first IHX 19. The low pressure refrigerant returns then to compressor 3.
    In this dehumidification mode, the coolant redirection device is configured so that the coolant 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 coolant leaving the first heat exchanger 9 does not circulate in the bypass line 30 and passes into the second heat exchanger 13.
    In this dehumidification mode, only the first IHX 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 IHX.
    In addition, the addition of enthalpy to the low-pressure refrigerant at the level of the first IHX 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 15 disposed downstream of the two-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. 5a, 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 loses enthalpy by heating the internal air flow 100. For this, the obstruction flap 310 is open or the fourth stop valve 53 is open.
    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 third stop valve 63 is open to allow the passage of the heat transfer fluid.
    This dehumidification mode is useful for dehumidifying the interior air flow 100 by subjecting it to cooling at the first heat exchanger 9 and by reheating it at the third heat exchanger 54.
    FIG. 6a shows a heat pump mode in which:
    • the refrigerant circulates in the compressor 3 where said refrigerant passes at high pressure and circulates successively in the two-fluid heat exchanger 5, the first IHX 19, the second IHX 19 ', and the first expansion device 7 where said fluid refrigerant passes to an intermediate pressure, said low pressure refrigerant then successively circulates 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 IHX 19 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 line 50, • the obstruction flap 310 is open from so as to allow the interior air flow 100 to circulate in the third heat exchanger 54.
    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 pressure and enthalpy variations undergone by the refrigerant during this heat pump mode are illustrated in the pressure / enthalpy diagram in FIG. 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 arrow 300, passing through the compressor 3. Said refrigerant is then said to be at high pressure.
    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 into the first IHX 19 where it loses enthalpy, as illustrated by arrow 190a. This enthalpy is transferred to the refrigerant at low pressure as illustrated by the arrow 190b.
    The high pressure refrigerant then passes into the second IHX 19 'where it does not lose enthalpy because there is no circulation of low pressure refrigerant in said second IHX 19'.
    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. The refrigerant is now at an intermediate pressure.
    The refrigerant then passes through the first heat exchanger 9 where it loses 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 is redirected to the second heat exchanger 13. Before arriving at the second heat exchanger 13, the refrigerant passes into the first expansion device 11 where it undergoes a second isenthalpic pressure loss. The refrigerant is now at low pressure.
    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 refrigerant thus joins the curve of saturation X and returns to the gaseous state.
    The low pressure refrigerant then passes into the first IHX 19 where it again gains enthalpy, as illustrated by the arrow 190b, coming from the high pressure refrigerant passing through the first IHX 19. The low pressure refrigerant returns then to compressor 3.
    In this heat pump mode, the coolant redirection device is configured so that the coolant 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 coolant leaving the first heat exchanger 9 does not circulate in the bypass line 30 and passes into the second expansion device 11 and the second heat exchanger 13.
    In this heat pump mode, only the first IHX 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 IHX.
    In addition, the addition of enthalpy to the low pressure refrigerant at the first IHX 19 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 includes a bottle. desiccant 15 disposed downstream of the two-fluid heat exchanger 5. The effect of the first IHX 19 is limited because its length is between 50 and 120mm. This size limits the heat exchange between the high pressure refrigerant and the low pressure refrigerant so that the exchanged enthalpy limits the proportion of refrigerant in liquid phase before entering the compressor 3 without as much to penalize the efficiency of 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 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, 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 and / or the fourth stop valve 53 is open. The third 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.
    FIG. 7 shows a first defrosting mode in which only the first loop of refrigerant A is in operation.
    In this first defrosting mode, the refrigerant circulates in the compressor 3 and successively circulates in the dual-fluid heat exchanger 5, the first IHX 19, the second IHX 19 ', the first expansion device 7, the first heat exchanger 9, the second expansion device 11, the second heat exchanger 13 and then in the first IHX 19 before returning to the compressor 3.
    This first defrosting mode is useful for supplying hot coolant to the second heat exchanger 13 in order to avoid the formation of frost at its level.
    In this first defrosting mode, the first expansion device 7 allows the refrigerant to pass without it undergoing a pressure loss or is bypassed. The refrigerant passes through the first heat exchanger 9 while losing little or no enthalpy, for example due to a stoppage of the interior air flow 100.
    The refrigerant then passes through the second expansion device 11 where it does not undergo pressure loss or bypasses it. The refrigerant then passes through the second heat exchanger 13 where it releases its enthalpy in order to avoid the formation of frost.
    In this first defrosting mode, the coolant redirection device is configured so that the coolant 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 coolant leaving the first heat exchanger 9 does not circulate in the bypass line 30 and passes into the second heat exchanger 13.
    Figures 8 and 9 show a second and a third defrosting mode where only the second heat transfer fluid loop B is in operation.
    In the second defrosting mode, illustrated in FIG. 8, the heat transfer fluid propelled by the pump 17 passes through the heat exchanger 5 but does not exchange enthalpy with the coolant of the first coolant loop A of the the latter does not work, for example by stopping compressor 3.
    The heat transfer fluid then passes through the electric heating element 55 which is in operation and heats said heat transfer fluid.
    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 internal 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 and allows to heat the second heat exchanger 13 in order to avoid the formation of frost on the latter. The third stop valve 63 is open to allow the passage of the heat transfer fluid.
    The third defrosting mode illustrated in FIG. 9 is similar to the second defrosting mode of FIG. 8, with the difference that the heat transfer fluid does not circulate in the first circulation line 50 due to the presence and the closing of the fourth stop valve 53. All the refrigerant therefore passes through the second circulation line 60 and passes through the fourth heat exchanger 64.
    Figure 10 shows an electric heating mode where only the second heat transfer fluid loop B is in operation.
    In this second mode of electric heating, the heat transfer fluid propelled by the pump 17 passes through the heat exchanger 5 but does not exchange enthalpy with the coolant of the first coolant loop A because the latter does not not working, for example by stopping compressor 3.
    The heat transfer fluid then passes through the electric heating element 55 which is in operation and heats said heat transfer fluid.
    The heat transfer fluid circulates only in the first circulation line 50 and passes through the third heat exchanger 54. The heat transfer fluid loses heat by transmitting it to the interior air flow 100. In order for the interior air flow 100 to pass through the third heat exchanger 54, the shutter 310 is open and / or the fourth stop valve 53 is open.
    The heat transfer fluid does not circulate in the second circulation line 60 because the third stop valve 63 is closed.
    Thus, we can see that due to its architecture and the presence of two IHX 19 and
    19 ′, the air conditioning circuit 1 allows operation in a cooling mode having improved cooling performance and COP and in a heat pump mode where its efficiency is little reduced by the effect of an IHX.
    权利要求:
    Claims (17)
    [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 expansion device (7), ° a first heat exchanger (9) being intended to be traversed by an internal air flow (100) in the motor vehicle, ° a second expansion (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 heat transfer fluid loop (B) in which a heat transfer fluid circulates, and • a two-fluid heat exchanger (5) 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 heat transfer fluid loop (B), so as to allow heat exchanges between the first refrigerant fluid loop (A) and the second fluid loop coolant (B), • a first internal heat exchanger (19), allowing a heat exchange between the high pressure refrigerant leaving the dual-fluid heat exchanger (5) and the low pressure refrigerant leaving the second heat exchanger (13) or the bypass line (30), characterized in that 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 fluid low pressure refrigerant circulating in the bypass line (30).
    [2" id="c-fr-0002]
    2. Indirect reversible air conditioning circuit (1) according to the preceding claim, characterized in that it comprises a device for redirecting the coolant coming from the first heat exchanger (9) to the second heat exchanger (13) or to the bypass line (30).
    [3" id="c-fr-0003]
    3. Indirect reversible air conditioning circuit (1) according to one of the preceding claims, characterized in that at least one of the first (19) or second (19 ') internal heat exchangers can be a coaxial heat exchanger.
    [4" id="c-fr-0004]
    4. Indirect reversible air conditioning circuit (1) according to the preceding claim, characterized in that the first internal coaxial heat exchanger (19) has a length of between 50 and 120mm and the second internal coaxial heat exchanger (19 ') has a length between 200 and 700mm.
    [5" id="c-fr-0005]
    5. Indirect reversible air conditioning circuit (1) according to one of the preceding claims, characterized in that the first expansion device (7) is an electronic expansion valve controllable by a control unit integrated into the vehicle and that the second expansion device (11) is a thermostatic expansion valve.
    [6" id="c-fr-0006]
    6. Indirect reversible air conditioning circuit (1) according to one of the preceding claims, characterized in that the second expansion device (11) is a thermostatic expansion valve incorporating a stop function.
    [7" id="c-fr-0007]
    7. 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 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 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 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 exchanger dual fluid heat (5) and the second junction point (62) disposed upstream of said dual fluid heat exchanger (5), and ° a pump (17) disposed downstream or upstream of the dual fluid heat exchanger (5) , between the first junction point (61) and the second junction point (62).
    [8" id="c-fr-0008]
    8. Indirect reversible air conditioning circuit (1) according to the preceding claim characterized in that the first loop of heat transfer fluid (B) comprises an electric heating element (55) of the heat transfer fluid disposed, 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).
    [9" id="c-fr-0009]
    9. Indirect reversible air conditioning circuit (1) according to one of claims 7 or 8, characterized in that it comprises a device for redirection of the heat transfer fluid coming from the two-fluid heat exchanger (5) towards the first pipe. circulation (50) and / or to the second circulation line (60).
    [10" id="c-fr-0010]
    10. Indirect reversible air conditioning circuit (1) according to one of claims 7 to
    9, characterized in that it comprises an obstruction flap (310) of the internal air flow (100) passing through the third heat exchanger (54).
    [11" id="c-fr-0011]
    11. Method for operating an indirect invertible air conditioning circuit (1) according to one of claims 7 to 10, according to a cooling mode in which:
    ° the refrigerant circulates in the compressor (3) where said refrigerant passes at high pressure and circulates successively in the dual-fluid heat exchanger (5), the first internal heat exchanger (19), the second internal heat exchanger ( 19 '), and 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 bypass branch (30) where it passes into the second internal heat exchanger (19 '), and then into the first internal heat exchanger (19) before returning to the compressor (3), ° the heat transfer fluid at the outlet of the dual-fluid heat exchanger (5) circulates in the fourth heat exchanger (64) of the second circulation line (50).
    [12" id="c-fr-0012]
    12. Method for operating an indirect invertible air conditioning circuit (1) according to one of claims 7 to 10, according to a dehumidification mode in which:
    ° the refrigerant circulates in the compressor (3) where said refrigerant passes at high pressure and circulates successively in the dual-fluid heat exchanger (5), the first internal heat exchanger (19), the second internal heat exchanger ( 19 ′), and the first expansion device (7) where said refrigerant passes at low pressure, said low pressure refrigerant then flows successively through the first heat exchanger (9), the second expansion device (11), the second heat exchanger (13) and then in the first internal heat exchanger (19) before returning to the compressor (3), ° a portion of the heat transfer fluid at the outlet of the dual-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 dual-fluid heat exchanger (5) circulates in the fourth heat exchanger (64) of the second pipe traffic flow (50).
    [13" id="c-fr-0013]
    13. Method for operating an indirect invertible air conditioning circuit (1) according to one of claims 7 to 10, according to a heat pump mode in which:
    ° the refrigerant circulates in the compressor (3) where said refrigerant passes at high pressure and circulates successively in the dual-fluid heat exchanger (5), the first internal heat exchanger (19), the second internal heat exchanger ( 19 '), and 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 fluid 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 dual-fluid heat exchanger (5 ) circulates only in the third heat exchanger (54) of the first circulation line (50).
    [14" id="c-fr-0014]
    14. A method of operating an indirect reversible air conditioning circuit (1) according to one of claims 1 to 10, according to a first defrosting mode in which only the first loop of refrigerant (A) is in operation, the fluid refrigerant flowing successively in the compressor (3), the two-fluid heat exchanger (5), the first internal heat exchanger (19), the second internal heat exchanger (19 '), the first expansion device (7) without undergo pressure loss, the first heat exchanger (9), the second expansion device (11) without undergoing pressure loss, the second heat exchanger (13) and then into the first internal heat exchanger (19) before returning to the compressor (3).
    [15" id="c-fr-0015]
    15. A method of operating an indirect reversible air conditioning circuit (1) according to claim 10, according to a second defrosting mode in which only the second loop of heat transfer fluid (B) is in operation, and in which the heat transfer fluid passes. successively in:
    ° the pump (17), ° the heat exchanger (5), without exchanging enthalpy with the coolant of the first coolant loop (A) because the latter does not work, ° the electrical element heater (55) which is in operation, and then where:
    ° a portion of the heat transfer fluid circulating in the first circulation pipe (50) and passing through the third heat exchanger (54) and where the obstruction flap (310) is closed, ° another portion of the heat transfer fluid circulates in the second circulation line (60) and passes through the fourth heat exchanger (64).
    [16" id="c-fr-0016]
    16. A method of operating an indirect reversible air conditioning circuit (1) according to one of claims 7 to 10, according to a third defrosting mode in which only the second loop of heat transfer fluid (B) is in operation, and in which the heat transfer fluid passes successively through:
    ° the pump (17), ° the heat exchanger (5), without exchanging enthalpy with the coolant of the first coolant loop (A) because the latter does not work, ° the electrical element heater (55) which is in operation, all the coolant then passing through the second circulation line (60) and passing through the fourth heat exchanger (64).
    [17" id="c-fr-0017]
    17. A method of operating an indirect reversible air conditioning circuit (1) according to one of claims 7 to 10, according to an electric heating mode where only the second loop of heat transfer fluid (B) is in operation and in which the heat transfer fluid passes successively through:
    ° the pump (17), ° the heat exchanger (5), without exchanging enthalpy with the coolant of the first coolant loop (A) because the latter does not work, ° the electrical element heater (55) which is in operation, the heat transfer fluid then circulating only in the first circulation line (50) and passing through the third heat exchanger (54).
    1/7
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    同族专利:
    公开号 | 公开日
    EP3496964B1|2020-07-08|
    EP3496964A1|2019-06-19|
    CN110114234A|2019-08-09|
    FR3055250B1|2018-08-10|
    WO2018042091A1|2018-03-08|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    FR3028016A1|2014-10-30|2016-05-06|Valeo Systemes Thermiques|THERMAL MANAGEMENT DEVICE FOR A MOTOR VEHICLE|WO2019243727A1|2018-06-18|2019-12-26|Valeo Systemes Thermiques|Heat treatment system for a vehicle|
    WO2021123544A1|2019-12-18|2021-06-24|Valeo Systemes Thermiques|Method for defrosting a thermal regulation circuit for a vehicle, in particular for a motor vehicle|JP2003252019A|2002-03-06|2003-09-09|Sanden Corp|Vehicular air conditioner|
    US8517087B2|2007-02-20|2013-08-27|Bergstrom, Inc.|Combined heating and air conditioning system for vehicles|
    FR2983284A1|2011-11-30|2013-05-31|Valeo Systemes Thermiques|CIRCUIT COMPRISING AN INTERNAL EXCHANGER HAVING A BRANCH FITTED BY A REFRIGERANT FLUID ACCORDING TO TWO OPPOSITE Senses|
    FR2984471B1|2011-12-15|2013-11-29|Valeo Systemes Thermiques|DEVICE FOR THERMALLY CONDITIONING A TRACTION CHAIN AND A VEHICLE HABITACLE|
    FR3020130B1|2014-04-16|2019-03-22|Valeo Systemes Thermiques|FRIGORIGENE FLUID CIRCUIT|EP3756916A1|2019-06-24|2020-12-30|Konvekta Aktiengesellschaft|Heating and/or air conditioning system with internal heat exchangers|
    法律状态:
    2017-08-31| PLFP| Fee payment|Year of fee payment: 2 |
    2018-03-02| PLSC| Publication of the preliminary search report|Effective date: 20180302 |
    2018-08-30| PLFP| Fee payment|Year of fee payment: 3 |
    2019-08-30| PLFP| Fee payment|Year of fee payment: 4 |
    2020-08-31| PLFP| Fee payment|Year of fee payment: 5 |
    2021-08-31| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1658035A|FR3055250B1|2016-08-30|2016-08-30|INDIRECT INDIRECT AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE AND METHOD OF OPERATING THE SAME|
    FR1658035|2016-08-30|FR1658035A| FR3055250B1|2016-08-30|2016-08-30|INDIRECT INDIRECT AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE AND METHOD OF OPERATING THE SAME|
    EP17754742.9A| EP3496964B1|2016-08-30|2017-07-21|Indirect reversible air-conditioning circuit for a motor vehicle and corresponding operating method|
    PCT/FR2017/052016| WO2018042091A1|2016-08-30|2017-07-21|Indirect reversible air-conditioning circuit for a motor vehicle and corresponding operating method|
    CN201780062940.5A| CN110114234A|2016-08-30|2017-07-21|Indirect reversible air conditioner loop and corresponding operation method for motor vehicles|
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