• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The present invention relates to an indirect reversible air conditioning circuit (1) for a motor vehicle comprising: a first refrigerant fluid loop (A) in which a refrigerant circulates; a second heat transfer fluid (Ω) loop in which a fluid circulates; coolant, and • a two-fluid heat exchanger (13) arranged jointly on the first refrigerant loop (A) and the second heat transfer fluid loop (Ω), so as to allow the exchange of heat between the first refrigerant loop (A) and the second coolant loop (Ω), at least one of the first refrigerant loop (A) and the second coolant loop (Ω) of the reversible air conditioning circuit (1) having a bypass branch (D). , D ') of the two-fluid heat exchanger (13).
    公开号:FR3052236A1
    申请号:FR1655176
    申请日:2016-06-07
    公开日:2017-12-08
    发明作者:Mohamed Yahia；Laetitia Clemaron
    申请人:Valeo Systemes Thermiques SAS；
    IPC主号:
    专利说明:

    The invention relates to the field of motor vehicles and more particularly to a motor vehicle air conditioning circuit and its method of operation.
    Today's motor vehicles are increasingly equipped with an air conditioning system. Generally, in a "conventional" air conditioning circuit, a refrigerant fluid passes successively in 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 and a second heat exchanger, called evaporator, placed in contact with a flow of air inside the motor vehicle to cool it.
    The air conditioning circuit can be reversible, that is to say that it can absorb heat energy in the outside air at the first heat exchanger, then called evapo-condenser, and return it in the passenger compartment in particular by means of a third dedicated heat exchanger.
    It is called direct heat pump when the third heat exchanger is fed directly by the refrigerant of the air conditioning circuit. It is called indirect heat pump when the third heat exchanger is fed by another coolant than the refrigerant. The refrigerant transfers heat energy to a heat transfer fluid circulating in a thermal management loop by means in particular of a bifluid heat exchanger.
    However, in the case of an indirect heat pump, when the outside temperature is less than or equal to -10 ° C and the temperature of the coolant is high, the temperature difference between the coolant and the coolant may not not be sufficient for the refrigerant to condense at the bifluid heat exchanger. This problem of condensation at the level of the two-fluid heat exchanger impairs the proper functioning of the heat pump and consequently adversely affects the thermal comfort of the occupants of the motor vehicle.
    One of the aims of the present invention is therefore to at least partially overcome the disadvantages of the prior art and to provide an improved air conditioning circuit.
    The present invention therefore relates to an indirect reversible air conditioning system for a motor vehicle comprising: a first refrigerant fluid loop in which a refrigerant circulates, a second heat transfer fluid loop in which a heat transfer fluid circulates, and a heat exchanger. bifluid arranged jointly on the first coolant loop and the second heat transfer fluid loop, so as to allow the exchange of heat between the first coolant loop and the second coolant loop, at least one of the first refrigerant loop and second heat transfer fluid loop of the reversible air conditioning circuit including a bypass branch of the two-fluid heat exchanger.
    This bypass branch prevents the refrigerant fluid of the first refrigerant loop and / or the heat transfer fluid of the second heat transfer fluid loop from circulating in the bifluid heat exchanger. This is of particular interest when the outside temperature is very low, for example of the order of -10 ° C and the heat transfer fluid is at high temperature. Under these conditions, the bifluid heat exchanger is bypassed and there is no exchange of heat energy between the first refrigerant loop and the second heat transfer fluid loop. All the heat energy of the refrigerant fluid drawn into the air outside the motor vehicle can be returned directly to the interior air flow to the passenger compartment of the vehicle via a dedicated heat exchanger.
    According to one aspect of the invention, a bypass branch is disposed on the first refrigerant loop.
    According to another aspect of the invention, the indirect reversible air conditioning circuit comprises a device for redirecting the refrigerant fluid to the two-fluid heat exchanger or to the bypass branch.
    According to another aspect of the invention, a bypass branch is disposed on the second heat transfer fluid loop.
    According to another aspect of the invention, the indirect reversible air conditioning circuit comprises a device for redirecting the heat transfer fluid to the two-fluid heat exchanger or to the bypass branch.
    According to another aspect of the invention, the first refrigerant loop comprises in the direction of circulation of the refrigerant in an air conditioning operating mode: a compressor, a first heat exchanger disposed downstream of the compressor, said first heat exchanger being intended to be traversed by a flow of air outside the motor vehicle, ° a first expansion device disposed downstream of the first heat exchanger, ° a second heat exchanger disposed downstream of the first expansion device, said second heat exchanger being intended to be traversed by an interior air flow to the cabin of the motor vehicle, said first refrigerant loop further comprising: a first connecting branch connecting a first junction point and a second junction point, said first junction point being disposed downstream of the compressor, said compressor and the first heat exchanger and said second junction point being disposed downstream of the second heat exchanger, between said second heat exchanger and the compressor, said first connecting branch including the bifluid heat exchanger, and a second connecting leg connecting a third junction point and a fourth junction point, said third junction point being disposed upstream of the first heat exchanger, between the first junction point and said first heat exchanger, and said fourth point junction being disposed upstream of the compressor, between the second heat exchanger and said compressor.
    According to another aspect of the invention, the bypass branch of the bifluid heat exchanger connects a fifth junction point and a sixth junction point, said fifth junction point being arranged upstream of the bifluid heat exchanger on the first connecting branch and said sixth joining point being disposed downstream of the two-fluid heat exchanger on the first connecting branch.
    According to another aspect of the invention, the second heat transfer fluid loop comprises in the direction of circulation of the coolant: a pump, the bifluid heat exchanger a third heat exchanger disposed downstream of the heat exchanger. bifluid heat, said third heat exchanger being intended to be traversed by the inner air flow and being disposed downstream of the second heat exchanger in said inner air flow.
    According to another aspect of the invention, a bypass branch of the bifluid heat exchanger connects a seventh junction point and an eighth junction point, said seventh junction point being disposed upstream of the bifluid heat exchanger on the second heat transfer fluid loop and said eighth junction point being disposed downstream of the two-fluid heat exchanger on the second heat transfer fluid loop.
    According to another aspect of the invention, the second heat transfer fluid loop comprises an electric heating element of the coolant disposed in the direction of circulation of the coolant downstream of the bifluid heat exchanger, between said two-fluid heat exchanger and the third heat exchanger.
    According to another aspect of the invention, the first connection branch comprises a second expansion device disposed downstream of the bifluid heat exchanger, in the direction of circulation of the refrigerant fluid within said first connection branch.
    According to another aspect of the invention, the first refrigerant loop comprises a branch branch connecting a ninth junction point, disposed between the first heat exchanger and the first expansion device, and a tenth junction point disposed between the second heat exchanger and the compressor, said branch branch comprising a third expansion device and a fourth heat exchanger disposed downstream of said third expansion device.
    According to another aspect of the invention, the second heat transfer fluid loop comprises a fifth heat exchanger connected in parallel with said second heat transfer fluid loop.
    The present invention also relates to a method of operating the indirect reversible air-conditioning circuit according to a heat pump operating mode in which the coolant and / or the coolant passes through the bypass branch so as not to circulate in the exchanger of bifluid heat. Other features 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 in which: FIG. 1 shows a schematic representation of a circuit indirect reversible air conditioning 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 the indirect reversible air conditioning circuit of Figure 1 according to a first FIG. 4 shows the indirect reversible air-conditioning circuit of FIG. 1 according to a second mode of operation, FIG. 5 shows the indirect reversible air-conditioning circuit of FIG. 1 according to a third mode of operation, FIG. the indirect reversible air conditioning circuit of Figure 2 according to the third mode of f FIG. 7 shows a schematic representation of an indirect reversible air conditioning circuit according to a variant of the first embodiment, FIG. 8 shows a schematic representation of an indirect reversible air conditioning circuit according to another variant of the first embodiment. FIG. 9 shows the indirect reversible air conditioning circuit of FIG. 8 according to a variant of the third mode of operation.
    In the different figures, the identical elements bear the same reference numbers.
    The following achievements 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 features apply only to a single embodiment. Simple features of different embodiments may also be combined and / or interchanged to provide other embodiments.
    In the present description, it is possible to index certain elements or parameters, for example first element or second element as well as first parameter and second parameter or else 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 one element, parameter or criterion with respect to another, and it is easy to interchange such denominations without departing from the scope of the present description. This indexing does not imply either an order in time for example to appreciate this or that criterion.
    In the present description, the term "placed upstream" means that one element is placed before another relative to the direction of flow of a fluid. Conversely, "downstream" means that one element is placed after another relative to the direction of fluid flow.
    Figure 1 shows an indirect reversible air conditioning circuit 1 for a motor vehicle. This indirect reversible air conditioning circuit 1 comprises in particular: a first refrigerant fluid loop A, in which a cooling fluid circulates, in particular a chemical refrigerant fluid, for example the R134a; a second heat transfer fluid loop in which a heat transfer fluid circulates; , for example water or brine, and • a bifluid heat exchanger 13 arranged jointly on the first refrigerant loop A and the second heat transfer fluid loop Ω, so as to allow heat exchanges between the first coolant loop A and the second coolant loop Ω.
    At least one of the first refrigerant fluid loop A and the second heat transfer fluid loop Ω of the reversible air conditioning circuit 1 also comprises a bypass branch D, D 'of the two-fluid heat exchanger 13.
    This bypass branch D, D 'makes it possible to prevent the refrigerant of the first coolant loop A and / or the coolant of the second coolant loop Ω from circulating in the two-fluid heat exchanger 13. This is of particular interest when the outside temperature is very low, for example of the order of -10 ° C and the heat transfer fluid is at high temperature. Under these conditions, the bifluid heat exchanger 13 is bypassed and there is no exchange of heat energy between the first refrigerant loop A and the second heat transfer fluid loop Ω. All the heat energy of the refrigerant fluid drawn into the outside air of the motor vehicle can be returned directly to the interior air flow to the passenger compartment of the vehicle via a dedicated heat exchanger 9.
    According to a first embodiment illustrated in FIG. 1, a bypass branch D is disposed on the first refrigerant fluid loop A. In this first embodiment, the refrigerant fluid can then bypass the bifluid heat exchanger 13.
    For this, the indirect reversible air-conditioning circuit 1 comprises a device for redirecting the refrigerant fluid to the two-fluid heat exchanger 13 or to the bypass branch D.
    According to a second embodiment illustrated in FIG. 2, a bypass branch D 'is disposed on the second heat transfer fluid loop Ω. In this second embodiment, the coolant can then bypass the bifluid heat exchanger 13.
    For this, the indirect reversible air conditioning circuit 1 comprises a device for redirecting the heat transfer fluid to the two-fluid heat exchanger 13 or to the bypass branch D '. However, it is quite possible to imagine a particular embodiment (not shown) where the first refrigerant fluid loop A and the second heat transfer fluid loop Ω both have a bypass branch D, D '.
    As shown in FIGS. 1 and 2, the first refrigerant fluid loop A may comprise more particularly, in the direction of circulation of the refrigerant fluid in an air conditioning operating mode: a compressor 3, a first heat exchanger 5 disposed downstream of the compressor 3, said first heat exchanger 5 being intended to be traversed by an external air flow 100 to the motor vehicle, 0 a first expansion device 7 disposed downstream of the first heat exchanger 5, a second heat exchanger of heat 9 arranged downstream of the first expansion device 7, said second heat exchanger 9 being intended to be traversed by an interior air flow 200 to the passenger compartment of the motor vehicle, said first refrigerant loop A can further comprising: 0 a first connecting branch B connecting a first junction point 21 and a second junction point 22. The first j junction point 21 is disposed downstream of the compressor 3, between said compressor 3 and the first heat exchanger 5. The second junction point 22 is in turn disposed downstream of the second heat exchanger 9 between said second heat exchanger 9 and the compressor 3, said first connecting leg B having the bifluid heat exchanger 13, and ° a second connecting leg C connecting a third junction point 23 and a fourth junction point 24. The third junction point 23 is located upstream of the first heat exchanger 5, between the first junction point 21 and said first heat exchanger 5. The fourth junction point 24 is arranged upstream of the compressor 3, between the second heat exchanger 9 and said compressor 3.
    The first refrigerant fluid loop A also comprises a device for redirecting the refrigerant fluid according to the different operating modes. This device for redirecting the refrigerant fluid allows in particular: • the redirection of the refrigerant fluid from the compressor 3 to the first heat exchanger 5 and / or to the first connection branch B, • the redirection of the refrigerant fluid from the first exchanger of heat 5 to the second bypass branch C, and • the redirection of the refrigerant fluid from the two-fluid heat exchanger 13 to the second heat exchanger 9.
    As in the examples illustrated in the various figures, this device for redirecting the refrigerant fluid can be composed of different shut-off valves, in particular: a first shut-off valve 31 arranged between the first junction point 21 and the third point of 23. This first stop valve 21 allows the passage or blocking of the refrigerant from the compressor 3 or the first heat exchanger 5, a second stop valve 32 disposed on the first connecting branch B, by example between the first junction point 21 and the bifluid heat exchanger 13. This second stop valve 32 allows the passage or blocking of the refrigerant from the compressor 3 or the second heat exchanger 9 in the first branch of connection B, • a third stop valve 33 disposed on the second connection branch C. This third stop valve 33 allows the passage or the blocking the refrigerant fluid from the first 5 or the second 9 heat exchanger in the second connection branch C, • a fourth stop valve 34 disposed between the second junction point 22 and the fourth connection point 24, upstream of the compressor 3. This fourth stop valve 34 allows the passage or blocking of the refrigerant from the second heat exchanger 9, the first B or the second C connecting branch.
    It is of course quite possible to imagine a different organization of the shut-off valves or to replace or combine them with other elements such as check valves or three-way valves placed at points of junctions.
    By shut-off valves is meant here mechanical or electronic stop valves that can be controlled by an electronic control unit on board the motor vehicle.
    According to the first embodiment illustrated in particular in Figure 1, the bypass branch D of the bifluid heat exchanger 13 connects a fifth junction point 25 and a sixth junction point 26. The fifth junction point 25 is here disposed upstream of the two-fluid heat exchanger 13 on the first connecting branch B. The sixth junction point 26 is disposed downstream of the bifluid heat exchanger 13 on the first connecting branch B.
    In this first embodiment, the device for redirecting the refrigerant fluid to the bifluid heat exchanger 13 or to the bypass branch D may in particular comprise a fifth stop valve 35 disposed on said bypass branch D. The second valve stopper 32 is then disposed on the first connection branch B between the fifth 25 and sixth 26 junction points. According to this example of the first embodiment, the bypass branch D requires only one fifth additional stop valve 35 which limits the production costs.
    The second loop of heat transfer fluid Ω can in turn comprise, in the direction of circulation of the coolant: 0 a pump 53, 0 the bifluid heat exchanger 13 ° a third heat exchanger 51 disposed downstream of the heat exchanger bifluid 13, said third heat exchanger 51 being intended to be traversed by the internal air flow 200 and being disposed downstream of the second heat exchanger 9 in said inner air flow 200.
    According to the second embodiment illustrated in FIG. 2, the bypass branch D 'of the bifluid heat exchanger 13 connects a seventh junction point 27 and an eighth junction point 28. The seventh junction point 27 is here disposed upstream of the two-fluid heat exchanger 13 on the second loop of heat transfer fluid Ω. The eighth junction point 28 is disposed downstream of the two-fluid heat exchanger 13 on the second heat transfer fluid loop Ω.
    In this second embodiment, the device for redirecting the heat transfer fluid to the bifluid heat exchanger 13 or to the bypass branch D 'may in particular comprise a sixth stop valve 36 disposed on said bypass branch D'. The second heat transfer fluid loop Ω may also comprise a seventh stop valve 37 disposed between the seventh 27 and eighth 28 junction points, upstream or downstream of the two-fluid heat exchanger 13.
    As illustrated in FIGS. 1 and 2, the second heat transfer fluid loop Ω can also comprise 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 13, between said bifluid heat exchanger 13 and the third heat exchanger 51. This electric heating element 55 allows for example a direct heating of the coolant, for example to help achieve the target temperature of the indoor air flow 200 through the third heat exchanger 51.
    Similarly, the indirect reversible air conditioning circuit 1 may also include a refrigerant accumulator 11 upstream of the compressor 3 on the first refrigerant fluid loop A.
    The present invention also relates to a method of operating the indirect reversible air-conditioning circuit 1 according to different modes of operation.
    In FIGS. 3 to 9 showing different modes of operation, the elements in which the coolant or the coolant circulate are shown in solid lines and the elements in which they do not circulate are shown in dashed lines. Arrows have also been inserted to show the flow direction of the coolant or coolant.
    A first mode of operation is illustrated in Figure 3, it is an air conditioning mode where the coolant passes successively in: • the compressor 3, where the refrigerant in the gas phase undergoes an increase in its pressure, • the first junction point 21, where the coolant is completely redirected to the third junction point 23, • the third junction point 23, where the coolant is completely redirected to the first heat exchanger 5, • the first heat exchanger 5, in which the cooling fluid loses enthalpy by yielding heat energy to the outside air flow 100 and wherein said refrigerant passes into the liquid phase, • the first expansion device 7, where the coolant undergoes a loss pressure, • the second heat exchanger 9, where the refrigerant regains enthalpy by absorbing heat energy to the interior air flow 200 and wherein said coolant passes into the gas phase, • the second junction point 22, where the coolant is completely redirected to the fourth junction point 24. At the fourth junction point 24 the coolant is then redirected to the compressor 3 .
    In this air conditioning mode, and according to the first embodiment, the coolant redirection device redirects the refrigerant for example by closing the second 32, third 33 and fifth 35 stop valves and opening the first 31 and fourth 34 shut-off valves. According to the second embodiment, the coolant redirection device redirects the refrigerant for example by closing the second 32 and third 33 stop valves and opening the first 31 and fourth 34 stop valves.
    In this air conditioning mode, the second heat transfer fluid loop Ω is generally at a standstill. The second heat transfer fluid loop Ω may possibly operate in order to heat the air at the outlet of the second heat exchanger 9 in order to dehumidify the interior air flow 200.
    A second mode of operation is illustrated in FIG. 4, it is a heat pump mode in which the coolant successively passes into: • the compressor 3, where the cooling fluid in the gas phase undergoes an increase in its pressure, The first junction point 21, where the coolant is completely redirected to the first connecting branch B, the fifth junction point 25, where the coolant is completely redirected to the two-fluid heat exchanger 13, two-fluid heat exchanger 13, wherein the refrigerant loses enthalpy by yielding heat energy to the coolant of the second coolant loop Ω and wherein said refrigerant passes into the liquid phase portion, • the sixth junction point. 26, where the coolant is completely redirected to the second junction point 22, • the sixth junction point 26, where the coolant is t otalement redirected to the second heat exchanger 9, • the second heat exchanger 9, where the coolant loses enthalpy by yielding heat energy to the inner air flow 200 and where said refrigerant ends to pass into liquid phase, • the first expansion device 7, where the refrigerant undergoes a loss of pressure, • the first heat exchanger 5, where the refrigerant regains enthalpy by absorbing heat energy to the air flow outside 100 and wherein said coolant passes into the gas phase, • the third junction point 23, where the coolant is completely redirected in the second connecting branch C, to the fourth junction point 24. At the fourth junction point 24 the refrigerant is then redirected to the compressor 3.
    In this heat pump mode and according to the first embodiment, the device for redirecting the coolant redirects the refrigerant for example by closing the first 31, fourth 34 and fifth 35 stop valves and opening the second 32 and third 33 stop valves.
    According to the second embodiment, the coolant redirection device redirects the refrigerant for example by closing the first 31, and fourth 34 stop valves and opening the second 32 and third 33 stop valves.
    In this heat pump mode, the second heat transfer fluid loop Ω is in operation in order to circulate the heat transfer fluid in the two-fluid heat exchanger 13. According to the second embodiment, the device for redirecting the heat transfer fluid redirects the fluid. heat transfer to the two-fluid heat exchanger 13 for example by closing the sixth stop valve 36 and opening the seventh stop valve 37.
    FIGS. 5 and 6 show a variant of the heat pump mode in which the cooling fluid and / or the coolant passes through the bypass branch D or D 'so as not to circulate in the bifluid heat exchanger 13. Alternative heat pump mode is particularly useful when the outside temperature is very low, for example of the order of -10 ° C and the heat transfer fluid is at high temperature. Under these conditions, the bifluid heat exchanger 13 is bypassed and there is no exchange of heat energy between the first refrigerant loop A and the second heat transfer fluid loop Ω. All the heat energy of the refrigerant fluid drawn into the air outside the motor vehicle can be returned directly to the inner air flow 200 via the second heat exchanger 9.
    FIG. 5 shows this variant of the heat pump mode according to the first embodiment. The refrigerant then circulates successively in: • the compressor 3, where the refrigerating fluid in the gaseous phase undergoes an increase in its pressure, • the first junction point 21, where the coolant is totally redirected towards the first connection branch B, The fifth junction point 25, where the coolant is completely redirected to the bypass branch D, the sixth junction point 26, where the coolant is completely redirected to the second junction point 22, junction 22, where the refrigerant is completely redirected to the second heat exchanger 9, • the second heat exchanger 9, where the refrigerant loses enthalpy by yielding heat energy to the inner air flow 200 and wherein said refrigerant fluid enters the liquid phase, • the first expansion device 7, where the refrigerant undergoes a loss of ession, • the first heat exchanger 5, where the refrigerant regains enthalpy by absorbing heat energy to the outside air flow 100 and wherein said refrigerant passes into the gas phase, • the third connection point 23 , where the coolant is completely redirected in the second connecting branch C, to the fourth junction point 24. At the fourth junction point 24 the coolant is then redirected to the compressor 3.
    In this variant of the heat pump mode according to the first embodiment, the coolant redirection device redirects the refrigerant for example by closing the first 31, second 32 and fourth 34 stop valves and opening the third 33 and fifth 35 stop valves. In this variant of the heat pump mode, the second heat transfer fluid loop Ω is in operation in order to circulate the heat transfer fluid in the two-fluid heat exchanger 13.
    Figure 6 shows this variant of the heat pump mode according to the second embodiment. The refrigerant then circulates successively in: • the compressor 3, where the refrigerating fluid in the gaseous phase undergoes an increase in its pressure, • the first junction point 21, where the coolant is totally redirected towards the first connection branch B, • the two-fluid heat exchanger 13, the refrigerant is only through without exchanging heat energy with the heat transfer fluid because in the second heat transfer fluid loop Ω, said heat transfer fluid circulates in the bypass branch D ', • the second heat exchanger 9, where the refrigerant loses enthalpy by yielding heat energy to the inner air flow 200 and wherein said coolant passes into the liquid phase, • the first expansion device 7, where the refrigerant undergoes a loss of pressure, • the first heat exchanger 5, where the refrigerant regains enthalpy absorbing from the heat energy to the outside air flow 100 and wherein said refrigerant passes into the gas phase, • the third junction point 23, where the coolant is totally redirected into the second connecting branch C, towards the fourth point of 24. At the fourth junction point 24 the refrigerant is then redirected to the compressor 3.
    In this variant of the heat pump mode according to the second embodiment, the coolant redirection device redirects the refrigerant for example by closing the first 31, and fourth 34 stop valves and opening the second 31 and third 33 shut-off valves. At the level of the heat transfer fluid redirection device, the latter redirects the heat transfer fluid into the bypass branch D 'for example by opening the sixth stop valve 36 and closing the seventh stop valve 37.
    Still for this variant of the heat pump mode, the second loop of heat transfer fluid Ω can be in operation, in particular to carry out additional heating of the internal air flow 200 by means of the electric heating element 55 and the third heat exchanger 51.
    As shown in FIGS. 7 and 8, the indirect reversible air-conditioning circuit 1 may comprise other elements.
    The first refrigerant fluid loop A may in particular comprise an internal heat exchanger 20 (also known by the acronym IHX for "internai heat exchanger" in English) which allows a heat exchange between the refrigerant at the outlet of the first heat exchanger 5 with the refrigerant at the outlet of the second heat exchanger 9. Said internal heat exchanger 20 is then connected to the refrigerant output of the first heat exchanger 5, between said first heat exchanger 5 and the first expansion device 7 , and connected to the coolant outlet of the second heat exchanger 9, between the second 22 and fourth 24 junction points. This internal heat exchanger 20 makes it possible in particular to improve the coefficient of performance of the indirect reversible air-conditioning circuit 1.
    The first connecting branch B can in turn comprise a second expansion device 15 disposed downstream of the two-fluid heat exchanger 13, in the direction of circulation of the refrigerant fluid within said first connection branch B. This second device The expansion valve 15 may more particularly be able to be completely open in order to let the cooling fluid pass without loss of pressure. An alternative solution may be a bypass of said second expansion device 15 to let the refrigerant fluid without losing pressure. This second expansion device 15 may be particularly useful for causing a loss of pressure in the refrigerant fluid in heat pump mode before it passes into the second heat exchanger 9. The second heat exchanger 9 will then allow dehumidification indoor airflow 200.
    As shown in FIG. 7, the indirect reversible air conditioning circuit 1 may also comprise, in addition to the electric heating element 55 heating the heat transfer fluid, an electric air heating element 55 'disposed downstream of the second heat exchanger 9 in the inner air stream 200. This electric air heating element 55 'can directly heat the internal air flow 200.
    As illustrated in FIG. 8, the first refrigerant fluid loop A may comprise a bypass branch F arranged in parallel with the first expansion device 7 and the second heat exchanger 9. This branch branch F more precisely connects a ninth point of contact. junction 29 and a tenth junction point 290. The ninth junction point 29 is disposed between the first heat exchanger 5 and the first expansion device 7, and the tenth junction point 290 is disposed between the second heat exchanger 9 and the compressor 3. This branch branch F comprises in particular a third expansion device 17 and a fourth heat exchanger 19 disposed downstream of said third expansion device 17. This fourth heat exchanger 19 can for example be used in cooling mode to cool some elements of the motor vehicle such as electrical components or batteries.
    As illustrated in FIG. 8, the second heat transfer fluid loop Ω may comprise a fifth heat exchanger 59 connected in parallel with said second heat transfer fluid loop Ω. In order to totally or partially redirect the coolant to said fifth heat exchanger 59 or not, the second heat transfer fluid loop Ω may comprise for example a three-way valve 57 or various stop valves. This fifth heat exchanger can in particular be connected to a thermal management system of the engine of the motor vehicle. This makes it possible in particular to use part of the heat energy generated at this fifth heat exchanger 59 and to transfer it to the internal air flow 200 to heat it via the third heat exchanger 51.
    As shown in FIG. 9, the bypass branch D, D 'may also have a utility, still in heat pump mode, but during a cold start with a low coolant temperature.
    In this case, the refrigerant and / or the coolant bypasses the bifluid heat exchanger 13 through a bypass branch D and / or D '. The heat transfer fluid passes into the fifth heat exchanger 59 and, in order to increase the temperature, is heated by the electric heating element 55. To prevent the heat energy of the heat transfer fluid from dissipating into the internal air flow 200, a valve 300 can be closed so as to prevent the flow of internal air 200 from circulating through the third heat exchanger 51. This allows an acceleration of the temperature rise of the coolant and therefore, for example, an acceleration of the engine temperature rise.
    The first coolant loop A operates in heat pump mode, as above, and in this case allows a heating of the internal air flow 200 at the second heat exchanger 9.
    Thus, it can clearly be seen that the indirect reversible air-conditioning circuit 1 according to the invention allows operation in heat pump mode, even with very low outside air temperatures, for example less than or equal to -10 ° C. due to the possibility of bypassing the two-fluid heat exchanger 13 via the bypass branch D.
    权利要求:
    Claims (14)
    [1" id="c-fr-0001]
    An indirect reversible air-conditioning circuit (1) for a motor vehicle comprising: a first refrigerant fluid loop (A) in which a refrigerant circulates, a second heat-transfer fluid (Ω) loop in which a heat-transfer fluid circulates, and A two-fluid heat exchanger (13) arranged jointly on the first refrigerant fluid loop (A) and the second heat transfer fluid loop (Ω), so as to allow heat exchanges between the first refrigerant fluid loop (A) and the second heat transfer fluid loop (Ω), characterized in that at least one of the first refrigerant loop (A) and the second heat transfer fluid loop (Ω) of the reversible air conditioning circuit (1) comprises a bypass branch (D, D ') of the two-fluid heat exchanger (13).
    [2" id="c-fr-0002]
    2. indirect reversible air conditioning circuit (1) according to claim 1, characterized in that a bypass branch (D) is disposed on the first refrigerant loop (A).
    [3" id="c-fr-0003]
    3. indirect reversible air conditioning circuit (1) according to the preceding claim, characterized in that it comprises a device for redirecting the refrigerant fluid to the two-fluid heat exchanger (13) or to the branch bypass (D).
    [4" id="c-fr-0004]
    4. indirect reversible air conditioning circuit (1) according to one of the preceding claims, characterized in that a bypass branch (D ') is disposed on the second heat transfer fluid loop (Ω).
    [5" id="c-fr-0005]
    5. Indirect reversible air conditioning circuit (1) according to the preceding claim, characterized in that it comprises a device for redirecting the heat transfer fluid to the two-fluid heat exchanger (13) or to the bypass branch (D ').
    [6" id="c-fr-0006]
    6. Indirect reversible air conditioning circuit (1) according to one of the preceding claims, characterized in that the first refrigerant loop (A) comprises in the direction of circulation of the refrigerant in an air conditioning operating mode: 0 a compressor (3), 0 a first heat exchanger (5) disposed downstream of the compressor (3), said first heat exchanger (5) being intended to be traversed by an outside air flow (100) to the motor vehicle, A first expansion device (7) disposed downstream of the first heat exchanger (5), a second heat exchanger (9) disposed downstream of the first expansion device (7), said second heat exchanger (9) being intended to be traversed by an interior air flow (200) to the passenger compartment of the motor vehicle, said first refrigerant loop (A) further comprising: a first connecting branch (B) connecting a first junction point (21) and a second junction point (22), said first junction point being disposed downstream of the compressor (3), between said compressor (3) and the first heat exchanger (5) and said second junction point (22) being disposed downstream of the second heat exchanger (9), between said second heat exchanger (9) and the compressor (3), said first connecting leg (B) having the heat exchanger bifluid (13), and ° a second connecting leg (C) connecting a third junction point (23) and a fourth junction point (24), said third junction point being disposed upstream of the first heat exchanger (5). ), between the first junction point (21) and said first heat exchanger (5), and said fourth junction point (24) being arranged upstream of the compressor (3), between the second heat exchanger (9) and said compressor (3).
    [7" id="c-fr-0007]
    An indirect reversible air conditioning circuit (1) according to claims 2 and 6 in combination, characterized in that the bypass branch (D) of the two-fluid heat exchanger (13) connects a fifth junction point (25) and a sixth junction point (26), said fifth junction point (25) being disposed upstream of the bifluid heat exchanger (13) on the first connecting branch (B) and said sixth junction point (26) being disposed downstream of the two-fluid heat exchanger (13) on the first connecting branch (B).
    [8" id="c-fr-0008]
    8. reversible indirect air conditioning circuit (1) according to one of the preceding claims, characterized in that the second heat transfer fluid loop (Ω) comprises in the flow direction of the heat transfer fluid: ° a pump (53), ° 1 bifluid heat exchanger (13), a third heat exchanger (51) disposed downstream of the bifluid heat exchanger (13), said third heat exchanger (51) being intended to be traversed by the flow of heat. indoor air (200) and being disposed downstream of the second heat exchanger (9) in said indoor air flow (200).
    [9" id="c-fr-0009]
    Indirect reversible air conditioning circuit (1) according to claims 4 and 8 in combination, characterized in that the bypass branch (D ') of the two-fluid heat exchanger (13) connects a seventh junction point (27). and an eighth junction point (28), said seventh junction point (27) being disposed upstream of the bifluid heat exchanger (13) on the second coolant loop (Ω) and said eighth junction point (28). ) being disposed downstream of the bifluid heat exchanger (13) on the second heat transfer fluid loop (Ω).
    [10" id="c-fr-0010]
    10. Indirect reversible air conditioning circuit (1) according to one of claims 8 or 9 characterized in that the second heat transfer fluid loop (Ω) comprises an electric heating element (55) of the heat transfer fluid disposed in the direction of circulation. heat transfer fluid, downstream of the two-fluid heat exchanger (13), between said two-fluid heat exchanger (13) and the third heat exchanger (51).
    [11" id="c-fr-0011]
    11. Indirect reversible air conditioning circuit (1) according to one of claims 6 to 10, characterized in that the first connecting leg (B) comprises a second expansion device (15) disposed downstream of the heat exchanger bifluid (13) in the direction of circulation of the refrigerant fluid within said first connecting branch (B).
    [12" id="c-fr-0012]
    12. Indirect reversible air conditioning circuit (1) according to one of claims 6 to 11, characterized in that the first refrigerant loop (A) comprises a branch branch (F) connecting a ninth junction point (29) disposed between the first heat exchanger (5) and the first expansion device (7), and a tenth junction point (290) disposed between the second heat exchanger (9) and the compressor (3), said bypass (F) comprising a third expansion device (17) and a fourth heat exchanger (19) arranged downstream of said third expansion device (17).
    [13" id="c-fr-0013]
    13. Indirect reversible air conditioning circuit (1) according to one of the preceding claims, characterized in that the second heat transfer fluid loop (Ω) comprises a fifth heat exchanger (59) connected in parallel with said second heat transfer fluid loop. (Ω).
    [14" id="c-fr-0014]
    14. A method of operating an indirect reversible air-conditioning circuit (1) according to one of the preceding claims, according to a heat pump operating mode in which the coolant and / or heat transfer fluid passes through the bypass branch ( D) so as not to circulate in the two-fluid heat exchanger (13).
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    同族专利:
    公开号 | 公开日
    EP3465025B1|2021-12-01|
    CN109312965B|2020-12-01|
    WO2017212158A1|2017-12-14|
    CN109312965A|2019-02-05|
    FR3052236B1|2019-05-10|
    EP3465025A1|2019-04-10|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE112013002754T5|2012-05-31|2015-07-30|Valeo Systemes Thermiques|Heating, ventilation and / or air conditioning system for a motor vehicle and method for operating such a system|
    EP2891849A1|2013-08-02|2015-07-08|O.Y.L. Research & Development Centre Sdn Bhd|Heat reclaim for a multifunction heat pump and a multifunction air conditioner|
    US20150121922A1|2013-11-06|2015-05-07|Automotive Research & Testing Center|Thermal management system for an electric vehicle|FR3078391A1|2018-02-23|2019-08-30|Psa Automobiles Sa|THERMAL EXCHANGE SYSTEM FOR AN ELECTRIC MOTOR VEHICLE, GENERATOR OF A SYNERGY BETWEEN A COLD LOOP AND A HOT LOOP.|
    FR3085624A1|2018-09-12|2020-03-13|Valeo Systemes Thermiques|HEAT LIQUID CIRCUIT|
    WO2021180894A1|2020-03-13|2021-09-16|Valeo Systemes Thermiques|Reversible air-conditioning system for a motor vehicle|
    WO2021249934A1|2020-06-10|2021-12-16|Valeo Systemes Thermiques|Device for the thermal management of an electric or hybrid motor vehicle comprising a heat-transfer fluid circuit|US20030182955A1|1999-06-07|2003-10-02|Toyotaka Hirao|Vehicular air conditioner|
    JP5581886B2|2010-08-11|2014-09-03|株式会社日立製作所|Vehicle air conditioning system|FR3081777B1|2018-06-01|2020-09-11|Valeo Systemes Thermiques|REFRIGERANT FLUID CIRCUIT FOR MOTOR VEHICLES|
    FR3086212A1|2018-09-26|2020-03-27|Valeo Systemes Thermiques|PASSENGER COMFORT MANAGEMENT SYSTEM|
    FR3092162A1|2019-01-25|2020-07-31|Valeo Systemes Thermiques|Motor vehicle air conditioning circuit and associated management method|
    FR3092161B1|2019-01-25|2021-02-19|Valeo Systemes Thermiques|Motor vehicle air conditioning circuit and associated management method|
    法律状态:
    2017-06-30| PLFP| Fee payment|Year of fee payment: 2 |
    2017-12-08| PLSC| Publication of the preliminary search report|Effective date: 20171208 |
    2018-06-27| PLFP| Fee payment|Year of fee payment: 3 |
    2019-06-28| PLFP| Fee payment|Year of fee payment: 4 |
    2020-06-30| PLFP| Fee payment|Year of fee payment: 5 |
    2021-06-30| PLFP| Fee payment|Year of fee payment: 6 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1655176A|FR3052236B1|2016-06-07|2016-06-07|AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE|
    FR1655176|2016-06-07|FR1655176A| FR3052236B1|2016-06-07|2016-06-07|AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE|
    PCT/FR2017/051416| WO2017212158A1|2016-06-07|2017-06-06|Motor vehicle air-conditioning circuit|
    EP17733508.0A| EP3465025B1|2016-06-07|2017-06-06|Motor vehicle air-conditioning circuit|
    CN201780035309.6A| CN109312965B|2016-06-07|2017-06-06|Air conditioning loop of motor vehicle|
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