• 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 a method for managing an invertible indirect air-conditioning circuit (1) for a motor vehicle comprising a first refrigerant fluid loop (A) in which a refrigerant circulates and comprising a first bifluid heat exchanger (5) arranged together on the first coolant loop (A) and on a second heat transfer fluid loop (B) in which a first heat transfer fluid circulates, the first heat transfer fluid loop (A) comprising a bypass line (80) comprising a second two-fluid heat exchanger (83) for exchanging heat between the refrigerant and a second heat transfer fluid, when the indirect cooling circuit (1) is in a dedicated cooling mode of the second heat transfer fluid in which the refrigerant passes through the pipe bypass (80), a central control unit (90) redirects the refrigerant fluid so that: • if the pressure measured at the pressure sensor (71) of the refrigerant at the outlet of the first bifluid heat exchanger (5) is lower than the limit pressure value, the refrigerant redirection device prevents the passage of the cooling fluid in the bypass loop (30), • if the pressure measured at the pressure sensor (71) of the refrigerant at the outlet of the first bifluid heat exchanger (5) is greater than or equal to a value of pressure limit, the coolant redirection device allows the passage of refrigerant in the bypass loop (30).
    公开号:FR3070316A1
    申请号:FR1758007
    申请日:2017-08-30
    公开日:2019-03-01
    发明作者:Jugurtha BENOUALI；Regis Beauvis；Muriel Porto；Jin-Ming Liu
    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 management 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 use a heat pump operating mode in which it is able to absorb heat. calorific 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 (for example a refrigerant on the one hand and glycol water on the other hand) in order to carry out the various heat exchanges.
    The air conditioning circuit thus comprises a first coolant loop in which a coolant circulates, a second coolant loop in which a first coolant circulates, and a first 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.
    The air conditioning circuit can also include a bypass line comprising an expansion device and a second dual-fluid heat exchanger. This second two-fluid heat exchanger makes it possible in particular to cool a second heat transfer fluid circulating in another circulation loop. This circulation loop and this second heat transfer fluid can for example be used to cool the batteries of an electric or hybrid motor vehicle.
    However, in the case where the air conditioning circuit is in an operating mode where it only cools this second heat transfer fluid, the refrigerant fluid can reach a high pressure, in particular at the level of the evaporator. This high pressure can cause deterioration of the evaporator.
    One of the aims of the present invention is therefore to at least partially remedy the drawbacks of the prior art and to propose a method for managing an improved reversible air conditioning circuit, in particular during a dedicated cooling mode of the second heat transfer fluid.
    The present invention therefore relates to a method for managing an indirect reversible air conditioning circuit for a motor vehicle comprising a first coolant loop in which a coolant circulates and comprising a first two-fluid heat exchanger arranged jointly on the first coolant loop and on a second loop of heat transfer fluid in which a first heat transfer fluid circulates, the first two-fluid heat exchanger being arranged so as to allow heat exchanges between the first loop of coolant and the second loop of heat transfer fluid, the first loop heat transfer fluid comprising:
    • a compressor, • the first two-fluid heat exchanger, placed downstream of said compressor, • a first expansion device constantly allowing coolant to pass through, • a first heat exchanger being intended to be traversed by a flow of air inside the motor vehicle, • a second expansion device, • a second heat exchanger being intended to be traversed by a flow of air outside the motor vehicle, and • a bypass loop of the second heat exchanger, • a device for redirection of the refrigerant from the first heat exchanger to the second heat exchanger or to the bypass loop, • a bypass line connected on the one hand between the first dual-fluid heat exchanger and the first expansion device and on the other hand between the output of the bypass loop and the compressor, said bypass line compo a third expansion device disposed upstream of a second two-fluid heat exchanger allowing the heat exchanges between the refrigerant and a second heat-transfer fluid, said circuit comprising a pressure sensor of the refrigerant fluid at the outlet of the first two-fluid heat exchanger , the indirect reversible air conditioning circuit comprising a central control unit connected to said coolant pressure sensor at the outlet of the first dual-fluid heat exchanger and capable of controlling the first coolant redirection device, when the indirect air conditioning circuit is in a dedicated cooling mode for the second heat transfer fluid in which the refrigerant passes through the bypass pipe and does not pass through the second heat exchanger, the central control unit controls the device for redirection of the coolant so that:
    If the pressure measured at the coolant pressure sensor at the outlet of the first two-fluid heat exchanger is less than the limit pressure value, the coolant redirection device prevents the coolant from passing through the bypass loop, • if the pressure measured at the coolant pressure sensor at the outlet of the first two-fluid heat exchanger is greater than or equal to a limit pressure value, the coolant redirection device allows the coolant to pass through the circumvention.
    According to one aspect of the invention, the third expansion device is an electronic expansion valve controlled by the central control unit and when the coolant passes through the bypass loop, the opening of the third expansion device is controlled so that the refrigerant entering the compressor reaches a target superheat value.
    According to another aspect of the invention, if the target superheating value of the refrigerant entering the compressor cannot be reached, the opening of the third expansion device is controlled to be at its minimum.
    According to one aspect of the invention, the target overheating is between 5 and 22 ° C.
    According to one aspect of the invention, the central control unit regulates the speed of the compressor so that the pressure of the coolant leaving the first heat exchanger reaches a target value, said target value of the pressure of the coolant being calculated. as a function of a target temperature of a second heat transfer fluid at the outlet of the second two-fluid heat exchanger.
    According to one aspect of the invention, the refrigerant is chosen from R1234yf and R134a.
    According to one aspect of the invention, the limit pressure value of the refrigerant at the outlet of the first two-fluid heat exchanger is between 10 and 15 bars.
    The present invention also relates to an indirect reversible air conditioning circuit for a motor vehicle comprising a first coolant loop in which a coolant circulates and comprising a first dual-fluid heat exchanger arranged jointly on the first coolant loop and on a second coolant loop. heat transfer fluid in which a first heat transfer fluid circulates, the first two-fluid heat exchanger being arranged so as to allow heat exchanges between the first coolant loop and the second heat transfer loop, the first heat transfer loop comprising:
    • a compressor, • the first two-fluid heat exchanger, placed downstream of said compressor, • a first expansion device constantly allowing coolant to pass through, • a first heat exchanger being intended to be traversed by a flow of air inside the motor vehicle, • a second expansion device, • a second heat exchanger being intended to be traversed by a flow of air outside the motor vehicle, and • a bypass loop of the second heat exchanger, • a device for redirection of the refrigerant from the first heat exchanger to the second heat exchanger or to the bypass loop, • a bypass line connected on the one hand between the first dual-fluid heat exchanger and the first expansion device and on the other hand between the output of the bypass loop and the compressor, said bypass line compo a third expansion device disposed upstream of a second two-fluid heat exchanger allowing the heat exchanges between the refrigerant and a second heat-transfer fluid, said circuit comprising a pressure sensor of the refrigerant fluid at the outlet of the first two-fluid heat exchanger the indirect reversible air conditioning circuit comprising a central control unit connected to said coolant pressure sensor at the outlet of the first dual-fluid heat exchanger and capable of controlling the first coolant redirection device, when the indirect air conditioning circuit is in a dedicated cooling mode of the second heat transfer fluid in which the coolant passes through the bypass line and does not pass through the second heat exchanger, centrale central control unit is configured to control the coolant redirection device so that:
    If the pressure measured at the coolant pressure sensor at the outlet of the first two-fluid heat exchanger is less than the limit pressure value, the coolant redirection device prevents the coolant from passing through the bypass loop, • if the pressure measured at the coolant pressure sensor at the outlet of the first two-fluid heat exchanger is greater than or equal to a limit pressure value, the coolant redirection device allows the coolant to pass through the circumvention.
    Other characteristics and advantages of the invention will appear more clearly on reading the following description, given by way of illustrative and nonlimiting example, and of the appended drawings among which:
    Figure 1 shows a schematic representation of an indirect reversible air conditioning circuit, Figure 2 shows a schematic representation of the second heat transfer fluid loop of the indirect invertible air conditioning circuit of Figure 1, according to an alternative embodiment, Figure 3 shows a schematic representation of a heating, ventilation and / or air conditioning device, FIG. 4 shows a schematic representation of an indirect reversible air conditioning circuit of FIG. 1 in a mode of operation for cooling the second heat transfer fluid, the Figure 5 shows a schematic representation of an indirect reversible air conditioning circuit of Figure 1 in a variant of the cooling operating mode of the second heat transfer fluid, Figure 6 shows a diagram of the evolution of certain parameters of the reversible air conditioning circuit indirect as a function of time in the cooling mode idea of the second heat transfer fluid in Figures 4 and 5.
    In the various figures, identical elements have the same reference numbers.
    The following embodiments are examples. Although the description refers to one or more embodiments, this does not necessarily mean that each reference relates to the same embodiment, or that the characteristics apply only to a single embodiment. Simple features of different embodiments can also be combined and / or interchanged to provide other embodiments.
    In the present description, it is possible to index certain elements or parameters, 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, for example R1234yf, R134a or any other coolant suitable for the application, • a second coolant loop B in which a coolant circulates, and • a first two-fluid heat exchanger 5 arranged jointly on the first coolant loop A and on the second coolant loop B, so as to allow heat exchanges between said first coolant loop A and said second coolant loop B.
    The first refrigerant loop A comprises more particularly in the direction of circulation of the refrigerant:
    ° a compressor 3, ° the first two-fluid heat exchanger 5, arranged downstream of said compressor 3, ° a first expansion device 7, ° a first heat exchanger 9 being intended to be traversed by an internal air flow 100 at motor vehicle, ° a second expansion device 11, ° a second heat exchanger 13 being intended to be traversed by a flow of air outside 200 to the motor vehicle, and ° a bypass loop 30 of the second heat exchanger 13.
    The bypass loop 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 quite possible to imagine that the first connection point 31 is disposed between the second expansion device 11 and the second heat exchanger 13 as long as the refrigerant has the possibility of bypassing said second 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.
    In order to control the passage of the coolant within the bypass loop 30 or not, the indirect air conditioning circuit 1 includes a device for redirecting the coolant from the first heat exchanger 9 to said bypass loop 30 or else to the second heat exchanger 13. This coolant redirection device can in particular comprise a first stop valve 33 disposed on the bypass loop 30. This first stop valve 33 can be an all-or-nothing valve or else another proportional valve whose opening amplitude is controlled. So that the coolant does not pass through the second heat exchanger 13, the second expansion device 11 may in particular include a stop function, that is to say that it is capable of blocking the flow of coolant when 'it is closed. An alternative may be to have a stop valve between the second expansion device 11 and the first connection point 31.
    Another alternative (not shown) may also be to have a three-way valve at the first connection point 31.
    The first refrigerant loop A can also include a non-return valve 23 disposed downstream of the second heat exchanger 13, between said second heat exchanger 13 and the second connection point 32 in order to prevent refrigerant from the first bypass loop 30 does not reflux to the second heat exchanger 13.
    By stop valve, non-return valve, three-way valve or expansion device with stop function, we mean here mechanical or electromechanical elements which can be controlled by an electronic control unit on board the motor vehicle.
    The first refrigerant loop A may also include a first internal heat exchanger (not shown) allowing heat exchange between the high pressure refrigerant leaving the first dual-fluid heat exchanger 5 and the low pressure refrigerant leaving of the second heat exchanger 13 or of the bypass loop 30. This first internal heat exchanger notably comprises an inlet and an outlet for low-pressure refrigerant coming from the second connection point 32, as well as an inlet and an outlet high pressure refrigerant from the first two-fluid heat exchanger 5.
    By high pressure refrigerant is meant by this a refrigerant having undergone an increase in pressure at the compressor 3 and has not yet suffered a loss of pressure due to one of the expansion devices. By low-pressure refrigerant is meant by this a refrigerant having undergone a pressure loss and at a pressure close to that at the inlet of the compressor 3.
    The first refrigerant loop A may also further include a second internal heat exchanger (not shown) allowing a heat exchange between the high pressure refrigerant leaving the first internal heat exchanger and the circulating low pressure refrigerant. in the bypass loop 30. This second internal heat exchanger 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 in from the first internal heat exchanger. As illustrated in FIG. 1, the second internal heat exchanger can be arranged downstream from the first stop valve 33.
    At least one of the first or second internal heat exchangers can be a coaxial heat exchanger, that is to say comprising two coaxial tubes and between which the heat exchanges take place.
    Preferably, the first internal heat exchanger can be a coaxial internal heat exchanger with a length between 50 and 120 mm while the second internal heat exchanger can be a coaxial internal heat exchanger with a length between 200 and 700mm.
    The first cooling fluid loop A may also include a desiccant bottle 14 disposed downstream of the first two-fluid heat exchanger 5, more precisely between said first two-fluid heat exchanger 5 and the first expansion device 7. Such a desiccant bottle 14 disposed on the high pressure side of the air conditioning circuit, that is to say downstream of the dual-fluid heat exchanger 5 and upstream of an expansion device, has a smaller footprint as well as a reduced cost compared to d other phase separation solutions such as an accumulator which would be disposed on the low pressure side of the air conditioning circuit, that is to say upstream of the compressor 3, in particular upstream of the first internal heat exchanger.
    The first coolant loop A also includes a bypass line 80 of the first expansion device 7 and the first heat exchanger 9. This bypass line 80 includes a third expansion device 12 disposed upstream of a second heat exchanger two-fluid 83. This second two-fluid heat exchanger 83 is also arranged jointly on a secondary thermal management loop. The secondary thermal management loop can more particularly be a loop in which a second heat transfer fluid circulates and connected to heat exchangers or cold plates at the level of batteries and / or electronic elements.
    The bypass line 80 is connected on the one hand upstream of the first expansion device 7. This connection is made at a first junction point 81 disposed upstream of the first expansion device 7, between the first heat exchanger dual fluid 5 and said first expansion device 7.
    The bypass line 80 is connected on the other hand at a second junction point 82 disposed upstream of the compressor 3, between the third heat exchanger 13 and said compressor 3. In FIG. 1, the second junction point 82 is arranged between the second connection point 32 of the bypass loop 30 and the compressor 3. It is however quite possible to imagine other embodiments, for example on the bypass loop 30 downstream of the first stop valve 33.
    The first 7 and second 11 expansion devices can be electronic expansion valves, that is to say the pressure of the refrigerant outlet fluid is controlled by an actuator which fixes the opening section of the expansion device, thereby fixing the fluid pressure at the outlet. Such an electronic expansion valve is in particular capable of allowing the coolant to pass without loss of pressure when said expansion device is fully open.
    These expansion devices can thus be electronic expansion valves controllable by a central control unit 90 integrated into the vehicle.
    More particularly, the first expansion device 7 is an expansion valve constantly allowing coolant to pass through. By this is meant that it does not have a stop function and that even at its smallest opening, it lets through a flow of coolant.
    The third expansion device 12 may in turn include a stop function in order to allow or not the refrigerant to pass through the bypass line 80. An alternative is to have a stop valve on the bypass line 80, in upstream of the third expansion device 12. This third expansion device 12 can be an electronic expansion valve controlled by the central control unit 90 or even a thermostatic expansion valve or a tube orifice.
    According to a variant not shown, the first coolant loop A can also include a first internal heat exchanger (IHX for "internai heat exchanger") allowing heat exchange between the coolant at the outlet of the two-fluid heat exchanger 5 and the refrigerant leaving the second heat exchanger 13 or the bypass pipe 30. This first internal heat exchanger comprises in particular an inlet and an outlet for refrigerant coming from the second connection point 32, as well as an inlet and a coolant outlet from the dual fluid heat exchanger 5.
    The first refrigerant loop A may comprise, in addition to the first internal heat exchanger, a second internal heat exchanger allowing a heat exchange between the high pressure refrigerant leaving the first internal heat exchanger and the refrigerant at low pressure circulating in the bypass pipe 30, that is to say coming from the first connection point 31. By high pressure refrigerant is meant by this a refrigerant having undergone a pressure increase at the compressor 3 and qu '' it has not yet suffered a pressure loss due to the electronic expansion valve 7 or the tube orifice 11. This second internal heat exchanger notably has an inlet and an outlet for coolant coming from the first connection point 31, as well as a high pressure refrigerant inlet and outlet from the pre mier internal heat exchanger.
    At least one of the first or second internal heat exchanger can be a coaxial heat exchanger, that is to say comprising two coaxial tubes and between which the heat exchanges take place.
    Preferably, the first internal heat exchanger can be a coaxial internal heat exchanger with a length between 50 and 120 mm while the second internal heat exchanger can be a coaxial internal heat exchanger with a length between 200 and 700mm.
    The second heat transfer fluid loop B can include:
    ° the first two-fluid heat exchanger 5, ° a first circulation pipe 50 of the first heat transfer fluid comprising an internal radiator 54 intended to be traversed by an internal air flow 100 to the motor vehicle, and connecting a first connection point 61 disposed downstream of the first two-fluid heat exchanger 5 and a second connection point 62 disposed upstream of said first two-fluid heat exchanger 5, ° a second circulation pipe 60 of the first heat transfer fluid comprising an external radiator 64 intended to be traversed by a flow outside air 200 to the motor vehicle, and connecting the first connection point 61 disposed downstream of the first dual-fluid heat exchanger 5 and the second connection point 62 disposed upstream of said first dual-fluid heat exchanger 5, and ° a pump 17 disposed downstream or upstream of the first two-fluid heat exchanger 5, between the first connection point 61 and the d second connection point 62.
    The indirect reversible air conditioning circuit 1 includes, within the second heat transfer fluid loop B, a device for redirection of the first heat transfer fluid coming from the first two-fluid heat exchanger 5 to the first circulation line 50 and / or to the second heat line traffic 60.
    As illustrated in FIG. 1, said device for redirection of the first heat-transfer fluid coming from the first two-fluid heat exchanger 5 may in particular comprise a second shut-off valve 63 disposed on the second circulation pipe 60 in order to block or not block the first fluid coolant and prevent it from circulating in said second circulation pipe 60.
    This embodiment makes it possible in particular to limit the number of valves on the second heat transfer fluid loop B and thus makes it possible to limit the production costs.
    According to an alternative embodiment illustrated in FIG. 2, representing the second heat transfer fluid loop B, the device for redirection of the first heat transfer fluid coming from the first two-fluid heat exchanger 5 may in particular comprise • a second stop valve 63 disposed on the second circulation line 60 in order to block or not block the first heat transfer fluid and in order to prevent it from circulating in said second circulation line 60, and • a third stop valve 53 arranged on the first circulation line 50 so whether or not to block the first heat transfer fluid and prevent it from circulating in said first circulation pipe 50.
    The second heat transfer fluid loop B can also include an electric heating element 55 of the first heat transfer fluid. Said electric heating element 55 is notably arranged, in the direction of circulation of the first heat-transfer fluid, downstream of the first two-fluid heat exchanger 5, between said first two-fluid heat exchanger 5 and the first junction point 61.
    The internal radiator 54 as well as the first heat exchanger 9 are more particularly arranged within a heating, ventilation and / or air conditioning device 40. As illustrated in FIG. 3, the heating, ventilation and / or air conditioning device 40 may include a supply pipe 41a for outside air and a supply pipe 41b for recirculated air (that is to say that comes from the passenger compartment). These two supply lines 41a and 41b both supply air to the first heat exchanger 9 so that it passes through it. In order to choose where the air passing through the first heat exchanger 9 comes from, the heating, ventilation and / or air conditioning device 40 comprises a shutter 410a, for example a drum type shutter, capable of completely closing or partially the supply line 41a for outside air or the supply line 41b for recirculated air.
    Within it, the heating, ventilation and / or air conditioning device 40 comprises a heating pipe 42a which makes it possible to bring air having passed through the first heat exchanger 9, at the level of the internal radiator 54 so that it the crosspiece and is heated before arriving in a distribution chamber 43. This heating pipe 42a also includes a shutter 420a able to close it completely or partially.
    The heating, ventilation and / or air conditioning device 40 may also include a bypass line 42b of the external radiator 54. This bypass line 42b allows the air having passed through the first heat exchanger 9 to go directly into the distribution chamber 43, without passing through the internal radiator 54. This bypass line 42b also includes a shutter 420b capable of closing it completely or partially.
    At the distribution chamber 43 the air can be sent to the windshield by an upper pipe 44a, the dashboard of the passenger compartment by a central pipe 44b and / or down from the dashboard of the passenger compartment by a lower pipe 44c. Each of these pipes 44a, 44b, 44c comprising a shutter 440 capable of closing them completely or partially.
    The heating, ventilation and / or air conditioning device 40 also includes a blower 46 in order to propel the internal air flow 100. This blower 46 can be arranged upstream of the first heat exchanger 9 according to the direction of circulation of the flow of indoor air 100.
    As illustrated in FIG. 1, the indirect reversible air conditioning circuit 1 comprises a central control unit 90 allowing it to switch from one operating mode to another. The central control unit 90 is in particular connected to a temperature sensor 72 of the first heat transfer fluid disposed downstream of the first two-fluid heat exchanger 5 and is capable of controlling the first stop valve 33. For this, the central control unit 90 is connected to the coolant redirection device. If said coolant redirection device comprises a first stop valve 33, the central control unit 90 controls its opening and closing as well as its opening amplitude if it is a progressive valve.
    The central control unit 90 may also be able to control the device for redirection of the first heat transfer fluid. For this, the central control unit 90 is also connected to the second stop valve 63 and controls its opening and closing.
    The central control unit 90 can also be connected to the compressor 3 in order to control the speed of the latter.
    The central control unit 90 can also be connected to the various expansion devices 7, 11 and 12, in order to control their opening and thus define the pressure loss that the refrigerant undergoes when passing through them, check whether they can be crossed without loss of pressure or if they block the flow of coolant.
    The central control unit 90 can also be connected to different sensors measuring different parameters of the coolant or of a secondary heat transfer fluid. By secondary heat transfer fluid is meant here a heat transfer fluid having exchanging heat energy with the refrigerant fluid. This can in particular be the first heat transfer fluid, the second heat transfer fluid or the internal air flow 100. These sensors can be for example:
    • a pressure sensor 71 at the outlet of the first dual-fluid heat exchanger 5, more precisely between the desiccant bottle 14 and the first junction point 81 • a temperature sensor 73 of the internal air flow 100 at the outlet of the first heat exchanger heat 9, • a temperature sensor 74 of the outside air, • a pressure and temperature sensor 75 at the inlet of the compressor 3 and • a temperature sensor 76 of the second heat transfer fluid within the thermal management loop secondary at the outlet of the second dual-fluid heat exchanger 83, and • a pressure sensor at the outlet of the first heat exchanger 9.
    The indirect reversible air conditioning circuit 1 described above can operate according to different operating modes, in particular a dedicated cooling mode for the second heat transfer fluid at the second dual-fluid heat exchanger 83, illustrated in FIG. 4.
    In this dedicated cooling mode of the second heat transfer fluid, the refrigerant passes through the bypass line 80 and does not pass through the second heat exchanger 13.
    More specifically, the refrigerant passes successively through:
    • the compressor 3 at which it undergoes a pressure increase, • the first two-fluid heat exchanger 5 at which the refrigerant transfers heat energy to the first heat transfer fluid in the second heat transfer fluid loop B, • the third expansion device 12 at which the refrigerant undergoes a pressure loss, • the second two-fluid heat exchanger 83 at which the refrigerant absorbs heat energy from the second heat transfer fluid, cooling it before joining the compressor 3.
    In this dedicated cooling mode of the second heat transfer fluid, the coolant redirection device ensures that the coolant does not circulate in the bypass loop 30, for example by closing the first stop valve 33. Similarly, the coolant redirection device ensures that the coolant does not circulate in the second expansion device 11 and the second heat exchanger 13. For this, the second expansion device 11 is completely closed if it has a stop function or a stop valve disposed upstream of said second expansion device 11 is closed.
    The first expansion device 7 is closed as far as possible in order to allow as little refrigerant fluid to pass through the first heat exchanger 9. The flow of interior air 100 is also stopped to avoid heat exchange at the level of the first heat exchanger 9.
    At the second heat transfer fluid loop B, the heat transfer fluid releases the heat energy recovered at the first two-fluid heat exchanger 5 in the external air flow 200 at the external radiator 64. For this, the second valve 63 is open. The heat transfer fluid does not exchange heat with the internal air flow 100. For this, the third stop valve 53 (visible in FIG. 2) is closed if it is present or the internal air flow 100 bypasses the internal radiator 54 within the heating, ventilation and / or air conditioning device 40.
    The present invention relates to a method for managing the indirect reversible air conditioning circuit 1 when it operates in this dedicated cooling mode of the second heat transfer fluid.
    In this management process, the central control unit 90 controls the coolant redirection device so that:
    • if the pressure measured at the pressure sensor 71 of the coolant leaving the first two-fluid heat exchanger 5 is less than the limit pressure value, the coolant redirection device prevents the coolant from passing through the bypass 30, as illustrated in FIG. 4, • if the pressure measured at the level of the pressure sensor 71 of the refrigerant fluid at the outlet of the first dual-fluid heat exchanger 5 is greater than or equal to a limit pressure value, the redirection device of the coolant allows the coolant to pass through the bypass loop 30, as illustrated in FIG. 5.
    In order for the coolant to pass through the bypass loop 30, the central control unit 90 more particularly opens the first stop valve 33.
    While part of the refrigerant passes through the bypass loop 30, another part of the refrigerant continues to pass through the bypass line 80.
    Passing the coolant through the bypass loop 30 reduces the pressure of the coolant at the first heat exchanger 9. Indeed, because the first expansion device 7 lets coolant pass, the pressure at the first heat exchanger 9 increases and can exceed a limit pressure above which the first heat exchanger 9 can be damaged. For example, the pressure at which the first heat exchanger 9 begins to deteriorate can be of the order of 30 bars. With a factor of safety coefficient of 2, the limit pressure beyond which the heat transfer fluid passes through the bypass loop 30 is between 10 and 15 bars.
    When the coolant passes through the bypass loop 80, the opening of the third expansion device 12 is controlled so that the coolant at the inlet of the compressor 3 reaches a target superheat value, for example between 5 and 22 ° C. .
    If the target superheating value of the refrigerant entering the compressor 3 cannot be reached, the opening of the third expansion device 12 is controlled to be at its minimum.
    According to this management method, the central control unit 90 can also regulate the speed of the compressor 3 so that the pressure of the refrigerant fluid measured by the pressure sensor 77 at the outlet of the first heat exchanger 9 reaches a target value. This target value of the pressure of the refrigerant fluid is more particularly calculated as a function of a target temperature of the second heat transfer fluid at the outlet of the second two-fluid heat exchanger 83. This target temperature of the second heat transfer fluid can for example be a set temperature in order to cool the batteries of an electric or hybrid vehicle.
    The diagram in FIG. 6 shows the variation of various parameters of the indirect invertible air conditioning circuit 1 as a function of time during its operation in dedicated cooling mode of the second heat transfer fluid and depending on whether the refrigerant passes or not through the loop bypass 30. The experimental parameters of this diagram are as follows:
    • a second dual-fluid heat exchanger 83 delivering a thermal power of 2 kW to the refrigerant, • an outside temperature illustrated by the T74 curve going from 45 to 25 ° C, • the refrigerant used within the first coolant loop A is R1234yf.
    The curve Pcomp_out corresponds to the change in the pressure of the coolant leaving the compressor 3.
    The curve P9_out corresponds to the change in the pressure of the coolant leaving the first heat exchanger 9.
    Curve T76 corresponds to the change in temperature of the second heat transfer fluid at the outlet of the second two-fluid heat exchanger 83.
    The EXV7 curve corresponds to the evolution of the opening of the first expansion device 7, expressed in pulses / 100.
    In the interval 20 to 80 min, part of the refrigerant passes through the bypass loop 30, the first stop valve 33 is open. The curve P9_out then shows that the pressure is relatively constant at a fairly low value, for example less than 6 bars. The temperature of the second heat transfer fluid at the outlet of the second two-fluid heat exchanger 83 shown by the curve T76 is for its part at a value of the order of 25 ° C. plus or minus 2 ° C.
    The EXV7 curve shows that in this interval, the first expansion device 7 has the smallest possible opening.
    In the interval from 80 to 103 min, the refrigerant does not pass through the bypass loop 30, the first stop valve 33 is closed. The curve P9_out shows a sudden rise in the pressure of the coolant leaving the first heat exchanger 9. The pressure of the coolant leaving the first heat exchanger 9 thus joins the pressure of the coolant leaving the compressor 3. the curves P9_out and Pcomp_out meet at a value between 18 and 11 bars during this interval.
    The temperature of the second heat transfer fluid leaving the second two-fluid heat exchanger 83 shown by the curve T76 remains at a value of the order of 25 ° C plus or minus 2 ° C.
    In this interval, the EXV7 curve shows that the first expansion device 7 has the smallest possible opening although greater than its opening during the interval of 80 to 103 min.
    In the interval 103 to 110 min, the first shut-off valve 33 is again open and part of the coolant passes through the bypass loop 30. The curve P9_out then shows that the pressure returns to a fairly low value, by example less than 6 bars. The temperature of the second heat-transfer fluid at the outlet of the second two-fluid heat exchanger 83 shown by the curve T76 is itself always at a value of the order of 25 ° C. plus or minus 2 ° C.
    The EXV7 curve shows that in this interval, the first expansion device 7 returns to the smallest possible opening.
    The passage of a portion of the refrigerant in the bypass loop 30 during the dedicated cooling mode of the second heat transfer fluid therefore does not penalize the cooling of said second heat transfer fluid.
    Thus, it can be seen that the method for managing the indirect invertible air conditioning circuit 1 according to the invention makes it possible to prevent the first heat exchanger 9 from undergoing too high refrigerant pressure when the indirect invertible air conditioning circuit 1 is in a dedicated cooling mode for the second heat transfer fluid.
    权利要求:
    Claims (8)
    [1" id="c-fr-0001]
    1. A method for managing a reversible indirect air conditioning circuit (1) for a motor vehicle comprising a first coolant loop (A) in which a coolant circulates and comprising a first two-fluid heat exchanger (5) arranged jointly on the first coolant loop (A) and on a second heat transfer fluid loop (B) in which a first heat transfer fluid circulates, the first two-fluid heat exchanger (5) being arranged so as to allow heat exchanges between the first loop coolant (A) and the second heat transfer fluid loop (B), the first heat transfer fluid loop (A) comprising:
    • a compressor (3), • the first two-fluid heat exchanger (5), arranged downstream of said compressor (3), • a first expansion device (7) constantly allowing coolant to pass through, • a first heat exchanger ( 9) being intended to be traversed by an interior air flow (100) to the motor vehicle, • a second expansion device (11), • a second heat exchanger (13) being intended to be traversed by a flow of outside air (200) to the motor vehicle, and • a bypass loop (30) of the second heat exchanger (13), • a device for redirecting the coolant coming from the first heat exchanger (9) to the second heat exchanger heat (13) or to the bypass loop (30), • a bypass line (80) connected on the one hand between the first two-fluid heat exchanger (5) and the first expansion device (7) and on the other share between the exit of the bypass loop (30) and the compressor (3), said bypass line (80) comprising a third expansion device (12) disposed upstream of a second dual-fluid heat exchanger (83) allowing the heat exchanges between the refrigerant and a second heat transfer fluid, said circuit comprising a pressure sensor (71) of the refrigerant at the outlet of the first dual-fluid heat exchanger (5), characterized in that the indirect reversible air conditioning circuit (1) comprises a central unit control (90) connected to said pressure sensor (71) of the refrigerant at the outlet of the first dual-fluid heat exchanger (5) and capable of controlling the first device for redirection of the refrigerant, when the indirect air conditioning circuit (1) is in a dedicated cooling mode of the second heat transfer fluid in which the refrigerant passes through the bypass pipe (80) and does not pass through the second heat exchanger (13), the central control unit (90) controls the coolant redirection device so that:
    • if the pressure measured at the pressure sensor (71) of the refrigerant leaving the first two-fluid heat exchanger (5) is lower than the limit pressure value, the refrigerant redirection device prevents the passage of the refrigerant in the bypass loop (30), • if the pressure measured at the pressure sensor (71) of the refrigerant leaving the first two-fluid heat exchanger (5) is greater than or equal to a limit pressure value, the device the coolant redirection allows the coolant to pass through the bypass loop (30).
    [2" id="c-fr-0002]
    2. Method for managing an indirect reversible air conditioning circuit (1) according to the preceding claim, characterized in that the third expansion device (12) is an electronic expansion valve controlled by the central control unit (90 ) and that when the coolant passes through the bypass loop (80), the opening of the third expansion device (12) is controlled so that the coolant at the inlet of the compressor (3) reaches a target superheat value.
    [3" id="c-fr-0003]
    3. Method for managing an invertible indirect air conditioning circuit (1) according to the preceding claim, characterized in that if the target superheating value of the refrigerant entering the compressor (3) cannot be reached, the opening the third expansion device (12) is controlled to be at its minimum.
    [4" id="c-fr-0004]
    4. Method for managing an invertible indirect air conditioning circuit (1) according to one of claims 2 or 3, characterized in that the target overheating is between 5 and 22 ° C.
    [5" id="c-fr-0005]
    5. Method for managing an indirect reversible air conditioning circuit (1) according to one of the preceding claims, characterized in that the central control unit (90) regulates the speed of the compressor (3) so that the pressure of the coolant leaving the first heat exchanger (9) reaches a target value, said target value of the pressure of the coolant being calculated as a function of a target temperature of a second heat transfer fluid leaving the second dual-fluid heat exchanger (83).
    [6" id="c-fr-0006]
    6. Method for managing an invertible indirect air conditioning circuit (1) according to one of the preceding claims, characterized in that the refrigerant is chosen from R1234yf and R134a.
    [7" id="c-fr-0007]
    7. Method for managing an invertible indirect air conditioning circuit (1) according to one of the preceding claims, characterized in that the limit pressure value of the refrigerant at the outlet of the first two-fluid heat exchanger (5) is included between 10 and 15 bars.
    [8" id="c-fr-0008]
    8. Indirect reversible air conditioning circuit (1) for a motor vehicle comprising a first coolant loop (A) in which a coolant circulates and comprising a first two-fluid heat exchanger (5) arranged jointly on the first coolant loop ( A) and on a second heat transfer fluid loop (B) in which a first heat transfer fluid circulates, the first dual-fluid heat exchanger (5) being arranged so as to allow heat exchanges between the first coolant loop (A) and the second heat transfer fluid loop (B), the first heat transfer fluid loop (A) comprising:
    • a compressor (3), • the first two-fluid heat exchanger (5), arranged downstream of said compressor (3), • a first expansion device (7) constantly allowing coolant to pass through, • a first heat exchanger ( 9) being intended to be traversed by an interior air flow (100) to the motor vehicle, • a second expansion device (11), • a second heat exchanger (13) being intended to be traversed by a flow of outside air (200) to the motor vehicle, and • a bypass loop (30) of the second heat exchanger (13), • a device for redirecting the coolant coming from the first heat exchanger (9) to the second heat exchanger heat (13) or to the bypass loop (30), • a bypass line (80) connected on the one hand between the first two-fluid heat exchanger (5) and the first expansion device (7) and on the other share between the exit of the bypass loop (30) and the compressor (3), said bypass line (80) comprising a third expansion device (12) disposed upstream of a second dual-fluid heat exchanger (83) allowing the heat exchanges between the refrigerant and a second heat transfer fluid, said circuit comprising a pressure sensor (71) of the refrigerant at the outlet of the first dual-fluid heat exchanger (5), characterized in that the indirect reversible air conditioning circuit (1) comprises a central unit control (90) connected to said pressure sensor (71) of the refrigerant at the outlet of the first dual-fluid heat exchanger (5) and capable of controlling the first device for redirection of the refrigerant, when the indirect air conditioning circuit (1) is in a dedicated cooling mode of the second heat transfer fluid in which the refrigerant passes through the bypass pipe (80) and does not pass through the second heat exchanger (13), Γ central control unit (90) being configured to control the refrigerant redirection device so that:
    • if the pressure measured at the pressure sensor (71) of the refrigerant leaving the first two-fluid heat exchanger (5) is lower than the limit pressure value, the refrigerant redirection device prevents the passage of the refrigerant in the bypass loop (30), • if the pressure measured at the pressure sensor (71) of the refrigerant leaving the first two-fluid heat exchanger (5) is greater than or equal to a limit pressure value, the device the coolant redirection allows the coolant to pass through the bypass loop (30).
    类似技术:
    公开号 | 公开日 | 专利标题
    FR3070316B1|2019-08-16|INDIRECT INDIRECT AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE AND METHOD FOR MANAGING THE SAME
    EP3606774B1|2021-08-18|Indirect reversible air-conditioning circuit for a motor vehicle and corresponding operating method
    EP3606776B1|2022-02-23|Indirect reversible air-conditioning circuit for a motor vehicle, and method for operation in defrosting mode
    EP3496964B1|2020-07-08|Indirect reversible air-conditioning circuit for a motor vehicle and corresponding operating method
    WO2018211200A1|2018-11-22|Indirect reversible air-conditioning circuit for a motor vehicle, and method for managing same in heat pump mode
    EP3658394B1|2021-06-09|Method for managing an indirect reversible air-conditioning circuit for a motor vehicle
    EP3661776B1|2022-01-05|Indirect reversible air-conditioning circuit for a motor vehicle
    EP3507114B1|2020-07-08|Indirect reversible air-conditioning circuit for a motor vehicle and corresponding operating method
    FR3058783A1|2018-05-18|INDIRECT INDIRECT AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE AND METHOD OF OPERATING THE SAME
    FR3066808B1|2019-06-07|METHOD FOR MANAGING AN INVERSIBLE AIR CONDITIONING CIRCUIT OF A MOTOR VEHICLE
    FR3066584A1|2018-11-23|INDIRECT INDIRECT AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE AND METHOD FOR MANAGING HEAT PUMP MODE
    WO2020165513A1|2020-08-20|Thermal management device for an electric or a hybrid motor vehicle
    EP3924673A1|2021-12-22|Device for thermal management of an electric or hybrid motor vehicle
    FR3069625A1|2019-02-01|METHOD FOR MANAGING AN INVERSIBLE AIR CONDITIONING CIRCUIT OF A MOTOR VEHICLE
    WO2021116564A1|2021-06-17|Reversible thermal-management device
    EP3924674A1|2021-12-22|Thermal management device for an electric or hybrid motor vehicle
    FR3056453A1|2018-03-30|INDIRECT INDIRECT AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE AND METHOD OF OPERATING THE SAME
    WO2020165526A1|2020-08-20|Thermal management device of a motor vehicle, having a constant pressure valve
    同族专利:
    公开号 | 公开日
    FR3070316B1|2019-08-16|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    EP3118035A1|2014-03-12|2017-01-18|Calsonic Kansei Corporation|In-vehicle temperature adjusting device, vehicle air-conditioning device, and battery temperature adjsuting device|
    EP2933586A1|2014-04-16|2015-10-21|Valeo Systemes Thermiques|Refrigeration circuit|
    DE102014226346A1|2014-12-18|2016-06-23|Bayerische Motoren Werke Aktiengesellschaft|Heating system for an electric or hybrid vehicle|
    WO2017005559A1|2015-07-06|2017-01-12|Bayerische Motoren Werke Aktiengesellschaft|Cooling circuit, method for air-conditioning a vehicle, and vehicle|
    US20170106725A1|2015-10-19|2017-04-20|Hyundai Motor Company|Battery cooling system for a vehicle|WO2020249579A1|2019-06-14|2020-12-17|Valeo Systemes Thermiques|Method for managing a thermal management device for a motor vehicle and associated thermal management device|
    WO2020260814A1|2019-06-28|2020-12-30|Valeo Systemes Thermiques|Method for managing a thermal management device for a motor vehicle|
    FR3111850A1|2020-06-29|2021-12-31|Psa Automobiles Sa|HIGH PERFORMANCE COOLING PERFORMANCE VEHICLE|
    FR3112994A1|2020-07-28|2022-02-04|Psa Automobiles Sa|THERMAL SYSTEM VEHICLE WITH OPTIMIZED COOLING PERFORMANCE|
    法律状态:
    2018-08-30| PLFP| Fee payment|Year of fee payment: 2 |
    2019-03-01| PLSC| Search report ready|Effective date: 20190301 |
    2019-08-30| PLFP| Fee payment|Year of fee payment: 3 |
    2020-08-31| PLFP| Fee payment|Year of fee payment: 4 |
    2021-08-31| PLFP| Fee payment|Year of fee payment: 5 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1758007A|FR3070316B1|2017-08-30|2017-08-30|INDIRECT INDIRECT AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE AND METHOD FOR MANAGING THE SAME|
    FR1758007|2017-08-30|FR1758007A| FR3070316B1|2017-08-30|2017-08-30|INDIRECT INDIRECT AIR CONDITIONING CIRCUIT FOR A MOTOR VEHICLE AND METHOD FOR MANAGING THE SAME|
    [返回顶部]