• 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 thermal management circuit (1) of a hybrid or electric vehicle, said thermal management circuit (1) comprising a first reversible air conditioning loop (A) in which a refrigerant circulates and comprises a heat exchanger bifluid (19) jointly arranged on a second circulation loop (B) of a heat transfer fluid, the second circulation loop (B) of a heat transfer fluid comprising: • a first circulation branch (B1) comprising in the direction of circulation of the coolant, a first pump (49), a first radiator (45) disposed in an internal air flow (100), and a battery heat exchanger (47), • a second connected circulation branch (B2) in parallel with the second radiator (45) and comprising a second pump (41) and an electric heating device (43) for the coolant, • a third circulation branch (B 3) connected in parallel of the first pump (49) and the battery heat exchanger (47), said third circulation branch (B3) having the two-fluid heat exchanger (19).
    公开号:FR3074272A1
    申请号:FR1761296
    申请日:2017-11-28
    公开日:2019-05-31
    发明作者:Bertrand NICOLAS；Mohamed Yahia
    申请人:Valeo Systemes Thermiques SAS；
    IPC主号:
    专利说明:

    The thermal management circuit of a hybrid or electric vehicle The invention relates to the field of motor vehicles and more particularly to a thermal management circuit for a hybrid or electric motor vehicle.
    In electric and hybrid vehicles, thermal management of the passenger compartment is generally managed by an invertible air conditioning loop. By invertible, it is meant that this air conditioning loop can operate in a cooling mode in order to cool the air intended for the passenger compartment and in a heat pump mode in order to heat the air intended for the passenger compartment. This reversible air conditioning loop can also include a bypass to manage the temperature of the batteries of the electric or hybrid vehicle. It is thus possible to heat or cool the batteries thanks to the reversible air conditioning loop. However, it is not possible to at least partially manage the temperature of the batteries without using the reversible air conditioning loop. So, for example when the passenger compartment does not need to be heated or cooled, it is still necessary to fully operate the reversible air conditioning loop to heat or cool the batteries. This results in a consumption of electricity which is too high and therefore can impact the autonomy of the electric or hybrid vehicle.
    One of the aims of the present invention is therefore to at least partially remedy the drawbacks of the prior art and to propose an improved thermal management circuit.
    The present invention therefore relates to a thermal management circuit of a hybrid or electric vehicle, said thermal management circuit comprising a first reversible air conditioning loop in which a refrigerant circulates and comprising a two-fluid heat exchanger arranged jointly on a second loop of circulation of a heat transfer fluid, the second circulation loop of a heat transfer fluid comprising: • a first circulation branch comprising, in the direction of circulation of the heat transfer fluid, a first pump, a first radiator arranged in an internal air flow and a battery heat exchanger, • a second circulation branch connected in parallel with the second radiator and comprising a second pump and an electric heating device for the heat transfer fluid, • a third circulation branch connected in parallel with the first pump and the battery heat exchanger es, said third circulation branch comprising the two-fluid heat exchanger.
    According to one aspect of the invention, the first reversible air conditioning loop comprises: • a first circulation pipe comprising, in the direction of circulation of the refrigerant, a compressor, a second radiator arranged in the internal air flow, a first device expansion, an evapo-condenser arranged in an external air flow, • a second circulation pipe connected in parallel with the evapo-condenser and comprising a second expansion device and an evaporator arranged in the internal air flow, • a third circulation pipe connecting the outlet of the evapo-condenser and the inlet of the second expansion device, and • a fourth circulation pipe connecting the inlet of the second expansion device and the inlet of the compressor, said third circulation line comprising a third expansion device and the two-fluid heat exchanger.
    According to another aspect of the invention, the first reversible air conditioning loop is configured to operate in a first cooling mode in which the refrigerant circulates successively in the compressor where it undergoes a pressure increase, the first radiator as the refrigerant crosses without exchange of heat energy with the internal air flow, the first expansion device that the refrigerant passes through without undergoing pressure loss, the evapo-condenser at the level of which the coolant releases heat energy into the outside air flow, the refrigerant then joins the second expansion device where the refrigerant undergoes a pressure loss via the third circulation line, the refrigerant then crosses the evaporator where it absorbs heat energy from the internal air flow before returning to the compressor.
    According to another aspect of the invention, the first reversible air conditioning loop is configured to operate in a heat pump mode in which the refrigerant circulates successively in the compressor where it undergoes a pressure increase, the first radiator at which the refrigerant transfers heat energy to the internal air flow, the first expansion device where it experiences a pressure loss, the evapo-condenser at which the refrigerant absorbs heat energy from the air flow outside before returning to the compressor.
    According to another aspect of the invention, at the first circulation loop, part of the refrigerant passes through the fourth circulation pipe, the refrigerant undergoing a pressure loss at the third expansion device, passing through the dual fluid heat exchanger at which it absorbs heat energy from the heat transfer fluid of the second circulation loop before joining the other part of the refrigerant upstream of the compressor.
    According to another aspect of the invention, the first circulation loop is configured to operate in a second cooling mode in which the refrigerant circulates successively in the compressor where it undergoes a pressure increase, the first radiator that the refrigerant passes through without exchange of heat energy with the internal air flow, the first expansion device that the refrigerant passes through without undergoing pressure loss, the evapo-condenser at which the coolant releases heat energy into the outside air flow, the refrigerant then passes through the third circulation line, passes through the third expansion device where the refrigerant undergoes a pressure loss, the refrigerant then crosses the two-fluid heat exchanger where it absorbs the heat energy from the heat transfer fluid before returning to the compressor.
    According to another aspect of the invention, the second circulation loop is configured to operate in a battery cooling mode in which the heat transfer fluid circulates successively in the second pump, the electric heating device that the heat transfer fluid passes through without being heated , the heat transfer fluid then circulating in the battery heat exchanger where it absorbs heat energy from the batteries before passing into the first pump, the coolant also circulating in the third circulation branch and thus passes through the heat exchanger dual fluid heat at which the heat transfer fluid transfers heat energy to the coolant.
    According to another aspect of the invention, the second circulation loop is configured to operate in a direct heating mode of the internal air flow in which the heat transfer fluid successively circulates in the second pump, the electric heating device at the level of which the heat transfer fluid is heated and the first radiator at which the heat transfer fluid heats the internal air flow.
    According to another aspect of the invention, the second circulation loop is configured to operate in a short operating mode in which the heat transfer fluid successively circulates in the first pump, the dual-fluid heat exchanger and the battery heat exchanger.
    According to another aspect of the invention, the second circulation loop is configured to operate in a mode for heating the passenger compartment and the batteries in which the heat-transfer fluid circulates successively in the second pump, the electric heating device at the level of which the heat transfer fluid is heated, • a first part of the heat transfer fluid then passing through the battery heat exchanger at which the heat transfer fluid heats the batteries and in the first pump, • a second part of the heat transfer fluid then passing through the first radiator at which the heat transfer fluid heats the internal air flow, the two parts of the heat transfer fluid joining upstream of the second pump. 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 a thermal management circuit according to a first embodiment, • Figures 2 to 18 show the thermal management circuit of Figure 1 according to different operating modes. • Figure 19 shows a schematic representation of a thermal management circuit according to a second embodiment, • Figure 20 shows the thermal management circuit of Figure 1 according to a particular mode of operation.
    In the various figures, identical elements have the same reference numbers.
    The following embodiments are examples. Although the description refers to one or more embodiments, this does not necessarily mean that each reference relates to the same embodiment, or that the characteristics apply only to a single embodiment. Simple features of different embodiments can also be combined and / or interchanged to provide other embodiments.
    In the present description, it is possible to index certain elements or parameters, such as for example first element or second element as well as first parameter and second parameter or even first criterion and second criterion etc. In this case, it is a simple indexing to differentiate and name elements or parameters or criteria 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 a thermal management circuit 1 of a hybrid or electric vehicle. This thermal management circuit 1 comprises a first reversible air conditioning loop A in which a refrigerant circulates and comprising a two-fluid heat exchanger 19 arranged jointly on a second circulation loop B of a heat transfer fluid.
    This second circulation loop B of a heat transfer fluid more particularly comprises a first circulation branch B 1 comprising, in the direction of circulation of the heat transfer fluid, a battery heat exchanger 47, a first pump 49 and a first radiator 45 arranged in a flow of internal air 100. The battery heat exchanger 47 is in particular a heat exchanger allowing the exchanges of heat energy between the batteries, more particularly the cells making up these batteries, and the heat transfer fluid circulating in the second circulation loop B The first radiator 45 is preferably arranged in a heating, ventilation and / or air conditioning device 110 through which the internal air flow 100 circulates.
    The second circulation loop B comprises a second circulation branch B2 connected in parallel with the second radiator 45. This second circulation branch B2 connects more specifically: • a first connection point 51 disposed upstream of the battery heat exchanger 47, between the first radiator 45 and said battery heat exchanger 47, and • a second connection point 52 disposed downstream of the first pump 49, between said first pump 49 and the first radiator 45,
    This second circulation branch B2 comprises in particular a second pump 41 and an electrical heating device 43 for the heat transfer fluid.
    The second circulation loop B also includes a third circulation branch B3 connected in parallel with the first pump 49 and the battery heat exchanger 47. This third circulation branch B3 more specifically connects: • a third connection point 53 arranged upstream of the battery heat exchanger 47, between the first connection point 51 and said battery heat exchanger 47, and • a fourth connection point 54 disposed downstream of the first pump 49, between said first pump 49 and the second connection point 52.
    This third circulation branch B3 notably comprises the two-fluid heat exchanger 19.
    The second circulation loop B also includes a device for redirection of the heat transfer fluid in order to define by which branch of circulation it circulates. In the example illustrated in FIG. 1, this device for redirection of the heat-transfer fluid comprises a first three-way valve 61 arranged at the first connection point 51 and a second three-way valve 62 arranged at the fourth connection point 54. It is however quite possible to imagine other means in order to define by which branch of circulation the heat transfer fluid circulates, such as for example stop valves strategically placed on the different branches of circulation Bl, B2 and B3 .
    The first reversible air conditioning loop A more particularly comprises a first circulation pipe A1 comprising, in the direction of circulation of the coolant, a compressor 3, a second radiator 5 disposed in the internal air flow 100, a first expansion device 7 , an evapo-condenser 9 disposed in an external air flow 200. The evapo-condenser 9 is thus generally disposed on the front face of the motor vehicle and the second radiator 5 in the heating, ventilation and / or air conditioning device 110. A shutter 120 can also be installed in the heating, ventilation and / or air conditioning device 110 in order to prevent or not the internal air flow 100 from passing through the second radiator 5. The first circulation pipe A1 can also include an accumulator 17 allowing a phase separation of the coolant and disposed upstream of the compressor 3, between the evapo-condenser 9 and the led it compressor 3.
    The first circulation loop A also comprises a second circulation pipe A2 connected in parallel with the evapo-condenser 9. This second circulation pipe A2 more particularly connects: a first junction point 31 disposed downstream of the second radiator 5, between said second radiator 5 and the first expansion device 7, and • a second junction point 32 disposed downstream of the evapo-condenser 9, between said evapo-condenser 9 and the compressor 3, more precisely upstream of the accumulator 17.
    This second circulation pipe A2 notably comprises a second expansion device 13 and an evaporator 11 disposed in the internal air flow 100.
    The first circulation loop A further comprises a third circulation pipe A3 connecting the outlet of the evapo-condenser 9 and the inlet of the second expansion device 13. This third circulation pipe A3 more particularly connects: • a third point junction 33 disposed downstream of the evapo-condenser 9, between said evapo-condenser 9 and the compressor 3, more precisely upstream of the accumulator 17, and • a fourth junction point 34 disposed on the second circulation pipe A2 upstream of the second expansion device 13, between the first junction point 31 and the second expansion device 13.
    The first circulation loop A also includes a fourth circulation pipe A4 connecting the inlet of the second expansion device 13 and the inlet of the compressor 3. This fourth circulation pipe A4 precisely connects: • a fifth junction point 35 disposed on the second circulation pipe A2 upstream of the second expansion device 13, between the fourth junction point 34 of the third circulation pipe A3 and said second expansion device 13, and • a sixth junction point 36 disposed upstream of the compressor 3, between the second junction point 32 of the second circulation line A2 and the compressor 3, more precisely upstream of the accumulator 17.
    The third circulation pipe A4 comprises in particular a third expansion device 21 and the two-fluid heat exchanger 19. The third expansion device 21 being arranged upstream of the two-fluid heat exchanger 19, between the fifth junction point 35 and said two-fluid heat exchanger 19.
    The first circulation loop A also includes a device for redirecting the refrigerant in order to define by which circulation pipe it circulates. In the example illustrated in FIG. 1, this device for redirecting the refrigerant fluid comprises in particular: • a first stop valve 23 disposed on the second circulation pipe A2 between the first junction point 31 and the fourth junction point 34 , • a second stop valve 24 disposed on the first circulation pipe
    Al between the third junction point 33 and the second junction point 32, • a non-return valve 25 disposed on the third circulation pipe A3, arranged so as to prevent the circulation of coolant from the fourth junction point 34 to the third junction point 33.
    The first 7, second 13 and third 21 expansion devices, for their part, have a stop function making it possible to prevent the coolant from passing through them.
    However, it is quite possible to imagine other means in order to define by which circulation line the refrigerant circulates, such as for example three-way valves strategically placed on junction points.
    The thermal management circuit 1 as described above is capable of operating according to different operating modes illustrated in FIGS. 2 to 18. In these operating modes, only the elements through which the various fluids pass are shown. 1) cooling of the passenger compartment alone
    Figures 2 and 3 show the thermal management circuit 1 according to an operating mode in which only the passenger compartment is cooled.
    As illustrated in FIGS. 2 and 3, the first circulation loop A is in a first cooling mode in which the cooling fluid circulates successively in: • the compressor 3, where it undergoes a pressure increase, • the first radiator 5 that the refrigerant passes through without exchange of heat energy with the internal air flow 100, for example because the shutter 120 is closed, • the first expansion device 7 which the coolant passes through without undergoing pressure loss, for example the fact that at its maximum opening the first expansion device 7 can allow the coolant to pass without loss of pressure, • the evapo-condenser 9 at which the coolant releases heat energy into the outside air flow 200, • the third circulation pipe A3, • the second expansion device 13 where the refrigerant undergoes a pressure loss, • the evapo rator 11 where the refrigerant absorbs heat energy from the internal air flow 100 before returning to the compressor 3.
    In order for the refrigerant to follow this stroke, the first 23 and second 24 stop valves are closed and the third expansion device 21 blocks the circulation of the refrigerant in the fourth circulation pipe A4. In the example illustrated in Figure 2, only the first circulation loop A is in operation. The second traffic loop B is stopped.
    In the example illustrated in FIG. 3, the second circulation loop B is running and it is in a so-called short operating mode. In this short operating mode, the heat transfer fluid successively circulates in the first pump 49, the dual-fluid heat exchanger 19 and the battery heat exchanger 47.
    In the case illustrated in FIG. 3, the heat transfer fluid cannot exchange heat energy with the coolant because the latter does not circulate in the fourth circulation pipe A4. Circulating the heat transfer fluid according to this short operating mode nevertheless makes it possible to homogenize the temperature within the batteries so that the different cells which compose them are at the same temperature.
    This short operating mode without heat exchange at the two-fluid heat exchanger 19 can also be used without the first circulation loop A being in operation. 2) cooling of the passenger compartment and batteries:
    Figures 4 and 5 show the thermal management circuit 1 according to operating modes in which the passenger compartment and the batteries are cooled. For this, the first circulation loop A and the second circulation loop B are in operation.
    Whether in FIG. 4 or in FIG. 5, the first circulation loop A is in the first cooling mode such as that described above, with the difference that part of the refrigerant passes through the fourth circulation pipe A4. This part of the refrigerant undergoes a pressure loss at the third expansion device 21 and passes through the two-fluid heat exchanger 19 at which it absorbs heat energy from the heat transfer fluid of the second circulation loop B before joining the other part of the refrigerant upstream of the compressor 3.
    In this mode of cooling the passenger compartment and the batteries, the part of the refrigerant passing through the fourth circulation pipe A4 comes from the third circulation pipe A3, more precisely coming from the evapo-condenser 9.
    As shown in Figures 4a and 4b, the second circulation loop B is configured to operate in a battery cooling mode. In this mode of cooling the batteries, the heat transfer fluid circulates successively in the second pump 41 and the electric heating device 43, which the heat transfer fluid passes through without being heated, in particular because the latter is not supplied with electricity and therefore does not produce heat.
    The heat transfer fluid then circulates in the battery heat exchanger 47 where it absorbs heat energy from the batteries before passing into the first pump 49.
    The refrigerant also circulates in the third circulation branch B3 and thus passes through the two-fluid heat exchanger 19 at which the heat transfer fluid transfers heat energy to the refrigerant.
    The fact that the heat transfer fluid is propelled by both the first 49 and the second pump 41 allows a control of the flow of the heat transfer fluid passing through the two-fluid heat exchanger 19 and the battery heat exchanger 47. Indeed, the second pump 41 makes it possible to define and control the flow of heat transfer fluid passing through the two-fluid heat exchanger 19 and the first pump 49 makes it possible to define and control the flow of heat transfer fluid passing through the battery heat exchanger 47. It is thus possible by controlling these heat transfer fluid flows, to precisely control the cooling capacity of the batteries. Generally, the flow of heat transfer fluid passing through the two-fluid heat exchanger 19 is less than the flow of heat transfer fluid passing through the battery heat exchanger 47.
    In the example of FIG. 4a, at the third junction point 53, a first part of the refrigerant passes through the battery heat exchanger 47 and the first pump 49. The other part of the refrigerant passes in turn in the third circulation branch B3 and thus passes through the two-fluid heat exchanger 19 at which the heat transfer fluid transfers heat energy to the refrigerant. The two parts of the refrigerant meet at the fourth junction point 54. This is in particular possible by the reuse in this example of a second three-way valve 62 called convergent. In this example, the flow rate of the refrigerant fluid given by the second pump 41 is then equal to the sum of the flow rate of the coolant fluid at the battery heat exchanger 47 and the flow rate of the coolant fluid at the heat exchanger bifluid 19. It is then possible to control the flow in the bifluid heat exchanger 19 and in the battery exchanger 47 by controlling the flow of the second pump 41.
    In the example of FIG. 4b, at the fourth junction point 54, a first part of the refrigerant passes through the second pump 41 and the electric heating device 43, which the heat transfer fluid passes through without being heated. The other part of the refrigerant passes through the third circulation branch B3 and thus passes through the two-fluid heat exchanger 19 at which the heat transfer fluid transfers heat energy to the refrigerant. The two parts of the refrigerant meet at the third junction point 53. This is in particular possible by the use in this example of a second three-way valve 62 said to be divergent. In this example, the flow rate of the refrigerant fluid given by the first pump 49 is then equal to the sum of the flow rate of the coolant fluid at the two-fluid heat exchanger 19 and the flow rate of the coolant fluid given by the second pump 41. Here , the flow rate in the battery heat exchanger 47 is controlled by the flow rate of the first pump 49 and the flow rate in the dual-fluid heat exchanger 19 by the difference in flow rate between the first 49 and the second 41 pump.
    As shown in FIG. 5, the second circulation loop B can on the contrary operate according to a short operating mode described above in which the heat transfer fluid circulates successively in the first pump 49, the two-fluid heat exchanger 19 and the exchanger heat batteries 47.
    In the case illustrated in FIG. 4, at the level of the battery heat exchanger 47, the heat transfer fluid absorbs heat energy coming from the batteries. This heat energy is then transferred to the refrigerant at the two-fluid heat exchanger. 3) cooling of the batteries alone:
    Figures 6 and 7 show the thermal management circuit 1 according to an operating mode in which only the batteries are cooled.
    As illustrated in FIGS. 6 and 7, the first circulation loop A is in a second cooling mode in which the coolant circulates successively in: • the compressor 3, where it undergoes a pressure increase, • the first radiator 5 that the refrigerant passes through without exchange of heat energy with the internal air flow 100, for example because the shutter 120 is closed, • the first expansion device 7 which the coolant passes through without undergoing pressure loss, for example the fact that at its maximum opening the first expansion device 7 can allow the coolant to pass without loss of pressure, • the evapo-condenser 9 at which the coolant releases heat energy into the outside air flow 200, • the third circulation pipe A3, • the third expansion device 21 where the refrigerant undergoes a pressure loss, • the ec two-fluid heat hanger 19 where the refrigerant absorbs heat energy from the heat transfer fluid before returning to the compressor 3.
    In the example illustrated in FIG. 6, the second circulation loop B is in its short operating mode and the heat transfer fluid circulates successively in the first pump 49, the dual-fluid heat exchanger 19 and the battery heat exchanger 47 The heat transfer fluid absorbs heat energy from the batteries and this heat energy is then transferred to the coolant at the level of the two-fluid heat exchanger 19.
    As shown in Figures 7a and 7b, the second circulation loop B is configured to operate in its battery cooling mode. In this mode of cooling the batteries, the heat transfer fluid circulates successively in the second pump 41 and the electric heating device 43, which the heat transfer fluid passes through without being heated, in particular because the latter is not supplied with electricity and therefore does not produce heat.
    The heat transfer fluid then circulates in the battery heat exchanger 47 where it absorbs heat energy from the batteries before passing into the first pump 49.
    The refrigerant also circulates in the third circulation branch B3 and thus passes through the two-fluid heat exchanger 19 at which the heat transfer fluid transfers heat energy to the refrigerant.
    As before, the fact that the heat transfer fluid is propelled by both the first 49 and the second pump 41 allows a control of the flow of the heat transfer fluid passing through the two-fluid heat exchanger 19 and the battery heat exchanger 47. Indeed , the second pump 41 makes it possible to define and control the flow of heat transfer fluid passing through the two-fluid heat exchanger 19 and the first pump 49 makes it possible to define and control the flow of heat transfer fluid passing through the battery heat exchanger 47. it is thus possible by controlling these heat transfer fluid flows, to precisely control the cooling capacity of the batteries. Generally, the flow of heat transfer fluid passing through the two-fluid heat exchanger 19 is less than the flow of heat transfer fluid passing through the battery heat exchanger 47.
    In the example of FIG. 7a, at the third junction point 53, a first part of the refrigerant passes through the battery heat exchanger 47 and the first pump 49. The other part of the refrigerant passes in turn in the third circulation branch B3 and thus passes through the two-fluid heat exchanger 19 at which the heat transfer fluid transfers heat energy to the refrigerant. The two parts of the refrigerant meet at the fourth junction point 54. This is in particular possible by the reuse in this example of a second three-way valve 62 called convergent. In this example, the flow rate of the refrigerant fluid given by the second pump 41 is then equal to the sum of the flow rate of the coolant fluid at the battery heat exchanger 47 and the flow rate of the coolant fluid at the heat exchanger bifluid 19. It is then possible to control the flow in the bifluid heat exchanger 19 and in the battery exchanger 47 by controlling the flow of the second pump 41.
    In the example of FIG. 7b, at the fourth junction point 54, a first part of the refrigerant passes through the second pump 41 and the electric heating device 43, which the heat transfer fluid passes through without being heated. The other part of the refrigerant passes through the third circulation branch B3 and thus passes through the two-fluid heat exchanger 19 at which the heat transfer fluid transfers heat energy to the refrigerant. The two parts of the refrigerant meet at the third junction point 53. This is in particular possible by the use in this example of a second three-way valve 62 said to be divergent. In this example, the flow rate of the refrigerant fluid given by the first pump 49 is then equal to the sum of the flow rate of the coolant fluid at the two-fluid heat exchanger 19 and the flow rate of the coolant fluid given by the second pump 41. Here , the flow rate in the battery heat exchanger 47 is controlled by the flow rate of the first pump 49 and the flow rate in the dual-fluid heat exchanger 19 by the difference in flow rate between the first 49 and the second 41 pump. 4) heating of the passenger compartment alone:
    Figures 8 to 10 show the thermal management circuit 1 according to an operating mode in which only the passenger compartment is heated.
    As illustrated in FIGS. 8 to 10, the first circulation loop A is in a heat pump mode in which the coolant circulates successively in: • the compressor 3 where the coolant undergoes a pressure increase, • the first radiator 5 at the level of which the refrigerant transfers heat energy to the internal air flow 100, for example because the flap 120 is open, • the first expansion device 7 where the refrigerant undergoes a pressure loss, • l 'Evapo-condenser 9 at which the refrigerant absorbs heat energy from the outside air flow 200 before returning to the compressor 3.
    In order for the coolant to follow this stroke, the first stop valve 23 is closed, the second 13 and third 21 expansion devices block the circulation of the coolant and the second stop valve 24 is open.
    In the example illustrated in Figure 8, only the first circulation loop A is in operation. The second traffic loop B is stopped.
    In the example illustrated in FIG. 9, the second circulation loop B is in operation and is in its short operating mode in which the heat-transfer fluid circulates successively in the first pump 49, the dual-fluid heat exchanger 19 and the battery heat exchanger 47.
    In the case illustrated in FIG. 9, the heat transfer fluid cannot exchange heat energy with the coolant because the latter does not circulate in the fourth circulation pipe A4. Circulating the heat transfer fluid in this short operating mode makes it possible to homogenize the temperature within the batteries so that the different cells that compose them are at the same temperature.
    As shown in FIG. 10, the second circulation loop B can also be in a direct heating mode of the internal air flow 100. For this, the heat transfer fluid circulates successively in the first pump 41, the electric heating device 43 which is in operation and heats the heat transfer fluid and in the first radiator 45 at which the heat transfer fluid releases heat energy into the internal air flow 100.
    As always shown in FIG. 10, this direct heating mode of the second circulation loop B can be simultaneous with its short operating mode. There are then two separate circulation circuits of the heat transfer fluid within the second circulation loop B. 51 heating of the passenger compartment and of the batteries:
    Figure 11 shows the thermal management circuit 1 according to an operating mode in which the passenger compartment and the batteries are heated. For this, the first circulation loop A and the second circulation loop B are in operation.
    The first circulation loop A is more particularly in its heat pump mode in order to heat the internal air flow 100 via the second radiator 5.
    The second circulation loop B is in a mode for heating the passenger compartment and the batteries. In this mode of heating the passenger compartment and the batteries, the heat transfer fluid circulates successively in the second pump 41 and the electric heating device 43 at which the heat transfer fluid is heated.
    At the outlet of the electric heating device 43, a first part of the heat transfer fluid passes through the battery heat exchanger 47 at which the heat transfer fluid heats the batteries and into the second pump 41.
    At the outlet of the electric heating device 43, a second part of the heat transfer fluid passes through the first radiator 45 at the level of which the heat transfer fluid heats the internal air flow 100.
    These two parts of the heat transfer fluid meet upstream of the second pump 41.
    In this mode of heating the passenger compartment and the batteries, the heat transfer fluid does not circulate in the third circulation branch B3 and therefore does not pass through the two-fluid heat exchanger 19. 6) heating of the passenger compartment and cooling of the batteries :
    Figures 12 to 14 show the thermal management circuit 1 according to an operating mode in which only the passenger compartment is heated and where the batteries are cooled. For this, the first circulation loop A and the second circulation loop B are in operation.
    The first circulation loop A is in its heat pump mode such as that described above, with the difference that part of the refrigerant passes through the fourth circulation pipe A4. This part of the refrigerant undergoes a pressure loss at the third expansion device 21 and passes through the two-fluid heat exchanger 19 at which it absorbs heat energy from the heat transfer fluid of the second circulation loop B before joining the other part of the refrigerant upstream of the compressor 3.
    In this mode of heating the passenger compartment and cooling the batteries illustrated in FIGS. 12 to 14, the part of the coolant passing through the fourth circulation pipe A4 does not come from the third circulation pipe A3 but from the second circulation pipe A4, more precisely from the second radiator 5.
    In order for the refrigerant to follow this stroke, the first 23 and second 24 stop valves are open and only the second expansion device 13 blocks the circulation of the refrigerant.
    As illustrated in FIG. 12, the second circulation loop B can be configured to operate in its mode of cooling the batteries in which the heat transfer fluid circulates successively in the second pump 41 and the electric heating device 43, which the heat transfer fluid passes through. without being heated, in particular because the latter is not supplied with electricity and therefore does not produce heat.
    A first part of the heat transfer fluid then passes through the third circulation branch B3 and thus passes through the two-fluid heat exchanger 19 at which the heat transfer fluid transfers heat energy to the refrigerant.
    A second part of the heat transfer fluid passes through the battery heat exchanger 47 where it absorbs heat energy from the batteries before passing into the first pump 49.
    The two parts of heat transfer fluid meet upstream of the second pump 41.
    The fact that the heat transfer fluid is propelled by both the first 49 and the second pump 41 allows a control of the flow rate of the heat transfer fluid passing through the two-fluid battery heat exchanger 19 and the battery heat exchanger 47. Indeed, the second pump 41 makes it possible to define and control the flow of heat transfer fluid passing through the two-fluid heat exchanger 19 and the first pump 49 makes it possible to define and control the flow of heat transfer fluid passing through the battery heat exchanger 47. It is thus possible by controlling these heat transfer fluid flows, precisely controlling the cooling capacity of the batteries. Generally, the flow of heat transfer fluid passing through the two-fluid heat exchanger 19 is less than the flow of heat transfer fluid passing through the battery heat exchanger 47.
    As shown in FIG. 13, the second circulation loop B can on the contrary operate according to a short operating mode described above in which the heat transfer fluid circulates successively in the first pump 49, the two-fluid heat exchanger 19 and the exchanger heat batteries 47.
    In the case illustrated in FIG. 13, at the level of the battery heat exchanger 47, the heat transfer fluid absorbs heat energy from the batteries.
    This heat energy is then transferred to the refrigerant at the two-fluid heat exchanger.
    As shown in FIG. 14, in order to increase the heating capacity of the internal air flow 100, when the second circulation loop B operates in its short operating mode, the second circulation loop B can also be in a mode direct heating of the internal air flow 100. For this, the heat transfer fluid successively circulates in the first pump 41, the electric heater 43 which is in operation and heats the heat transfer fluid and in the first radiator 45 at which the heat transfer fluid releases heat energy into the internal air flow 100. There are then two separate circulation loops of the heat transfer fluid within the second circulation loop B.
    In this mode of heating the passenger compartment and cooling the batteries, the heat energy recovered from the batteries by the heat transfer fluid and transmitted to the refrigerant fluid is used in particular to heat the internal air flow 100 via the second radiator 5. 71 strict electric heating of the batteries:
    FIG. 15 shows the thermal management circuit 1 according to a strict electric heating mode of the batteries in which only the second circulation loop B is in operation.
    In this strict electric heating mode of the batteries, the heat transfer fluid circulates successively in the second pump 41, the electric heater 43 at the level of which the heat transfer fluid is heated, the battery heat exchanger 47 at which the heat transfer fluid heats up The batteries. The heat transfer fluid then passes through the first pump 49 before joining the second pump 41.
    This strict mode of electric heating of the batteries can in particular be useful when the electric or hybrid vehicle is charging, for example connected to a charging station, so that the batteries are at an optimal temperature so that their charging is the most rapid and efficient. possible. 8) strict electric heating of the passenger compartment and batteries:
    FIG. 16 shows the thermal management circuit 1 according to a strict electric heating mode for the passenger compartment and the batteries in which only the second circulation loop B is in operation.
    In this strict electric heating mode for the passenger compartment and the batteries, the heat transfer fluid circulates successively in the second pump 41 and the electric heating device 43 at which the heat transfer fluid is heated.
    A first part of the heat transfer fluid then passes through the battery heat exchanger 47 at which the heat transfer fluid heats the batteries. The heat transfer fluid then passes through the first pump 49.
    A second part of the heat transfer fluid passes through the first radiator 45 at which the heat transfer fluid heats the internal air flow 100.
    The two parts of the heat transfer fluid meet upstream of the second pump 41.
    This strict electric heating mode for the passenger compartment and the batteries can be particularly useful when the electric or hybrid vehicle is charging, for example connected to a charging station, so that the batteries are at an optimal temperature so that their charging is as fast and efficient as possible while warming the passenger compartment, especially when the outside temperature is below 0 ° C. 9) interior heating with heat recovery:
    Figures 17 and 18 show the thermal management circuit 1 according to an operating mode in which the passenger compartment is heated with heat recovery. In this operating mode, the second circulation loop B can in particular be in its so-called short operating mode. In this short operating mode, the heat transfer fluid successively circulates in the first pump 49, the dual-fluid heat exchanger 19 and the battery heat exchanger 47.
    In the case illustrated in FIGS. 17 and 18, the coolant cannot exchange heat energy with the coolant because the latter does not circulate in the fourth circulation pipe A4. Circulating the heat transfer fluid according to this short operating mode nevertheless makes it possible to homogenize the temperature within the batteries so that the different cells which compose them are at the same temperature.
    In addition, in order to increase the heating capacity of the internal air flow 100, the second circulation loop B can also be in a direct heating mode of the internal air flow 100. For this, the heat transfer fluid circulates successively in the first pump 41, the electric heating device 43 which is in operation and heats the heat transfer fluid and in the first radiator 45 at the level of which the heat transfer fluid releases heat energy into the internal air flow 100. There is then two separate circulation circuits of the heat transfer fluid within the second circulation loop B.
    As shown in Figure 17, the first circulation loop A can operate according to a first heat recovery mode in which the refrigerant circulates successively in: • the compressor 3 where it undergoes a pressure increase, • the first radiator 5 at level at which the refrigerant transfers heat energy to the internal air flow 100, • a first part of the refrigerant passes through the first expansion device 7 where it undergoes a pressure loss and the evapo-condenser 9 at the level from which the refrigerant absorbs heat energy from the external air flow 200, • a second part of the refrigerant passing through the second expansion device 13 where it experiences a pressure loss and the evaporator 11 at which the fluid refrigerant absorbs heat energy from the internal air flow 100.
    The two parts of the coolant meet upstream of the compressor 3. In order for the coolant to follow this stroke, the first 23 and second 24 stop valves are open and only the third expansion device 21 blocks the circulation of the coolant.
    This first heat recovery mode is particularly useful for an outside temperature between 10 and 25 ° C. and when the internal air flow 100 comes from a recirculation of the air present in the passenger compartment.
    As shown in Figure 18, the first circulation loop A can operate according to a second heat recovery mode in which the refrigerant circulates successively in: • the compressor 3 where it undergoes a pressure increase, • the first radiator 5 at level at which the refrigerant transfers heat energy to the internal air flow 100, • the first expansion device 7 where the refrigerant undergoes a first pressure loss, • the evapo-condenser 9 at which the refrigerant absorbs heat energy from the outside air flow 200, • the third circulation pipe A3, • the second expansion device 13 where the refrigerant undergoes a second pressure loss, • the refrigerant then passes through the evaporator 11 at which it absorbs heat energy from the internal air flow 100 before returning to the compressor 3.
    In order for the refrigerant to follow this stroke, the first 23 and second 24 stop valves are closed and only the third expansion device 21 blocks the circulation of the refrigerant.
    This second heat recovery mode is particularly useful for an outside temperature between 0 and 10 0 and when the internal air flow 100 comes from a recirculation of the air present in the passenger compartment.
    FIG. 19 shows the thermal management circuit 1 according to a particular embodiment in which the first A and the second B circulation loop are identical to those of FIG. 1 with the difference that the thermal management circuit 1 comprises a heat exchanger additional two-fluid heat 20 arranged jointly on the first A and the second B circulation loop.
    This additional dual-fluid heat exchanger 20 is disposed on the first circulation loop A downstream of the compressor 3, between said compressor 3 and the second radiator 5. The additional dual-fluid heat exchanger 20 is disposed on the second circulation loop B on the first circulation branch B1, downstream of the first compressor 49, more precisely between the second connection point 52 of the second circulation branch B2 and the first radiator 45.
    This particular embodiment allows the thermal management circuit 1 to operate in a particular operating mode for heating the batteries, illustrated in FIG. 20.
    In this particular mode of heating the batteries, at the level of the first circulation loop A, the refrigerant passes successively through: • the compressor 3 at which it undergoes a pressure increase, • the additional dual-fluid heat exchanger 20 at which the refrigerant transfers heat energy to the heat transfer fluid, • the second radiator 5 through which the refrigerant passes without exchanging heat with the internal air flow 100, for example because shutter 120 is closed, • the first expansion device 7 where the refrigerant undergoes a pressure loss, • the evapo-condenser 9 at which the refrigerant absorbs heat energy from the outside air flow 200 before returning to the compressor 3.
    At the second circulation loop B, the heat transfer fluid successively circulates in: • the first pump 49, • the additional dual-fluid heat exchanger 20 at which the heat transfer fluid recovers heat energy from the refrigerant, • the first radiator 45 which the refrigerant passes through without exchanging heat with the internal air flow 100, for example because shutter 120 is closed and also blocks the circulation of the internal air flow 100 upstream of the first radiator 45, • the battery heat exchanger 47 at which the heat transfer fluid releases the heat energy gained to heat the batteries.
    Here, the heat transfer fluid does not pass into the second B2 and third B3 circulation branches.
    Thus, it can be seen that due to its particular architecture, the thermal management circuit 1 makes it possible to directly heat the batteries via the electric heating device 43. In addition, it is also possible to dissociate the heating or cooling of the batteries with that of the passenger compartment.
    权利要求:
    Claims (10)
    [1" id="c-fr-0001]
    1. Thermal management circuit (1) of a hybrid or electric vehicle, said thermal management circuit (1) comprising a first reversible air conditioning loop (A) in which a refrigerant circulates and comprising a dual-fluid heat exchanger (19 ) arranged jointly on a second circulation loop (B) of a heat transfer fluid, the second circulation loop (B) of a heat transfer fluid comprising: • a first circulation branch (Bl) comprising in the direction of circulation of the fluid coolant, a first pump (49), a first radiator (45) arranged in an internal air flow (100) and a battery heat exchanger (47), • a second circulation branch (B2) connected in parallel with the second radiator (45) and comprising a second pump (41) and an electric heating device (43) for the heat transfer fluid, • a third circulation branch (B 3) connected in parallel with the first pump (49) and the battery heat exchanger (47), said third circulation branch (B3) comprising the dual-fluid heat exchanger (19).
    [2" id="c-fr-0002]
    2. Thermal management circuit according to the preceding claim, characterized in that the first reversible air conditioning loop (A) comprises: • a first circulation pipe (Al) comprising, in the direction of circulation of the refrigerant, a compressor (3) , a second radiator (5) arranged in the internal air flow (100), a first expansion device (7), an evapo-condenser (9) arranged in an external air flow (200), • a second circulation pipe (A2) connected in parallel with the evaporator-condenser (9) and comprising a second expansion device (13) and an evaporator (11) arranged in the internal air flow (100), • a third pipe circulation (A3) connecting the outlet of the evapo-condenser (9) and the inlet of the second expansion device (13), and • a fourth circulation pipe (A4) connecting the inlet of the second expansion device ( 13) and the compressor input (3), the said e third circulation line (A4) comprising a third expansion device (21) and the two-fluid heat exchanger (19).
    [3" id="c-fr-0003]
    3. Thermal management circuit (1) according to claim 2, characterized in that the first reversible air conditioning loop (A) is configured to operate in a first cooling mode in which the refrigerant circulates successively in the compressor (3) where it undergoes an increase in pressure, the first radiator (5) that the refrigerant passes through without exchange of heat energy with the internal air flow (100), the first expansion device (7) that the refrigerant passes through without undergo pressure loss, the evapo-condenser (9) at the level of which the refrigerant releases heat energy into the external air flow (200), the refrigerant then joins the second expansion device (13) where the refrigerant undergoes a pressure loss via the third circulation line (A3), the refrigerant then crosses the evaporator (11) where it absorbs energy heat transfer of the internal air flow (100) before returning to the compressor (3).
    [4" id="c-fr-0004]
    4. Thermal management circuit (1) according to claim 2, characterized in that the first reversible air conditioning loop (A) is configured to operate in a heat pump mode in which the refrigerant circulates successively in the compressor (3) where it undergoes an increase in pressure, the first radiator (5) at the level of which the refrigerant transfers heat energy to the internal air flow (100), the first expansion device (7) where it undergoes a loss of pressure, the evapo-condenser (9) at which the refrigerant absorbs heat energy from the outside air flow (200) before returning to the compressor (3).
    [5" id="c-fr-0005]
    5. Thermal management circuit (1) according to one of claims 3 or 4, characterized in that at the first circulation loop (A), part of the coolant passes through the fourth circulation pipe (A4 ), the refrigerant undergoing a pressure loss at the third expansion device (21), passing through the dual-fluid heat exchanger (19) at which it absorbs heat energy from the heat transfer fluid of the second circulation loop (B) before joining the other part of the refrigerant upstream of the compressor (3).
    [6" id="c-fr-0006]
    6. Thermal management circuit (1) according to claim 2, characterized in that the first circulation loop (A) is configured to operate in a second cooling mode in which the coolant circulates successively in the compressor (3) where it undergoes an increase in pressure, the first radiator (5) that the refrigerant passes through without exchange of heat energy with the internal air flow (100), the first expansion device (7) that the refrigerant passes through without undergoing pressure loss, the evapo-condenser (9) at the level of which the refrigerant releases heat energy into the external air flow (200), the refrigerant then passes into the third circulation pipe (A3) , passes into the third expansion device (Î3) where the refrigerant undergoes a pressure loss, the refrigerant then passes through the dual-fluid heat exchanger (19) where it absorbs heat energy from the heat transfer fluid before returning to the compressor (3).
    [7" id="c-fr-0007]
    7. Thermal management circuit (1) according to one of claims 5 or 6, characterized in that the second circulation loop (B) is configured to operate in a battery cooling mode in which the heat transfer fluid successively circulates in the second pump (41), the electric heating device (43) which the heat transfer fluid passes through without being heated, the heat transfer fluid then circulates in the heat exchanger batteries (47) where it absorbs heat energy from the batteries before passing through the first pump (49), the refrigerant also circulates in the third circulation branch (B 3) and thus passes through the two-fluid heat exchanger (19) at which the heat transfer fluid transfers heat energy with refrigerant.
    [8" id="c-fr-0008]
    8. Thermal management circuit (1) according to one of claims 1, 2 or 4 or according to claim 5 in combination with claim 4, characterized in that the second circulation loop (B) is configured to operate in a direct heating mode of the internal air flow (100) in which the heat transfer fluid successively circulates in the second pump (41), the electric heating device (43) at which the heat transfer fluid is heated and the first radiator (45 ) at which the heat transfer fluid heats the internal air flow (100).
    [9" id="c-fr-0009]
    9. Thermal management circuit (1) according to one of claims 1 to 6 or 8 characterized in that the second circulation loop (B) is configured to operate in a short operating mode in which the heat transfer fluid circulates successively in the first pump (49), the dual fluid heat exchanger (19) and the battery heat exchanger (47).
    [10" id="c-fr-0010]
    10. Thermal management circuit (1) according to claim 4 or according to claim 5 in combination with claim 4, characterized in that the second circulation loop (B) is configured to operate in a heating mode of the passenger compartment. and batteries in which the heat transfer fluid successively circulates in the second pump (41), the electric heating device (43) at which the heat transfer fluid is heated, • a first part of the heat transfer fluid then passing through the heat exchanger batteries (47) at which the heat transfer fluid heats the batteries and in the first pump (49), • a second part of the heat transfer fluid then passing into the first radiator (45) at which the heat transfer fluid heats the air flow internal (100), the two parts of the heat transfer fluid joining upstream of the second pump (41).
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    同族专利:
    公开号 | 公开日
    FR3074272B1|2019-10-18|
    CN111788437A|2020-10-16|
    US20210031588A1|2021-02-04|
    WO2019106258A1|2019-06-06|
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    法律状态:
    2018-11-29| PLFP| Fee payment|Year of fee payment: 2 |
    2019-05-31| PLSC| Publication of the preliminary search report|Effective date: 20190531 |
    2019-11-29| PLFP| Fee payment|Year of fee payment: 3 |
    2020-11-30| PLFP| Fee payment|Year of fee payment: 4 |
    2021-11-30| PLFP| Fee payment|Year of fee payment: 5 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1761296|2017-11-28|
    FR1761296A|FR3074272B1|2017-11-28|2017-11-28|THERMAL MANAGEMENT CIRCUIT OF A HYBRID OR ELECTRIC VEHICLE|FR1761296A| FR3074272B1|2017-11-28|2017-11-28|THERMAL MANAGEMENT CIRCUIT OF A HYBRID OR ELECTRIC VEHICLE|
    US16/767,618| US20210031588A1|2017-11-28|2018-11-16|Circuit for the thermal management of a hybrid or electric vehicle|
    CN201880085666.8A| CN111788437A|2017-11-28|2018-11-16|Circuit for thermal management of a hybrid or electric vehicle|
    PCT/FR2018/052893| WO2019106258A1|2017-11-28|2018-11-16|Circuit for the thermal management of a hybrid or electric vehicle|
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