Heat transfer fluid circuit for a heat treatment system

Abstract

Heat transfer fluid circuit for a heat treatment system. The present invention relates to a heat transfer fluid circuit (2), comprising: a main branch (4) extending between a convergence zone (7) and a divergence zone (8), a first loop (9) comprising a main section (10) and a secondary section (11), the main section (10) being provided with a first control device (14) configured to circulate the heat transfer fluid to the convergence zone (7) or to the secondary section (11), a second loop (23) controlled by a second control device (27) configured to circulate the heat transfer fluid to the second loop (23) or to the convergence zone (7), a third loop (31) comprising a third control device (35) configured to circulate the heat transfer fluid to the third loop (31) or to the convergence zone (7). (Figure 1)

Description

Title of the invention: Heat transfer fluid circuit for a heat treatment system

[0001] The present invention relates to the field of heat treatment systems of a motor vehicle, and more particularly concerns a heat transfer circuit integrated into such heat treatment systems.

[0002] Motor vehicles are commonly equipped with a refrigerant circuit and at least one heat transfer fluid circuit, both used to contribute to the thermal treatment of different areas or components of the vehicle. It is particularly known to use the refrigerant circuit and / or the heat transfer fluid circuit to thermally treat an airflow sent into the passenger compartment of a vehicle equipped with such a circuit. This thermal treatment is achieved, in particular, by circulating the refrigerant within a ventilation, heating, and / or air conditioning system installed in the vehicle.

[0003] In another application of this circuit, it is known to use the heat transfer fluid circuit to cool components of the vehicle's powertrain, such as, for example, an electrical storage device, the latter being used to supply energy to an electric motor capable of propelling the vehicle. The heat treatment system thus provides the energy needed to cool the electrical storage device during its use in driving phases.

[0004] Several refrigerants have been used for this type of heat treatment system, such as R134a or R1234yf. However, following new European standards, these refrigerants have been banned from use in Europe due to their environmental harmfulness. For future heat treatment systems, it has therefore been decided to use R290 as the refrigerant. However, R290 is pure propane. As a safety precaution, it is therefore essential to avoid circulating propane directly in the ventilation, heating, and / or air conditioning system. Thus, the vehicle's interior is heated indirectly by the refrigerant, and only the heat transfer fluid circulates within the ventilation, heating, and / or air conditioning system.

[0005] Such a condition leads to rethinking the configuration of the heat treatment system, in particular in order to design a heat transfer fluid circuit combining compactness, simplicity and multiple heat treatment functions.

[0006] In order to meet these objectives, the present invention proposes a heat transfer fluid circuit for a vehicle heat treatment system, intended to be traversed by a heat transfer fluid, comprising: - a main branch comprising a first heat exchanger configured to perform heat exchange between the heat transfer fluid and an outside airflow, and extending between a convergence zone and a divergence zone, - a first loop comprising a main section and a secondary section, the main section starting at the divergence zone and being equipped with a second heat exchanger configured to thermally treat an electric motor of the vehicle, a first pumping device and a first control device, the first control device being configured to circulate the heat transfer fluid to the convergence zone or to the secondary section, the secondary section comprising a second pumping device, a third heat exchanger configured to operate a heat exchange between the heat transfer fluid and a refrigerant circulating in a refrigerant circuit and a fourth heat exchanger configured to thermally treat an electrical storage device of the vehicle, - a second loop comprising a fifth heat exchanger configured to perform heat exchange between the heat transfer fluid and the refrigerant circulating in the refrigerant circuit, a third pumping device and a sixth heat exchanger configured to perform heat exchange between the heat transfer fluid and an interior airflow intended to be sent into the vehicle's passenger compartment, the second loop being placed under the control of a second control device configured to circulate the heat transfer fluid towards the second loop to the sixth heat exchanger or to the convergence zone via a junction branch, - a third loop comprising a seventh heat exchanger configured to operate a heat exchange between the heat transfer fluid and the refrigerant circulating in the refrigerant circuit, a fourth pumping device, a third control device and an eighth heat exchanger configured to operate a heat exchange between the heat transfer fluid and the interior airflow intended to be sent into the vehicle's passenger compartment, the third control device being configured to circulate the heat transfer fluid to the third loop up to the eighth heat exchanger or to the convergence zone via a connecting branch.

[0007] A heat transfer fluid circuit configured in this way guarantees a good compromise between multiple functions and simplicity. On the one hand, the heat transfer fluid circuit It performs a variety of functions without circulating the refrigerant through a ventilation, heating, and / or air conditioning system associated with the heat treatment system. Furthermore, the heat transfer fluid circuit architecture is simple to implement, eliminating the need for costly and / or complex components.

[0008] The main branch is fluidically connected to all the loops of the heat transfer fluid circuit. In other words, the heat transfer fluid from the first, second, or third loop can subsequently circulate through the main branch. The main branch provides passive heat treatment of the heat transfer fluid via the first heat exchanger and the outside airflow passing through it. Outside airflow refers to airflow that is not intended to be directed into the vehicle's passenger compartment. To be positioned along the path of the outside airflow, the first heat exchanger can, for example, be located on the front of the vehicle.

[0009] By convergence zone, it should be understood that it is a section of the main branch comprising one or more convergence points through which the heat transfer fluid from the different loops of the heat transfer fluid circuit flows.

[0010] The divergence zone, for its part, corresponds to a section of the main branch comprising one or more divergence points allowing the distribution of the heat transfer fluid within the different loops of the heat transfer fluid circuit. Depending on the requirement, the divergence zone can supply one or more loops with heat transfer fluid.

[0011] The first loop allows in particular the heat transfer fluid to provide thermal treatment, which can be heating or cooling, of the electric motor via the main section and the second heat exchanger and / or of the electrical storage device via the secondary section and the fourth heat exchanger.

[0012] Such an operation may be necessary if the electric motor or the electrical storage device reaches an excessively high or low temperature. For example, the electric motor may reach a high temperature when driving at high speed, for example on the highway, while the electrical storage device may need to be heated when the vehicle is started or cooled down after a rapid vehicle recharge.

[0013] The third heat exchanger contributes, for example, to the cooling of the electric motor and / or the electrical storage device by exchanging heat between the refrigerant and the heat transfer fluid. The refrigerant being previously expanded before passing through the third heat exchanger, the heat transfer fluid is then cooled within the third heat exchanger before circulating within the second or fourth heat exchanger. thermal to respectively cool the electric motor or the electrical storage device.

[0014] The first pumping device circulates the heat transfer fluid, particularly in the main section of the first loop. The first control device directs the heat transfer fluid to the main branch or to the secondary section. The second pumping device circulates the heat transfer fluid within the secondary section, for example, to generate fluid circulation independent of any other potential fluid circulation within the main section.

[0015] The second loop provides cooling for the vehicle's passenger compartment. The third pumping device circulates the heat transfer fluid within this second loop. Like the third heat exchanger, the fifth heat exchanger is configured to cool the heat transfer fluid using the previously expanded refrigerant.

[0016] The cooled heat transfer fluid then circulates to the sixth heat exchanger, thereby cooling the interior airflow which is then sent into the vehicle's passenger compartment. The second loop thus contributes to the air conditioning of the vehicle's passenger compartment. As such, the sixth heat exchanger can be integrated into the ventilation, heating, and / or air conditioning system mentioned previously. The second control device is located downstream of the fifth heat exchanger and allows either the heat transfer fluid from the fifth heat exchanger to circulate to the sixth heat exchanger, or to circulate it to the main branch via the connecting branch.

[0017] The third loop's primary function is to provide heating within the vehicle's passenger compartment. The fourth pumping device circulates the heat transfer fluid within the third loop. The seventh heat exchanger, like the third and fifth heat exchangers, allows for heat exchange with the refrigerant. However, the heat exchange within the seventh heat exchanger occurs with the refrigerant, which is pre-compressed and not expanded. The seventh heat exchanger thus heats the heat transfer fluid via the high-pressure refrigerant. Subsequently, the heated heat transfer fluid passes through the eighth heat exchanger to heat the incoming airflow. This heated airflow is then sent into the vehicle's passenger compartment for heating.Like the sixth heat exchanger, the eighth heat exchanger can be integrated into the ventilation, heating, and / or air conditioning system. The vehicle's passenger compartment is heated via the sixth and / or eighth heat exchanger. Thermal technology can thus be used for heating or cooling.

[0018] Just like the first and second control devices, the third control device is configured to provide a direct fluid connection between its loop and the main branch. The third loop is thus connected to the main branch via the connecting branch.

[0019] Thus, the set of loops that partially constitute the heat transfer fluid circuit includes at least one fluid connection with the first heat exchanger, via its respective control device. These fluid connections ensure a wide range of functionalities for the heat transfer fluid circuit, whether for the thermal treatment of the vehicle's passenger compartment or for the thermal treatment of the vehicle's powertrain components.

[0020] According to one feature of the invention, the first loop comprises a first transfer branch between the main section and the secondary section, the first transfer branch extending between the first control device and the secondary section. This first transfer branch allows the circulation of the heat transfer fluid from the main section to the secondary section or vice versa. Thanks to this first transfer branch, a fluid connection is ensured, in particular, between the second heat exchanger and the third heat exchanger, allowing for motor cooling, or between the second heat exchanger and the fourth heat exchanger in order to enable indirect heat exchange between the electric motor and the electrical storage device.

[0021] According to one feature of the invention, the first loop comprises a second transfer branch extending between the main section and the secondary section. The second transfer branch completes the first loop and connects the main section to the secondary section in a closed manner, also thanks to the aforementioned first transfer branch. The second transfer branch is therefore essential for performing the functions described above.

[0022] According to one feature of the invention, the secondary section of the first loop includes an electric heating element. The electric heating element heats the heat transfer fluid using an external energy input to the heat transfer fluid circuit. Depending on the requirement, the electric heating element is therefore capable of heating the heat transfer fluid circulating in the secondary section.

[0023] According to one feature of the invention, the first loop comprises a control element and a bypass branch, the control element being configured to circulate the heat transfer fluid to the fourth heat exchanger or within the bypass branch, the bypass branch being fluidically connected to the control element and arranged in parallel with the fourth heat exchanger. The bypass branch allows the circulation of the heat transfer fluid in the secondary section of the first loop without the latter passing through the fourth heat exchanger. Thus, when there is no need to thermally treat the electrical storage device but the heat transfer fluid is heated via the electric heating element or cooled via the third heat exchanger for a thermal treatment purpose other than that of the electrical storage device, the bypass branch makes it possible to avoid the heat transfer fluid passing through the fourth heat exchanger and disturbing the temperature of the heat transfer fluid.

[0024] According to one feature of the invention, the first control device is a three-way valve comprising three ports, at least one port extending from the main section to the convergence zone and at least one other port being connected to the secondary section. The third control device is a three-way valve comprising three ports, at least one port extending from the third loop to the eighth heat exchanger and at least one other port being connected to the convergence zone via the connecting branch. It is by means of these three-way valves that the heat transfer fluid circulating in the first loop, or respectively in the third loop, can be directed to the convergence zone of the main branch or to the secondary section, or respectively to the eighth heat exchanger or to the convergence zone of the main branch. Each of these three-way valves comprises one inlet and two outlets.It is possible that, depending on one or more parameters of the heat transfer fluid circuit, certain ports may act as inlet or outlet depending on a given circulation mode of the heat transfer fluid circuit.

[0025] According to one feature of the invention, the second control device may be a three-way valve comprising three ports, at least one port extending the second loop to the sixth heat exchanger and another port being connected to the convergence zone via the connecting branch. In a first embodiment of the heat transfer fluid circuit, the second control device, like the first and third control devices, is a three-way valve comprising one inlet and two outlets. It is by means of this three-way valve that the heat transfer fluid circulating in the second loop can be sent to the sixth heat exchanger or to the convergence zone of the main branch.

[0026] According to one feature of the invention, the control element may be a three-way valve comprising three ports, at least one port extending the secondary section to the fourth heat exchanger and at least one other port being connected to the bypass branch. Also in the first embodiment of the heat transfer fluid circuit according to the invention, the control element is likewise a three-way valve channels comprising one inlet and two outlets, thus ensuring the circulation of the heat transfer fluid so as to pass through the fourth heat exchanger or bypass it.

[0027] According to one feature of the invention, the first pumping device and / or the second pumping device and / or the third pumping device may be reversible pumps configured to circulate the heat transfer fluid in a first direction of circulation or in a second direction of circulation opposite to the first direction of circulation. In a second embodiment of the heat transfer fluid circuit, at least one of the pumping devices among the first, second, and third pumping devices is reversible. In other words, it is possible for these pumping devices to circulate the heat transfer fluid in two directions of circulation opposite to each other, in order to guarantee all the different functions of the heat transfer fluid circuit according to the invention.

[0028] According to one feature of the invention, the control element comprises a first check valve disposed on the bypass branch and / or a second check valve disposed on a pipe of the secondary section that includes the fourth heat exchanger. Due to the reversibility of certain pumping devices, the control element is composed of several check valves ensuring the control of the heat transfer fluid circulation, depending on its direction of flow. The first and second check valves, associated with the direction of flow of the heat transfer fluid, control the flow of the heat transfer fluid through or around the fourth heat exchanger. The check valves are configured to allow the heat transfer fluid to flow in one direction and to prevent its flow in the opposite direction.This configuration of the control device is specific to the second embodiment, as opposed to the three-way valve of the first embodiment.

[0029] According to one feature of the invention, the second control device comprises a first check valve disposed on the second loop and / or a second check valve disposed in the main branch upstream of the second loop. If the third pumping device is a reversible pump, the first and second check valves are arranged to circulate the heat transfer fluid towards the sixth heat exchanger or towards the convergence zone of the main branch instead of a three-way valve, depending on the direction of flow of the heat transfer fluid. Like the check valves, the check valves are configured to allow the flow of the heat transfer fluid in one direction and to prevent the flow of the heat transfer fluid in the opposite direction.

[0030] Other features and advantages of the invention will become apparent from the following description on the one hand, and from several illustrative and non-limiting examples of embodiments given with reference to the accompanying schematic drawings on the other hand, in which:

[0031] [Fig. 1] represents a heat treatment system comprising a first embodiment of a heat transfer fluid circuit according to the invention,

[0032] [Fig.2] illustrates a first mode of circulation of the fluid(s) circulating in the heat treatment system,

[0033] [Fig.3] illustrates a second mode of circulation of the fluid(s) circulating in the heat treatment system,

[0034] [Fig.4] illustrates a third mode of circulation of the fluid(s) circulating in the heat treatment system,

[0035] [Fig.5] illustrates a fourth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0036] [Fig.6] illustrates a fifth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0037] [Fig.7] illustrates a sixth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0038] [Fig.8] illustrates a seventh mode of circulation of the fluid(s) circulating in the heat treatment system,

[0039] [Fig.9] illustrates an eighth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0040] [Fig. 10] illustrates a ninth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0041] [Fig. 11] illustrates a tenth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0042] [Fig. 12] illustrates an eleventh mode of circulation of the fluid(s) circulating in the heat treatment system,

[0043] [Fig. 13] illustrates a twelfth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0044] [Fig. 14] illustrates a thirteenth mode of circulation of the fluid(s) circulating in the heat treatment system,

[0045] [Fig. 15] represents the heat treatment system comprising a second embodiment of a heat transfer fluid circuit according to the invention,

[0046] [Fig. 16] is a diagram of a secondary section of a first loop of the second embodiment of the heat transfer fluid circuit when the heat transfer fluid flows in a first direction of circulation,

[0047] [Fig. 17] is a diagram of the secondary section of the first loop of the second

[0048] [Fig. 18] is a diagram of the first loop of the second embodiment of the heat transfer fluid circuit when the heat transfer fluid flows in a second direction of circulation, opposite to the first direction of circulation.

[0049] [Fig. 19] is a variant of the circulation of the heat transfer fluid in the first loop of the second embodiment of the heat transfer fluid circuit when the heat transfer fluid flows in the first direction of circulation,

[0050] [Fig.20] is a diagram of the first loop of the second embodiment of the heat transfer fluid circuit when the heat transfer fluid flows in the second direction, opposite to the first direction of flow.

[0051] [Fig.21] is a diagram of a second loop of the second embodiment of the heat transfer fluid circuit when the heat transfer fluid flows in the first direction of circulation,

[0052] [Fig.22] is a diagram of the second loop of the second embodiment of the heat transfer fluid circuit when the heat transfer fluid flows in the second direction of circulation, opposite to the first direction of circulation.

[0053] The terms upstream and downstream used in the following description refer to the direction of flow of the fluid in question, i.e. the refrigerant or the heat transfer fluid.

[0054] In Figures 1 and 15, a heat transfer fluid circuit 2 is shown with solid lines and a refrigerant fluid circuit 3 is shown with dashed lines. In Figures 2 to 14 and 16 to 22, for each circuit, the portions through which their respective fluid flows are shown with solid lines and the portions without fluid circulation are shown with short dashed lines. Regarding Figures 2 to 14, the solid lines indicating fluid circulation are also of different thicknesses for the refrigerant fluid circuit 3 when it is in use. More specifically, the thickest solid lines correspond to portions where the refrigerant flows at high pressure and the thinnest solid lines correspond to portions where the refrigerant flows at low pressure.

[0055] Figure 1 represents a heat treatment system 1 that can be integrated into a motor vehicle and includes a first embodiment of a heat transfer fluid circuit 2 according to the invention. This heat treatment system 1 is capable of providing heat treatment for the vehicle's passenger compartment, as well as heat treatment for various components of the vehicle's powertrain.

[0056] To achieve this, the heat treatment system comprises the heat transfer fluid circuit 2, through which a heat transfer fluid circulates, and the refrigerant fluid circuit 3, through which a refrigerant circulates. The treatment system Thermal unit 1 is configured to manage various interactions between the heat transfer fluid and the refrigerant in order to optimally heat the vehicle's passenger compartment and / or the different components of the vehicle's powertrain. The heat transfer fluid can, for example, be glycol water, while the refrigerant can advantageously be an R290 type fluid, i.e., propane, which meets European environmental standards, unlike other types of refrigerants used for heat treatment.

[0057] The heat transfer fluid circuit 2 is divided into several fluidically connected sections to enhance the functionality of the heat treatment system 1. The heat transfer fluid circuit includes, in particular, a main branch 4 equipped with a first heat exchanger 5. This exchanger is configured to perform heat exchange between the heat transfer fluid circulating within it and an outside airflow 6 passing through the first heat exchanger 5. Outside airflow refers to airflow that is not intended to be directed into the vehicle's passenger compartment. To be positioned along the path of the outside airflow 6, the first heat exchanger 5 can, for example, be located on the front of the vehicle.

[0058] The main branch 4 extends between a convergence zone 7 and a divergence zone 8. The convergence zone 7 corresponds to a region of the main branch 4 comprising one or more convergence points at which one or more heat transfer fluid flows can converge. The divergence zone 8, for its part, corresponds to a region comprising one or more divergence points at which one or more heat transfer fluid flows can be distributed. Thus, the convergence zone 7 is located upstream of the first heat exchanger 5, while the divergence zone 8 is located downstream of the first heat exchanger 5.

[0059] The heat transfer fluid circuit also includes a first loop 9 divided into a main section 10 and a secondary section 11. The main section 10 extends between the divergence zone 8 and the convergence zone 7, and includes a first pumping device 12, a second heat exchanger 13 and a first control device 14.

[0060] The first pumping device 12 circulates the heat transfer fluid within the first loop 9. The second heat exchanger 13 provides thermal treatment to an electric motor of the vehicle using the heat transfer fluid. By circulating in the second heat exchanger 13, the heat transfer fluid is thus able to heat or cool the electric motor according to their respective temperatures.

[0061] The first control device 14 is located downstream of the first pumping device 12 and the second heat exchanger 13. The first control device 14 is in the form of a three-way valve comprising three ports. In the first embodiment of the heat transfer fluid circuit 2, these three ports are an inlet through which the heat transfer fluid from the second heat exchanger 13 enters, a first outlet extending the main section 10 to the convergence zone 7 of the main branch 4, and a second outlet providing a fluid connection between the main section 10 and the secondary section 11. The first loop 9 thus comprises a first transfer branch 15 extending between the second outlet of the first control device 14 and the secondary section 11.

[0062] The secondary section 11 includes a second pumping device 16, an electric heating element 17, a third heat exchanger 18 and a fourth heat exchanger 19. The second pumping device 16 allows the heat transfer fluid to be circulated in the secondary section 11, independently of any potential fluid circulation in the main section 10. The electric heating element 17 allows the heat transfer fluid to be heated via an external energy input to the heat treatment system 1.

[0063] The third heat exchanger 18 is configured to operate a heat exchange between the heat transfer fluid circulating in the secondary section 11 and the refrigerant circulating in the refrigerant circuit 3. As will be detailed later, the third heat exchanger 18 allows the heat transfer fluid to be cooled.

[0064] Finally, the fourth heat exchanger 19 allows for the thermal treatment of an electrical storage device of the vehicle by the heat transfer fluid. By circulating in the fourth heat exchanger 19, the heat transfer fluid is thus able to heat or cool the electrical storage device according to their respective temperatures.

[0065] The first loop 9 also includes a second transfer branch 20 which, like the first transfer branch 15, provides a fluid connection within the first loop 9 between the main section 10 and the secondary section 11. The two transfer branches 15, 20 make it possible to form a closed circuit composed at least partially of the main section 10 and at least partially of the secondary section 11. Such a configuration makes it possible to multiply the functions of the heat transfer fluid circuit 2 according to the invention.

[0066] The first loop 9 finally includes a control element 21 located on the secondary section 11 downstream of the third heat exchanger 18 and upstream of the fourth heat exchanger 19. The control element 21 is in the form of a three-way valve comprising three ports. In the first embodiment of the heat transfer fluid circuit 2, these three ports are an inlet through which the heat transfer fluid from the third heat exchanger 18 flows, a first outlet extending the secondary section 11 to the fourth heat exchanger 19 and a second outlet from which a bypass branch 22 begins. The bypass branch 22 is arranged in parallel with the fourth heat exchanger 19 and allows it to be bypassed when the heat transfer fluid is not intended to thermally treat the electrical storage device.

[0067] The heat transfer fluid circuit 2 also includes a second loop 23. Just like the first loop 9, the second loop 23 is connected to the divergence zone 8 of the main branch 4. The second loop 23 includes a third pumping device 24, a fifth heat exchanger 25 and a sixth heat exchanger 26. In addition, the second loop 23 is placed under the control of a second control device 27.

[0068] The third pumping device 24 circulates the heat transfer fluid in the second loop 23. The fifth heat exchanger 25, just like the third heat exchanger 18 of the first loop 9, is configured to operate a heat exchange between the heat transfer fluid and the refrigerant circulating in the refrigerant circuit 3. As will be detailed later, the fifth heat exchanger 25 allows the heat transfer fluid to be cooled.

[0069] The sixth heat exchanger 26 is configured to perform heat exchange between the heat transfer fluid and an interior airflow 28. Unlike the exterior airflow 6, the interior airflow 28 is intended to be sent to the vehicle's passenger compartment for thermal treatment. As such, the sixth heat exchanger 26 can be arranged within a ventilation, heating, and / or air conditioning system 29 that directs the interior airflow 28, notably through the sixth heat exchanger 26, before sending it to the vehicle's passenger compartment. As will be detailed later, the sixth heat exchanger 26 contributes to the air conditioning of the vehicle's passenger compartment.

[0070] The second control device 27 is arranged downstream of the fifth heat exchanger 25 and upstream of the sixth heat exchanger 26. The second control device 27 is in the form of a three-way valve comprising three ports. In the first embodiment of the heat transfer fluid circuit, these three ports are an inlet through which the heat transfer fluid from the fifth heat exchanger 25 flows, a first outlet that extends the second loop 23 to the sixth heat exchanger 26, and a second outlet through which the heat transfer fluid can flow to the convergence zone 7 of the main branch 4. Accordingly, the heat transfer fluid circuit 2 includes a connecting branch 30 that extends between the second outlet of the second control device 27 and the convergence zone. convergence 7 of the main branch 4. The junction branch 30 therefore ensures the fluidic link between the second loop 23 and the main branch 4.

[0071] The heat transfer fluid circuit 2 further comprises a third loop 31 provided with a fourth pumping device 32, a seventh heat exchanger 33, an eighth heat exchanger 34 and a third control device 35. The third loop 31 can be supplied with heat transfer fluid via the divergence zone 8.

[0072] The fourth pumping device 32 is suitable for circulating the heat transfer fluid in the third loop 31, while the seventh heat exchanger 33 is configured to perform heat exchange between the heat transfer fluid and the refrigerant. As will be detailed later, the seventh heat exchanger 33 allows the heat transfer fluid to be heated.

[0073] Just like the sixth heat exchanger 26, the eighth heat exchanger 34 is configured to perform a heat exchange between the heat transfer fluid and the interior airflow 28. The eighth heat exchanger 34 is therefore also advantageously located within the ventilation, heating and / or air conditioning system 29. As will be detailed later, the eighth heat exchanger 34 contributes to heating the vehicle's passenger compartment.

[0074] The third control device 35 is arranged downstream of the seventh heat exchanger 33 and upstream of the eighth heat exchanger 34. The third control device 35 is in the form of a three-way valve comprising an inlet through which the heat transfer fluid from the seventh heat exchanger 33 circulates, a first outlet which extends the third loop 31 to the eighth heat exchanger 34, and a second outlet through which the heat transfer fluid can circulate to the convergence zone 7 of the main branch 4. Accordingly, the heat transfer fluid circuit 2 includes a connecting branch 36 which extends between the second outlet of the third control device 35 and the convergence zone 7 of the main branch 4. The connecting branch 36 thus provides the fluid connection between the third loop 31 and the main branch 4.

[0075] The set of loops 9, 23, 31 of the heat transfer fluid circuit therefore includes a branch connecting them directly to the main branch, upstream of the first heat exchanger 5. This characteristic makes it possible to multiply the possible operating modes of the heat transfer fluid circuit 2, while maintaining a simple architecture.

[0076] The refrigerant circuit 3 includes a main channel 37 equipped with a compression device 38 that circulates the refrigerant in the refrigerant circuit. The main channel 37 extends to pass through the seventh heat exchanger 33, then splits into a first channel 43 comprising a first release mechanism 39 and in a second way 40 comprising a second release mechanism 41.

[0077] Each of the expansion valves 39, 41 ensures an expansion of the refrigerant, which then decreases in pressure and temperature. Subsequently, the refrigerant can pass through the third heat exchanger 18 or the fifth heat exchanger 25, depending on the path through which the refrigerant flows. This choice of path is obviously dependent on the objectives that the heat treatment system 1 must fulfill.

[0078] Subsequently, the first path 43 and the second path 40 join together to reform the main path 37. Since the compression device 38 is only capable of compressing refrigerant in a gaseous state, the refrigerant circuit 3 may advantageously include an accumulation device 42 disposed on the main path upstream of the compression device 38 in order to retain a liquid fraction of the refrigerant before it passes through the compression device 38 and damages it.

[0079] Since the refrigerant is advantageously propane, it is not intended to circulate within the ventilation, heating and / or air conditioning system 29 for safety reasons. Thus, as illustrated in [Fig. 1], only the heat transfer fluid circulates within the ventilation, heating and / or air conditioning system 29.

[0080] Figure 2 illustrates a first circulation mode of the fluid(s) within the heat treatment system 1. In this circulation mode and in each of the following ones, one or more heat treatment objectives are achieved by the heat treatment system. The various circulation modes presented below are not exhaustive and can even be combined with each other to achieve more objectives simultaneously.

[0081] In [Fig.2], the objective is to heat the vehicle's passenger compartment by means of the interior airflow 28. The heat transfer fluid therefore circulates within at least the third loop 31. The fourth pumping device 32 circulates the heat transfer fluid, and the latter passes through the seventh heat exchanger 33.

[0082] In order to heat the heat transfer fluid so that it can subsequently release its heat to the internal airflow 28, the refrigerant circuit 3 is also activated using the compression device 38. This device compresses the refrigerant to high pressure, which causes its temperature to rise. The refrigerant can then condense, releasing its heat to the heat transfer fluid within the seventh heat exchanger 33.

[0083] At the outlet of the seventh heat exchanger 33, the hot heat transfer fluid circulates to the third control device 35, which directs the hot heat transfer fluid to the eighth heat exchanger 34. As it passes through this last exchanger, the heat from the fluid- loporteur are transferred to the internal airflow 28, which is then sent into the vehicle's passenger compartment to provide heating.

[0084] Since the refrigerant has been used to heat the heat transfer fluid in the seventh heat exchanger 33, the thermodynamic cycle of the refrigerant must be continued to maintain the efficiency of the heat treatment. To do this, the at least partially condensed refrigerant continues its circulation in the main channel 37, then in the first channel 43. The refrigerant is then expanded by the first expansion valve 39 and passes through the third heat exchanger 18.

[0085] Simultaneously, another heat transfer fluid loop is put into circulation at the secondary section 11 of the first loop 9. The second pumping device 16 circulates the heat transfer fluid, and the electric heating element 17 is activated to heat the heat transfer fluid circulating in the secondary section 11. The heated heat transfer fluid then passes through the third heat exchanger 18. The heat exchange occurring in the third heat exchanger 18 thus completes the thermodynamic cycle of the refrigerant by evaporating it with the help of the heated heat transfer fluid.

[0086] The evaporated refrigerant can then circulate to the compression device 38, with the storage device 42 optionally retaining a liquid fraction of the refrigerant. The heat transfer fluid, meanwhile, circulates in the secondary section 11 until it rejoins the second pumping device 16. Since the electrical storage device does not require heat treatment, the control unit 21 directs the heat transfer fluid to the bypass branch 22.

[0087] Figure 3 illustrates a second circulation method for the fluid(s) within the heat treatment system 1. In Figure 3, the electrical storage device requires heating. This may be necessary, for example, when starting the vehicle and / or in the event of low ambient temperatures. Figure 3 illustrates one circulation method for heating the electrical storage device, but as will be detailed later, several circulation methods can achieve this objective.

[0088] The electrical storage device is heated here solely by means of the electric heating element 17. This circulation method therefore does not require the circulation of the refrigerant. Only the heat transfer fluid circulates within the secondary section 11 by means of the second pumping device 16. The heat transfer fluid is thus heated by the electric heating element 17 and passes through the third heat exchanger 18 without heat exchange, as the refrigerant does not circulate.

[0089] Subsequently, the control unit 21 directs the heat transfer fluid to the fourth heat exchanger 19, which passes through it in order to transfer its heat to the device electrical storage which is then heated. Subsequently, the heat transfer fluid circulates again to the second pumping device 16.

[0090] Figure 4 illustrates a third mode of circulation of the fluid(s) within the Heat treatment system 1. For this circulation mode, the electrical storage device requires cooling. As with the previous circulation modes, the heat transfer fluid circulates within the secondary section 11 of the first loop via the second pumping device 16. The heat transfer fluid then passes through the electric heating element 17, but since the latter is inactive, the heat transfer fluid remains at the same temperature.

[0091] The heat transfer fluid is, however, cooled within the third heat exchanger 18 by means of the refrigerant circulating in the first channel 43 and previously expanded by the first expansion device 39. The cooled heat transfer fluid then circulates to the fourth heat exchanger 19 in order to capture the heat from the electrical storage device and thus cool the latter, before being pumped again by the second pumping device 16.

[0092] In order to operate an optimal thermodynamic cycle, the compressed refrigerant must be condensed before being expanded and evaporated to cool the heat transfer fluid circulating in the third heat exchanger 18. To achieve this, another heat transfer fluid loop must be implemented to condense the refrigerant within the seventh heat exchanger 33. The fourth pumping device 32 circulates the heat transfer fluid, which then passes through the seventh heat exchanger 33 to capture heat from the high-pressure refrigerant and condense it. The heat transfer fluid then circulates to the third control device 35, which directs the heat transfer fluid within the connecting branch 36 to the convergence zone 7 of the main branch 4.This allows the heat transfer fluid to pass through the first heat exchanger 5 so that the outside airflow 6 dissipates the heat from the heat transfer fluid captured during the heat exchange within the seventh heat exchanger 33.

[0093] At the outlet of the first heat exchanger 5, the heat transfer fluid continues its circulation in the main branch 4 to the divergence zone 8 and can recirculate within the third loop 31 to be pumped again by the fourth pumping device 32.

[0094] Figure 5 illustrates a fourth mode of circulation of the fluid(s) within the thermal treatment system 1. This fourth circulation mode is similar to the third circulation mode except that it is the vehicle's passenger compartment that needs to be cooled and not the electrical storage device.

[0095] Consequently, there is no circulation of heat transfer fluid within the first loop 9. The refrigerant, however, must also be condensed as it passes through the seventh heat exchanger 33 in order to respect the thermodynamic cycle, therefore the circulation of the heat transfer fluid within the seventh heat exchanger 33 and the first heat exchanger 5 as described in [Fig.4] is always implemented and we will refer to the description of [Fig.4] concerning the details of this heat exchange.

[0096] The condensed refrigerant fluid continues its circulation in the main channel 37 and then in the second channel 40 in order to be expanded by the second expansion device 41 and to pass through the fifth heat exchanger 25 to be evaporated and then compressed again by the compression device 38.

[0097] In parallel, the heat transfer fluid is circulated within the second loop 23 by the third pumping device 24 and passes through the fifth heat exchanger 25 to be cooled by the expanded refrigerant. The cooled heat transfer fluid then circulates to the second control device 27, which directs the cooled heat transfer fluid to the sixth heat exchanger 26. As it circulates within the sixth heat exchanger 26, the heat transfer fluid cools the interior airflow 28, which is then sent into the vehicle's passenger compartment to provide air conditioning. At the outlet of the sixth heat exchanger 26, the heat transfer fluid is pumped again by the third pumping device 24.

[0098] Fig. 6 illustrates a fifth mode of circulation of the fluid(s) within the heat treatment system 1. The objective of this fifth mode of circulation is to perform passive cooling of the electric motor by means of the heat transfer fluid and the first heat exchanger 5.

[0099] To achieve this, the heat transfer fluid circuit 2 is configured so that the heat transfer fluid circulates in a loop in the main section 10 of the first loop 9 and in the main branch 4. The heat transfer fluid is put into circulation by the first pumping device 12 and then captures the heat generated by the electric motor by circulating in the second heat exchanger 13. Subsequently, the heat transfer fluid travels through the entire main section 10 until it reaches the convergence zone 7 to continue its circulation within the main branch 4.

[0100] The heat transfer fluid then circulates within the first heat exchanger 5 and the heat from the electric motor captured by the heat transfer fluid is then dissipated by the outside air flow 6 passing through the first heat exchanger 5. Subsequently the heat transfer fluid circulates to the divergence zone 8 and recirculates in the main section 10 being pumped again by the first pumping device 12.

[0101] The electric motor is thus passively cooled by transferring its heat to the heat transfer fluid, and said heat is dissipated by the outside air flow 6 thanks to the circulation of the heat transfer fluid which has stored said heat at the level of the second heat exchanger 13.

[0102] Figure 7 illustrates a sixth mode of circulation of the fluid(s) within the thermal treatment system 1. This sixth circulation mode is actually a combination of the third circulation mode and the fifth circulation mode, i.e. a cooling of the electrical storage device using the refrigerant and a passive cooling of the electric motor simultaneously.

[0103] At the divergence zone 8, the heat transfer fluid is thus distributed between the main section 10 of the first loop 9 and the third loop 31. The heat transfer fluid is therefore circulated by the first pumping device 12 and by the fourth pumping device 32. In both cases, heat is captured by the heat transfer fluid, i.e. the heat generated by the electric motor, or the heat from the high-pressure refrigerant compressed by the compression device 38 and circulating in the refrigerant circuit 3. Subsequently, in both cases, the heat transfer fluid reaches the convergence zone 7 to circulate within the main branch 4 and the first heat exchanger 5 so that the heat captured within the second heat exchanger 13 or the seventh heat exchanger 33 is dissipated by the outside air flow 6.The heat transfer fluid is subsequently redistributed within the main section 10 or the third loop 31 via the divergence zone 8.

[0104] The electrical storage device is cooled by the heat transfer fluid circulating in the secondary section 11 of the first loop 9, which is itself cooled in the third heat exchanger 18 by the expanded refrigerant. The electric heating element 17 is, of course, inactive. As described previously, the heat exchange ensuring the cooling of the electrical storage device takes place in the fourth heat exchanger 19. The refrigerant performs its cooling function optimally because it has been at least partially condensed in the seventh heat exchanger 33 by the heat transfer fluid circulating in the third loop 31.

[0105] Regarding the sixth mode of circulation, reference may be made to the description of figures 4 and 6 for further details.

[0106] Figure 8 illustrates a seventh mode of circulation of the fluid(s) within the Heat treatment system 1. The objective of this seventh circulation mode is to heat the vehicle's passenger compartment. The heat transfer fluid therefore circulates within the third loop 31, is heated within the seventh heat exchanger 33 by the high-pressure refrigerant compressed by the compression device 38, then circulates to the eighth heat exchanger 34 where the heat is transferred to the interior airflow 28 passing through the eighth heat exchanger 34. The interior airflow 28 is thus heated and sent into the vehicle's passenger compartment.

[0107] Just like the first mode of transport whose objective was also to To heat the vehicle's passenger compartment, the refrigerant was used to heat the heat transfer fluid through the seventh heat exchanger 33, and the thermodynamic cycle of the refrigerant must be continued in order to maintain the efficiency of the heat treatment.

[0108] Unlike the first circulation method where the expanded refrigerant was evaporated in the third heat exchanger 18 via the heat transfer fluid preheated by the electric heating element 17, the seventh circulation method uses the heat from the electric motor to heat the heat transfer fluid. This avoids the need for additional energy input to power the electric heating element 17.

[0109] To achieve this, the first transfer branch 15 and the second transfer branch 20 are used to form a junction between the main section 10 and the secondary section 11 of the first loop 9. The transfer branches 15, 20 thus ensure a direct fluidic connection between the second heat exchanger 13 and the third heat exchanger 18. The first control element 14 is also used to direct the heat transfer fluid from the main section 10 to the first transfer branch 15.

[0110] The heat transfer fluid is circulated by the first pumping device 12 and flows through the second heat exchanger 13 to capture the heat from the electric motor, which emits heat during its operation. The heat transfer fluid then flows to the first control device 14, which directs it to the first transfer branch 15. The heat transfer fluid thus flows from the main section 10 to the secondary section 11.

[0111] The heat transfer fluid subsequently transfers the heat captured from the electric motor to the refrigerant during the heat exchange occurring within the third heat exchanger 18. The refrigerant is thus evaporated and its thermodynamic cycle is completed, thereby optimizing the thermal performance of the heat treatment system 1. At the outlet of the third heat exchanger 18, the heat transfer fluid flows through the bypass branch 22 to bypass the fourth heat exchanger 19 because the electrical storage device does not require heat treatment, then flows through the second transfer branch 20 to rejoin the main section 10 and be pumped by the first pumping device 12.

[0112] Figure 9 illustrates an eighth circulation mode of the fluid(s) within the heat treatment system 1. Just as with the seventh circulation mode, the eighth circulation mode provides heating for the vehicle passenger compartment, but instead of subsequently using the heat from the electric motor to evaporate the refrigerant, it uses the heat emitted by the electrical storage device. used.

[0113] The heat transfer fluid circulates entirely within the secondary section 11 and is circulated by the second pumping device 16. The heat transfer fluid absorbs the heat generated by the electrical storage device as it circulates through the fourth heat exchanger 19 and continues its circulation through the secondary section 11 to the third heat exchanger 18, where it transfers the heat to the refrigerant. In [Fig. 9], the electric heating element 17 is inactive, but it can be activated to further raise the temperature of the heat transfer fluid before it circulates through the third heat exchanger 18.

[0114] In an unillustrated circulation mode, it is possible to combine the seventh and eighth circulation modes to recover both the heat generated by the electric motor and the heat generated by the electrical storage device. In this circulation mode, the heat transfer fluid circulates in the first loop, absorbs heat from the electrical storage device by circulating in the fourth heat exchanger 19, and separates into two fractions at the second transfer branch 20. One fraction continues its circulation in the secondary section 11, while the other fraction joins the main section 10 via the second transfer branch 20 and circulates in the second heat exchanger 13 to absorb the heat generated by the electric motor. The two fractions then rejoin upstream of the third heat exchanger 18.

[0115] Figure 10 illustrates a ninth circulation method for the fluid(s) within the heat treatment system 1. The objective of this circulation method is to heat the electrical storage device using the heat emitted by the electric motor. This circulation method is therefore particularly advantageous because it eliminates the need to use the refrigerant circuit 3.

[0116] The transfer branches 15, 20 are once again used to form the junction between the main section 10 and the secondary section 11 of the first loop 9. The heat transfer fluid is put into circulation by the first pumping device 12, captures the heat generated by the electric motor by circulating within the second heat exchanger 13, then circulates in the first transfer branch 15 to join the secondary section 11.

[0117] The heat transfer fluid then passes through the third heat exchanger 18 without consequence, since the refrigerant circuit 3 is inactive, and then circulates to the fourth heat exchanger 19 to transfer the heat to the electrical storage device to heat it. Subsequently, the heat transfer fluid returns to the main section 10 via the second transfer branch 20.

[0118] Figure 11 illustrates a tenth mode of circulation of the fluid(s) within the heat treatment system 1. The objective here is to defrost the first heat exchanger 5 when the ambient temperature is very low.

[0119] To do this, the heat transfer fluid circulates between the third loop 31 and the main branch 4 via the connecting branch 36. The aim is to heat the heat transfer fluid within the seventh heat exchanger 33 via the refrigerant compressed by the compression device 38. The heated heat transfer fluid then exits the third loop 31 via the connecting branch 36 and joins the main branch 4 via the convergence zone 7.

[0120] Next, the hot heat transfer fluid circulates in the first heat exchanger 5 in order to defrost it, and rejoins the third loop 31 via the divergence zone 8.

[0121] The completion of the thermodynamic cycle of the refrigerant is carried out as for example for the first circulation mode, that is to say that the evaporation of the expanded refrigerant takes place within the third heat exchanger 18. The heat transfer fluid ensuring the evaporation of the refrigerant circulates in the secondary section 11 of the first loop 9, is preheated using the electric heating element 17 and bypasses the fourth heat exchanger 19 by means of the bypass branch 22.

[0122] In a circulation mode not shown, the defrosting of the first heat exchanger 5 can be achieved using the heat generated by the electric motor. This circulation mode is strictly identical to the fifth circulation mode shown in [Fig. 6], i.e., the refrigerant circuit 3 is inactive and the heat transfer fluid circulates between the main branch 4 and the main section 10 of the first loop 9.

[0123] Instead of cooling the electric motor using the outside air flow 6 as described in [Fig.6], in this unillustrated circulation mode the first heat exchanger 5 is defrosted using the heat generated by the heat engine and captured by the heat transfer fluid during its circulation within the second heat exchanger 13.

[0124] In another circulation method not shown, it is possible to combine the two defrosting methods described above, i.e. the tenth circulation method with the circulation method not shown described above, in order to improve the defrosting of the first heat exchanger 5. The heat transfer fluid thus separates into two fractions, one of which is heated by the refrigerant via the seventh heat exchanger 33, while the other captures the heat generated by the electric motor by circulating within the second heat exchanger 13. The two fractions of heated heat transfer fluid then rejoin at the convergence zone 7 and then perform the defrosting by circulating within the first heat exchanger 5.

[0125] Figure 12 illustrates an eleventh mode of circulation of the fluid(s) within the thermal treatment system 1. This circulation method consists of heating the vehicle's passenger compartment and evaporating the refrigerant using the third heat exchanger 18 while heating the electrical storage device, notably using the heat generated by the electric motor.

[0126] Just as with the circulation methods described above and having in particular the objective of heating the passenger compartment of the vehicle, the heat transfer fluid circulates within the third loop 31, is heated within the seventh heat exchanger 33 by the high-pressure refrigerant fluid compressed by the compression device 38, then circulates to the eighth heat exchanger 34 where the calories are transferred to the interior airflow 28 passing through the eighth heat exchanger 34. The interior airflow 28 is thus heated and is sent into the passenger compartment of the vehicle.

[0127] The condensed refrigerant then circulates within the first channel 43, is expanded by the first expansion device 39 and is evaporated within the third heat exchanger 18 by the heat transfer fluid. The refrigerant then circulates to the compression device 38.

[0128] In order to store sufficient heat to both evaporate the refrigerant and subsequently heat the electrical storage device, the combined effect of the electric heating element 17 and the heat generated by the electric motor is required. The heat transfer fluid circulating in the first loop 9 then separates into two fractions. The first fraction flows into the second transfer branch 20, is pumped by the first pumping device 12, and circulates within the second heat exchanger 13 to capture the heat generated by the electric motor before returning to the secondary section 11 via the first transfer branch 15. The second fraction is pumped by the second pumping device 16 and is heated by the electric heating element 17.Subsequently, the two heated fractions of heat transfer fluid combine and circulate together within the third heat exchanger 18 to evaporate the refrigerant. Thanks to the combined heat of the two fractions of heat transfer fluid and the heat they previously absorbed, the heat transfer fluid exits the third heat exchanger 18 still sufficiently hot to circulate within the fourth heat exchanger 19 and release the remaining heat to warm the electrical storage device. From the outlet of the fourth heat exchanger 19, the heat transfer fluid continues its circulation in the secondary section 11 until it again separates into two fractions.

[0129] The distribution of the heat transfer fluid between the two fractions of heat transfer fluid can be regulated to optimize the temperature of the heat transfer fluid. This distribution can, for example, depend on the temperature of the electric motor, which can encourage Send more heat transfer fluid through the second heat exchanger 13 if the temperature is very high. The heating power of the electric heating element 17 can also be modulated as needed. The distribution of the heat transfer fluid can, for example, be regulated by the pumping devices 12 and 16 if their pumping speed can be adjusted.

[0130] Figure 13 illustrates a twelfth circulation method for the fluid(s) within the heat treatment system 1. This twelfth circulation method is designed to dehumidify the interior airflow 28 intended for distribution into the vehicle's passenger compartment. Dehumidification involves circulating heat transfer fluid through both the sixth heat exchanger 26 and the eighth heat exchanger 34 to dehumidify the interior airflow 28. This process avoids sending a humid airflow into the passenger compartment, which can cause several problems such as fogging of the vehicle windows, impairing visibility, or discomfort for the vehicle's occupants. In Figure 13, the dehumidification process is coupled with passive cooling of the electric motor, but dehumidification can also be implemented independently.

[0131] For this twelfth circulation mode, the heat transfer fluid circulates in particular within the third loop 31. After being put into circulation by the fourth pumping device 32, the heat transfer fluid is heated within the seventh heat exchanger 33 by the high-pressure refrigerant fluid compressed by the compression device 38, then circulates to the eighth heat exchanger 34 where the calories are transferred to the flow of interior air 28 passing through the eighth heat exchanger 34.

[0132] In parallel, heat transfer fluid is also circulated within the second loop 23 by the third pumping device 24 and passes through the fifth heat exchanger 25 to be cooled by the expanded refrigerant. The cooled heat transfer fluid then circulates to the sixth heat exchanger 26. As it circulates within the sixth heat exchanger 26, the heat transfer fluid then cools the internal airflow 28.

[0133] Thus, before being sent into the vehicle's passenger compartment, the interior airflow 28 is first cooled by passing through the sixth heat exchanger 26. Cooling the interior airflow 28 allows the moisture present in it to condense and be retained. The interior airflow 28 therefore exits the sixth heat exchanger 26 cool and dry.

[0134] Next, with the objective of heating and dehumidifying the vehicle's interior, the interior airflow 28 passes through the eighth heat exchanger 34 to be heated. The interior airflow 28 is thus sent into the warm, dry vehicle's interior.

[0135] Thanks to the dehumidification process, the management of the refrigerant circuit 3 is simplified. Indeed, after being compressed by the compression device 38, the refrigerant is condensed within the seventh heat exchanger 33 and transfers its heat to the heat transfer fluid intended to heat the interior airflow 28. The refrigerant then circulates within the second channel 40, is expanded by the second expansion valve 41, and is evaporated within the fifth heat exchanger 25, thus cooling the heat transfer fluid intended to cool the interior airflow 28. The evaporated refrigerant then continues its circulation until it is compressed again by the compression device 38.The dehumidification process is therefore sufficient for the refrigerant to complete a full thermodynamic cycle, and it is therefore not necessary to implement other functionalities of the heat transfer fluid circuit 2 to complete this thermodynamic cycle.

[0136] Optionally, the heat transfer fluid circuit, in parallel with the dehumidification process, can provide passive cooling for the electric motor. The circulation of the heat transfer fluid is identical to that illustrated in [Fig. 6]. The heat transfer fluid circulates in the main section 10 of the first loop 9 and cools the electric motor by absorbing its heat within the second heat exchanger. The heat transfer fluid then joins the main branch 4 and circulates within the first heat exchanger 5, where the outside airflow 6 dissipates the heat from the heat transfer fluid. The heat transfer fluid then returns to the main section 10 via the divergence zone 8.

[0137] Fig. 14 illustrates a thirteenth mode of circulation of the fluid(s) within the heat treatment system 1. This mode of circulation consists of heating the vehicle's passenger compartment and evaporating the refrigerant fluid using the fifth heat exchanger 25.

[0138] Just as with the circulation methods described above and having in particular the objective of heating the passenger compartment of the vehicle, the heat transfer fluid circulates within the third loop 31, is heated within the seventh heat exchanger 33 by the high-pressure refrigerant fluid compressed by the compression device 38, then circulates to the eighth heat exchanger 34 where the calories are transferred to the interior airflow 28 passing through the eighth heat exchanger 34. The interior airflow 28 is thus heated and is sent into the passenger compartment of the vehicle.

[0139] To evaporate the refrigerant previously condensed by its heat exchange within the seventh heat exchanger 33, the refrigerant circulates this way within the second way 40, is expanded by the second expansion member 41 and is evaporated within the fifth heat exchanger 25.

[0140] For the evaporation of the refrigerant, another heat transfer fluid loop is formed, said other loop being formed from the main branch 4 and a portion of the second loop 23, the latter and the main branch 4 being fluidly linked by way of the junction branch 30. The heat transfer fluid is thus put into circulation by the third pumping device 24 and captures the heat from the expanded refrigerant fluid by circulating within the fifth heat exchanger 25.

[0141] The heat transfer fluid then flows to the second control device 27, which guides it through the recovery branch 30. The heat transfer fluid then rejoins the main branch 4 via the convergence zone 7. The captured heat is then dissipated as the heat transfer fluid circulates through the first heat exchanger 5 and is traversed by the outside airflow 6. Since the passenger compartment heating is active, this means that the ambient temperature is relatively low. The outside airflow 6 therefore provides a very good means of dissipating heat from the heat transfer fluid, thus optimizing the thermodynamic cycle of the refrigerant. At the outlet of the first heat exchanger 5, the heat transfer fluid continues its circulation in the main branch 4 and rejoins the second loop 23 via the divergence zone 8.

[0142] Figure 15 represents a heat treatment system 1 comprising a second embodiment of the heat transfer fluid circuit 2. This second embodiment differs from the first embodiment illustrated previously, notably in that the first pumping device 12, the second pumping device 16, and the third pumping device 24 are reversible pumps. In other words, the first pumping device 12, the second pumping device 16, and the third pumping device 24 are capable of circulating the heat transfer fluid in two directions. Furthermore, the control element 21 is no longer in the form of a three-way valve but in the form of two check valves 53, 54. The second control device 27 is in the form of two check valves 56, 57 instead of a three-way valve.

[0143] The first control device 14 is always in the form of a three-way valve, but depending on the circulation mode applied to the heat treatment system 1, some of the ports of the first control device 14 can act as inlet or outlet.

[0144] As will be described below, the heat treatment system 1 equipped with the second embodiment of the heat transfer fluid circuit 2 is capable of applying all the circulation modes applicable to the heat treatment system 1 equipped with the first embodiment of the heat transfer fluid circuit 2 and described above. The second embodiment therefore differs from the first embodiment only in structural terms.

[0145] At the secondary section 11 of the first loop 9, the control element 21 comprises a first non-return valve 53 disposed on the bypass branch 22 and a second non-return valve 54 arranged on a pipe 55 at which the fourth heat exchanger 19 is located. In this second embodiment, the positioning of the non-return valves 53, 54 and the direction of flow of the heat transfer fluid determine whether, in the case of circulation in the secondary section 11, the heat transfer fluid circulates within the fourth heat exchanger 19 or bypasses it by circulating within the bypass branch 22. The direction of flow of the heat transfer fluid in the secondary section 11 is determined by the first pumping device 12 and / or by the second pumping device 16.

[0146] The first transfer branch 15 and the second transfer branch 20 are structurally identical with respect to the first embodiment, but due to the reversibility of the first pumping device 12 and the second pumping device 16, the transfer branches 15, 20 can be traversed by the heat transfer fluid in two directions of circulation, unlike the first embodiment.

[0147] As previously mentioned, the third pumping device 24 is also a reversible pump. The second control device 27, governing the circulation of the heat transfer fluid in the second loop 23, comprises a first non-return device 56 disposed on the second loop 23 and a second non-return device 57 disposed on the main branch 4, at the divergence zone 8 upstream of the second loop 23. As with the first loop 9, the direction of circulation of the heat transfer fluid is defined by the third pumping device 24 in conjunction with the positioning of the non-return devices 56, 57.

[0148] The remaining elements of the heat treatment system 1 being identical to those of the heat treatment system 1 provided with the first embodiment of the heat transfer fluid circuit 2, reference will be made to the description of [Fig.1] concerning the details relating to the elements common to the two embodiments of the heat transfer fluid circuit.

[0149] Figures 16 to 22 illustrate portions of the heat transfer fluid circuit, detailing the circulation of the heat transfer fluid according to a flow direction 58, 59 of said heat transfer fluid. For each of Figures 16 to 22, the flow direction 58, 59 is indicated by an arrow and by a color code of the pumping device 12, 16, 24 considered. As with Figures 2 to 14, the circulation of the heat transfer fluid is represented by solid lines, and the portions without heat transfer fluid circulation are represented by short dashed lines.

[0150] Figure 16 is a representation of the secondary section 11 alone. For Figures 16 and 17, the direction of flow of the heat transfer fluid is defined by the second pumping device 16. In Figure 16, the direction of flow of the heat transfer fluid is defined by the white arrow of the second pumping device 16. The heat transfer fluid The heat transfer fluid therefore circulates in a first direction of circulation 58 and the check valves 53, 54 are arranged so that the heat transfer fluid circulates within the fourth heat exchanger 19. The first check valve 53 prevents the circulation of the heat transfer fluid within the bypass branch 22 at the outlet of the third heat exchanger 18 and forces the circulation of the heat transfer fluid within the fourth heat exchanger 19.

[0151] With reference to the circulation modes described above, by way of non-exhaustive examples, the direction of circulation illustrated in [Fig. 16] is defined to implement the second circulation mode illustrated in [Fig. 3], where the electrical storage device is heated by means of the electrical heating element 17, or to implement the third and sixth circulation modes illustrated respectively in Figures 4 and 7, where the electrical storage device is cooled by means of the third heat exchanger 18. This direction of circulation is also defined to implement the eighth circulation mode illustrated in [Fig. 9], where the heat generated by the electrical storage device is used to evaporate the refrigerant via the third heat exchanger 18.

[0152] Fig. 17 still illustrates the secondary section 11 of the first loop 9, but this time when the heat transfer fluid circulates in a second direction of circulation 59 opposite to the first direction of circulation 58 illustrated in Fig. 16.

[0153] When the heat transfer fluid circulates in the secondary section 11 of the first loop 9 in the second direction of circulation 59, the second check valve 54 prevents the circulation of the heat transfer fluid within the pipe 55 at which the fourth heat exchanger 19 is located. The circulation of the heat transfer fluid is therefore forced within the bypass branch 22 and the heat transfer fluid thus bypasses the fourth heat exchanger 19.

[0154] Referring to the circulation modes described above, by way of non-exhaustive examples, the direction of circulation illustrated in [Fig. 17] is defined to implement the first circulation mode illustrated in [Fig. 2] or the tenth circulation mode illustrated in [Fig. 11]. For both of these circulation modes, the electric heating element 17 is used to heat the heat transfer fluid, which subsequently ensures the evaporation of the refrigerant by circulating within the third heat exchanger 18.

[0155] Fig. 18 represents the first loop 9 in its entirety, with the main section 10 and the secondary section 11. In Figures 18 to 20, the direction of circulation of the heat transfer fluid is defined at least by the white arrow of the first pumping device 12.

[0156] In [Fig. 18], the heat transfer fluid circulates in the first loop 9 in the first direction of flow 58. Just as described in [Fig. 16], the first The direction of flow 58 allows the heat transfer fluid to circulate within the fourth heat exchanger 19 and not in the bypass branch 22.

[0157] For this configuration, the heat transfer fluid circulates in the first transfer branch 15 from the main section 10 to the secondary section 11 and in the second transfer branch 20 from the secondary section 11 to the main section 10. The second pumping device 16 is inactive.

[0158] The configuration illustrated in [Fig. 18] is used in particular to implement the ninth circulation mode illustrated in [Fig. 10], in which the heat generated by the electric motor is captured by the heat transfer fluid as it circulates in the second heat exchanger 13, and is then transferred to heat the electrical storage device when the heat transfer fluid circulates within the fourth heat exchanger 19.

[0159] Fig. 19 is a variant of what is illustrated in Fig. 18, where the second pumping device 16 is also active in addition to the first pumping device 12 and also circulates the heat transfer fluid in the first direction of circulation 58. The heat transfer fluid therefore always circulates within the fourth heat exchanger 19.

[0160] The configuration illustrated in [Fig. 19] is used in particular to implement the eleventh circulation mode illustrated in [Fig. 12], in which the heat transfer fluid is divided into two fractions, one of which captures the heat generated by the electric motor by circulating in the second heat exchanger 13 while the other is heated by the electric heating element 17, and this in order both to evaporate the refrigerant by circulating in the third heat exchanger 18 and to heat the electrical storage device by circulating in the fourth heat exchanger 19.

[0161] Fig. 20 still illustrates the first loop 9 in its entirety, but this time when the heat transfer fluid circulates in the second direction of circulation 59 opposite to the first direction of circulation 58 illustrated in Figures 18 and 19. The second direction of circulation 59 is imposed here by the first pumping device 12.

[0162] Compared to Figures 18 and 19, the heat transfer fluid flows in the transfer branches 15, 20 in the opposite direction. In other words, the heat transfer fluid flows in the second transfer branch 20 from the main section 10 to the secondary section 11 and in the first transfer branch 15 from the secondary section 11 to the main section 10. Furthermore, compared to Figures 18 and 19, the ports of the first control device 14 through which the heat transfer fluid flows reverse their function, i.e., an inlet port becomes an outlet port and vice versa.

[0163] As described in [Fig. 17], when the heat transfer fluid circulates in the Secondary section 11 according to the second direction of circulation 59, the heat transfer fluid bypasses the fourth heat exchanger 19 by circulating in the bypass branch 22. The second pumping device 16 is inactive here.

[0164] The configuration illustrated in [Fig.20] is used in particular to implement the seventh circulation mode illustrated in [Fig.8], in which the heat generated by the electric motor circulating in the second heat exchanger 13 is used to evaporate the refrigerant within the third heat exchanger 18. According to a circulation mode not illustrated, the configuration illustrated in [Fig.20] can also be used to operate cooling of the electric motor via the second heat exchanger 13 using the third heat exchanger 18.

[0165] Figure 21 is a representation of the second loop 23 alone. For Figures 21 and 22, the direction of flow of the heat transfer fluid is defined by the third pumping device 24. In Figure 21, the direction of flow of the heat transfer fluid is defined by the white arrow of the third pumping device 24. The heat transfer fluid therefore flows in the first direction of flow 58. It should be noted that the directions of flow 58 and 59 of the heat transfer fluid within the second loop 23 illustrated in Figures 21 and 22 are completely independent of the directions of flow 58 and 59 of the heat transfer fluid within the first loop 9 illustrated in Figures 16 to 20.

[0166] When the heat transfer fluid circulates within the second loop 23 in the first direction of circulation 58, the non-return devices 56, 57 are arranged so that the heat transfer fluid circulates to the junction branch 30 without passing through the sixth heat exchanger 26. The first non-return device 56 prevents the circulation of the heat transfer fluid within the sixth heat exchanger 26 at the outlet of the fifth heat exchanger 25 and forces the circulation of the heat transfer fluid within the junction branch 30.

[0167] With reference to the circulation modes described above, by way of non-exhaustive examples, the direction of circulation illustrated in [Fig. 21] is defined to implement the thirteenth circulation mode illustrated in [Fig. 14], where the refrigerant is evaporated with the help of the heat transfer fluid circulating within the fifth heat exchanger 25, the heat transfer fluid subsequently circulating to the main branch via the junction branch 30 so that the calories captured within the fifth heat exchanger 25 are dissipated by the outside air flow within the first heat exchanger, as illustrated in [Fig. 14].

[0168] Fig. 22 still illustrates the second loop 23, but this time when the heat transfer fluid circulates in the second direction of circulation 59 opposite to the first direction of circulation 58 illustrated in Fig. 21.

[0169] When the heat transfer fluid circulates in the second loop 23 in the second direction of flow 59, the second non-return device 57 prevents the circulation of the heat transfer fluid within the main branch via divergence zone 8. The circulation of the heat transfer fluid is therefore forced within the second loop 23 up to the sixth heat exchanger 26.

[0170] The circulation of the heat transfer fluid in the second direction of circulation 59 within the second loop 23 allows circulation of the heat transfer fluid within the sixth heat exchanger 26 in order to operate air conditioning of the vehicle's passenger compartment or to participate in dehumidification of the interior airflow 28. The direction of circulation illustrated in [Fig.22] is therefore defined to implement, by way of example, the fourth circulation mode illustrated in [Fig.5], or the twelfth circulation mode illustrated in [Fig.13].

[0171] Of course, the invention is not limited to the examples just described and many modifications can be made to these examples without departing from the scope of the invention.

[0172] The invention, as described above, achieves its intended purpose and provides a heat transfer fluid circuit that avoids the circulation of refrigerant within a ventilation, heating, and / or air conditioning system, while combining structural simplicity with multiple functions. Variations not described here could be implemented without departing from the scope of the invention, provided that, in accordance with the invention, they include a heat transfer fluid circuit conforming to the invention.

Claims

Claims

1. Heat transfer fluid circuit (2) for a heat treatment system (1) of a vehicle and intended to be traversed by a heat transfer fluid, comprising: - a main branch (4) comprising a first heat exchanger (5) configured to carry out a heat exchange between the heat transfer fluid and an external air flow (6), and extending between a convergence zone (7) and a divergence zone (8), - a first loop (9) comprising a main section (10) and a secondary section (11), the main section (10) starting at the divergence zone (8) and being provided with a second heat exchanger (13) configured to heat treat an electric motor of the vehicle, a first pumping device (12) and a first control device (14), the first control device (14) being configured to circulate the heat transfer fluid to the convergence zone (7) or to the secondary section (11), the secondary section (11) comprising a second pumping device (16), a third heat exchanger (18) configured to carry out a heat exchange between the heat transfer fluid and a refrigerant circulating in a refrigerant circuit (3) and a fourth heat exchanger (19) configured to heat treat an electrical storage device of the vehicle, - a second loop (23) comprising a fifth heat exchanger (25) configured to carry out a heat exchange between the heat transfer fluid and the refrigerant circulating in the refrigerant circuit (3), a third pumping device (24) and a sixth heat exchanger (26) configured to carry out a heat exchange between the heat transfer fluid and an interior air flow (28) intended to be sent into the passenger compartment of the vehicle, the second loop (23) being placed under the control of a second control device (27) configured to circulate the heat transfer fluid towards the second loop (23) up to the sixth heat exchanger (26) or towards the convergence zone (7) by via a junction branch (30), - a third loop (31) comprising a seventh heat exchanger (33) configured to carry out a heat exchange between the heat transfer fluid and the refrigerant circulating in the refrigerant circuit (3), a fourth pumping device (32), a third control device (35) and an eighth heat exchanger (34) configured to carry out a heat exchange between the heat transfer fluid and the interior air flow (28) intended to be sent into the passenger compartment of the vehicle, the third control device (35) being configured to circulate the heat transfer fluid towards the third loop (31) to the eighth heat exchanger (34) or towards the convergence zone (7) via a connection branch (36).

2. A heat transfer fluid circuit (2) according to claim 1, wherein the first loop (9) comprises a first transfer branch (15) between the main section (10) and the secondary section (11), the first transfer branch (15) extending between the first control device (14) and the secondary section (11).

3. Heat transfer fluid circuit (2) according to claim 2, in which the first loop (9) comprises a second transfer branch (20) extending between the main section (10) and the secondary section (11).

4. A heat transfer fluid circuit (2) according to any preceding claim, wherein the secondary section (11) of the first loop (9) comprises an electric heating element (17).

5. Heat transfer fluid circuit (2) according to the preceding claim, in which the first loop (9) comprises a control member (21) and a bypass branch (22), the control member (21) being configured to circulate the heat transfer fluid to the fourth heat exchanger (19) or within the bypass branch (22), the bypass branch (22) being fluidically linked to the control member (21) and being arranged in parallel with the fourth heat exchanger (19).

6. Heat transfer fluid circuit (2) according to any one of the preceding claims, in which the first control device (14) is a three-way valve comprising three ports, at least one port pro- running along the main section (10) to the convergence zone (7) and at least one other port being connected to the secondary section (11), the third control device (35) being a three-way valve comprising three ports, at least one port extending the third loop (31) to the eighth heat exchanger (34) and at least one other port being connected to the convergence zone (7) via the connecting branch (36).

7. Heat transfer fluid circuit (2) according to any one of the preceding claims, in which the second control device (27) is a three-way valve comprising three ports, at least one port extending the second loop (23) to the sixth heat exchanger (26) and another port being connected to the convergence zone (7) via the junction branch (30).

8. A heat transfer fluid circuit (2) according to any preceding claim, in combination with claim 5, wherein the control member (21) is a three-way valve comprising three ports, at least one port extending the secondary section (11) to the fourth heat exchanger (19) and at least one other port being connected to the bypass branch (22).

9. Heat transfer fluid circuit (2) according to any one of claims 1 to 6, wherein the first pumping device (12) and / or the second pumping device (16) and / or the third pumping device (24) are reversible pumps configured to circulate the heat transfer fluid in a first circulation direction (58) or in a second circulation direction (59) opposite to the first circulation direction (58).

10. Heat transfer fluid circuit (2) according to the preceding claim, in combination with claim 5, in which the control member (21) comprises a first non-return valve (53) arranged on the bypass branch (22) and / or a second non-return valve (54) arranged on a pipe (55) of the secondary section (11) which comprises the fourth heat exchanger (19).

11. Heat transfer fluid circuit (2) according to claim 9 or 10, in which the second control device (27) comprises a first non-return device (56) arranged on the second loop (23) and / or a second non-return device (57) arranged in the main branch (4) upstream of the second loop (23).

Images