Battery thermal management system for electric or hybrid vehicles

Abstract

Thermal management device for an electric or hybrid motor vehicle comprising a thermal management circuit (1) within which a refrigerant is intended to circulate, said thermal management circuit (1) comprising a main loop (A) comprising, in the direction of refrigerant circulation, - a compressor (2), - a first heat exchanger (4), - an ejector (5) having a variable opening diameter and configured to be passable with little or no pressure loss at a so-called maximum opening, - a phase separation device (6) for the refrigerant, - a first expansion device (7), - a second heat exchanger (8) disposed downstream of the first expansion device (7), the thermal management circuit (1) further comprising a first bypass branch (B) connecting the compressor (2) to the first expansion device (7) and comprising a radiator (10),the thermal management circuit (1) comprising a second bypass branch (C) connecting the refrigerant outlet of the radiator (10) to the first heat exchanger (4), said second bypass branch (C) comprising a second expansion device (11). Abbreviated figure: Fig 1,

Description

Title of the invention: Battery thermal management device for electric or hybrid vehicles

[0001] The invention relates to the field of electric and hybrid motor vehicles and more particularly to a thermal management device for the passenger compartment and batteries of such a motor vehicle.

[0002] Current electric and hybrid vehicles increasingly incorporate thermal management systems for both the batteries and the passenger compartment. Indeed, for the batteries to operate at maximum efficiency, they must maintain an optimal operating temperature. Therefore, it is necessary to cool them during use to prevent them from excessively exceeding this optimal operating temperature. Similarly, it may also be necessary to heat them, for example in cold weather, so that the batteries reach this optimal operating temperature as quickly as possible. It is also important to be able to heat or cool the passenger compartment to ensure the comfort of its occupants.

[0003] It is thus known for efficient thermal management of batteries and passenger compartment, to use refrigerant fluid circuits comprising one or more expansion devices and heat exchangers.

[0004] The performance of a refrigerant circuit is generally expressed by a coefficient of performance (COP) which corresponds to the ratio between the heat returned, at the level of the condenser, and the work supplied, in particular by the compressor.

[0005] In order to improve the COP of the air conditioning circuit, it is known to use as an expansion device an ejector which includes: - a first refrigerant inlet, - a refrigerant outlet towards a phase separation device, and - a second refrigerant inlet from a heat exchanger.

[0006] At the level of the phase separation device, the liquid phase of the refrigerant is thus redirected to the heat exchanger and the gaseous phase of the refrigerant is redirected to a compressor.

[0007] However, such an architecture, in order to have optimal efficiency, is generally complex and energy-intensive, particularly to allow all the desired operating modes.

[0008] One of the aims of the present invention is therefore to remedy at least partially the disadvantages of the prior art and to propose an improved management device.

[0009] The present invention relates to a thermal management device for an electric or hybrid motor vehicle comprising a thermal management circuit within which a refrigerant is intended to circulate, said thermal management circuit comprising a main loop comprising, in the direction of refrigerant circulation, - a compressor, - a first heat exchanger intended to be traversed by an external airflow, - an ejector comprising a first refrigerant inlet disposed downstream of said first heat exchanger, a second refrigerant inlet and a refrigerant outlet, said ejector having a variable opening diameter and configured to be passable with little or no pressure loss at a so-called maximum opening, - a refrigerant phase separation device comprising a refrigerant inlet disposed downstream of the refrigerant outlet of the ejector,a first refrigerant outlet in gaseous phase located upstream of the compressor and a second refrigerant outlet in liquid phase, - a first expansion device located downstream of the second outlet of the phase separation device, - a second heat exchanger disposed downstream of the first expansion device and upstream of the second refrigerant inlet of the ejector, the thermal management circuit further comprising a first branch connecting the refrigerant outlet of the compressor to the first expansion device, said first branch comprising a radiator intended to be traversed by an internal airflow, the thermal management circuit comprising a second branch connecting the refrigerant outlet of the radiator on the first branch to the refrigerant inlet of the first heat exchanger on the main branch, said second branch comprising a second expansion device.

[0010] According to one aspect of the invention, the thermal management device includes an internal heat exchanger disposed on the main loop and configured to allow heat exchange between the refrigerant at the outlet of the first heat exchanger and the refrigerant from the first outlet of the phase separation device.

[0011] According to another aspect of the invention, the device is configured to operate in a first operating mode in which: the refrigerant is compressed by the compressor to reach high pressure before passing through the first heat exchanger in which the refrigerant The refrigerant transfers heat energy to the external airflow. It then enters the ejector via its first inlet. The refrigerant passes through the ejector, undergoing an initial pressure drop to reach an intermediate pressure before entering the phase separation device. The liquid refrigerant exits the phase separation device through its second outlet to reach the first expansion device. The refrigerant passes through the first expansion device, undergoing a second pressure drop to reach a low pressure. The refrigerant then passes through the second heat exchanger, where it recovers heat energy by passing at least partially into the gaseous phase. The low-pressure refrigerant then returns to the ejector via its second inlet and mixes with the refrigerant from the first ejector inlet to return to an intermediate pressure.The refrigerant in gaseous phase exits the phase separation device through its first outlet to return to the compressor.

[0012] According to another aspect of the invention, said device is configured to operate in a second operating mode in which: The refrigerant is compressed by the compressor to reach high pressure before entering the first bypass branch and the radiator. The refrigerant passes through the radiator, transferring heat energy to the internal airflow. The refrigerant then enters the second bypass branch and passes through the second expansion device, undergoing an initial pressure drop to reach an intermediate pressure. The refrigerant then passes through the first heat exchanger, where it transfers heat energy to the external airflow. The refrigerant then enters the ejector via its first inlet. The refrigerant passes through the ejector, undergoing a second pressure drop to reach low pressure before entering the phase separation device.The refrigerant in liquid phase exits the phase separation device through its second outlet to reach the first expansion device. The refrigerant passes through the first expansion device without pressure loss. The refrigerant then passes through the second heat exchanger where it recovers heat energy by passing at least partially into the gaseous phase. The low-pressure refrigerant then returns to the ejector via its second inlet and mixes with the refrigerant from the first ejector inlet. The refrigerant in gaseous phase exits the phase separation device through its first outlet to reach the compressor.

[0013] According to another aspect of the invention, said device is configured to operate in a third operating mode in which: The refrigerant is compressed by the compressor to reach high pressure before entering the first bypass branch and the radiator. The refrigerant passes through the radiator, transferring heat energy to the internal airflow. At the radiator outlet, a portion of the refrigerant enters the second bypass branch and passes through the second expansion device, undergoing a pressure loss to reach low pressure. The refrigerant then passes through the first heat exchanger, where it recovers heat energy from the external airflow. The refrigerant then returns to the ejector via its first inlet. The refrigerant passes through the ejector without pressure loss before entering the phase separation device. Upon exiting the radiator, a second portion of the refrigerant in liquid phase joins the main loop upstream of the first expansion device. The refrigerant passes through the first expansion device, undergoing a pressure loss to reach a low pressure. The refrigerant then passes through the second heat exchanger where it recovers heat energy by passing at least partially into the gaseous phase. The low-pressure refrigerant then returns to the ejector via its second inlet and mixes with the refrigerant from the first inlet of the ejector. the refrigerant in gaseous phase exits the phase separation device (6) through its first outlet to reach the compressor.

[0014] According to another aspect of the invention, said device is configured to operate in a fourth operating mode in which: The refrigerant is compressed by the compressor to reach high pressure before entering the first bypass branch and the radiator. The refrigerant passes through the radiator, transferring heat energy to the internal airflow. The refrigerant then enters the second bypass branch and passes through the second expansion device, undergoing a pressure drop to reach low pressure. The refrigerant then passes through the first heat exchanger, where it recovers heat energy from the external airflow, at least partially changing into a gaseous phase. The refrigerant then returns to the ejector via its first inlet. The refrigerant passes through the ejector without pressure loss before entering the phase separation device. The refrigerant in gaseous phase exits the phase separation device through its first outlet to reach the compressor.

[0015] According to another aspect of the invention, the thermal management device comprises a third bypass branch arranged in parallel with the first expansion device and the second heat exchanger, said third bypass branch connecting the second outlet of the phase separation device and the refrigerant outlet. from the first branch of the bypass to the second refrigerant inlet of the ejector, said third branch of the line comprising in the direction of circulation of the refrigerant a third expansion device and a third heat exchanger.

[0016] According to another aspect of the invention, said device is configured to operate in a fifth operating mode in which: The refrigerant is compressed by the compressor to reach high pressure before passing through the first heat exchanger where the refrigerant releases heat energy to the external airflow. The refrigerant then returns to the ejector via its first inlet. The refrigerant passes through the ejector, undergoing an initial pressure loss to reach intermediate pressure before reaching the phase separation device. The refrigerant in liquid phase exits the phase separation device through its second outlet to join the third bypass branch and the third expansion device. The refrigerant passes through the third expansion device, undergoing a second pressure drop to reach low pressure. The refrigerant then passes through the third heat exchanger where it recovers heat energy by passing at least partially into the gaseous phase. The low-pressure refrigerant then returns to the ejector via its second inlet and mixes with the refrigerant from the first inlet of the ejector to return to intermediate pressure. the refrigerant in gaseous phase exits the phase separation device (6) through its first outlet to reach the compressor.

[0017] According to another aspect of the invention, said device is configured to operate in a sixth operating mode in which: The refrigerant is compressed by the compressor to reach high pressure before passing through the first heat exchanger where the refrigerant releases heat energy to the external airflow. The refrigerant then returns to the ejector via its first inlet. The refrigerant passes through the ejector, undergoing an initial pressure loss to reach intermediate pressure before reaching the phase separation device. At the outlet of the second phase separation device, a first part of the refrigerant fluid joins the first expansion device; the refrigerant fluid passes through the first expansion device, undergoing a second pressure loss to reach low pressure; the refrigerant fluid then passes through the second heat exchanger in which it recovers heat energy by passing at least partially into the gaseous phase. At the outlet of the second phase separation device, a second portion of the refrigerant joins the third bypass branch and the third expansion device. The refrigerant passes through the third expansion device, undergoing a second pressure drop to reach a low pressure. The refrigerant then passes through the third heat exchanger, where it recovers heat energy by passing at least partially into the gaseous phase. The low-pressure refrigerant from the first and second heat exchangers then rejoins before returning to the ejector via its second inlet and mixes with the refrigerant from the first inlet of the ejector to return to an intermediate pressure. The refrigerant in gaseous phase exits the phase separation device through its first outlet to reach the compressor.

[0018] According to another aspect of the invention, the thermal management device comprises on the main branch a fourth expansion device, said fourth expansion device being disposed in the direction of circulation of the refrigerant fluid downstream of the compressor and upstream of the refrigerant fluid outlet of the second bypass branch.

[0019] According to another aspect of the invention, said device is configured to operate in a seventh operating mode in which: The refrigerant is compressed by the compressor to reach high pressure. At the compressor outlet, a first portion of the refrigerant passes through the fourth expansion device, undergoing a pressure loss to reach an intermediate pressure. The refrigerant then passes through the first heat exchanger, in which it releases heat energy. The refrigerant then returns to the ejector via its first inlet. The refrigerant passes through the ejector without pressure loss before reaching the phase separation device. At the compressor outlet, a second portion of the refrigerant returns to the first bypass branch and the radiator. The refrigerant passes through the radiator, releasing heat energy to the internal airflow. Upon exiting the radiator, the refrigerant joins the main loop upstream of the third bypass branch. The refrigerant then passes through this third bypass branch and the third expansion device. Passing through the third expansion device, the refrigerant undergoes a pressure drop to reach an intermediate pressure. The refrigerant then passes through the third heat exchanger where it recovers heat energy, passing at least partially into a gaseous phase. The refrigerant then returns to the ejector via its second inlet and mixes with the refrigerant from the first inlet of the ejector. The refrigerant in gaseous phase exits the phase separation device through its first outlet to reach the compressor.

[0020] Other features and advantages of the present invention will become more apparent upon reading the following description, provided by way of illustration and not limitation, and the accompanying drawings in which:

[0021] [Fig-1] Fig. 1 is a schematic representation of a cooling circuit of a thermal management system,

[0022] [Fig.2] Fig.2 is a schematic representation of the refrigerant fluid circuit device of Fig.1 according to a first operating mode,

[0023] [Fig.3] [Fig.3] is a schematic representation of the refrigerant fluid circuit device of [Fig.1] according to a second operating mode,

[0024] [Fig.4] Fig.4 is a schematic representation of the refrigerant fluid circuit device of Fig.1 according to a third operating mode,

[0025] [Fig.5] Fig.5 is a schematic representation of the refrigerant fluid circuit device of Fig.1 according to a fourth operating mode,

[0026] [Fig.6] Fig.6 is a schematic representation of the refrigerant fluid circuit device of Fig.1 according to a fifth operating mode,

[0027] [Fig.7] The [Fig.7] is a schematic representation of the refrigerant fluid circuit device of the [Fig.1] according to a sixth operating mode,

[0028] [Fig.8] The [Fig.8] is a schematic representation of the refrigerant fluid circuit device of the [Fig.1] according to a seventh operating mode.

[0029] In the different figures, the identical elements bear the same reference numbers.

[0030] 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 features apply only to a single embodiment. Simple features from different embodiments can also be combined and / or interchanged to provide other embodiments.

[0031] In this description, certain elements or parameters can be indexed, such as first element or second element, first parameter and second parameter, first criterion and second criterion, etc. In this case, it is simply a matter of indexing to differentiate and name similar but not identical elements, parameters, or criteria. This indexing does not imply any priority of one element, parameter, or criterion over another, and such designations can easily be interchanged without departing from the scope of this description. Nor does this indexing imply any order in time, for example, for evaluating one criterion or another.

[0032] In this description, "placed upstream" means that an element is positioned before another with respect to the direction of fluid flow. Conversely, "placed downstream" means that an element is positioned after another with respect to the direction of fluid flow.

[0033] Figure 1 shows a thermal management device for an electric or hybrid motor vehicle comprising a thermal management circuit 1 through which a refrigerant fluid is intended to circulate. This refrigerant fluid may, for example, be R744.

[0034] This thermal management circuit 1 includes in particular in this illustrated architecture, a main loop A and three branch lines B, C and D.

[0035] The main loop A comprises, in the direction of circulation of the refrigerant fluid, a compression device 2, a first heat exchanger 4, an ejector 5, a phase separation device 6 of the refrigerant fluid, a first expansion device 7 and a second heat exchanger 8.

[0036] The compression device 2 may more particularly be a compressor, comprising a low pressure refrigerant inlet and a high pressure refrigerant outlet.

[0037] The first heat exchanger 4 may in particular be an evaporative condenser or a gas evaporative cooler arranged on the vehicle so as to be traversed by an external airflow, for example at the front.

[0038] The ejector 5 includes, in particular: - a first inlet 5a of refrigerant fluid arranged downstream of said first heat exchanger 4, - a second refrigerant inlet 5b, and - a refrigerant outlet 5c.

[0039] The ejector 5 has a variable opening diameter and is configured to be passable with little or no pressure loss at a so-called maximum opening. This allows, in particular, certain operating modes to be possible with such an architecture.

[0040] The phase separation device 6 of the refrigerant comprises: - a refrigerant inlet 6a disposed downstream of the refrigerant outlet 5c of the ejector 5, - a first outlet 6b of gaseous refrigerant located upstream of compressor 2, and - a second 6c outlet of liquid phase refrigerant.

[0041] The first expansion device 7 is in particular located downstream of the second outlet 6c of the phase separation device 6.

[0042] The second heat exchanger 8 can be an evaporator, for example, located within a heating, ventilation, and air conditioning (HVAC) system. The second heat exchanger 8 is thus designed to carry an airflow destined for the vehicle's passenger compartment. More specifically, the second heat exchanger 8 is located downstream of the first expansion device 7 and upstream of the second refrigerant inlet 5b of the ejector 5.

[0043] The thermal management circuit 1 may also include an internal heat exchanger 9. The internal heat exchanger 9 is located on the main loop A and is configured to allow heat exchange between the refrigerant from the first heat exchanger 4 with the refrigerant from the first outlet 6b of the phase separation device 6. This internal heat exchanger 9 makes it possible in particular to improve the coefficient of performance of the thermal management device 1 in certain operating modes.

[0044] In the example illustrated in [Fig. 1], the internal heat exchanger 9 is located on the main loop A, downstream of the first heat exchanger 4 with regard to its so-called high-pressure part, more particularly between the first heat exchanger 4 and the first refrigerant inlet 5a of the ejector 5. As regards the so-called low-pressure part of the internal heat exchanger 9, the latter is located, also on the main loop A, upstream of the low-pressure refrigerant inlet of the compressor 2, more particularly between the first outlet 6b of the phase separation device 6 and the compressor 2.

[0045] The thermal management circuit 1 may also include on the main branch A a check valve 14 located upstream of the first refrigerant inlet 5a of the ejector 5. More specifically, the check valve 14 is located between the first heat exchanger 4 and the first refrigerant inlet 5a of the ejector 5. As illustrated in [Fig. 1], the check valve 14 is notably located downstream of the internal heat exchanger 9. The check valve 14 is notably configured to prevent the backflow of refrigerant from the second refrigerant inlet 5b of the ejector 5 to the first heat exchanger 4.

[0046] As illustrated in [Fig.1], the thermal management circuit 1 also includes a first branch B connecting the refrigerant outlet of the compressor 2 to the first expansion device 7. This first branch B includes a radiator 10 intended to be traversed by an internal airflow.

[0047] The first branch branch B can thus connect a first connection point 20a to a second connection point 20b. The first connection point 20a is located on the main loop A downstream of the high-pressure refrigerant outlet of the compression device 2, between said fluid outlet high pressure refrigerant of the compression device 2 and the first heat exchanger 4. The second connection point 20b is located on the main loop A, downstream of the second outlet 6c of liquid phase refrigerant of the phase separation device 6, between said second outlet 6c of refrigerant and the second expansion device 7.

[0048] The radiator 10 may be a condenser or a gas cooler located, for example, within a heating, ventilation, and air conditioning system. The radiator 10 is thus also intended to carry an internal airflow destined for the vehicle's passenger compartment. More specifically, the radiator 10 may be located downstream of the second heat exchanger 8, in the direction of the internal airflow.

[0049] The thermal management circuit 1 also includes a first refrigerant redirection device 16, 3 to the first heat exchanger 4 and / or to the first branch B. In the example illustrated in [Fig. 1], this first redirection device includes a first shut-off valve 16 and a fourth expansion device 3, for example, an electronic expansion valve with a shut-off function (described later). The first shut-off valve 16 is located on the first branch B downstream of the first connection point 20a, between the first connection point 20a and the radiator 10. The fourth expansion device 3 is located on the main loop A downstream of the first connection point 20a of the first branch B, between the first connection point 20a and the first heat exchanger 4.Other embodiments of this first redirection device 16, 3 can also be envisaged such as for example a three-way valve disposed on the first connection point 20a of the first branch of bypass B. .

[0050] The thermal management circuit 1 may also include, on the main branch A, a non-return valve 18 located downstream of the phase separation device 6, in particular between the second outlet 6c of the phase separation device 6 and the second connection point 20b of the first branch B. This non-return valve 18 is configured in particular to prevent the backflow of refrigerant fluid from the second branch B to the phase separation device 6.

[0051] The thermal management circuit 1 further comprises a second branch C including a second expansion device 11. This second branch C connects the refrigerant outlet of the radiator 10 on the first branch B to the refrigerant inlet of the first heat exchanger 4 on the main branch A. This second branch C can thus connect a first connection point 30a to a second connection point 30a. connection 30b. The first connection point 30a is located on the first branch branch B downstream of the radiator 10, between the radiator 10 and the second connection point 20b of the first branch branch B. The second connection point 20b is located on the main branch A downstream of the first connection point 20a of the first branch branch A, between the first connection point 20a of the first branch branch A and the first heat exchanger 4.

[0052] The thermal management circuit 1 also includes a second redirection device 11, 17 of the refrigerant to the second branch C and / or to the second heat exchanger 8. In the example illustrated in [Fig. 1], this second redirection device 11, 17 consists of the second expansion device 11, which may be an electronic expansion valve including a shut-off function, and a second shut-off valve 17 located on the first branch B between the first connection point 30a of the second branch C and the second connection point 20b of the first branch B. Other embodiments of this second redirection device 11, 17 can also be considered, such as a three-way valve located on the first connection point 30a of the second branch C or simple shut-off valves.

[0053] The thermal management circuit 1 may also include a third branch line D arranged in parallel with the first expansion device 7 and the second heat exchanger 8. This third branch line D connects the second outlet 6c of the phase separation device 6 and the refrigerant outlet of the first branch line B to the second refrigerant inlet 5b of the ejector 5. The third branch line D can thus connect a first connection point 40a to a second connection point 40b. The first connection point 40a is, in particular, located on the main loop A upstream of the first expansion device 7, between the second connection point 20b of the first branch line B and the first expansion device 7.The second connection point 40b is located on the main branch A downstream of the second heat exchanger 8, between the second heat exchanger 8 and the second refrigerant inlet 5b of the ejector 5.

[0054] The thermal management circuit 1 also includes a third refrigerant redirection device 7, 12 to the third bypass branch D and / or to the second heat exchanger 8. In the example illustrated in [Fig. 1], this third redirection device 7, 12 consists of the first 7 and the third 12 expansion devices, which may be electronic expansion valves with a shut-off function. Other embodiments of this third device Redirection 7, 12 can also be considered as for example a three-way valve arranged on the first connection point 40a of the third branch of bypass D or simple stop valves.

[0055] The third branch D also includes, in the direction of refrigerant flow, a third expansion device 12 and a third heat exchanger 13. The third heat exchanger 13 may be configured to thermally regulate the vehicle's batteries. This third heat exchanger 13 may thus be in direct contact with the batteries or be thermally connected to a heat transfer fluid loop itself configured to thermally manage the batteries.

[0056] The thermal management circuit 1 may also include, on the main branch A, a non-return valve 15 arranged upstream of the second connection point 40b of the third branch D, between the second heat exchanger 8 and said second connection point 40b of the third branch D. The non-return valve 15 is configured in particular to prevent the backflow of refrigerant fluid from the third branch D to the second heat exchanger 8.

[0057] The thermal management circuit 1 may also include, on the main branch A, a fourth expansion device 3. This fourth expansion device 3 is arranged in the direction of refrigerant flow downstream of the compressor 2 and upstream of the refrigerant outlet of the second branch C. More specifically, the fourth expansion device 3 is arranged on the main branch A between the first connection point 20a of the first branch B and the second connection point 30b of the second branch C.

[0058] The first 7, second 11, third 12, and fourth 3 expansion devices can thus be electronic expansion valves incorporating a shut-off function to block the flow of refrigerant when closed. The first 7, second 11, third 12, and fourth 3 expansion devices can also be configured to allow the flow of refrigerant with little or no pressure loss when opened to a so-called maximum opening.

[0059] The thermal management device 1 can be configured to operate according to different operating modes illustrated in Figures 2 to 8. In these figures, arrows are shown to illustrate the direction of refrigerant flow. Active pipes and components are shown with solid lines, and inactive pipes and components are shown with dashed lines.

[0060] First mode of operation:

[0061] The thermal management device 1 can be configured to operate in a first operating mode illustrated in [Fig. 2] and in which the refrigerant The refrigerant is compressed by the compressor 2 to reach high pressure before passing through the first heat exchanger 4, in which the refrigerant releases heat energy to the external airflow. If the fourth expansion device 3 is present, it is opened to its maximum opening so that the refrigerant passes through it with little or no pressure loss. The refrigerant then enters the ejector 5 via its first inlet 5a and passes through said ejector 5, undergoing an initial pressure loss to reach an intermediate pressure before entering the phase separation device 6 via the refrigerant outlet 5c of the ejector 5.

[0062] The refrigerant in liquid phase exits the phase separation device 6 through its second outlet 6c to enter the first expansion device 7.The refrigerant passes through the first expansion device 7, undergoing a second pressure drop to reach a low pressure. The refrigerant then passes through the second heat exchanger 8, where it recovers heat energy by passing, at least partially, into the gaseous phase. The low-pressure refrigerant then returns to the ejector 5 via its second inlet 5b and mixes with the refrigerant from the first inlet 5a of the ejector 5 to return to an intermediate pressure.

[0063] The refrigerant in gaseous phase exits the phase separation device 6 through its first outlet 6b to reach the compressor 2.

[0064] In this first operating mode, the first diverter device 16, 3 is configured so that the refrigerant does not circulate in the first branch B. To achieve this, the first shut-off valve 16 is closed and the fourth expansion device 3 is open. The second diverter device 11, 17 is configured so that the refrigerant also does not circulate in the second branch C. To achieve this, the second expansion device 11 and the second shut-off valve 17 are closed. The third diverter device 7, 12 is configured so that the refrigerant also does not circulate in the third branch D, if the latter is present. To achieve this, the third expansion device 12 is closed.

[0065] This first mode of operation corresponds more particularly to a mode of operation allowing cooling of the internal airflow passing through the second heat exchanger 8 towards the passenger compartment, for example in order to ensure the comfort of the occupants.

[0066] Second mode of operation:

[0067] The thermal management device 1 can be configured to operate in a second operating mode illustrated in [Fig. 3] in which the refrigerant is compressed by compressor 2 to reach high pressure before reaching the first branch B and the radiator 10. The refrigerant The refrigerant flows through the radiator 10, transferring heat energy to the internal airflow. It then enters the second bypass branch C and passes through the second expansion device 11, undergoing an initial pressure drop to reach an intermediate pressure. The refrigerant then flows through the first heat exchanger 4, where it transfers heat energy to the external airflow. Finally, the refrigerant enters the ejector 5 via its first inlet 5a and flows through it, undergoing a second pressure drop to reach a low pressure before entering the phase separation device 6.

[0068] The liquid refrigerant exits the phase separation device 6 through its second outlet 6c to enter the first expansion device 7. The refrigerant passes through the first expansion device 7 without pressure loss. The refrigerant then passes through the second heat exchanger 8 where it recovers heat energy by passing at least partially into the gaseous phase. The low-pressure refrigerant then returns to the ejector 5 via its second inlet 5b and mixes with the refrigerant exiting the first inlet 5a of the ejector 7.

[0069] The refrigerant in gaseous phase exits the phase separation device 6 through its first outlet 6b to reach the compressor 2.

[0070] In this second operating mode, the first redirection device 16, 3 is configured so that the refrigerant exiting the compressor 2 flows into the first bypass branch B. To achieve this, the first shut-off valve 16 is open and the fourth expansion device 3 is closed. The second redirection device 11, 17 is configured so that the refrigerant also flows into the second bypass branch C. To achieve this, the second shut-off valve 17 is closed. The third redirection device 7, 12 is configured so that the refrigerant does not flow into the third bypass branch D if it is present. To achieve this, the third expansion device 12 is closed.

[0071] This second operating mode corresponds more specifically to an operating mode that allows, for example, the demisting of the windshield. Indeed, for this purpose, the internal airflow is cooled by passing through the second heat exchanger 8 and is then heated by the radiator 10 in order to reduce its humidity. In this second operating mode, the heat energy not used to heat the internal airflow via the radiator 10 is transferred to the external airflow via the first heat exchanger 4.

[0072] Third mode of operation:

[0073] The thermal management device 1 can be configured to operate in a third operating mode illustrated in [Fig. 4] in which the refrigerant is compressed by the compressor 2 to reach high pressure before join the first branch of branch B and the radiator 10. The refrigerant fluid passes through the radiator 10, giving up heat energy to the internal airflow.

[0074] Upon exiting the radiator 10, a first portion of the refrigerant flows into the second branch of the bypass C and passes through the second expansion device 11, undergoing a pressure drop to reach a low pressure. The refrigerant then passes through the first heat exchanger 4, where it recovers heat energy from the external airflow. The refrigerant then enters the ejector 5 via its first inlet 5a. The refrigerant flows through the ejector 5 without pressure loss before reaching the phase separation device 6. For this purpose, the ejector 5 is opened to its maximum opening.

[0075] At the outlet of the radiator 10, a second portion of the liquid refrigerant joins the main loop A upstream of the first expansion device 7, passing through the first bypass branch B to its second connection point 20b. The refrigerant passes through the first expansion device 7, undergoing a pressure drop to reach a low pressure. The refrigerant then passes through the second heat exchanger 8, where it recovers heat energy by passing at least partially into the gaseous phase. The low-pressure refrigerant then returns to the ejector 5 via its second inlet 5b and mixes with the refrigerant from the first inlet 5a of the ejector 5.

[0076] The refrigerant in gaseous phase exits the phase separation device 6 through its first outlet 6b to reach the compressor 2.

[0077] In this third operating mode, the first redirection device 16, 3 is configured so that the refrigerant exiting the compressor 2 flows into the first bypass branch B. To achieve this, the first shut-off valve 16 is open and the fourth expansion device 3 is closed. The second redirection device 11, 17 is configured so that the refrigerant flows both into the second bypass branch C and through the first bypass branch B. To achieve this, the second shut-off valve 17 is open. The third redirection device 7, 12 is configured so that the refrigerant does not flow into the third bypass branch D if it is present. To achieve this, the third expansion device 12 is closed.

[0078] In this third mode of operation, the refrigerant also does not use the second outlet 6c of the phase separation device 6. Indeed, the refrigerant from the first branch of the bypass B is at high pressure and by putting pressure on the check valve 18, prevents the low-pressure refrigerant from the second outlet 6c of the phase separation device 6 from passing through said check valve 18.

[0079] This third operating mode corresponds more specifically to an operating mode that allows, for example, the demisting of the windshield. Indeed, for this purpose, the internal airflow is cooled by passing through the second heat exchanger 8 and is then heated by the radiator 10 in order to reduce its humidity. In this third operating mode, the circulation of the refrigerant fluid through the first heat exchanger 4 allows for heat recovery from the external airflow.

[0080] Fourth mode of operation:

[0081] The thermal management device 1 can be configured to operate in a fourth operating mode illustrated in [Fig. 5], in which the refrigerant is compressed by the compressor 2 to reach a high pressure before entering the first bypass branch B and the radiator 10. The refrigerant passes through the radiator 10, transferring heat energy to the internal airflow. The refrigerant then enters the second bypass branch C and passes through the second expansion device 11, undergoing a pressure drop to reach a low pressure. The refrigerant then passes through the first heat exchanger 4, in which the refrigerant recovers heat energy from the external airflow, passing at least partially into a gaseous phase.The refrigerant then enters the ejector 5 via its first inlet 5a. The refrigerant passes through the ejector 5 without pressure loss before reaching the phase separation device 6. For this, the ejector 5 is opened to its so-called maximum opening.

[0082] The refrigerant in gaseous phase exits the phase separation device 6 through its first outlet 6b to reach the compressor 2.

[0083] In this fourth operating mode, the first redirection device 16, 3 is configured so that the refrigerant exiting the compressor 2 flows into the first bypass branch B. To achieve this, the first shut-off valve 16 is open and the fourth expansion device 3 is closed. The second redirection device 11, 17 is configured so that the refrigerant flows into the second bypass branch C. To achieve this, the second shut-off valve 17 is closed. The third redirection device 7, 12 is configured so that the refrigerant does not flow into the third bypass branch D if it is present. To achieve this, the third expansion device 12 is closed.

[0084] In this third mode of operation, the refrigerant also does not use the second outlet 6c of the phase separation device 6. Indeed, the first expansion device 7 is also closed so that the refrigerant cannot pass through either the third branch of bypass D or through the second heat exchanger 8.

[0085] This third operating mode corresponds more particularly to an operating mode allowing heat recovery in the external airflow via the first heat exchanger 4 in order to heat the internal airflow via the radiator 10.

[0086] Fifth mode of operation:

[0087] The thermal management device 1 can be configured to operate in a fifth operating mode illustrated in [Fig. 6], in which the refrigerant is compressed by the compressor 2 to reach a high pressure before passing through the first heat exchanger 4, where the refrigerant releases heat energy to the external airflow. If the fourth expansion device 3 is present, it is opened to its maximum opening so that the refrigerant passes through it with little or no pressure loss. The refrigerant then enters the ejector 5 via its first inlet 5a. The refrigerant passes through the ejector 5, undergoing an initial pressure loss to reach an intermediate pressure before entering the phase separation device 6.

[0088] The liquid refrigerant exits the phase separation device 6 through its second outlet 6c to join the third bypass branch D and the third expansion device 12. The refrigerant passes through the third expansion device 12, undergoing a second pressure drop to reach a low pressure. The refrigerant then passes through the third heat exchanger 13, where it recovers heat energy by passing at least partially into the gaseous phase. The low-pressure refrigerant then returns to the ejector 5 via its second inlet 5b and mixes with the refrigerant from the first inlet 5a of the ejector to return to an intermediate pressure.

[0089] The refrigerant in gaseous phase exits the phase separation device 6 through its first outlet 6b to reach the compressor 2.

[0090] In this fifth operating mode, the first diverter device 16, 3 is configured so that the refrigerant does not circulate in the first branch line B. To achieve this, the first shut-off valve 16 is closed and the fourth expansion valve 3 is open. The second diverter device 11, 17 is configured so that the refrigerant also does not circulate in the second branch line C. To achieve this, the second expansion valve 11 and the second shut-off valve 17 are closed. The third diverter device 7, 12 is configured so that the refrigerant circulates in the third branch line D. To achieve this, the first expansion valve 7 is closed.

[0091] This fifth operating mode corresponds more particularly to an operating mode allowing cooling of the vehicle's batteries via the third heat exchanger 13.

[0092] Sixth mode of operation:

[0093] The thermal management device 1 can be configured to operate in a sixth operating mode illustrated in [Fig. 7], in which the refrigerant is compressed by the compressor 2 to reach a high pressure before passing through the first heat exchanger 4, where the refrigerant releases heat energy to the external airflow. If the fourth expansion device 3 is present, it is opened to its maximum opening so that the refrigerant passes through it with little or no pressure loss. The refrigerant then enters the ejector 5 via its first inlet 5a. The refrigerant passes through the ejector 5, undergoing an initial pressure loss to reach an intermediate pressure before entering the phase separation device 6.

[0094] At the outlet of the second outlet 6c of the phase separation device 6, a first portion of the refrigerant flows into the first expansion device 7. The refrigerant passes through the first expansion device 7, undergoing a second pressure drop to reach a low pressure. The refrigerant then passes through the second heat exchanger 8, in which it recovers heat energy by passing at least partially into the gaseous phase.

[0095] At the outlet of the second outlet 6c of the phase separation device 6, a second portion of the refrigerant flows into the third branch D and the third expansion device 12. The refrigerant passes through the third expansion device 12, undergoing a second pressure drop to reach a low pressure. The refrigerant then passes through the third heat exchanger 13, where it recovers heat energy by passing at least partially into the gaseous phase.

[0096] The low-pressure refrigerant from the first 8 and the second 13 heat exchanger then joins before returning to the ejector 5 via its second inlet 5b. The low-pressure refrigerant mixes with the refrigerant from the first inlet 5a of the ejector 5 to return at intermediate pressure.

[0097] The refrigerant in gaseous phase exits the phase separation device 6 through its first outlet 6b to reach the compressor 2.

[0098] In this sixth operating mode, the first redirection device 16, 3 is configured so that the refrigerant does not circulate in the first branch of the line B. To achieve this, the first shut-off valve 16 is closed and the fourth expansion device 3 is open. The second redirection device 11, 17 is configured so that the refrigerant also does not circulate in the second branch of the line C. To achieve this, the second expansion device 11 and the second shut-off valve 17 are closed. The third redirection device 7, 12 is, for its part configured so that the refrigerant flows both in the third branch of bypass D and in the first heat exchanger 8. For this, the first expansion device 7 and the third expansion device 12 are open.

[0099] This sixth operating mode corresponds more particularly to a mixed operating mode allowing both cooling of the vehicle's batteries and cooling of the internal airflow passing through the second heat exchanger 8 towards the passenger compartment, for example in order to ensure the comfort of the occupants.

[0100] Seventh mode of operation:

[0101] The thermal management device 1 can be configured to operate in a seventh operating mode illustrated in [Fig.8] and in which the refrigerant is compressed by the compressor 2 to reach high pressure.

[0102] At the outlet of compressor 2, a first portion of the refrigerant passes through the fourth expansion device 3, undergoing a pressure drop to reach an intermediate pressure. The refrigerant then passes through the first heat exchanger 4, in which it releases heat energy to the external airflow. The refrigerant then enters the ejector 5 via its first inlet 5a. The refrigerant passes through the ejector 5 without pressure loss before reaching the phase separation device 6. For this purpose, the ejector 5 is opened to its maximum opening.

[0103] At the outlet of the compressor 2, a second part of the refrigerant joins the first branch of the bypass B and the radiator 10. The refrigerant passes through the radiator 10, giving up heat energy to the internal airflow.

[0104] At the outlet of the radiator 10, the refrigerant joins the main loop A upstream of the third branch D, passing through the first branch B to its second connection point 20b. The refrigerant then passes through said third branch D and the third expansion device 12. The refrigerant passes through the third expansion device 12, undergoing a pressure drop to reach an intermediate pressure. The refrigerant then passes through the third heat exchanger 13, where it recovers heat energy by passing at least partially into the gaseous phase. The refrigerant then returns to the ejector 5 via its second inlet 5b and mixes with the refrigerant from the first inlet 5a of the ejector 5.

[0105] The refrigerant in gaseous phase exits the phase separation device 6 through its first outlet 6b to reach the compressor 2.

[0106] In this seventh operating mode, the first redirection device 16, 3 is configured so that the refrigerant at the outlet of the compressor 2 flows both towards the first bypass branch B and through the fourth device Expansion 3. For this, the first shut-off valve 16 and the fourth expansion device 3 are open. The second redirection device 11, 17 is configured so that the refrigerant flows through the first branch B. For this, the second expansion device 11 is closed and the second shut-off valve 17 is open. The third redirection device 7, 12 is configured so that the refrigerant flows through the third branch D. For this, the first expansion device 7 is closed.

[0107] In this seventh mode of operation, the refrigerant also does not use the second outlet 6c of the phase separation device 6. Indeed, the refrigerant from the first branch of the bypass B is at high pressure and, by putting pressure on the check valve 18, prevents the intermediate pressure refrigerant from the second outlet 6c of the phase separation device 6 from passing through said check valve 18.

[0108] This seventh operating mode corresponds more specifically to an operating mode that allows the first heat exchanger 4 to be defrosted in cold weather while maintaining a certain level of comfort in the passenger compartment. Indeed, to achieve this, the refrigerant releases heat energy simultaneously via the radiator 10 to warm the internal airflow and via the first heat exchanger 4 to warm and defrost it. The heat energy required for this is recovered, in particular, from the batteries via the third heat exchanger 13.

[0109] Thus, it is clear that the architecture of the thermal management device 1 allows optimal operation and a multitude of operating modes, in particular thanks to the ejector 5 having a variable opening diameter and configured to be passable with little or no pressure loss at a so-called maximum opening.

Claims

1. Demands Thermal management device for electric or hybrid motor vehicle comprising a thermal management circuit (1) within which a refrigerant fluid is intended to circulate, said thermal management circuit (1) comprising a main loop (A) comprising, in the direction of refrigerant fluid circulation, - a compressor (2), - a first heat exchanger (4) intended to be traversed by an external airflow, - an ejector (5) comprising a first refrigerant inlet (5a) disposed downstream of said first heat exchanger (4), a second refrigerant inlet (5b) and a refrigerant outlet (5c), said ejector (5) having a variable opening diameter and configured to be passable with little or no pressure loss at a so-called maximum opening, - a refrigerant phase separation device (6) comprising a refrigerant inlet (6a) disposed downstream of the refrigerant outlet (5c) of the ejector (5), a first refrigerant outlet (6b) in gaseous phase disposed upstream of the compressor (2) and a second refrigerant outlet (6c) in liquid phase, - a first expansion device (7) arranged downstream of the second outlet (6c) of the phase separation device (6), - a second heat exchanger (8) located downstream of the first expansion device (7) and upstream of the second refrigerant inlet (5b) of the ejector (5), the thermal management circuit (1) further comprising a first bypass branch (B) connecting the refrigerant outlet of the compressor (2) to the first expansion device (7), said first bypass branch (B) comprising a radiator (10) intended to be traversed by an internal airflow, the thermal management circuit (1) comprising a second branch (C) connecting the refrigerant outlet of the radiator (10) on the first branch (B) to the refrigerant inlet of the first heat exchanger (4) on the main branch (A), said second branch (C) comprising a second expansion device (11).

2. Thermal management device according to claim 1, characterized in that it comprises an internal heat exchanger (9) disposed on the main loop (A) and configured to allow heat exchange between the refrigerant at the outlet of the first heat exchanger (4) and the refrigerant from the first outlet (6b) of the phase separation device (6).

3. Thermal management device according to any one of the preceding claims, characterized in that said device is configured to operate in a first mode of operation in which: the refrigerant is compressed by the compressor (2) to reach high pressure before passing through the first heat exchanger (4) in which the refrigerant releases heat energy to the external airflow, the refrigerant then reaches the ejector (5) via its first inlet (5a), the refrigerant passes through the ejector (5) undergoing a first pressure loss to reach intermediate pressure before reaching the phase separation device (6), the refrigerant in liquid phase exits the phase separation device (6) through its second outlet (6c) to reach the first expansion device (7),The refrigerant passes through the first expansion device (7), undergoing a second pressure drop to reach a low pressure. The refrigerant then passes through the second heat exchanger (8) where it recovers heat energy by passing at least partially into the gaseous phase. The low-pressure refrigerant then returns to the ejector (5) via its second inlet (5b) and mixes with the refrigerant from the first inlet (5a) of the ejector (5) to return to an intermediate pressure. The refrigerant in the gaseous phase exits the phase separation device (6) through its first outlet (6b) to return to the compressor (2).

4. Thermal management device according to any one of the preceding claims, characterized in that said device is configured to operate in a second operating mode in which: the refrigerant is compressed by the compressor (2) to reach high pressure before joining the first bypass branch

5. (B) and the radiator (10), the refrigerant flows through the radiator (10) releasing heat energy to the internal airflow, the refrigerant then joins the second bypass branch (C) and passes through the second expansion device (11) undergoing a first pressure drop to reach intermediate pressure, the refrigerant then passes through the first heat exchanger (4) in which the refrigerant releases heat energy to the external airflow, the refrigerant then joins the ejector (5) via its first inlet (5a), the refrigerant flows through the ejector (5) undergoing a second pressure drop to reach low pressure before joining the phase separation device (6), the refrigerant in liquid phase exits the phase separation device (6) through its second outlet (6c) to join the first expansion device (7),The refrigerant passes through the first expansion device (7) without pressure loss; the refrigerant then passes through the second heat exchanger (8) in which it recovers heat energy by passing at least partially into the gaseous phase; the low-pressure refrigerant then returns to the ejector (5) via its second inlet (5b) and mixes with the refrigerant from the first inlet (5a) of the ejector (7); the refrigerant in the gaseous phase exits the phase separation device (6) through its first outlet (6b) to return to the compressor (2). Thermal management device according to any one of the preceding claims, characterized in that said device is configured to operate in a third operating mode in which: The refrigerant is compressed by the compressor (2) to reach high pressure before entering the first bypass branch (B) and the radiator (10). The refrigerant flows through the radiator (10), transferring heat energy to the internal airflow. At the outlet of the radiator (10), a portion of the refrigerant enters the second bypass branch (C) and passes through the second expansion device (11), undergoing a pressure drop to reach low pressure. The refrigerant then passes through the first heat exchanger (4) where it recovers heat energy from the external airflow.

6.

7. The refrigerant then enters the ejector (5) via its first inlet (5a). The refrigerant passes through the ejector (5) without pressure loss before entering the phase separation device (6). At the outlet of the radiator (10), a second part of the refrigerant in liquid phase enters the main loop (A) upstream of the first expansion device (7). The refrigerant passes through the first expansion device (7), undergoing a pressure loss to reach a low pressure. The refrigerant then passes through the second heat exchanger (8) in which it recovers heat energy by passing at least partially into the gaseous phase. The low-pressure refrigerant then returns to the ejector (5) via its second inlet (5b) and mixes with the refrigerant from the first inlet (5a) of the ejector (7).The refrigerant in gaseous phase exits the phase separation device (6) through its first outlet (6b) to reach the compressor (2). Thermal management device according to any one of the preceding claims, characterized in that said device is configured to operate in a fourth operating mode in which: The refrigerant is compressed by the compressor (2) to reach high pressure before joining the first bypass branch (B) and the radiator (10). The refrigerant passes through the radiator (10), transferring heat energy to the internal airflow. The refrigerant then joins the second bypass branch (C) and passes through the second expansion device (11), undergoing a pressure loss to reach low pressure. The refrigerant then passes through the first heat exchanger (4) in which the refrigerant recovers heat energy from the external airflow, passing at least partially into the gaseous phase. The refrigerant then reaches the ejector (5) via its first inlet (5a). The refrigerant passes through the ejector (5) without pressure loss before joining the phase separation device (6).The refrigerant in gaseous phase exits the phase separation device (6) through its first outlet (6b) to reach the compressor (2). A thermal management device according to any one of the preceding claims, characterized in that it comprises a third branch (D) arranged in parallel with the first expansion device (7) and the second heat exchanger (8), said third branch (D) connecting the second outlet (6c) of the phase separation device (6) and the refrigerant outlet of the first branch (B) to the second refrigerant inlet (5b) of the ejector (5), said third branch (D) comprising in the direction of refrigerant flow a third expansion device (12) and a third heat exchanger (13).

8. Thermal management device according to claim 7, characterized in that said device is configured to operate in a fifth operating mode in which: the refrigerant is compressed by the compressor (2) to reach high pressure before passing through the first heat exchanger (4) in which the refrigerant releases heat energy to the external airflow, the refrigerant then reaches the ejector (5) via its first inlet (5a), the refrigerant passes through the ejector (5) undergoing a first pressure loss to reach intermediate pressure before reaching the phase separation device (6), the refrigerant in liquid phase exits the phase separation device (6) through its second outlet (6c) to reach the third bypass branch (D) and the third expansion device (12),The refrigerant passes through the third expansion device (12), undergoing a second pressure drop to reach low pressure. The refrigerant then passes through the third heat exchanger (13) where it recovers heat energy by passing at least partially into the gaseous phase. The low-pressure refrigerant then returns to the ejector (5) via its second inlet (5b) and mixes with the refrigerant from the first inlet (5a) of the ejector to return to intermediate pressure. The gaseous refrigerant exits the phase separation device (6) through its first outlet (6b) to return to the compressor (2).

9. Thermal management device according to any one of claims 7 or 8, characterized in that said device is

10. configured to operate in a sixth operating mode in which: The refrigerant is compressed by the compressor (2) to reach high pressure before passing through the first heat exchanger (4) in which the refrigerant releases heat energy to the external airflow. The refrigerant then reaches the ejector (5) via its first inlet (5a). The refrigerant passes through the ejector (5), undergoing a first pressure loss to reach intermediate pressure before reaching the phase separation device (6). At the outlet of the second outlet (6c) of the phase separation device (6), a first part of the refrigerant fluid joins the first expansion device (7), the refrigerant fluid passes through the first expansion device (7) undergoing a second pressure loss to reach low pressure, the refrigerant fluid then passes through the second heat exchanger (8) in which it recovers heat energy by passing at least partially into the gaseous phase, At the outlet of the second outlet (6c) of the phase separation device (6), a second part of the refrigerant joins the third bypass branch (D) and the third expansion device (12). The refrigerant passes through the third expansion device (12), undergoing a second pressure drop to reach low pressure. The refrigerant then passes through the third heat exchanger (13) where it recovers heat energy by passing at least partially into the gaseous phase. The low-pressure refrigerant from the first (8) and second (13) heat exchangers then rejoins before returning to the ejector (5) via its second inlet (5b) and mixes with the refrigerant from the first inlet (5a) of the ejector (5) to return to intermediate pressure.The refrigerant in gaseous phase exits the phase separation device (6) through its first outlet (6b) to reach the compressor (2). Thermal management device according to any one of the preceding claims, characterized in that it comprises on the main branch (A) a fourth expansion device (3), said fourth expansion device (3) being arranged in the direction of

11. circulation of the refrigerant downstream of the compressor (2) and upstream of the refrigerant outlet of the second bypass branch (C). Thermal management device according to claim 10, characterized in that said device is configured to operate in a seventh operating mode in which: The refrigerant is compressed by the compressor (2) to reach high pressure, At the outlet of the compressor (2), a first part of the refrigerant passes through the fourth expansion device (3), undergoing a pressure loss to reach an intermediate pressure. The refrigerant then passes through the first heat exchanger (4), in which it releases heat energy. The refrigerant then reaches the ejector (5) via its first inlet (5a). The refrigerant passes through the ejector (5) without pressure loss before reaching the phase separation device (6). At the outlet of the compressor (2), a second part of the refrigerant reaches the first bypass branch (B) and the radiator (10). The refrigerant passes through the radiator (10), releasing heat energy to the internal airflow. At the outlet of the radiator (10), the refrigerant rejoins the main loop (A) upstream of the third bypass branch (D).The refrigerant passes through said third bypass branch (D) and the third expansion device (12). The refrigerant passes through the third expansion device (12), undergoing a pressure loss to reach an intermediate pressure. The refrigerant then passes through the third heat exchanger (13) in which it recovers heat energy by passing at least partially into the gaseous phase. The refrigerant then returns to the ejector (5) via its second inlet (5b) and mixes with the refrigerant from the first inlet (5a) of the ejector (5). The refrigerant in the gaseous phase exits the phase separation device (6) through its first outlet (6b) to return to the compressor (2).

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