Cooling production device comprising an improved single-ejector refrigeration cycle and associated cooling production process

Abstract

Cooling production device comprising an improved simple ejector refrigeration cycle and associated cooling production method. The invention is a cooling production device comprising an ejector refrigeration cycle comprising a working fluid circulation circuit comprising three branches arranged in parallel: A driving branch on which are arranged a pump (101) and a generator (102), and a refrigeration branch on which are arranged an expansion valve (103) and an evaporator (104), and a mixing branch on which are arranged an ejector (200) and a condenser (105) characterized in that it comprises a first reversible compression element (300) arranged on the mixing branch downstream of the ejector (200) and upstream of the condenser (105).The invention will find particular application in cooling devices operating from a low-temperature heat source, for example, in the range of 80°C to 150°C, which may be fluctuating or even intermittent. Figure 10 illustrates this point.

Description

Title of the invention: Cooling production device comprising an improved single-ejector refrigeration cycle and associated cooling production method technical field

[0001] The present invention relates to the field of refrigeration production. More particularly, the invention will find its application in refrigeration production devices operating from a low-temperature heat source, for example, in the range of 80°C to 150°C, which may be fluctuating or even intermittent. The invention specifically relates to systems based on a simple ejector refrigeration cycle. It will find applications in stationary refrigeration production for industry or residential use, as well as in mobile refrigeration production applications. STATE OF THE ART

[0002] The supply of energy for refrigeration and air conditioning plays an important role worldwide. Equipment used for refrigeration and air conditioning relies primarily on fossil fuels. Research has led to the use of clean energy sources such as solar, geothermal, and waste heat as direct sources to power this equipment.

[0003] With this in mind, the mechanical compressor, the main source of electrical energy consumption in this equipment, has been replaced by a thermal compressor, also called a thermo-compressor or ejector. Single ejector refrigeration cycles, abbreviated as SERS (Single Ejector Refrigeration System), use an ejector instead of a mechanical compressor. An ejector refrigeration cycle operates using thermal power supplied to a generator (Qgen) which is used to evaporate a high-pressure working fluid. The high-pressure, high-temperature vapor, called the primary fluid, is expanded and used to draw in a low-pressure secondary vapor from an evaporator. It is the passage of the secondary vapor through the evaporator that produces the useful effect of the cycle. Indeed, the secondary fluid evaporates in the evaporator, absorbing the thermal power of the surrounding environment (Qevap), which is then cooled.This cycle exhibits a good COP (Coefficient of Performance), defined as Qevap / / Qgen, around its design point, but if the generator pressure and / or the condenser pressure vary, the COP drops sharply until total machine malfunction occurs.

[0004] The ejectors ([Fig. 1]) are simple components, without moving parts, and are small Expensive systems allow the mixing of two incoming flows: a high-pressure fluid (the primary) and a low-pressure fluid (the secondary), to produce an output flow at an intermediate pressure. The major limitation of ejectors is that, lacking any moving parts, they have no regulation capabilities and therefore lose significant efficiency outside their nominal operating range. Furthermore, when using a fluctuating or even intermittent heat source, such as solar thermal energy, the heat source itself prevents the ejector from operating at its nominal capacity, thus limiting the development of this technology.

[0005] There therefore remains the need to propose a solution for producing cold in a stable and continuous manner independently of the variation in temperatures of the supply sources of a SERS cycle. SUMMARY

[0006] To achieve this objective, according to one embodiment, a cold production device is provided comprising an ejector refrigeration cycle (SERS) including a working fluid circulation circuit comprising three branches arranged in parallel: • a drive branch on which are arranged a pump and a generator designed to ensure heat exchange between a heat source and the working fluid, and • a refrigeration branch on which are arranged an expansion valve and an evaporator designed to extract heat from a source to be cooled, and • a mixing branch on which are arranged an ejector intended to ensure the mixing of the working fluid from the drive branch and the working fluid from the refrigeration branch, and a condenser intended to ensure heat exchange between an intermediate source and the mixed working fluid from the ejector, characterized in that it comprises: • a first reversible compression element arranged on the mixing branch downstream of the ejector and upstream of the condenser.

[0007] The presence of the first reversible compression element at the ejector outlet allows for precise and efficient regulation of the conditions at the ejector outlet, thus enabling operation as close as possible to its nominal operating conditions. In particular, the presence of the first compression element allows the ejector's operation to be adapted according to the conditions of the intermediate source ensuring heat exchange with the condenser. Thus, when the intermediate source, which is advantageously ambient air, heats up or cools down, the pressure in the condenser This increases or decreases the ejector's operation, moving it away from its nominal regime and therefore its COP. The reversible expansion / compression device, or the expansion and compression device, thus allows, depending on the conditions of the intermediate source and therefore the condenser's operation, the compression or expansion of the fluid at the ejector outlet to bring it as close as possible to the ejector's nominal operating range.

[0008] According to another embodiment that can be implemented alone or in combination with the preceding embodiment, a cooling production device comprising an ejector refrigeration cycle (SERS) including a working fluid circulation circuit comprising three branches arranged in parallel: • a drive branch on which are arranged a pump and a generator intended to ensure heat exchange between a heat source and the working fluid, and • a refrigeration branch on which are arranged an expansion valve and an evaporator designed to extract heat from a source to be cooled, and • a mixing branch on which are arranged an ejector intended to ensure the mixing of the working fluid from the drive branch and the working fluid from the refrigeration branch and a condenser intended to ensure heat exchange between an intermediate source and the mixed working fluid, characterized in that it comprises: • a second reversible compression device arranged on the drive branch upstream of the ejector and downstream of the generator.

[0009] The presence of the second reversible compression element at the ejector inlet allows for precise and efficient regulation of the ejector inlet conditions, thus enabling operation as close as possible to its nominal operating range. In particular, the presence of the second expansion / compression element allows the ejector's operation to be adapted according to the conditions of the hot source ensuring heat exchange with the generator. Thus, when the hot source, for example solar thermal energy, heats up or cools down, the pressure in the generator increases or decreases, moving the ejector's operation away from its nominal operating range and therefore its COP.The reversible expansion / compression device, or the expansion and compression device, allows, depending on the conditions of the hot source and therefore the operation of the generator, the compression or expansion of the fluid at the ejector inlet so that it is as close as possible to the nominal operation of the ejector.

[0010] According to another aspect, the invention relates to a method for producing cold from a device such as described above comprising the circulation of a fluid of work in a circulation circuit of a working fluid comprising three branches arranged in parallel: • a drive branch on which are arranged a pump, advantageously ensuring the circulation of a working fluid in the fluidic circuit, and a generator ensuring heat exchange between a heat source and the working fluid, and • a refrigeration branch on which are arranged an expansion valve and an evaporator designed to extract heat from a source to be cooled, and • a mixing branch on which are arranged an ejector ensuring the mixing of the working fluid from the drive branch and the working fluid from the refrigeration branch, and a condenser intended to ensure heat exchange between an intermediate source and the mixed working fluid, characterized in that it comprises: • A first reversible compression device arranged on the mixing branch downstream of the ejector and upstream of the condenser operating alternately in a compression mode so as to compress the working fluid from the ejector before it enters the condenser, or in an expansion mode so as to expand the working fluid from the ejector before it enters the condenser.

[0011] According to another alternative or cumulative aspect to the previous aspect, the invention relates to a method of producing cold from a device as described above comprising the circulation of a working fluid in a working fluid circulation circuit comprising three branches arranged in parallel: • a drive branch on which are arranged a pump, advantageously ensuring the circulation of a working fluid in the fluidic circuit, and a generator ensuring heat exchange between a heat source and the working fluid, and • a refrigeration branch on which are arranged an expansion valve and an evaporator designed to extract heat from a source to be cooled, and • a mixing branch on which are arranged an ejector ensuring the mixing of the working fluid from the drive branch and the working fluid from the refrigeration branch, and a condenser intended to ensure heat exchange between an intermediate source and the mixed working fluid, characterized in that it comprises: • A second reversible compression device arranged on the drive branch upstream of the ejector and downstream of the generator, operating alternately tively according to a compression mode so as to compress the working fluid from the generator before it enters the ejector, or an expansion mode so as to expand the working fluid from the generator before it enters the ejector. BRIEF DESCRIPTION OF THE FIGURES

[0012] The aims, objects, features and advantages of the invention will become clearer from the detailed description of an embodiment thereof, which is illustrated by the following accompanying drawings in which:

[0013] [Fig.1] Fig.1 represents a model of an ejector that can be used in the invention.

[0014] [Fig.2] Figures 2 to 5 represent a first embodiment of the invention. Figure [Fig.2] represents the cold production device with all fluidic connections visible according to this first embodiment.

[0015] [Fig.3] Fig.3 represents the cooling production device in operation according to the first embodiment in the case where the condenser is at a pressure greater than the design pressure of the ejector.

[0016] [Fig.4] [Fig.4] represents the cold production device in operation according to the first embodiment in the case where the condenser is at a pressure lower than the design pressure of the ejector.

[0017] [Fig.5] [Fig.5] represents the cold production device in operation according to the first embodiment in the case where the condenser is at a pressure equal to the design pressure of the ejector.

[0018] [Fig. 6] Figures 6 to 9 represent a second embodiment of the invention. [Fig. 6] shows the cooling production devices with all fluid connections visible according to this second embodiment.

[0019] [Fig.7] [Fig.7] represents the cooling production device in operation according to the second embodiment in the case where the generator has a pressure greater than the design pressure of the ejector

[0020] [Fig.8] [Fig.8] represents the cold production device in operation according to the second embodiment in the case where the generator has a pressure lower than the design pressure of the ejector.

[0021] [Fig.9] [Fig.9] represents the cold production device in operation according to the second embodiment in the case where the generator has a pressure equal to the design pressure of the ejector.

[0022] [Fig. 10] The [Fig. 10] represents the cold production device according to a third embodiment combining the first embodiment and the second embodiment.

[0023] [Fig. 11] Fig. 11 represents the cold production device according to a fourth embodiment that can ensure co-production of cold and electricity.

[0024] The drawings are given by way of example and are not limiting of the invention. They constitute schematic representations of principle intended to facilitate understanding of the invention and are not necessarily to scale with practical applications. DETAILED DESCRIPTION

[0025] Before proceeding to a detailed review of embodiments of the invention, optional features that may be used in combination or alternatively are listed below:

[0026] - By way of example, the first reversible compression element 300 and / or the The second reversible compression unit 400 is of the volumetric type,

[0027] - By way of example, the first reversible compression element 300 arranged on the The mixing branch and the second reversible compression member 400 arranged on the driving branch are mechanically connected so that one reversible compression member 300,400 mechanically drives the other reversible compression member 300,400. Advantageously, this allows the member which performs an expansion of the working fluid to mechanically drive the other member responsible for performing a compression.

[0028] - By way of example, the first reversible compression element 300 arranged on the The mixing branch and the second reversible compression element 400 arranged on the driving branch are electrically connected so that one reversible compression element 300,400 produces electricity used directly or indirectly by the other reversible compression element 300,400. Advantageously, the element that performs an expansion of the working fluid produces electricity which is either stored in a battery or used directly to power the other element responsible for performing a compression.

[0029] - By way of example, the cooling production device includes a battery intended to store the electricity produced by at least one reversible compression unit 300,400 and to supply stored electricity to a reversible compression unit 300,400.

[0030] - By way of example, the refrigeration production device includes a component of additional expansion 500 intended to produce electricity and arranged on a branch parallel to the ejector 200 located between the downstream of the generator 102, or of the second compression element 400 of the driving branch, and the downstream of the ejector 200, preferably upstream of the condenser 105 or of the first reversible compression element 300 of the mixing branch.

[0031] - By way of example, the cooling production device includes a heat exchanger thermal arranged on the mixing branch downstream of ejector 200 and on the driving branch upstream of generator 102 to transfer thermal energy between the mixing branch and the driving branch.

[0032] - By way of example, the hot source is a solar thermal source and the in source The termedial is the ambient air.

[0033] - By way of example, the refrigeration production device includes a module of control comprising a plurality of valves 301, 302, 303, 401, 402, 403 intended to control the circulation of the working fluid in the fluidic circuit and in particular in the first reversible compression element 300. Advantageously, the control module includes a plurality of sensors.

[0034] According to one aspect, the cold production method according to the invention in which the device includes a control module comprises a plurality of valves 301, 302, 303, 401, 402, 403 intended to control the circulation of the working fluid in the fluidic circuit and in particular in the first reversible compression member 300 and a plurality of sensors intended to measure predefined parameters on the fluidic circuit, the method comprising the measurement of predefined parameters on the fluidic circuit by sensors, the comparison of the measurements with predefined values ​​and the alternative implementation of a compression mode or an expansion mode of the first reversible compression member or of a bypass of the first reversible compression member.

[0035] According to one aspect, the cold production process in which alternatively: • when the control module identifies that the pressure in the condenser 105 is greater than a target value of the ejector pressure 200, the control module sets up the expansion mode of the first reversible compression element 300, • when the control module identifies that the pressure in the condenser 105 is lower than a target value for the ejector pressure 200, the control module activates the compression mode of the first reversible compression element 300, • when the control module identifies that the pressure in the condenser 105 is equal to a target value of the ejector pressure 200, the control module sets up the bypass mode of the first reversible compression element 300.

[0036] According to one aspect, the cold production process according to the invention, in which the device includes a control module, comprises a plurality of valves 301, 302, 303, 401, 402, 403 intended to control the circulation of the working fluid in the fluidic circuit and in particular in the second reversible compression element 400 and a plurality of sensors intended to measure predefined parameters on the fluidic circuit, the process comprising the measurement of predefined parameters on the fluidic circuit by sensors, the comparison of the measurements with predefined values ​​and the alternative implementation of a compression mode or a relaxation mode of the second reversible compression element or of a bypass of the second reversible compression element.

[0037] According to one aspect, the cold production process in which alternatively: • when the control module identifies that the pressure in the generator 102 is greater than a target value of the ejector pressure 200, the control module sets up the expansion mode of the second reversible compression element 400, • when the control module identifies that the pressure in the generator 102 is lower than a target value for the pressure of the ejector 200, the control module activates the compression mode of the second reversible compression element 400, • when the control module identifies that the pressure in the generator 102 is equal to a target value of the pressure of the ejector 200, the control module sets up the bypass mode of the second reversible compression member 400.

[0038] The upstream and downstream, the inlet, the outlet, at a given point are taken in reference to the direction of fluid flow.

[0039] A parameter "approximately equal to / greater than / less than" or "of the order of" a given value means that this parameter is equal to / greater than / less than the given value, to within 10% or even 5% of that value.

[0040] The term "fluidically connected" or "in fluidic connection" means when a line provides a connection through or in which a fluid flows.

[0041] In this description, the expression "A fluidically connected to B" is synonymous with "A is in fluidic connection with B" and does not necessarily mean that there is no component between A and B. The expressions "arranged on" or "on" are synonymous with "fluidically connected to." Thus, these expressions refer to a fluidic connection between two elements, this connection being either direct or indirect. This means that it is possible that between a first element and a second element that are fluidically connected, a fluid path exists through one or more conduits, possibly an additional component. Conversely, the term "fluidically connected directly" refers to a direct fluidic connection between two elements. This means that between a first element and a second element that are fluidly connected directly, no other element is present, other than one or more conduits.

[0042] Hot, cold, cooled means a relative temperature with respect to another point in the system.

[0043] The use of the indefinite article "a" or "an" for an element or a step does not exclude, unless otherwise stated, the presence of a plurality of such elements or steps.

[0044] The terms "first", "second" and "third", etc., are used simply as labels and are not intended to impose numerical requirements on their objects.

[0045] An ejector refrigeration cycle, also called a simple ejector refrigeration cycle (SERS), advantageously comprises a pump 101, a generator 102, an expansion valve 103, an evaporator 104, a condenser 105 and an ejector 200.

[0046] Advantageously, the refrigeration cycle includes a fluidic circuit enabling the fluidic connection of the different elements as well as the circulation of a working fluid.

[0047] The fluidic circuit includes a drive branch on which the pump 101 and the generator 102 are arranged. The drive branch extends from the inlet of the pump 101 to the primary fluid inlet 201 of the ejector 200. Advantageously, the drive branch operates at high pressure. The working fluid circulating in this drive branch is preferentially compressed by the pump 101. The pressure in the branches depends strongly on the working fluid. For example, using R600 as the working fluid, the pressure in the drive branch is on the order of 15 bar, for example, between 10 bar (for a heat source at 80 °C) and 35 bar (for a heat source at 150 °C).

[0048] The fluid circuit includes a refrigeration branch on which the expansion valve 103 and the evaporator 104 are arranged. The refrigeration branch extends from the inlet of the expansion valve 103 to the secondary fluid inlet 202 of the ejector 200. Advantageously, the refrigeration branch operates at low pressure. The working fluid circulating in this refrigeration branch is preferentially expanded by the expansion valve 103. For example, for R600, the pressure in the refrigeration branch is on the order of 1.5 bar, for example, between 1 and 2 bar.

[0049] The fluid circuit includes a mixing branch on which the ejector 200 and the condenser 105 are arranged. The mixing branch extends from the inlets 201, 202 of the ejector 200 to the outlet of the condenser 105. Advantageously, the mixing branch operates at an intermediate pressure. The working fluid circulating in this mixing branch is a mixture of the working fluid from the drive branch and the working fluid from the refrigeration branch. By way of example, the pressure in the mixing branch is on the order of 2 bar, for example, between 2 and 2.5.

[0050] As illustrated in all the figures, the three branches of the fluidic circuit are arranged in parallel with each other.

[0051] Preferably, the fluid circuit comprises a drive loop, or primary loop, including the drive branch and the mixing branch. The drive loop includes the ejector 200, the condenser 105, the expansion valve 103, and the generator 102. The working fluid is herein referred to as the driving fluid or primary fluid. The working fluid exits the condenser 105 in liquid form and is herein referred to as the driving fluid or working fluid. The liquid driving fluid is compressed by the pump 101 arranged on the drive branch to be sent to the generator 102. In the generator 102, the compressed liquid driving fluid is vaporized, advantageously by heat transfer from a hot source. At the outlet of the generator 102, the motive fluid in the state of compressed vapor, preferably at high pressure, enters the ejector 200, through the primary fluid inlet 201. The ejector 200 is configured to create an acceleration of the motive fluid.The working fluid carries the vapor from the refrigeration loop, thus mixing the working fluid and the refrigerant. At outlet 206 of the ejector 200, the mixed fluid in vapor form enters the condenser 105 to be condensed.

[0052] Preferably, the fluid circuit comprises a refrigeration loop, or secondary loop, including the refrigeration branch and the mixing branch. The refrigeration loop includes the ejector 200, the condenser 105, the expansion valve 103, and the evaporator 104. The working fluid exits the condenser 105 in liquid form and is herein referred to as the refrigerant or secondary fluid. The liquid refrigerant undergoes a preferably isenthalpic expansion through the expansion valve 103 before being routed to the evaporator 104 for cooling. In the evaporator 104, the refrigeration working fluid is evaporated by recovering thermal energy from a source to be cooled. Preferably, the source to be cooled is ambient air.At the outlet of the evaporator 104, the refrigerant working fluid is in a preferably low-pressure vapor state which is drawn in by the working fluid into the ejector 200 through the secondary fluid inlet 202.

[0053] The working fluid which is sent to the refrigeration branch corresponds to the working fluid which can be carried by the ejector and therefore which is not sucked up by the pump 101.

[0054] The advantage of this simple ejector refrigeration cycle is to replace the work consumed by a compressor with much less work consumed by the pump 101, and with heat supplied to the generator 102 preferably at medium or high temperature.

[0055] Advantageously, the working fluid is selected from ammonia, water, HSC, or HFO.

[0056] The device according to the invention is particularly suitable for use with a heat source whose thermal energy is derived from renewable energy sources. Solar thermal, geothermal, waste heat. The hot source supplies a quantity of energy Qgen into the generator 102 for the benefit of the working fluid. For example, the hot source is at a temperature between 80 and 150 °C. Preferably, the temperature of the working fluid in the generator 102 is around 100 °C.

[0057] At the evaporator 104, the refrigerant working fluid evaporates using the thermal energy of a source to be cooled. The source to be cooled is preferably the ambient fluid, such as air. The source to be cooled supplies a quantity of energy Qevap to the evaporator 104 for the benefit of the refrigerant working fluid. For example, the source to be cooled is at a temperature between -20 °C and 20 °C. Preferably, the temperature of the refrigerant working fluid in the evaporator 104 is around 5 °C.

[0058] At the condenser 105, the mixed working fluid from the ejector, in a vapor state, is condensed to a liquid state at the outlet of the condenser 105. The condensation of the mixed working fluid occurs through the transfer of thermal energy from the mixed working fluid to the environment, and in particular to an intermediate source. The quantity of thermal energy transferred is Qcond. For example, the intermediate source is the environment, such as ambient air. For example, the intermediate source is at a temperature between 20 and 35 °C. Preferably, the temperature of the mixed working fluid in the condenser 105 is around 20 °C.

[0059] The regulator 104 is advantageously a pressure relief valve.

[0060] The ejector 200 is advantageously a steam ejector. The ejector 200 is chosen from a conventional ejector as illustrated in [Fig. 1] or may be a variable section ejector known to those skilled in the art. In [Fig. 1], the ejector 200 comprises a primary fluid inlet 201, a secondary fluid inlet 202, a sonic throat of the primary injector 203, a mixing chamber 204, a diffuser 205, and a mixed working fluid outlet 206. In the ejector 200, the high-pressure flow from the generator 102 accelerates in the primary fluid inlet 201 at the inlet of the sonic throat 203. This creates a low pressure at the outlet of the sonic throat 203. This low pressure is lower than the pressure at the outlet of the evaporator 104, and the refrigerant working fluid in vapor form from the evaporator 104 is drawn into the ejector 200. In the mixing chamber 204, the two flows are mixed.The mixing speed becomes supersonic, which allows the pressure difference between the drive branch and the refrigeration branch to be balanced. Then the mixing speed becomes subsonic in the diffuser 205 and the pressure of the mixed working fluid adapts to the pressure at the inlet of the condenser 105.

[0061] The device according to the invention comprises, in a first aspect, a first component reversible compression unit 300 arranged downstream of ejector 200 and upstream of condenser 105. Advantageously, the first reversible compression unit 300 is arranged on the mixing branch. The first reversible compression element 300 is advantageously designed to maintain the operation of the ejector 200 within its nominal regime, particularly during variations in the conditions of the intermediate source at the condenser 105. Indeed, the intermediate source extends a source advantageously derived from the environment; it is subject to temperature variations that affect the operation of the condenser 105. In particular, depending on the amount of sunlight, when it increases, the temperature of the intermediate source at the condenser 105 increases, which contributes to increasing the saturation pressure in the condenser 105. However, it has been observed that when the pressure in the condenser 105 increases, the drive ratio and therefore the COP of the cycle decrease.Conversely, when sunlight decreases, the temperature of the intermediate source at the condenser 105 decreases, which contributes to decreasing the saturation pressure in the condenser 105. However, it has been observed that this decreases the efficiency of the ejector 200.

[0062] It is therefore advantageous to seek to control the pressure of the fluid passing through the condenser 105. For this purpose, the invention includes the first reversible compression member 300 arranged between the outlet of the ejector 200 and the inlet of the condenser 105.

[0063] The first reversible compression element 300 is configured to operate either in compressor mode or in expansion mode. The term "first reversible compression element 300" refers to a single element or to a combination of separate compression and expansion elements. For simplicity, the following description refers to a reversible compression element without limitations, but the description also applies to embodiments in which the device comprises a first compression element and a first expansion element. The use of a single-element first reversible compression element 300 allows for savings in investment, mass, and size by limiting the number of elements in the thermodynamic system.

[0064] The first reversible compression element 300 is advantageously chosen from among positive displacement compressors. This means that the fluid is compressed by reducing the volume of the compression chamber. For example, the compression element is a piston compressor, a screw compressor, a scroll compressor (also called a scroll compressor), or a rotary compressor.

[0065] The first reversible compression unit is advantageously associated with an electric motor or generator referenced 304.

[0066] The refrigeration production device according to the invention advantageously comprises a control module comprising at least one, and preferably a plurality of Control valves are arranged on the fluid circuit to control the circulation of the working fluid in the various branches and components of the device. Preferably, the control module also includes at least one, and preferably a plurality, of measuring devices such as temperature, pressure, and flow sensors, arranged on the fluid circuit of the device.

[0067] According to this first aspect, the device includes a set of fluidic connections G, H, I, J, K, L, M, as well as valves 301,3 102,303 allowing control of the circulation of the mixed working fluid between the outlet of the ejector 200 and the inlet of the condenser 105 and in particular through the first reversible compression member 300.

[0068] Advantageously, the device includes sensors ensuring the measurement of parameters on the fluidic circuit which are collected and analyzed by the control module so that the latter can control the circulation of the working fluid in the fluidic circuit, in particular by actuating valves and the operation of the reversible compression member so as to select alternatively the compression mode, the expansion mode, or the bypass of the reversible compression member.

[0069] Figure [Fig. 2] illustrates the device according to this first aspect of the invention in which all the fluidic connections are represented.

[0070] The outlet of the condenser 105 is fluidically connected by a fluidic connection A, preferably directly, to the inlet of the pump 101. The outlet of the pump 101 is fluidically connected by a fluidic connection B, preferably directly, to the inlet of the generator 102. The outlet of the generator 102 is fluidly connected by a connection C, preferably directly, to the primary fluid inlet 201 of the ejector 200.

[0071] The outlet of the condenser 105 is also fluidically connected by a fluidic connection D, preferably directly, to the inlet of the expansion valve 103. The outlet of the expansion valve 103 is fluidically connected by a fluidic connection E, preferably directly, to the inlet of the evaporator 104. The outlet of the evaporator 104 is fluidly connected by a fluidic connection F, preferably directly, to the secondary fluid inlet 202 of the ejector 200.

[0072] According to the first aspect of the invention, the outlet 206 of the ejector 200 is fluidically connected, preferably directly, via a fluidic connection G to a 3-way valve 301. The 3-way valve 301 is fluidly connected, preferably directly, to the outlet 206 of the ejector 200 via the fluidic connection G, to the 3-way valve 302 via the fluidic connection H, and to the 3-way valve 303 via the fluidic connection L. The 3-way valve 302 is fluidly connected, preferably directly, to the 3-way valve 301 via the fluidic connection H, at the inlet from the condenser 105 by the fluidic connection M, to a first end of the first reversible compression member 300 by the fluidic connection I. The 3-way valve 303 is fluidically connected, preferably directly, to the 3-way valve 301 by the fluidic connection L, to a second end of the first reversible compression member 300 by the fluidic connection J and to the inlet of the condenser 105 by the fluidic connection K.

[0073] Figure 3 illustrates the device according to this first aspect of the invention in a first embodiment in which the condenser is at a pressure higher than the design pressure of the ejector 200. The aim here is to compress the mixing fluid between the outlet 206 of the ejector 200 and the inlet of the condenser 105. The control module is thus configured to allow the circulation of the mixed working fluid in the first reversible compression element 300 operating in compression mode. The control module is configured to direct the mixed working fluid exiting the outlet 206 of the ejector 200 into the first reversible compression element 300 operating in compression mode and then to direct the compressed mixed working fluid towards the inlet of the condenser 105.

[0074] In the case of [Fig. 3], the control module identifies a difference between the measured parameters and the target values. More specifically, the control module identifies that the pressure in the condenser 105 is higher than the target design pressure of the ejector 200. The control module selects the compression mode to increase the pressure.

[0075] More specifically, the mixed working fluid exits through the outlet 206 of the ejector 200 and then enters the 3-way valve 301, preferably directly, through the fluid connection G. The 3-way valve 301 is configured to direct the mixed working fluid to the fluid connection H, which in turn directs the mixed working fluid to the 3-way valve 302. The 3-way valve 302 is configured to direct the mixed working fluid to the fluid connection I. The mixed working fluid flows from the 3-way valve 302, preferably directly, to the first end of the first reversible compression member 300. With the first reversible compression member 300 in compression mode, the mixed working fluid is compressed. The mixed working fluid exits the first reversible compression member 300 through its second end.The compressed mixed working fluid exiting the first reversible compression unit 300 flows through the 3-way valve 303, preferably directly, via the fluid connection J. The 3-way valve 303 is configured to direct the compressed mixed working fluid into the fluid connection K, bringing the compressed mixed working fluid to the inlet of the condenser 105.

[0076] Figure 4 illustrates the device according to the first aspect of the invention following a A second embodiment in which the condenser is at a pressure lower than the design pressure of the ejector 200. The aim here is to expand the mixing fluid between the outlet 206 of the ejector 200 and the inlet of the condenser 105. The control module is thus configured to allow the circulation of the mixed working fluid in the first reversible compression element 300 operating in expansion mode. The control module is configured to direct the mixed working fluid exiting the outlet 206 of the ejector 200 into the first reversible compression element 300 operating in expansion mode, and then to direct the expanded mixed working fluid to the inlet of the condenser 105.

[0077] In the case of [Fig. 4], the control module identifies a difference between the measured parameters and the target values. More specifically, the control module identifies that the pressure in the condenser 105 is lower than the target design pressure of the ejector 200. The control module selects the expansion mode to reduce the pressure

[0078] More specifically, the mixed working fluid exits through the outlet 206 of the ejector 200 and then enters the 3-way valve 301, preferably directly, through the fluid connection G. The 3-way valve 301 is configured to direct the mixed working fluid to the fluid connection L, which then directs the mixed working fluid to the 3-way valve 303. The 3-way valve 303 is configured to direct the mixed working fluid to the fluid connection J. The mixed working fluid flows from the 3-way valve 303 preferably directly to the second end of the first reversible compression member 300. With the first reversible compression member 300 in expansion mode, the mixed working fluid is expanded. The mixed working fluid exits the first reversible compression member 300 through its first end.The relaxed mixed working fluid exiting the first reversible compression unit 300 flows through the 3-way valve 302, preferably directly, via the fluid connection I. The 3-way valve 302 is configured to direct the relaxed mixed working fluid towards the fluid connection M, bringing the relaxed mixed working fluid to the inlet of the condenser 105.

[0079] Figure 5 illustrates the device according to this first aspect of the invention in an embodiment in which the condenser 105 is at a pressure equivalent to the design pressure of the ejector 200. In this configuration, it is not necessary to act on the mixed working fluid between the outlet 206 of the ejector 200 and the inlet of the condenser 105. The control module is configured to direct the mixed working fluid from the outlet 206 of the ejector 200, preferably directly, to the inlet of the condenser 105. The control module is configured to direct the mixed working fluid into a bypass of the first compression element. reversible 300. The cycle illustrated in [Fig.5] corresponds to a classic SERS single ejector refrigeration cycle.

[0080] In the case of [Fig. 5], the control module does not detect any difference between the measured parameters and the target values. More specifically, the control module determines that the pressure in the condenser 105 corresponds to the target design pressure of the ejector 200. The control module then selects the bypass mode for the reversible compression element.

[0081] More preferably, the mixed working fluid exits through the outlet 206 of the ejector 200 and then enters the 3-way valve 301, preferably directly, through the fluid connection G. The 3-way valve 301 is configured to direct the mixed working fluid towards the fluid connection H, bringing the mixed working fluid to the 3-way valve 302. The 3-way valve 302 is configured to direct the mixed working fluid towards the fluid connection M, bringing the mixed working fluid to the inlet of the condenser 105.

[0082] According to one possibility, the first reversible compression element 300, in compression mode, is powered by electrical energy from, for example, a battery or a conventional electrical network. In expansion mode, the first reversible compression element 300 is advantageously connected to a battery so as to store the electrical energy produced by the expansion of the mixed working fluid for later use.

[0083] The device according to the invention comprises, in a second aspect, a second reversible compression element 400 arranged upstream of the ejector 200 and downstream of the generator 102. Advantageously, the second reversible compression element 400 is arranged on the drive branch. The second reversible compression element 400 is advantageously designed to maintain the operation of the ejector 200 within its nominal range, particularly during variations in the conditions of the hot source at the generator 102. Indeed, since the hot source is advantageously drawn from the environment, it is subject to temperature variations that affect the operation of the condenser 105. In particular, depending on the amount of sunlight, when it increases, the temperature of the hot source at the generator 102 increases, which contributes to increasing the saturation pressure in the generator 102.However, it has been observed that when the pressure in generator 102 increases, the drive ratio and therefore the COP of the cycle decrease. Conversely, when sunlight decreases, the temperature of the hot source at generator 102 decreases, which contributes to a decrease in the saturation pressure in generator 102. This has been observed to decrease the efficiency of ejector 200.

[0084] It is therefore advantageous to seek to control the pressure of the fluid exiting the generator 102. To this end, the invention includes the second compression element reversible 400 arranged between the outlet of generator 102 and the inlet 201 of the primary fluid of ejector 200.

[0085] The second reversible compression element 400 is configured to operate either in compressor mode or in expansion mode. A reversible compression element is understood to be a single element, or a separate compression element and expansion element instead of a single second reversible compression element. In the following description, only a reversible compression element is referred to for simplicity and without limitation; however, the description also applies to embodiments in which the device includes a second compression element and a second expansion element. The use of a second reversible compression element 400 consisting of a single element allows for savings in investment, mass, and size by limiting the number of elements in the thermodynamic system.

[0086] The second reversible compression element 400 is advantageously chosen from among positive displacement compressors. This means that the fluid is compressed by reducing the volume of the compression chamber. For example, the compression element is a piston compressor, a screw compressor, a scroll compressor (also called a scroll compressor), or a rotary compressor.

[0087] The choice of a reversible compression element 300,400 allows operation alternately in compression expansion mode as well as advantageously to have variable flow operation, through regulation of its rotation speed as well as its ability to operate over a compression ratio range.

[0088] The second reversible compression unit is advantageously associated with an electric motor or generator referenced 404.

[0089] According to this second aspect, the device includes a set of fluidic connections N, O, P, Q, R, S, T, as well as valves 401, 402, 403 allowing control of the circulation of the engine working fluid between the outlet of the generator 102 and the inlet 201 of the ejector 200 and in particular through the second reversible compression member 400.

[0090] Figure 6 illustrates the device according to this second aspect of the invention in which all the fluidic connections are represented.

[0091] The outlet of the condenser 105 is fluidically connected via a fluid connection A, preferably directly, to the inlet of the pump 101. The outlet of the pump 101 is fluidly connected via a fluid connection B, preferably directly, to the inlet of the generator 102. The outlet of the generator 102 is fluidly connected, preferably directly, via a connection N, to a 3-way valve 401. The 3-way valve 401 is fluidly connected, preferably directly, to the outlet of the generator 102 via the fluid connection N, to the The 3-way valve 402 is fluidically connected, preferably directly, to the 3-way valve 401 via fluidic connection S, to the inlet 201 of the primary fluid of the ejector 200 via fluidic connection R, and to a second end of the second reversible compression member 400 via fluidic connection Q. The 3-way valve 403 is fluidically connected, preferably directly, to the 3-way valve 401 via fluidic connection O, to a first end of the second reversible compression member 400 via fluidic connection P, and to the inlet 200 of the primary fluid of the ejector 200 via fluidic connection T.

[0092] The outlet of the condenser 105 is also fluidically connected by a fluidic connection D, preferably directly, to the inlet of the expansion valve 103. The outlet of the expansion valve 103 is fluidically connected by a fluidic connection E, preferably directly, to the inlet of the evaporator 104. The outlet of the evaporator 104 is fluidly connected by a fluidic connection F, preferably directly, to the secondary fluid inlet 202 of the ejector 200.

[0093] According to the second aspect of the invention, the outlet 206 of the ejector 200 is fluidically connected, preferably directly, by a fluidic connection U to the inlet of the condenser 105.

[0094] Figure 7 illustrates the device according to this second aspect of the invention following a The first embodiment in which the generator 102 is at a pressure higher than the design pressure of the ejector 200. The aim here is to expand the working fluid between the outlet of the generator 102 and the inlet 201 of the ejector 200. The control module is thus configured to allow the circulation of the working fluid in the second reversible compression element 400 operating in expansion mode. The control module is configured to direct the working fluid exiting the generator 102 into the second reversible compression element 400 operating in expansion mode and then to direct the expanded working fluid to the inlet 201 of the ejector 200.

[0095] Advantageously, sensors measure parameters of the fluidic circuit, which are transmitted to the control module. The measured parameters are compared to target values ​​by the control module. Depending on the difference between the measured parameters and the target values, the control module selects the appropriate operating mode: alternatively, compression mode, expansion mode, or bypass of the reversible compression element. In the case of [Fig. 7], the control module identifies a difference between the measured parameters and the target values. More specifically, the control module identifies that the pressure in the generator 102 is higher than the target design pressure value of the ejector 200. The The control module selects the decompression mode to reduce the pressure.

[0096] More specifically, the engine working fluid exits the generator 102 and then enters the 3-way valve 401, preferably directly, through the fluid connection N. The 3-way valve 401 is configured to direct the engine working fluid to the fluid connection O, which directs the engine working fluid to the 3-way valve 403. The 3-way valve 403 is configured to direct the engine working fluid to the fluid connection P. The engine working fluid flows from the 3-way valve 403, preferably directly, to the first end of the second reversible compression member 400. With the second reversible compression member 300 in expansion mode, the engine working fluid is expanded. The engine working fluid exits the second reversible compression member 400 through its second end.The expanded engine working fluid exiting the second reversible compression member 400 flows through the 3-way valve 402, preferably directly, via the fluid connection Q. The 3-way valve 402 is configured to direct the expanded engine working fluid into the fluid connection R, bringing the expanded engine working fluid to the inlet 201 of the ejector 200.

[0097] Figure 8 illustrates the device according to the second aspect of the invention in a second embodiment in which the generator 102 is at a pressure lower than the design pressure of the ejector 200. The aim here is to compress the mixing fluid between the outlet of the generator 102 and the inlet 201 of the ejector 200. The control module is thus configured to allow the circulation of the working fluid in the second reversible compression element 400 operating in compression mode. The control module is configured to direct the working fluid exiting the generator 102 into the second reversible compression element 400 operating in compression mode and then to direct the compressed working fluid towards the inlet 200 of the ejector 200.

[0098] In the case of [Fig. 8], the control module identifies a difference between the measured parameters and the target values. More specifically, the control module identifies that the pressure in the generator 102 is lower than the target design pressure value of the ejector 200. The control module selects the compression mode to increase the pressure.

[0099] More specifically, the engine working fluid exits through the generator outlet 102 and then enters the 3-way valve 401, preferably directly, through the fluid connection N. The 3-way valve 401 is configured to direct the engine working fluid to the fluid connection S, bringing the engine working fluid to the 3-way valve 402. The 3-way valve 402 is configured to direct the engine working fluid to the fluid connection Q. The engine working fluid flows from the 3-way valve 402, preferably directly, to the second end of the Second reversible compression member 400. With the second reversible compression member 400 in compression mode, the working fluid is compressed. The compressed working fluid exits the second reversible compression member 400 at its first end. The compressed working fluid exiting the second reversible compression member 400 flows through the 3-way valve 403, preferably directly, via the fluid connection P. The 3-way valve 403 is configured to direct the compressed working fluid to the fluid connection T, bringing the compressed working fluid to the inlet 201 of the ejector 200.

[0100] Figure 9 illustrates the device according to this second aspect of the invention in an embodiment in which the generator 102 is at a pressure equivalent to the design pressure of the ejector 200. In this configuration, it is not necessary to act on the working fluid between the outlet of the generator 102 and the inlet 201 of the ejector 200. The control module is configured to direct the working fluid from the outlet of the generator 102, preferably directly, to the inlet 201 of the ejector 200. The control module is configured to direct the working fluid into a bypass of the second reversible compression element 400. The cycle illustrated in Figure 9 corresponds to a conventional single-ejector refrigeration cycle, SERS.

[0101] In the case of [Fig. 9], the control module does not detect any difference between the measured parameters and the target values. More specifically, the control module identifies that the pressure in the generator 102 corresponds to the target value of the design pressure of the ejector 200. The control module selects the bypass mode of the reversible compression element.

[0102] More preferably, the mixed working fluid exits through the outlet of the generator 102 and then enters the 3-way valve 401, preferably directly, through the fluid connection N. The 3-way valve 401 is configured to direct the engine working fluid towards the fluid connection O, bringing the engine working fluid to the 3-way valve 403. The 3-way valve 403 is configured to direct the engine working fluid towards the fluid connection T, bringing the mixed working fluid to the inlet 201 of the ejector 200.

[0103] According to one possibility, the second reversible compression element 400, in compression mode, is powered by electrical energy from, for example, a battery or a conventional electrical network. In expansion mode, the second reversible compression element 400 is advantageously connected to a battery so as to store the electrical energy produced by the expansion of the working fluid for later use.

[0104] According to a third aspect of the invention, the cold production device includes the first reversible compression member 300 and the second reversible compression member 400. This third aspect of the invention is illustrated in [Fig. 10].

[0105] This third aspect of the invention is particularly advantageous since it allows control of both the pressure of the working fluid at the inlet of the ejector and at the outlet of the ejector.

[0106] In this third aspect of the invention, the first reversible compression element 300 and the second reversible compression element 400 are connected. By connected, it is understood that the first reversible compression element 300 and the second reversible compression element 400 are linked together such that the work produced by one of the elements powers the other.

[0107] According to a first possibility, the first reversible compression element 300 and the second reversible compression element 400 are mechanically linked to each other. In this case, one element mechanically drives the other. For example, one of the two elements 300, 400 in expansion mode, which expands the working fluid, mechanically drives, preferably in rotation, the other element 300, 400 in compression mode, which compresses the working fluid.

[0108] According to a second possibility, the first reversible compression element 300 and the second reversible compression element 400 are electrically connected to each other. In this case, an element 300, 400 in expansion mode is connected to an electric generator and thus produces electricity which can either be used directly by the other element 300, 400 in compression mode, or be stored in a battery for later use by either of the elements 300, 400.

[0109] According to a fourth aspect of the invention, the cooling device comprises an additional expansion element 500. The additional expansion element 500 is intended to produce electricity alternatively or simultaneously with the cooling process. The additional expansion element 500 is advantageously arranged on a branch of the ejector 200. More specifically, the additional expansion element 500 is arranged to receive the working fluid. The additional expansion element 500 is arranged between the inlet 201 of the ejector 200 and the outlet 206 of the ejector 200, more precisely, between the inlet of the condenser 105.

[0110] This fourth aspect of the invention can be combined with the first aspect and / or the second aspect of the invention as illustrated in [Fig. 11].

[0111] In [Fig. 11] the components and fluidic connections described with reference to the first aspect of the invention and the second aspect of the invention are shown. In this fourth aspect, the device comprises the fluidic connections V, W, X, Y, Z, Gl, G2 and preferably at least two valves 501, 502.

[0112] More specifically, the 3-way valve 500 is fluidly connected, preferably 3-way valve 502 is connected fluidically, preferably directly, to the 3-way valve 402 via the fluidic connection V, to the 3-way valve 403 via the fluidic connection W, the first end of the additional expansion member 500 via the fluidic connection X. The 3-way valve 502 is connected fluidically, preferably directly, to the second end of the additional expansion member 500, to the 3-way valve 301 via the fluidic connection I have one and the fluidic connection I have of, to the inlet of the condenser 105 via the fluidic connection Z.

[0113] More specifically, regardless of the operating mode of the second reversible compression member 400, the working fluid exits the 3-way valve 403 or the 3-way valve 402 and enters the 3-way valve 501 respectively via the fluid connection V or the fluid connection W. The working fluid exits the 3-way valve 501 and enters the additional expansion member 500 at its first end, preferably directly, via the fluid connection X. The working fluid is expanded in the additional expansion member 500, thus producing electricity, preferably via an electric generator 503. The expanded working fluid exits the additional expansion member 500 at its second end, which is in fluid connection, preferably directly, with the 3-way valve 502 via the fluid connection Y.The expanded working fluid can then be transmitted directly to the condenser 105 via the fluid connection Z.

[0114] In one embodiment, the device and associated method are configured to allow the co-production of electricity and cooling. In this embodiment, the three-way valve 401 allows the fluid to flow simultaneously to the fluid connection, or line, S and the fluid connection, or line, O. The fluid connection S is then fluidly connected to the valve 402, and then the valve 402 is fluidly connected to the valve 501, allowing at least partial circulation of the fluid from the outlet of the generator 102 into the additional expansion member 500 and thus producing electricity, as described above. In parallel, the fluid connection O is then fluidly connected to 403, which is fluidly connected to the inlet of the ejector 200 via the fluid connection T, allowing at least partial circulation of the fluid from the outlet of the generator 102 into the ejector 200 and thus producing cooling, as described above.

[0115] According to an embodiment applicable to any one of the aspects of the invention described above, the cooling device comprises a heat exchanger arranged between the mixing branch and the drive branch. More preferably, the heat exchanger is arranged to ensure heat transfer between the mixed working fluid circulating in the mixing branch and the driving working fluid circulating in the drive branch. More specifically, on the mixing branch The heat exchanger is arranged downstream of the ejector 200 and preferably upstream of the condenser 105, more specifically upstream of the first reversible compression unit 300. More precisely, on the drive branch, the heat exchanger is arranged upstream of the generator 102 and preferably downstream of the pump 101. This heat exchanger allows the transfer of some of the thermal energy from the mixed working fluid to the engine working fluid. This heat exchanger acts as a preheater for the engine working fluid. This arrangement has the advantages of reducing the thermal power required by the generator 102, reducing the size of the generator 102, and reducing the size of the condenser 105. Examples

[0116] A comparison is made numerically between the cycles shown on [Fig.5] or 9 (classical simple ejector cold production cycle without the invention) and on [Fig. 10] (cold production device according to the third aspect of the invention comprising a first reversible compression member 300 and a second reversible compression member 400).

[0117] The comparison is made for the design point of a device presented in Table 1, with butane (R600) as the refrigerant.

[0118] [Tables 1] Typical Configuration Component Generator 102 Hot Source Temperature: 100°C Superheat: 0°C Heat Recovery: 100 kW Condenser 105 Intermediate Source Temperature: 20°C Evaporator 104 Source Temperature to be Cooled: 5°C Superheat: 0°C Pump 101 Flow Rate: 765 kg / h, Efficiency: 80%, Power: 0.6 kW Table 1 - Nominal operating point of the refrigeration cycle

[0119] The geometric design of the ejector 200 for the design point in Table 1 is given in Table 2. The designation of the sections of the ejector 200 refers to [Fig. 2].

[0120] [Tables2] Section Dimension [mm2] Section A 47.56 Section B 151.9 Section C 877 Table 2 - Geometry of the designated ejector

[0121] Table 3 shows the impact of variations in the temperature of the hot source at the generator 102 and of the intermediate source at the condenser 105 on the cycle of Figures 5 or 9. Table 4 shows the impact of variations in the hot source at the generator 102 and of the intermediate source at the condenser 105 on the cycle of [Fig. 10].

[0122] It is clear that at the design point of the cycle, the cycles of [Fig.5] or 9 and of [Fig. 10] give the same results (line 5), because the 2 reversible compression elements are not used at the design point.

[0123] [Tables3] # Tgen (°C) TCOnd (°C) Tevap (°C) QgentkW] Qevap [kW] W ’ ’ pump [kW] îlex [%] 1 85 15 5 73,3 90,3 0,32 23% 2 85 20 5 71,4 23,0 0,31 10% 3 85 25 5 0 0 0 0% 4 100 15 5 102,5 88,5 0,61 14% 5 100 20 5 100,0 84,1 0,60 21% 6 100 25 5 97,4 22,8 0,593 8% 7 115 15 5 140,1 81 1,11 8% 8 115 20 5 136,7 78,3 1,10 13% 9 115 25 5 133,3 75,5 1,09 18% Tableau 3

[0124] [Tableaux4] # Tgen [°C] Tcond [°C] T A evap [°C] Qgen [kW] Qevap [kW] W h ’’ scroll.gene [kW] W n ’’ scroll.cond [kW] W ’’ pump [kW] îlex [%] 1 85 15 5 99,2 87,0 -3,1 2,6 0,43 16% 2 85 20 5 96,6 84,1 -3,1 0 0,42 21% 3 85 25 5 94,1 81,1 -3,1 -3,9 0,41 25% 4 100 15 5 102,5 87,1 0 2,6 0,61 24% 5 100 20 5 100 84,1 0 0 0,60 21% 6 100 25 5 97,4 81,1 0 -3,9 0,59 24% 7 115 15 5 104,9 87,1 1,8 2,6 0,83 27% 8 115 20 5 102,3 84,2 1,8 0 0,82 25% 9 115 25 5 99,8 81,2 1,8 -3,9 0,81 22% Tableau 4

[0125] Table 5 (from the combination of the 2 previous tables) shows the difference in cold production AQevap (kW) and the difference in electricity production AWtot (kW) between the cycle of [Fig. 10] and that of [Fig. 5] or 9.

[0126] [Tables5] # Tgen [°C] Tcond [°C] TA evap [°C] A Qevap [kW] AWw [kW] Absolute Aî|ex Relativ e \i|n Case name 1 85 15 5 -3.33 -0.7189 -7% -31% #1 2 85 20 5 61.1 -3.2663 +12% + 124% #2 3 85 25 5 81.15 -7.4311 +25% + “' #3 4 100 15 5 -1.41 2.5539996 3 +10% + 74% #4 5 100 20 5 0 -3.863E-07 0% 0% #5 =design 6 100 25 5 58.38 -3.8710004 +16% +190% #6 7 115 15 5 6.11 4.6534 +19% +234% #7 8 115 20 5 5.91 2.0886999 7 +12% +95% #8 9 115 25 5 5.7 -1.798 +5% +28% #9 Table 5

[0127] From this comparison table, the following information can be derived regarding the interest of the invention when the temperatures of the sources fluctuate around the design point:

[0128] In case 1 (#1), the device according to the invention is not useful because it produces less cooling while consuming more electricity. This is also evidenced by the reduced exergetic efficiency of the cycle. In this case, it is therefore preferable not to use any of the reversible compression elements 300, 400.

[0129] In one case (#4), the device according to the invention produces 1.4 kW less cooling than a conventional simple ejector cooling device, but allows for the production of an additional 2.5 kW of electricity. This is advantageous when the cooling requirement is constant, since the cooling output remains the same as in the design point, but additional electricity is generated. In fact, even in this case, the exergetic efficiency of the cycle increases with the invention.

[0130] In 3 cases (#2, #6 and #9), the device according to the invention produces more cooling (gain of 61.1kW, 53.38kW and 5.7kW) than a device without the invention, at the cost of higher electrical consumption (overconsumption of 3.2kW, 3.8kW and 1.7kW respectively). However, the electrical COP of the production of The additional cooling capacity, COPeiec,SuP = AQevap / AWtot, is very high (19, 14 in cases #2 and #6), and indeed the exegetical efficiency of the cycle also increases. In these respects, the device according to the invention makes it possible to continue meeting the design cooling requirements with the use of only a modest amount of additional electrical power, much more efficiently than, for example, a normal vapor compression cycle.

[0131] In one case (#3), the device according to the invention allows the cycle to operate whereas it would be stopped without the invention. The gain in cooling production is 81.1 kW for an electrical cost of 7.4 kW (COPeiec,SuP = 11).

[0132] In 2 cases (#7 and #8), the device according to the invention makes it possible to both produce more cold (gain of 6.1kW and 5.9kW) while producing more electricity (gain of 4.6kW and 2kW respectively).

[0133] In conclusion to this quantitative analysis: it should be noted that the device according to the invention is particularly useful in all cases where constant cooling power is required and there are heat sources with fluctuating temperatures.

[0134] In fact, the device according to the invention allows the cycle to always operate in its design point, in some cases thanks to the very efficient use of a small electrical power, and in others even allowing the production of a small electrical power in addition to the cold.

[0135] The invention is not limited to the embodiments previously described and extends to all embodiments covered by the invention.

[0136] List of references 101. Pump 102. Generator 103. Regulator 104. Evaporator 105. Condenser 200. Ejector 201. Primary fluid inlet 202. Secondary fluid inlet 203. Sonic throat of the primary injector 204. Mixing chamber 205. Broadcaster 206. Mixed fluid outlet 207. Section 208. Section 209. Section 210. Section 300. First reversible expansion / compression organ 301. 3-way valve 302. 3-way valve 303. 3-way valve 304. Electricity 400. Second reversible expansion / compression mechanism 401. 3-way valve 402. 3-way valve 403. 3-way valve 404. Electricity 500. Third reversible expansion / compression mechanism 501. 3-way valve 502. 3-way valve 503. Electricity Production A. Fluid connection between the outlet of condenser 105 and the inlet of pump 101 B. Fluid connection between the outlet of pump 101 and the inlet of generator 102 C. Fluid connection between the generator outlet 102 and the primary fluid inlet 201 of the ejector 200 D. Fluid connection between the outlet of condenser 105 and the inlet of expansion valve 103 E. Fluid connection between the outlet of the expansion valve 103 and the inlet of the evaporator 104 F. Fluid connection between the evaporator outlet and the secondary fluid inlet 202 of the ejector 200 G. Fluid connection between the outlet 206 of the ejector 200 and a 3-way valve 301. Gl. Fluid connection between the outlet 206 of the ejector 200 and the inlet of a 3-way valve 502. G2. Fluidic connection between the outlet 206 of the ejector 200 and the inlet of a 3-way valve 301 H. Fluid connection between a 3-way valve 301 and a 3-way valve 302 I. Fluidic connection between a 3-way valve 302 and the first reversible expansion / compression device 300 J. Fluidic connection between the first reversible expansion / compression device 300 and a 3-way valve 303 K. Fluid connection between a 3-way valve 303 and the condenser inlet 105 L. Fluid connection between a 3-way valve 301 and a second 3-way valve 303 M. Fluidic connection between a 3-way valve 302 and the inlet of the condenser 105. N. Fluid connection between the generator outlet 102 and a 3-way valve 401 O. Fluid connection between a 3-way valve 400 and a 3-way valve 403 P. Fluidic connection between a 3-way valve 403 and a second reversible expansion / compression device 400 Q. Fluidic connection between a second reversible expansion / compression device 400 and a 3-way valve 402 R. Fluid connection between a 3-way valve 402 and the primary fluid inlet 201 of the ejector 200 S. Fluid connection between a 3-way valve 401 and a 3-way valve 402 T. Fluid connection between a 3-way valve 403 and the primary fluid inlet 201 of the ejector 200 U. Fluidic connection between the outlet 206 of the ejector 200 and the condenser inlet 105 V. Fluid connection between a 3-way valve 402 and a 3-way valve 501 W. Fluid connection between a 3-way valve 501 and the primary fluid inlet 201 of an ejector 200 X. Fluidic connection between a 3-way valve 501 and a third reversible expansion / compression device Y. Fluidic connection between the third reversible expansion / compression device and a 3-way valve 502 Z. Fluid connection between a 3-way valve 502 and the condenser inlet 105

Claims

Claims

1. Cold production device comprising an ejector refrigeration cycle (SERS) comprising a circuit for circulating a working fluid comprising three branches arranged in parallel: • A driving branch on which are arranged a pump (101) and a generator (102) intended to ensure a heat exchange between a heat source and the working fluid, and • a refrigerating branch on which are arranged an expansion valve (103) and an evaporator (104) intended to ensure heat extraction from a source to be cooled, and • a mixing branch on which are arranged an ejector (200) intended to ensure the mixing of the working fluid from the driving branch and the working fluid from the refrigerating branch and a condenser (105) intended to ensure a heat exchange between an intermediate source and the mixed working fluid,And the device comprising a first reversible compression member (300) arranged on the mixing branch downstream of the ejector (200) and upstream of the condenser (105), Characterized in that it comprises: a second reversible compression member (400) arranged on the driving branch upstream of the ejector (200) and downstream of the generator (102), and that the first reversible compression member (300) arranged on the mixing branch and the second reversible compression member (400) arranged on the driving branch are mechanically connected so that a reversible compression member (300,400) mechanically drives the other reversible compression member (300,400).,

2. Cold production device according to the preceding claim in which the first reversible compression member (300) and / or the second reversible compression member (400) is of the volumetric type.

3. Cold production device according to any one of the preceding claims in which the first reversible compression member (300) arranged on the mixing branch and the second member reversible compression member (400) arranged on the drive branch are electrically connected so that a reversible compression member (300,400) produces electricity used directly or indirectly by the other reversible compression member (300,400).

4. Cold production device according to the preceding claim comprising a battery intended to store the electricity produced by at least one reversible compression member (300,400) and to supply stored electricity to a reversible compression member (300,400).

5. Cold production device according to any one of the preceding claims comprising an additional expansion member (500) intended to produce electricity and arranged on a branch parallel to the ejector (200) between the downstream of the generator (102) of the second compression member (400) of the driving branch, and the downstream of the ejector (200), preferably upstream of the condenser (105) or of the first reversible compression member (300) of the mixing branch.

6. A cold production device according to any one of the preceding claims comprising a heat exchanger arranged on the mixing branch downstream of the ejector (200) and on the driving branch upstream of the generator (102) to transfer thermal energy between the mixing branch and the driving branch.

7. A cold production device according to any one of the preceding claims in which the hot source is a solar thermal source and the intermediate source is ambient air.

8. Cold production device according to any one of the preceding claims comprising a control module comprising a plurality of valves (301, 302, 303, 401, 402, 403) intended to control the circulation of the working fluid in the fluid circuit and in particular in the first reversible compression member (300).

9. Method for producing cold from a device according to any one of the preceding claims comprising the circulation of a working fluid in a circuit for circulating a working fluid comprising three branches arranged in parallel: • a driving branch on which are arranged a pump (100) and a generator (102) ensuring a heat exchange between a heat source and the working fluid, and • a refrigerating branch on which are arranged a expansion valve (103) and an evaporator (104) intended to ensure heat extraction from a source to be cooled, and • a mixing branch on which are arranged an ejector (200) ensuring the mixing of the working fluid from the driving branch and the working fluid from the refrigerating branch and a condenser (105) intended to ensure a heat exchange between an intermediate source and the mixed working fluid, Characterized in that it includes: • A reversible compression member (300) arranged on the mixing branch downstream of the ejector (200) and upstream of the condenser (105) operating alternately in a compression mode so as to compress the working fluid coming from the ejector (200) before it enters the condenser (105), or an expansion mode so as to expand the working fluid coming from the ejector (200) before it enters the condenser (105) and / or a second reversible compression member (400) arranged on the driving branch upstream of the ejector (200) and downstream of the generator (102) operating alternately in a compression mode so as to compress the working fluid coming from the generator (102) before it enters the ejector (200), or an expansion mode so as to expand the working fluid coming from the generator (102) before it enters the ejector (200).

10. Method for producing cold according to the preceding claim in which the device comprises a control module comprising a plurality of valves (301, 302, 303, 401, 402, 403) intended to control the circulation of the working fluid in the fluid circuit and in particular in the first reversible compression member (300) and a plurality of sensors intended to measure predefined parameters on the fluid circuit, the method comprising the measurement of predefined parameters on the fluid circuit by sensors, the comparison of the measurements with predefined values ​​and the alternate establishment of a compression mode or an expansion mode of the first reversible compression member (300).

11. reversible pressure or a bypass of the first reversible compression member. Method for producing cold according to the preceding claim in which alternatively: • when the control module identifies that the pressure in the condenser (105) is greater than a target value of the pressure of the ejector (200), the control module sets up the expansion mode of the first reversible compression member (300), • when the control module identifies that the pressure in the condenser (105) is lower than a target value of the pressure of the ejector (200), the control module sets up the compression mode of the first reversible compression member (300), • when the control module identifies that the pressure in the condenser (105) is equal to a target value of the ejector pressure (200), the control module sets up the bypass mode of the first reversible compression member (300).

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