Heat pump with two thermal energy storage and discharge systems

Abstract

The present invention relates to a heat pump, at least one of the at least two thermal energy storage systems is configured to store thermal energy in a hot form at a temperature between +100 ° C and +800 ° C; at least one of the at least two thermal energy storage systems is configured to store thermal energy in cold form at a temperature between -100°C and +150°C; at least one thermal energy emission system is configured to emit heat and / or cold, either separately or in parallel, over time; or At least one thermal energy emission system is configured to operate in a parallel emission mode, which can be alternated over time with an operating mode of separate emission of heat and / or cold.

Description

[Technical field]

[0001] The present invention relates to an electric heat pump comprising at least two thermal energy storage systems allowing thermal energy release between -100°C and +800°C, in particular in the form of hot heat at temperatures between +100°C and +800°C and / or in the form of cold heat at temperatures between -100°C and +150°C, as well as to a method for supplying such thermal energy using such a heat pump. In the context of the present invention, "cold heat" is to be understood as "relative" cold heat compared to the temperature involved in the generation of thermal energy in the form of hot heat.

[0002] In its 2019 report (Decarbonizing the Electricity sector & Beyond; Report from the 2019 ASPEN Winter Energy Roundtable), the ASPEN Winter Energy Roundtable identified five key elements involved in achieving deep decarbonization of the energy system: 1. Maximize energy efficiency to reduce energy requirements. 2. Decarbonize the electricity supply. 3. Economy-wide electrification to propel clean electricity to other sectors. 4. Utilize carbon-free fuels for the remaining areas that cannot be efficiently electrified. 5. Use carbon capture, utilization and storage (CCUS), and carbon dioxide removal (CDR) for areas where fossil fuels are still needed and to achieve negative emissions.

[0003] There has been a lot of effort, investment and innovation in these areas.

[0004] Efforts to improve energy efficiency in industry include: - improvements and investments in energy efficient technologies such as heat pumps and cooling units; and - Recovery of so-called "waste" energy: again, the use of heat pumps, ORC systems (Organic Rankine Cycle) or the simple storage of thermal energy (i.e. release with an efficiency less than 1).

[0005] Waste energy is the residual energy (i.e., that which is lost if not captured) generated by buildings and industries.

[0006] Efforts to decarbonise the power grid and meet the need for flexibility, especially with regard to storage, will in particular: -Large investments in renewable energies (wind, solar, tidal and hydro). However, the intermittency of most of these sources of generation is a major problem, e.g. - through the activation of electrical storage or electricity consumption systems when the grid is overloaded; and -leading to an increased need for flexibility, i.e. simultaneous matching of electricity demand and generation, through systems for shedding electrical loads (machines) or for using electrical storage in case of shortages.

[0007] This is the sector that is likely to see the most investment. Historically dominated by pumped hydro storage systems (also known as pumped hydro storage or PHS) and, more recently, by large-scale Li-ion battery systems, the electricity storage sector has seen the emergence of many new technologies.

[0008] When powering high-temperature industrial processes, the need and generation of high-temperature heat and cooling is rarely optimized at the design stage. The industries are separate, since the manufacture of high-temperature and very-high-temperature heat-generating equipment (boilers, burners, furnaces, steam, etc.) is one discipline in itself, and the manufacture of low-temperature and very-low-temperature cold-generating equipment (cooling units, refrigeration, cryogenics, etc.) is another. This follows a historical and technological logic that explains the separation of the two sectors and their specific characteristics.

[0009] However, end-use industries have long since integrated the reliability (i.e. constant availability) and low cost of industrial heat, especially gas and / or fuel oil, into their practices and business models for their needs above 100°C. With 2019 costs of around 50-55 euros per MWh of thermal energy from natural gas in France (ADEME, brochure reference 010895, January 2020, 51-85 euros per MWh), as well as in many other European countries (for large sites), it is very difficult for manufacturers to electrify their own heat generation facilities or replace them with renewable energy-based generation facilities, since this would entail additional heat costs of around 50% or more (again, additional costs, technical limitations and intermittency problems).

[0010] In addition, it is interesting to note that many sectors have industrial processes that require: -High temperature heat (>100~120℃ and up to 400℃), and -Low temperature / freezing (down to -50°C).

[0011] For example, these needs are particularly found in the following industries: - Agricultural foods (especially ready-made meals, dried foods, powders (milk, coffee, etc.)), -Medicines (powders, pills...), -Petrochemicals (gas and oil, plastics, rubber, etc.), chemicals in the broad sense, such as adhesives (product preparation, packaging and storage), and - Certain supermarkets and large catering establishments (especially fast food restaurants).

[0012] In this connection, specific heat pump systems for simultaneous heating and cooling are known from the prior art.

[0013] For example, German Patent No. 102018221850(A1) discloses a heat pump system enabling heating and cooling (-15°C to 60°C), in which a liquid-liquid heat pump is connected on one side to a heat source and on the other side to a heat sink, and which is characterized in particular by a hot water tank.

[0014] Application Publication No. 2016211830(A) discloses the use of a heat pump for heating and cooling. More specifically, the temperature range disclosed is from 0°C to about 100°C.

[0015] Patent No. 3037649 (B2) discloses a dehumidifying air conditioning system that increases the energy efficiency of the entire air conditioning system to reduce operating costs while minimizing energy consumption during the day and minimizing heat radiation to the outside air during nighttime heat accumulation.

[0016] However, none of these systems are capable of simultaneously or alternating between high and / or very high heat and low and / or very low cold.

[0017] Other systems exist for storing heat and cold, possibly simultaneously, in the specific context of the manufacturing and power supply industries. EP 2220343, EP 2574740, US 10907510, US 8627665, US 20140223910 can illustrate this type of technology. However, the devices described in these documents are specific to the electricity manufacturing and supply industry, as they are specifically designed for electricity storage and are therefore dimensioned to operate in a "temperature re-equilibration must" cycle after filling and discharging. Therefore, such devices cannot be used in other industries (particularly mentioned above) or even personally. Summary of the Invention

[0018] It is therefore an object of the present invention to overcome the drawbacks of the prior art by providing an electric heat pump, the electric heat pump comprising: - at least two thermal energy storage systems; at least one thermal energy release system, At least one of the thermal energy storage systems is configured to store thermal energy in a hot form at a temperature between +100 ° C and +800 ° C; At least one of the thermal energy storage systems is configured to store thermal energy in cold form at a temperature between -100°C and +150°C; - the at least one thermal energy emission system is configured to emit heat and / or cold, either separately or in parallel; or The at least one thermal energy discharge system is configured to operate in a parallel discharge mode that can be alternated with operation in time-separate discharge modes of hot and / or cold, the heat pump being configured with a reverse Brayton cycle (e.g., no phase change) operating on gas and comprising a single-stage centrifugal electric turbocharger.

[0019] The simultaneous generation of two flows (hot and cold, usually negative) allows to achieve better energy performance and provide manufacturers with thermal energy supply solutions that significantly reduce CO2 emissions without increasing the generation costs, or even reduce them depending on the price of locally available energy sources. Furthermore, the use of a single-stage centrifugal electric turbocharger increases the compactness and efficiency of the heat pump as well as reduces its cost. In addition, such a single-stage centrifugal electric turbocharger operates without oil, preventing any contamination or acidification in the system. The use of a single turbocharger means that there is only one operating point (usually defined by the flow rate / compression ratio) for the compressor / turbine pair in the gas circulation circuit, common to the charge and discharge cycles of the heat pump.

[0020] The term "single turbocharger", also known as "single turbomachine", is used in the context of the present invention to mean a single machine capable of both simultaneously increasing gas pressure and reducing gas pressure at another point in the circuit. In addition to the high-power radial turbocharger, there are at least two types of radial turbochargers: piston turbochargers (usually referred to as "compressors") and centrifugal turbochargers. Centrifugal turbochargers have fewer frictional moving parts, are relatively energy efficient, and have a higher gas flow rate than a similarly sized reciprocating compressor. Turbochargers cannot achieve compression ratios as high as reciprocating compressors, which can reach pressures of 100 MPa with multiple stages.

[0021] In the context of the present invention, the term "single stage turbocharger" refers to a turbocharger with a single compression and expansion train, i.e., a single compression structure (or component), also known as the "compressor," and a single expansion structure (or component), also known as the "turbine."

[0022] Preferably, the single stage centrifugal electric turbocharger has a compression ratio of 1 to 5, the compression ratio being defined as the ratio between the outlet pressure of the compressor part of the turbocharger and the inlet pressure of said compressor part. The selection of this particular range of values ​​for the compression ratio provides a single operating point for the compressor / turbine pair that is particularly suitable for enabling both the charge and discharge cycles of the heat pump at the applied pressure and temperature levels and flow conditions. In this particular range of values, the heat pump also maintains high energy efficiency and a significant flow of the displaced gas.

[0023] Preferably, the heat pump according to the invention comprises: at least one of the thermal energy storage systems is configured to store thermal energy at a temperature between −50° C. and +100° C.; and / or At least one of the thermal energy storage systems may be characterized in that it is configured to store thermal energy at a temperature between +150°C and +500°C, preferably between +200°C and +400°C.

[0024] Preferably, the heat pump according to the invention may be characterised in that said at least two thermal energy storage systems are adapted to store thermal energy in hot and cold form.

[0025] Preferably, the gas used in the reverse Brayton cycle of the heat pump can be air (i.e., about 20% oxygen in about 80% nitrogen), or a noble gas such as helium or argon, or a mixture of these gases.

[0026] The gas may alternatively be an inert gas, such as nitrogen.

[0027] Preferably the single stage centrifugal electric turbocharger produces a pressure of up to 8 bar, preferably between 1 and 5 bar (initially for gas at atmospheric pressure, corresponding to a compression ratio of between 1 and 5).

[0028] Preferably, the heat pump according to the invention may be characterized in that the various operating elements of the heat pump are isolated in modules, the modules being configured to be connected to each other by physical connections, such as valves (e.g. remotely controllable), connected pipes and / or hoses.

[0029] Preferably, the heat pump according to the invention can be characterized in that it is configured to be coupled to at least one natural heat source and / or at least one artificial heat source, such as a gas boiler, a gas furnace, heat of solar origin, a dryer, and / or heat losses of artificial origin.

[0030] Preferably, the heat pump according to the invention can be characterized in that it is configured to be coupled to the exhaust, loss or outlet of at least one artificial heat source, in particular an artificial heat source such as a gas boiler, a gas furnace, solar or waste heat, a dryer and / or heat losses of artificial origin.

[0031] "Exhaust" is understood in the context of the present invention to mean the final control stage of the energy circulation, for example in the form of hot steam or smoke from an artificial heat source.

[0032] In the context of the present invention, "loss" means the useful loss of energy from an artificial heat source, which in most cases is uncontrolled, difficult to control, or is the result of poor management or construction of the artificial heat source.

[0033] In the context of the present invention, the term "output" of a heat source is understood to mean the delivered and expected output from the heat source, i.e. from the place where the majority of said heat is expected to be recovered (e.g. from the steam condensate via the process return circuit).

[0034] In a particular embodiment, the heat pump according to the invention can be characterized in that it is adapted to be connected to a heating circuit and / or a cooling circuit. Preferably, the heat pump according to the invention can be characterized in that it is adapted to be connected to a primary heating circuit and / or a primary cooling circuit.

[0035] Preferably, the heat pump according to the invention can be characterized in that it is dimensioned to provide between 50 kWh and 5 MWh of energy.

[0036] In a particular embodiment, the heat pump comprises four thermal energy storage systems, two thermal energy discharge systems, two three-way valves, and two pumping members. A first end of the first thermal energy storage system is connected to a first end of the second thermal energy storage system via a first gas flow branch. A first end of the third thermal energy storage system is connected to a first end of the fourth thermal energy storage system via a second gas flow branch. The first thermal energy discharge system is arranged to exchange thermal energy with the first gas flow branch, and the second thermal energy discharge system is arranged to exchange thermal energy with the second gas flow branch. The first three-way valve is connected to the second end of the first thermal energy storage system, to the second end of the second thermal energy storage system, and to the second end of the third thermal energy storage system. The second three-way valve is connected to the second end of the second thermal energy storage system, to the second end of the third thermal energy storage system, and to the second end of the fourth thermal energy storage system. The first pumping member connects the second end of the second thermal energy storage system to the corresponding channel of the first three-way valve. The second pumping member connects the second end of the third thermal energy storage system to the corresponding channel of the second three-way valve. The inlet of the compressor part of the electric turbocharger is connected to the first end of the first thermal energy storage system at a first connection point on the first gas flow branch. The outlet of the compressor part of the electric turbocharger is connected to the first end of the second thermal energy storage system at a second connection point on the first gas flow branch. The inlet of the turbine part of the electric turbocharger is connected to the first end of the fourth thermal energy storage system at a first connection point on the second gas flow branch. An outlet of the turbine component of the electric turbocharger is connected to a first end of a third thermal energy storage system at a second connection point on the second gas flow branch.

[0037] This particular embodiment allows for specific sequences of gas flow through the various thermal energy storage systems (and therefore associated temperatures), which are not the same depending on whether the heat pump is in a charge or discharge cycle (through the use of valves and pumping components). Such a configuration thus allows for the gas to be compressed from a potentially higher temperature, thus either producing a higher temperature, or producing the same temperature at a lower compression ratio. The heat pump in this particular embodiment can also produce hot and / or cold at different times of use, and can store both types of thermal energy. With separate discharge circuits, the heat pump can also provide heating and / or cooling, either simultaneously or independently.

[0038] According to a preferred variant of this particular embodiment, the heat pump further comprises a two-way valve and three check valves. The two-way valve is connected on the first gas flow branch between the first connection point and the second connection point. The first check valve is connected between the outlet of the compressor part of the electric turbocharger and the second connection point of the first gas flow branch. The second check valve is connected between the outlet of the turbine part of the electric turbocharger and the second connection point of the second gas flow branch. The third check valve is connected on the second gas flow branch. The second check valve is connected between the output of the turbine part of the electric turbocharger and the second connection point of the second gas flow branch. The third check valve is connected on the second gas flow branch between the first connection point and the second connection point.

[0039] In another particular embodiment, which is an improvement of the embodiment described above, the heat pump further comprises three additional thermal energy emission systems, four additional two-way valves, and four additional three-way valves. A first end of the first additional thermal energy emission system is connected to a first end of the first thermal energy emission system via a first two-way valve. A second end of the first additional thermal energy emission system is connected to a second end of the first thermal energy emission system via a second two-way valve. A first end of the second additional thermal energy emission system is connected to a first end of the second thermal energy emission system via a third two-way valve. A second end of the second additional thermal energy emission system is connected to a second end of the second thermal energy emission system via a fourth two-way valve. A first end of the third additional thermal energy emission system is connected to a first connection point on the first gas flow branch. A second end of the third additional thermal energy emission system is connected to a second connection point on the second gas flow branch. The first additional three-way valve is connected to the inlet of the compressor section of the electric turbocharger, to a first connection point on the first gas flow branch, and to a first end of the third additional thermal energy release system. The second additional three-way valve is connected via a first gas line to the outlet of the compressor part of the electric turbocharger, to a second connection point on the first gas flow branch, and to one of the channels of the third additional three-way valve. The third additional three-way valve is further connected to the inlet of the turbine part of the electric turbocharger and to a first connection point on the second gas flow branch. The fourth additional three-way valve is connected via a second gas line to the outlet of the turbine part of the electric turbocharger, to a second connection point on the second gas flow branch, and to a second end of the third additional thermal energy release system. The first and third additional thermal energy release systems are each arranged to exchange thermal energy with the first gas line. A second additional thermal energy discharge system is disposed to exchange thermal energy with the second gas line.

[0040] In addition to the advantages associated with the previous designs (and outlined above), this particular heat pump design can instantly generate heat and cold at the same time as it discharges heat and cold from the thermal energy storage system. This is advantageous because it allows instantaneous power to be added to the heat pump discharge cycle, for example, to handle peak demand with minimal additional capital costs (three additional thermal energy discharge systems). This avoids the need to oversize the system (e.g., by increasing the size of the thermal energy storage system to store more, and / or by increasing the size of the machine, for example, to produce and store more at night).

[0041] A further object of the invention relates to a process for supplying thermal energy in the form of heat at temperatures between +100°C and +800°C and / or in the form of cold at temperatures between -100°C and +150°C using a heat pump as described above, the process comprising the steps of: (a) a fill cycle step by mechanical compression of at least one gas, preferentially accompanied by mechanical expansion of said at least one gas; (b) a discharge cycle step without compression and / or expansion, in which the thermal energy is discharged via at least one thermal energy discharge system, for example via at least one valve, at least one circulator (typically a pump), and / or at least one heat exchanger (i.e., a heat exchanger).

[0042] In a particular embodiment, step (a) is a fill cycle with mechanical compression of at least one vapor, preferably with mechanical expansion of said at least one vapor.

[0043] Preferably, the method according to the invention may be characterized in that step (b) of the discharge cycle is carried out in parallel with step (a) of the filling cycle.

[0044] The discharge cycle induces a flow of a fluid (such as a heat transfer gas) called a “discharge stream.” Thus, in one particular embodiment, the discharge stream can be split into several discharge streams, called split discharge streams, each of which can be directed to a different application.

[0045] For example, the split discharge flow can be directed to a storage system, such as a secondary storage system, which can allow for temperature stratification.

[0046] definition In the context of the present invention, the term "heat pump" refers to a device that transfers thermal energy from a first medium to a second, hotter medium, thus proceeding against the natural spontaneous direction of the thermal energy. In particular, there are so-called high-temperature heat pumps, very high-temperature heat pumps, low-temperature heat pumps and cryogenic heat pumps. Conventionally, there are different types of heat pumps, namely vapor compression heat pumps, Peltier effect heat pumps, thermoacoustic heat pumps, thermomagnetic heat pumps, gas absorption heat pumps and Stirling heat pumps. Preferably, a "heat pump" in the context of the present invention is an electric heat pump of the air cycle type (e.g. with a gas refrigeration cycle). This method follows the inverse Brayton thermodynamic cycle, in which a gas is compressed, cooled to ambient temperature and then expanded in a turbine, without any phase change, which distinguishes it from vapor compression heat pumps ("conventional" heat pumps, also known as "thermodynamic" heat pumps), which most often follow a vapor compression refrigeration cycle, or from gas absorption heat pumps.

[0047] The heat pump works by recovering heat from a low pressure storage tank known as the "cold" tank. The gas is then compressed in a compressor to increase its temperature. In the context of the present invention, this heat is stored. At the same time, the cold produced at the turbine outlet (expansion) is also recovered and stored.

[0048] A Brayton cycle driven in the opposite direction is called a reverse Brayton cycle. Its purpose is to transfer heat from a colder body to a warmer body, rather than producing work. According to the second principle of thermodynamics, heat cannot flow spontaneously from a cold system to a hot system without external work being done on the system. Heat can flow from a colder body to a warmer body, but only if it is forced by external work. That is exactly what refrigerators and heat pumps accomplish. They are driven by electric motors that need work from their environment to operate. Thus, one possible cycle is the reverse Brayton cycle, which is similar to the normal Brayton cycle, but driven in the opposite direction through a network input. This cycle is also known as a gas refrigeration cycle, air cycle, or Bell-Coleman cycle. This type of cycle is widely used in commercial aircraft or trains for air conditioning systems that use air from the engine compressor. It is also widely used in the LNG (Liquefied Natural Gas) industry, where the largest Brayton reverse cycle is for LNG subcooling using 86 MW of power from a gas turbine driven compressor and nitrogen refrigerant (source of this common knowledge: thermal engineering.org).

[0049] "High temperature" is understood in the context of the present invention to mean a temperature range of +60 to +100 °C, preferably +70 to +95 °C. Heat pumps of this type can be found among commercial heat pumps, including so-called "consumer" heat pumps. Their efficiency decreases as the temperature difference between the cold and hot sources increases.

[0050] Temperatures given in the context of the present invention, unless otherwise indicated, refer to a temperature of 0° C., i.e. the freezing temperature of water at sea level and 1 atmosphere (i.e. 101325 Pa, which corresponds to an absolute pressure of 1 bar).

[0051] "Very high temperature" is understood in the context of the present invention to mean a temperature range above +100° C., for example above +150° C., above +200° C., above +300° C., above +400° C. Thus, very high temperatures in the context of the present invention may include temperatures between +150 and +500° C., preferably between +150 and +400° C., or even between +250 and +350° C.

[0052] "Low temperature" is understood in the context of the present invention to mean a temperature range of from -20 to +5°C, preferably from -15 to -5°C.

[0053] "Very low temperatures" are understood in the context of the present invention to mean a temperature range below -20° C., for example below -30° C., below -40° C., below -50° C., below +60° C. Thus, very low temperatures in the context of the present invention may include temperatures of -30 to -150° C., preferably -40 to -100° C., or even -50 to -80° C.

[0054] In the context of the present invention, "thermal energy storage system" means any means of storing a quantity of energy of a thermal nature for later use. The thermal nature can be heat or cold. In fact, heat itself is a form of energy. In the case of stored cold, the production of cold requires energy, so storing cold represents energy storage.

[0055] In the context of the present invention, the term "thermal energy delivery system" means a means for delivering thermal energy. Furthermore, the expression "thermal energy delivery system configured for" means that the tanks are interchangeable (one can be used for heating and then for cooling in a series of other filling / dispensing cycles).

[0056] In the context of the present invention, the term "separate or parallel release of thermal energy" means separate or parallel release of thermal energy from at least two different storage systems. Separate delivery thus allows thermal energy from at least one first storage system to be supplied first, followed by thermal energy from at least one second storage system. Parallel delivery allows thermal energy from at least one first storage system and thermal energy from at least one second storage system to be supplied simultaneously.

[0057] In the context of the present invention, a "module" means an element that can be juxtaposed or combined with one or more others, which may be of the same nature as a first one or which may be complementary.

[0058] In the context of the present invention, the term "natural heat source" is taken to mean thermal energy obtained without human intervention, such as, for example, geothermal sources or water sources (lakes, seas, rivers, etc.).

[0059] In the context of the present invention, "artificial heat source" is understood to mean thermal energy generated by human intervention, such as furnaces, boilers, air conditioners and similar installations, compressors, machines, generators, residential, commercial, tertiary industrial and / or computer processes, energy from solar thermal systems, or even waste heat.

[0060] In the context of the present invention, "charge cycle" is understood to mean a sequence of events that can occur periodically, i.e. a cycle that allows the generation of thermal energy that can be instantly distributed or stored in the form of thermal energy.

[0061] In the context of the present invention, "gas" means any substance in a gaseous state. Gas therefore also includes the vapour resulting from the evaporation of a liquid (at any temperature).

[0062] In the context of the present invention, the term "mechanical expansion" refers to the expansion of a gas that has initially been compressed through a turbine.

[0063] In the context of the present invention, the term "discharge cycle" is understood to mean the inverse function of the fill cycle, i.e. the release of thermal energy stored in the storage system.

[0064] In the context of the present invention, "heat exchanger" means a device for transferring thermal energy from one fluid to another without mixing them. It is therefore a matter of a "carrier fluid", i.e. a fluid as defined above, that allows the thermal energy to be transferred from one place to another.

[0065] By way of example, liquid / liquid, gas / liquid, or gas / gas heat exchangers such as plate heat exchangers or tube and tube heat exchangers may be used within the scope of the present invention. There are many suppliers of such heat exchangers, such as Alfa-Laval®. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0066] The object of the invention is to make it possible to adapt, improve and simultaneously combine: -Proven technology to increase efficiency and meet the needs of thermal processes (heating and cooling). -For example, special electric turbomachines (electric turbochargers) whose speed can be controlled using power electronics and software (via adjusting the flow rate / rotational speed and compression ratio). - Thermal storage (separate cooling and heating) to add flexibility to the system and increase the attractiveness of the solution to industrial users.

[0067] Thus, the subject of the invention may comprise one or more sensors which, in combination with the use of software (and its algorithms), enable the heat pump to be controlled according to the invention.

[0068] In addition, the subject matter of the present invention offers several important innovations in terms of technology and functionality. Electrical generation of high temperature heating (>150°C and up to 500-800°C) and industrial cooling (down to -50°C) with a COP (coefficient of performance-efficiency) of above -1.5. - Use of refrigerants with a GWP (global warming potential) of 0 (such as air or argon). - High density energy storage in thermal form of this generated or heated / supercooled energy: hot (>150°C) and industrial cold (down to -50°C) in the same module, capable of storing energy for hours or even days.

[0069] The various components of the heat pump according to the invention (electric turbo compressor, motor, storage system, etc.) can be arranged in one or more modules or sub-modules that can be combined or integrated with each other. The entire assembly can be housed in a container (e.g. a standard "20 ft" or "40 ft" container, i.e. about 6 meters or 12 meters) or placed on a chassis.

[0070] Modules or sub-modules as defined above may be combined with other similar modules or sub-modules as required.

[0071] All these modules and / or sub-modules can be used to integrate and upgrade waste energy or solar thermal energy streams, for example by adding one or more heat exchangers. The subject of the present invention therefore further provides a method for increasing the temperature of the recovered waste heat or solar thermal energy, storing it and then releasing it when required.

[0072] Thus, in certain embodiments, the various functional elements of the heat pump according to the invention can be isolated in modules. The modular system therefore allows the heat pump to be easily adapted to the physical layout of the place where it is installed. In practice, modularity means that the heat pump can be adapted according to the on-site generation, for example by increasing or decreasing the thermal energy generation (power) or storage (energy) capacity. Furthermore, modularity allows the modification of the original assembly. For example, modularity can allow several storage systems to be inserted in order to provide temperature diversity, regardless of the input (recovery of waste energy with different temperature levels and / or temperature fluctuations) and / or output (generation of thermal energy at a specific temperature and / or with variable temperature requirements).

[0073] Additionally, it may be advantageous to install a rail and / or chassis system ("aggregate") to promote modularity.

[0074] In a particular embodiment, a module comprising the various elements is adapted to move within a container.

[0075] Modular recombination makes it possible to limit the number of modular variations and thus optimize the cost of the system while being able to address a larger number of different needs.

[0076] In addition, thermal energy storage according to the invention can be achieved by installing in a storage system such as a tank (for example the one mentioned above) elements that allow thermal energy to be absorbed and stored during the filling phase, for example by stacking blocks of reduced size (compared to the tank) on different levels. These blocks can take the form of gravel, firebricks, ceramic pieces, cement pieces, rock pieces (for example volcanic or granular) or zeolites.

[0077] Alternatively, the stacks at different levels can take the form of conventional PCM (phase change materials), for example capsules of kerosene or CaCl2 6H2O, containing particular sands (such as molten salts), KNO3-60%NaNO3 or NaCl / MgCl2 (57 / 43), which have been used for more than 20 years in concentrated solar power plants (CSP).

[0078] All these materials and elements have been used abundantly for many years in various fields and systems and are very well documented in numerous journals, publications, to give just an example in the document "State-of-the-Art Review: "Insulation and Thermal Storage Materials", 2013 (Eclipse, Cambridge Architectural Research Limited)".

[0079] This same heat energy (minus the heat losses inherent in the system) will of course be released upon exhalation.

[0080] This storage aspect is advantageous for the proper functioning of the present invention.

[0081] The tanks and piping will be insulated with conventional insulating materials such as Woollock or other standard insulation.

[0082] The heat pump according to the invention therefore comprises at least two cycles, one called the charge cycle and the other called the discharge cycle.

[0083] For example, a fill cycle may include: -Compression of a fluid (i.e. gas) at 1-5 bar (starting at 1 bar with a compression ratio of 1-5) in a compressor (thus heating it up to 150-300 °C, for example, if the gas is air). -Discharge of heat from the fluid in the material / storage element to the first tank. - Expansion in a turbine of the compressed air, which has been cooled during its passage through the first vessel but is still under pressure. - Reheating in a second tank of very cold air (-100 to +10) with a large pressure reduction caused by expansion through a turbine (hence the "transmission of cold"). -The "heated" cold air returns to the compressor. -The cycle is restarted until the tank is full (information provided by sensors and / or system controlled shut down of the electric turbocharger).

[0084] For example, a dispense cycle may include: - Circulators installed in the external loop of each tank (distribution) that transfer the energy from the tank to a heat exchanger installed in the client's process loop. At the switch exit, the distribution loop restores the client process return.

[0085] Thus, in this cycle, no compression or expansion is used, only the circulator and / or pump. The cold and hot energy distribution systems are independent, so the discharge can be simultaneous or alternating. The discharge stops when the client demand is reached or the tank is empty (again, information provided by the sensor is used by the circulator control system to stop the process). [Brief description of the drawings]

[0086] By way of non-limiting example, embodiments of the invention will now be described with reference to the accompanying drawings, in which: [Figure 1] 1 shows a perspective view of a heat pump according to the invention, on a chassis. [Diagram 2] FIG. 2 is a conceptual diagram showing the charge cycle of the heat pump according to the present invention. [Diagram 3] FIG. 2 is a conceptual diagram showing the discharge cycle of the heat pump according to the present invention. [Figure 4] 1 is a schematic conceptual diagram of a heat pump according to the present invention, seen from above. [Diagram 5] FIG. 1 is a conceptual schematic diagram of a heat pump according to the invention seen from above, in which the heat pump is connected to a waste energy source. [Figure 6] FIG. 1 is a conceptual schematic diagram of a heat pump according to the invention seen from above, in which the heat pump is connected to two additional thermal energy storage systems. [Figure 7] 1 shows a perspective view of the inside of a container of a heat pump according to the present invention. [Figure 8] FIG. 2 is a schematic diagram showing a specific embodiment of a heat pump charging cycle of a heat pump according to the present invention, the heat pump comprising four thermal energy storage systems. [Figure 9] FIG. 9 is a simplified schematic diagram of the thermal energy storage system shown in FIG. [Figure 10] FIG. 9 is a conceptual diagram of the heat pump discharge cycle of the heat pump of FIG. [Figure 11] FIG. 11 is a simplified schematic diagram of the thermal energy storage system of FIG. [Figure 12] FIG. 2 is a schematic diagram of another specific embodiment of a heat pump according to the invention in a heat pump charging cycle, the heat pump comprising four thermal energy storage systems. [Figure 13] FIG. 13 is a simplified schematic diagram of the thermal energy storage system of FIG. [Figure 14] FIG. 12 is a conceptual diagram of a heat pump discharge cycle of the heat pump. [Figure 15] FIG. 15 is a simplified schematic diagram of the thermal energy storage system of FIG.

[0087] With reference to FIG. 1 , where a heat pump according to the invention is shown in perspective on a chassis 15, one can see a compressor 1 and a turbine 2, connected to each other by an electrical and / or mechanical link 13, driven by an electric motor 3. Both the compressor and the turbine are connected by piping 10, on the one hand, to a first storage system 4 and on the other hand, to a second storage system 5, thus establishing a loop between the compressor 1, the turbine 2, the first storage system 4 and the second storage system 5. The compressor 1 and the turbine 2 form a single-stage centrifugal electric turbocharger.

[0088] [Figure 2] is a schematic diagram of the heat pump shown in [Figure 1], here shown in a charging cycle, connected to a thermal energy discharge system 6. A first storage system 4 and a second storage system 5 are each connected to the thermal energy discharge system 6 for supplying heat or cold to a customer system 7. The flow direction represented by the arrow 8 means that the thermal energy in the form of heat is concentrated in the second storage system 5, whereas the thermal energy in the form of cold is concentrated in the first storage system 4. The storage of cold energy is carried out at low pressure. Then, theoretically, a temperature gradient can be created in the first storage system 4 and the second storage system 5, such that Q1 is at a higher temperature (i.e. hotter) than Q2 and Q3 is at a lower temperature (i.e. colder) than Q4. In [Figure 2], the discharge is not shown.

[0089] With reference to FIG. 3, the same assembly diagram as shown in FIG. 2 is now depicted for the discharge cycle. By discharging the thermal energy stored in the first storage system 4 and the second storage system 5 to the two thermal energy discharge systems 6, it is possible to supply hot and cold heat to the customer system 7. In FIG. 3, the second storage system 5 is cooled by this discharge, and thus a temperature gradient can be created such that theoretically Q6 is at a lower temperature (i.e. colder) than Q5. Similarly, theoretically a temperature gradient can be created in the first storage system 4 such that the temperature of Q8 is higher (i.e. hotter) than Q7. It is clear in FIG. 2 and FIG. 3 that the filling cycle and the discharging cycle can be performed in parallel.

[0090] [Figure 4] is a top view of the assembly diagram shown in Figures 2 and 3. The compressor 1, the turbine 2 and the motor 3, together with their (electrical) power unit and any standard connections, are grouped together in a so-called working group 9. The working group 9, the first storage system 4, the second storage system 5 and the piping 10 constitute a first heat pump assembly 14 according to the invention.

[0091] [Figure 5] is a top view of an assembly diagram based on the elements shown in [Figure 4], with the addition of a source 11 of waste energy (or thermal energy of natural or solar origin) for supplying thermal energy, represented by an arrow 12. Any means of capturing this waste energy can be applied, for example a heat exchanger connected to the piping circuit 10 of the heat pump assembly 14 according to the invention. It is possible to arrange the thermal energy input between the storage system 5 and the turbine of the working group 9 and / or between the storage system 4 and the (turbo)compressor of the working group 9.

[0092] [Figure 6] shows a heat pump assembly 14 according to the invention, comprising two thermal energy storage systems 4A and 5A and a work group 9. An assembly 15 comprising two thermal energy storage systems 4B and 5B is connected to the heat pump assembly 14 according to the invention. The work group 9 is doubly connected to each storage system 4A, 4B, 5A and 5B. In addition, the thermal energy storage system 4A is connected to the thermal energy storage system 4B by piping 10. The thermal energy storage system 5A is connected to the thermal energy storage system 5B by piping 10.

[0093] 4, 5 and 6, the heat exchanger 6 is positioned outside the assemblies 14, 15. Alternatively, the heat exchanger may be located within the assemblies 14, 15.

[0094] In practice, the assemblies 14, 15 of Figures 4, 5 and 6 may be containers.

[0095] FIG. 7 is a perspective view of the heat pump shown in FIG.

[0096] [Figure 8] is a schematic diagram illustrating a specific embodiment of a heat pump charging cycle of a heat pump according to the present invention. In this specific embodiment, in addition to the single-stage centrifugal electric turbochargers 1, 2, the heat pump features four thermal energy storage systems 16A-16D, two thermal energy discharge systems 18A, 18B, two three-way valves 20A, 20B, two pumping elements 22A, 22B, a two-way valve 24, and three check valves 26A-26C.

[0097] A first end 16A1 of the first thermal energy storage system 16A is connected to a first end 16B1 of the second thermal energy storage system 16B via a first gas flow branch 28A. A first end 16C1 of the third thermal energy storage system 16C is connected to a first end 16D1 of the fourth thermal energy storage system 16D via a second gas flow branch 28B.

[0098] The first thermal energy release system 18A (preferably a heat exchanger) is arranged to exchange thermal energy with the first gas flow branch 28A. The second thermal energy release system 18B (preferably a heat exchanger) is arranged to exchange thermal energy with the second gas flow branch 28B. The first three-way valve 20A is connected to the second end 16A2 of the first thermal energy storage system 16A, to the second end 16B2 of the second thermal energy storage system 16B, and to the second end 16C2 of the third thermal energy storage system 16C. The second three-way valve 20B is connected to the second end 16B2 of the second thermal energy storage system 16B, to the second end 16C2 of the third thermal energy storage system 16C, and to the second end 16D2 of the fourth thermal energy storage system 16D.

[0099] A first pumping member 22A (typically a pump) connects the second end 16B2 of the second thermal energy storage system 16B to the corresponding channel 20A1 of the first three-way valve 20A. Another channel 20A2 of the first three-way valve 20A is connected to the second end 16A2 of the first thermal energy storage system 16A, and a final channel 20A3 of the first three-way valve 20A is connected to the second end 16C2 of the third thermal energy storage system 16C. A second pumping member 22B (typically a pump) connects the second end 16C2 of the third thermal energy storage system 16C to the corresponding channel 20B1 of the second three-way valve 20B. Another channel 20B2 of the second three-way valve 20B is connected to the second end 16D2 of the fourth thermal energy storage system 16D, and the last channel 20B3 of the second three-way valve 20B is connected to the second end 16B2 of the second thermal energy storage system 16B.

[0100] The inlet 1E of the electric turbocharger compressor part 1 is connected to the first end 16A1 of the first thermal energy storage system 16A at a first connection point 30A on the first gas flow branch 28A. The output 1S of the electric turbocharger compressor part 1 is connected to the first end 16B1 of the second thermal energy storage system 16B at a second connection point 30B on the first gas flow branch 28A. The inlet 2E of the electric turbocharger turbine part 2 is connected to the first end 16D1 of the fourth thermal energy storage system 16D at a first connection point 32A on the second gas flow branch 28B. The outlet 2S of the electric turbocharger turbine part 2 is connected to the first end 16C1 of the third thermal energy storage system 16C at a second connection point 32B on the second gas flow branch 28B.

[0101] The two-way valve 24 is connected to the first gas flow branch 28A between the first connection point 30A and the second connection point 30B. The first check valve 26A is connected between the outlet 1S of the compressor part 1 of the electric turbocharger and the second connection point 30B of the first gas flow branch 28A. The second check valve 26B is connected between the outlet 2S of the turbine part 2 of the electric turbocharger and the second connection point 32B of the second gas flow branch 28B. The third check valve 26C is connected on the second gas flow branch 28B between the first connection point 32A and the second connection point 32B.

[0102] The operation of the heat pump in this particular embodiment, when the pump is in the charge cycle, is illustrated in Figures 8 and 9. The flow direction represented by the arrows 34 means that here the thermal energy in hot form is concentrated in the second storage system 16B (after being extracted from the first storage system 16A and then compressed in the compressor 1), whereas the thermal energy in cold form is concentrated in the third storage system 16C (after being extracted from the fourth storage system 16D and then expanded in the turbine 2). The cold energy storage is at low pressure (typically about 1 bar absolute if the gas used is air), whereas the hot energy storage is at high pressure (typically 1 to 5 bar absolute if the gas used is air). The cold energy extraction is at high pressure, whereas the hot energy extraction is at low pressure. The temperature gradient created within the second and third storage systems 16B, 16C causes thermal energy to be transferred from the second storage system 16B to the fourth storage system 16D, on the one hand, and from the third storage system 16C to the first storage system 16A, on the other hand.

[0103] The operation of the heat pump in this particular embodiment, when the pump is in the discharge cycle, is illustrated in Figures 10 and 11. It is possible to supply hot and cold heat to the client systems by discharging the thermal energy stored in the second storage system 16B and the third storage system 16C to the two thermal energy discharge systems 18A, 18B. In this way, a first loop 38 is established between the first storage system 16A and the second storage system 16B on the one hand, and a second loop 40 is established between the third storage system 16C and the fourth storage system 16D on the other hand. In the first loop 38 (the first pumping member 22A is started and the heat pump supplies hot heat to the first thermal energy discharge system 18A), the second storage system 16B is cooled by discharging, creating a temperature gradient that circulates the gas in the direction of flow represented by the arrow 41. In the second loop 40 (the second pumping member 22B is started and the heat pump supplies cold to the second thermal energy release system 18B), the third storage system 16C is heated by discharge, creating a temperature gradient that circulates the gas in the direction of flow represented by arrow 42.

[0104] This particular embodiment of the heat pump illustrated in Figures 8-11 allows the gas flow order in the first and fourth storage systems 16A, 16D to be "swapped" during a discharge operation compared to a fill operation without physically moving the storage systems 16A-16D. The advantage of this operation is that it prevents the establishment of a thermocline in the 16A-16D thermal energy storage systems and thus avoids the introduction of excessive temperature differences (thermal shocks) that are detrimental to the performance and general application of thermal storage.

[0105] As an example of the particular embodiment of the heat pump illustrated in FIGS. 8-11, non-limiting temperature values ​​are given below. The first end 16A1 of the first storage system 16A has, for example, a temperature substantially equal to +60°C and the second end 16A2 of the first storage system 16A has a temperature substantially equal to +80°C. The first end 16B1 of the second storage system 16B has, for example, a temperature substantially equal to +210°C and the second end 16B2 of the second storage system 16B has a temperature substantially equal to +80°C. The first end 16C1 of the third storage system 16C has, for example, a temperature substantially equal to -30°C and the second end 16C2 of the third storage system 16C has a temperature substantially equal to +80°C. The first end 16D1 of the fourth storage system 16D has, for example, a temperature substantially equal to +20°C and the second end 16D2 of the fourth storage system 16D has a temperature substantially equal to +80°C. The fluid circulating in the first thermal energy discharge system 18A enters this system 18A at a temperature substantially equal to, for example, +20°C and leaves this system 18A at a temperature substantially equal to, for example, +200°C. The fluid circulating in the second thermal energy discharge system 18B enters this system 18B at a temperature substantially equal to, for example, +25°C and leaves this system 18B at a temperature substantially equal to, for example, -25°C.

[0106] [Figure 12] is a schematic diagram showing a specific embodiment of a heat pump according to the present invention in a heat pump charging cycle. As with the previous embodiment described with reference to Figures 8 to 11, the heat pump according to this specific embodiment comprises single-stage centrifugal electric turbochargers 1, 2, four thermal energy storage systems 16A-16D, two thermal energy discharge systems 18A, 18B, two three-way valves 20A, 20B, two pumping members 22A, 22B, a two-way valve 24, and three check valves 26A-26C, all connected in the same manner as in the previous embodiment. Except for the turbochargers 1, 2 and the two thermal energy discharge systems 18A, 18B, the other aforementioned components are not shown in [Figure 12] for clarity. The heat pump also features three additional thermal energy discharge systems 44A-44C, four additional two-way valves 46A-46D, four additional three-way valves 48A-48D and four additional pumping elements 49A-49D. This particular embodiment shown in Figures 12-15 is therefore an improvement over the previous embodiment described with reference to Figures 8-11. Elements described in Figures 12-15 with the same reference numbers as in Figures 8-11 are identical to the latter and will therefore not be described in more detail below.

[0107] As illustrated in FIG. 12, a first end 44A1 of the first additional thermal energy release system 44A is connected to a first end 18A1 of the first thermal energy release system 18A via a first and a second additional two-way valve 46A, 46B. A second end 44A2 of the additional first thermal energy release system 44A is connected to a second end 18A2 of the first thermal energy release system 18A. A first end 44B1 of the additional second thermal energy release system 44B is connected to a first end 18B1 of the second thermal energy release system 18B. A second end 44B2 of the second additional thermal energy release system 44B is connected to a second end 18B2 of the second thermal energy release system 18B via a third and a fourth additional two-way valve 46C, 46D. A first end 44C1 of the third additional thermal energy release system 44C is connected to a first connection point 30A on the first gas flow branch 28A, and a second end 44C2 of the third additional thermal energy release system 44C is connected to a second connection point 32B on the second gas flow branch 28B.

[0108] The first additional three-way valve 48A is connected to the inlet 1E of the electric turbocharger compressor part 1, to the first connection point 30A on the first gas flow branch 28A, and to a first end 44C1 of the third additional thermal energy release system 44C. The second additional three-way valve 48B is connected via a first gas line 50A to the outlet 1S of the electric turbocharger compressor part 1, to the second connection point 30B on the first gas flow branch 28A, and to one of the channels 48C1 of the third additional three-way valve 48C. The third additional three-way valve 48C is further connected to the inlet 2E of the electric turbocharger turbine part 2, and to the first connection point 32A on the second gas flow branch 28B. The fourth additional three-way valve 48D is connected via a second gas line 50B to the outlet 2S of the turbine part 2 of the electric turbocharger, to a second connection point 32B on the second gas flow branch 28B, and to a second end 44C2 of the third additional thermal energy discharge system 44C.

[0109] First and third additional thermal energy discharge systems 44A, 44C are each arranged to exchange thermal energy with the first gas line 50A. An additional second thermal energy discharge system 44B is arranged to exchange thermal energy with the second gas line 50B.

[0110] A first additional pumping member 49A (typically a pump) connects the second end 44A2 of the first additional discharge system 44A to a "hot" output 56 of the assembly formed by the first discharge system 18A and the first additional discharge system 44A. A second additional pumping member 49B (typically a pump) connects the second end 18A2 of the first discharge system 18A to a "hot" output 56 of the assembly formed by the first discharge system 18A and the first additional discharge system 44A. A third additional pumping member 49C (typically a pump) connects the first end 44B1 of the second additional discharge system 44B to a "cold" output 58 of the assembly formed by the second discharge system 18B and the second additional discharge system 44B. A fourth additional pumping member 49D (typically a pump) connects the first end 18B1 of the second discharge system 18B to a “cold” outlet 58 of the assembly formed by the second discharge system 18B and the second additional discharge system 44B.

[0111] The operation of the heat pump in this particular embodiment, when the pump is in the fill cycle, is illustrated in Figures 12 and 13. When in the fill cycle, the heat pump operates in a similar manner to the previous embodiments described with reference to Figures 8 to 11. In other words, thermal energy in hot form is concentrated in the second storage system 16B (after being extracted from the first storage system 16A and then compressed in the compressor 1), whereas thermal energy in cold form is concentrated in the third storage system 16C (after being extracted from the fourth storage system 16D and then expanded in the turbine 2).

[0112] The operation of the heat pump in this particular embodiment is illustrated in Figures 14 and 15 when the pump is in the discharge cycle. During the discharge of the heat pump, it is possible to supply hot and cold to the customer systems while continuing the parallel filling cycle of the second and third storage systems 16B, 16C. Indeed, as illustrated in Figure 15, two hot discharge loops 52A, 52B are established on the one hand (corresponding to hot discharge to the first discharge system 18A and the first additional discharge system 44A) and two cold discharge loops 54A, 54B are established on the other hand (corresponding to cold discharge to the second discharge system 18B and the second additional discharge system 44B). For each discharge circuit (hot on the one hand, cold on the other), each loop 52A, 54A can operate independently of the other loop 52B, 54B, respectively, in parallel with the latter or separately.

[0113] In the first loop 52A of the heat discharge circuit (the first pumping member 22A and the second additional pumping member 49B are activated - this loop 52A is established between the first storage system 16A and the second storage system 16B), the gas flows in the direction of flow represented by the arrow 60. In the second loop 52B of the heat discharge circuit (the first additional pumping member 49A is activated - this loop 52B is established with the compressor 1 part of the electric turbocharger, the instantaneous energy is generated by the turbochargers 1, 2 and in particular flows through the first gas line 50A), the gas flows in the direction of flow represented by the arrow 62. In a first loop 54A of the cold discharge circuit (the second pumping member 22B and the fourth additional pumping member 49D are activated - this loop 54A is established between the third storage system 16C and the fourth storage system 16D), the gas flows in the direction of flow represented by the arrow 64. In a second loop 54B of the cold discharge circuit (the third additional pumping member 49C is activated - this loop 54B is established in the turbine 2 of the electric turbocharger, cyclic energy is generated by the turbochargers 1, 2, and in particular flows in the second gas line 50B), the gas flows in the direction of flow represented by the arrow 66.

[0114] In addition to the advantages associated with the previous embodiments (and described above), this particular embodiment of the heat pump can instantaneously generate heat and cold while simultaneously discharging heat and cold from the thermal energy storage system, as illustrated in Figures 12-15. This is advantageous because it allows instantaneous power (from electric turbochargers 1, 2) to be added to previously stored energy and then discharged in parallel with the instantaneously generated energy, for example to meet peak demand with minimal additional capital costs (three additional thermal energy discharge systems 44A-44C). In this particular embodiment illustrated in Figures 12-15, the discharge of the heat pump can be performed as follows: Either by supplying only the instantaneous energy generated by a single-stage centrifugal electric turbocharger 1, 2. Either by simultaneously supplying the stored energy of a thermal energy storage system and the stored energy of a single-stage centrifugal electric turbocharger (i.e. by discharging the energy generated during the previous charge added to the energy of the instantaneous electrical power generated by the turbocharger).

[0115] This avoids, for example, the need to oversize the system (e.g., by increasing the size of the thermal energy storage system to store more and / or by increasing the size of the machine to, for example, produce more at night). EXAMPLES

[0116] The accompanying drawings may be reproduced using the parts described below.

[0117] 1. Electric turbo compressor and turbine The turbine and electric compressor are combined into a single turbomachine that is a single stage centrifugal electric turbocharger.

[0118] For example, one of the following turbochargers may be used: -Garrett "Electric turbo compressor with recovery turbine for fuel cell electric vehicles" -Fisher EMTCT-120k Air / EMTCT-90k Air: Electric micro turbo compressor with turbine or similar for energy recovery -BorgWarner eTurbo -IHI fuel cell turbocharger - Electric compressor with Liebherr turbine (ETC) 25 kW and 55 kW -Mitsubishi® electric turbocharger -Holset® electric turbocharger (part of Cummins)

[0119] 2.Storage system: Tank Metal tanks such as standard cylindrical metal vessels (steel or stainless steel) of various sizes can be insulated and can withstand pressures up to 10 bar, 0.5 to 10 m 3 , or even higher pressures.

[0120] There are numerous manufacturers around the world. For example, the following companies sell tanks that may be suitable: -Herpasa (registered trademark); "Insulated tank" -EMI compressed air (registered trademark); see for example P265GH-EN10028-2; P275NH-EN10028-3; P265GH-EN10028-2; or P275NH-EN10028-3 tanks -Kaeser Compressors(R); - Colibris Compression®; see for example Vertical Galvanized Pauchard Tank 2000L BP RTCABJA000

Claims

1. An electric heat pump, at least two thermal energy storage systems (4, 5; 16A-16D), at least one thermal energy emission system (6; 18A, 18B), at least one of said thermal energy storage systems (5; 16B) is configured to store thermal energy in hot form at a temperature between +100°C and +800°C; at least one of said thermal energy storage systems (4; 16C) is configured to store thermal energy in the form of cold at a temperature between -100°C and +150°C; the at least one thermal energy emission system (6; 18A, 18B) is configured to emit heat and / or cold separately or in parallel over time, the at least one thermal energy release system (6; 18A, 18B) is configured to operate in a parallel release mode that can be alternated over time with separate release modes of heat and / or cold, the heat pump being configured to have a reverse Brayton cycle operating on gas, A heat pump, characterized in that said heat pump comprises a single-stage centrifugal electric turbocharger (1, 2).

2. 2. The heat pump according to claim 1, characterized in that the single-stage centrifugal electric turbocharger (1, 2) has a compression ratio of 1 to 5, the compression ratio being defined as the ratio between the outlet pressure of the compressor section (1) of the turbocharger and the inlet pressure of the compressor section (1).

3. at least one of said thermal energy storage systems (4; 16C) is configured to store thermal energy at a temperature between -50°C and +100°C, and / or - A heat pump according to claim 1 or 2, characterized in that at least one of the thermal energy storage systems (5; 16B) is configured to store thermal energy at a temperature between +150°C and +500°C, preferably between +200°C and +400°C.

4. 2. A heat pump according to claim 1, characterized in that said at least two thermal energy storage systems (4, 5; 16A-16D) are configured to store thermal energy in said hot and cold form.

5. 2. The heat pump of claim 1, wherein the various operating components of the heat pump are isolated within modules, and the modules are configured to be connected to each other by physical connections, such as valves, connecting pipes, and / or hoses.

6. 2. The heat pump according to claim 1, characterized in that it is configured to be coupled to at least one natural and / or at least one artificial heat source, such as a gas boiler, a gas furnace, solar or waste heat (11), a dryer, and / or heat losses of artificial origin.

7. 2. A heat pump according to claim 1, characterized in that the gas used in the reverse Brayton cycle of the heat pump is air or a noble gas such as helium or argon, or a mixture of these gases.

8. The heat pump comprises four thermal energy storage systems (16A-16D), two thermal energy release systems (18A, 18B), two three-way valves (20A, 20B), and two pumping members (22A, 22B), and the first end (16A1) of the first thermal energy storage system (16A) is connected to the first end (16B1) of the second thermal energy storage system (16B) via a first gas flow branch (28A), and the first end (16C1) of the third thermal energy storage system (16C) is connected to the first end (16B1) of the third thermal energy storage system (16C) via a second gas flow branch (28B). a first thermal energy release system (18A) arranged to exchange thermal energy with the first gas flow branch (28A); a second thermal energy release system (18B) arranged to exchange thermal energy with the second gas flow branch (28B); a first three-way valve (20A) connected to a second end (16A2) of the first thermal energy storage system (16A), to a second end (16B2) of the second thermal energy storage system (16B), and to a first end (16D1) of a fourth thermal energy storage system (16D); a first thermal energy release system (18A) arranged to exchange thermal energy with the first gas flow branch (28A); a second thermal energy release system (18B) arranged to exchange thermal energy with the second gas flow branch (28B); a second end (16C2) of a third thermal energy storage system (16C); a second three-way valve (20B) connected to the second end (16B2) of the second thermal energy storage system (16B), to the second end (16C2) of the third thermal energy storage system (16C), and to a second end (16D2) of the fourth thermal energy storage system (16D); a first pumping member (22A) connecting the second end (16B2) of the second thermal energy storage system (16B) to a corresponding channel of the first three-way valve (20A); a second pumping member (22B) connecting the second end (16C2) of the third thermal energy storage system (16C) to a corresponding path (20B1) of the second three-way valve (20B); the inlet (1E) of the compressor part (1) of the electric turbocharger is connected to the first end (16A1) of the first thermal energy storage system (16A) at a first connection point (30A) on the first gas flow branch (28A);2. The heat pump according to claim 1, characterized in that at a second connection point (30B) on the first gas flow branch (28A) the inlet (2E) of the turbine part (2) of the electric turbocharger is connected to the first end (16D1) of the fourth thermal energy storage system (16D) at a first connection point (32A) on the second gas flow branch (28B), and the outlet (2S) of the turbine part (2) of the electric turbocharger is connected to the first end (16C1) of the third thermal energy storage system (16C) at a second connection point (32B) on the second gas flow branch (28B).

9. The heat pump further comprises a two-way valve (24) and three check valves (26A, 26B, 26C), the two-way valve (24) being connected to the first gas flow branch (28A) between the first connection point (30A) and the second connection point (30B), and the first check valve (26A) being connected to the outlet (1S) of the compressor part (1) of the electric turbocharger and the second connection point (30B) of the first gas flow branch (28A). a second check valve (26B) is connected between the outlet (2S) of the turbine part (2) of the electric turbocharger and the second connection point (32B) of the second gas flow branch (28B), and a third check valve (26C) is connected on the second gas flow branch (28B) between the first connection point (32A) and the second connection point (32B).

10. The heat pump further comprises three additional thermal energy release systems (44A-44C), four additional two-way valves (46A-46D), and four additional three-way valves (48A-48D), wherein a first end (44A1) of a first additional thermal energy release system (44A) is connected to a first end (18A1) of the first thermal energy release system (18A) via first and second two-way valves (46A, 46B), and a second end (44A2) of the first additional thermal energy release system (44A) is connected to a first end (18A1) of the first thermal energy release system (18A) via first and second two-way valves (46A, 46B). a first end (44B1) of a second additional thermal energy release system (44B) connected to the first end (18B1) of said second thermal energy release system (18B), a second end (44B2) of said second additional thermal energy release system (44B) connected to the second end (18B2) of said second thermal energy release system (18B) via third and fourth two-way valves (46C, 46D), and a first end (44C1) of a third additional thermal energy release system (44C) connected to the second end (18B2) of said second thermal energy release system (18B) via third and fourth two-way valves (46C, 46D), a first additional three-way valve (48A) connected to the inlet (1E) of the compressor part (1) of the electric turbocharger, to the first connection point (30A) on the first gas flow branch (28A) and to the first end (44C1) of the third additional thermal energy release system (44C); a second end (44C2) of the third additional thermal energy release system (44C) connected to the second connection point (32B) on the second gas flow branch (28B); a first additional three-way valve (48A) connected to the inlet (1E) of the compressor part (1) of the electric turbocharger, to the first connection point (30A) on the first gas flow branch (28A) and to the first end (44C1) of the third additional thermal energy release system (44C); via a line (50A) connected to the outlet (1S) of the compressor part (1) of the electric turbocharger, to the second connection point (30B) on the first gas flow branch (28A) and to one of the channels (48C1) of a third additional three-way valve (48C), which is further connected to the inlet (2E) of the turbine part (2) of the electric turbocharger and to the first connection point (32A) on the second gas flow branch (28B); and via a second gas line (50B) an additional fourth three-way valve (48D),10. The heat pump according to claim 8 or 9, characterized in that the first and third additional thermal energy discharge systems (44A, 44C) are each arranged to exchange thermal energy with the first gas line (50A), and the second additional thermal energy discharge system (44B) is arranged to exchange thermal energy with the second gas line (50B).

11. 10. A method for supplying thermal energy in the form of heat at temperatures between +100°C and +800°C and / or in the form of cold at temperatures between -100°C and +150°C using a heat pump according to claim 1, comprising: (a) a fill cycle step by mechanical compression of at least one gas, preferably accompanied by mechanical expansion of said at least one gas; a discharge cycle step without compression and / or expansion, wherein the thermal energy is discharged via at least one thermal energy release system, for example via at least one valve, at least one circulator, and / or at least one heat exchanger.

12. 12. The method of claim 11, wherein the dispensing cycle step (b) is performed in parallel with the filling cycle step (a).

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