Heat pump having two thermal-energy storage and release systems

Abstract

The invention relates to a heat pump, wherein: - at least one of the at least two thermal-energy storage systems is configured to store thermal energy in the form of heat 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 the form of cold at a temperature between -100°C and +150°C; and - at least one thermal-energy release system is configured to release heat and / or cold separately or in parallel over time, or - at least one thermal-energy release system is configured to operate in a parallel release mode that may be alternated with an operation mode of separate release of heat and / or cold over time.

Description

[0001] The invention relates to an electric heat pump comprising at least two thermal energy storage systems enabling the release of thermal energy at temperatures ranging from -100°C to +800°C, in particular the release of thermal energy in the form of heat at temperatures between +100°C and +800°C and / or cooling at temperatures between -100°C and +150°C, as well as a method for supplying such thermal energy using such a heat pump. In the context of the present invention, "cooling" refers to a "relative" cooling, compared to the temperatures involved in the production of thermal energy in the form of heat.

[0002] Five basic elements have been identified as being involved in achieving a deep decarbonization of the energy system: 1. Maximize energy efficiency to reduce energy needs; 2. Decarbonize electricity supply; 3. Economy-wide electrification to push clean electricity into other sectors; 4. Use carbon-free fuels for the remaining areas that cannot be efficiently electrified; and 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] We are seeing a lot of effort, investment and innovation in these areas.

[0004] Efforts to improve energy efficiency in industry include, in particular: improvement and investment in technologies enhancing the energy efficiency of, in particular, heat pumps and chillers; and recovery of so-called "waste" energy: use once again of heat pumps, ORC systems ("Organic Rankine Cycle" in French) or simple storage (i.e. a release with efficiency less than 1) of thermal energy.

[0005] Waste energy corresponds to residual energy (i.e., lost if not recovered) produced by buildings and industries.

[0006] Efforts to decarbonize the electricity grid and to meet the need for flexibility, particularly in storage, are specifically: massive investments in renewable energies (wind, solar, tidal, hydro). However, the intermittency of most of these means of production leads to an increased need for flexibility, that is to say a simultaneous adaptation of the demand and production of electricity, for example: via electricity storage or the activation of electricity-consuming systems in case of excess on the grid; and via systems for shedding electrical loads (machines) or the use of electricity storage in case of deficit.

[0007] This is the sector where there seems to be the most investment. Historically dominated by pumped-storage systems (pumped-storage power plants are also called PSPs for "Pumped Power Plants") and in recent years by large-scale Li-Ion battery systems, the electricity storage sector is thus seeing the emergence of many new technologies.

[0008] Regarding the electrification of high-temperature industrial processes, the needs and production of high-temperature heat and cooling are rarely optimized at the design stage. The manufacture of high- and very-high-temperature heat production equipment (boilers, burners, furnaces, steam generators, etc.) is a specialized field, and the manufacture of low- and very-low-temperature cooling production equipment (chillers, refrigeration units, cryogenics, etc.) is another specialized field; therefore, these industries are separate. This follows a historical and technological logic, which explains the separation of the two sectors and their specific characteristics.

[0009] However, end-use industries have long integrated reliability (i.e., constant availability) and low cost of industrial heat, particularly gas and / or fuel oil, into their practices and business models for their needs above 100°C. With a cost in 2019 of around €50-55 per MWh of thermal natural gas in France (ADEME, Brochure ref. 010895, Jan. 2020, €51-85 per MWh), as well as in many other European countries (for large sites), it is very difficult for industrialists to electrify their heat production methods – as this would lead to an additional cost of heat of around 50% or more – or to replace them with production methods based on renewable energies (again: additional costs, technical limitations and problems of intermittency).

[0010] Furthermore, it is interesting to note that many sectors have industrial processes requiring: high temperature heat (> 100-120°C and up to 400°C); and cold / refrigeration (down to -50°C).

[0011] For example, these needs are found particularly in the following industries: agri-food (including prepared meals, dried food, powders (milk, coffee...); pharmaceuticals (powders, pills...); chemicals in the broad sense (preparation, packaging and storage of products), such as for petrochemical products (gas and oil, plastics, rubber), adhesives, etc.; and certain supermarkets and large catering centers (in particular so-called fast food).

[0012] In this context, certain heat pump systems for simultaneous heating and cooling are known from the state of the art.

[0013] For example, DE102018221850A1 discloses a heat pump system enabling heating and cooling (between -15°C and 60°C), with a liquid-liquid heat pump connected on one side to a heat source and on the other side to a heat sink featuring in particular a hot water tank.

[0014] JP2016211830A discloses the use of a heat pump for heating and cooling. More specifically, the disclosed temperature ranges are between 0°C and approximately 100°C.

[0015] JP3037649B2 discloses a dehumidifying air conditioning system, in which the energy efficiency of the air conditioning system as a whole is increased to reduce operating costs, while minimizing energy consumption during the day and minimizing thermal radiation to the outside air during nighttime heat buildup.

[0016] However, none of these systems allow for the simultaneous or alternative release of high and / or very high temperature heat and low and / or very low temperature cold.

[0017] Within the specific context of the power generation and supply industry, other systems exist for storing heat and cold, possibly simultaneously. Patent documents EP2220343, EP2574740, US10907510, US8627665, and US20140223910 illustrate this type of technology. However, the devices described in these documents are specific to the power generation and supply industry, as they are designed specifically for electricity storage and are therefore sized to operate in cycles that must re-equilibrate in temperature after charging and discharging. Such devices cannot be used as such in other industries (particularly those mentioned above) or even for private purposes. US 2010 / 301614 A1 discloses a heat pump according to the preamble of claim 1. Summary of the invention

[0018] The aim of the present invention is therefore to overcome the drawbacks of the prior art by proposing an electric heat pump, as defined in claim 1, comprising: at least two thermal energy storage systems, and at least one thermal energy release system, in which: at least one of the thermal energy storage systems is configured to store thermal energy as heat at a temperature between +100°C and +800°C, at least one of the thermal energy storage systems is configured to store thermal energy as cold at a temperature between -100°C and +150°C; and said at least one thermal energy release system is configured to release heat and / or cold separately or in parallel over time, or said at least one thermal energy release system is configured for parallel release operation that can be alternated with separate release operation of heat and / or cold over time; the heat pump being configured to include a reverse Brayton cycle (for example, without phase change) operating with a gas, and comprising a single-stage centrifugal electric turbo-compressor.

[0019] The simultaneous production of two flows (high-temperature heat and cold, most often negative) enables improved energy efficiency and provides industrial users with a thermal energy supply solution that drastically reduces CO2 emissions without increasing production costs, or even lowers them depending on the prices of locally available energy sources. Furthermore, the use of a single-stage, centrifugal electric turbocompressor increases the compactness and efficiency of the heat pump, as well as reducing its cost. Moreover, such a single-stage, centrifugal electric turbocompressor operates without oil, thus preventing any contamination or acidification within the system.The use of a single turbocharger means that there is only one operating point (usually defined by the flow rate / compression ratio pair) for the compressor / turbine pair in the gas circulation circuit, common for a charge and discharge cycle of the heat pump.

[0020] In the context of this invention, a "single turbocharger," also called a "single turbomachine," is understood to mean a single machine capable of simultaneously increasing gas pressure and reducing gas pressure at another point in the circuit. In addition to high-power axial turbochargers, there are at least two types of radial turbochargers: piston turbochargers (more commonly called "compressors") and centrifugal turbochargers. Centrifugal turbochargers have few moving parts subject to friction, relatively high energy efficiency, and move a higher gas flow rate than similarly sized reciprocating compressors. Turbochargers cannot achieve the same high compression ratio as reciprocating compressors, which, in multi-stage configurations, can reach pressures of 100 MPa.

[0021] For the purposes of this invention, "single-stage turbocharger" means a turbocharger comprising a single compression and expansion train, in other words, a single compression structure (or part), also called a "compressor"; and a single expansion structure (or part), also called a "turbine".

[0022] Preferably, the single-stage centrifugal electric turbocharger has a compression ratio between 1 and 5, the compression ratio being defined as the ratio between the outlet pressure of the turbocharger's compressor section and the inlet pressure of said compressor section. Choosing this specific range of compression ratio values ​​allows for a single operating point for the compressor / turbine combination, particularly well-suited for both charging and discharging the heat pump, with appropriate pressure, temperature, and flow rates. Within this specific range, the heat pump also maintains high energy efficiency and a substantial gas flow rate.

[0023] Preferably, the heat pump according to the present invention can be characterized in that: at least one of the thermal energy storage systems is configured to store thermal energy at temperatures between -50°C and +100°C, and / or in that at least one of the thermal energy storage systems is configured to store thermal energy at temperatures between +150°C and +500°C, preferably between +200°C and +400°C.

[0024] Preferably, the heat pump according to the present invention can be characterized in that said at least two thermal energy storage systems are configured to store thermal energy in the form of heat and in the form of cold.

[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] Alternatively, the gas can be an inert gas such as nitrogen.

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

[0028] Preferably, the heat pump according to the present invention can be characterized in that the different operating components of said heat pump are isolated in modules, said modules being configured to be connected to each other, for example, by physical connections such as valves (for example, remotely controllable), pipes to be connected and / or hoses.

[0029] Preferably, the heat pump according to the present 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 oven, solar heat, a dryer and / or artificial heat loss.

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

[0031] For the purposes of this invention, "escape" means a final controlled phase of energy circulation, for example in the form of hot steam or smoke, from an artificial heat source.

[0032] In the context of this invention, "loss" refers to a useful deprivation of energy from the artificial heat source. This deprivation is most often uncontrolled, difficult to control, or results from poor management or configuration of the artificial heat source.

[0033] By "output" of a heat source, it is understood in the context of the present invention to mean a channeled and expected output of a heat source, that is to say, where it is expected to recover the majority of said heat (for example, steam condensates, via the return circuit of a process).

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

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

[0036] In a particular embodiment, the heat pump comprises four thermal energy storage systems, two thermal energy release systems, two three-way valves and two pumping elements; a first end of a first thermal energy storage system being connected to a first end of a second thermal energy storage system via a first gas circulation branch; a first end of a third thermal energy storage system being connected to a first end of a fourth thermal energy storage system via a second gas circulation branch; a first thermal energy release system being arranged to exchange thermal energy with the first gas circulation branch, a second thermal energy release system being arranged to exchange thermal energy with the second gas circulation branch;a first three-way valve being connected to a second end of the first thermal energy storage system, to a second end of the second thermal energy storage system and to a second end of the third thermal energy storage system; a second three-way valve being 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 a second end of the fourth thermal energy storage system; a first pumping element connecting the second end of the second thermal energy storage system to the corresponding port of the first three-way valve; a second pumping element connecting the second end of the third thermal energy storage system to the corresponding port of the second three-way valve;the inlet of the compressor part of the electric turbocharger being connected to the first end of the first thermal energy storage system at a first connection point on the first gas circulation branch; the outlet of the compressor part of the electric turbocharger being connected to the first end of the second thermal energy storage system at a second connection point on the first gas circulation branch; the inlet of the turbine part of the electric turbocharger being connected to the first end of the fourth thermal energy storage system at a first connection point on the second gas circulation branch; the outlet of the turbine part of the electric turbocharger being connected to the first end of the third thermal energy storage system at a second connection point on the second gas circulation branch.

[0037] This particular embodiment allows for a different order in which the gas passes through the various thermal energy storage systems (and therefore the temperatures involved) depending on whether the heat pump is in a charging or discharging cycle (thanks to the use of valves and pumping devices). This configuration makes it possible to compress the gas from potentially higher temperatures, thus either producing higher temperatures or producing the same temperature but with a lower compression ratio. Furthermore, the heat pump in this particular embodiment can produce heat and / or cooling at different times of use, and can store both types of thermal energy. Thanks to the presence of separate distribution circuits, the heat pump can also provide heat and / or cooling 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 being connected on the first gas circulation branch between the first connection point and the second connection point; a first check valve being connected between the outlet of the compressor part of the electric turbocharger and the second connection point of the first gas circulation branch; a second check valve being connected between the outlet of the turbine part of the electric turbocharger and the second connection point of the second gas circulation branch; a third check valve being connected on the second gas circulation branch between the first connection point and the second connection point.

[0039] In another particular embodiment, which constitutes an improvement of the embodiment previously described, the heat pump further comprises three additional thermal energy recovery systems, four additional two-way valves and four additional three-way valves; a first end of a first additional thermal energy recovery system being connected to a first end of the first thermal energy recovery system via a first two-way valve; a second end of the first additional thermal energy recovery system being connected to a second end of the first thermal energy recovery system via a second two-way valve; a first end of a second additional thermal energy recovery system being connected to a first end of the second thermal energy recovery system via a third two-way valve;a second end of the second additional thermal energy recovery system being connected to a second end of the second thermal energy recovery system via a fourth two-way valve; a first end of a third additional thermal energy recovery system being connected to the first connection point on the first gas circulation branch; a second end of the third additional thermal energy recovery system being connected to the second connection point on the second gas circulation branch; a first additional three-way valve being connected to the inlet of the compressor part of the electric turbocharger, to the first connection point on the first gas circulation branch and to the first end of the third additional thermal energy recovery system;a second additional three-way valve being connected to the outlet of the compressor part of the electric turbocharger, to the second connection point on the first gas circulation branch and to one of the ways of a third additional three-way valve via a first gas line; the third additional three-way valve being further connected to the inlet of the turbine part of the electric turbocharger and to the first connection point on the second gas circulation branch; a fourth additional three-way valve being connected to the outlet of the turbine part of the electric turbocharger, to the second connection point on the second gas circulation branch and to the second end of the third additional thermal energy recovery system via a second gas line;the first and third additional thermal energy recovery systems each being arranged to exchange thermal energy with the first gas line; the second additional thermal energy recovery system being arranged to exchange thermal energy with the second gas line.

[0040] In addition to the advantages of the previous embodiment (and described above), this particular embodiment of the heat pump is capable of producing instantaneous heating and cooling while simultaneously discharging heat and cold from the thermal energy storage systems. This is advantageous because it allows for the addition of instantaneous power to the heat pump's discharge cycle, for example, to meet peak demand with minimal additional equipment costs (three additional thermal energy recovery systems). This avoids the need to oversize the system (particularly by increasing the size of the thermal energy storage systems to store more energy and / or by increasing the size of the machine, for example, to produce and store more energy at night).

[0041] Another object of the present invention relates to a method for supplying thermal energy in the form of heat at a temperature between +100°C and +800°C and / or cold at a temperature between -100°C and +150°C, by using a heat pump as described above, comprising the following steps: (a) a charging cycle step by mechanical compression of at least one gas with preferably a mechanical expansion of said at least one gas; (b) a discharge cycle step without compression and / or expansion in which thermal energy is discharged via at least one thermal energy recovery 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 mechanical compression charging cycle of at least one vapor with preferably a mechanical expansion of said at least one vapor.

[0043] Preferably, the process according to the present invention can be characterized in that the discharge cycle step (b) is carried out in parallel with the charge cycle step (a).

[0044] The discharge cycle induces a fluid flow (such as a heat transfer gas) called the "discharge flow". Thus, in a particular embodiment, the discharge flow can be divided into several discharge flows, called split discharge flows, each of which can be directed to different applications.

[0045] For example, a split discharge stream can be directed to a storage system, such as a secondary storage system, which can allow for temperature scaling. DEFINITIONS

[0046] In the context of this invention, a "heat pump" is understood to mean a device that transfers thermal energy from one medium to a second medium at a higher temperature, thus reversing the natural, spontaneous flow of thermal energy. Specifically, there are high-temperature (HT) heat pumps, very high-temperature (VHT) heat pumps, low-temperature (LT) heat pumps, and very low-temperature (VLT) heat pumps. There are several classic types of heat pumps: 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 this invention is an electric heat pump of the air cycle type (for example, a gas refrigeration cycle).This process follows an inverted Brayton thermodynamic cycle in which a gas is compressed, cooled to room temperature, then expanded in a turbine, and does not involve a phase change, which distinguishes it from vapor compression heat pumps (so-called "conventional" or "thermodynamic" heat pumps) which most often follow a vapor compression refrigeration cycle, or a gas absorption heat pump.

[0047] This heat pump operates by extracting heat from a low-pressure storage tank, referred to as a "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. Simultaneously, the cold generated at the turbine outlet (expansion) is also recovered and stored.

[0048] A Brayton cycle driven in reverse is called a reversed Brayton cycle. Its purpose is to move heat from a colder body to a warmer body, rather than doing work. According to the second law of thermodynamics, heat cannot spontaneously flow 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 when forced by external work. This is precisely what refrigerators and heat pumps accomplish. These are driven by electric motors that require work from their surroundings to operate. Thus, one possible cycle is a reversed Brayton cycle, which is similar to the ordinary Brayton cycle but is driven in the opposite direction, via a net work input.This cycle is also known as the gas refrigeration cycle, air cycle, or Bell Coleman cycle. This type of cycle is widely used in airliners and trains for air conditioning systems that utilize air from the engine compressors. It is also widely used in the LNG (Liquefied Natural Gas) industry, where the largest reverse Brayton cycle is used for LNG subcooling, employing 86 MW of power from a gas turbine-driven compressor and nitrogen refrigerant (source of this information: thermal-engineering.org).

[0049] For the purposes of this invention, "high temperature" refers to a temperature range between +60 and +100°C, preferably between +70 and +95°C. This type of heat pump can be found in commercial heat pumps, including those marketed to consumers. Their efficiency decreases as the temperature difference between the cold source and the source to be heated increases.

[0050] The temperatures given in the context of the present invention, unless otherwise indicated, are in reference to the temperature of 0°C, i.e. the freezing point of water at one atmosphere at sea level (i.e. 101325 Pa corresponding to an absolute pressure of 1 bar).

[0051] For the purposes of this invention, "very high temperature" means a range of temperatures above +100°C, for example, greater than or equal to +150°C, greater than or equal to +200°C, greater than or equal to +300°C, greater than or equal to +400°C. Thus, a very high temperature in the context of this invention may include temperatures between +150 and +500°C, preferably between +150 and +400°C, or between +250 and +350°C.

[0052] For the purposes of this invention, "low temperature" means a temperature range between -20 and +5°C, preferably between -15 and -5°C.

[0053] For the purposes of this invention, "very low temperature" means a range of temperatures below -20°C, for example, less than or equal to -30°C, less than or equal to -40°C, less than or equal to -50°C, or less than or equal to +60°C. Thus, a very low temperature in the context of this invention may include temperatures between -30 and -150°C, preferably between -40 and -100°C, or between -50 and -80°C.

[0054] In the context of this invention, "thermal energy storage systems" means any means of preserving a quantity of thermal energy for later use. Thermal energy can be either hot or cold. Indeed, heat itself is a form of energy. In the case of stored cold, since producing cold requires energy, storing cold constitutes energy storage.

[0055] In the context of this invention, "thermal energy recovery system" means a means of delivering thermal energy. Furthermore, the expression "thermal energy recovery systems configured for" implies that the tanks are interchangeable (one tank can be used for heating and then for cooling during other series of charge and discharge cycles).

[0056] In the context of this invention, "separate or parallel delivery" refers to the separate or parallel delivery of thermal energy from at least two different storage systems. Separate delivery allows for the initial supply of thermal energy from at least one storage system followed by thermal energy from at least one second storage system. Parallel delivery allows for the simultaneous supply of thermal energy from at least one storage system and thermal energy from at least one second storage system.

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

[0058] For the purposes of this invention, "natural heat source" means thermal energy that does not result from any human intervention, such as a geothermal or water source (lake, sea, river, etc.).

[0059] For the purposes of this invention, "artificial heat source" means thermal energy from human intervention, such as an oven, boiler, equipment such as air conditioning, compressors, machines, generators, a residential, commercial, tertiary, industrial and / or computer process, energy from a solar thermal system or even waste heat.

[0060] In the context of the present invention, "load cycle" means a series of events that may be recurrent, i.e., a cycle, enabling the production of thermal energy that is either distributed instantaneously or stored as thermal energy.

[0061] For the purposes of this invention, "gas" means any substance in a gaseous state. Thus, a gas also includes a vapor, which results from the vaporization of a liquid (at any temperature).

[0062] In the context of the present invention, "mechanical expansion" refers to the expansion of gas initially compressed via a turbine.

[0063] In the context of the present invention, "discharge cycle" means the inverse function of a charge cycle, i.e., enabling the release of thermal energy stored in storage systems.

[0064] In the context of this invention, a "heat exchanger" is understood to mean a device that transfers thermal energy from one fluid to another without mixing them. This refers to a "transfer fluid," that is, a fluid as defined above, that allows the thermal energy to be moved from one location to another.

[0065] For example, there are liquid / liquid, gas / liquid, or gas / gas heat exchangers such as plate heat exchangers or shell and tube heat exchangers that can be used in the context of the present invention. There are many suppliers of such heat exchangers, such as those from Alfa-Laval®. DETAILED DESCRIPTION

[0066] The object of the present invention is to adapt, improve and combine: a proven technology to increase its efficiency and adapt it to the needs of thermal processes (heat and cooling), special electric turbomachines (electric turbocompressors), whose regime can be controlled (via the regulation of the flow / rotation speed and the compression ratio) for example via the use of power electronics and software, thermal storage (refrigeration and heat, separate) to add flexibility to the system and the interest of the solution for an industrialist.

[0067] Thus, the object of the present invention may include one or more sensors, which combined with the use of software (and its algorithms) allow the heat pump to be controlled according to the present invention.

[0068] Furthermore, the object of the present invention introduces several key innovative elements in terms of technology and functionality: Electric production of high temperature heat (> 150°C and up to 500-800°C) and industrial cooling (down to -50°C) with a COP (coefficient of performance - efficiency) of 1.5 or more, using a refrigerant (such as air or argon) with a GWP (global warming potential) of 0; high-density energy storage in thermal form of this energy produced or heated / supercooled: heat (> 150°C) and industrial cooling (down to -50°C) in the same module, capable of storing the energy for several hours, or even a few days.

[0069] It is possible to place the various constituent elements (electric turbo-compressor, motor, storage system, etc.) of the heat pump according to the present invention in one or more modules or sub-modules which can be combined or integrated with each other; the whole can be contained in a container (for example standard containers called "20 feet" or "40 feet", i.e. about 6 meters or 12 meters) or placed on a chassis.

[0070] The modules or sub-modules as defined above can be combined with other similar modules or sub-modules as needed.

[0071] It is possible to integrate and utilize waste or solar thermal energy flows with all of these modules and / or sub-modules, for example, by adding one or more heat exchangers. Thus, the object of the present invention also makes it possible to raise the temperature level of the recovered waste or solar thermal energy, to store it, and to release it according to the desired use.

[0072] Thus, in a particular embodiment, the various functional elements of the heat pump according to the present invention can be isolated in modules. This modular system allows the heat pump to be easily arranged according to the physical layout of the site where it is to be installed. Indeed, modularity allows the heat pump to be adapted to on-site production needs, for example, by increasing or decreasing the production (power) or storage (energy) capacities of thermal energy. Furthermore, modularity allows for variations in original configurations. For example, modularity can allow the insertion of several storage systems to achieve a diversity of temperatures, whether at the input (recovery of waste heat at different temperature levels and / or temperature variations) and / or at the output (production of thermal energy at a specific temperature and / or with varying temperature requirements).

[0073] In addition, it can be advantageous to use rail and / or chassis systems (“skids” in English) to facilitate modularity.

[0074] In one particular embodiment, the modules comprising the different elements are adapted for their movement in containers.

[0075] Module recombination makes it possible to limit the number of module variants and therefore optimize the cost of systems while being able to address a greater number of different needs.

[0076] Furthermore, thermal energy storage according to the present invention can be achieved by installing elements in storage systems such as tanks (for example, those mentioned above) that, during a charging phase, absorb and store thermal energy, for example, by stacking smaller blocks (compared to said tanks) at different levels. These blocks can be in the form of gravel, refractory bricks, ceramic pieces, cement pieces, rock pieces (for example, volcanic or granitic), or even zeolites.

[0077] Alternatively, stacking on different levels can take the form of capsules containing conventional PCMs (phase change materials) such as certain sands (such as molten salts), notably KNO3 - 60%NaNO3 or NaCl / MgCl2 (57 / 43) used for more than 20 years in concentrated solar power (CSP) plants, paraffin, CaCl2 6H2O.

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

[0079] This same thermal energy (minus the thermal losses inherent in the system) will of course be returned to the landfill.

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

[0081] The tanks and pipes will be thermally insulated with conventional insulating materials such as rock wool or other standard insulation.

[0082] The heat pump according to the present invention thus comprises at least two cycles, one called charging and the other called discharging.

[0083] For example, a charging cycle might include: a compression of the fluid (i.e., the gas) between 1-5 bar (starting from 1 bar with a compression ratio between 1 and 5) (and therefore, for example, heated to 150-300 °C in the case where the gas is air) in the compressor; a discharge of the heat from the fluid into the storage material / element in a first tank; an expansion in the turbine of the compressed air, which has been cooled during its passage through the first tank, but is still under pressure; heating in a second tank of the very cold air (between -100 and +10) and at a pressure largely reduced due to the expansion by the turbine (and therefore "transmission of cold"); the "heated" cold air returns to the compressor; the cycle repeats until the tanks are full (information given by sensors and / or by the stopping of the electric turbocompressor controlled by the system).

[0084] For example, a discharge cycle may include: Circulators installed on the external loop of each of the tanks (distribution) transfer the energy from the tanks to the heat exchangers which are mounted on the customer's process loops; at the outlet of the exchanger, the distribution loop recovers the return from the customer's process;

[0085] Thus, no compression or expansion is used in this cycle; only circulators and / or pumps are employed. The hot and cold energy distribution systems are independent, so discharge can occur simultaneously or alternately. Discharge stops if customer demand is met or if the tanks are empty (again, information from sensors triggers the circulator control system to stop the system). Brief description of the drawings

[0086] The following are examples of embodiments of the present invention, by way of non-limiting illustration, with reference to the accompanying figures in which: [ Fig.1 ] represents in perspective a heat pump according to the present invention on a chassis; [ Fig. 2 ] is a conceptual diagram representing a charging cycle of a heat pump according to the present invention; [ Fig.3 ] is a conceptual diagram representing a discharge cycle of a heat pump according to the present invention: [ Fig. 4 ] is a schematic conceptual representation of a heat pump according to the present invention, viewed from above; [ Fig. 5 ] is a schematic conceptual representation of a heat pump according to the present invention, viewed from above, in which said heat pump is connected to a waste energy source; [ Fig. 6] is a schematic conceptual representation of a heat pump according to the present invention, viewed from above, in which said heat pump is connected to two additional thermal energy storage systems; Fig. 7 ] represents in perspective a heat pump according to the present invention in a container; [ Fig. 8 ] is a conceptual diagram representing a particular embodiment of a heat pump according to the present invention, in a heat pump charging cycle, the heat pump comprising four thermal energy storage systems; Fig. 9 ] is a simplified schematic representation of thermal energy storage systems of the [ Fig. 8 ] ; ] Fig. 10 ] is a conceptual diagram of the heat pump of the [ Fig. 8 ], in a heat pump discharge cycle; [ Fig. 11 ] is a simplified schematic representation of thermal energy storage systems of the [ Fig. 10] ; And [ Fig. 12 ] is a conceptual diagram representing another particular embodiment of a heat pump according to the present invention, in a heat pump charging cycle, the heat pump comprising four thermal energy storage systems; [ Fig. 13 ] is a simplified schematic representation of thermal energy storage systems of the [ Fig. 12 ] ; ] Fig. 14 ] is a conceptual diagram of the heat pump of the [ Fig. 12 ], in a heat pump discharge cycle; and [ Fig. 15 ] is a simplified schematic representation of thermal energy storage systems of the [ Fig. 14 ].

[0087] With reference to the [ Fig.1[ ], where a heat pump according to the present invention is shown in perspective on a chassis 15, a compressor 1 and a turbine 2 can be seen connected to each other by an electrical and / or mechanical link 13, driven by an electric motor 3. The compressor and the turbine are both connected by pipes 10 to a first storage system 4 on the one hand, and to a second storage system 5 on the other hand, 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 turbocompressor.

[0088] There [ Fig. 2 ] is a schematic representation of the heat pump of the [ Fig.1], connected to thermal energy release systems 6, represented here in a load cycle. The first storage system 4 and the second storage system 5 are thus each respectively connected to a thermal energy release system 6, allowing them to supply heat or cold to a customer system 7. The direction of the flow represented by the arrows 8 implies here that thermal energy in the form of heat is concentrated in the second storage system 5, while thermal energy in the form of cold is concentrated in the first storage system 4. The cold thermal energy storage is at low pressure. A temperature gradient can then be created in the first storage system 4 and in the second storage system 5 such that, theoretically, Q1 is at a higher temperature (i.e., hotter) than Q2, and Q3 is at a lower temperature (i.e., colder) than Q4. In the [ Fig. 2 ], no discharge is shown.

[0089] With reference to the [ Fig.3 ], the assembly diagram identical to that shown in [ Fig. 2 ] is represented here on a discharge cycle. By discharging the thermal energy stored in the first storage system 4 and the second storage system 5 to two thermal energy release systems 6, it is possible to supply heat and cold to customer systems 7. In the [ Fig.3 The second storage system 5 is cooled by this discharge, and therefore a temperature gradient can be created such that, theoretically, Q6 is at a lower temperature (i.e., colder) than Q5. Similarly, a temperature gradient can be created in the first storage system 4 such that, theoretically, Q8 is at a higher temperature (i.e., warmer) than Q7. In the figures 2 And 3 Therefore, it is apparent that charging and discharging cycles can operate in parallel.

[0090] There [ Fig. 4 ] is a top-view representation of the assembly diagram according to the figures 2 And 3 Compressor 1, turbine 2, and motor 3, along with its (electrical) power unit and any standard fittings, are assembled in a working group 9. Working group 9, first storage system 4, second storage system 5, and pipes 10 constitute a first heat pump assembly 14 according to the present invention.

[0091] There [ Fig. 5 ] is a top-view representation of an assembly diagram showing the elements of the [ Fig. 4[furthermore, it presents a source 11 of waste energy (or thermal energy of natural or solar origin) allowing a thermal energy input represented by arrow 12. Any means of capturing this waste energy can be applied (for example, a heat exchanger connected to the pipe circuit 10 of the heat pump assembly 14 according to the present invention). It is possible to place a thermal energy input between the storage system 5 and the turbine of the working unit 9, and / or between the storage system 4 and the (turbo-)compressor of the working unit 9.]

[0092] There [ Fig. 6[ ] represents a heat pump assembly 14 according to the present invention, comprising two thermal energy storage systems 4A and 5A and a working unit 9. An assembly 15, comprising two thermal energy storage systems 4B and 5B, is connected to the heat pump assembly 14 according to the present invention. The working unit 9 is doubly connected to each of the storage systems 4A, 4B, 5A, and 5B. Furthermore, the thermal energy storage system 4A is connected by a pipe 10 to the thermal energy storage system 4B. The thermal energy storage system 5A is connected by a pipe 10 to the thermal energy storage system 5B.

[0093] In the figures 4, 5 And 6 The exchangers 6 are placed outside the assemblies 14, 15. It is also possible that the heat exchangers are placed inside the assemblies 14, 15.

[0094] From a practical point of view, sets 14 and 15 of figures 4, 5 And6 can be containers.

[0095] There [ Fig. 7 ] is a perspective representation of the heat pump of the [ Fig.1 inserted into a container 14.

[0096] There [ Fig. 8 [ ] is a conceptual diagram representing a particular embodiment of a heat pump according to the present invention, in a heat pump charging cycle. In this particular embodiment, in addition to the single-stage centrifugal electric turbocompressor 1, 2, the heat pump comprises four thermal energy storage systems 16A-16D, two thermal energy release systems 18A, 18B, two three-way valves 20A, 20B, two pumping elements 22A, 22B, one two-way valve 24 and three non-return valves 26A-26C.

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

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

[0099] A first pumping element 22A (typically a pump) connects the second end 16B2 of the second thermal energy storage system 16B to the corresponding port 20A1 of the first three-way valve 20A. Another port 20A2 of the first three-way valve 20A is connected to the second end 16A2 of the first thermal energy storage system 16A, and the last port 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 element 22B (typically a pump) connects the second end 16C2 of the third thermal energy storage system 16C to the corresponding port 20B1 of the second three-way valve 20B.Another 20B2 channel 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 20B3 channel 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 compressor section 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 circulation branch 28A. The outlet 1S of the compressor section 1 of the electric turbocharger 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 circulation branch 28A. The inlet 2E of the turbine section 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 circulation branch 28B.The output 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 circulation branch 28B.

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

[0102] The operation of the heat pump according to this particular embodiment is illustrated in the figures 8 and 9When the pump is in a load cycle, the direction of flow represented by arrows 34 implies that thermal energy in the form of heat is concentrated in the second storage system 16B (after being extracted from the first storage system 16A and then compressed in compressor 1), while thermal energy in the form of cold is concentrated in the third storage system 16C (after being extracted from the fourth storage system 16D and then expanded in turbine 2). Cold thermal energy storage is at low pressure (typically around one bar when the gas used is air), while hot thermal energy storage is at high pressure (typically between one and five bars when the gas used is air). Cold thermal energy extraction is at high pressure, while hot thermal energy extraction is at low pressure.The temperature gradients that are created in the second and third storage systems 16B, 16C cause 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.

[0103] The operation of the heat pump according to this same particular embodiment is illustrated on the Figures 10 and 11When the pump is in a discharge cycle, by discharging the thermal energy stored in the second storage system 16B and the third storage system 16C to the two thermal energy recovery systems 18A and 18B, it is possible to supply heat and cooling to customer systems. This establishes a first loop 38 between the first storage system 16A and the second storage system 16B, and a second loop 40 between the third storage system 16C and the fourth storage system 16D. In the first loop 38 (in which the first pumping unit 22A is activated, and the heat pump supplies heat to the first thermal energy recovery system 18A), the second storage system 16B is cooled by the discharge, thus creating a temperature gradient that causes the gas to circulate in the direction of the flow represented by the arrows 41.In the second loop 40 (in which the second pumping unit 22B is started, and the heat pump provides cold to the second thermal energy recovery system 18B), the third storage system 16C heats up by the discharge and a temperature gradient is therefore created which makes the gas circulate in the direction of the flow represented by the arrows 42.

[0104] This particular embodiment of the heat pump is illustrated on the figures 8 to 11This allows the order of gas flow in the first and fourth storage systems 16A, 16D to be "interchanged" during the discharge operation compared to the charging operation, without physically moving the storage systems 16A-16D. The advantage of this operation is that it avoids introducing excessively large temperature differences (thermal shocks) that would disrupt the establishment of thermoclines in the thermal energy storage systems 16A-16D and thus be detrimental to the efficiency of the thermal storage and the application in general.

[0105] Indicative, non-limiting temperature values ​​are given below as examples for the specific embodiment of the heat pump illustrated in the figures 8 to 11 : the first end 16A1 of the first storage system 16A has, for example, a temperature approximately equal to +60°C, and the second end 16A2 of the first storage system 16A has a temperature approximately equal to +80°C; the first end 16B1 of the second storage system 16B has, for example, a temperature approximately equal to +210°C, and the second end 16B2 of the second storage system 16B has a temperature approximately equal to +80°C; the first end 16C1 of the third storage system 16C has, for example, a temperature approximately equal to -30°C, and the second end 16C2 of the third storage system 16C has a temperature approximately equal to +80°C; the first end 16D1 of the fourth storage system 16D has for example a temperature approximately equal to + 20°C, and the second end 16D2 of the fourth storage system 16D has a temperature approximately equal to + 80°C;The fluid circulating in the first thermal energy recovery system 18A enters this system 18A with a temperature, for example, approximately +20°C and exits this system 18A with a temperature, for example, approximately +200°C; the fluid circulating in the second thermal energy recovery system 18B enters this system 18B with a temperature, for example, approximately +25°C and exits this system 18B with a temperature, for example, approximately -25°C.

[0106] There [ Fig. 12 [ ] is a conceptual diagram representing a particular embodiment of a heat pump according to the present invention, in a heat pump charging cycle. Analogously to the preceding embodiment described with reference to the figures 8 to 11The heat pump according to this particular embodiment comprises a single-stage centrifugal electric turbocompressor 1, 2, four thermal energy storage systems 16A-16D, two thermal energy release systems 18A, 18B, two three-way valves 20A, 20B, two pumping elements 22A, 22B, a two-way valve 24, and three non-return valves 26A-26C (all of which are connected in the same way as in the previous embodiment). Apart from the turbocompressor 1, 2 and the two thermal energy release systems 18A, 18B, the other aforementioned elements are not shown in the [ Fig. 12 For the sake of clarity, the heat pump also includes three additional thermal energy recovery 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 of the figures 12 to 15therefore constitutes an improvement on the previous embodiment described with reference to figures 8 to 11 In the figures 12 to 15 the elements described with the same numerical references as those of the figures 8 to 11 are identical to the latter and will therefore not be described in more detail later.

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

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

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

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

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

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

[0113] In the first loop 52A of the heat recovery circuit (in which the first pumping unit 22A and the second additional pumping unit 49B are activated – this loop 52A being established between the first storage system 16A and the second storage system 16B), the gas flows in the direction of the flow indicated by the arrows 60. In the second loop 52B of the heat recovery circuit (in which the first additional pumping unit 49A is activated) this loop 52B being established at the compressor part 1 of the electric turbocharger, with instantaneous energy produced by the turbocharger 1, 2 and circulating in particular in the first gas line 50A), the gas flows in the direction of the flow represented by the arrows 62. In the first loop 54A of the cold recovery circuit (in which the second pumping element 22B and the fourth additional pumping element 49D are started - this loop 54A being established between the third storage system 16C and the fourth storage system 16D), the gas flows in the direction of the flow represented by the arrows 64.In the second loop 54B of the cold recovery circuit (in which the third additional pumping unit 49C is started up - this loop 54B being established at the turbine part 2 of the electric turbocharger, with instantaneous energy produced by the turbocharger 1, 2 and circulating in particular in the second gas line 50B), the gas flows in the direction of the flow represented by the arrows 66.

[0114] In addition to the advantages associated with the previous embodiment (and explained previously), this particular embodiment of the heat pump, as illustrated in the figures 12 to 15is capable of producing instantaneous heat and cold, while simultaneously discharging heat and cold from thermal energy storage systems. This is advantageous because it allows for the addition of instantaneous power (from the electric turbocompressor 1, 2) to the previously stored energy, which is then released in parallel with the instantaneously produced energy, for example, to meet a peak demand with minimal additional equipment costs (three additional thermal energy recovery systems 44A-44C). Indeed, in this particular embodiment illustrated in the figures 12 to 15 The heat pump discharge can be performed: either by supplying only the instantaneous energy produced by the single-stage centrifugal electric turbocharger 1, 2; or by supplying at the same time the stored energy from the thermal energy storage systems and that of the single-stage centrifugal electric turbocharger (therefore with a discharge of the energy produced during the previous charge added to that of the instantaneous power produced by the turbo-compressor).

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

[0116] The attached figures can be reproduced using the parts described below. 1. Electric turbo-compressor and turbine

[0117] The turbine and electric compressor are combined into a single turbomachine, which is a single-stage centrifugal electric turbocompressor.

[0118] For example, one of the turbochargers below can 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 for energy recovery or similar BorgWarner eTurbo IHI Fuel Cell Turbocharger Liebherr - Electrical compressor with turbine (ETC) 25kW and 55kW Mitsubishi ®< electric turbo-chargers Holset ®< electric turbochargers (part of Cummins) 2. Storage system: tanks

[0119] Metal tanks, such as standard cylindrical metal tanks (steel or stainless steel) of various sizes, can be thermally insulated and capable of holding compressed air under a pressure of up to 10 bar, between 0.5 and 10m3, or even more.

[0120] There are several dozen manufacturers worldwide. The following companies, for example, sell tanks that may be suitable: Herpasa®; "tanks with thermal insulation" EMI compressed air®; see for example P 265 GH - EN10028-2; P 275 NH - EN10028-3; P 265 GH - EN10028-2; or the P 275 NH - EN10028-3 tank. Kaeser Compressors®; Colibris Compression®; see for example the Pauchard 2000L galvanized vertical tank BP RTCABJA000

Claims

1. An electric heat pump, comprising: - at least two thermal-energy storage systems (4, 5; 16A-16D), and - at least one thermal-energy release system (6; 18A, 18B): - at least one of the thermal-energy storage systems (5; 16B) being configured to store thermal energy in the form of heat at a temperature between + 100°C and +800°C, - at least one of the thermal-energy storage systems (4; 16C) being configured to store thermal energy in the form of cold at a temperature between - 100°C and +150°C; and - said at least one thermal-energy release system (6; 18A, 18B) being configured to release heat and / or cold separately or in parallel over time, or - said at least one thermal-energy release system (6; 18A, 18B) being configured for operation in a parallel release mode which can be alternated with an operation mode of separate release of heat and / or cold over time; the heat pump being configured to comprise a reversed Brayton cycle operating with a gas; characterized in that the heat pump comprises a single, single-stage centrifugal electric turbocharger (1, 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 between 1 and 5, the compression ratio being defined as the ratio between the outlet pressure of the compressor part (1) of the turbocharger and the inlet pressure of said compressor part (1).

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

4. The heat pump according to any of the preceding claims, characterized in that said at least two thermal-energy storage systems (4, 5; 16A-16D) are configured to store thermal energy in the form of heat and in the form of cold.

5. The heat pump according to any of the preceding claims, characterized in that the various operating members of said heat pump are isolated in modules, said modules being configured to be connected to one another by, for example, physical connections such as valves, connecting pipes and / or hoses.

6. The heat pump according to any of the preceding claims, 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 from solar origin or waste heat (11), a dryer and / or loss of heat of artificial origin.

7. The heat pump according to any of the preceding claims, characterized in that the gas used in the reversed 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 according to any of the preceding claims, characterized in that 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); a first end (16A1) of a first thermal-energy storage system (16A) being connected to a first end (16B1) of a second thermal-energy storage system (16B) via a first gas flow branch (28A); a first end (16C1) of a third thermal-energy storage system (16C) being connected to a first end (16D1) of a fourth thermal-energy storage system (16D) via a second gas flow branch (28B); a first thermal-energy release system (18A) being arranged to exchange thermal energy with the first gas flow branch (28A), a second thermal-energy release system (18B) being arranged to exchange thermal energy with the second gas flow branch (28B); a first three-way valve (20A) being 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 second end (16C2) of the third thermal-energy storage system (16C); a second three-way valve (20B) being 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 the corresponding channel (20A1) 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 the corresponding channel (20B1) of the second three-way valve (20B); the inlet (1E) of the compressor part (1) of the electric turbocharger being 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 outlet (1S) of the compressor part (1) of the electric turbocharger being 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 turbine part (2) of the electric turbocharger being connected to the first end (1601) of the fourth thermal-energy storage system (16D) at a first connection point (32A) on the second gas flow branch (28B); the output (2S) of the turbine part (2) of the electric turbocharger being 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 according to the preceding claim, characterized in that the heat pump further comprises a two-way valve (24) and three non-return 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); a first non-return valve (26A) being 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); a second non-return valve (26B) being 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); a third non-return valve (26C) being connected on the second gas flow branch (28B) between the first connection point (32A) and the second connection point (32B).

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

11. A method for supplying thermal energy in the form of heat at a temperature between +100°C and +800°C and / or cold at a temperature between -100°C and +150°C, using a heat pump according to any of claims 1 to 10, comprising the following steps: (a) a charge cycle step by mechanical compression of at least one gas with preferably a mechanical expansion of said at least one gas; and (b) 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. The method according to claim 11, characterized in that the discharge cycle step (b) is performed in parallel with the charge cycle step (a).

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