HEAT PUMP WITH TWO SYSTEMS FOR STORING AND RELEASING THERMAL ENERGY

Abstract

The invention relates to a heat pump in which: - at least one of at least two 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 at least two thermal energy storage systems is configured to store thermal energy as 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 for parallel release operation that can alternate with separate release of heat and / or cold over time. Abstract figure: Fig. 1

Description

Title of the invention: HEAT PUMP WITH TWO THERMAL ENERGY STORAGE AND RELEASE SYSTEMS

[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 between -100°C and +800°C, in particular the release of 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, as well as a method for supplying such thermal energy using such a heat pump. In the context of the present invention, "cold" refers to a "relative" cold, compared to the temperatures involved in the production of thermal energy in the form of heat.

[0002] In its 2019 report (Decarbonizing the Electricity sector & Beyond; a report from the 2019 ASPEN Winter Energy Roundtable), the “ASPEN Winter Energy Roundtable” identified five basic elements involved in achieving a deep decarbonization of the energy system:

[0003] 1. to make maximum use of energy efficiency in order to reduce energy requirements genetics to satisfy;

[0004] 2. decarbonize the electricity supply;

[0005] 3. Economy-wide electrification to push clean electricity towards other sectors;

[0006] 4. Use carbon-free fuels for the remaining areas that cannot be efficiently electrified; and

[0007] 5. utilize carbon capture, utilization and storage (“CCUS”) and carbon dioxide removal (“CDR”) for areas where fossil fuels are still needed and to achieve negative emissions.

[0008] There are many efforts, both in terms of investment and innovation, in these areas.

[0009] Efforts to improve energy efficiency in industry include, in particular:

[0010] - improvement and investment in technologies that enhance efficiency energy efficiency, including heat pumps and refrigeration units; and

[0011] - recovery of so-called "waste" energy: use once again of pumps heat, ORC systems (“Organic Rankine Cycle” in French) or simple storage (i.e. a release with efficiency less than 1) of thermal energy.

[0012] Fatal energy corresponds to residual energy (i.e., lost if it is not recovered) produced by buildings and industries.

[0013] Efforts to decarbonize the electricity grid and to meet the need for flexibility, particularly in storage, are specifically:

[0014] - massive investments in renewable energies (wind, solar, etc.) (remote turbine, tidal turbine). 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 electricity demand and production, for example:

[0015] - via electricity storage or the activation of electricity-consuming systems in case of network overload; and

[0016] - via electrical load shedding systems (machines) or the use of electricity storage in case of deficit.

[0017] It is in this sector that there seems to be the most investment. Historically dominated by pump-storage systems (pumped-storage power plants are also called PSW for "Pumped Storage Power Plants") and for some years by large-scale Li-Ion battery systems, the electricity storage sector is thus seeing the emergence of many new technologies.

[0018] With regard to the electrification of high-temperature industrial processes, the requirements 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 in itself, and the manufacture of low- and very-low-temperature cooling production equipment (chillers, refrigeration units, cryogenics, etc.) is another specialized field; therefore, the industries are separate. This follows a historical and technological logic, which explains the separation of the two sectors and their specific characteristics.

[0019] However, end-use industries have long integrated into their practices and business models the reliability (i.e., constant availability) and low cost of industrial heat, particularly gas and / or fuel oil, 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 facilities – as this would lead to an additional cost of heat of around 50% or more – or to replace them with production facilities based on renewable energies (again: additional costs, technical limitations and problems of intermittency).

[0020] Furthermore, it is interesting to note that many sectors have industrial processes requiring:

[0021] - high-temperature heat (> 100-120°C and up to 400°C); and

[0022] - cold / refrigeration (down to -50°C).

[0023] For example, these needs are found particularly in the following industries:

[0024] - agri-food (in particular prepared meals, dried food, powders (milk, coffee...) ;

[0025] - pharmaceuticals (powders, pills...);

[0026] - chemicals in the broadest sense (preparation, packaging and storage of products), such as than for petrochemical products (gas and oil, plastics, rubber), adhesives, etc.; and

[0027] - certain supermarkets and large catering centers (in particular catering said to be fast - from the English "fast-foods").

[0028] In this context, certain heat pump systems for simultaneous heating and cooling are known from the prior art.

[0029] 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 having in particular a hot water tank.

[0030] 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.

[0031] 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.

[0032] However, none of these systems allows for the simultaneous or alternative release of high and / or very high temperature heat and low and / or very low temperature cold.

[0033] In 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 therefore be used as such in other industries (particularly those mentioned above) or even for private purposes. Summary of the invention

[0034] The aim of the present invention is therefore to overcome the drawbacks of the prior art by proposing an electric heat pump, comprising:

[0035] - at least two thermal energy storage systems, and

[0036] - at least one thermal energy recovery system,

[0037] in which:

[0038] - at least one of the thermal energy storage systems is configured for to store thermal energy in the form of heat at a temperature between +100°C and +800°C,

[0039] - at least one of the thermal energy storage systems is configured for to store thermal energy in the form of cold at a temperature between -100°C and +150°C; and

[0040] - said at least one thermal energy recovery system is configured to to release heat and / or cold separately or in parallel over time, or

[0041] - said at least one thermal energy release system is configured for a operation of a parallel output which can be alternated with an operation in separate output in time of heat and / or cold; the heat pump being configured to include an inverted Brayton cycle (for example without phase change) operating with a gas, and comprising a single single-stage centrifugal electric turbocompressor.

[0042] The simultaneous production of the two flows (high-temperature heat and cold, most often negative) makes it possible to achieve better energy performance 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 one charge and discharge cycle of the heat pump.

[0043] In the context of the present invention, the term "single turbocharger," also called "single turbomachine," refers to a single machine that simultaneously increases gas pressure and reduces gas pressure at another point in the circuit. In addition to high-power axial-type turbochargers, it 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 compression ratio as reciprocating compressors, which are capable of reaching pressures of 100 MPa in multi-stage configurations.

[0044] By "single-stage turbocharger", in the context of the present invention, 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".

[0045] 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 particular range of values ​​for the compression ratio makes it possible to obtain a single operating point for the compressor / turbine combination, particularly suitable for enabling both charging and discharging cycles of the heat pump, with appropriate pressure and temperature levels and flow rates. Within this particular range, the heat pump also maintains high energy efficiency and a substantial displaced gas flow.

[0046] Preferably, the heat pump according to the present invention can be characterized in that:

[0047] - at least one of the thermal energy storage systems is configured for storing thermal energy at temperatures between -50°C and +100°C, and / or

[0048] - 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.

[0049] 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.

[0050] 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. gas.

[0051] The gas can alternatively be an inert gas such as nitrogen.

[0052] Preferably, the single-stage centrifugal electric turbocharger produces a pressure less than or equal to 8 bars, preferably between 1 and 5 bars (corresponding to said compression ratio between 1 and 5, for a gas initially at atmospheric pressure).

[0053] 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.

[0054] 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.

[0055] 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.

[0056] By "escape" in the context of the present invention is understood a final controlled phase of energy circulation, for example in the form of hot steam or smoke, from an artificial heat source.

[0057] In the context of the present invention, "loss" means 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.

[0058] By "outlet" of a heat source, it is understood in the context of the present invention to mean a channeled and expected outlet 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).

[0059] 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. cooling.

[0060] 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.

[0061] 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 branch; gas circulation.

[0062] This particular embodiment allows for a different order of gas flow through the various thermal energy storage systems (and therefore different temperatures involved) depending on whether the heat pump is in a charging or discharging cycle (thanks to the use of valves and pumping devices). Such a configuration makes it possible to compress the gas from potentially higher temperatures and thus either produce higher temperatures or produce the same temperature but with a lower compression ratio. The heat pump in this particular embodiment can also produce heat and / or cooling at different times of use and allow for the storage of both types of thermal energy. Thanks to the presence of separate return circuits, the heat pump can also provide heat and / or cooling simultaneously or independently.

[0063] 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.

[0064] In another particular embodiment, which constitutes an improvement of the embodiment described above, 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 restitution system being connected to a second end of the second thermal energy restitution 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 section 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 section 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.

[0065] In addition to the advantages associated with the previous embodiment (and described above), this particular embodiment of the heat pump is capable of producing instantaneous heating and cooling while simultaneously discharging heating and cooling 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 a peak demand with minimal additional equipment costs (three additional thermal energy recovery systems). This avoids the need to oversize the system (in particular 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).

[0066] 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:

[0067] (a) a charging cycle step by mechanical compression of at least one gas with preferably a mechanical expansion of said at least one gas;

[0068] (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).

[0069] 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.

[0070] 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).

[0071] 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.

[0072] For example, a divided discharge stream can be directed to a storage system, such as a secondary storage system, which can allow for temperature scaling.

[0073] DEFINITIONS

[0074] In the context of the present invention, "heat pump" refers to a device that transfers thermal energy from a first medium to a second medium at a higher temperature, thus reversing the natural, spontaneous flow of thermal energy. In particular, there are high-temperature ("HT"), very high-temperature ("VHT"), low-temperature ("LT"), 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 the present invention is an electric heat pump of the air cycle type (for example, a gas refrigeration cycle).This process follows a reverse Brayton thermodynamic cycle in which a gas is compressed, cooled to ambient temperature, then expanded in a turbine, and does not involve a phase change, which distinguishes it from vapor compression heat pumps (classic or "thermodynamic" heat pumps) which most often follow a vapor compression refrigeration cycle, or a gas absorption heat pump.

[0075] This heat pump operates by recovering heat from a low-pressure storage tank, referred to as a "cold" tank. The gas is then compressed in a... pressurizer to increase its temperature. In the context of the present invention, this heat is stored. In parallel, the cold generated at the turbine outlet (expansion) is also recovered and stored.

[0076] 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 to do work. According to the second law 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 when forced by external work. This is exactly 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 reversed Brayton cycle is used for LNG subcooling, employing 86 MW of power from a gas turbine-driven compressor and nitrogen refrigerant (source of this common knowledge: "thermal-engineering.org").

[0077] In the context of the present 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 is lower the greater the temperature difference between the cold source and the source to be heated.

[0078] 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).

[0079] In the context of the present 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 the present invention may include temperatures between +150 and +500°C, preferably between +150 and +400°C, or between +250 and +350°C.

[0080] By "low temperature", it is understood in the context of the present invention a temperature range between -20 and +5°C, preferably between -15 and -5°C.

[0081] In the context of the present 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, less than or equal to +60°C. Thus, a very low temperature in the context of the present invention may include temperatures between -30 and -150°C, preferably between -40 and -100°C, or between -50 and -80°C.

[0082] In the context of the present 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.

[0083] In the context of the present invention, the term "thermal energy recovery system" means a means for delivering thermal energy. Furthermore, the expression "thermal energy recovery systems configured for" implies that the tanks are interchangeable (one being able to be used for heating and then for cooling during other series of charging and discharging cycles).

[0084] For the purposes of this invention, "to deliver separately or in parallel over time" means the separate or parallel delivery of thermal energy from at least two different storage systems. Separate delivery thus 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.

[0085] By “module”, in the context of the present invention is understood an element which can be juxtaposed or even combined with one or more others, which may be of the same nature or of a complementary nature to the first.

[0086] 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.).

[0087] For the purposes of this invention, "artificial heat source" means thermal energy from human intervention, such as an oven, a 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.

[0088] By "load cycle", in the context of the present invention, is understood a series of events which may be recurrent, i.e. a cycle, enabling the production of thermal energy which is either distributed instantaneously or stored in the form of thermal energy.

[0089] 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).

[0090] By "mechanical expansion", it is understood in the context of the present invention to mean the expansion of gas initially compressed via a turbine.

[0091] By "discharge cycle", in the context of the present invention, is understood the inverse function of that of a charge cycle, i.e. enabling the release of thermal energy stored in storage systems.

[0092] In the context of the present invention, the term "heat exchanger" means a device for transferring thermal energy from one fluid to another without mixing them. It therefore refers to a "transfer fluid," that is, a fluid as defined above, that allows thermal energy to be moved from one location to another.

[0093] By way of 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

[0094] The object of the present invention is to adapt, improve and at the same time combine:

[0095] - a proven technology to increase its efficiency and adapt it to needs of thermal processes (heating and cooling),

[0096] - specific electric turbomachinery (electric turbochargers), of which the The operating regime can be controlled (via regulation of flow rate / rotation speed and compression ratio), for example, through the use of power electronics and software,

[0097] - thermal storage (separate cooling and heat) to add flexibility to the system and the benefit of the solution for an industrial company.

[0098] 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.

[0099] Furthermore, the object of the present invention provides several key innovative elements in terms of technology and functionality:

[0100] - High-temperature electrical heat production (> 150°C and up to 500-800°C) and industrial refrigeration (down to -50°C) with a COP (coefficient of performance) yield) of 1.5 or more,

[0101] - use of a refrigerant (such as air or argon) having a GWP (“global warming potential”, “planetary warming potential” in English) of 0 (GWP, English acronym for “global warming potential”);

[0102] - high-density energy storage in thermal form of this energy produced or heated / supercooled: heat (> 150°C) and industrial cold (down to -50°C) in the same module, capable of storing energy for several hours, or even a few days.

[0103] 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 known as "20 feet" or "40 feet", i.e. about 6 meters or 12 meters) or placed on a chassis.

[0104] The modules or sub-modules as defined above can be combined with other similar modules or sub-modules as required.

[0105] It is possible to integrate and recover 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.

[0106] 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 mounting designs.For example, modularity can allow the insertion of several storage systems to have a diversity of temperatures, whether at the input (recovery of waste energy with different temperature levels and / or temperature variations) and / or at the output (production of thermal energy at a certain temperature and / or with variable temperature requirements).

[0107] In addition, it may be advantageous to use rail and / or chassis systems (“skids” in English) to facilitate modularity.

[0108] In a particular embodiment, the modules comprising the different elements are adapted for their movement in containers.

[0109] Module recombination makes it possible to limit the number of module variants and thus optimize the cost of systems while being able to address a larger number of different needs.

[0110] 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) on different levels. These blocks can take the form of gravel, refractory bricks, ceramic pieces, cement pieces, rock pieces (for example, volcanic or granitic), or even zeolites.

[0111] Alternatively, the stacking on different levels can take the form of capsules containing conventional PCMs (phase change materials) such as certain sands (such as molten salts), in particular KNO3-60%NaNO3 or NaCl / MgCl2 (57 / 43) used for more than 20 years in concentrated solar power (CSP) plants, paraffin, CaCl26H2O.

[0112] 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).

[0113] This same thermal energy (less the thermal losses inherent in the system) will of course be returned to the discharge.

[0114] This storage aspect is advantageous to the proper functioning of the invention.

[0115] The tanks and pipes will be thermally insulated with insulating materials classics such as rock wool or other standard insulation.

[0116] The heat pump according to the present invention thus comprises at least two cycles, one called charging and the other called discharging.

[0117] For example, a charging cycle may include:

[0118] - a compression of the fluid (i.e., the gas) between 1-5 bars (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;

[0119] - a discharge of heat from the fluid into the storage material / element in a first vat;

[0120] - an expansion in the turbine of compressed air, which has been cooled during its passage in the first tank, but is still under pressure;

[0121] - Heating in a second tank of very cold air (between -100 and +10) and to pressure is significantly reduced due to expansion by the turbine (and therefore "transmission of cold")

[0122] - the “warmed” cold air returns to the compressor;

[0123] - the cycle restarts until the tanks are full (information provided by sensors and / or by stopping the electric turbocharger controlled by the system).

[0124] For example, a discharge cycle may include:

[0125] - circulators installed on the external loop of each of the tanks (distribution) transferring energy from the tanks to the heat exchangers which are mounted on the customer's process loops;

[0126] - at the outlet of the heat exchanger, the distribution loop recovers the return flow from the process customer ;

[0127] Thus, no compression or expansion is used in this cycle; only circulators and / or pumps are used. 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). Brief description of the drawings

[0128] The following are non-limiting examples of embodiments of the present invention, with reference to the accompanying figures in which:

[0129] [Fig. 1] represents in perspective a heat pump according to the present invention on a chassis;

[0130] [Fig.2] is a conceptual diagram representing a charging cycle of a heat pump according to the present invention;

[0131] [Fig.3] is a conceptual diagram representing a discharge cycle of a heat pump according to the present invention:

[0132] [Fig.4] is a schematic conceptual representation of a heat pump according to the present invention, top view;

[0133] [Fig.5] is a schematic conceptual representation of a heat pump according to the present invention, top view, in which said heat pump is connected to a waste energy source;

[0134] [Fig.6] is a schematic conceptual representation of a heat pump according to the present invention, top view, in which said heat pump is connected to two additional thermal energy storage systems;

[0135] [Fig.7] represents in perspective a heat pump according to the present invention in a container;

[0136] [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 storage systems of thermal energy;

[0137] [Fig.9] is a simplified schematic representation of storage systems of thermal energy from [Fig.8];

[0138] [Fig. 10] is a conceptual diagram of the heat pump of [Fig.8], in a heat pump discharge cycle;

[0139] [Fig. 11] is a simplified schematic representation of the thermal energy storage systems of [Fig. 10]; and

[0140] [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;

[0141] [Fig. 13] is a simplified schematic representation of the thermal energy storage systems of [Fig. 12];

[0142] [Fig. 14] is a conceptual diagram of the heat pump of [Fig. 12], in a heat pump discharge cycle; and

[0143] [Fig. 15] is a simplified schematic representation of the thermal energy storage systems of [Fig.14].

[0144] With reference to [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, 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.

[0145] Figure 2 is a schematic representation of the heat pump of Figure 1, connected to thermal energy delivery systems 6, shown 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 delivery system 6, enabling the supply of 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).e. plus . cold) than Q4. In [Fig.2], no discharge is shown.

[0146] With reference to [Fig. 3], the same assembly diagram as that shown in [Fig. 2] is shown here for 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 [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, a temperature gradient can be created in the first storage system 4 such that, theoretically, Q8 is at a higher temperature (i.e., hotter) than Q7. In Figures 2 and 3, it is therefore apparent that charge and discharge cycles can operate in parallel.

[0147] Figure 4 is a top-view representation of the assembly diagram according to 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. This working group 9, the first storage system 4, the second storage system 5, and pipes 10 constitute a first heat pump assembly 14 according to the present invention.

[0148] Figure 5 is a top-view representation of an assembly diagram incorporating the elements of Figure 4, further showing a waste heat source 11 (or thermal energy of natural or solar origin) providing a thermal energy input represented by arrow 12. Any means of capturing this waste heat 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.

[0149] Figure 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. In addition, 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.

[0150] In Figures 4, 5 and 6, the heat exchangers 6 are located outside the assemblies 14, 15. It is also possible for the heat exchangers to be located inside the sets 14, 15.

[0151] From a concrete point of view, sets 14, 15 of figures 4, 5 and 6 can be containers.

[0152] Fig. 7 is a perspective representation of the heat pump of Fig. 1 inserted into a container 14.

[0153] Figure 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.

[0154] 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.

[0155] 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.

[0156] 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 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.

[0157] 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.

[0158] 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.

[0159] The operation of the heat pump according to this particular embodiment is illustrated in Figures 8 and 9, when the pump is in a load cycle. The direction of flow represented by arrows 34 implies here 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 the 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 the turbine 2). The cold thermal energy storage is at low pressure (typically around one bar in absolute value when the gas used is air), while the hot thermal energy storage is at high pressure (typically between one and five bars in absolute value 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 develop 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.

[0160] The operation of the heat pump according to this same particular embodiment is illustrated in Figures 10 and 11, when the pump is in a discharge cycle. By discharging the thermal energy stored in the second storage system 16B and in the third storage system 16C to the two thermal energy recovery systems 18A, 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 on the one hand, and a second loop 40 between the third storage system 16C and the fourth storage system 16D on the other.In the first loop 38 (in which the first pumping unit 22A is started, and the heat pump supplies heat to the first thermal energy recovery system 18A), the second storage system 16B is cooled by the discharge and a temperature gradient is therefore created which causes the gas to circulate in the direction of the flow represented by the arrows 4L. In the second loop 40 (in which the second pumping unit 22B is started, and the heat pump supplies cold to the second thermal energy recovery system 18B), the third storage system 16C is heated by the discharge and a temperature gradient is therefore created which causes the gas to circulate in the direction of the flow represented by the arrows 42.

[0161] This particular embodiment of the heat pump illustrated in Figures 8 to 11 allows the order of gas circulation 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) which would disrupt the establishment of thermoclines in the thermal energy storage systems 16A-16D and would therefore be detrimental to the efficiency of the thermal storage and the application in general.

[0162] Indicative, non-limiting temperature values ​​are given below by way of example for the particular embodiment of the heat pump illustrated in Figures 8 to 11: - the first end 16A1 of the first storage system 16A, for example, has a temperature approximately equal to +60°C, and the second end 16A2 of the first 16A storage system 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 restitution system 18A enters this system 18A with a temperature for example substantially equal to + 20°C and exits this system 18A with a temperature for example substantially equal to + 200°C; - the fluid circulating in the second thermal energy restitution system 18B enters this system 18B with a temperature for example substantially equal to + 25°C and exits this system 18B with a temperature for example substantially equal to - 25°C.

[0163] Figure 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 Figures 8 to 11, the 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 check valves 26A-26C (which are all connected in the same way as in the preceding embodiment). Apart from the turbocharger 1, 2 and the two thermal energy recovery systems 18A, 18B, the other aforementioned elements are not shown in [Fig. 12] for reasons of clarity.The heat pump further comprises three additional thermal energy recovery systems 44A-44C, four additional two-way valves 46A-46D and four additional three-way valves 48A-48D and four additional pumping elements 49A-49D. This particular embodiment of Figures 12 to 15 therefore constitutes an improvement on the previous embodiment. described with reference to figures 8 to 11. In figures 12 to 15, the elements described with the same numerical references as those in figures 8 to 11 are identical to the latter and will therefore not be described in more detail thereafter.

[0164] As illustrated in [Fig. 12], a 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 a 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 a fourth additional two-way valves 46C, 46D.A first end 44C1 of a third additional thermal energy recovery 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 recovery system 44C is connected to the second connection point 32B on the second gas circulation branch 28B.

[0165] 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.

[0166] 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 thermal energy recovery system Additional thermal 44B is arranged to exchange thermal energy with the second gas line 50B.

[0167] 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 return system 18B to the "cold" outlet 58 of the assembly formed by the second return system 18B and the second additional return system 44B.

[0168] The operation of the heat pump according to this particular embodiment is illustrated in 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 Figures 8 to 11. In 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 the 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 the turbine 2).

[0169] The operation of the heat pump according to this same particular embodiment is illustrated in 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 [Fig. 15], two heat return loops 52A, 52B are established on the one hand (corresponding to heat return to the first return system 18A and to the first additional return system 44A), and two cooling return loops 54A, 54B are established on the other hand (corresponding to cooling return to the second return system 18B and to the second additional return system 44B).For each output circuit (hot on one hand and cold on the other), each 52A loop, respectively 54A, can operate in. depending on the other loop 52B, respectively 54B, in parallel with the latter or individually.

[0170] 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 started - 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 represented by the arrows 60. In the second loop 52B of the heat recovery circuit (in which the first additional pumping unit 49A is started - 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 cooling recovery circuit (in which the second pumping unit 22B and the fourth additional pumping unit 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 cooling recovery circuit (in which the third additional pumping unit 49C is started - 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.

[0171] In addition to the advantages of the previous embodiment (and described above), this particular embodiment of the heat pump, as illustrated in Figures 12 to 15, 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 (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 Figures 12 to 15, the heat pump discharge can be carried out: • either by supplying only the instantaneous energy produced by the single-stage centrifugal electric turbocharger 1,2; • either by simultaneously supplying 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 charging added to that of the instantaneous power produced by the turbo compressor).

[0172] 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).

[0173] EXAMPLES

[0174] The attached figures can be reproduced using the parts described below.

[0175] 1. Electric turbo-compressor and turbine

[0176] The turbine and the electric compressor are combined into a single turbomachine, which is a single-stage centrifugal electric turbocompressor.

[0177] For example, one of the following turbochargers may be used:

[0178] - Garrett “Electric Turbo Compressor (with recovery turbine) for Fuel Cell Electric Vehicles”

[0179] - Fisher EMTCT-120k Air / EMTCT-90k Air: Electric Micro Turbo compressor with turbine for energy recovery or similar

[0180] - BorgWarner eTurbo

[0181] - IHI Fuel Cell Turbocharger

[0182] - Liebherr - Electrical compressor with turbine (ETC) 25kW and 55kW

[0183] - Mitsubishi ® electric turbo-chargers

[0184] - Holset® electric turbochargers (part of Cummins)

[0185] 2. Storage system: tanks

[0186] Metal tanks, such as standard (steel or stainless steel) cylindrical metal tanks of various sizes, can be thermally insulated and capable of containing compressed air under a pressure of up to 10 bar, between 0.5 and 10m3, or even more.

[0187] There are several dozen manufacturers worldwide. The following companies, for example, sell tanks that may be suitable:

[0188] - Herpasa®; "tanks with thermal insulation"

[0189] - 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 tank - EN10028-3

[0190] - Kaeser Compresseurs®;

[0191] - Colibris Compression ®; see for example the galvanized vertical Pauchard tank 2000L BP RTCABJA000

Claims

Demands

1. 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), wherein: - at least one of the thermal energy storage systems (5; 16B) 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 (4; 16C) 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 (6; 18A, 18B) is 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) is configured for parallel operation which can be alternated with separate operation of heat and / or cold in time; the heat pump being configured to include a reverse Brayton cycle operating with a gas; characterized in that the heat pump comprises a single single-stage centrifugal electric turbocompressor (1,2).;

2. Heat pump according to claim 1 characterized in that the single-stage centrifugal electric turbocharger (1,2) has a compression ratio 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. 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. Heat pump according to any one 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. Heat pump according to any one of the preceding claims characterized in that the various 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, pipes to be connected and / or hoses.

6. Heat pump according to any one 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, solar heat or waste heat (11), a dryer and / or artificial heat loss.

7. Heat pump according to any one of the preceding claims characterized in that the gas used in the reverse Brayton cycle of the heat pump is air, or a noble gas of the helium or argon type, or a mixture of these gases.

8. Heat pump according to any one 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 elements (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 circulation 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 circulation branch (28B);a first thermal energy recovery system (18A) being arranged to exchange thermal energy with the first gas circulation branch (28A), a second thermal energy recovery system (18B) being arranged to exchange thermal energy with the second gas circulation 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 port (20A1) of the first three-way valve (20A); a second pumping unit (22B) connecting the second end (16C2) of the third thermal energy storage system (16C) to the corresponding port (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 circulation 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 circulation branch (28A); the inlet (2E) of the turbine part (2) of the electric turbocharger being 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 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 circulation branch (28B).

9. A heat pump according to the preceding claim, characterized in that 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 circulation branch (28A) between the first connection point (30A) and the second connection point (30B); a first check valve (26A) being 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) 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 circulation branch (28B); a third check valve (26C) being connected on the second gas circulation branch (28B) between the first connection point (32A) and the second connection point (32B).

10. Heat pump according to claim 8 or 9 characterized in that the heat pump further comprises three additional thermal energy recovery 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 recovery system (44A) being connected to a first end (18A1) of the first thermal energy recovery system (18A) via a first and a second two-way valve (46A, 46B); a second end (44A2) of the first additional thermal energy recovery system (44A) being connected to a second end (18A2) of the first thermal energy recovery system (18A); a first end (44B1) of a second additional thermal energy restitution system (44B) being connected to a first end (18B1) of the second thermal energy restitution system (18B);a second end (44B2) of the second additional thermal energy recovery system (44B) being connected to a second end (18B2) of the second thermal energy recovery system (18B) via a third and a fourth two-way valves (46C, 46D); a first end (44C1) of a third additional thermal energy recovery system (44C) being connected to the first connection point (30A) on the first gas circulation branch (28A); a second end (44C2) of the third additional thermal energy recovery system (44C) being connected to the second connection point (32B) on the second gas circulation branch (28B);an additional first 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 circulation branch (28A) and to the first end (44C1) of the third additional thermal energy recovery system (44C); an additional second 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 circulation branch (28A) and to one of the ways (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 circulation 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 circulation branch (28B) and to the second end (44C2) of the third additional thermal energy recovery system (44C) via a second gas line (50B);the first and third additional thermal energy recovery systems (44A, 44C) each being arranged to exchange thermal energy with the first gas line (50A); the second additional thermal energy recovery 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, by using a heat pump according to any one of claims 1 to 10, comprising the following steps: (a) a charging cycle step involving mechanical compression of at least one gas, preferably with mechanical expansion of said at least one gas; and (b) a discharge cycle stage 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 and / or at least one heat exchanger.

12. A method according to claim 11, characterized in that the discharge cycle step (b) is carried out in parallel with the charge cycle step (a).

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