FR3133430A1 - HEAT PUMP WITH TWO THERMAL ENERGY STORAGE AND RELEASE SYSTEMS - Google Patents

Abstract

The invention relates to a heat pump in which: - 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 + 20°C; And - at least one thermal energy restitution system is configured to restore heat and/or cold separately or in parallel over time, or - at least one thermal energy restitution system is configured for parallel restitution operation which can be alternated with operation in separate restitution over time of heat and/or cold. Abstract Figure: Fig. 1

Description

HEAT PUMP WITH TWO THERMAL ENERGY STORAGE AND RELEASE SYSTEMS

The invention relates to a heat pump, preferably electric, comprising at least two thermal energy storage systems allowing thermal energy restitutions of between - 100°C and + 800°C, in particular restitutions 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 + 20°C, as well as a method for supplying such energy thermal by the use of such a heat pump.

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 core elements involved in achieving deep decarbonization of the energy system:

1. use energy efficiency as much as possible in order to reduce the energy needs to be met;

2. decarbonize the electricity supply;

3. economy-wide electrification to push clean electricity to other sectors;

4.use carbon-free fuels for remaining areas that cannot be effectively 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.

We are seeing numerous efforts, both investments and innovation, in these areas.

Efforts at the level of energy efficiency in industry are in particular:

- improvement and investment in technologies enhancing the energy efficiency of, in particular, heat pumps and refrigeration units; And

- so-called “fatal” energy recovery: once again use of heat pumps, ORC systems (“Organic Rankine Cycle” in French) or simple storage (i.e. restitution with yield less than 1) of thermal energy.

Fatal energy corresponds to the residual energy (i.e. lost if not recovered) produced by buildings and industries.

Efforts regarding the decarbonization of the electricity network and the need for flexibility, particularly storage, are in particular:

- massive investments in renewable energies (wind, solar, tidal, tidal turbines). 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 demand and production of electricity, for example:

- via the storage of electricity or the activation of electricity consuming systems in the event of excess on the network; And

- via electrical load shedding systems (machines) or use of electricity storage in the event of a deficit.

It is in this sector that there seems to be the most investment. Historically dominated by pumped-storage systems (pumped-storage power plants are also called STEPs for “Pumped Energy Transfer Stations”) and for several years by large-scale Li-Ion battery systems, the sector electricity storage is thus seeing the emergence of many new technologies.

Regarding the electrification of high-temperature industrial processes, the needs and production of high-temperature heat and cold are rarely optimized at design. The manufacture of heat production equipment, high and very high temperatures (boilers, burners, ovens, steam, etc.), being in itself a specialty, and the manufacture of cold production equipment, low and very low temperatures (groups cold, refrigeration, cryogenics, etc.), being another specialty in itself, the industries are separated. This follows a historical and technological logic, which explains the separation of the two sectors and their specific characteristics.

However, final industries have long integrated into their practices and business models, the reliability (i.e. constant availability) and the low cost of industrial heat, particularly gas and/or fuel oil, for their need above 100°C. With a cost in 2019 of around €50-55 per natural gas thermal MWh 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 manufacturers to electrify their means of heat production - because this would result in an additional cost of heat of around 50% or more - or to replace them with means of production on the renewable energy base (again: additional costs and intermittency problems).

In addition, 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 (up to -50°C).

For example, these needs are found particularly in industries:

- agri-food (notably ready-made meals, dried food, powders (milk, coffee, etc.);

- pharmaceuticals (powders, pills, etc.);

- chemical 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 – from the English “fast-foods”).

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

For example, DE102018221850A1 discloses a heat pump system allowing heating and cooling (between -15°C and 60°C), with a liquid-liquid heat pump connected on one side to a heat source and another side to a heat sink having in particular a hot water tank.

JP2016211830A discloses the use of a heat pump enabling heating and cooling. More precisely, the temperature ranges disclosed are between 0°C and approximately 100°C.

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 air outside during nocturnal heat build-up.

However, none of these systems allow simultaneous or alternative restitution of high and/or very high temperature heat and low and/or very low temperature cold.

In the particular context of the electricity manufacturing and supply industry, there are other systems allowing the accumulation of heat and cold, possibly simultaneously. Patent documents EP2220343, EP2574740, US10907510, US8627665, US20140223910 can illustrate this type of technology. However, the devices described in these documents are specific to the electricity manufacturing and supply industry and cannot be used as such in other industries (in particular those mentioned above) or even privately. .

The aim of the present invention is therefore to overcome the drawbacks of the prior art by proposing a heat pump, preferably electric, comprising:

- at least two thermal energy storage systems, and

- at least one thermal energy restitution system,

in which :

- at least one of the 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 thermal energy storage systems is configured to store thermal energy in the form of cold at a temperature between - 100°C and + 20°C; And

- said at least one thermal energy restitution system is configured to restore heat and/or cold separately or in parallel over time, or

- said at least one thermal energy restitution system is configured for parallel restitution operation which can be alternated with operation in separate restitution over time of heat and/or cold.

The simultaneous production of the two flows (high temperature heat and cold, most often negative) makes it possible to achieve better energy performance and give manufacturers a solution for supplying thermal energy by drastically reducing CO ₂ emissions without increasing the cost production, or even reducing it depending on the prices of locally available energy sources.

Preferably, the heat pump (preferably electric) 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 in the form of heat at temperatures less than or equal to - 20°C, preferably less than or equal to - 50°C, and /Or

- in that at least one of the thermal energy storage systems is configured to store thermal energy at temperatures greater than or equal to + 150°C, preferably greater than or equal to + 200°C.

Preferably, the heat pump (preferably electric) 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.

Preferably, the heat pump (preferably electric) according to the present invention can be characterized in that it is configured to comprise an inverted Brayton cycle (for example without phase change) capable of operating with a gas such as air or argon.

Preferably, the gas may be an inert gas such as nitrogen or argon.

The gas can be chosen a noble gas, such as argon.

The gas can be air (i.e. about 20% oxygen in about 80% nitrogen).

Preferably, the heat pump (preferably electric) according to the present invention can be characterized in that it comprises a turbocharger, such as a centrifugal electric turbocharger producing a pressure less than or equal to 8 bars, preferably between 1 and 5 bars.

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

Preferably, the heat pump (preferably electric) 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 heat loss of artificial origin.

Preferably, the heat pump (preferably electric) 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 in exhaust, loss or outlet. an artificial heat source such as exhaust, loss or output from a gas boiler, a gas oven, solar heat, a dryer and/or heat loss of artificial origin .

By “exhaust” is understood in the context of the present invention a last controlled phase of energy circulation, for example in the form of hot steam(s) or smoke(s), from an artificial heat source.

By “loss” is meant in the context of the present invention a useful deprivation of energy coming from the artificial heat source. This deprivation is most often uncontrolled, difficult to control or the result of poor management or configuration of the artificial heat source.

By “output” of a heat source, it is understood in the context of the present invention a channeled and expected output of a heat source, that is to say where it is expected to recover the majority of said heat (e.g. steam condensate).

In a particular embodiment, the heat pump (preferably electric) 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 (preferably electric) 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.

Preferably, the heat pump (preferably electric) according to the present invention can be characterized in that it is sized to provide energy of between 50 kWh to 5MWh.

Another object of the present invention relates to a method of 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 + 20°C, by the use of a heat pump (preferably electric) as described above, comprising the following steps:

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

(b) a discharge cycle step without compression and/or expansion in which the thermal energy is discharged via at least one thermal energy restitution system, for example via at least one valve, at least one circulator and/or at least one heat exchanger (i.e. a heat exchanger).

In a particular embodiment, step (a) is a charging cycle by mechanical compression of at least one vapor with preferably mechanical expansion of said at least one vapor.

Preferably, the method 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).

The discharge cycle induces a flow of fluid (such as a heat transfer gas) called “discharge flow”. Thus, in a particular embodiment, the discharge flow can be divided into several discharge flows called divided discharge flows, which can each be directed towards different applications.

For example, a split discharge flow may be directed to a storage system, such as a secondary storage system, which may allow for temperature scaling.

DEFINITIONS

By “heat pump”, it is understood in the context of the present invention a device making it possible to transfer thermal energy from a first medium to a second medium of higher temperature, thus going in the spontaneous natural opposite direction of thermal energy. In particular, there are so-called high temperature (“HT”), very high temperature (“THT”), low temperature (“BT”) or even very low temperature (“TBT”) heat pumps. There are typically different types of heat pumps: a vapor compression heat pump, a Peltier effect heat pump, a thermo-acoustic heat pump, a thermomagnetic heat pump, a gas absorption heat pump, a so-called Stirling heat pump. Preferably, a “heat pump” in the context of the present invention is an electric heat pump of the air cycle type (for example with a gas refrigeration cycle). This process follows a reverse 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 ( “classic” heat pumps, called “thermodynamic”), most often following a vapor compression refrigeration cycle, or a gas absorption heat pump.

This heat pump works by recovering calories in a so-called “cold” low-pressure storage tank. The gas is then compressed in a compressor to increase its temperature. In the context of the present invention, this heat is stored. At the same time, the cold generated at the turbine outlet (expansion) is also recovered and stored.

A Brayton cycle driven in reverse is called a reverse Brayton cycle. Its purpose is to move heat from a colder body to a warmer body, rather than to produce work. According to the second law of thermodynamics, heat cannot flow spontaneously from the cold system to the 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 requiring work from their environment to function. So, one of the possible cycles is a reverse Brayton cycle, which is similar to the ordinary Brayton cycle but this one is driven in reverse, via a net work input. This cycle is also known as the gas refrigeration cycle, air cycle or Coleman Bell cycle. This type of cycle is widely used in airliners for air conditioning systems using air from engine compressors. It is also widely used in the LNG (Liquefied Natural Gas) industry where the largest reverse Brayton cycle is for subcooling of LNG using 86 MW of power from a gas turbine driven compressor and d a nitrogen refrigerant (source of this usual knowledge: “thermal-engineering.org”).

By “high temperature” is meant in the context of the present invention a range of temperatures between + 60 and + 100°C, preferably between + 70 and + 95°C. This type of heat pump can be found in commercial heat pumps, including “consumer” heat pumps. Their efficiency is all the lower as the temperature difference between the cold source and the source to be heated is significant.

Temperatures given in the context of the present invention, unless otherwise indicated, are in reference to the temperature of 0°C, i.e. the solidification temperature of water at one atmosphere at sea level (i.e. say 101325 Pa corresponding to an absolute pressure of 1 bar).

By “very high temperature” is meant in the context of the present invention a range of temperatures greater than +100°C, for example greater than or equal to +150°C, greater than or equal to +200°C, greater than or equal to +150°C, equal to + 300°C, greater than or equal to + 400°C. Thus, a very high temperature in the context of the present invention can include temperatures between + 150 and + 500°C, preferably between + 200 and + 400°C, or even between + 250 and + 350°C.

By “low temperature” is meant in the context of the present invention a range of temperatures between - 20 and + 5°C, preferably between - 15 and - 5°C.

By “very low temperature” is meant in the context of the present invention a range of temperatures less than - 20°C, for example less than or equal to - 30°C, less than or equal to - 40°C, less than or equal to - 40°C, less than or equal to - 40°C, less than or equal to equal to - 50°C, less than or equal to + 60°C. Thus, a very low temperature in the context of the present invention can include temperatures between - 30 and - 150°C, preferably between - 40 and - 100°C, or even between - 50 and - 80°C.

By “thermal energy storage systems” is meant in the context of the present invention any means making it possible to preserve a quantity of thermal energy for later use. Thermal nature can be hot and cold. Indeed, heat as such is energy. In the case of stored cold, given that cold production requires energy, storing cold represents energy storage.

By “thermal energy restitution system”, it is understood in the context of the present invention a means making it possible to deliver thermal energy. In addition, the expression “thermal energy restitution systems configured for” implies that the tanks are interchangeable (one can be used for hot then for cold during other series of charge and discharge cycles).

By “returning in a separate or parallel manner over time”, it is understood in the context of the present invention the separate or parallel delivery over time of thermal energy from at least two different storage systems. The separate delivery thus makes it possible to initially provide thermal energy from at least a first storage system and then thermal energy from at least a second storage system. Parallel delivery makes it possible to provide thermal energy from at least a first storage system and thermal energy from at least a second storage system at the same time.

By “turbocharger”, also called “turbomachine”, is understood in the context of the present invention a machine allowing at the same time to increase the gas pressure and to relax the gas pressure at another point of the circuit. In addition to high-power axial-type turbochargers, there are at least two types of radial-type turbochargers: piston turbochargers (usually called “compressors”) and centrifugal turbochargers. Centrifugal turbochargers are primarily used in industry as well as automobiles because they have few moving parts in friction, have relatively high fuel efficiency, and move a higher flow of gas than reciprocal compressors of similar size. Turbochargers cannot achieve a compression ratio as high as reciprocating compressors, the latter being capable of reaching, in multi-stage, a pressure of 100 MPa.

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

By “natural heat source” is understood in the context of the present invention thermal energy resulting from no human intervention, such as a geothermal or water source (lake, sea, river, etc.) for example.

By “artificial heat source” is understood in the context of the present invention thermal energy resulting from human intervention, such as an oven, energy resulting from a solar thermal system or even waste heat. .

By “charging cycle”, it is understood in the context of the present invention a series of events which can be recurring, that is to say a cycle, allowing the storage of thermal energy.

By “gas”, it is understood in the context of the present invention any body in the gaseous state. Thus a gas also includes a vapor, which results from the vaporization of a liquid (at whatever temperature).

By “mechanical expansion” is meant in the context of the present invention an expansion of gas initially compressed via a turbine.

By “discharge cycle”, it is understood in the context of the present invention the inverse function of that of a charge cycle, that is to say allowing the release of thermal energy stored in storage systems.

By “heat exchanger” is understood in the context of the present invention a device making it possible to transfer thermal energy from one fluid to another without mixing them. It is therefore a question of “vector fluid”, that is to say a fluid as defined above, allowing thermal energy to be moved from one location to another.

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

DETAILED DESCRIPTION

The object of the present invention makes it possible to adapt, improve and at the same time combine:

- proven technology to increase its efficiency and adapt it to the needs of thermal processes (heat and refrigeration),

- specific electric turbomachines (turbocompressors), the speed of which can be controlled (via regulating the flow rate/rotation speed and the compression ratio) for example via the use of software,

- thermal storage (refrigeration and heat, separated) to add flexibility to the system and the interest of the solution for an industrialist.

Thus, the object of the present invention may include one or more sensors, which combined with the use of software (and its algorithms) make it possible to control the heat pump according to the present invention.

In addition, the subject of the present invention provides several key innovative elements in terms of technology and functionalities:

- electrical production of high temperature heat (> 150°C and up to 200-300°C) and industrial cold (up to -50°C) with a COP (coefficient of performance - efficiency) of 1.5 or more,

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

- high density energy storage in thermal form of this energy produced or reheated/supercooled: heat (> 250°C) and industrial cold (up to -50°C) in the same module, capable of conserving energy for several hours, or even a few days.

It is possible to place the different constituent elements (compressor, turbine, motor, storage system, etc.) of the heat pump according to the present invention in one or different modules or sub-modules which can be combined or integrated with each other; the assembly can be contained in a container (for example standard containers called “20 feet” or “40 feet” or approximately 6 meters or 12 meters) or placed on a chassis.

Modules or sub-modules as defined above may be combined with other similar modules or sub-modules as needed.

It is possible to integrate and upgrade 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 restore it according to the desired use.

Thus, in a particular embodiment, the different functional elements of the heat pump (preferably electric) according to the present invention can be isolated in modules. Thus, a modular system makes it easy to arrange the heat pump according to the physical layout of the site where it is to be installed. Indeed, modularity makes it possible to upgrade the heat pump (preferably electric) according to on-site production, for example by increasing or decreasing the production (power) or storage (energy) capacities of thermal energy. In addition, modularity allows for original assembly variations. For example, modularity can make it possible to insert several storage systems to have a diversity of temperatures, whether at input (recovery of fatal energy with different temperature levels and/or temperature variations) and/or at output. (production of thermal energy at a certain temperature and/or with variable temperature requirements).

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

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

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

Furthermore, the storage of thermal energy according to the present invention can be carried out by the installation in storage systems such as tanks (for example those cited above), of elements allowing, during a charging phase, absorb and store thermal energy, for example by stacking blocks of reduced size on different levels (in comparison with said tanks). These blocks can take the form of refractory bricks, ceramic parts, cement parts, rock parts (for example volcanic or granitic), or even zeolites.

Alternatively, stacking on different levels can take the form of capsules containing classic PCMs (phase change materials) such as certain sands (such as molten salts), in particular KNO ₃ -60% NaNO ₃ or NaCl/MgCl ₂ (57/43) used for more than 20 years in concentrated solar thermal power plants (CSP “concentrated solar power”, that is to say a concentrated solar thermal power plant” in French), paraffin, CaCl ₂ 6H ₂ O.

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 “State-of-the-Art Review” document: “Insulation and Thermal Storage Materials”, 2013 (Eclipse, Cambridge Architectural Research Limited).

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

This storage aspect is advantageous for the proper functioning of the invention.

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

The heat pump (preferably electric) according to the present invention thus comprises at least two cycles, one called charging and the other called discharging.

For example, a charge cycle may include:

- compression of the fluid (such as a gas) between 2-5 bars (and therefore heated to 150-300°C) in the compressor;

- a discharge of heat from the fluid into the material/storage element in a first tank;

- an expansion in the compressed air turbine, which was cooled during its passage through the first tank, but is still under pressure;

- Heating in a second tank of very cold air (between -100 and +10) and at greatly reduced pressure due to expansion by the turbine (and therefore “cold transmission”)

- the “heated” cold air returns to the compressor;

- the cycle resumes until the tanks are full (information given by sensors and/or by stopping the electric turbocharger controlled by the system).

For example, a discharge cycle may include:

- circulators installed on the external loop of each of the tanks (distribution) passing 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 feedback from the customer process;

Therefore, no compression or expansion is used in this cycle. The cold and hot energy distribution systems are independent, the discharge can therefore take place at the same time or alternately. The discharge stops if the customer's request is reached or if the tanks are empty (here again, the information given by sensors causes the circulator control system to stop)

We will describe below, by way of non-limiting examples, embodiments of the present invention, with reference to the appended figures in which:

represents in perspective a heat pump according to the present invention on a chassis;

is a conceptual diagram representing a charging cycle of a heat pump according to the present invention;

is a conceptual diagram representing a discharge cycle of a heat pump according to the present invention:

is a conceptual schematic representation of a heat pump according to the present invention, seen from above;

is a conceptual schematic representation of two heat pumps according to the present invention, seen from above, placed in parallel;

is a conceptual schematic representation of a heat pump according to the present invention, seen from above, in which two turbocharger modules are coupled in parallel;

is a conceptual schematic representation of a heat pump according to the present invention, seen from above, in which two turbocharger modules are coupled in series;

is a conceptual schematic representation of a heat pump according to the present invention, seen from above, in which said heat pump is connected to a fatal energy source;

is a conceptual schematic representation of two heat pumps according to the present invention, seen from above, with a connection system making it possible to implement operation according to the embodiments represented in Figures 4, 5, 6, 7 and 8.

is a conceptual schematic representation of a heat pump according to the present invention, seen from above, in which said heat pump is connected to two additional thermal energy storage systems;

represents in perspective a heat pump according to the present invention in a container; And

represents in perspective a heat pump according to the present invention on a chassis with two working groups (each comprising a turbocharger).

In reference to the , where a heat pump according to the present invention is shown in perspective on a chassis 15, it can be seen a compressor 1 and a turbine 2 connected together by an electrical and/or mechanical link 13, actuated by a motor 3 which can be electric. The compressor and the turbine are both connected by pipes 10 to a first storage system 4 on the one hand, as well as 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.

There is a schematic representation of the heat pump of the , connected to thermal energy restitution systems 6, represented here in a charging cycle. The first storage system 4 and the second storage system 5 are thus each respectively connected to a restitution system 6 of thermal energy making it possible to supply heat or cold to a client system 7. The direction of the flow represented by the arrows 8 imply here that thermal energy in the form of heat is concentrated in the second storage system 5, while thermal energy in cold form is concentrated in the first storage system 4. The storage of cold thermal energy is at low pressure. A temperature gradient can then be created in the first storage system 4 and in the second storage system 5 so that, theoretically, Q1 has a higher temperature (i.e. hotter) than Q2, and Q3 has a temperature lower (ie colder) than Q4. In the , there is no discharge shown.

In reference to the , the assembly diagram identical to that shown in is shown 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 restitution systems 6, it is possible to provide heat and cold to client systems 7. In there , the second storage system 5 is cooled by this discharge and therefore a temperature gradient can be created so that, theoretically, Q6 has a lower temperature (ie colder) than Q5. Similarly, a temperature gradient can be created in the first storage system 4 so that, theoretically, Q8 has a higher temperature (ie hotter) than Q7. In Figures 2 and 3, it is therefore apparent that charge and discharge cycles can operate in parallel.

There is a top view representation of the assembly diagram according to Figures 2 and 3. Compressor 1, turbine 2 and motor 3 and its power unit (which can be electric) and any standard connections are brought together in a so-called 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.

There is a top view representation of an assembly diagram showing the elements of the presenting two heat pump assemblies 14 according to the present invention, coupled in parallel. The advantage in this configuration is the increase in the production of thermal energy in the form of cold and heat, while doubling the storage capacities (and therefore duration of restitution) of thermal energy, without modification and/or or addition (with associated additional costs) of the heat exchanger (heat exchanger).

There is a top view representation of an assembly diagram showing the elements of the presenting two working groups 9 mounted in parallel, connected directly or via a T as shown. The advantage in this configuration is the increase in the production of thermal energy in the form of cold and heat. In comparison with the assembly of the , the assembly of the has the same production capacities but less storage. The assembly according to is therefore well suited for example to a system requiring a charge and discharge cycle working together requiring less storage or requiring a given power achievable over a shorter charging time (for the same quantity of energy stored)

There is a top view representation of an assembly diagram showing the elements of the presenting two working groups 9 mounted in series. The advantage in this configuration is the increase in temperature differences between the thermal energies produced in the form of cold and heat.

There is a top view representation of an assembly diagram showing the elements of the further presenting a source 11 of fatal energy (or of thermal energy of natural origin or of solar origin) allowing a supply of thermal energy represented by the arrow 12. Any means of capturing this fatal energy can be applied (for example heat exchanger linked 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 group 9 of work, and/or between the storage system 4 and the (turbo-)compressor of the group 9 of work.

There represents two heat pump assemblies 14 according to the present invention comprising different coupling means via pipes 10. Thus, each working group 9A, 9B is connected to the four storage systems 4A, 4B, 5A and 5B. Thus, the first working group 9A is connected to the four storage systems 4A, 4B, 5A and 5B. The second working group 9B is connected directly to the storage systems 4B and 5B and is connected to the storage systems 4A and 5A via two Ts at the level of the pipes 10 connecting the first working group 9A to the storage systems 4A and 5A. 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.

There represents a heat pump assembly 14 according to the present invention comprising two thermal energy storage systems 4A and 5A and a working group 9. An assembly 15 comprising two thermal energy storage systems 4B and 5B, is connected to the heat pump assembly 14 according to the present invention. The working group 9 is doubly connected to each storage system 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.

In Figures 4, 5, 6, 7, 8, 9 and 10, the exchangers 6 are placed outside the assemblies 14, 15. It is also possible that the heat exchangers are placed in the assemblies 14, 15.

From a concrete point of view, the sets 14, 15 of Figures 4, 5, 6, 7, 8, 9 and 10 can be containers.

There is a perspective representation of the heat pump of the inserted in a container 14.

There is a perspective representation of a heat pump according to the present invention comprising two directly mounted workgroups (another embodiment includes T's as illustrated in ) in parallel between a first storage system 4 and a second storage system 5.

There allows us to illustrate one of the achievements using the advantage of the modularity provided by this invention.

EXAMPLES

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

1. Electric turbo-compressor and turbine

The turbine and the electric compressor can be combined into a single turbomachine.

For example, a turbocharger comprising an electric compressor and a turbine, newly developed for automotive and/or fuel cell applications can be used. One of the turbochargers below can be used:

- Garrett “Two-Stage Electric Compressor 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 ® turbo-chargers

- Holset® turbochargers

2. Storage system: tanks

Metal tanks, such as standard cylindrical metal tanks (steel or stainless steel) of different sizes, can be thermally insulated and capable of containing compressed air under a pressure of up to 10 bars, between 0.5 and 10m3, see more.

There are several dozen manufacturers around the world. 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 tank - EN10028-3

- Kaeser Compressors®;

- Hummingbirds Compression ® ; see for example the Pauchard vertical galvanized tank 2000L BP RTCABJA000

Claims (10)

Heat pump, preferably electric, comprising:
- at least two thermal energy storage systems, and
- at least one thermal energy restitution system,
in which :
- at least one of the 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 thermal energy storage systems is configured to store thermal energy in the form of cold at a temperature between - 100°C and + 20°C; And
- said at least one thermal energy restitution system is configured to restore heat and/or cold separately or in parallel over time, or
- said at least one thermal energy restitution system is configured for parallel restitution operation which can be alternated with operation in separate restitution over time of heat and/or cold. Heat pump according to claim 1 characterized in that:
- at least one of the thermal energy storage systems is configured to store thermal energy in the form of heat at temperatures less than or equal to - 20°C, preferably less than or equal to - 50°C, and /Or
- in that at least one of the thermal energy storage systems is configured to store thermal energy at temperatures greater than or equal to + 150°C, preferably greater than or equal to + 200°C. Heat pump according to claim 1 or 2 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. Heat pump according to any one of the preceding claims, characterized in that it is configured to comprise an inverted Brayton cycle capable of operating with a gas such as air or argon. Heat pump according to claim 4 characterized in that it comprises a turbocharger, such as a centrifugal electric turbocharger producing a pressure less than or equal to 8 bars, preferably between 1 and 5 bars. Heat pump according to any one of the preceding claims characterized in that the different operating members 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 connect and/or pipes. 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, an oven gas, solar heat, a dryer and/or heat loss of artificial origin. Heat pump according to any one of the preceding claims, characterized in that it is sized to provide energy of between 50 kWh to 5MWh. Process 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 + 20°C, by the use of 'a heat pump according to any one of claims 1 to 8, comprising the following steps:
(a) a charge cycle step by mechanical compression of at least one gas with preferably mechanical expansion of said at least one gas; And
(b) a discharge cycle step without compression and/or expansion in which the thermal energy is discharged via at least one thermal energy restitution system, for example via at least one valve, at least one circulator and/or at least one heat exchanger. Method according to claim 9, characterized in that the discharge cycle step (b) is carried out in parallel with the charge cycle step (a).