Heat pump with two thermal energy storage and release systems

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 DEG C and + 800 DEG C; at least one of the at least two thermal energy storage systems is configured to store thermal energy in cold form at a temperature between-100 DEG C and + 150 DEG C; and-the at least one thermal energy release system is configured to release heat and / or cold individually or in parallel over time, or-the at least one thermal energy release system is configured to operate in a parallel release mode capable of alternating with an operating mode in which heat and / or cold is released individually over time.

Description

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

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

[0003] 1. Maximize energy efficiency to reduce energy demand;

[0004] 2. Decarbonize electricity supply;

[0005] 3. Electrification of the entire economy to drive clean electricity to other sectors;

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

[0007] 5. Apply carbon capture, utilization and storage (“CCUS”) and carbon dioxide removal (“CDR”) to areas that still require fossil fuels and achieve negative emissions.

[0008] There has been a lot of effort, investment, and innovation in these areas.

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

[0010] - Improvements and investments in energy-saving technologies such as heat pumps and cooling units; and

[0011] - Recovery of so-called "waste" energy: reuse of heat pumps, ORC systems (Organic Rankine Cycle) or simple thermal energy storage (i.e. release with an efficiency of less than 1).

[0012] Waste energy is residual energy generated by buildings and industry (ie, lost if not recovered).

[0013] Efforts to decarbonize the grid and meet the need for flexibility, especially in terms of storage, are specifically:

[0014] - Significant investments in renewable energy sources (wind, solar, tidal and hydro). However, the intermittent nature of most of these production methods leads to an increased need for flexibility, i.e. the simultaneous adaptation of electricity demand and production, e.g.:

[0015] - via power storage or activation of power consuming systems in case of excess on the grid; and

[0016] - via systems for reducing electrical loads (machines) in case of shortage or using electricity storage.

[0017] This is the sector that appears to have the most investment. The electricity storage sector has seen a number of new technologies emerge, historically dominated by pumped storage systems (also known as pumped hydro or PHS) and in more recent years by large-scale lithium-ion battery systems.

[0018] When it comes to electrifying high temperature industrial processes, the need and production of high temperature heating and cooling is rarely optimized at the design stage. Since the manufacture of high and very high temperature heat production equipment (boilers, burners, furnaces, steam, etc.) is a specialized technology in itself, and the manufacture of low and very low temperature cold production equipment (cooling units, refrigeration, cryogenic physics, etc.) is another specialized technology, these industries are separated. This follows a historical and technological logic, which explains the separation of the two industries and their specific characteristics.

[0019] However, it has been a long time since end-use industries integrated into their practices and business models the reliability (i.e. constant availability) and low cost of industrial heat (especially gas and / or fuel oil) for their needs above 100°C. With heat energy from natural gas costing around €50-55 / MWh in 2019 in France (ADEME, Brochure ref. 010895, January 2020) and in many other European countries (for large sites) around €50-55 / MWh, it is very difficult for manufacturers to electrify their heat production facilities - since this would require additional heat costs of around 50% or more - or to replace them with production facilities based on renewable energy sources (again: additional costs, technical limitations and intermittency issues).

[0020] Additionally, it is interesting to note that many industries have industrial processes that require:

[0021] - high temperature heating (>100°C to 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 products (especially ready meals, dry foods, powders (milk, coffee, etc.));

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

[0026] - chemicals in a broad sense (preparation, packaging and storage of products), such as petrochemicals (gases and oils, plastics, rubber, etc.), adhesives, etc.; and

[0027] - Certain supermarkets and large restaurants (especially fast food restaurants).

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

[0029] For example, DE 10 2018 221 850 A1 discloses a heat pump system allowing heating and cooling (between -15° C. and 60° C.), wherein a liquid-liquid heat pump is connected on one side to a heat source and on the other side to a radiator, in particular featuring a hot water tank.

[0030] JP2016211830A discloses the use of a heat pump for heating and cooling. More specifically, the temperature range disclosed is between 0°C and about 100°C.

[0031] JP3037649B2 discloses a dehumidification air-conditioning system in which the energy efficiency of the air-conditioning system as a whole is improved to reduce operating costs while minimizing daytime energy consumption and minimizing heat radiation to the outside air during nighttime heat accumulation.

[0032] However, none of these systems are capable of simultaneously or alternately delivering high and / or very high temperature heat and low and / or very low temperature cool.

[0033] In the specific context of the manufacturing and power supply industries, there are other systems for storing heat and cold (possibly simultaneously). Patents EP2220343, EP2574740, US10907510, US8627665, US20140223910 may exemplify this type of technology. However, the devices described in these documents are specific to the power manufacturing and supply industries, since they are specifically designed for power storage and are therefore dimensioned to operate in a cycle where "temperature must be rebalanced" after charging and discharging. Therefore, such devices cannot be used like this in other industries (especially those mentioned above) or even for private use. Summary of the invention

[0034] Therefore, the object of the present invention is to overcome the disadvantages of the prior art by providing an electric heat pump comprising:

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

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

[0037] in:

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

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

[0040] - the at least one thermal energy release system is configured to release heat and / or cold individually or in parallel, or

[0041] - the at least one thermal energy release system is configured to operate in a parallel release mode which can be alternated with operation in a time-separated hot and / or cold release mode;

[0042] The heat pump is configured to include a reverse Brayton cycle operating with gas (eg, without phase change) and includes a single-stage centrifugal electric turbocharger.

[0043] The simultaneous production of these two flows (high temperature heat and cold, usually negative) makes it possible to achieve better energy performance and to provide manufacturers with a thermal energy supply solution that significantly reduces CO2 emissions without increasing production costs, or even reducing production costs depending on the price of locally available energy. In addition, the use of a single-stage centrifugal electric turbocharger improves the compactness and efficiency of the heat pump and reduces its cost. In addition, such a single-stage centrifugal electric turbocharger operates without oil, thereby 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) for the compressor / turbine pair in the gas circulation loop, which is common to the filling and discharge cycles of the heat pump.

[0044] The term "single turbocharger" (also called "single turbine") is used in the context of the present invention to refer to a single machine that is capable of simultaneously increasing the pressure of the gas and reducing the pressure of the gas at another point in the circuit. In addition to high-output axial-type turbochargers, there are at least two types of radial-type turbochargers: piston-type turbochargers (commonly called "compressors") and centrifugal turbochargers. Centrifugal turbochargers have fewer frictional moving parts, relatively high energy efficiency, and higher gas flow rates than reciprocating compressors of similar size. Turbochargers cannot achieve compression ratios as high as reciprocating compressors, which can reach pressures of 100 MPa in multiple stages.

[0045] In the context of the present invention, the term "single-stage turbocharger" refers to a turbocharger that includes a single compression and expansion unit, i.e. a single compression structure (or part), also known as a "compressor"; and a single expansion structure (or part), also known as a "turbine".

[0046] 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 compressor part of the turbocharger and the inlet pressure of said compressor part. The choice of this particular range of values ​​for the compression ratio provides a single operating point for the compressor / turbine pair, particularly suitable for enabling both the charging and discharge cycles of the heat pump, with adapted pressure and temperature levels and flow rates. Within this particular range of values, the heat pump also maintains high energy efficiency and a significant displacement gas flow.

[0047] Preferably, the heat pump according to the invention may be characterized in that:

[0048] - at least one thermal energy storage system is configured to store thermal energy at a temperature between -50°C and +100°C, and / or

[0049] - wherein at least one thermal energy storage system is configured to store thermal energy at a temperature between +150°C and +500°C, preferably between +200°C and +400°C.

[0050] Preferably, the heat pump according to the invention may be characterized in that the at least two thermal energy storage systems are configured to store thermal energy in hot form and in cold form.

[0051] Preferably, the gas used in the reverse Brayton cycle of the heat pump may be air (ie about 20% oxygen in about 80% nitrogen), or a noble gas such as helium or argon, or a mixture of these gases.

[0052] Alternatively, the gas may be an inert gas, such as nitrogen.

[0053] Preferably, the single-stage centrifugal electric turbocharger generates a pressure less than or equal to 8 bar, preferably between 1 and 5 bar (corresponding to said compression ratio between 1 and 5, for a gas initially at atmospheric pressure).

[0054] Preferably, the heat pump according to the invention may be characterized in that the individual operating elements of the heat pump are isolated in modules, which are configured to be connected to each other, for example by physical connections such as (e.g. remotely controllable) valves, pipes to be connected and / or hoses.

[0055] Preferably, the heat pump according to the invention may be characterized in that it is configured to be coupled to at least one natural heat source and / or at least one artificial heat source, such as a gas boiler, a gas furnace, heat of solar origin, a dryer and / or heat losses of artificial origin.

[0056] Preferably, the heat pump according to the invention may be characterized in that it is configured to be connected to at least one artificial heat source, in particular the exhaust gases, losses or outlets of an artificial heat source, such as a gas boiler, a gas furnace, solar heat or waste heat, a dryer and / or the exhaust gases, losses or outlets of heat losses of artificial origin.

[0057] “Waste gases” in the context of the present invention are understood to mean the final controlled stage of the energy cycle from an artificial heat source, for example in the form of hot steam or smoke.

[0058] In the context of the present invention, "loss" refers to the loss of available energy from an artificial heat source. This loss is usually uncontrollable, difficult to control or the result of poor management or configuration of the artificial heat source.

[0059] In the context of the present invention, the term "output" of a heat source is understood to mean the directed and intended output from the heat source, ie where a large part of the heat is expected to be recovered (from steam condensate, eg via a return loop of the process).

[0060] In a particular embodiment, the heat pump according to the invention may 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 invention may be characterized in that it is configured to be connected to a main heating circuit and / or a main cooling circuit.

[0061] Preferably, the heat pump according to the invention may be characterized in that it is dimensioned to supply between 50 kWh and 5 MWh of energy.

[0062] In a specific embodiment, the heat pump includes four thermal energy storage systems, two thermal energy release systems, two three-way valves and two pumping components; a first end of the first thermal energy storage system is connected to a first end of the second thermal energy storage system via a first gas flow branch; a first end of the third thermal energy storage system is connected to a first end of the fourth thermal energy storage system via a second gas flow branch; the first thermal energy release system is arranged to exchange thermal energy with the first gas flow branch, and the second thermal energy release system is arranged to exchange thermal energy with the second gas flow branch; the first three-way valve is connected to the second end of the first thermal energy storage system, to the second end of the second thermal energy storage system and to the second end of the third thermal energy storage system; the second three-way valve is connected to the second end of the second thermal energy storage system, to the second end of the third thermal energy storage system and to the fourth thermal energy storage system a second end of the thermal energy storage system; a first pumping member connects the second end of the second thermal energy storage system to the corresponding channel of the first three-way valve; a second pumping member connects the second end of the third thermal energy storage system to the corresponding channel of the second three-way valve; an inlet of the compressor part of the electric turbocharger is connected to the first end of the first thermal energy storage system at a first connection point on the first gas flow branch; an outlet of the compressor part of the electric turbocharger is connected to the first end of the second thermal energy storage system at a second connection point on the first gas flow branch; an inlet of the turbine part of the electric turbocharger is connected to the first end of the fourth thermal energy storage system at a first connection point on the second gas flow branch; and an outlet of the turbine part of the electric turbocharger is connected to the first end of the third thermal energy storage system at a second connection point on the second gas flow branch.

[0063] This particular embodiment allows a specific sequence of gas flows through each thermal energy storage system (and therefore the temperatures involved), which are not the same depending on whether the heat pump is in a charging or discharge cycle (by means of the use of valves and pumping components). Such a configuration therefore allows the gas to be compressed from a potentially higher temperature, and thus produce a higher temperature, or produce the same temperature but with a lower compression ratio. The heat pump in this particular embodiment can also generate heat and / or cold at different times of use, and can store these two types of thermal energy. Through a separate release loop, the heat pump can also provide heat and / or cooling simultaneously or independently.

[0064] According to a preferred variant of this particular embodiment, the heat pump also includes a two-way valve and three check valves; the two-way valve is connected to the first gas flow branch between the first connection point and the second connection point; the first check valve is connected between the outlet of the compressor part of the electric turbocharger and the second connection point of the first gas flow branch; the second check valve is connected between the outlet of the turbine part of the electric turbocharger and the second connection point of the second gas flow branch; the third check valve is connected to the second gas flow branch; the second check valve is connected between the output of the turbine part of the electric turbocharger and the second connection point of the second gas flow branch; the third check valve is connected to the second gas flow branch between the first connection point and the second connection point.

[0065] In another specific embodiment as an improvement of the aforementioned embodiment, the heat pump also includes three additional heat energy release systems, four additional two-way valves and four additional three-way valves; the first end of the first additional heat energy release system is connected to the first end of the first heat energy release system via the first two-way valve; the second end of the first additional heat energy release system is connected to the second end of the first heat energy release system via the second two-way valve; the first end of the second additional heat energy release system is connected to the first end of the second heat energy release system via the third two-way valve; the second end of the second additional heat energy release system is connected to the second end of the second heat energy release system via the fourth two-way valve; the first end of the third additional heat energy release system is connected to the first connection point on the first gas flow branch; the second end of the third additional heat energy release system is connected to the second connection point on the second gas flow branch; the first additional three-way valve is connected to the compressor part of the electric turbocharger of the electric turbocharger, connected to the first connection point on the first gas flow branch and connected to the first end of the third additional thermal energy release system; the additional second three-way valve is connected to the outlet of the compressor part of the electric turbocharger, connected to the second connection point on the first gas flow branch, and connected to one of the channels of the additional third three-way valve via the first gas pipeline; the additional third three-way valve is also connected to the inlet of the turbine part of the electric turbocharger and connected to the first connection point on the second gas flow branch; the fourth additional three-way valve is connected to the outlet of the turbine part of the electric turbocharger, connected to the second connection point on the second gas flow branch, and connected to the second end of the third additional thermal energy release system via the second gas pipeline; the first and third additional thermal energy release systems are each arranged to exchange thermal energy with the first gas pipeline; the second additional thermal energy release system is arranged to exchange thermal energy with the second gas pipeline.

[0066] In addition to the advantages associated with the previous designs (and outlined above), this particular heat pump design is able to instantaneously generate heat and cold while discharging heat and cold from the thermal energy storage system. This is advantageous because it allows instantaneous power to be added to the discharge cycle of the heat pump, for example to address peak demand with minimal additional equipment cost (three additional thermal energy discharge systems). This avoids the need to oversize the system (e.g., by increasing the size of the thermal energy storage system to store more and / or by increasing the size of the machine, for example to produce and store more at night).

[0067] Another object of the 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 using a heat pump as described above, comprising the following steps:

[0068] (a) a filling cycle step performed by mechanical compression of at least one gas and preferential mechanical expansion of said at least one gas;

[0069] (b) A discharge cycle step without compression and / or expansion, wherein the thermal energy is discharged via at least one thermal energy release system, for example via at least one valve, at least one circulator (typically a pump) and / or at least one heat exchanger (i.e., a heat exchanger).

[0070] In a particular embodiment, step (a) is a charging cycle performed by mechanical compression of at least one vapor, preferably with mechanical expansion of said at least one vapor.

[0071] Preferably, the method according to the invention may be characterized in that step (b) of the discharge cycle is carried out in parallel with step (a) of the filling cycle.

[0072] The exhaust cycle results in a flow of fluid (such as a heat transfer gas) referred to as a “exhaust stream.” Thus, in a particular embodiment, the exhaust stream may be divided into several exhaust streams, referred to as split exhaust streams, each of which may be directed to a different application.

[0073] For example, separate exhaust streams may be directed to a storage system, such as an auxiliary storage system, which may allow for temperature stratification.

[0074] definition

[0075] In the context of the present invention, the term "heat pump" refers to a device for transferring thermal energy from a first medium to a second, higher temperature medium, thus in the opposite direction of the natural spontaneous direction of the thermal energy. In particular, there are so-called high temperature, very high temperature, low temperature and very low temperature heat pumps. Traditionally, there are different 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 (e.g., with a gas refrigeration cycle). This method follows the reverse Brayton thermodynamic cycle, in which the gas is compressed, cooled to ambient temperature, and then expanded in a turbine, and does not involve any phase change, which distinguishes it from a vapor compression heat pump ("conventional" heat pump, called a "thermodynamic" heat pump) or a gas absorption heat pump, which most often follows a vapor compression refrigeration cycle.

[0076] The heat pump works by recovering heat from a low pressure storage tank, called the "cold" tank. The gas is then compressed in the compressor to raise its temperature. In the context of the present invention, this heat is stored. At the same time, the cold (expansion) produced at the turbine outlet is also recovered and stored.

[0077] The reverse-driven Brayton cycle is called the reverse 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 principle of thermodynamics, heat cannot flow spontaneously from a cold system to a hot system without external work acting on the system. Heat can flow from a colder body to a hotter body, but only when driven by external work. This is exactly what refrigerators and heat pumps achieve. These are driven by electric motors that require work from their environment to operate. Therefore, one possible cycle is the reverse Brayton cycle, which is similar to a conventional Brayton cycle, but driven in the opposite direction via a net work input. The cycle is also known as a gas refrigeration cycle, an air cycle, or a Bell-Colman cycle. This type of cycle is widely used in commercial aircraft or trains for air conditioning systems using air from engine compressors. It is also widely used in the LNG (liquefied natural gas) industry, where the largest Brayton reverse cycle is used for LNG subcooling using 86MW power from a gas turbine-driven compressor and nitrogen refrigerant (the source of this common sense: thermal-engineering.org).

[0078] "High temperature" is understood in the context of the present invention to mean a temperature range between +60°C and +100°C, preferably between +70°C and +95°C. Heat pumps of this type can be found in commercial heat pumps, including so-called "consumer" heat pumps. Their efficiency decreases as the temperature difference between the cold source and the hot source increases.

[0079] Unless otherwise stated, the temperatures given in the context of the present invention refer to a temperature of 0° C., ie the solidification temperature of water at sea level at one atmosphere of pressure (ie 101325 Pa, corresponding to an absolute pressure of 1 bar).

[0080] In the context of the present invention, the term "very high temperature" is understood to mean a temperature range above +100° C., for example above or equal to +150° C., above or equal to +200° C., above or equal to +300° C., above or equal to +400° C. Thus, in the context of the present invention, very high temperatures may include temperatures between +150° C. and +500° C., preferably between +150° C. and +400° C., or even between +250° C. and +350° C.

[0081] In the context of the present invention, "low temperature" is understood to mean a temperature range between -20°C and +5°C, preferably between -15°C and -5°C.

[0082] The term "very low temperature" is understood in the context of the present invention to mean a temperature range below -20°C, for example below or equal to -30°C, below or equal to -40°C, below or equal to -50°C, below or equal to +60°C. Thus, in the context of the present invention, very low temperatures may include temperatures between -30°C and -150°C, preferably between -40°C and -100°C, or even between -50°C and -80°C.

[0083] In the context of the present invention, a "thermal energy storage system" refers to any device that stores a certain amount of energy of a thermal nature for later use. The thermal nature can be heat or cold. In fact, heat itself is a form of energy. In the case of storing cold, since the production of cold requires energy, storing cold represents energy storage.

[0084] In the context of the present invention, the term "thermal energy delivery system" refers to a device that delivers thermal energy. In addition, the expression "thermal energy release system configured for..." means that the tanks are interchangeable (one can be used for heating and then for cooling in the other series of filling / discharging cycles).

[0085] In the context of the present invention, the term "split or parallel release of thermal energy" refers to the split or parallel release of thermal energy from at least two different storage systems. Thus, the split delivery enables first the supply of thermal energy from at least one first storage system and subsequently the supply of thermal energy from at least one second storage system. The parallel delivery enables the simultaneous supply of thermal energy from at least one first storage system and thermal energy from at least one second storage system.

[0086] In the context of the present invention, a "module" refers to an element that can be juxtaposed or even combined with one or more others, which may have the same properties as the first or complementary properties.

[0087] In the context of the present invention, the term "natural heat source" refers to thermal energy without artificial intervention, such as, for example, geothermal or water sources (lakes, seas, rivers, etc.).

[0088] In the context of the present invention, "artificial heat source" is understood to mean thermal energy generated by artificial intervention, such as furnaces, boilers, equipment such as air conditioners, compressors, machines, generators, residential, commercial, tertiary, industrial and / or computer processes, energy from solar thermal systems, or even waste heat.

[0089] In the context of the present invention, a "charging cycle" is understood to mean a series of events, which may be recurring, ie cyclic, enabling the generation of thermal energy which is either instantaneously distributed or stored in the form of heat.

[0090] In the context of the present invention, "gas" means any body in the gaseous state. Gases therefore also include vapors produced by evaporation of liquids (at any temperature).

[0091] In the context of the present invention, the term "mechanical expansion" refers to the expansion of an initially compressed gas via a turbine.

[0092] In the context of the present invention, the term "discharge cycle" is understood to mean the opposite function of the filling cycle, ie the release of thermal energy stored in the storage system.

[0093] In the context of the present invention, a "heat exchanger" refers to a device for transferring thermal energy from one fluid to another without mixing them. It is therefore a matter of a "carrier fluid", i.e. a fluid as defined above that allows thermal energy to move from one location to another.

[0094] For example, liquid / liquid, gas / liquid or gas / gas heat exchangers, such as plate heat exchangers or tube or shell and tube heat exchangers, can be used within the scope of the present invention. There are many suppliers of such heat exchangers, such as DETAILED DESCRIPTION

[0095] The object of the invention is to make it possible to adapt, improve and at the same time combine:

[0096] - a proven technology for increasing efficiency and adapting it to the needs of thermal processes (heating and cooling),

[0097] - a special electric turbine (electric turbocharger) whose speed can be controlled (via regulation of flow rate / speed and compression ratio) using, for example, power electronics and software,

[0098] - Thermal storage (separate cooling and heating) to increase the flexibility of the system and enhance the attractiveness of the solution for industrial users.

[0099] Thus, an object of the present invention may include one or more sensors which, in combination with the use of software (and its algorithms), allow a heat pump to be controlled according to the present invention.

[0100] Furthermore, the invention aims to provide several key innovative elements in terms of technology and functionality:

[0101] - Electrically generate high temperature heat (>150°C and up to 500°C to 800°C) and industrial cooling (down to -50°C) at a COP (Coefficient of Performance - Efficiency) of 1.5 or higher,

[0102] - Use a refrigerant with a GWP (global warming potential) of zero (such as air or argon);

[0103] - High density energy storage in the same module in the form of heat (>150°C) and industrial cold (down to -50°C) of this generated or heated / supercooled energy, capable of storing energy for hours or even days.

[0104] The various components of the heat pump according to the invention (electric turbine compressor, motor, storage system, etc.) can be placed in one or more modules or sub-modules that can be combined or integrated with each other; the entire assembly can be housed in a container (for example, a standard "20-foot" or "40-foot" container, i.e. approximately 6 meters or 12 meters) or placed on a base.

[0105] The modules or sub-modules defined above may be combined with other similar modules or sub-modules as desired.

[0106] All these modules and / or submodules can be used to integrate and upgrade waste energy or solar thermal energy flows, for example by adding one or more heat exchangers. It is therefore also an object of the present invention to provide a method for increasing the temperature of recovered waste heat or solar heat, storing it and subsequently releasing it as required.

[0107] Therefore, in a particular embodiment, each functional element of the heat pump according to the present invention can be isolated in a module. Therefore, the modular system allows the heat pump to be easily adapted to the physical layout of the site where it will be installed. In fact, modularization means that the heat pump can be adapted according to the on-site production, for example by increasing or reducing the thermal energy production (power) or storage (energy) capacity. In addition, modularization allows the original assembly to change. For example, modularization allows the insertion of several storage systems to provide a diversity of temperatures, both at the input (recovery of waste energy with different temperature levels and / or temperature variations) and / or at the output (generation of thermal energy at a specific temperature and / or with variable temperature requirements).

[0108] Additionally, it may be advantageous to install rails and / or base systems ("slides") to facilitate modularity.

[0109] In certain embodiments, the module comprising the individual elements is adapted for movement within the container.

[0110] The recombining of modules allows limiting the number of module variants and thus optimizing the costs of the system, while being able to address a greater number of different requirements.

[0111] Furthermore, the thermal energy storage according to the invention can be achieved by installing in a storage system such as a tank (for example those described above) elements which enable the absorption and storage of thermal energy during the filling phase, for example by stacking blocks of reduced size (compared to the tank) at different levels. These blocks can take the form of gravel, refractory bricks, ceramic components, cement components, rock components (for example volcanic rock or granite) or zeolites.

[0112] Alternatively, the stacking at different levels may take the form of capsules containing conventional PCMs (Phase Change Materials), such as certain sands (such as molten salts), notably KNO3-60% NaNO3 or NaCl / MgCl2 (57 / 43), kerosene or CaCl26H2O which have been used for more than 20 years in concentrated solar power plants (CSP).

[0113] All these materials and components have been used extensively for many years in various fields and systems and are also well documented in many journals and publications, to give just one example, in the document “State-of-the-Art Review: “Insulation and Thermal Storage Materials”, 2013 (Eclipse, Cambridge Architectural Research Limited).

[0114] This same thermal energy (minus inherent heat losses in the system) will of course be released upon discharge.

[0115] This storage aspect facilitates the proper operation of the present invention.

[0116] The tanks and pipes will be insulated with conventional insulation materials such as asbestos stone or other standard insulation materials.

[0117] The heat pump according to the invention therefore comprises at least two cycles, one called the charging cycle and the other called the discharge cycle.

[0118] For example, a filling cycle may include:

[0119] - compressing a fluid (ie a gas) in a compressor between 1-5 bar (starting from 1 bar, a compression ratio between 1 and 5) (and thus heating to 150° C. to 300° C., for example, if the gas is air);

[0120] - discharge heat from the fluid in the material / storage element to the first tank;

[0121] - expansion of compressed air in the turbine, which compressed air has been cooled during its passage through the first volume but is still under pressure;

[0122] - Reheating of very cold air (between -100 and +10) in a second tank at a much reduced pressure due to expansion through the turbine (and therefore also "cold transmission")

[0123] - "Heated" cold air returns to the compressor;

[0124] - The cycle restarts until the tank is full (information provided by the sensor and / or closing of the electric turbocharger controlled by the system).

[0125] For example, a discharge cycle may include:

[0126] - Circulators installed on the external loop of each tank (distribution), transferring energy from the tank to the heat exchangers installed on the customer's process loop;

[0127] - At the switch exit, the distribution loop recycles the client process return;

[0128] Thus, no compression or expansion is used in this cycle, only the circulator and / or pump. The cold and hot energy distribution systems are independent, so discharge can occur simultaneously or alternately. Discharge stops if the customer's request is reached or if the tank is empty (again, information provided by sensors is used by the circulator control system to stop the process). BRIEF DESCRIPTION OF THE DRAWINGS

[0129] Embodiments of the invention will now be described by way of non-limiting examples with reference to the accompanying drawings, in which:

[0130] [ Figure 1 ] shows a perspective view of a heat pump according to the invention on a base;

[0131] [ Figure 2 ] is a conceptual diagram showing a charging cycle of a heat pump according to the present invention;

[0132] [ Figure 3 ] is a conceptual diagram showing a discharge cycle of a heat pump according to the present invention;

[0133] [ Figure 4 ] is a schematic conceptual representation of a heat pump according to the invention, seen from above;

[0134] [ Figure 5 ] is a conceptual schematic diagram of a heat pump according to the present invention, seen from above, wherein the heat pump is connected to a waste energy source;

[0135] [ Figure 6 ] is a conceptual schematic diagram of a heat pump according to the present invention, seen from above, wherein the heat pump is connected to two additional thermal energy storage systems;

[0136] [ Figure 7 ] shows a perspective view of a heat pump according to the invention in a container;

[0137] [ Figure 8 ] is a conceptual diagram showing a specific embodiment of a heat pump according to the present invention in a heat pump charging cycle, the heat pump including four thermal energy storage systems;

[0138] [ Fig. 9 ]yes[ Figure 8 ] is a simplified schematic diagram of a thermal energy storage system shown;

[0139] [ Fig.10 ] is in the heat pump discharge cycle [ Figure 8 ] conceptual diagram of the heat pump;

[0140] [ Fig.11 ]yes[ Fig.10 ] a simplified schematic diagram of a thermal energy storage system; and

[0141] [ Fig.12 ] is a conceptual diagram showing another specific embodiment of a heat pump according to the present invention in a heat pump charging cycle, the heat pump including four thermal energy storage systems;

[0142] [ Fig.13 ]yes[ Fig.12 ] a simplified schematic diagram of a thermal energy storage system;

[0143] [ Fig.14 ] is in the heat pump discharge cycle [ Fig.12 ]; and

[0144] [ Fig.15 ]yes[ Fig.14 ]Simplified schematic diagram of the thermal energy storage system in ].

[0145] Reference [ Figure 1 ], in which a heat pump according to the invention is shown in perspective on a base 15, showing a compressor 1 and a turbine 2 connected to each other by an electrical and / or mechanical connection 13 driven by an electric motor 3. Both the compressor and the turbine are connected to a first storage system 4 on the one hand and to a second storage system 5 on the other hand by a pipeline 10, so that a loop is established between the compressor 1, the turbine 2, the first storage system 4 and the second storage system 5. The compressor 1 and the turbine 2 form a single-stage centrifugal electric turbocharger.

[0146] [ Figure 2 ]yes[ Figure 1 ] is a schematic diagram of a heat pump connected to a thermal energy release system 6, shown here in a charging cycle. The first storage system 4 and the second storage system 5 are each connected to a thermal energy release system 6 for supplying heat or cold to a user system 7. The flow direction indicated by the arrows 8 shows that thermal energy in hot form 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 generated in the first storage system 4 and the second storage system 5, so that theoretically Q1 is at a higher temperature (i.e. hotter) than Q2, and Q3 is at a lower temperature (i.e. colder) than Q4. In [ Figure 2 ], no emissions are shown.

[0147] Reference [ Figure 3 ],and[ Figure 2 The same assembly diagram as shown in [ ] is depicted here on the discharge cycle. By discharging the thermal energy stored in the first storage system 4 and the second storage system 5 to the two thermal energy release systems 6, it is possible to supply heat and cold to the user system 7. Figure 3 ], the second storage system 5 is cooled by this discharge and thus a temperature gradient may be created such that theoretically Q6 is at a lower temperature (i.e., cooler) than Q5. Similarly, a temperature gradient may be created in the first storage system 4 such that theoretically Q8 is at a higher temperature (i.e., hotter) than Q7. Figure 2 and Figure 3 In the embodiment of the present invention, it is clear that the filling and draining cycles can be performed in parallel.

[0148] [ Figure 4 ]yes Figure 2 and Figure 3The compressor 1, the turbine 2 and the electric machine 3 together with their (electrical) power units and any standard connections are grouped in a so-called workgroup 9. The workgroup 9, the first storage system 4, the second storage system 5 and the pipeline 10 constitute a first heat pump assembly 14 according to the invention.

[0149] [ Figure 5 ] is based on [ Figure 4 ], in which a source 11 of waste energy (or thermal energy of natural or solar origin) is added to supply thermal energy, indicated by arrow 12. Any device for capturing this waste energy can be applied (e.g. a heat exchanger connected to the pipe loop 10 of the heat pump assembly 14 according to the invention). It is possible to place the thermal energy input between the storage system 5 and the turbine of the work group 9, and / or between the storage system 4 and the (turbine) compressor of the work group 9.

[0150] [ Figure 6 ] shows a heat pump assembly 14 according to the invention, which comprises 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 invention. The working group 9 is doubly connected to each storage system 4A, 4B, 5A and 5B. In addition, the thermal energy storage system 4A is connected to the thermal energy storage system 4B via a pipe 10. The thermal energy storage system 5A is connected to the thermal energy storage system 5B via a pipe 10.

[0151] exist Figure 4 , Figure 5 and Figure 6 In the embodiment, the heat exchanger 6 is located outside the components 14, 15. Alternatively, the heat exchanger can be located in the components 14, 15.

[0152] In fact, Figure 4 , Figure 5 and Figure 6 The components 14, 15 may be containers.

[0153] [ Figure 7 ] is inserted into the container 14 [ Figure 1 ]A perspective view of a heat pump shown in FIG.

[0154] [ Figure 8 ] is a conceptual diagram showing a specific embodiment of the heat pump according to the present invention in a heat pump charging cycle. In this specific embodiment, in addition to the single-stage centrifugal electric turbochargers 1, 2, the heat pump also has 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.

[0155] The first end 16A1 of the first thermal energy storage system 16A is connected to the first end 16B1 of the second thermal energy storage system 16B via a first gas flow branch 28A. The first end 16C1 of the third thermal energy storage system 16C is connected to the first end 16D1 of the fourth thermal energy storage system 16D via a second gas flow branch 28B.

[0156] The first thermal energy release system 18A, preferably a heat exchanger, is arranged to exchange thermal energy with the first gas flow branch 28A. The second thermal energy release system 18B, preferably a heat exchanger, is arranged to exchange thermal energy with the second gas flow branch 28B. The first three-way valve 20A is connected to the second end 16A2 of the first thermal energy storage system 16A, to the second end 16B2 of the second thermal energy storage system 16B, and to the second end 16C2 of the third thermal energy storage system 16C. The second three-way valve 20B is connected to the second end 16B2 of the second thermal energy storage system 16B, to the second end 16C2 of the third thermal energy storage system 16C, and to the second end 16D2 of the fourth thermal energy storage system 16D.

[0157] A first pumping member 22A (usually a pump) connects the second end 16B2 of the second thermal energy storage system 16B to the corresponding channel 20A1 of the first three-way valve 20A. Another channel 20A2 of the first three-way valve 20A is connected to the second end 16A2 of the first thermal energy storage system 16A, and the last channel 20A3 of the first three-way valve 20A is connected to the second end 16C2 of the third thermal energy storage system 16C. A second pumping member 22B (usually 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.

[0158] The inlet 1E of the compressor part 1 of the electric turbocharger is connected to the first end 16A1 of the first thermal energy storage system 16A at a first connection point 30A on the first gas flow branch 28A. The output 1S of the compressor part 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 flow branch 28A. The inlet 2E of the turbine part 2 of the electric turbocharger is connected to the first end 16D1 of the fourth thermal energy storage system 16D at a first connection point 32A on the second gas flow branch 28B. The outlet 2S of the turbine part 2 of the electric turbocharger is connected to the first end 16C1 of the third thermal energy storage system 16C at a second connection point 32B on the second gas flow branch 28B.

[0159] The two-way valve 24 is connected to the first gas flow branch 28A between the first connection point 30A and the second connection point 30B. The first check valve 26A is connected between the outlet 1S of the compressor part 1 of the electric turbocharger and the second connection point 30B of the first gas flow branch 28A. The second check valve 26B is connected between the outlet 2S of the turbine part 2 of the electric turbocharger and the second connection point 32B of the second gas flow branch 28B. The third check valve 26C is connected to the second gas flow branch 28B between the first connection point 32A and the second connection point 32B.

[0160] When the pump is in the filling cycle, Figure 8 and Fig. 9 The operation of the heat pump in this particular embodiment is shown in FIG. The flow direction represented by arrow 34 here indicates that the thermal energy in hot form is concentrated in the second storage system 16B (after having been extracted from the first storage system 16A and then compressed in the compressor 1), while the thermal energy in cold form is concentrated in the third storage system 16C (after having been extracted from the fourth storage system 16D and then expanded in the turbine 2). The cold thermal energy storage is at low pressure (typically about 1 bar absolute pressure when the gas used is air), while the hot thermal energy storage is at high pressure (typically between 1 bar absolute pressure and 5 bar absolute pressure when the gas used is air). The cold thermal energy extraction is high pressure, while the hot thermal energy extraction is low pressure. The temperature gradient generated in the second and third storage systems 16B, 16C causes thermal energy to be transferred from the second storage system 16B to the fourth storage system 16D on the one hand, and from the third storage system 16C to the first storage system 16A on the other hand.

[0161] When the pump is in the discharge cycle, Fig.10 and Fig.11 The operation of the heat pump in this particular embodiment is shown in . By discharging the thermal energy stored in the second storage system 16B and the third storage system 16C to the two thermal energy release systems 18A, 18B, it is possible to supply heat and cold to the client system. Therefore, a first loop 38 is established between the first storage system 16A and the second storage system 16B on the one hand, and a second loop 40 is established between the third storage system 16C and the fourth storage system 16D on the other hand. In the first loop 38 (in which the first pumping member 22A is activated and the heat pump supplies heat to the first thermal energy release system 18A), the second storage system 16B is cooled by the discharge, thereby generating a temperature gradient, which causes the gas to circulate in the flow direction indicated by the arrow 41. In the second loop 40 (in which the second pumping member 22B is activated and the heat pump supplies cold to the second thermal energy release system 18B), the third storage system 16C is heated by the discharge and a temperature gradient is generated, causing the gas to circulate in the flow direction indicated by the arrow 42.

[0162] Figures 8 to 11 This particular embodiment of the heat pump shown in allows the gas flow sequence in the first and fourth storage systems 16A, 16D to be "interchanged" during the discharge operation compared to the filling operation without physically moving the storage systems 16A-16D. The advantage of this operation is that it avoids the introduction of excessive thermal differences (thermal shocks) that would disrupt the establishment of the thermocline in the 16A-16D thermal energy storage system and thus be detrimental to the performance of the thermal storage and to the application as a whole.

[0163] for Figures 8 to 11 For a specific embodiment of the heat pump shown in , representative, non-limiting temperature values ​​are given below as an example:

[0164] The first end 16A1 of the first storage system 16A has, for example, a temperature substantially equal to +60°C, and the second end 16A2 of the first storage system 16A has a temperature substantially equal to +80°C.

[0165] Temperature;

[0166] - the first end 16B1 of the second storage system 16B has, for example, a temperature substantially equal to +210° C., and the second end 16B2 of the second storage system 16B has a temperature substantially equal to +80° C.

[0167] Temperature;

[0168] The first end 16C1 of the third storage system 16C has, for example, a temperature substantially equal to -30°C, and the second end 16C2 of the third storage system 16C has a temperature substantially equal to +80°C.

[0169] Temperature;

[0170] The first end 16D1 of the fourth storage system 16D has, for example, a temperature substantially equal to +20°C, and the second end 16D2 of the fourth storage system 16D has a temperature substantially equal to +80°C.

[0171] Temperature;

[0172] the fluid circulating in the first thermal energy release system 18A enters this system 18A at a temperature, for example, substantially equal to +20° C. and leaves this system 18A at a temperature, for example, substantially equal to +200° C.;

[0173] The fluid circulating in the second thermal energy release system 18B enters this system 18B at a temperature, for example substantially equal to +25°C, and leaves this system 18B at a temperature, for example substantially equal to -25°C.

[0174] [ Fig.12] is a conceptual diagram showing a specific embodiment of a heat pump according to the present invention in a heat pump charging cycle. Figures 8 to 11 The aforementioned embodiment described, the heat pump according to this particular embodiment comprises a single-stage centrifugal electric turbocharger 1, 2, four thermal energy storage systems 16A-16D, two thermal energy release systems 18A, 18B, two three-way valves 20A, 20B, two pumping members 22A, 22B, a two-way valve 24 and three check valves 26A-26C (all of which are connected in the same manner as in the aforementioned embodiment). In addition to the turbochargers 1, 2 and the two thermal energy release systems 18A, 18B, for the sake of clarity, in [ Fig.12 ] The other aforementioned components are not shown. The heat pump also includes three additional heat energy release 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. Therefore, Figures 12 to 15 The specific embodiment shown in Figures 8 to 11 An improvement of the aforementioned embodiment described. Figures 12 to 15 In, use Figures 8 to 11 The same reference numerals as in the reference numerals in the drawings describe elements that are Figures 8 to 11 The elements in are the same and therefore will not be described in further detail below.

[0175] like[ Fig.12 ] As shown in FIG. 1 , a first end 44A1 of a first additional thermal energy release system 44A is connected to a first end 18A1 of a first thermal energy release system 18A via first and second additional two-way valves 46A, 46B. A second end 44A2 of an additional first thermal energy release system 44A is connected to a second end 18A2 of a first thermal energy release system 18A. A first end 44B1 of an additional second thermal energy release system 44B is connected to a first end 18B1 of a second thermal energy release system 18B. A second end 44B2 of a second additional thermal energy release system 44B is connected to a second end 18B2 of a second thermal energy release system 18B via third and fourth additional two-way valves 46C, 46D. A first end 44C1 of a third additional thermal energy release system 44C is connected to a first connection point 30A on a first gas flow branch 28A; and a second end 44C2 of a third additional thermal energy release system 44C is connected to a second connection point 32B on a second gas flow branch 28B.

[0176] The first additional three-way valve 48A is connected to the inlet 1E of the compressor part 1 of the electric turbocharger, to the first connection point 30A on the first gas flow branch 28A and to the first end 44C1 of the third additional thermal energy release system 44C. The second additional three-way valve 48B is connected to the outlet 1S of the compressor part 1 of the electric turbocharger, to the second connection point 30B on the first gas flow branch 28A and to one of the channels 48C1 of the third additional three-way valve 48C via a first gas line 50A. The third additional three-way valve 48C is also connected to the inlet 2E of the turbine part 2 of the electric turbocharger and to the first connection point 32A on the second gas flow branch 28B. The fourth additional 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 flow branch 28B and to the second end 44C2 of the third additional thermal energy release system 44C via a second gas line 50B.

[0177] The first and third additional thermal energy release systems 44A, 44C are each arranged to exchange thermal energy with the first gas line 50 A. The additional second thermal energy release system 44B is arranged to exchange thermal energy with the second gas line 50B.

[0178] A first additional pumping member 49A (typically a pump) connects the second end 44A2 of the first additional release system 44A to the "hot" output 56 of the assembly formed by the first release system 18A and the first additional release system 44A. A second additional pumping member 49B (typically a pump) connects the second end 18A2 of the first release system 18A to the "hot" output 56 of the assembly formed by the first release system 18A and the first additional release system 44A. A third additional pumping member 49C (typically a pump) connects the first end 44B1 of the second additional release system 44B to the "cold" outlet 58 of the assembly formed by the second release system 18B and the second additional release system 44B. A fourth additional pumping member 49D (typically a pump) connects the first end 18B1 of the second release system 18B to the "cold" outlet 58 of the assembly formed by the second release system 18B and the second additional release system 44B.

[0179] When the pump is in the filling cycle, Fig.12 and Fig.13 The operation of the heat pump in this particular embodiment is shown in FIG. When in the charging cycle, the heat pump operates at the same speed as the reference Figures 8 to 11 The previously described embodiments operate in a similar manner. 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).

[0180] When the pump is in the discharge cycle, Fig.14 and Fig.15 The operation of the heat pump in this particular embodiment is shown in FIG. During discharge of the heat pump, it is possible to supply heat and cold to the client system while continuing the parallel charging cycle of the second and third storage systems 16B, 16C. In fact, as [ Fig.15 ], on the one hand, two hot release loops 52A, 52B are established (corresponding to the hot release to the first release system 18A and the first additional release system 44A), and on the other hand, two cold release loops 54A, 54B are established (corresponding to the cold release to the second release system 18B and the second additional release system 44B). For each release circuit (hot on the one hand and cold on the other hand), each loop 52A, respectively 54A can be operated independently of the other loop 52B, respectively 54B, in parallel with the latter or separately.

[0181] In the first loop 52A of the hot release circuit (where the first pumping member 22A and the second additional pumping member 49B are activated - the loop 52A is established between the first storage system 16A and the second storage system 16B), the gas flows in the flow direction indicated by the arrow 60. In the second loop 52B of the hot release circuit (where the first additional pumping member 49A is activated - the loop 52B is established at the compressor 1 part of the electric turbocharger, where the transient energy is generated by the turbochargers 1, 2 and flows in particular through the first gas line 50A), the gas flows in the flow direction indicated by the arrow 62. In the first loop 54A of the cold release circuit (where the second pumping member 22B and the fourth additional pumping member 49D are activated - the loop 54A is established between the third storage system 16C and the fourth storage system 16D), the gas flows in the flow direction indicated by the arrow 64. In the second loop 54B of the cold release circuit (in which the third additional pumping member 49C is activated—this loop 54B is established at the turbine 2 of the electric turbocharger, in which the transient energy is generated by the turbochargers 1 , 2 and flows in particular in the second gas line 50B), the gas flows in the flow direction indicated by the arrow 66 .

[0182] In addition to the advantages associated with the previous embodiments (and described above), Figures 12 to 15 This particular embodiment of the heat pump shown is capable of instantaneously generating heat and cold while simultaneously discharging heat and cold from the thermal energy storage system. This is advantageous because it allows instantaneous power (from the electric turbochargers 1, 2) to be added to previously stored energy, which is then released in parallel with the instantaneously generated energy, e.g. to address peak demand with minimal additional equipment cost (three additional thermal energy release systems 44A-44C). Figures 12 to 15 In the particular embodiment shown, discharge of the heat pump may be performed as follows:

[0183] Either by supplying only the instantaneous energy generated by the single-stage centrifugal electric turbocharger 1, 2;

[0184] Either by simultaneously supplying the stored energy of the thermal energy storage system and the energy of the single-stage centrifugal electric turbocharger (ie by discharging the energy produced during the previous charge which is added to the energy of the instantaneous power produced by the turbocharger).

[0185] This avoids, for example, the need to oversize the system (eg by increasing the size of the thermal energy storage system to store more and / or by increasing the size of the machinery, for example to produce more at night).

[0186] Example

[0187] The drawings may be reproduced using the components described below.

[0188] 1. Electric Turbine - Compressor and Turbine

[0189] The turbine and electric compressor are combined in a single turbine, which is a single-stage centrifugal electric turbocharger.

[0190] For example, one of the following turbochargers may be used:

[0191] -Garrett "Electric turbo compressor (with recovery turbine) for fuel cell electric vehicles"

[0192] -Fisher EMTCT-120k Air / EMTCT-90k Air: Electric micro-turbine compressor or similar with turbine for energy recovery

[0193] -BorgWarner eTurbo

[0194] -IHI fuel cell turbocharger

[0195] - Liebherr - Electric compressor with turbine (ETC) 25kW and 55kW

[0196] - Electric turbocharger

[0197] - Electric turbocharger (part of Cummins)

[0198] 2. Storage system: tank

[0199] Metal tanks, such as standard cylindrical metal containers (steel or stainless steel) of various sizes, can be thermally insulated and capable of maintaining pressures up to 10 bar at 0.5 m 3and 10m 3 or even higher compressed air.

[0200] There are many manufacturers around the world. For example, the following companies sell cans that may be suitable:

[0201] - "Thermal insulation tank"

[0202] -EMI Compressed Air See for example P 265GH-EN10028-2; P 275NH-EN10028-3; P 265GH-EN10028-2; or P 275NH-EN10028-3 cans

[0203] -Kaeser compressor

[0204] -Colibris compression See for example Vertical Galvanized Pauchard Tank 2000L BPRTCABJA000.

Claims

1. An electric heat pump, comprising: - at least two thermal energy storage systems (4, 5; 16A-16D), and - at least one thermal energy release system (6; 18A, 18B), in: - at least one of said thermal energy storage systems (5; 16B) is configured to store thermal energy in the form of heat at a temperature between +100°C and +800°C, - at least one of said thermal energy storage systems (4; 16C) is configured to store thermal energy in cold form at a temperature between -100°C and +150°C; and - the at least one thermal energy release system (6; 18A, 18B) is configured to release heat and / or cold over time, either individually or in parallel, or - the at least one thermal energy release system (6; 18A, 18B) is configured to operate in a parallel release mode that can alternate with an operating mode in which heat and / or cold are released individually over time; the heat pump is configured to include a reverse Brayton cycle operating with gas; Characterized in that the heat pump comprises a single-stage centrifugal electric turbocharger (1, 2).

2. The heat pump according to claim 1, characterized in that The single-stage centrifugal electric turbocharger (1, 2) has a compression ratio 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 the compressor part (1).

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

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

5. A heat pump according to any one of the preceding claims, characterised in that The various operating components of the heat pump are isolated in modules, which are configured to be connected to each other through, for example, physical connections such as valves, connecting pipes and / or hoses.

6. A heat pump according to any one of the preceding claims, characterised in that The heat pump is configured to be coupled to at least one natural heat source and / or at least one artificial heat source, such as a gas boiler, a gas furnace, heat from a solar source or waste heat (11), a dryer and / or heat losses from artificial sources.

7. A heat pump according to any one of the preceding claims, characterised in that The gas used in the reverse Brayton cycle of the heat pump is air, or a noble gas such as helium or argon, or a mixture of these gases.

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

9. Heat pump according to the preceding claim, characterized in that The heat pump also includes a two-way valve (24) and three check valves (26A, 26B, 26C); the two-way valve (24) is connected to the first gas flow branch (28A) between the first connection point (30A) and the second connection point (30B); the first check valve (26A) is connected between the outlet (1S) of the compressor part (1) of the electric turbocharger and the second connection point (30B) of the first gas flow branch (28A); the second check valve (26B) is connected between the outlet (2S) of the turbine part (2) of the electric turbocharger and the second connection point (32B) of the second gas flow branch (28B); the third check valve (26C) is connected to the second gas flow branch (28B) between the first connection point (32A) and the second connection point (32B).

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

11. Method for supplying thermal energy in the form of heat at a temperature between +100°C and +800°C and / or cold at a temperature between -100°C and +150°C using a heat pump according to any one of claims 1 to 10, comprising the following steps: (a) a filling cycle step by mechanical compression of at least one gas and preferably also mechanical expansion of said at least one gas; and (b) a discharge cycle step without compression and / or expansion, wherein the thermal energy is discharged via at least one thermal energy release system, such as via at least one valve, at least one circulator and / or at least one heat exchanger.

12. The method according to claim 11, characterized in that The discharge cycle step (b) is performed in parallel with the filling cycle step (a).

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