EP4490449B1 - Wärmepumpe mit zwei wärmeenergiespeicher- und -abgabesystemen - Google Patents

Wärmepumpe mit zwei wärmeenergiespeicher- und -abgabesystemen

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Publication number
EP4490449B1
EP4490449B1 EP23710891.5A EP23710891A EP4490449B1 EP 4490449 B1 EP4490449 B1 EP 4490449B1 EP 23710891 A EP23710891 A EP 23710891A EP 4490449 B1 EP4490449 B1 EP 4490449B1
Authority
EP
European Patent Office
Prior art keywords
thermal
heat pump
energy
energy storage
heat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP23710891.5A
Other languages
English (en)
French (fr)
Other versions
EP4490449C0 (de
EP4490449A1 (de
Inventor
Christophe Poncelet
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Propellane SAS
Original Assignee
Propellane SAS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from FR2202181A external-priority patent/FR3133430B1/fr
Application filed by Propellane SAS filed Critical Propellane SAS
Publication of EP4490449A1 publication Critical patent/EP4490449A1/de
Application granted granted Critical
Publication of EP4490449C0 publication Critical patent/EP4490449C0/de
Publication of EP4490449B1 publication Critical patent/EP4490449B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/0034—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/12—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having two or more accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D11/00—Central heating systems using heat accumulated in storage masses
    • F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
    • F24D11/0214—Central heating systems using heat accumulated in storage masses using heat pumps water heating system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
    • F25B25/005—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00 using primary and secondary systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B30/00—Heat pumps
    • F25B30/02—Heat pumps of the compression type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2250/00—Special cycles or special engines
    • F02G2250/03—Brayton cycles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/24—Storage receiver heat

Definitions

  • the invention relates to an electric heat pump comprising at least two thermal energy storage systems enabling the release of thermal energy at temperatures ranging from -100°C to +800°C, in particular the release of thermal energy in the form of heat at temperatures between +100°C and +800°C and/or cold at temperatures between -100°C and +150°C, as well as a method for supplying such thermal energy using such a heat pump.
  • cold refers to a "relative" cold, compared to the temperatures involved in the production of thermal energy in the form of heat.
  • Fatal energy corresponds to residual energy (i.e., lost if it is not recovered) produced by buildings and industries.
  • DE102018221850A1 discloses a heat pump system enabling heating and cooling (between -15°C and 60°C), with a liquid-liquid heat pump connected on one side to a heat source and on the other side to a heat sink including in particular a hot water tank.
  • JP2016211830A discloses the use of a heat pump for heating and cooling. More specifically, the disclosed temperature ranges are between 0°C and approximately 100°C.
  • JP3037649B2 discloses a dehumidifying air conditioning system, in which the energy efficiency of the air conditioning system as a whole is increased to reduce operating costs, while minimizing energy consumption during the day and minimizing thermal radiation to the outside air during nighttime heat buildup.
  • the simultaneous production of two flows allows for improved energy efficiency and provides industrial users with a thermal energy supply solution that drastically reduces CO2 emissions without increasing production costs, or even lowers them depending on the prices of locally available energy sources.
  • the use of a single-stage, centrifugal electric turbocompressor increases the compactness and efficiency of the heat pump, as well as reducing its cost.
  • such a single-stage, centrifugal electric turbocompressor operates without oil, thus preventing contamination or acidification within the system.
  • the use of a single turbocompressor means that there is only one operating point (usually defined by the flow rate/compression ratio) for the compressor/turbine combination in the gas circulation circuit, which is common for a single charge and discharge cycle of the heat pump.
  • a “single turbocharger,” also called a “single turbomachine,” is understood to mean a single machine that simultaneously increases gas pressure and reduces gas pressure at another point in the circuit.
  • radial turbochargers piston turbochargers (more commonly called “compressors”) and centrifugal turbochargers.
  • piston turbochargers more commonly called “compressors”
  • centrifugal turbochargers have few moving parts subject to friction, relatively high energy efficiency, and move a higher gas flow rate than similarly sized reciprocating compressors.
  • Turbochargers cannot achieve the same compression ratio as reciprocating compressors, which are capable of reaching pressures of 100 MPa in multi-stage configurations.
  • single-stage turbocharger means a turbocharger comprising a single compression and expansion train, in other words, a single compression structure (or part), also called a “compressor”; and a single expansion structure (or part), also called a “turbine”.
  • the single-stage centrifugal electric turbocharger has a compression ratio between 1 and 5, the compression ratio being defined as the ratio between the outlet pressure of the turbocharger's compressor section and the inlet pressure of said compressor section.
  • the compression ratio being defined as the ratio between the outlet pressure of the turbocharger's compressor section and the inlet pressure of said compressor section.
  • the heat pump according to the present invention can be characterized in that said at least two thermal energy storage systems are configured to store thermal energy in the form of heat and in the form of cold.
  • the gas used in the reverse Brayton cycle of the heat pump can be air (i.e., about 20% oxygen in about 80% nitrogen), or a noble gas such as helium or argon, or a mixture of these. gas.
  • the gas can be an inert gas such as nitrogen.
  • the single-stage centrifugal electric turbocharger produces a pressure less than or equal to 8 bar, preferably between 1 and 5 bar (corresponding to said compression ratio between 1 and 5, for a gas initially at atmospheric pressure).
  • the heat pump according to the present invention can be characterized in that the different operating components of said heat pump are isolated in modules, said modules being configured to be connected to each other, for example, by physical connections such as valves (for example, remotely controllable), pipes to be connected and/or hoses.
  • modules being configured to be connected to each other, for example, by physical connections such as valves (for example, remotely controllable), pipes to be connected and/or hoses.
  • the heat pump according to the present invention can be characterized in that it is configured to be coupled to at least one natural heat source and/or at least one artificial heat source such as a gas boiler, a gas oven, solar heat, a dryer and/or artificial heat loss.
  • at least one natural heat source such as a gas boiler, a gas oven, solar heat, a dryer and/or artificial heat loss.
  • at least one artificial heat source such as a gas boiler, a gas oven, solar heat, a dryer and/or artificial heat loss.
  • the heat pump according to the present invention can be characterized in that it is configured to be coupled to at least one artificial heat source, in particular at the exhaust, loss or outlet of an artificial heat source such as at the exhaust, loss or outlet of a gas boiler, a gas furnace, solar heat or waste heat, a dryer and/or artificial heat loss.
  • at least one artificial heat source in particular at the exhaust, loss or outlet of an artificial heat source such as at the exhaust, loss or outlet of a gas boiler, a gas furnace, solar heat or waste heat, a dryer and/or artificial heat loss.
  • scape means a final controlled phase of energy circulation, for example in the form of hot steam or smoke, from an artificial heat source.
  • loss refers to a useful deprivation of energy from the artificial heat source. This deprivation is most often uncontrolled, difficult to control, or results from poor management or configuration of the artificial heat source.
  • output of a heat source it is understood in the context of the present invention to mean a channeled and expected output of a heat source, that is to say, where it is expected to recover the majority of said heat (for example, steam condensates, via the return circuit of a process).
  • the heat pump according to the present invention can be characterized in that it is configured to be connected to a heating circuit and/or a cooling circuit.
  • the heat pump according to the present invention can be characterized in that it is configured to be connected to a primary heating circuit and/or a primary cooling circuit.
  • the heat pump according to the present invention can be characterized in that it is sized to supply energy between 50 kWh and 5 MWh.
  • the heat pump comprises four thermal energy storage systems, two thermal energy release systems, two three-way valves and two pumping elements; a first end of a first thermal energy storage system being connected to a first end of a second thermal energy storage system via a first gas circulation branch; a first end of a third thermal energy storage system being connected to a first end of a fourth thermal energy storage system via a second gas circulation branch; a first thermal energy release system being arranged to exchange thermal energy with the first gas circulation branch, a second thermal energy release system being arranged to exchange thermal energy with the second gas circulation branch; a first three-way valve being connected to a second end of the first thermal energy storage system, to a second end of the second thermal energy storage system and to a second end of the third thermal energy storage system; a second three-way valve being connected to the second end of the second thermal energy storage system, to the second end of the third thermal energy storage system and to a second end of the fourth thermal energy storage system; a first pumping element connecting the second end of the second thermal energy
  • This particular embodiment allows for a different order in which the gas passes through the various thermal energy storage systems (and therefore the temperatures involved) depending on whether the heat pump is in a charging or discharging cycle (thanks to the use of valves and pumping devices).
  • This configuration makes it possible to compress the gas from potentially higher temperatures, thus either producing higher temperatures or producing the same temperature but with a lower compression ratio.
  • the heat pump in this particular embodiment can produce heat and/or cooling at different times of use, and can store both types of thermal energy. Thanks to the presence of separate distribution circuits, the heat pump can also provide heat and/or cooling simultaneously or independently.
  • the heat pump further comprises a two-way valve and three check valves; the two-way valve being connected on the first gas circulation branch between the first connection point and the second connection point; a first check valve being connected between the outlet of the compressor part of the electric turbocharger and the second connection point of the first gas circulation branch; a second check valve being connected between the outlet of the turbine part of the electric turbocharger and the second connection point of the second gas circulation branch; a third check valve being connected on the second gas circulation branch between the first connection point and the second connection point.
  • the heat pump further comprises three additional heat recovery systems, four additional two-way valves, and four additional three-way valves; a first end of a first additional heat recovery system being connected to a first end of the first heat recovery system via a first two-way valve; a second end of the first additional heat recovery system being connected to a second end of the first heat recovery system via a second two-way valve; a first end of a second additional heat recovery system being connected to a first end of the second heat recovery system via a third two-way valve; a second end of the second additional heat recovery system being connected to a second end of the second heat recovery system via a fourth two-way valve; a first end of a third additional thermal energy recovery system being connected to the first connection point on the first gas circulation branch; a second end of the third additional thermal energy recovery system being connected to the second connection point on the second gas circulation branch; a first additional three-way valve being connected to the inlet of the compressor section of the electric turbocharger,
  • this particular embodiment of the heat pump is capable of producing instantaneous heating and cooling while simultaneously discharging heat and cold from the thermal energy storage systems. This is advantageous because it allows for the addition of instantaneous power to the heat pump's discharge cycle, for example, to meet peak demand with minimal additional equipment costs (three additional thermal energy recovery systems). This avoids the need to oversize the system (particularly by increasing the size of the thermal energy storage systems to store more energy and/or by increasing the size of the machine, for example, to produce and store more energy at night).
  • step (a) is a mechanical compression charging cycle of at least one vapor with preferably a mechanical expansion of said at least one vapor.
  • the process according to the present invention can be characterized in that the discharge cycle step (b) is carried out in parallel with the charge cycle step (a).
  • discharge flow a fluid flow (such as a heat transfer gas) called the "discharge flow".
  • discharge flow a fluid flow (such as a heat transfer gas)
  • the discharge flow can be divided into several discharge flows, called split discharge flows, each of which can be directed to different applications.
  • a split discharge stream can be directed to a storage system, such as a secondary storage system, which can allow for temperature scaling.
  • a "heat pump” is understood to mean a device that transfers thermal energy from one medium to a second medium at a higher temperature, thus reversing the natural, spontaneous flow of thermal energy.
  • HT high-temperature
  • VHT very high-temperature
  • LT low-temperature
  • VLT very low-temperature
  • heat pumps There are several classic types of heat pumps: vapor compression heat pumps, Peltier effect heat pumps, thermoacoustic heat pumps, thermomagnetic heat pumps, gas absorption heat pumps, and Stirling heat pumps.
  • a "heat pump” in the context of this invention is an electric heat pump of the air cycle type (for example, a gas refrigeration cycle).
  • This heat pump works by extracting heat from a low-pressure storage tank, also known as a "cold" tank. The gas is then compressed in a compressor. in order to increase its temperature. In the context of the present invention, this heat is stored. In parallel, the cold generated at the turbine outlet (expansion) is also recovered and stored.
  • a Brayton cycle driven in reverse is called a reversed Brayton cycle. Its purpose is to move heat from a colder body to a warmer body, rather than doing work. According to the second law of thermodynamics, heat cannot spontaneously flow from a cold system to a hot system without external work being done on the system. Heat can flow from a colder body to a warmer body, but only when forced by external work. This is precisely what refrigerators and heat pumps accomplish. These are driven by electric motors that require work from their surroundings to operate.
  • a reversed Brayton cycle which is similar to the ordinary Brayton cycle but is driven in the opposite direction, via a net work input. This cycle is also known as the gas refrigeration cycle, air cycle, or Bell-Coleman cycle.
  • This type of cycle is widely used in airliners and trains for air conditioning systems that utilize air from the engine compressors. It is also widely used in the LNG (Liquefied Natural Gas) industry, where the largest reversed Brayton cycle is for subcooling LNG using 86 MW of power from a gas turbine-driven compressor and nitrogen refrigerant (source of this common knowledge: "thermal-engineering.org”).
  • LNG Liquefied Natural Gas
  • high temperature refers to a temperature range between +60 and +100°C, preferably between +70 and +95°C.
  • This type of heat pump can be found in commercial heat pumps, including those marketed to consumers. Their efficiency decreases as the temperature difference between the cold source and the source to be heated increases.
  • temperatures given in the context of the present invention are in reference to the temperature of 0°C, i.e. the freezing point of water at one atmosphere at sea level (i.e. 101325 Pa corresponding to an absolute pressure of 1 bar).
  • very high temperature means a range of temperatures above +100°C, for example, greater than or equal to +150°C, greater than or equal to +200°C, greater than or equal to +300°C, greater than or equal to +400°C.
  • a very high temperature in the context of this invention may include temperatures between +150 and +500°C, preferably between +150 and +400°C, or between +250 and +350°C.
  • low temperature it is understood in the context of the present invention that “low temperature” is understood to mean a temperature range between -20 and +5°C, preferably between -15 and -5°C.
  • very low temperature means a range of temperatures below -20°C, for example, less than or equal to -30°C, less than or equal to -40°C, less than or equal to -50°C, or less than or equal to +60°C.
  • a very low temperature in the context of this invention may include temperatures between -30 and -150°C, preferably between -40 and -100°C, or between -50 and -80°C.
  • thermal energy storage systems means any means of preserving a quantity of thermal energy for later use.
  • Thermal energy can be either hot or cold. Indeed, heat itself is a form of energy. In the case of stored cold, since producing cold requires energy, storing cold constitutes energy storage.
  • thermo energy recovery system means a means of delivering thermal energy.
  • thermal energy recovery systems configured for implies that the tanks are interchangeable (one tank can be used for heating and then for cooling during other series of charge and discharge cycles).
  • “separate or parallel delivery” refers to the separate or parallel delivery of thermal energy from at least two different storage systems. Separate delivery allows for the initial supply of thermal energy from at least one storage system followed by thermal energy from at least one second storage system. Parallel delivery allows for the simultaneous supply of thermal energy from at least one storage system and thermal energy from at least one second storage system.
  • module means an element that can be juxtaposed or even combined with one or more others, which may be of the same nature or complementary to the first.
  • natural heat source means thermal energy that does not result from any human intervention, such as a geothermal or water source (lake, sea, river, etc.).
  • artificial heat source means thermal energy from human intervention, such as an oven, boiler, equipment such as air conditioning, compressors, machines, generators, a residential, commercial, tertiary, industrial and/or computer process, energy from a solar thermal system or even waste heat.
  • load cycle means a series of events that may be recurrent, i.e., a cycle, enabling the production of thermal energy that is either distributed instantaneously or stored as thermal energy.
  • gas means any substance in a gaseous state.
  • a gas also includes a vapor, which results from the vaporization of a liquid (at any temperature).
  • mechanical expansion refers to the expansion of gas initially compressed via a turbine.
  • discharge cycle means the inverse function of a charge cycle, i.e., enabling the release of thermal energy stored in storage systems.
  • a heat exchanger is understood to mean a device that transfers thermal energy from one fluid to another without mixing them. This refers to a “transfer fluid,” that is, a fluid as defined above, that allows the thermal energy to be moved from one location to another.
  • liquid/liquid, gas/liquid, or gas/gas heat exchangers such as plate heat exchangers or shell and tube heat exchangers that can be used in the context of the present invention.
  • the object of the present invention may include one or more sensors, which combined with the use of software (and its algorithms) allow the heat pump to be controlled according to the present invention.
  • modules or sub-modules as defined above can be combined with other similar modules or sub-modules as needed.
  • waste or solar thermal energy flows with all of these modules and/or sub-modules for example, by adding one or more heat exchangers.
  • the object of the present invention also makes it possible to raise the temperature level of the recovered waste or solar thermal energy, to store it, and to release it according to the desired use.
  • the various functional elements of the heat pump according to the present invention can be isolated in modules.
  • This modular system allows the heat pump to be easily arranged according to the physical layout of the site where it is to be installed. Indeed, modularity allows the heat pump to be adapted to on-site production needs, for example, by increasing or decreasing the production (power) or storage (energy) capacities of thermal energy. Furthermore, modularity allows for variations in original configurations. For example, modularity can allow the insertion of several storage systems to achieve a diversity of temperatures, whether at the input (recovery of waste heat at different temperature levels and/or temperature variations) and/or at the output (production of thermal energy at a specific temperature and/or with varying temperature requirements).
  • the modules comprising the different elements are adapted for their movement in containers.
  • Module recombination limits the number of module variants, thus optimizing system costs while enabling the ability to address a larger range of applications. number of different needs.
  • thermal energy storage can be achieved by installing elements in storage systems such as tanks (for example, those mentioned above) that, during a charging phase, absorb and store thermal energy, for example, by stacking smaller blocks (compared to said tanks) at different levels.
  • These blocks can be in the form of gravel, refractory bricks, ceramic pieces, cement pieces, rock pieces (for example, volcanic or granitic), or even zeolites.
  • stacking on different levels can take the form of capsules containing conventional PCMs (phase change materials) such as certain sands (such as molten salts), notably KNO3 - 60% NaNO3 or NaCl/ MgCl2 (57/43) used for more than 20 years in concentrated solar power (CSP) plants, paraffin, CaCl2 6H2O .
  • PCMs phase change materials
  • sands such as molten salts
  • KNO3 - 60% NaNO3 or NaCl/ MgCl2 (57/43) used for more than 20 years in concentrated solar power (CSP) plants, paraffin, CaCl2 6H2O .
  • the tanks and pipes will be thermally insulated with conventional insulating materials such as rock wool or other standard insulation.
  • the heat pump according to the present invention thus comprises at least two cycles, one called charging and the other called discharging.
  • a compressor 1 and a turbine 2 can be seen connected to each other by an electrical and/or mechanical link 13, driven by an electric motor 3.
  • the compressor and the turbine are both connected by pipes 10 to a first storage system 4 on the one hand, and to a second storage system 5 on the other hand, thus establishing a loop between the compressor 1, the turbine 2, the first storage system 4 and the second storage system 5.
  • the compressor 1 and the turbine 2 form a single-stage centrifugal electric turbocompressor.
  • FIG. 2 is a schematic representation of the heat pump of the [ Fig.1 [ ], connected to thermal energy release systems 6, represented here in a load cycle.
  • the first storage system 4 and the second storage system 5 are thus each respectively connected to a thermal energy release system 6, allowing them to supply heat or cold to a customer system 7.
  • the direction of the flow represented by the arrows 8 implies here that thermal energy in the form of heat is concentrated in the second storage system 5, while thermal energy in the form of cold is concentrated in the first storage system 4.
  • the cold thermal energy storage is at low pressure.
  • a temperature gradient can then be created in the first storage system 4 and in the second storage system 5 such that, theoretically, Q1 is at a higher temperature (i.e., hotter) than Q2, and Q3 is at a lower temperature (i.e., cooler) than Q3. cold) than Q4.
  • Q1 is at a higher temperature (i.e., hotter) than Q2
  • Q3 is at a lower temperature (i.e., cooler) than Q3. cold) than Q4.
  • no discharge is shown in the [ Fig. 2 ].
  • FIG. 4 is a top-view representation of the assembly diagram according to the figures 2 And 3 Compressor 1, turbine 2, and motor 3, along with its (electrical) power unit and any standard fittings, are assembled in a working group 9.
  • Working group 9 first storage system 4, second storage system 5, and pipes 10 constitute a first heat pump assembly 14 according to the present invention.
  • FIG. 5 is a top-view representation of an assembly diagram showing the elements of the [ Fig. 4 [furthermore, it presents a source 11 of waste energy (or thermal energy of natural or solar origin) allowing a thermal energy input represented by arrow 12. Any means of capturing this waste energy can be applied (for example, a heat exchanger connected to the pipe circuit 10 of the heat pump assembly 14 according to the present invention). It is possible to place a thermal energy input between the storage system 5 and the turbine of the working unit 9, and/or between the storage system 4 and the (turbo-)compressor of the working unit 9.]
  • FIG. 6 [ ] represents a heat pump assembly 14 according to the present invention, comprising two thermal energy storage systems 4A and 5A and a working unit 9.
  • the working unit 9 is doubly connected to each of the storage systems 4A, 4B, 5A, and 5B.
  • 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.
  • the heat exchangers 6 are located outside the assemblies 14 and 15. It is also possible for the heat exchangers to be located inside the sets 14, 15.
  • sets 14 and 15 of figures 4, 5 And 6 can be containers.
  • FIG. 7 is a perspective representation of the heat pump of the [ Fig.1 inserted into a container 14.
  • Fig. 8 [ ] is a conceptual diagram representing a particular embodiment of a heat pump according to the present invention, in a heat pump charging cycle.
  • the heat pump comprises four thermal energy storage systems 16A-16D, two thermal energy release systems 18A, 18B, two three-way valves 20A, 20B, two pumping elements 22A, 22B, one two-way valve 24 and three non-return valves 26A-26C.
  • a first end 16A1 of a first thermal energy storage system 16A is connected to a first end 16B1 of a second thermal energy storage system 16B via a first gas circulation branch 28A.
  • a first end 16C1 of a third thermal energy storage system 16C is connected to a first end 16D1 of a fourth thermal energy storage system 16D via a second gas circulation branch 28B.
  • a first thermal energy recovery system 18A (preferably a heat exchanger) is arranged to exchange thermal energy with the first gas circulation branch 28A.
  • a second thermal energy recovery system 18B (preferably a heat exchanger) is arranged to exchange thermal energy with the second gas circulation branch 28B.
  • a first three-way valve 20A is connected to a second end 16A2 of the first thermal energy storage system 16A, to a second end 16B2 of the second thermal energy storage system 16B, and to a second end 16C2 of the third thermal energy storage system 16C.
  • a second three-way valve 20B is connected to the second end 16B2 of the second thermal energy storage system 16B, to the second end 16C2 of the third thermal energy storage system 16C and to a second end 16D2 of the fourth thermal energy storage system 16D.
  • a first pumping element 22A (typically a pump) connects the second end 16B2 of the second thermal energy storage system 16B to the corresponding port 20A1 of the first three-way valve 20A.
  • Another port 20A2 of the first three-way valve 20A is connected to the second end 16A2 of the first thermal energy storage system 16A, and the last port 20A3 of the first three-way valve 20A is connected to the second end 16C2 of the third thermal energy storage system 16C.
  • a second pumping element 22B (typically a pump) connects the second end 16C2 of the third thermal energy storage system 16C to the corresponding channel 20B1 of the second three-way valve 20B.
  • Another channel 20B2 of the second three-way valve 20B is connected to the second end 16D2 of the fourth thermal energy storage system 16D, and the last channel 20B3 of the second three-way valve 20B is connected to the second end 16B2 of the second thermal energy storage system 16B.
  • the inlet 1E of the compressor section 1 of the electric turbocharger is connected to the first end 16A1 of the first thermal energy storage system 16A at a first connection point 30A on the first gas circulation branch 28A.
  • the outlet 1S of the compressor section 1 of the electric turbocharger is connected to the first end 16B1 of the second thermal energy storage system 16B at a second connection point 30B on the first gas circulation branch 28A.
  • the inlet 2E of the turbine section 2 of the electric turbocharger is connected to the first end 16D1 of the fourth thermal energy storage system 16D at a first connection point 32A on the second gas circulation branch 28B.
  • the output 2S of the turbine part 2 of the electric turbocharger is connected to the first end 16C1 of the third thermal energy storage system 16C at a second connection point 32B on the second gas circulation branch 28B.
  • the two-way valve 24 is connected to the first gas circulation branch 28A between the first connection point 30A and the second connection point 30B.
  • a first check valve 26A is connected between the outlet 1S of the compressor section 1 of the electric turbocharger and the second connection point 30B of the first gas circulation branch 28A.
  • a second check valve 26B is connected between the outlet 2S of the turbine section 2 of the electric turbocharger and the second connection point 32B of the second gas circulation branch 28B.
  • a third check valve 26C is connected to the second gas circulation branch 28B between the first connection point 32A and the second connection point 32B.
  • the direction of flow represented by arrows 34 implies that thermal energy in the form of heat is concentrated in the second storage system 16B (after being extracted from the first storage system 16A and then compressed in compressor 1), while thermal energy in the form of cold is concentrated in the third storage system 16C (after being extracted from the fourth storage system 16D and then expanded in turbine 2).
  • Cold thermal energy storage is at low pressure (typically around one bar when the gas used is air), while hot thermal energy storage is at high pressure. (typically between one and five bars in absolute value when the gas used is air).
  • Cold thermal energy extraction is at high pressure, while hot thermal energy extraction is at low pressure.
  • the temperature gradients that develop in the second and third storage systems 16B, 16C cause thermal energy to be transferred from the second storage system 16B to the fourth storage system 16D on the one hand, and from the third storage system 16C to the first storage system 16A on the other.
  • the second storage system 16B is cooled by the discharge, thus creating a temperature gradient that causes the gas to circulate in the direction of the flow represented by the arrows 41.
  • the third storage system 16C is heated by the discharge, thus creating a temperature gradient that causes the gas to circulate in the direction of the flow represented by the arrows 42.
  • This particular embodiment of the heat pump is illustrated on the figures 8 to 11 This allows the order of gas flow in the first and fourth storage systems 16A, 16D to be "interchanged" during the discharge operation compared to the charging operation, without physically moving the storage systems 16A-16D.
  • the advantage of this operation is that it avoids introducing excessively large temperature differences (thermal shocks) that would disrupt the establishment of thermoclines in the thermal energy storage systems 16A-16D and thus be detrimental to the efficiency of the thermal storage and the application in general.
  • FIG. 12 [ ] is a conceptual diagram representing a particular embodiment of a heat pump according to the present invention, in a heat pump charging cycle.
  • the heat pump according to this particular embodiment comprises a single-stage centrifugal electric turbocompressor 1, 2, four thermal energy storage systems 16A-16D, two thermal energy release systems 18A, 18B, two three-way valves 20A, 20B, two pumping elements 22A, 22B, a two-way valve 24, and three non-return valves 26A-26C (all of which are connected in the same way as in the previous embodiment).
  • the heat pump also includes three additional thermal energy recovery systems 44A-44C, four additional two-way valves 46A-46D, four additional three-way valves 48A-48D, and four additional pumping elements 49A-49D.
  • This particular embodiment of the figures 12 to 15 therefore constitutes an improvement on the previous embodiment described with reference to figures 8 to 11
  • the elements described with the same numerical references as those of the figures 8 to 11 are identical to the latter and will therefore not be described in more detail later.
  • a first end 44A1 of a first additional thermal energy recovery system 44A is connected to a first end 18A1 of the first thermal energy recovery system 18A via a first and second additional two-way valve 46A, 46B.
  • a second end 44A2 of the first additional thermal energy recovery system 44A is connected to a second end 18A2 of the first thermal energy recovery system 18A.
  • a first end 44B1 of a second additional thermal energy recovery system 44B is connected to a first end 18B1 of the second thermal energy recovery system 18B.
  • a second end 44B2 of the second additional thermal energy recovery system 44B is connected to a second end 18B2 of the second thermal energy recovery system 18B via a third and fourth additional two-way valve 46C, 46D.
  • a first end 44C1 of a third additional thermal energy restitution system 44C is connected to the first connection point 30A on the first gas circulation branch 28A; and a second end 44C2 of the third additional thermal energy restitution system 44C is connected to the second connection point 32B on the second gas circulation branch 28B.
  • a first additional three-way valve 48A is connected to the inlet 1E of the compressor section 1 of the electric turbocharger, to the first connection point 30A on the first gas circulation branch 28A, and to the first end 44C1 of the third additional thermal energy recovery system 44C.
  • a second additional three-way valve 48B is connected to the outlet 1S of the compressor section 1 of the electric turbocharger, to the second connection point 30B on the first gas circulation branch 28A, and to one of the ports 48C1 of a third additional three-way valve 48C via a first gas line 50A.
  • the third additional three-way valve 48C is further connected to the inlet 2E of the turbine section 2 of the electric turbocharger and to the first connection point 32A on the second gas circulation branch 28B.
  • An additional fourth three-way valve 48D is connected to the outlet 2S of the turbine part 2 of the electric turbocharger, to the second connection point 32B on the second gas circulation branch 28B and to the second end 44C2 of the third additional thermal energy recovery system 44C via a second gas line 50B.
  • the first and third additional thermal energy recovery systems 44A, 44C are each arranged to exchange thermal energy with the first gas line 50A.
  • the second thermal energy recovery system Additional thermal 44B is arranged to exchange thermal energy with the second gas line 50B.
  • a first additional pumping element 49A (typically a pump) connects the second end 44A2 of the first additional return system 44A to the "hot" outlet 56 of the assembly formed by the first return system 18A and the first additional return system 44A.
  • a second additional pumping element 49B (typically a pump) connects the second end 18A2 of the first return system 18A to the "hot" outlet 56 of the assembly formed by the first return system 18A and the first additional return system 44A.
  • a third additional pumping element 49C (typically a pump) connects the first end 44B1 of the second additional return system 44B to the "cold" outlet 58 of the assembly formed by the second return system 18B and the second additional return system 44B.
  • a fourth additional pumping element 49D (typically a pump) connects the first end 18B1 of the second restitution system 18B to the "cold" outlet 58 of the assembly formed by the second restitution system 18B and the second additional restitution system 44B.
  • thermo energy in the form of heat is concentrated in the second storage system 16B (after being extracted from the first storage system 16A and then compressed in compressor 1), while thermal energy in the form of cold is concentrated in the third storage system 16C (after being extracted from the fourth storage system 16D and then expanded in turbine 2).
  • the turbine and electric compressor are combined into a single turbomachine, which is a single-stage centrifugal electric turbocompressor.
  • Metal tanks such as standard cylindrical metal tanks (steel or stainless steel) of various sizes, can be thermally insulated and capable of holding compressed air under a pressure of up to 10 bar, between 0.5 and 10m3, or even more.

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Claims (12)

  1. Elektrische Wärmepumpe, umfassend:
    - mindestens zwei Wärmeenergiespeichersysteme (4, 5; 16A-16D), und
    - mindestens ein Wärmeenergierückgewinnungssystem (6; 18A, 18B), wobei:
    - mindestens eines der Wärmeenergiespeichersysteme (5; 16B) zum Speichern der Wärmeenergie in Form von Wärme bei einer Temperatur zwischen + 100 °C und + 800 °C konfiguriert ist,
    - mindestens eines der Wärmeenergiespeichersysteme (4; 16C) zum Speichern der Wärmeenergie in Form von Kälte bei einer Temperatur zwischen - 100 °C und + 150 °C konfiguriert ist; und
    - das mindestens eine Wärmeenergierückgewinnungssystem (6; 18A, 18B) zum Zurückgewinnen der Wärme und/oder der Kälte im Laufe der Zeit auf getrennte oder parallele Weise konfiguriert ist, oder
    - das mindestens eine Wärmeenergierückgewinnungssystem (6; 18A, 18B) für einen Betrieb einer parallelen Rückgewinnung konfiguriert ist, der mit einem Betrieb einer getrennten Rückgewinnung der Wärme und/oder der Kälte im Laufe der Zeit abgewechselt werden kann; wobei die Wärmepumpe zum Umfassen eines umgekehrten Brayton-Kreisprozesses konfiguriert ist, der mit einem Gas betrieben wird;
    dadurch gekennzeichnet, dass die Wärmepumpe einen einzelnen einstufigen elektrischen Zentrifugenturboverdichter (1, 2) umfasst.
  2. Wärmepumpe nach Anspruch 1, dadurch gekennzeichnet, dass der einstufige elektrische Zentrifugenturboverdichter (1, 2) einen Verdichtungsgrad zwischen 1 und 5 aufweist, wobei der Verdichtungsgrad als das Verhältnis zwischen dem Auslassdruck des Verdichterteils (1) des Turboverdichters und dem Einlassdruck des Verdichterteils (1) definiert ist.
  3. Wärmepumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass:
    - mindestens eines der Wärmeenergiespeichersysteme (4; 16C) zum Speichern der Wärmeenergie bei Temperaturen zwischen - 50 °C und + 100 °C konfiguriert ist, und/oder
    - dass mindestens eines der Wärmeenergiespeichersysteme (5; 16B) zum Speichern der Wärmeenergie bei Temperaturen zwischen + 150 °C und + 500 °C, vorzugsweise zwischen + 200 °C und + 400 °C konfiguriert ist.
  4. Wärmepumpe nach einem der vorstehenden Ansprüche,
    dadurch gekennzeichnet, dass die mindestens zwei Wärmeenergiespeichersysteme (4, 5; 16A-16D) zum Speichern der Wärmeenergie in Form von Wärme und in Form von Kälte konfiguriert sind.
  5. Wärmepumpe nach einem der vorstehenden Ansprüche,
    dadurch gekennzeichnet, dass die verschiedenen Betriebskomponenten der Wärmepumpe in Modulen isoliert sind, wobei die Module zum Verbundenwerden miteinander beispielsweise durch physische Verbindungen wie Ventile, Verbindungsrohre und/oder Schläuche konfiguriert sind.
  6. Wärmepumpe nach einem der vorstehenden Ansprüche,
    dadurch gekennzeichnet, dass sie zum Gekoppeltwerden mit mindestens einer natürlichen Wärmequelle und/oder mindestens einer künstlichen Wärmequelle, beispielsweise einem Gaskessel, einem Gasofen, einer Wärme aus Sonnenenergie oder einer Abwärme (11), einem Trockner und/oder einer Abgabe von Wärme künstlichen Ursprungs konfiguriert ist.
  7. Wärmepumpe nach einem der vorstehenden Ansprüche,
    dadurch gekennzeichnet, dass das Gas, das in dem umgekehrten Brayton-Kreisprozess der Wärmepumpe verwendet wird, Luft oder ein Edelgas der Art Helium oder Argon oder auch eine Mischung dieser Gase ist.
  8. Wärmepumpe nach einem der vorstehenden Ansprüche,
    dadurch gekennzeichnet, dass die Wärmepumpe vier Wärmeenergiespeichersysteme (16A-16D), zwei Wärmeenergierückgewinnungssysteme (18A, 18B), zwei Dreiwegeventile (20A, 20B) und zwei Pumpenkomponenten (22A, 22B) vorweist; wobei ein erstes Ende (16A1) eines ersten Wärmeenergiespeichersystems (16A) über einen ersten Gaszirkulationszweig (28A) an ein erstes Ende (16B1) eines zweiten Wärmeenergiespeichersystems (16B) angeschlossen ist; ein erstes Ende (16C1) eines dritten Wärmeenergiespeichersystems (16C) über einen zweiten Gaszirkulationszweig (28B) an ein erstes Ende (16D1) eines vierten Wärmeenergiespeichersystems (16D) angeschlossen ist; ein erstes Wärmeenergierückgewinnungssystem (18A) so angeordnet ist, dass es Wärmeenergie mit dem ersten Gaszirkulationszweig (28A) austauscht, ein zweites Wärmeenergierückgewinnungssystem (18B) so angeordnet ist, dass es Wärmeenergie mit dem zweiten Gaszirkulationszweig (28B) austauscht; ein erstes Dreiwegeventil (20A) an ein zweites Ende (16A2) des ersten Wärmeenergiespeichersystems (16A), an ein zweites Ende (16B2) des zweiten Wärmeenergiespeichersystems (16B) und an ein zweites Ende (16C2) des dritten Wärmeenergiespeichersystems (16C) angeschlossen ist; ein zweites Dreiwegeventil (20B) an das zweite Ende (16B2) des zweiten Wärmeenergiespeichersystems (16B), an das zweite Ende (16C2) des dritten Wärmeenergiespeichersystems (16C) und an ein zweites Ende (16D2) des vierten Wärmeenergiespeichersystems (16D) angeschlossen ist; eine erste Pumpenkomponente (22A) das zweite Ende (16B2) des zweiten Wärmeenergiespeichersystems (16B) mit dem entsprechenden Weg (20A1) des ersten Dreiwegeventils (20A) verbindet; eine zweite Pumpenkomponente (22B) das zweite Ende (16C2) des dritten Wärmeenergiespeichersystems (16C) mit dem entsprechenden Weg (20B1) des zweiten Dreiwegeventils (20B) verbindet; der Einlass (1E) des Verdichterteils (1) des elektrischen Turboverdichters an einem ersten Verbindungspunkt (30A) an dem ersten Gaszirkulationszweig (28A) an das erste Ende (16A1) des ersten Wärmeenergiespeichersystems (16A) angeschlossen ist; der Auslass (1S) des Verdichterteils (1) des elektrischen Turboverdichters an einem zweiten Verbindungspunkt (30B) an dem ersten Gaszirkulationszweig (28A) an das erste Ende (16B1) des zweiten Wärmeenergiespeichersystems (16B) angeschlossen ist; wobei der Einlass (2E) des Turbinenteils (2) des elektrischen Turboverdichters an einem ersten Verbindungspunkt (32A) an dem zweiten Gaszirkulationszweig (28B) an das erste Ende (16D1) des vierten Wärmeenergiespeichersystems (16D) angeschlossen ist; wobei der Auslass (2S) des Turbinenteils (2) des elektrischen Turboverdichters an einem zweiten Verbindungspunkt (32B) an dem zweiten Gaszirkulationszweig (28B) an das erste Ende (16C1) des dritten Wärmeenergiespeichersystems (16C) angeschlossen ist.
  9. Wärmepumpe nach dem vorstehenden Anspruch,
    dadurch gekennzeichnet, dass die Wärmepumpe ferner ein Zweiwegeventil (24) und drei Rückschlagventile (26A, 26B, 26C) vorweist; wobei das Zweiwegeventil (24) an dem ersten Gaszirkulationszweig (28A) zwischen dem ersten Verbindungspunkt (30A) und dem zweiten Verbindungspunkt (30B) verbunden ist; ein erstes Rückschlagventil (26A) zwischen dem Auslass (1S) des Verdichterteils (1) des elektrischen Turboverdichters und dem zweiten Verbindungspunkt (30B) des ersten Gaszirkulationszweigs (28A) verbunden ist; ein zweites Rückschlagventil (26B) zwischen dem Auslass (2S) des Turbinenteils (2) des elektrischen Turboverdichters und dem zweiten Verbindungspunkt (32B) des zweiten Gaszirkulationszweigs (28B) verbunden ist; ein drittes Rückschlagventil (26C) an dem zweiten Gaszirkulationszweig (28B) zwischen dem ersten Verbindungspunkt (32A) und dem zweiten Verbindungspunkt (32B) verbunden ist.
  10. Wärmepumpe nach Anspruch 8 oder 9, dadurch gekennzeichnet, dass die Wärmepumpe ferner drei zusätzliche Wärmeenergierückgewinnungssysteme (44A-44C), vier zusätzliche Zweiwegeventile (46A-46D) und vier zusätzliche Dreiwegeventile (48A-48D) umfasst; wobei ein erstes Ende (44A1) eines ersten zusätzlichen Wärmeenergierückgewinnungssystems (44A) über ein erstes und ein zweites Zweiwegeventil (46A, 46B) an ein erstes Ende (18A1) des ersten Wärmeenergierückgewinnungssystems (18A) angeschlossen ist; ein zweites Ende (44A2) des ersten zusätzlichen Wärmeenergierückgewinnungssystems (44A) an ein zweites Ende (18A2) des ersten Wärmeenergierückgewinnungssystems (18A) angeschlossen ist; ein erstes Ende (44B1) eines zweiten zusätzlichen Wärmeenergierückgewinnungssystems (44B) an ein erstes Ende (18B1) des zweiten Wärmeenergierückgewinnungssystems (18B) angeschlossen ist; ein zweites Ende (44B2) des zweiten zusätzlichen Wärmeenergierückgewinnungssystems (44B) über ein drittes und ein viertes Zweiwegeventil (46C, 46D) an ein zweites Ende (18B2) des zweiten Wärmeenergierückgewinnungssystems (18B) angeschlossen ist; ein erstes Ende (44C1) eines dritten zusätzlichen Wärmeenergierückgewinnungssystems (44C) an den ersten Verbindungspunkt (30A) an dem ersten Gaszirkulationszweig (28A) angeschlossen ist; ein zweites Ende (44C2) des dritten zusätzlichen Wärmeenergierückgewinnungssystems (44C) an den zweiten Verbindungspunkt (32B) an dem zweiten Gaszirkulationszweig (28B) angeschlossen ist; ein erstes zusätzliches Dreiwegeventil (48A) an den Einlass (1E) des Verdichterteils (1) des elektrischen Turboverdichters, an den ersten Verbindungspunkt (30A) an dem ersten Gaszirkulationszweig (28A) und an das erste Ende (44C1) des dritten zusätzlichen Wärmeenergierückgewinnungssystems (44C) angeschlossen ist; ein zweites zusätzliches Dreiwegeventil (48B) über eine erste Gasleitung (50A) an den Auslass (1S) des Verdichterteils (1) des elektrischen Turboverdichters, an den zweiten Verbindungspunkt (30B) an dem ersten Gaszirkulationszweig (28A) und an einen der Wege (48C1) eines dritten zusätzlichen Dreiwegeventils (48C) angeschlossen ist; das dritte zusätzliche Dreiwegeventil (48C) ferner an den Einlass (2E) des Turbinenteils (2) des elektrischen Turboverdichters und an den ersten Verbindungspunkt (32A) an dem zweiten Gaszirkulationszweig (28B) angeschlossen ist; ein viertes zusätzliches Dreiwegeventil (48D) über eine zweite Gasleitung (50B) an den Auslass (2S) des Turbinenteils (2) des elektrischen Turboverdichters, an den zweiten Verbindungspunkt (32B) an dem zweiten Gaszirkulationszweig (28B) und an das zweiten Ende (44C2) des dritten zusätzlichen Wärmeenergierückgewinnungssystems (44C) angeschlossen ist; wobei das erste und das dritte zusätzliche Wärmeenergierückgewinnungssystem (44A, 44C) jeweils so angeordnet sind, dass sie Wärmeenergie mit der ersten Gasleitung (50A) austauschen; wobei das zweite zusätzliche Wärmeenergierückgewinnungssystem (44B) so angeordnet ist, dass es Wärmeenergie mit der zweiten Gasleitung (50B) austauscht.
  11. Verfahren zum Bereitstellen von Wärmeenergie in Form von Wärme mit einer Temperatur zwischen + 100 °C und + 800 °C und/oder Kälte mit einer Temperatur zwischen - 100 °C und + 150 °C unter Verwendung einer Wärmepumpe nach einem der Ansprüche 1 bis 10, umfassend die folgenden Schritte:
    (a) einen Schritt für einen Ladezyklus durch mechanische Verdichtung mindestens eines Gases mit vorzugsweise einer mechanischen Ausdehnung des mindestens einen Gases; und
    (b) einen Schritt für einen Entladezyklus ohne Verdichtung und/oder Ausdehnung, wobei die Wärmeenergie über mindestens ein Wärmeenergierückgewinnungssystem, zum Beispiel über mindestens ein Ventil, mindestens einen Zirkulator und/oder mindestens einen Wärmetauscher, abgeführt wird.
  12. Verfahren nach Anspruch 11, dadurch gekennzeichnet, dass Schritt (b) des Entladezyklus parallel zu Schritt (a) des Ladezyklus durchgeführt wird.
EP23710891.5A 2022-03-11 2023-03-10 Wärmepumpe mit zwei wärmeenergiespeicher- und -abgabesystemen Active EP4490449B1 (de)

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FR2202181A FR3133430B1 (fr) 2022-03-11 2022-03-11 Pompe a chaleur a deux systemes de stockage et restitution d’energie thermique
FR2302010A FR3133431B1 (fr) 2022-03-11 2023-03-03 Pompe a chaleur a deux systemes de stockage et restitution d’energie thermique
PCT/EP2023/056238 WO2023170300A1 (fr) 2022-03-11 2023-03-10 Pompe a chaleur a deux systemes de stockage et restitution d'energie thermique

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FR2916101B1 (fr) * 2007-05-11 2009-08-21 Saipem Sa Installation et procedes de stockage et restitution d'energie electrique
PT2220343E (pt) 2007-10-03 2013-08-22 Isentropic Ltd Aparelho d e armazenamento de energia e método para armazenar energia
EP2574740A1 (de) 2011-09-29 2013-04-03 Siemens Aktiengesellschaft Anlage zur Speicherung thermischer Energie
EP2574865A1 (de) 2011-09-29 2013-04-03 Siemens Aktiengesellschaft Energiespeichervorrichtung sowie Verfahren zur Speicherung von Energie
JP2016211830A (ja) 2015-05-13 2016-12-15 多門 山内 温冷両熱同時獲得保存装置の無駄を無くし効果をより高める方法
WO2017029819A1 (ja) * 2015-08-17 2017-02-23 三菱電機株式会社 熱利用装置
US10233787B2 (en) 2016-12-28 2019-03-19 Malta Inc. Storage of excess heat in cold side of heat engine
DE102018221850A1 (de) 2018-12-14 2020-06-18 Glen Dimplex Deutschland Gmbh Wärmepumpenanlage
CN110206599B (zh) * 2019-06-04 2022-03-29 中国科学院工程热物理研究所 一种冷热电联储联供系统
DE102019127431B4 (de) * 2019-10-11 2021-05-06 Enolcon Gmbh Thermischer Stromspeicher mit Festbett-Wärmespeicher und Festbett-Kältespeicher und Verfahren zum Betreiben eines thermischen Stromspeichers

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CN119546910A (zh) 2025-02-28
WO2023170300A1 (fr) 2023-09-14
EP4490449A1 (de) 2025-01-15
US20250180303A1 (en) 2025-06-05
JP2025509337A (ja) 2025-04-11
KR20240163676A (ko) 2024-11-19

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