System block comprising solid block material for storing and transferring heat

Abstract

The invention relates to a system for storing and transferring heat, comprising at least one heat source for generating heat energy; the high-temperature heat storage device is provided with a blocky refractory material filled in a high-temperature storage space, and the high-temperature storage space is used for storing the generated heat energy; at least one heat consuming system for consuming the stored heat energy; and the heat transfer mechanism is used for transferring the heat energy from the heat source to the high-temperature heat storage device and transferring the heat energy from the high-temperature heat storage device to the heat consumption system. The heat transfer mechanism is a closed gas loop connected with the heat source, the high-temperature heat storage device and the heat consumption system. And the high-temperature heat storage device is partially wrapped in the bearing inner shell (3). The bulk refractory material (1) comprises particle fractions having a sphericity in the range of 0.4 to 1 and an average particle size in the range of 0.5 mm to 20 mm. The volume ratio of the maximum particles to the minimum particles does not exceed 5: 1. The bearing inner shell (3) is wrapped with a heat insulation outer shell (5), so that a gas gap (4.1) is formed between the bearing inner shell (3) and the heat insulation outer shell (5) and used for recovering heat loss which comes from the high-temperature heat storage device and penetrates through the bearing inner shell (3). The gas gap (4.1) and the communicating gas channel (4.3) connect the high-temperature heat storage device with at least one process area (4.2), and the process area (4.2) is further connected with the at least one heat consumption system. A hot gas channel (7) connects the high-temperature heat storage device to the at least one heat source. The invention also relates to a method for storing and transferring heat using a system according to any one of the preceding claims.

Description

Technical Field

[0001] This invention relates to a system for storing and transferring heat in a high-temperature thermal storage system, wherein thermal energy is stored in a solid block material. Background Technology

[0002] International patent application WO 2020183063 A1 describes a system and method for storing and transferring heat (reference numerals in WO 2020183063 A1 are referred to herein). The system (100, 300, 400) includes: at least one resistor (101, 301, 401) for generating heat energy from electrical energy; at least one heat storage device (102, 302, 402) having a solid material (e.g., sand, granules, gravel) for storing the generated heat energy, preferably located underground and with a storage temperature up to 1200°C; and a heat transfer mechanism (103, 303, 403) for transferring heat from the heat storage device (102, 302, 402) to a heat dissipation system (104, 304, 404) for subsequent use. The resistor (101) may be located inside or outside the heat storage device (102). The heat transfer mechanism (103, 303, 403) can be a closed gas circuit (first embodiment of the prior art) or a multi-tube thermosiphon system closed at both ends (second embodiment of the prior art). The heat storage device (102, 302, 402) includes pipes (such as stainless steel) disposed in a solid material for transporting gas.

[0003] In a first embodiment, a closed gas loop facilitates heat transfer between the thermal storage devices (102, 302, 402) and nitrogen gas (preferably using a bidirectional fan) at a pressure of 1 to 50 Pa. In this embodiment, the gas circulates through pipes within the thermal storage devices (102, 302, 402). In a second embodiment, the thermosiphon system may include thermosiphon pipes, the liquid filling of which does not exceed 25% of its volume. For example, vertically arranged stainless steel thermosiphon pipes are filled with water at the bottom, which, upon heating, can be completely converted into steam or even supercritical steam and rise to the top of the pipes. Optionally, the system includes auxiliary heat transfer loops (312, 412) and / or auxiliary thermal storage devices (313, 413). Optionally, the system includes a generator for converting fluctuating power sources or excess grid power, such as solar panels, wind turbines, tidal power plants, or overloaded grids, into electrical energy. The thermal storage devices (102, 302, 402) can be wrapped in an insulation layer of low thermal conductivity material, such as artificial particles with a thermal conductivity of less than 0.3 W / mK.

[0004] The aforementioned system, which uses a closed gas loop within the storage space as the heat transfer mechanism, has drawbacks. It requires additional components, known as "pipelines," to provide a heat transfer surface for the gaseous medium. The number of heat transfer surfaces and implanted components is directly proportional to the required power and stored energy, and constitutes a significant portion of the heat storage unit's mass. Heat conduction between the storage material and the pipe walls requires a temperature gradient, which increases the temperature difference between the inlet and outlet, thus reducing the efficiency of the heat storage device. The additional components used for medium conduction must withstand the highest temperatures within the heat storage unit, and sometimes the internal pressure of the medium. The high-heat-resistant metals used in these components are expensive, significantly increasing the cost of the heat storage unit relative to its stored energy. Even with durable metals, their mechanical properties decrease significantly with increasing temperature, typically failing to match the heat resistance of conventional refractory materials. Therefore, the application of metals in high-temperature ranges is limited, restricting both operating temperature and storage capacity. Due to the high cost of the piping, its cross-sectional area must be minimized, leading to excessively high fluid velocities and limiting the possibility of temperature stratification within the heat storage unit. Systems utilizing the heat of the stored medium must withstand significant fluctuations in the medium's outlet temperature.

[0005] The aforementioned system, which uses a thermosiphon system as the heat transfer mechanism, has the following drawbacks: its operation depends on the physical parameters of the medium and the relationship between pressure and temperature in the heat exchange loop; furthermore, under high-temperature conditions, the heat exchange loop must operate under high pressure. The unidirectional flow of energy from bottom to top in the closed pipeline makes it impossible to achieve temperature stratification of the energy storage medium. In addition, this system also suffers from the aforementioned drawbacks of closed gas loop systems.

[0006] Similar systems including piping can be found in Chinese patent application CN 108007246 A (thermal energy storage in molten salt), Japanese patent application JP H102616 A (thermal energy storage in a metal block), and US patent application US 2012111006A1 (thermal energy storage in a block material of a structural labyrinth of thermal storage space).

[0007] Therefore, in the existing technology, there is an urgent need to provide a system and corresponding method for storing and transferring heat energy with higher heat storage efficiency, and with the following characteristics: meeting the necessary heat resistance, lower operating pressure, enabling temperature stratification within the heat storage device, and lower investment cost relative to the stored heat energy. Summary of the Invention

[0008] The purpose of this invention is to provide a thermal storage and heat transfer system that uses non-metallic materials to distribute the heat transfer medium within the thermal storage device and can recover heat losses through the insulated thermal storage shell. Simultaneously, the system allows for highly stratified thermal storage, thereby enabling the recovery of stored thermal energy at sustained high temperatures with minimal difference from the inlet temperature. A blower system (detailed below) allows for precise control of the outlet temperature and power.

[0009] The aforementioned features aim to improve the economic and technical parameters of high-temperature thermal storage devices. The increased maximum operating temperature and continuous output of high-temperature thermal energy will enable the application of thermal storage technology in untapped fields. High temperatures can also typically improve the efficiency of process flows and other energy conversions.

[0010] The present invention also aims to provide a method for storing and transferring heat using the system.

[0011] The above objective is achieved through a heat storage and transfer system, which includes: The core design concept of this system is as follows: the blocky refractory material includes a granular portion with a sphericity ranging from 0.4 to 1 and an average particle size ranging from 0.5 mm to 20 mm, and the volume ratio of the largest to the smallest particle does not exceed 5:1. This granular portion ensures free permeability of both hot and cooling gases, eliminating the need for gas conduction pipelines within the blocky refractory material body. The maximum ratio of 5:1 represents the maximum uniformity of particle size, thus ensuring consistency in particle spacing and uniformity of particle temperature changes in the flowing gas, thereby minimizing the range of steep temperature gradient regions. Requiring uniform particle size distribution and a very narrow particle size range is technically more challenging than allowing for larger particle size tolerances. A particle size tolerance greater than 5:1 has a significant impact on aggregate spacing and heating uniformity, but has minimal impact on the technical complexity (and cost) of aggregate preparation. A ratio exceeding 5:1 will result in particles with excessively large size differences within the aggregate, thereby reducing the average size of the particle gaps.

[0012] The load-bearing inner shell is further enclosed by an insulating outer shell, creating a gas gap between the load-bearing inner shell and the insulating outer shell to recover heat loss from the high-temperature thermal storage device through the load-bearing inner shell. The gas gap and a connecting gas channel connect the high-temperature thermal storage device to at least one process area, which is also connected to at least one heat consumption system. A hot gas channel connects the high-temperature thermal storage device to at least one heat source.

[0013] The load-bearing inner shell may have a high-temperature insulation layer on the side near the high-temperature storage space to more effectively prevent heat from being transferred from the high-temperature storage space to the load-bearing inner shell.

[0014] In one embodiment of the invention, the heat source is an input heat exchanger. A blower system may be provided within the process area to conduct cooling gas from the high-temperature storage space through the gas gap, the communicating gas channel, the process area, and the first output gas channel to at least one input heat exchanger. At least one hot gas channel may be configured to transfer hot gas from the input heat exchanger to a gas layer above the high-temperature storage space.

[0015] As an alternative or supplement to the above embodiments, the heat source is at least one electric heating element. A blower system is provided within the process area to conduct the cooling gas from the high-temperature storage space through the gas gap, the connecting gas channel, and the process area to the second connecting gas channel and the hot gas channel. The hot gas channel also has thermal contact with the electric heating element to heat the gas into the gas layer above the high-temperature storage space. The electric heating element is disposed inside the load-bearing inner shell and outside the high-temperature storage space, preferably within the hot gas channel.

[0016] As a supplement to the above embodiments, the heat transfer mechanism is an output heat exchanger. The blower system is provided within the process area for conducting the cooling gas from the output heat exchanger through a second input gas channel, the process area, the communicating gas channel, and the gas gap to the high-temperature storage space. At least one of the hot gas channels may be configured to conduct the hot gas from the high-temperature storage space from the gas layer above it to at least one output heat exchanger.

[0017] The first input gas channel and the first output gas channel are coaxially arranged so that the first output gas channel surrounds the first input gas channel. Similarly, the second input gas channel and the second output gas channel are coaxially arranged so that the second input gas channel surrounds the second output gas channel. Likewise, the connecting gas channel and the hot gas channel are coaxially arranged so that the connecting gas channel surrounds the hot gas channel. This coaxial arrangement prevents heat transfer from the hot gas to the external environment and allows for heat recovery from the cooling gas.

[0018] The gas gap can be connected to a two-way valve via an air passage, and the two-way valve is further connected to the surrounding environment via a safety inlet gas passage and a safety outlet gas passage. This ensures operational safety and the possibility of achieving pressure equalization.

[0019] The blocky refractory material is selected from any one of the following groups: basalt, andesite, dacite, artificial sintered aggregate, ceramic materials, blast furnace slag, compressed graphite with glassy carbon coating, carbides, and nitrides.

[0020] Temperature sensors can be located in the first input gas channel, the first output gas channel, the second input gas channel, the second output gas channel, the space of the cooling gas input / output channel, the space where the housing of the electric heating element connects to the gas layer above the high-temperature storage space, and the space upstream of the hot gas channel at the housing inlet. Each temperature sensor is connected to the control unit.

[0021] A maintenance area may be provided below the high-temperature storage space to accommodate a system for collecting and conveying separated dust and / or a system for collecting and conveying materials to be reprocessed.

[0022] At least one distribution valve can be installed in the gas layer above the high-temperature storage space to allow the blocky refractory material to enter at the operating temperature of the high-temperature storage space.

[0023] The average particle size ranges from 0.5 mm to 20 mm, preferably from 0.5 mm to 10 mm. The ratio of the average particle size of the blocky refractory material to the total height of the high-temperature storage space ranges from 1:1500 to 1:6000.

[0024] The above objective is also achieved by a method for storing and transferring heat using the system for storing and transferring heat described herein. The method includes the following heat storage steps: The following storage heat dissipation steps are then performed: f. The cooling gas is transferred from the heat dissipation system to the high-temperature heat storage device through the closed gas loop as the heat transfer system; g. Obtaining stored thermal energy from the high-temperature thermal storage device to form hot gas, the high-temperature thermal storage device having a blocky refractory material included in a high-temperature storage space; h. Transferring the hot gas from the high-temperature thermal storage device to the heat dissipation system via the closed gas loop as the heat transfer system; and i. Consume the thermal energy stored in the thermal gas in at least one heat-consuming system.

[0025] The core concept of this method is that the blocky refractory material comprises particles with a sphericity ranging from 0.4 to 1 and an average particle size ranging from 0.5 to 20 mm, wherein the volume ratio of the largest particle to the smallest particle is at most 5:1. In steps d and f, heat loss from the high-temperature heat storage device caused by heat transfer through the load-bearing inner shell surrounding the device is recovered by guiding cooling gas into the gas gap between the load-bearing inner shell and the insulating outer shell surrounding it.

[0026] The term "block material" refers to "loose" material.

[0027] The core concept of this invention lies in directly storing thermal energy within blocky refractory materials, eliminating the need for a closed piping system inside the storage space. By recovering heat losses, the dependence of the amount of heat lost to the external environment on the internal temperature is significantly reduced. Therefore, the economically achievable maximum internal temperature is significantly increased.

[0028] To limit heat leakage from the high-temperature storage space, a high-temperature insulation layer is installed on the inner side of the load-bearing inner shell. This high-temperature insulation layer can be made of various refractory materials and high-temperature insulation materials to form a layered insulation layer. The optimal parameters of the high-temperature insulation layer and the inner shell need to be determined through optimization calculations after determining the economic, operational, and physical parameters. The size and shape of the thermal storage device, as well as the time and power parameters required for heat storage and release, all have a significant impact.

[0029] The optimization calculation takes into account the difference between the heat flux intensity (Ti) through the high-temperature insulation layer and the heat flux intensity (Te) through the insulation shell, and combines this with the surface heat capacity (Cpl) of the shell. From this, the heating rate (Rpl; unit K·s) of the shell of the high-temperature storage space when the cooling gas in the gas gap stops (i.e., stops extracting heat energy from the output heat exchanger) can be obtained.

[0030]

[0031] The basic design parameters include: the time (T; in seconds) during which no heat energy needs to be extracted from the heat storage unit (or the minimum heat energy removal parameter within a specific time period), and the temperature difference between the cooling gas (T_chl) returned to the heat storage unit after heat energy is removed in the output heat exchanger and the highest possible temperature (T_max) in the gas gap and process area.

[0032]

[0033] Calculations show that when energy is uniformly extracted from the thermal storage device, the heat loss through the insulated shell of the heat exchanger is minimized (where the cooling gas exiting the heat exchanger keeps the temperature of the gas gap at a minimum). When heat extraction from the thermal storage device is interrupted, the temperature of the gas gap (and the total heat loss) will slowly increase with the temperature of the load-bearing inner shell. Therefore, interruptions in heat extraction lasting several hours, high non-uniformity of energy supply, and the charging state (average temperature) of the thermal storage device have limited impact on the total heat loss to the external environment. To minimize heat loss to the external environment, the key is to increase the thermal resistance of the insulated shell and maintain a regular extraction of heat energy. The longer the period of no energy extraction that the thermal storage device needs to maintain, the higher the required heat capacity per unit area of ​​the inner shell, or the higher the thermal resistance requirements of the insulated shell and the equipment in the process area.

[0034] The main advantages of the system described in this article are: • This system solves the problem of time mismatch between thermal and electrical energy supply and demand, has lower requirements for expensive materials, and is easier to achieve lower heat loss, thereby improving efficiency.

[0035] • The storage of high-temperature energy and the continuous power supply of high-temperature gas medium enable thermal energy storage technology to be applied to areas that were previously impossible.

[0036] • The high-temperature characteristics make it more efficient to convert energy (on demand) to other forms (such as using gas turbines, heat engines or thermoelectric generators to convert it into electrical energy).

[0037] • High temperatures are technically easier to achieve, enabling energy storage devices to reach high energy storage densities at lower costs. For example, using silicate refractory materials (such as basalt with a spacing parameter of 0.46 and a temperature difference of 800K), the thermal storage device can achieve a heat capacity of 1.27 GJ / m³, equivalent to 120 to 180 kWh of electricity generated when a heat engine achieves a thermal energy conversion efficiency of 35% to 50% (the highest efficiency can be achieved in a steam power plant using a combination of gas turbines and steam turbines).

[0038] • The internal airflow system ensures the recovery of heat lost through the refractory insulation. The heat loss from the outer shell of the thermal storage unit to the external environment is low, and its temperature depends on the temperature of the thermal storage unit after cooling.

[0039] • No toxic or chemically active liquid substances are used, so it will neither harm the environment nor increase operational risks.

[0040] • Both the storage materials and the storage casing are made from materials that are already mass-produced in road and building engineering.

[0041] In terms of bulk supply and price, common natural and artificial bulk materials are applicable. Through optimized calculations, after determining the economic and physical parameters of locally available materials, suitable particle size, dimensions, porosity, and surface density can be determined. The size and shape of the thermal storage device are also key influencing factors. For optimal thermal storage, the ideal shape is a cylinder or a three-dimensional structure with vertical / near-vertical walls, with a planar cross-section of square, circular, elliptical, or regular polyhedron (five or more faces). Generally, the surface area to volume ratio should be minimized to achieve higher efficiency with larger storage volumes. The potential energy stored and recovered depends directly on the base area of ​​the thermal storage device, and indirectly on its height.

[0042] The parameters of the storage device primarily depend on the physical parameters of the solid particles (bulk refractory material) filling its high-temperature storage space. Among natural materials, microcrystalline leachable rocks are suitable, requiring minimal alkali content (Na₂O, K₂O), high strength, and heat resistance; these mainly include basalt, andesite, and dacite. The suitability of specific materials needs to be evaluated through thermal cycling resistance testing. For smaller thermal storage devices, high-temperature sintered artificial aggregates similar to ceramics are particularly suitable, and blast furnace slag is also applicable.

[0043] Besides its own mass and heat capacity, a bulk solid material must also possess a significant proportion of gaps to allow gas to flow between the solids, thereby ensuring ideal storage parameters. This condition is best achieved by having a narrow solid composition range, no fine powder or dust components, and high sphericity (approximately spherical). The roundness of particle edges has no significant positive or negative impact on the physical parameters of the thermal storage device. Sharp or only slightly rounded edges increase specific surface area and spacing, thus improving parameters; however, on the other hand, they lengthen and bend the gas path between particles, producing the opposite effect. From the perspective of mechanical compressive strength and particle lifespan, higher edge roundness is more suitable. Particles with a microcrystalline structure have lower surface roughness, and their effect on pressure drop is usually negligible under slow laminar flow conditions. A larger heat transfer surface area (the surface area per unit volume or mass of solid particles—specific surface area) provides favorable parameters for heat transfer in the thermal storage device; this surface area mainly depends on the average particle size. While smaller particle sizes are beneficial for heat transfer, reducing particle size will lead to an increase in pressure drop.

[0044] Based on mathematical and physical analysis, the ratio of the total height of the storage space to the average particle size of the blocky refractory material should ideally be maintained within the range of 1:1500 to 1:6000. In conventional engineering practice, this corresponds to a medium particle size range of 0.5 mm to 20 mm, preferably 0.5 mm to 10 mm, with the maximum particle size difference not exceeding 5:1 (maximum particle size to minimum particle size) in specific applications. The basic parameter is the required thermal energy storage and extraction capacity calculated based on the floor area per square meter of the storage space. This parameter may vary significantly in thermal energy storage and recovery scenarios. Apart from the blower power, the maximum thermal energy storage / extraction capacity is primarily limited by the height of the steep thermal gradient region formed when gas flows through the storage space. This region can be defined as the area where 90% of the temperature change occurs as gas flows through the storage space. The height of the steep thermal gradient region is a core design parameter of the storage space compartment. Calculating this height requires mathematical and physical analysis of gas flow in the porous medium (material particle layer). Under otherwise identical conditions, this height increases with increasing gas flow rate, i.e., with increasing power.

[0045] An example of this dependence is shown in Figure 2—the increasing trend of the steep thermal gradient region height with varying flow rate. For thermal storage, the maximum extent of the steep thermal gradient region is half the height of the storage space. Typically, higher thermal storage efficiency is achieved when the power / flow ratio increases the ratio of the steep thermal gradient region height to the storage space height (e.g., 1:4, 1:5, 1:6, 1:7, or 1:8).

[0046] When it is necessary to improve the performance parameters of the storage area per unit area, the average particle size of the refractory material must be reduced to lower the height of the steep thermal gradient region. Figure 3An example illustrating this dependency is shown—as the average particle size of the bulk refractory decreases, the height of the steep thermal gradient region decreases accordingly.

[0047] The bidirectional gas drive of the thermal storage device will be provided by a blower system. Ideally, the blower system's power should be sufficient to compensate for pressure drop and maintain an economical proportion to the design heat output of the flowing gaseous medium within the thermal storage device. When the input heat energy is at least partially generated by electricity, a significantly higher flow rate (i.e., higher blower system performance) may be more advantageous during the thermal energy storage stage, as almost all the energy used for mechanical work during thermal energy storage is ultimately converted into stored heat energy. Regarding blower performance requirements, the interlayer flow velocity parameters should range from 0.01 to 1 m / s (i.e., 0.01 to 1 cubic meter of gas per second per square meter area), and the height of the storage space should be 10... 2至 10 4 The pressure drop of Pa / m meets the requirements of engineering practice.

[0048] The computational mathematical and physical modeling of thermal storage space must be highly reliable, which is a necessary condition for the feasibility of energy storage technology. The key parameters describing specific materials in the mathematical and physical model (such as pressure drop, heat transfer coefficient, and specific heat capacity) can be verified in the laboratory with a small sample of the material.

[0049] As the scale of thermal storage facilities expands, the importance of energy storage material costs (including processing and transportation expenses) will become increasingly prominent. For small energy storage sites with volumes in the tens of cubic meters, the ideal choice is to use blocky ceramic materials or artificially sintered particles (such as lightweight expanded clay particles labeled Liapor 4-8 / 600) with low thermal conductivity and low requirements for volume and weight. For large storage sites, the importance of thermal conductivity parameters will decrease, and inexpensive natural materials without post-heat treatment can be used efficiently. The overall performance of storage materials can also be optimized by mixing solid particles with similar particle sizes but different material parameters, or by layering particles of different materials to promote thermal stratification of the storage layer.

[0050] In reality, even particles made of highly resistant materials will experience surface damage and dust particle shedding under thermal cycling and the resulting volume changes. These dust particles accumulate in the channels between normal-sized particles and are entrained by the gas, especially as the gas flows downwards. During normal storage operation, the required peak input heat performance will be higher than the output heat performance, therefore the downward airflow rate in the high-temperature storage space will be higher than the upward rate. Therefore, after leaving the lower part of the high-temperature storage space, the gas must pass through a dust collector (ideally a cyclone separator equipped with a filter) to prevent dust from clogging the channels and heat exchangers. The heat recovery gas flows upwards, carrying only extremely fine dust particles and preventing deposition in the gas channel system. This airflow also recovers heat from the separator's filters (preferably equipped with a vibrator).

[0051] Particle erosion, especially in durable sintered ceramic materials, while slow, can permanently degrade the functional parameters of storage devices. Particle erosion leads to fouling and reduced cross-sectional area in interparticle channels, resulting in increased pressure drop and a decreased heat transfer coefficient due to reduced particle surface thermal conductivity. Therefore, the design of thermal storage devices must consider the possibility of a phased replacement of the entire refractory material within the high-temperature storage space. For large thermal storage tanks, a gradual reprocessing and replenishment process is more practical, eliminating the need to cool the entire tank and thus avoiding significant operational disruptions.

[0052] One specific embodiment of the present invention provides a solution for the gradual replacement of block refractory materials (filling high-temperature storage spaces). This solution aims to provide standardized and sustainable energy storage conditions. Erosion manifests as surface fragmentation, the size of which corresponds to the fineness of the material structure. Natural materials erode faster, and the separated dust particles are larger and less uniform than those of artificial ceramic materials (which are finer, more uniform, and have a denser sintered structure). It is generally considered that the reprocessing of block refractory materials can be achieved through impact (e.g., in a drum mixer) and sieving (e.g., on a slightly inclined vibrating screen). To reduce dust and noise and improve process quality, simultaneous water washing is recommended. Surface moisture and dust are removed from the material before it leaves the screen by airflow. During washing, the material is dried by slowly rotating rollers or further dried in a hopper by forced airflow with reduced humidity. Waste materials that are insufficient in strength and size are thus separated, while usable materials are cleaned of surface erosion, dust, and excess fine particles. The final product is an ideal fine-grained graded refractory material that can be reused. The reprocessed residue (i.e., "undersize") can be used in smaller or more efficient storage devices requiring finer particles, or for other purposes. Residual dust and crushed material can be further sorted and processed for use in ceramic material production, or to create new types of ceramic refractory sintering particles. This energy storage technology thus achieves extremely low environmental impact.

[0053] Theoretically, thermal storage devices can operate at temperatures exceeding the tolerance of traditional silicate refractory materials. However, this requires all high-temperature components of the thermal storage system to use materials with higher temperature resistance and to use an inert gas as the medium. Sufficiently robust forms of carbon or its compounds (such as carbides) can serve as the highest-temperature thermal storage material. Fiber felt or foam materials made of carbon fiber and graphite can serve as insulation layers, withstanding temperatures up to 3000℃. When the energy storage medium is heated above 1200℃, efficient heating can only be achieved through electrical energy, graphite resistance elements, carbon fiber resistance elements, or non-contact induction systems. Attached Figure Description

[0054] Figure 1 The diagram schematically shows a high-temperature thermal storage system (solid lines with arrows represent hot gas, dashed lines with arrows represent cooling gas, and dashed lines without arrows represent electrical wires).

[0055] Figure 2 This shows the increase in the height of the steep thermal gradient region as the flow rate increases (the top of the column represents the highest temperature, and the bottom of the column represents the lowest temperature).

[0056] Figure 3 This shows that as the average particle size of the blocky refractory material decreases, the height of the steep thermal gradient region decreases (the top of the column represents the highest temperature, and the bottom of the column represents the lowest temperature).

[0057] Figure 4 A functional diagram of the heat exchange circuit is shown (solid lines with arrows represent hot gas, and dashed lines with arrows represent cooling gas).

[0058] Figure 5 The distribution valve is shown schematically. Detailed Implementation

[0059] Design of high temperature thermal storage devices Figure 1 A high-temperature thermal energy storage device is shown, wherein thermal energy is stored through a solid block refractory material. In this embodiment, the high-temperature energy storage device includes an insulated space within an insulated outer shell 5. The insulated space within the insulated outer shell 5 is mainly filled by a load-bearing inner shell 3 and a high-temperature storage space 14. The load-bearing inner shell 3 is equipped with a high-temperature insulation layer 2. The top and sides of the high-temperature storage space 14 are surrounded by the load-bearing inner shell 3 with the high-temperature insulation layer 2, and the bottom is supported by a mesh with gas channels 14.7. A gas gap 4.1 is formed between the insulated outer shell 5 and the load-bearing inner shell 3, and preferably, a connecting gas channel 4.3 or an air channel 13.3 is also provided (see below for details).

[0060] The lower part of the insulated space inside the insulated outer shell 5 is filled with a maintenance area 22. Within the maintenance area 22, below the grid with gas passages 14.7, at least one hopper 21.1 and at least one dust collector 20.1 are provided. This maintenance area may also be equipped with a collection and conveying system 20 for separating dust and a conveying system 21 for collecting materials to be reprocessed. Preferably, the volume of the refractory material in the hopper 21.1 and the dust collector 20.1 is insulated from the rest of the maintenance area 22 by the insulation layer 5.2 of the maintenance area. The base structure of the high-temperature thermal storage tank preferably includes a base plate 3.1 supported on a load-bearing insulation layer 5.1 (e.g., foamed glass gravel) adjacent to the insulated outer shell 5.

[0061] Within the heat-insulating outer shell 5, at least one process area 4.2 can be arbitrarily arranged relative to the load-bearing inner shell 3, or set in an independent space, preferably located in the height direction of the maintenance area and / or adjacent to the load-bearing inner shell 3. Preferably, the independent process area 4.2 is connected to other parts of the heat-insulating space within the heat-insulating outer shell 5 via a coaxial heat input / output channel 7.3, wherein the high-temperature gas channel is located inside the low-temperature gas channel.

[0062] The high-temperature gas channel in the coaxial heat input / output channel 7.3 is connected to the hot gas channel 7, which penetrates the high-temperature insulation layer 2 and flows into the upper part of the high-temperature storage space 14 (entering the gas layer 14.6). The low-temperature gas channel in the coaxial heat input / output gas channel 7.3 is connected to the connecting gas channel 4.3, which penetrates between the insulation shell 5 and the load-bearing inner shell 3 and flows into the gas gap 4.1 at the cooling gas input / output gas channel 6. The cooling gas input / output gas channel 6 is always located above the high-temperature storage space 14, near the highest point of the gas gap 4.1. Therefore, preferably, the hot gas channel 7 and the connecting gas channel 4.3 can be coaxially arranged with the heat input / output gas channel 7.3 so that the connecting gas channel 4.3 surrounds the hot gas channel 7. When the bottom area of ​​the storage space is large, using multiple connecting gas channels 4.3 and hot gas channels 7 may be more advantageous.

[0063] Furthermore, process region 4.2 can be connected to at least one output heat exchanger 12. Preferably, the output heat exchanger 12 is connected via a coaxial heat output channel 7.2, wherein the high-temperature gas channel is located inside the low-temperature gas channel. Additionally, process region 4.2 can be connected to at least one input heat exchanger 11. Preferably, the input heat exchanger 11 is connected via a coaxial input-output channel 7.3.

[0064] The bottom side of the gas gap 4.1 is further connected to the maintenance area 22 and the air passage 13.3. The air passage 13.3 is connected to the insulated two-way valve 13, which is also connected to the safety input gas passage 13.2. The two-way valve 13 can be connected to the servo motor valve drive 15.3 via a magnetic coupling device 15.4.

[0065] The load-bearing inner shell 3 defines a high-temperature storage space 14 around the internal space of the heat storage device. Its material must possess sufficient density and load-bearing capacity to maintain the shape of the filled blocky storage space. Examples include monolithically cast concrete, tightly bonded precast concrete components, steel plates, ceramic components, dense and high-temperature resistant fiber composite boards, and combinations of the above materials. The load-bearing inner shell 3 also includes the load-bearing structure of the heat storage device and forms a secondary heat storage layer. On the inner side of the load-bearing inner shell 3, near the high-temperature storage space 14, a high-temperature insulation layer 2 is provided to define the high-temperature storage space 14, which is filled with blocky refractory material 1.

[0066] The base area and height of the high-temperature storage space 14 depend not only on the design capacity but also on a reasonable proportion that ensures the surface area of ​​the average thermal storage volume 14.4 is minimized, and on the appropriate height of the entire high-temperature storage space 14. This is because the height of the steep thermal gradient region 14.3 must be at least twice that of the average temperature difference in the cooling storage space 14 (optimally 4 to 8 times). This region is defined as the area where the temperature change of the flowing gas reaches 90% of the average temperature difference in the cooling storage space 14. The height of the steep thermal gradient region 14.3 increases with the gas flow rate ( Figure 2 ), and at the same flow rate, the decrease is due to the decrease in refractory particle size ( Figure 3 The height of the steep thermal gradient region 14.3 was calculated using the Ergun equation for porous flow and the heat distribution equation in the mathematical model. The recommended average particle size of the blocky refractory material 1 filling the high-temperature storage space 14 should be between 1 / 1500 and 1 / 6000 of its height, with a maximum particle size difference not exceeding 5:1 in specific applications.

[0067] In natural materials, bulk refractory materials can primarily be considered as microcrystalline leachable rocks with extremely low alkaline impurity content, such as basalt, andesite, and dacite. In man-made materials, high-density, spherical ceramic sintered aggregates are particularly suitable. For special applications above 1200℃, sufficiently robust carbon forms (such as pressed graphite spheroids coated with glassy carbon) or their carbides and nitrides can be selected. Even better overall performance can be achieved by mixing or layering particles of similar size but different material properties (such as bulk density and thermal conductivity).

[0068] High-temperature insulation layer 2 can employ a layered structure combining refractory and high-temperature insulation materials. Besides price differences, refractory materials exhibit significant variations in thermal resistance and insulation performance. The internal local temperature decreases from the inner to the outer surface of the insulation layer. Insulation materials that perform exceptionally well at high temperatures can cost several times more than those effective only at low temperatures. Therefore, it is recommended to divide the overall insulation layer into multiple operating temperature ranges, with each layer designed based on the calculated maximum local temperature, thereby optimizing the cost and thickness of the insulation layer. Microporous ceramic insulation materials (such as dense fumed silica mixtures containing silicon carbide or titanium dioxide, for example, PROMAT's FREEFLOW brand products) perform best at high temperatures. However, less expensive materials with slightly lower performance (such as expanded perlite and / or expanded vermiculite) may be more cost-effective.

[0069] Thermal insulation materials have low mechanical resistance; therefore, in practical thermal storage applications, they must be encased within pressure- and abrasion-resistant materials. Layered structures assembled from ground insulating ceramic bricks (such as POROTHERM products, with an outer layer of expanded perlite and an inner layer of microporous insulation material) are perfectly suited for temperature ranges of 500-1200°C. For smaller applications, a high-density surface layer can protect the lower-mechanical-strength high-temperature insulation material, such as heat-resistant metal plates (e.g., 1.4828 grade heat-resistant alloy stainless steel austenitic steel conforming to AISI 309 and CSN 17251 standards). Vacuum treatment of this layer can achieve even better insulation performance.

[0070] For the low-temperature working layer outside the high-temperature insulation layer (where the local temperature can reach 500-600°C), the use of mineral fiber and ceramic fiber materials (such as ISOVER brand ORSTECH 100 rock wool board) with significantly lower cost can effectively meet the requirements.

[0071] The thermal insulation shell 5 may include prefabricated components that are sealed to each other, and adopt a sandwich structure (shell-insulation core-shell), which is anchored to the load-bearing inner shell 3 by forming an air gap 4.1, such as an industrially produced metal plate-mineral wool-metal plate sandwich panel.

[0072] Preferably, at least one housing 8.1 for an electric heating element 8.2 is provided on the upper part of the high-temperature insulation layer 2. The lower part of the housing 8.1 is connected to the hot gas channel 7, and the upper part is connected to the gas layer 14. The housing 8.1 has an outlet on the outer surface of the insulation shell 5, and its internal space from the outlet to the inner surface of the high-temperature insulation layer 2 is filled with insulation material. At least one electric heating element 8.2 (e.g., resistor, induction heater) is disposed inside the housing 8.1 and connected to the power supply 8.

[0073] A blower system 10 is provided within process area 4.2. This blower system 10 includes a combination of at least two blowers, enabling gas flow between a single input gas heat exchange circuit 9.1 or 9.3 and a single output gas heat exchange circuit 9.2. Preferably, the blower system 10 also includes additional valves and blowers to achieve synchronous operation and interconnection of multiple heat exchange circuits. Preferably, the blower drive device 15.5 and the servo motor valve drive device 15.3 are located outside the heat-insulating housing 5.

[0074] heat exchange circuit The blower system 10 has at least one input heat exchange circuit and at least one output heat exchange circuit. Figure 4The blower system 10 provides airflow to the output heat exchange circuit 9.2 or the output heat exchange circuit 9.4 with an output temperature control device, and / or provides airflow to the input-dominant heat exchange circuit combination 9.5 and the output-dominant heat exchange circuit combination 9.6. Preferably, the blower system 10 can reduce the output temperature of the output heat exchanger 12 in the aforementioned combined heat exchange circuits (9.5 and 9.6). When all heat exchange circuits are operating, the electric heating element 8.2 can provide heat. A schematic diagram of the heat exchange circuits is shown below. Figure 4 As shown in a to 4f.

[0075] Input heat exchange circuit 9.1 ( Figure 4 a) The blower system 10 is connected in sequence on the intake side to the process area 4.2, the connecting gas channel 4.3, the cooling gas input / output channel 6, the gas gap 4.1, the dust collector 20.1, and the grid with gas channel 14.7 below the high-temperature storage space 14. On the outlet side, the blower system 10 is connected in sequence to the first output channel 10.1, the input heat exchanger 11, the first input channel 11.1, the hot gas channel 7, and the hot gas layer 14.6 above the high-temperature storage space 14. Preferably, the housing 8.1 with the electric heating element 8.2 is disposed between the end of the hot gas channel 7 and the hot gas layer 14.6.

[0076] Output heat exchange circuit 9.2 ( Figure 4 (b) indicates that the blower system 10 is sequentially connected on the intake side to the second input gas channel 10.2, the output heat exchanger 12, the second output channel 12.1, the high-temperature gas channel 7, and the hot gas layer 14.6 above the high-temperature storage space 14. Preferably, the housing 8.1 with the electric heating element 8.2 is disposed between the end of the hot gas channel 7 and the hot gas layer 14.6. On the outlet side, the blower system 10 is sequentially connected to the process area 4.2, the connecting gas channel 4.3, the cooling gas input / output channel 6, the gas gap 4.1, the dust collector 20.1, and the grid with the gas channel 14.7 below the high-temperature storage space 14.

[0077] 9.3 (with electrically heated input heat exchange circuit) Figure 4 c) indicates that the blower system 10 is sequentially connected on the intake side to the process area 4.2, the connecting gas passage 4.3, the cooling gas input / output passage 6, the gas gap 4.1, the dust collector 20.1, and the grid with the gas passage 14.7. On the outlet side, the blower system 10 is sequentially connected to the second connecting gas passage 10.3, the hot gas passage 7, the housing 8.1 with the electric heating element 8.2, and the hot gas layer 14.6 above the high-temperature storage space 14.

[0078] The remaining heat exchange circuits (9.4, 9.5, 9.6) only adopt the physical connection method of the above-mentioned input and output heat exchange circuits (9.1, 9.2, 9.3).

[0079] Additional functions and controls The distribution valve 16 is used for the outlet of the refilled block refractory material and is always located above the hot gas layer 14.6. When the bottom area of ​​the thermal storage tank is large, it is more advantageous to use multiple distribution valves 16.6. A vibrating plate 18 is installed in the hot gas layer 14.6 space of the lower part 17.6 of the inner shell of the distribution valve. This distribution valve includes an electrical control component consisting of a servo motor valve drive 15.3, a vibrator 15.8, and an electromagnetic coupler 17.7, which is connected to a thermal fuse 15.6. The internal structure and function of the distribution valve 16 are as follows... Figure 5 As shown, detailed descriptions are provided below. This distribution valve is connected to the block refractory material conveying system 19 via supply channel 19.3. When multiple distribution valves 16 are used, supply channel 19.3 extends from distributor 19.1 and ultimately connects to the block refractory material conveying system 19.

[0080] This exemplary high-temperature thermal storage system also includes a measurement and control system comprising a control unit 15.1 connected to a power supply 8, a blower system 10 driver 15.5 and a servo motor driver, an electromagnetic coupler 15.4 and a servo motor valve driver 15.3 via a thermal fuse 15.6, and then to the electric components of a distribution valve 16. The control unit is also connected to the servo motor valve driver 15.3 and a vibrator 15.8 via the thermal fuse 15.6, and then indirectly to the distribution valve's electromagnetic coupler 17.7. When multiple distribution valves 16 are used, the control unit is preferably also connected to a distributor servo motor driver 19.2, a block refractory material conveying system 19, and monitors the pressure drop of a dust collector 20.1 and controls its regeneration, controls a dust collection and conveying system 20, and controls a material collection and transporting system 21 for reprocessing materials.

[0081] Furthermore, the control unit 15.1 is connected to temperature sensors 15.2 disposed in the first output gas channel 10.1 and the first input gas channel 11.1, to temperature sensors 15.2 disposed in the second input gas channel 10.2 and the second output gas channel 12.1, and to temperature sensors 15.2 within the space of the cooling gas input / output channel 6. Preferably, the control unit is connected to temperature sensors 15.2 at the connection between the housing 8.1 and the gas layer 14.6, and to temperature sensors 15.2 at the connection between the housing 8.1 and the hot gas channel 7.

[0082] The control unit 15.1 is also connected to the accelerometer 15.9 in the distribution valve 16, and preferably also to the flow and differential pressure gauge 15.7 in the first output gas passage 10.1.

[0083] Operating principle of high temperature thermal storage system High-temperature thermal storage is achieved through a heat exchange circuit using gas as the working medium, such as... Figure 4 As shown in the schematic diagram, this heat exchange circuit is driven by a blower system 10. The operating temperature of the blower system 10 is determined by the temperature of the process zone 4.2, which in turn depends on the gas temperature in the second input gas channel 10.2 and the temperature of the gas gap 4.1.

[0084] The thermal storage system operates in at least two heat exchange loops, one transferring heat to the storage system and the other to the output gas. Output heat exchange loop 9.2 transfers heat from the storage device to the output heat exchanger 12. Heat transfer to the storage medium can be achieved through two heat exchange loops: input heat exchange loop 9.1 or an input heat exchange loop 9.3 with electric heating. The advantage is that the output temperature of the gas entering the output heat exchanger 12 can be reduced through heat exchange loop 9.4 with an output temperature control device. Another advantage is that the thermal storage system can simultaneously achieve multiple combinations of heat input and heat output modes; this function can be achieved through the combination of heat exchange loops 9.5.

[0085] When heat is supplied to the input heat exchanger 11 or power is simultaneously supplied to the electric heating element 8.2, the input heat exchange circuit 9.1 (which transfers heat to the gas flow through at least one input heat exchanger 11) is activated. The blower system 10 draws gas from the process area 4.2 and delivers it to the input heat exchanger 11 through the first output gas channel 10.1. Preferably, the first output gas channel 10.1 is connected to the first input gas channel 11.1 of the input heat exchanger 11 via a coaxial conduit in the form of a heat input device 7.1. The pressure gradient generated by the blower system 10 allows the gas to flow both through the high-temperature heat storage device and simultaneously into the input heat exchanger 11. The hot gas from the first input gas channel 11.1 flows into the hot gas channel 7 and can continue flowing through the shell 8.1 past the electric heating element 8.2—where the gas temperature will further increase when there is an active power supply. It then enters the hot gas layer 14.6 above the high-temperature storage space 14 and into the blocky refractory material 1 at the top of the heat storage chamber 14.4. After passing through the heat storage chamber 14.4, the gas enters the steep thermal gradient zone 14.3, where it transfers heat to the bulk refractory material 1. The gas continues to flow into the cooling storage chamber 14.5, and after passing through the cooling storage chamber 14.5 at its bottom, it flows into the grid of gas channels 14.7 provided around the load-bearing inner shell 3 of the high-temperature storage space 14. The gas gap 4.1 is connected to the process area 4.2 through the cooling gas input / output channel 6 and the connecting gas channel 4.3, thereby closing the gas flow loop.

[0086] When heating is required, the output heat exchange circuit 9.2 is activated, transferring heat to the gas flow through at least one output heat exchanger 12. The blower system 10 draws gas from the second input gas channel 10.2 and delivers it to the process area 4.2. Preferably, the second input gas channel 12.1 and the second output gas channel 10.2 of the output heat exchanger 12 merge via a coaxial channel (i.e., in the form of a heat output channel 7.2). The pressure gradient generated by the blower system 10 allows the gas to flow through both the high-temperature heat storage device and the output heat exchanger 12 simultaneously. After flowing into the process area 4.2 and the connecting gas channel 4.3, the cooling gas enters the gas gap 4.1 surrounding the load-bearing inner shell 3 through the cooling gas input / output channel 6. The cooling gas is preheated while surrounding the load-bearing inner shell 3, and then (in a counter-current manner without requiring a specific effect) passes through the dust collector 20.1, a grid with gas channels 14.7, and finally enters the blocky refractory material 1 at the bottom of the cooling accumulation solid 14.5. After passing through the cooling storage chamber 14.5, heat is absorbed from the bulk refractory material 1 in the steep thermal gradient region 14.3, and further enters the high-temperature gas layer 14.6 through the high-temperature storage chamber 14.4. Subsequently, it may pass through the shell 8.1, through the electric heating element 8.2, and enter the high-temperature gas channel 7 and the output gas channel 12.1. After passing through the output heat exchanger 12, the cooling gas returns through the second input gas channel 10.2, completing the cycle.

[0087] When power is supplied to the electric heating element 8.2, the input heat exchange circuit 9.3 (electrically driven) is activated, which transfers heat to the airflow through at least one electric heating element 8.2. The blower system 10 draws gas from the process area 4.2, delivers it to the hot gas channel 7 via the second connecting gas channel 10.3, then flows through the housing 8.1 surrounding the electric heating element 8.2, enters the high-temperature gas layer 14.6 above the high-temperature storage space 14, and finally injects it into the blocky refractory material 1 above the storage space 14. After passing through the high-temperature accumulation chamber 14.4, the gas enters the steep thermal gradient zone 14.3, where it transfers heat to the blocky refractory material 1. The gas continues to flow into the cooling accumulation chamber 14.5, and after passing through its bottom, flows through a grid with gas channels 14.7. The gas then flows through the dust collector 20.1 and enters the gas gap 4.1 around the load-bearing inner shell 3 of the high-temperature storage space 14. The gas gap 4.1 is connected to the process area 4.2 through the cooling gas input and output channel 6 and the connecting gas channel 4.3, thereby closing the gas flow loop.

[0088] Preferably, the storage device is also suitable for the following heat exchange circuit: The output heat exchange circuit 9.4, equipped with an output temperature control device, has the same heat transfer method to the air as the output heat exchange circuit 9.2, but also functions as the blower system 10. Preferably, the blower system 10 also needs to continuously control the gas flow rate in the process zone 4.2, and deliver it to the high-temperature gas channel 7 through the second connecting gas channel 10.3.

[0089] The heat exchange circuit combination 9.5 has the same airflow heat transfer method as the input heat exchange circuit 9.1 and the output heat exchange circuit 9.2, but also has the function of the blower system 10. Preferably, the blower system 10 should also have the following functions: continuous control of the airflow flowing into the first output channel 10.1; continuous control of the airflow from the second input channel 10.2; and continuous control of the airflow from the process area 4.2—which enters the high-temperature gas channel 7 via the second connecting gas channel 10.3.

[0090] Before entering the input heat exchanger 11, the cooling gas is preheated by bypassing the load-bearing inner shell 3, utilizing the heat energy entering the load-bearing inner shell 3 through the high-temperature insulation layer 2. The mass of the load-bearing inner shell 3 accumulates this heat energy within a finite time (this time is measured in units, at most tens of hours, determined by the temperature rise limit and the ratio of the heat capacity of the load-bearing inner shell to the heat flux of the high-temperature insulation layer), which is the maximum time limit for the interruption of the output heat exchanger 12. This time is determined by the ratio of the heat capacity of the load-bearing inner shell 3 to the heat transfer flux of the high-temperature insulation layer 2, as well as the limiting temperatures of the gas gap 4.1 and the process zone 4.2.

[0091] When the measurement and control system is operating normally, the inner side of the insulation housing 5, the gas gap 4.1, and the process area 4.2 are not exposed to extreme temperature environments, but are only affected by the temperature rise relative to the return cooling gas temperature of the output heat exchanger 12. The potential temperature rise of the process area 4.2 depends on the thermal resistance of the blower structure and the thermal resistance characteristics of the insulation housing 5. If the measurement and control system malfunctions or fails, the thermal fuse 15.6 will automatically cut off the power supply to the electromagnetic coupler 15.4 and the servo motor valve driver 15.3. The two-way valve 13 simultaneously opens the passage between the safety output gas passage 13.1 and the connecting gas passage 4.3, as well as the passage between the air passage 13.3 and the safety input gas passage 13.2. At this time, the hot gas in the gas gap 4.1 and the maintenance area 22 is discharged by gravity. The exhaust efficiency can be enhanced by the "chimney effect," specifically by extending the safety output gas passage 13.1 to a height higher than the insulation housing 5.

[0092] The control unit 15.1 will also handle the continuous assessment of pressure drop changes during gas flow within the high-temperature storage space 14. For this purpose, the control unit 15.1 will be connected to a flow and differential pressure gauge 15.7 to measure the pressure difference between the gas in the first output gas channel 10.1 and the gas in the process zone 4.2—when the input heat exchange circuit 9.1 is operating, or when the input heat exchange circuit 9.3 is electrically heated—and the pressure difference between the gas in the second connecting channel 10.3 and the gas in the process zone 4.2.

[0093] Refractory material treatment When a pressure drop exceeding the normal range is detected, the system will issue a replacement (reprocessing) request signal for the bulk refractory material 1. The replacement operation will be initiated through the collection and conveying system 21 for the block refractory material under at least one hopper 21.1. For large storage areas, it is recommended to design multiple hoppers 21.1, ensuring that the inclined walls of the hoppers 21.1 have sufficient slope to avoid excessively increasing the height required for the maintenance area. When the block refractory material 1 is uniformly removed, the material will sink evenly through the grid with gas channels 14.7 to the entire cross-section of the high-temperature storage space 14, thereby increasing the height of the hot gas layer 14.6.

[0094] Figure 5The distribution valve 16 and its working principle are described. A vibrating plate 18, installed in the lower part 17.6 of the internal main body of the distribution valve (within the hot gas layer 14.6), enables uniform distribution of bulk refractory material particles around the distribution valve 16. The vibrating plate 18 tilts slightly from the inlet of the distribution valve 16 towards the edge, thus ensuring uniform distribution of particles across its entire surface until the pores are filled. Particles cannot remain at the inlet of the distribution valve 16 until the space around the vibrating plate 18 is almost completely filled. The eccentricity of the vibrating plate, measured by the accelerometer 15.9, reflects the degree of contact between the vibrating plate and the bulk refractory material particles. Eccentric vibration refers to the extreme range of the vibrating plate's movement; that is, under constant excitation energy, as the number of particles in contact with the vibrating plate increases, the acceleration value of the vibrating plate's mass gradually decreases during vibration. When the contact rate between the particles and the vibrating plate 18 is high, the eccentricity of the vibrating plate 18 decreases, indicating that the high-temperature storage space 14 is filled. The vibrating plate 18 must be made of refractory material suitable for its operating temperature and mechanical load.

[0095] The bulk refractory material 1 to be reprocessed can be conveyed to at least one distribution valve 16 through the bulk refractory conveying system 19 and the feeding channel 19.3 with a sufficient slope, so that the particles can move freely by gravity or vibration. When the system is equipped with multiple distribution valves 16, the bulk refractory material conveying system 19 will be equipped with a distributor 19.1, whose servo motor driver 19.2 is responsible for controlling the distribution of particles to each distribution valve 16.

[0096] Specifically, during the operation of the input heat exchange circuit 9.1, i.e., during the storage of thermal energy in the heat storage device, the gas flow may be entrained by detached dust particles. This is due to the erosive effect caused by drastic temperature changes and the resulting changes in particle size. The airflow flowing through the blocky refractory material 1 will terminate at the bottom of the high-temperature storage space 14 through a mesh with gas channels 14.7. The gas will then be directed to at least one dust collector 20.1 before entering the gas gap 4.1. The dust collector 20.1 should preferably be a cyclone separator design to ensure maximum uniformity and minimum pressure drop. To capture extremely fine particles, the cyclone dust collector 20.1 may be additionally equipped with a recyclable filter cartridge and a differential pressure sensor 20.2, which is connected to the control unit 15.1. (When the operation of the output heat exchange circuit 9.2 causes a reduction in backflow, efficient filter cartridge recovery can be achieved by adding a vibration device and starting its operation).

[0097] Maintenance area 22 is located below the high-temperature storage space. This area is used for the maintenance or repair of the dust collection and conveying system 20, at least one dust separator 20.1, and the collection and conveying system 21 for materials to be reprocessed. For larger floor plans, an automated collection and conveying system is recommended, requiring only occasional maintenance. Preferably, maintenance area 22 comprises a space within the insulated housing 5. During normal operation of the thermal storage device, the temperature within maintenance area 22 may reach levels prohibiting direct human operation. During maintenance work, the temperature of this space must be reduced to a permissible range for human operation. This is achieved by opening a two-way valve 13, which can both release cooling gases (whose temperature may exceed human tolerance) and introduce ambient air if necessary. To maintain a suitable operating temperature, preferably, the ceiling of maintenance area 22 uses the same insulation material as maintenance area 5.2.

[0098] Distribution valve function Figure 5 The structure and operating position of the distribution valve are schematically illustrated. The exemplary setup describes the process of adding blocky refractory material 1 to the high-temperature gas layer 14.6 above the high-temperature storage space 14 at operating temperature. This exemplary solution prevents heat transfer and ensures the safety of the valve when it enters a high-temperature region. An electromechanical system is employed in the example embodiment of the distribution valve 16. If more distribution valves 16 are required, a hydraulic system can be used to achieve similar functionality.

[0099] The distribution valve 16 includes a cylindrical distribution valve housing 17 with a vertical axis and a supply channel 19.3 at its upper end. Inside the cylindrical distribution valve housing 17, a servo motor drive housing 17.2 with a small outer diameter (at least 6 times the particle diameter) is disposed. The upper part 17.3 of the internal body of the distribution valve moves within this housing via a spring hinge 17.8. The movable portion of the main shut-off element 17.4 of the distribution valve is externally connected to the upper part 17.3 of the internal body of the distribution valve. This component fills the space between the distribution valve housing 17 and the servo motor drive housing 17.2 when closed (upper position). The upper part 17.3 of the internal body of the distribution valve is separated from the lower part 17.6 of the internal body of the distribution valve by a damper 17.5 located below the connection point of the main shut-off element 17.4. The lower part 17.6 of the internal body of the distribution valve has a tapered cross-section, with a wide horizontal base at the bottom and a narrow section at the top connecting the vibration damper 17.5. It is made of solid heat-insulating material (such as porous ceramic). The vibrator 15.8 and the accelerometer 15.9 are mounted at the upper end of the lower part 17.6 of the internal body of the distribution valve, where the thermal effects are minimal.

[0100] The distribution valve housing 17 transitions into a distribution valve insulation housing 17.1 at the bottom, extending along the outer surface of the lower part 17.6 of the distribution valve's internal body. The distribution valve insulation housing 17.1 penetrates the insulation outer shell 5, the gas gap 4.1, the load-bearing inner shell 3, and the high-temperature insulation layer 2. At each layer height of the high-temperature insulation layer 2, sealing insulation material rings are embedded in the grooves of the distribution valve insulation housing 17.1. At the height of the gas gap 4.1, the distribution valve insulation housing 17.1 has a through hole connecting the gas gap 4.1 to the sealing gap formed at the middle position 16.2 of the distribution valve and the open distribution valve 16.3. The opening size is just large enough that the pressure difference generated by the operation of the heat exchanger output circuit 9.2 during operation, which guides the cooling gas from the gas gap 4.1 into the hot gas layer 14.6, is sufficient to block the diffusion of heat to the top of the distribution valve 16. The spring hinge 17.8 applies sufficient force to the upper part 17.3 of the inner body of the distribution valve and the lower part 17.6 of the inner body of the distribution valve connected to the vibrating plate 18 to counteract their combined weight, while applying sufficient sealing pressure to the heat insulation housing 17.1 of the distribution valve.

[0101] The distribution valve 16 functions through the vertical movement of the lower part 17.6 of its internal body and other closely connected components, particularly the main shut-off element 17.4, the upper part 17.3 of the internal body, the vibration damper 17.5, the vibrator 15.8, and the accelerometer 15.9. This vertical movement is achieved by the servo motor valve driver 15.3, the feed brake 17.9, and the spring hinge 17.8.

[0102] The distribution valve 16 has three operating positions. In the first position—the closed distribution valve 16.1—the lower part 17.6 of the internal body of the distribution valve engages with the seal inside the insulating housing 17.1 of the distribution valve, and the main shut-off element 17.4 of the distribution valve is in the closed state. The closure of the main shut-off element 17.4 of the distribution valve does not need to be a complete seal, but only needs to restrict the movement of particles in the block refractory material 1.

[0103] In the middle position 16.2 (second operating position) of the distribution valve, there is a gap between the lower part 17.6 of the inner body of the distribution valve and the insulating shell of the distribution valve, which allows the particles of block refractory material 1 to pass freely with a margin, but prevents them from passing through the main shut-off element 17.4 of the distribution valve.

[0104] In the third position—the open distribution valve 16.3—the main shut-off element 17.4 of the distribution valve is simultaneously opened, and the particles of the blocky refractory material 1 fall into the high-temperature gas layer 14.6 through the distribution valve 16.

[0105] The design of the servo motor-driven valve actuation phase 15.3 ensures that, in the event of a power outage (even in the event of a random emergency), external force will close the valve by cutting off the power to the distribution valve electromagnetic coupler 16.4. During the intermediate position 16.2 of the distribution valve until the gap between the distribution valve insulating housing 17.1 and the lower part 17.6 of the distribution valve's internal body narrows to below the particle size of the blocky refractory material 1, the valve closing time should be long enough to allow particles to pass through the primary shut-off element 17.4. When the high-temperature gas layer 14.6 has sufficient clearance, particles of the blocky refractory material 1 will not be trapped inside the distribution valve 16. The inlet opening size of the feed channel 19.3 leading to the distribution valve 16 is just large enough to prevent blockage of the distribution valve 16.3 when it is open.

[0106] In the schematic design of the distribution valve 16, an adjustable closing speed is ensured by a combination of a hydrodynamically powered brake 17.9 and a spring hinge 17.8. Even if the internal temperature of the distribution valve housing 17 exceeds the design limit, the valve will still close when the thermal fuse 15.6 is activated to cut off the power. After the distribution valve electromagnetic coupler 16.4 is disconnected, the drive unit separates from the upper part 17.3 of the distribution valve's internal body, achieving slow closing under the fixed setting of the feed brake 17.9. The vibration damper 17.5 isolates the static part of the valve from the vibration zone of the lower part 17.6 of the distribution valve's internal body.

[0107] Industrial applicability High-temperature thermal storage devices are suitable for transferring heat from gaseous media that remain stable and chemically inert at high temperatures, such as nitrogen or air. The thermal energy can be stored in blocky refractory materials.

[0108] List of reference numerals 1 block refractory material 2 High-temperature insulation layer 3. Load-bearing inner shell 3.1Substrate 4.1 Gas gap 4.2 Process Area 4.3 Connecting Gas Channels 5. Insulated outer shell 5.1 Load-bearing insulation layer 5.2 Maintenance of the insulation layer in area 22 6 Cooling gas input and output channels 7 hot gas channels 7.1 Hot Input Channel 7.2 Heat Output Channel 7.3 Hot Input / Output Channels 8 power supplies 8.1 Housing 8.2 Electric heating element 9.1 Input heat exchange circuit 9.2 Output heat exchange circuit 9.3 Input heat exchange circuit with electric heating device 9.4 Output heat exchange circuit with output temperature control device 9.5 Heat exchange circuit assembly 10 Blower System 10.1 First gas output channel 10.2 Second Input Gas Channel 10.3 Second connecting gas channel 11 Input Gas Heat Exchanger 11.1 First Input Gas Channel 12-output heat exchanger 12.1 Second Output Gas Channel 13 Two-way ventilation valve 13.1 Safe gas output channel 13.2 Safe gas input channel 13.3 Air passage 14 High-temperature storage space 14.1 Hot gas flow 14.2 Cooling Gas Flow 14.3 Steep thermal gradient region 14.4 Heat Storage Chamber 14.5 Cooling Accumulation Chamber 14.6 Thermal Gas Layer 14.7 Grid with gas channels 15.1 Control Unit 15.2 Temperature Sensor 15.3 Servo motor valve drive 15.4 Electromagnetic Coupler 15.5 drive 15.6 Thermal fuse 15.7 Flow and Differential Pressure Gauges 15.8 Vibrator 15.9 Accelerometer 16-way distribution valve 16.1 Closed distribution valve 16.2 The middle position of the distribution valve 16.3 Opening of the distribution valve 17 Distributor Valve Housing 17.1 Distribution valve heat insulation housing 17.2 Servo Motor Drive Housing 17.3 Upper part of the internal body of the distribution valve 17.4 Main shut-off element of the distribution valve 17.5 Vibration Damper 17.6 Lower part of the internal body of the distribution valve 17.7 Electromagnetic Coupler for Distribution Valve 17.8 Spring Hinge 17.9 Feed brake 18 Vibrating Plate 19 Block Refractory Material Conveying System 19.1 Distributor 19.2 Distributor Servo Motor Driver 19.3 Feeding Channel 20. Dust collection and conveying system 20.1 Dust Collector 20.2 Differential pressure sensor 21 Collection and conveying system for materials awaiting reprocessing 21.1 Hopper 22 Maintenance Area

Claims

1. A system for storing and transferring heat, comprising: a. At least one heat source for generating heat energy; b. A high-temperature thermal energy storage device having a blocky refractory material (1) filled in a high-temperature storage space (14) for storing the generated thermal energy; c. At least one heat dissipation system for utilizing the stored thermal energy; as well as d. A heat transfer mechanism for transferring the heat energy from the heat source to the high-temperature heat storage device and from the high-temperature heat storage device to the heat consumption system, wherein the heat transfer mechanism is a closed gas loop connecting the heat source, the high-temperature heat storage device and the heat consumption system, and the high-temperature heat storage device is partially enclosed in a load-bearing inner shell (3). The blocky refractory material (1) is characterized in that it comprises a granular portion with a sphericity ranging from 0.4 to 1 and an average particle size ranging from 0.5 mm to 20 mm, and the volume ratio of the largest particle to the smallest particle does not exceed 5:

1. The load-bearing inner shell (3) is enclosed by an insulating outer shell (5) so that a gas gap (4.1) is formed between the load-bearing inner shell (3) and the insulating outer shell (5) for recovering heat loss from the high-temperature heat storage device through the load-bearing inner shell (3). The gas gap (4.1) and the connecting gas channel (4.3) connect the high-temperature heat storage device to at least one process area (4.2), which is also connected to at least one heat consumption system. A hot gas channel (7) connects the high-temperature heat storage device to at least one heat source.

2. The system according to claim 1, characterized in that, The load-bearing inner shell (3) has a high-temperature insulation layer (2) on the side close to the high-temperature storage space (14).

3. The system according to any one of the preceding claims, characterized in that, The heat source is an input heat exchanger (11), and a blower system (10) is provided in the process area (4.2) for conducting cooling gas from the high-temperature storage space (14) through the gas gap (4.1), the connecting gas channel (4.3), the process area (4.2), and the first output gas channel (10.1) to at least one input heat exchanger (11); wherein, in order to conduct the hot gas from the input heat exchanger (11), at least one hot gas channel (7) is provided for transferring the hot gas from the input heat exchanger (11) to the gas layer (14.6) above the high-temperature storage space (14). And / or, characterized in that, the heat source is at least one electric heating element (8.2), the blower system (10) is provided in the process area (4.2) for conducting the cooling gas from the high-temperature storage space (14) through the gas gap (4.1), the connecting gas channel (4.3) and the process area (4.2) to the second connecting gas channel (10.3) and the hot gas channel (7), the hot gas channel (7) is also in thermal contact with the electric heating element (8.2) for heating the gas to the gas layer (14.6) above the high-temperature storage space (14), wherein the electric heating element (8.2) is disposed inside the load-bearing inner shell (3) and outside the high-temperature storage space (14), preferably, inside the hot gas channel (7); Furthermore, the heat transfer mechanism is an output heat exchanger (12), and the blower system (10) is provided in the process area (4.2) for conducting the cooling gas from the output heat exchanger (12) through the second input gas channel (10.2), the process area (4.2), the connecting gas channel (4.3) and the gas gap (4.1) to the high-temperature storage space (14). The high-temperature storage space (14) transports the hot gas from the gas layer (14.6) above it to at least one output heat exchanger (12) through at least one hot gas channel (7).

4. The system according to any one of the preceding claims, characterized in that, The first input gas channel (11.1) is coaxially arranged with the first output gas channel (10.1) such that the first output gas channel (10.1) surrounds the first input gas channel (11.1); and / or, the second input gas channel (10.2) is coaxially arranged with the second output gas channel (12.1) such that the second input gas channel (10.2) surrounds the second output gas channel (12.1); and / or, the connecting gas channel (4.3) is coaxially arranged with the hot gas channel (7) such that the connecting gas channel (4.3) surrounds the hot gas channel (7).

5. The system according to any one of the preceding claims, characterized in that, The gas gap (4.1) is connected to the two-way valve (13) through the air passage (13.3), wherein the two-way valve (13) is also connected to the external environment through the safety input gas passage (13.2) and the safety output gas passage (13.1).

6. The system according to any one of the preceding claims, characterized in that, The blocky refractory material (1) is selected from any one of the following groups: basalt, andesite, dacite, artificial sintered particles, ceramic materials, blast furnace slag, compressed graphite with glassy carbon coating, carbides and nitrides.

7. The system according to any one of the preceding claims, characterized in that, Temperature sensors (15.2) are disposed in the first input gas channel (11.1), the first output gas channel (10.1), the second input gas channel (10.2), the second output gas channel (12.1), the space of the cooling gas input / output channel (6), the space where the housing (8.1) of the electric heating element (8.2) connects to the gas layer (14.6) above the high-temperature storage space (14), and the space upstream of the inlet of the housing (8.1) of the hot gas channel (7), wherein each temperature sensor (15.2) is connected to the control unit (15.1).

8. The system according to any one of the preceding claims, characterized in that, Below the high-temperature storage space (14) is a maintenance area (22) for accommodating a collection and conveying system (20) for separating dust and / or a collection and conveying system (21) for accommodating materials to be reprocessed.

9. The system according to any one of the preceding claims, characterized in that, At least one distribution valve (16) for inputting block refractory material (1) at the operating temperature of the high-temperature thermal storage space (14) is introduced into the gas layer (14.6) above the high-temperature thermal storage space (14).

10. The system according to any one of the preceding claims, characterized in that, The average particle size ranges from 0.5 mm to 20 mm, and the ratio of the average particle size of the blocky refractory material (1) to the total height of the high-temperature storage space (14) ranges from 1:1500 to 1:6000.

11. A method for storing and transferring heat using the system of any one of the preceding claims, wherein a high-temperature heat storage device is partially enclosed within a load-bearing inner shell (3), the load-bearing inner shell (3) being enclosed by a heat-insulating outer shell (5), such that a gas gap (4.1) is formed between the load-bearing inner shell (3) and the heat-insulating outer shell (5); The method includes the following heat storage steps: a. To generate thermal energy in at least one heat source to form a hot gas; b. The hot gas is transferred from the heat source to the high-temperature heat storage device through a closed gas loop as a heat transfer system; c. Using the blocky refractory material (1) included in the high-temperature storage space (14), the thermal energy generated by the hot gas is stored in the high-temperature heat storage device to form a cooling gas; d. The cooling gas is transferred from the high-temperature thermal storage device to the heat source via the closed gas loop as a heat transfer system; and e. Optionally, repeat steps a through d; in, The method further includes the following heat dissipation storage steps: f. The cooling gas is transferred from the heat dissipation system to the high-temperature heat storage device through the closed gas loop as the heat transfer system; g. Obtaining stored thermal energy from the high-temperature thermal storage device to form hot gas, the high-temperature thermal storage device having a blocky refractory material (1) included in the high-temperature storage space (14). h. Transferring the hot gas from the high-temperature thermal storage device to the heat dissipation system via the closed gas loop as the heat transfer system; and i. Consuming the thermal energy stored in the thermal gas in at least one heat-consuming system; The blocky refractory material (1) is characterized in that it comprises a granular portion with a sphericity ranging from 0.4 to 1 and an average particle size ranging from 0.5 to 20 mm, wherein the volume ratio of the largest particle to the smallest particle is at most 5:

1. In steps d and f, the heat loss from the high-temperature heat storage device caused by heat transfer through the load-bearing inner shell (3) enclosing the high-temperature heat storage device is recovered by guiding cooling gas to the gas gap (4.1) provided between the load-bearing inner shell (3) and the heat-insulating outer shell (5) enclosing the load-bearing inner shell (3).

Images