Fluidized heat storage and release system based on solid particles

Abstract

The invention provides a fluidized heat storage and release system based on solid particles. The fluidized heat storage and release system can be applied to the technical field of heat storage and release. The fluidized heat storage and release system based on the solid particles comprises a lifting chamber, a heating tank, a heat storage tank and a heat release tank. Wherein the lifting chamber is used for lifting a gas-solid mixture at a first temperature from the heat release tank upwards, and the gas-solid mixture comprises circulating solid particles and circulating gas; the heating tank is used for heating the first temperature circulating solid particles separated from the gas-solid mixture by using a heat source outside the system to obtain second temperature circulating solid particles; the heat storage tank is used for receiving and storing the circulating solid particles at the second temperature; the heat release tank is used for heating water fed from the outside of the system by using the heat of the circulating solid particles at the second temperature to obtain superheated steam, and the circulating solid particles at the second temperature generate circulating solid particles at the third temperature after releasing the heat; and the circulating solid particles at the third temperature are mixed with the fluidizing air introduced into the heat release tank to obtain a gas-solid mixture at the first temperature, and the gas-solid mixture is fed into the lifting chamber.

Description

Technical Field

[0001] This disclosure relates to the field of thermal energy storage and release technology, specifically to a fluidized thermal energy storage and release system based on solid particles. Background Technology

[0002] Thermal energy storage technology, as a key support for energy transition, plays a crucial role in areas such as flexible retrofitting of coal-fired power plants, renewable energy integration, industrial heating and waste heat recovery, concentrated solar power (CSP), multi-energy complementarity, and energy system optimization. It not only mitigates fluctuations in renewable energy sources but also provides necessary grid regulation services, enhancing system flexibility and reliability. With its advantages of long-term operation, flexibility, low cost, high safety, and long lifespan, thermal energy storage technology has become one of the key technologies for achieving efficient, low-carbon, and stable operation in the renewable energy sector. It demonstrates competitiveness in terms of economics, technological maturity, and environmental adaptability. Particularly in large-scale energy dispatch and grid stability, thermal energy storage technology provides a highly flexible, cost-effective, and reliable solution.

[0003] Traditional sensible heat storage technologies (such as molten salt and thermal storage bricks) suffer from problems such as high cost of storage materials, low storage temperature, narrow storage temperature range, low heat exchange efficiency, and high operation and maintenance costs. High-temperature solid particle thermal storage, as a novel sensible heat storage technology, uses inexpensive solid particles as the high-temperature storage medium. It offers advantages such as low cost, wide temperature range, high storage density, high reliability, long lifespan, and ease of scalability. This provides a strong impetus for developing large-capacity, low-cost, high-efficiency, long-life, and highly safe thermal energy storage equipment, thereby achieving a low-carbon energy transition. Summary of the Invention

[0004] In view of the above problems, this disclosure provides a fluidized thermal storage and release system based on solid particles that can improve thermal storage and release efficiency.

[0005] According to a first aspect of this disclosure, a fluidized bed heat storage and release system based on solid particles is provided, comprising: a lifting chamber, a heating tank, a heat storage tank, and a heat release tank; wherein, the lifting chamber is used to lift a gas-solid mixture originating from the heat release tank at a first temperature, the gas-solid mixture including circulating solid particles and circulating gas; the heating tank is used to heat the circulating solid particles separated from the gas-solid mixture at the first temperature using an external heat source to obtain circulating solid particles at a second temperature; the heat storage tank is used to receive and store the circulating solid particles at the second temperature; the heat release tank is used to heat water supplied from outside the system using the heat from the circulating solid particles at the second temperature to obtain superheated steam, wherein the circulating solid particles at the second temperature release heat to generate circulating solid particles at a third temperature, and the circulating solid particles at the third temperature are mixed with fluidizing air introduced into the heat release tank to obtain a gas-solid mixture at the first temperature which is then sent into the lifting chamber.

[0006] According to an embodiment of this disclosure, a gas-solid mixture is fed into the bottom of a lifting chamber; the lifting chamber is used to lift the gas-solid mixture at a first temperature to the top of the lifting chamber using fluidizing air fed from the bottom of the lifting chamber and flowing upward, so that a material circulation from bottom to top in the vertical direction is formed in the lifting chamber; a heating tank, a heat storage tank, and a heat release tank are distributed from top to bottom in the vertical direction and connected in sequence, so that the circulating solid particles can pass through the heating tank, the heat storage tank, and the heat release tank in sequence in the vertical direction under the action of gravity, forming a material circulation from top to bottom in the vertical direction.

[0007] According to embodiments of this disclosure, the lifting chamber uses a fluidized bed; the heating tank uses a moving bed; and the exothermic tank uses a bubbling bed.

[0008] According to embodiments of this disclosure, the heating tank includes a flue gas heating unit and / or an electric heating unit; the flue gas heating unit utilizes high-temperature flue gas or high-temperature exhaust gas from the furnace of an external boiler as a heat source.

[0009] According to embodiments of this disclosure, when the heating tank includes a flue gas heating unit and an electric heating unit: the flue gas heating unit is used to heat the circulating solid particles at a first temperature using the high-temperature flue gas in the furnace to obtain circulating solid particles at an intermediate temperature; the electric heating unit is used to continue heating the circulating solid particles at the intermediate temperature to obtain circulating solid particles at a second temperature.

[0010] According to embodiments of this disclosure, the numerical range of the first temperature is 250-350℃; the numerical range of the second temperature is 900-1000℃; the numerical range of the third temperature is 300-400℃; the numerical range of the intermediate temperature is 600-700℃; and the numerical range of the high-temperature flue gas in the furnace is 800-1100℃.

[0011] According to an embodiment of this disclosure, the exothermic tank includes a preheating chamber, an evaporation chamber, and a superheating chamber. Water supplied from outside the system flows through the preheating chamber to obtain preheated water, the preheated water flows through the evaporation chamber to obtain saturated water vapor, and the saturated water vapor flows through the superheating chamber to obtain superheated steam.

[0012] According to embodiments of this disclosure, the inlets of the preheating chamber, evaporation chamber, and superheating chamber are connected in parallel to the outlet of the heat storage tank, so that the preheating chamber, evaporation chamber, and superheating chamber simultaneously receive circulating solid particles at a second temperature; or, the inlet of the preheating chamber is connected to the outlet of the heat storage tank, and the preheating chamber, evaporation chamber, and superheating chamber are connected in series sequentially, so that the circulating solid particles at a second temperature pass through the preheating chamber, evaporation chamber, and superheating chamber in sequence.

[0013] According to an embodiment of the present disclosure, a separator is disposed between a lifting chamber and a heating tank for gas-solid separation of a gas-solid mixture to obtain circulating gas at a first temperature and circulating solid particles at a first temperature, and the circulating solid particles at the first temperature are fed into the heating tank through the solid phase outlet of the separator.

[0014] According to an embodiment of this disclosure, a cold particle heater is used to receive supplementary solid particles at an initial temperature supplied from outside the system, and to preheat the supplementary solid particles at the initial temperature using circulating gas at a first temperature originating from the gas phase outlet of the separator, to obtain supplementary solid particles at a fourth temperature, which are then fed into the lifting chamber; the initial temperature is consistent with the ambient temperature outside the system; the numerical range of the fourth temperature is 50-100°C.

[0015] According to an embodiment of this disclosure, after the circulating gas at the first temperature is cooled down by heat exchange with the supplementary solid particles at the initial temperature, a circulating gas at the fifth temperature is obtained; the numerical range of the fifth temperature is 150-250°C.

[0016] According to embodiments of this disclosure, a circulating fan is used to introduce circulating gas at a fifth temperature as fluidizing air into the lift chamber and the heat release tank.

[0017] According to an embodiment of this disclosure, a first air distribution device is provided at the bottom of the lifting chamber, the air supply direction of the first air distribution device is vertically upward, and the air chamber of the first air distribution device is connected to the outlet of the circulating fan; a second air distribution device is provided at the bottom of the heat release tank, the air supply direction of the second air distribution device is vertically upward, and the air chamber of the second air distribution device is connected to the outlet of the circulating fan.

[0018] According to embodiments of this disclosure, the recycled solid particles are at least one of quartz sand, ceramic particles, alumina microspheres, steel slag, and industrial waste.

[0019] According to embodiments of this disclosure, by using solid particles as the heat storage medium and a small amount of gas as the heat transfer medium, the system achieves high heat exchange efficiency. The excellent contact and heat transfer performance between solid particles and between the solid particles and the gas enable rapid heat transfer and storage. Simultaneously, the solid particles have a wide heat storage temperature range of 200℃ to 1000℃, meeting various industrial needs. Compared to molten salt heat storage, solid particles have a higher heat storage density and do not suffer from high-temperature decomposition, high-temperature corrosion, or low-temperature solidification, reducing system maintenance costs and safety risks. Furthermore, by constructing a circulating flow loop consisting of an lifting chamber, heating tank, heat storage tank, and heat release tank, and coordinating with combined air conditioning, the static heat exchange mode of solid heat storage is broken. The entire system allows the solid particles to circulate continuously, and fluidized heat exchange is achieved in the heat release tank through fluidized air, increasing the heat transfer coefficient and intensity, thereby achieving efficient and rapid heat storage and release. This solves the problems of low thermal efficiency, bulky equipment, and low power density in traditional systems, resulting in a more compact system structure and higher energy efficiency in heat storage and exchange. Attached Figure Description

[0020] The foregoing contents, as well as other objects, features, and advantages of this disclosure, will become clearer from the following description of embodiments with reference to the accompanying drawings, in which:

[0021] Figure 1 A schematic diagram of the structure of a fluidized thermal storage and release system based on solid particles according to an embodiment of the present disclosure is shown.

[0022] Figure 2A A schematic diagram of the structure of a heating tank according to a first embodiment of the present disclosure is shown.

[0023] Figure 2B A schematic diagram of the structure of a heating tank according to a second embodiment of the present disclosure is shown.

[0024] Figure 2C A schematic diagram of the structure of a heating tank according to a third embodiment of the present disclosure is shown.

[0025] Figure 3A and Figure 3B A schematic diagram of the structure of a heat-releasing vessel according to an embodiment of the present disclosure is shown.

[0026] Figure 4 A schematic diagram of the structure of a fluidized thermal storage and release system based on solid particles according to a second embodiment of the present disclosure is shown.

[0027] Figure 5 A schematic diagram of the structure of a fluidized thermal storage and release system based on solid particles according to a third embodiment of the present disclosure is shown.

[0028] Figure 6 A schematic diagram of the structure of a fluidized thermal storage and release system based on solid particles according to a fourth embodiment of the present disclosure is shown.

[0029] Figure 7 A schematic diagram of a fluidized thermal storage and release system based on solid particles according to a fifth embodiment of the present disclosure is shown. Detailed Implementation

[0030] The embodiments of the present disclosure will now be described with reference to the accompanying drawings. However, it should be understood that these descriptions are exemplary only and are not intended to limit the scope of the disclosure. In the following detailed description, numerous specific details are set forth to provide a thorough understanding of the embodiments of the present disclosure for ease of explanation. However, it will be apparent that one or more embodiments may be practiced without these specific details. Furthermore, descriptions of well-known structures and techniques are omitted in the following description to avoid unnecessarily obscuring the concepts of the present disclosure.

[0031] The terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit this disclosure. The terms “comprising,” “including,” etc., as used herein indicate the presence of the stated features, steps, operations, and / or components, but do not exclude the presence or addition of one or more other features, steps, operations, or components.

[0032] All terms used herein (including technical and scientific terms) have the meanings commonly understood by those skilled in the art, unless otherwise defined. It should be noted that the terms used herein are to be interpreted in a manner consistent with the context of this specification, and not in an idealized or overly rigid way.

[0033] When using expressions such as "at least one of A, B and C", they should generally be interpreted in accordance with the meaning that is commonly understood by those skilled in the art (e.g., "a system having at least one of A, B and C" should include, but is not limited to, a system having A alone, a system having B alone, a system having C alone, a system having A and B, a system having A and C, a system having B and C, and / or a system having A, B and C, etc.).

[0034] In sensible heat storage, molten salt storage is a common method. However, molten salt storage has several drawbacks. First, molten salt decomposes at high temperatures, producing harmful substances and causing high-temperature corrosion to storage equipment, while it easily solidifies at low temperatures, affecting the normal operation of the storage system. Second, molten salt materials are expensive, which puts significant economic pressure on the large-scale application of molten salt thermal energy storage technology. Furthermore, molten salt storage has a relatively narrow temperature range and low thermal density, meaning that a larger storage space is needed to store the same amount of heat energy, increasing investment costs. These problems restrict the further development and widespread application of molten salt thermal energy storage technology.

[0035] In the field of solid thermal energy storage, fixed-bed heat exchange is currently the primary method, with air or nitrogen as the heat transfer medium. Fixed-bed heat exchange suffers from low heat transfer efficiency. Due to the limited contact area and time between the solid and the gas, heat transfer is insufficient, hindering efficient storage and release of thermal energy. To achieve adequate heat storage and exchange, a large equipment footprint is often required, increasing investment costs and potentially limiting space availability. Furthermore, the high investment cost of fixed-bed heat exchange equipment, including equipment purchase, installation, and subsequent maintenance, significantly increases the overall cost of solid thermal energy storage technology.

[0036] Figure 1 A schematic diagram of the structure of a fluidized thermal storage and release system based on solid particles according to an embodiment of the present disclosure is shown.

[0037] like Figure 1As shown, the heat storage and release system of this embodiment includes a lifting chamber 1, a heating tank 3, a heat storage tank 4, and a heat release tank 5.

[0038] The lifting chamber 1 is used to lift the gas-solid mixture 15, which originates from the first temperature of the exothermic tank 5, upward. The gas-solid mixture 15 includes circulating solid particles and circulating gas.

[0039] The lifting chamber 1 may have multiple inlets, at least one of which is connected to the outlet of the gas-solid mixture 15 of the exothermic tank 5 to receive the gas-solid mixture 15 at a first temperature delivered from the outlet of the exothermic tank 5. It may also include an outlet as a feed inlet for solid particles, used for initial feeding or supplementary feeding during circulation. The first temperature is low throughout the heat storage and release system, for example, 200°C, 250°C, or 250~300°C. After receiving the gas-solid mixture 15 at the first temperature delivered from the outlet of the exothermic tank 5, the lifting chamber 1 connects to the feed inlet of the heating tank 3 via a pipe through the gas-solid outlet at the upper part of the chamber, so as to lift the gas-solid mixture 15 at the first temperature upwards and allow it to enter the gas-solid separation device 2 for gas-solid separation, obtaining circulating solid particles and circulating gas. The separated circulating solid particles then enter the heating tank 3 for heating. The heating tank 3 is used to heat the circulating solid particles separated from the gas-solid mixture 15 at the first temperature using an external heat source to obtain circulating solid particles at a second temperature.

[0040] The heating tank 3 has at least one inlet, which is connected to the solid phase outlet of the gas-solid separation device 2 via a pipe, for receiving circulating solid particles from the lifting chamber 1 at a first temperature. Furthermore, the heating tank 3 also needs to be connected to an external heat source to heat the circulating solid particles at the first temperature inside the tank, raising their temperature to a second temperature. This external heat source can be an electric heater, molten salt coil, high-temperature flue gas channel, etc. The second temperature is the second highest temperature in the entire heat storage and release system, second only to the external heat source, because it needs to be heated to a preset second temperature in the heating tank 3 for heat storage. The second temperature can be, for example, 900℃, 1100℃, or 900~1000℃. The bottom of the heating tank 3 also has an outlet, which is connected to the inlet of the heat storage tank 4 via a pipe, for conveying the heated circulating solid particles at the second temperature to the heat storage tank 4 for storage. Furthermore, a first control valve 34 can be installed on the connecting pipeline. This first control valve 34 is used to regulate the flow rate of circulating solid particles at the second temperature delivered from the heating tank 3 to the heat storage tank 4, thereby controlling the amount of solid particles entering the storage stage to adapt to different upstream heating powers or meet different heat storage requirements of the system. The first control valve 34 can be a mechanical regulating valve.

[0041] Thermal storage tank 4 is used to receive and store circulating solid particles at a second temperature.

[0042] The heat storage tank 4 has at least one inlet, which is connected to the outlet at the bottom of the heating tank 3 via a pipe, for receiving circulating solid particles at a second temperature from the heating tank 3. The tank body of the heat storage tank 4 is made of high-temperature resistant insulation material to ensure good heat preservation performance, reduce heat loss, and achieve long-term stable storage of high-temperature solid particles. The bottom of the heat storage tank 4 also has an outlet, which is connected to the inlet of the exothermic tank 5 via a pipe. A second control valve 45 can be installed on this pipe to control and regulate the flow rate of the circulating solid particles at the second temperature entering the exothermic tank 5 from the heat storage tank 4 when the system needs to release heat. The second control valve 45 can be a mechanical regulating valve.

[0043] The exothermic tank 5 is used to heat water supplied from outside the system to obtain superheated steam by utilizing the heat of circulating solid particles at a second temperature. The circulating solid particles at the second temperature release heat to generate circulating solid particles at a third temperature. The circulating solid particles at the third temperature are mixed with fluidizing air introduced into the exothermic tank to obtain a gas-solid mixture at a first temperature, which is then sent into the lifting chamber 1.

[0044] The exothermic tank 5 may have at least one inlet, which is connected to the outlet at the bottom of the heat storage tank 4 via a pipe, for receiving circulating solid particles at a second temperature from the heat storage tank 4. The exothermic tank 5 also contains a heat exchange device, such as a buried tube heat exchanger. The inlet of the heat exchanger is connected to an external water supply pipeline for introducing ambient or low-temperature water; the steam outlet of the heat exchanger is used to output superheated steam to the outside of the system. Furthermore, the circulating solid particles at the second temperature flow within the exothermic tank 5, indirectly exchanging heat with the heat exchange device, transferring their heat to the water inside the tubes, thereby generating superheated steam; the solid particles themselves are cooled, and their temperature drops to a third temperature. The circulating solid particles at the third temperature can be 300~400℃.

[0045] The bottom of the exothermic tank 5 is also provided with a fluidizing air inlet for introducing fluidizing air supplied from outside the system. The fluidizing air mixes with the circulating solid particles at the third temperature in the lower part of the tank to form a fluidized gas-solid mixture 15 at the first temperature. The bottom of the exothermic tank 5 is also provided with a mixture outlet, which is connected to the bottom inlet of the riser chamber 1 through a pipe to send the gas-solid mixture 15 at the first temperature back to the riser chamber 1, thereby completing the entire cycle.

[0046] The number of heat exchange chambers within the heat exchange tank 5 can be set according to actual needs. For example, for a large-scale heat storage and release system, three heat exchange chambers can be set. The heating surface in each heat exchange chamber adopts the form of spiral coils or U-shaped tubes to increase the contact time and area between the high-temperature solid particles and the working fluid. The water or steam working fluid flowing inside the tubes is determined according to the actual application scenario. For example, high-pressure steam can be used for power generation. This disclosure only illustrates the number of heat exchange chambers by way of example, and is not actually limited to this.

[0047] The pipes in this system are all made of high-temperature and corrosion-resistant alloy materials, such as chromium-nickel alloy steel, to adapt to the environment of high-temperature flue gas.

[0048] According to embodiments of this disclosure, by using solid particles as the heat storage medium and a small amount of gas as the heat transfer medium, the system achieves high heat exchange efficiency. The excellent contact and heat transfer performance between solid particles and between the solid particles and the gas enable rapid heat transfer and storage. Simultaneously, the solid particles have a wide heat storage temperature range of 200℃ to 1000℃, meeting various industrial needs. Compared to molten salt heat storage, solid particles have a higher heat storage density and do not suffer from high-temperature decomposition, high-temperature corrosion, or low-temperature solidification, reducing system maintenance costs and safety risks. Furthermore, by constructing a circulating flow loop consisting of an lifting chamber, heating tank, heat storage tank, and heat release tank, and coordinating with combined air conditioning, the static heat exchange mode of solid heat storage is broken. The entire system allows the solid particles to circulate continuously, and fluidized heat exchange is achieved in the heat release tank through fluidized air, increasing the heat transfer coefficient and intensity, thereby achieving efficient and rapid heat storage and release. This solves the problems of low thermal efficiency, bulky equipment, and low power density in traditional systems, resulting in a more compact system structure and higher energy efficiency in heat storage and exchange.

[0049] According to embodiments of this disclosure, the recycled solid particles are at least one of quartz sand, ceramic particles, alumina microspheres, steel slag, and industrial waste.

[0050] According to an embodiment of this disclosure, a gas-solid mixture 15 is fed into the bottom of a lifting chamber 1; the lifting chamber 1 is used to lift the gas-solid mixture at a first temperature to the top of the lifting chamber 1 using fluidizing air fed from the bottom of the lifting chamber 1 and flowing upward, so that a material circulation from bottom to top in the vertical direction is formed in the lifting chamber 1; the heating tank 3, the heat storage tank 4, and the heat release tank 5 are distributed from top to bottom in the vertical direction and connected in sequence, so that the circulating solid particles can pass through the heating tank 3, the heat storage tank 4, and the heat release tank 5 in the vertical direction in sequence under the action of gravity, forming a material circulation from top to bottom in the vertical direction.

[0051] The bottom of the lift chamber 1 is also equipped with a fluidizing air inlet 12 for introducing upward-flowing lifting fluidizing air. The bottom of the lift chamber 1 also includes an air chamber 13. Fluidizing air with a certain pressure and velocity, supplied from an external air source (such as a fan), first enters the air chamber 13 through the fluidizing air inlet 12. Through its specific volume and structure, the air chamber 13 can make the velocity and pressure fields of the incoming airflow more uniform and stable, eliminating or reducing airflow pulsations from the ductwork.

[0052] According to an embodiment of this disclosure, a first air distribution device is provided at the bottom of the lifting chamber 1, the air supply direction of the first air distribution device is vertically upward, and the air chamber 13 of the first air distribution device is connected to the outlet 12 of the circulating fan; a second air distribution device is provided at the bottom of the heat release tank 5, the air supply direction of the second air distribution device is vertically upward, and the air chamber 51 of the second air distribution device is connected to the outlet 12 of the circulating fan.

[0053] like Figure 1 As shown, the bottom of the lifting chamber 1 is also equipped with a first air distribution device, which consists of a perforated plate, a wind cap, air ducts, and a screen, etc., and is fixedly installed on the upper part of the air chamber 13 to uniformly distribute airflow and support the bed material. If a wind cap is used, the wind caps should be evenly distributed on the air distribution plate, and the spacing between the wind caps should be determined according to the fluidization requirements. If an air duct is used, the air ducts should be reasonably arranged to ensure uniform air delivery. For the screen-type air distribution device, a suitable screen aperture should be selected to ensure that the fluidizing air can pass through while preventing solid particles from leaking down. The small holes, wind caps, air ducts, screens, etc. on the first air distribution device disperse the passing fluidizing air into a large number of fine and uniform airflows, so that the airflow can pass evenly through the entire cross-section of the lifting chamber 1. This avoids local airflow that is too strong or too weak, thereby preventing unstable flow states such as channeling and surging, and ensuring that solid particles can be uniformly and steadily lifted upward to form a stable gas-solid two-phase flow. Before system startup or in non-operational state, the physical structure of the first air distribution device can bear and support the solid particle bed material in the lifting chamber 1 above it, preventing particles from falling into the air chamber 13. The combination of the air chamber 13 and the first air distribution device transforms the original, uneven inlet airflow into a stable, uniformly distributed, vertically upward airflow. This allows the gas-solid mixture 15 at a first temperature from the exothermic tank 5 to be efficiently and controllably lifted to the heating tank 3.

[0054] Thus, the fluidizing air generates a strong upward airflow within the lifting chamber 1, which fully mixes with the incoming gas-solid mixture 15, entraining and lifting the circulating solid particles, forming a rapidly moving gas-solid two-phase flow vertically from bottom to top. This material flow eventually exits from the outlet at the top of the lifting chamber 1, thereby forming a stable and continuous bottom-up material circulation within the lifting chamber 1, providing initial power for the particle circulation of the entire system.

[0055] like Figure 1As shown, the bottom of the exothermic tank 5 is also equipped with a second air distribution device, which can also be a perforated plate, air cap, air duct, screen, etc., fixedly installed on the upper part of its lower air chamber 51, for uniformly distributing airflow and supporting the bed material. The second air distribution device makes its fluidizing air fully mixed with the circulating solid particles at the third temperature after exothermic cooling, forming a uniform, fluidized gas-solid mixture 15 at the first temperature.

[0056] The heating tank 3, heat storage tank 4, and heat release tank 5 are arranged vertically from top to bottom. Specifically, as shown... Figure 1 As shown, the heating tank 3 is located at the highest point, and its bottom outlet is connected to the top inlet of the heat storage tank 4 located below it via a pipe; similarly, the bottom outlet of the heat storage tank 4 is connected to the top inlet of the heat release tank 5 located below it via a pipe. This physical layout utilizes the gravity of the particles themselves, allowing the circulating solid particles that have entered the heating tank 3 from the lifting chamber 1 and completed heating to the second temperature to automatically and sequentially flow from the heating tank 3 into the heat storage tank 4, and then from the heat storage tank 4 into the heat release tank 5, without the need for additional mechanical conveying equipment. This process forms a stable and energy-efficient top-down gravity-driven material circulation between the heating tank, the heat storage tank, and the heat release tank.

[0057] According to embodiments of this disclosure, the lifting chamber 1 is a fluidized bed; the heating tank 3 is a moving bed; and the exothermic tank 5 is a bubbling bed.

[0058] The lifting chamber 1 uses a fluidized bed to achieve dynamic lifting of solid particles in the lifting chamber 1, low-temperature storage, and preheating of supplementary materials using the system's waste heat.

[0059] Heating tank 3 uses a moving bed, which can effectively reduce heat exchange losses because the moving bed does not require fluidizing air.

[0060] The heat exchange tank 5 uses a bubbling bed, which has a high heat exchange efficiency, much higher than that of a moving bed. Therefore, using a bubbling bed at the heat exchange end can enhance heat exchange.

[0061] The fluidized bed can provide circulating power. The lifting chamber 1 introduces fluidized air through the fluidized air inlet 12 at the bottom. The powerful airflow generated by the fluidized air provides stable and controllable power for conveying solid particles with gravity in the vertical upward direction.

[0062] The fluidized bed can serve as a buffer and storage unit. The lifting chamber 1 itself has a certain volume, which can receive the solid material provided during the initial feeding, as well as the supplementary feeding during the circulation process. It can also store the solid material in the gas-solid mixture 15 output from the exothermic tank 5. As a buffer container, it balances the fluctuations in material flow between the preceding and following processes and enhances the stability of the system operation.

[0063] The fluidized bed can preheat cold materials initially. The gas-solid mixture 15 entering the lifting chamber has a first temperature of 300~400℃, and newly added room-temperature materials also enter through this chamber. The intense heat exchange within the fluidized bed utilizes the residual heat of the circulating particles at the first temperature to effectively preheat the newly added room-temperature materials. This not only recovers low-temperature waste heat and improves system efficiency, but also avoids problems such as thermal stress that may be caused by room-temperature materials directly entering high-temperature equipment.

[0064] Figure 2A A schematic diagram of the structure of a heating tank according to a first embodiment of the present disclosure is shown. Figure 2B A schematic diagram of the structure of a heating tank according to a second embodiment of the present disclosure is shown. Figure 2C A schematic diagram of the structure of a heating tank according to a third embodiment of the present disclosure is shown.

[0065] like Figure 2A , Figure 2B , Figure 2C As shown, the heating tank 3 in this embodiment includes a flue gas heating unit 31 and / or an electric heating unit 32; the flue gas heating unit uses high-temperature flue gas or high-temperature waste gas from the boiler furnace outside the system as a heat source.

[0066] Specifically, such as Figure 2A As shown, when the heating tank 3 only includes a flue gas heating unit, the system inputs the high-temperature flue gas 311 (800-1000℃) from the boiler into the heating tank 3. The heat contained in the flue gas is transferred to the circulating solid particles, providing basic heating to the solid particles. The low-temperature flue gas is discharged from the outlet 312. Although this method may not be able to heat the particles to the highest ideal temperature, it maximizes the recovery of high-temperature flue gas heat, reduces the operating cost of the heat storage process, and is suitable for applications where peak temperature requirements are not extremely stringent. The tail flue gas 311 can be taken from the boiler furnace, the boiler tail flue, or the furnace and tail flue, as well as industrial high-temperature heat source gases.

[0067] Specifically, such as Figure 2B As shown, when the heating tank 3 only includes an electric heating unit, the system heats the circulating solid particles in the heating tank 3 through an external power source. This configuration facilitates precise temperature control and the direct absorption of renewable energy power. The power source 321 can quickly and precisely heat the solid particles to a high temperature target such as 900~1000℃, ensuring the temperature of the heat storage medium. This is suitable for low-cost charging during off-peak electricity hours or when wind and solar power generation is excessive, or as the main heat source for systems lacking a stable high-temperature industrial waste gas heat source. The power source 321 is derived from off-peak electricity or zero-price electricity. Heating elements such as resistance heating wires or electromagnetic induction heating elements can be used, evenly distributed inside the heating tank 3.

[0068] According to embodiments of this disclosure, the heating tank 3 may further include a flue gas heating unit 31 and an electric heating unit 32. Specifically, as Figure 2C As shown, when the heating tank 3 includes both a flue gas heating unit 31 and an electric heating unit 32: the flue gas heating unit 31 is used to heat the circulating solid particles at a first temperature using the high-temperature flue gas 311 from the furnace, resulting in circulating solid particles at an intermediate temperature; the electric heating unit 32 is used to further heat the circulating solid particles at the intermediate temperature, resulting in circulating solid particles at a second temperature. Specifically, in the case where the heating tank 3 includes both a flue gas heating unit 31 and an electric heating unit 32, under this configuration, the high-temperature flue gas 311 from the boiler furnace first serves as the basic heat source, heating the circulating solid particles at the first temperature (250-350°C) in the first stage, raising their temperature to 600-700°C, thereby storing the heat from the flue gas in the solid particles. Further, the electric heating unit 321 performs a second stage of precise temperature increase, heating the solid particles at 600-700°C to a second temperature, i.e., 900-1000°C. Therefore, this method effectively recovers heat from high-temperature flue gas, utilizes electricity to ensure the achievement of the final temperature target and the stability and controllability of the system, and significantly saves energy consumption and operating costs by reducing the load on electric heating, thus improving the overall energy utilization efficiency. Using flue gas alone as a heat source is insufficient to directly heat solid particles to a high temperature of 900-1000℃ to ensure that water is heated to superheated steam in the subsequent heat release stage. By coupling flue gas and electric heating, the problem of low flue gas heating temperature can be solved. Simultaneously, the problem of low energy utilization efficiency of pure electric heating can be addressed.

[0069] This two-stage moving bed heating method first uses the high-temperature flue gas 311 in the furnace to heat the solid particles to an intermediate temperature, and then uses electricity to heat them to a second temperature. This overcomes the problems of low solid particle temperature when heating with pure flue gas and low efficiency of pure electric heating systems, while reducing gas heat loss and achieving ultra-high temperature heat storage of solid particles.

[0070] Figure 3A and Figure 3B A schematic diagram of the structure of an exothermic tank according to an embodiment of the present disclosure is shown.

[0071] like Figure 3A and Figure 3B As shown, the exothermic tank 5 includes a preheating chamber 51, an evaporation chamber 52, and a superheating chamber 53. Water supplied from outside the system flows through the preheating chamber 51 to obtain preheated water. The preheated water flows through the evaporation chamber 52 to obtain saturated water vapor. The saturated water vapor flows through the superheating chamber 53 to obtain superheated steam.

[0072] Low-temperature water (feedwater) supplied from outside the system first enters the preheating chamber 51. The water flows through heat exchange tubes immersed in a bed of solid particles, absorbing heat from the particles and raising its temperature to near saturation, becoming preheated water. This preheated water then enters the evaporation chamber 52, where it absorbs a large amount of latent heat of phase change at a constant temperature, completely transforming into saturated steam. Finally, the generated saturated steam flows into the superheating chamber 53, where it further exchanges heat with the hottest solid particles, absorbing sensible heat and ultimately being heated into parameter-stable superheated steam. This superheated steam is then directly output outside the system for use in scenarios such as centralized heating systems or industrial process equipment.

[0073] This continuous design of preheating, evaporation, and superheating allows the low-temperature feedwater to exchange heat with relatively low-temperature particles in the preheating chamber, while the nearly completed steam exchanges heat with the hottest particles in the superheating chamber, improving the overall heat exchange efficiency of the system. Simultaneously, by coupling with external energy systems, industrial waste heat that might otherwise be wasted is transformed into a stable and reliable heat supply.

[0074] According to embodiments of this disclosure, there are various ways to connect the inlets of the preheating chamber 51, the evaporation chamber 52, and the superheating chamber 53. For example... Figure 3A As shown, the inlets of the preheating chamber 51, evaporation chamber 52, and superheating chamber 53 are connected in parallel to the outlet of the heat storage tank 4, so that the preheating chamber 51, evaporation chamber 52, and superheating chamber 53 simultaneously receive circulating solid particles at a second temperature; or, as shown... Figure 3B As shown, the inlet of the preheating chamber 51 is connected to the outlet of the heat storage tank 4, and the preheating chamber 51, the evaporation chamber 52, and the superheating chamber 53 are connected in series in sequence, so that the circulating solid particles at the second temperature pass through the preheating chamber 51, the evaporation chamber 52, and the superheating chamber 53 in sequence.

[0075] like Figure 3A As shown, the inlets of the preheating chamber 51, evaporation chamber 52, and superheating chamber 53 are connected in parallel to the outlet of the heat storage tank 4. High-temperature circulating solid particles with a second temperature (900-1000℃) flowing out of the heat storage tank 4 are simultaneously and in parallel distributed to the three chambers. This ensures that the high-temperature circulating solid particles maintain their highest temperature. Both the preheating chamber, which requires a low-temperature heat source, and the superheating chamber, which requires a high-temperature heat source, directly obtain particles at the highest temperature, thus enabling them to independently and efficiently complete their specific heat exchange tasks. By using corresponding flow valves, the particle flow rate entering each chamber can be precisely controlled to flexibly match the different heat requirements of the water / steam side at different stages, achieving heat load regulation capability.

[0076] like Figure 3BAs shown, the preheating chamber 51, evaporation chamber 52, and superheating chamber 53 are connected in series. High-temperature circulating solid particles (900-1000℃) flowing from the heat storage tank 4 first enter the preheating chamber 51, where they exchange heat with the low-temperature feedwater input from outside the system, preheating them. After preheating, the particle temperature naturally decreases, and the particles, maintaining a medium-to-high temperature, flow into the evaporation chamber 52, providing a large amount of latent heat required for water evaporation. The particles that have released heat in the evaporation chamber 52 experience a further temperature decrease, but remain above the saturation temperature, and then enter the superheating chamber 53, using their remaining heat to heat the saturated steam into the final superheated steam. Thus, the temperature difference between the heat source (particles) and the cold source (water / steam) remains within a relatively reasonable and small range, thereby reducing heat loss during the heat transfer process.

[0077] Each heat exchange chamber has an independent air chamber 511, 521, or 531 at its bottom, which can be designed as rectangular or circular. The volume of the air chamber is calculated based on the required fluidizing air volume. The air inlet at the bottom of the air chamber is connected to an air inlet pipe, and the air volume is controlled by adjusting the valve on the air inlet pipe. The air cap or air distribution device at the top of the air chamber has an opening ratio and aperture that ensures the fluidizing air enters the heat exchange chamber uniformly, allowing the solid particles to form a good bubbling fluidization state within the heat exchange chamber. A return pipe is located in the upper part of each heat exchange chamber, and its diameter is designed according to the solid particle flow rate and velocity. The inclination angle of the return pipe is set between 45 and 60 degrees to ensure that the solid particles can smoothly return to the lower part of the lifting chamber to participate in circulation.

[0078] Figure 4 The schematic diagram illustrates the structure of a fluidized thermal storage and release system based on solid particles according to a second embodiment of the present disclosure.

[0079] like Figure 4 As shown, the fluidized thermal storage and release system based on solid particles also includes a separator 2, which is located between the lifting chamber 1 and the heating tank 3, for gas-solid separation of the gas-solid mixture 15 to obtain circulating gas at a first temperature and circulating solid particles at a first temperature, and feeding the circulating solid particles at the first temperature into the heating tank 3 through the solid phase outlet of the separator.

[0080] Figure 5 The schematic diagram illustrates the structure of a fluidized thermal storage and release system based on solid particles according to a third embodiment of the present disclosure.

[0081] like Figure 5As shown, the fluidized thermal storage and release system based on solid particles also includes a cold particle heater 6, which is used to receive supplementary solid particles 11 at an initial temperature supplied from outside the system, and preheat the supplementary solid particles 11 at the initial temperature using circulating gas at a first temperature from the gas phase outlet of the separator, to obtain supplementary solid particles 11 at a fourth temperature, which are then fed into the lift chamber 1; the initial temperature is consistent with the ambient temperature outside the system; the numerical range of the fourth temperature is 50-100℃.

[0082] The cold particle heater 6 may have a solid particle inlet 611 for receiving supplementary solid particles 11 supplied from outside the system at an initial temperature, typically consistent with the ambient temperature outside the system, i.e., room temperature, for example, 20~30°C. Thus, the source of solid particles in the lifting chamber 1 can be either supplementary solid particles 11 at 20~30°C supplied through the solid particle inlet 611 of the cold particle heater 6, or a gas-solid mixture 15 at a first temperature output from the outlet of the exothermic tank 5. After the supplementary solid particles 11 are mixed with the gas-solid mixture 15 at the first temperature, they are lifted to the top of the lifting chamber 1 by fluidizing air within the lifting chamber 1 and conveyed to the inlet of the separator 2 or the heating tank 3. The outlet of the cold particle heater 6 is connected to at least one inlet of the lifting chamber 1 via a pipe, and a third control valve 61 is installed on the pipe to control the feed rate of the supplementary solid particles 11. The third control valve 61 may be an electrically operated regulating valve.

[0083] Figure 6 A schematic diagram of the structure of a fluidized thermal storage and release system based on solid particles according to a fourth embodiment of the present disclosure is shown.

[0084] like Figure 6 As shown, the solid particle-based heat storage and release system further includes: the gas outlet 21 of the separator 2 is connected to the gas inlet of the circulating fan 7 via a pipeline, and a fourth control valve 27 is installed on the pipeline, wherein the fourth control valve 27 can be an electrically operated regulating valve. After the separator 2 separates the gas-solid mixture 15 at the first temperature, it obtains circulating solid particles and circulating gas. The circulating solid particles fall into the heating tank 3 due to gravity, and the circulating gas is input to the circulating fan 7 through the gas outlet 21 of the separator 2 to lift the particles in the lifting chamber 1 or the heat release tank 5.

[0085] According to an embodiment of this disclosure, the circulating fan 7 is used to introduce circulating gas at a fifth temperature as fluidizing air into the lift chamber 1 and the heat release tank 5.

[0086] Figure 7 A schematic diagram of a fluidized thermal storage and release system based on solid particles according to a fifth embodiment of the present disclosure is shown.

[0087] like Figure 7 As shown, the fluidized thermal storage and release system based on solid particles further includes: after the circulating gas at the first temperature exchanges heat with the supplementary solid particles at the initial temperature to cool down, a circulating gas at the fifth temperature is obtained; the numerical range of the fifth temperature is 150-250℃.

[0088] The cold particle heater 6 also has a hot gas inlet 621, which is connected to the gas outlet 21 of the separator 2 via a pipe for introducing circulating gas at a first temperature. A fifth control valve 26 is installed on this pipe to control the gas flow rate entering the cold particle heater 6. The fifth control valve 26 can be an electrically operated regulating valve. Inside the cold particle heater 6, the high-temperature circulating gas exchanges heat directly or indirectly with the room-temperature supplementary solid particles 11, transferring the residual heat carried in the circulating gas to the cold particles. After heat exchange, the circulating gas at the first temperature is cooled and is then transported to the circulating fan through the gas outlet 631 of the cold particle heater 6. On one hand, the high-temperature circulating gas preheats the supplementary solid particles from their initial temperature to a fourth temperature; on the other hand, the temperature of the circulating gas is reduced to a fifth temperature through heat exchange before being transported to the circulating fan 7 through the gas outlet 631 of the cold particle heater 6. This process protects the circulating fan by lowering the gas temperature, extending equipment life and reducing system losses. Furthermore, the supplementary solid particles 11, which have been preheated to a fourth temperature, are drawn out from the solid discharge port of the cold particle heater 6 and fed into one of the feed ports of the lifting chamber 1, entering the main circulation system.

[0089] According to embodiments of this disclosure, the numerical range of the first temperature is 250-350℃; the numerical range of the second temperature is 900-1000℃; the numerical range of the third temperature is 300-400℃; the numerical range of the intermediate temperature is 600-700℃; and the numerical range of the high-temperature flue gas in the furnace is 800-1100℃.

[0090] like Figure 7As shown, the entire cycle begins with particles at a third temperature (300-400℃) mixing with fluidizing air in the exothermic tank 5, forming a gas-solid mixture at a first temperature (250-350℃). This temperature ensures the particles have good fluidity and can be smoothly lifted, while the sensible heat they carry is sufficient to effectively preheat the initial temperature supplementary solid particles 11 in the lifting chamber 1. After the gas-solid mixture at the first temperature (250-350℃) enters the heating tank 3, the system first uses the high-temperature flue gas 311 from the boiler furnace at a temperature of 800-1100℃ to heat it in the first stage, lifting the particles to an intermediate temperature (600-700℃). This achieves efficient recovery of heat from the high-temperature flue gas. The electric heating unit 32 heats the particles from the intermediate temperature to a second temperature (900-1000℃) to improve the system's energy storage effect and density, meeting the needs of high-end industrial applications or high-efficiency power generation. Finally, the high-temperature particles transfer heat to the feed water in the heat release tank 5 through heat exchange, and are cooled back to the third temperature (300-400℃), ensuring that the heat release process is sufficient (with enough temperature drop), thus forming a circulating heat storage and release system.

[0091] According to embodiments of this disclosure, the first stage of heating (preheating) involves using waste heat from the system's own low-temperature flue gas within the cold particle heater 6 to preheat the supplementary solid particles, initially at room temperature, to approximately 50-100°C. This facilitates an initial increase in particle temperature and reduces energy consumption for subsequent heating. The second stage of heating (intermediate-temperature heating) involves using the medium-low temperature flue gas from the heat exchange tank 5 within the lifting chamber 1 to further heat the particles to 250-300°C during transport. The third stage of heating (high-temperature heating) involves using high-temperature flue gas from an external boiler within the heating tank 3 as the main heat source to deeply heat the particles to an intermediate temperature of 600-700°C. This fully utilizes high-grade waste heat commonly found in industrial processes, undertaking most of the heating load. The fourth stage of heating (precision temperature increase) involves using electrical energy within the heating tank to heat the particles from the intermediate temperature to a second temperature of 900-1000°C. The precise controllability of electric heating ensures that the required maximum temperature is reached to meet the demands of high-end applications.

[0092] The mechanical and electric control valves in this embodiment enable precise control of the solid particle movement speed, ensuring its residence time within the heating tank. By precisely adjusting the outlet valve of the heating tank, the particle movement speed is flexibly controlled according to the heating requirements of the solid particles and the heat source supply, ensuring that the solid particles absorb sufficient heat to meet ultra-high temperature thermal storage requirements, further improving the stability and reliability of the thermal storage.

[0093] This embodiment uses solid particles as the heat storage medium. During peak periods of green electricity output from wind and solar power, an electric heating unit converts potentially wasted surplus electricity into high-quality heat energy (900-1000°C) stored in the solid particles. When green electricity output is insufficient, the system switches to a heat release mode, utilizing the heat storage particles to efficiently exchange heat with the working medium in the heat release tank, continuously and stably outputting industrial-grade heat sources such as steam or hot air. This smooths out the originally randomly fluctuating green electricity supply into a safe and reliable heat supply that matches user load, solving the supply-demand imbalance caused by the intermittency of green electricity. Simultaneously, by providing the grid with cross-period regulation capabilities, the utilization efficiency of renewable energy is improved.

[0094] The embodiments of this disclosure have been described above. However, these embodiments are for illustrative purposes only and are not intended to limit the scope of this disclosure. Although various embodiments have been described above, this does not mean that the measures in the various embodiments cannot be used advantageously in combination. Various substitutions and modifications can be made by those skilled in the art without departing from the scope of this disclosure, and all such substitutions and modifications should fall within the scope of this disclosure.

Claims

1. A heat storage and release system based on solid particles, characterized in that, The system includes an lifting chamber, a heating tank, a heat storage tank, and a heat release tank; wherein... A lift chamber for lifting a gas-solid mixture originating from a first temperature of the exothermic tank upwards, the gas-solid mixture comprising circulating solid particles and circulating gas; A heating tank is used to heat the first temperature circulating solid particles separated from the gas-solid mixture using an external heat source to obtain second temperature circulating solid particles. Thermal storage tank for receiving and storing solid particles in the second temperature cycle; The exothermic tank is used to heat water supplied from outside the system to obtain superheated steam by utilizing the heat of circulating solid particles at the second temperature. The circulating solid particles at the second temperature release heat to generate circulating solid particles at the third temperature. The circulating solid particles at the third temperature are mixed with fluidizing air introduced into the exothermic tank to obtain a gas-solid mixture at the first temperature, which is then sent into the lifting chamber.

2. The system according to claim 1, characterized in that: The gas-solid mixture is fed into the bottom of the lifting chamber; The lifting chamber is used to lift the gas-solid mixture at the first temperature to the top of the lifting chamber using fluidizing air fed from the bottom of the lifting chamber and flowing upward, so as to form a material circulation from bottom to top in the vertical direction in the lifting chamber; The heating tank, heat storage tank, and heat release tank are distributed vertically from top to bottom and connected in sequence, so that the circulating solid particles can pass through the heating tank, heat storage tank, and heat release tank in sequence in the vertical direction under the action of gravity, forming a material circulation from top to bottom in the vertical direction.

3. The system according to claim 1, characterized in that: The lifting chamber uses a fluidized bed; The heating tank is a movable bed; The exothermic tank uses a bubbling bed.

4. The system according to claim 1, characterized in that: The heating tank includes a flue gas heating unit and / or an electric heating unit; The flue gas heating unit uses the flue gas or waste gas from the boiler furnace outside the system as a heat source.

5. The system according to claim 4, characterized in that, In the case where the heating tank includes a flue gas heating unit and an electric heating unit: The flue gas heating unit is used to heat the circulating solid particles at the first temperature using the flue gas in the furnace to obtain circulating solid particles at an intermediate temperature; the electric heating unit is used to further heat the circulating solid particles at the intermediate temperature to obtain circulating solid particles at the second temperature.

6. The system according to claim 1, characterized in that, The numerical range of the first temperature is 250-350℃; The numerical range of the second temperature is 900-1000℃; The numerical range of the third temperature is 300-400℃; The numerical range of the intermediate temperature is 600-700℃; The temperature range of the flue gas in the furnace is 800-1100℃.

7. The system according to claim 1, characterized in that: The exothermic tank includes a preheating chamber, an evaporation chamber, and a superheating chamber. Water supplied from outside the system flows through the preheating chamber to obtain preheated water, which then flows through the evaporation chamber to obtain saturated water vapor. The saturated water vapor then flows through the heating chamber to obtain superheated steam.

8. The system according to claim 7, characterized in that: The inlets of the preheating chamber, evaporation chamber, and superheating chamber are connected in parallel to the outlet of the heat storage tank, so that the preheating chamber, evaporation chamber, and superheating chamber simultaneously receive circulating solid particles at the second temperature. Alternatively, the inlet of the preheating chamber is connected to the outlet of the heat storage tank, and the preheating chamber, evaporation chamber, and superheating chamber are connected in series in sequence, so that the circulating solid particles at the second temperature pass through the preheating chamber, evaporation chamber, and superheating chamber in sequence.

9. The system according to claim 1, characterized in that, Also includes: A separator, located between the lifting chamber and the heating tank, is used to separate the gas-solid mixture to obtain circulating gas at a first temperature and circulating solid particles at the first temperature, and to feed the circulating solid particles at the first temperature into the heating tank through the solid phase outlet of the separator.

10. The system according to claim 9, characterized in that, Also includes: A cold particle heater is used to receive supplementary solid particles at an initial temperature supplied from outside the system, and to preheat the supplementary solid particles at the initial temperature using circulating gas at a first temperature from the gas phase outlet of the separator, to obtain supplementary solid particles at a fourth temperature, which are then fed into the lifting chamber. The initial temperature is the same as the ambient temperature outside the system. The numerical range of the fourth temperature is 50-100℃.

11. The system according to claim 10, characterized in that: After the circulating gas at the first temperature is cooled down by heat exchange with the supplementary solid particles at the initial temperature, the circulating gas at the fifth temperature is obtained. The numerical range of the fifth temperature is 150-250℃.

12. The system according to claim 11, characterized in that, Also includes: A circulating fan is used to introduce the circulating gas at the fifth temperature as fluidizing air into the lifting chamber and the heat release tank.

13. The system according to claim 12, characterized in that: The bottom of the lifting chamber is provided with a first air distribution device. The air supply direction of the first air distribution device is vertically upward, and the air chamber of the first air distribution device is connected to the outlet of the circulating fan. The bottom of the heat-dissipating tank is provided with a second air distribution device. The air supply direction of the second air distribution device is vertically upward, and the air chamber of the second air distribution device is connected to the outlet of the circulating fan.

14. The system according to claim 1, characterized in that: The recycled solid particles are selected from at least one of the following: quartz sand, ceramic particles, alumina pellets, steel slag, and industrial waste.

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